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EP3123251B1 - Timepiece comprising a turning collar - Google Patents

Timepiece comprising a turning collar Download PDF

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Publication number
EP3123251B1
EP3123251B1 EP15708215.7A EP15708215A EP3123251B1 EP 3123251 B1 EP3123251 B1 EP 3123251B1 EP 15708215 A EP15708215 A EP 15708215A EP 3123251 B1 EP3123251 B1 EP 3123251B1
Authority
EP
European Patent Office
Prior art keywords
flange
crown
timepiece
friction
rotation
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
EP15708215.7A
Other languages
German (de)
French (fr)
Other versions
EP3123251A1 (en
Inventor
Philipp Tschumi
Sébastien Briswalter
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.)
Swatch Group Management Services AG
Original Assignee
Swatch Group Management Services AG
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 Swatch Group Management Services AG filed Critical Swatch Group Management Services AG
Publication of EP3123251A1 publication Critical patent/EP3123251A1/en
Application granted granted Critical
Publication of EP3123251B1 publication Critical patent/EP3123251B1/en
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
    • 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
    • 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
    • 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
    • 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 timepiece provided with a rotating flange.
  • the patent FR1027587 describes for example such a control system by cooperation of teeth of the flange and a crown pinion, where the gear is only possible in a working position pulled from the crown, and a needle mounted on spring acts as an element index for the angular positions of the flange.
  • a drawback of this type of control system is that it requires relatively deep teeth to ensure the engagement between the teeth of the terminal pinion of the crown and the notching of the flange. Consequently, the overall height is quite large and increases the size of the case making it possible to accommodate such a system ensuring the transmission between the rotation of the crown and that of the flange. Furthermore, the mutual cooperation of the two toothings 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 following the actuation of the crown is conditioned by the number of teeth of the terminal pinion of the latter, the diameter of which is generally markedly 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 considerably influences the gear ratios, that is to say the reduction of the angular travel of the flange in relation to to that of the crown.
  • the document CH691199 discloses for example a control ring arranged to actuate, in a predefined axial working position, in rotation a rod provided with a terminal knob devoid of teeth cooperating by friction with a peripheral bead of a timer wheel, and consequently all the timer cog when setting the time.
  • An aim of the present invention is consequently to propose an alternative solution for a control system, in particular of a flange, and more generally of a rotating member for a timepiece, devoid of these known limitations.
  • the invention relates to a timepiece as defined in independent claim 1.
  • Preferred embodiments are defined in the dependent claims.
  • a first advantage of the proposed solution is that it gives a significant gain in overall height thanks to the flattened profile of the running surface of the driving wheel set or of the driven wheel body 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 confers a silent character of the gear mechanism thanks to the drive roller made of elastomeric material, the flexibility of which avoids jolts and rattling noise of the gear, unlike mutual cooperation. teeth of the moving and driven moving parts of a solution known from the prior art.
  • Yet another advantage of the proposed solution is that it allows a reduction in costs thanks to the economy both of the complex machining of a toothing of a small-diameter mobile, such as typically a drive pinion, and saving in material thanks to the flattening of the drive notches, typically on a driven mobile of larger diameter.
  • Yet another advantage of the proposed solution is that it facilitates the mutual positioning of the control member and the rotating member, in particular in a housing, since the elastic properties of the drive roller made of elastomeric material make it possible to recover positioning clearances for the respective axes of the driving and driven movable elements involved in the proposed gear device.
  • a roller is a part traditionally formed by a steel roller, and which aims to replace sliding friction by rolling friction (see GA Illustrated Professional Dictionary of Watchmaking. Berner, p.518, reference 2221 ). Reference will therefore be made, in the context of the present application, by extension to a drive roller for a part intended to transmit a rotational movement by rolling friction with another moving part.
  • the figures 1A, 1B and 1C respectively show a top view, in section and in three dimensions of a middle part 5 intended to receive the control system according to the invention, formed by a crown 1 and a flange 3, illustrated on figures 2A, B, C and 3A, B, C that follow.
  • the middle 5 comprises two pairs of strap attachment horns 53, as well as a bearing surface 50 forming a bearing surface for the rotating flange 3.
  • a first threaded through hole 51 and a second threaded through hole 52 are drilled in the middle part, preferably for mounting crown tubes.
  • At the level of each of these threaded holes are respectively arranged a first notch 501 and a second notch 502, visible on the figure 1A .
  • These notches make it possible to pass a key for mounting or changing various constituent elements of the crown 1 assembled to the middle 5 during after-sales service, and in particular drive roller 25 on its axis.
  • the figure 1B shows a sectional view of the middle 5 along the first cutting axis BB of the figure 1A , passing through the first threaded through hole 51, on which we can see the thickness of the seat 50, while on the figure 1C we distinguish the same elements as on the figure 1A , except for the first and second indentations 501,502.
  • the figure 2A shows a top view of the flange 3 intended to be mounted on the middle 5 of the figures 1A, 1B, and 1C previous ones, on which we can distinguish its upper face, consisting of an oblique display surface 34, here devoid of display elements, but which can be discerned later on the figure 4 , as well as the upper surface 371 of a peripheral rim 37, intended to provide a bearing surface for an annular element disposed at its periphery.
  • the figure 2B shows flange 3 along the second cutting axis CC of the figure 2A , and highlights the peripheral rim 37, and the upper surface 371 as well as the lower surface 372 thereof, the oblique display surface 34, but above all the rolling teeth 32 which cooperates with the drive roller 25 , visible on figures 3A, 3B and 3C following the crown.
  • This rolling toothing 32 aimed at transmitting the rotational movement of the crown 1 when the latter is actuated by the user of the watch, extends along an annular lower face of the flange 3, and it is possible to note that this rolling toothing 32 is located in a gear plane 35 perpendicular to the second axis of rotation 30 of the flange 3.
  • This rolling toothing 32 is preferably formed by a flat toothing, as illustrated later on figure 5 , but one could consider using, as an alternative, another type of rolling surface such as knurling or even a material having sufficient roughness to guarantee the transmission of the roller bearing. drive 25 avoiding any slippage.
  • the figure 2C illustrates the same components of flange 3 as the figure 2A described above, namely the oblique display surface 34, as well as the peripheral rim 37 and its upper surface 371.
  • the figure 3A illustrates a profile view of a crown 1 according to a preferred embodiment of the invention.
  • this is an unscrewed crown having only one axial position relative to the caseband, it will be understood that the hybrid gear system as well as the arrangement of a drive roller 25 on a crown is independent of the crown structure employed, and that thus a crown of the screwed type could quite well also be used without departing from the scope of the invention nor imposing structural limits on the hybrid gear mechanism proposed between the roller d 'drive 25 and the rolling teeth 32 of the flange 3.
  • the crown 1, movable around 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 11 operable by the watch user.
  • the drive roller 25 At the level of the proximal end of the crown, to the left of the figures 3A, 3B, and 3B , is arranged the drive roller 25, in the form of a first O-ring type O-ring or an overmolded seal.
  • the advantage of using an O-ring type seal is to be able to use the drive roller 25 as a wearing part, replaceable independently of the rest of the ring 1.
  • the drive roller 25 is made of precisely elastomeric material. to increase frictional forces and improve the quality of rolling transmission, much like a vehicle tire on a road surface.
  • a friction ring 14 which is in the form of a second preferably section seal rectangular in order to maximize the friction surface with each part.
  • the friction surfaces are then present in an annular shape in each of the friction planes.
  • This friction ring 14 aims to increase the torque for setting the flange 3 in rotation and thus eliminate the parasitic and involuntary movements of the flange 3 during handling of the crown 1.
  • the crown 1 is not a screwed crown
  • a friction ring 14 is particularly advantageous for a screwed crown having several axial positions, in particular during the transition from a locked or screwed position "T0" to a pulled or unscrewed position "T1" of setting.
  • the advantage of a screw-down crown would consist in blocking the rotation of the flange 3 on demand and by screwing in, in order to avoid any accidental displacement thereof. This is essential for safety reasons, since time-critical indications for a dive, such as for example a time remaining before performing a decompression stop, must not be able to be modified under any circumstances.
  • the friction ring 14 remains in this case essential to prevent any accidental rotation of the flange 3 precisely during unscrewing operations, and especially when screwing the crown 1 back on.
  • the figure 3B shows a sectional view along the third cutting axis AA of the figure 3A , where we can see, in addition to the other elements already described on the figure 3A , a central cylinder 12 threaded to be connected to a control rod, as well as the axial skirt 111 and the cover 112 of the cover 11.
  • a central cylinder 12 threaded to be connected to a control rod, as well as the axial skirt 111 and the cover 112 of the cover 11.
  • a third seal 16 also of O-ring shape, covered by a deckring 15.
  • the third O-ring 16 is also maintained axially using a spacer 17.
  • the elements of the crown 1 illustrated are similar to those already described in view of the figure 3A , that is to say the drive roller 25, the friction ring 14 and the tube 13; nevertheless, we can distinguish an "H" logo on the external face 113 of the cover 11, and better visualize the knurling on the periphery of the axial skirt 111 of the cover 11, provided to facilitate the gripping and handling of the crown by the user.
  • the figure 4 shows a sectional view of the detail of the control mechanism according to the preferred embodiment of the invention, where the flange 3 and the control ring 1 illustrated separately by the figures 2 and 3 previous ones are now integrated into the middle 5 of a watch.
  • the hybrid gear device of the proposed rotary member control system relates to the transmission of a rotational movement between a first movable member and a second movable member about their respective axis of rotation by means of 'a gear by rolling friction between the two moving parts, one being equipped on 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 teeth.
  • the gear used in the context of the present invention is thus qualified 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 make surfaces of a different nature, such as a notch, a knurling and or even a rough surface with a smooth surface, such as that of the drive roller 25.
  • surfaces of a different nature such as a notch, a knurling and or even a rough surface with a smooth surface, such as that of the drive roller 25.
  • the cooperation of elements of a different nature that is to say of which the materials and surface profiles are heterogeneous, is unusual for a traditional watchmaking gear transmission mechanism where in general the metal teeth of a first mobile are provided to cooperate with another metal teeth of another mobile.
  • no toothing is ever used as a running surface either.
  • the second movable element 31 can be considered as the body of the flange 3, referenced on the figure 4 , while the flange 3 here further comprises a Teflon washer 33 arranged above its peripheral rim 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 crown 1, also integral in rotation with the cover 11 of the crown 1 following the screwing of its part. upper thread 21 in the threaded blind hole 121 of the central cylinder 12.
  • the drive 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.
  • such an arrangement of the drive roller 25 of elastomeric material is advantageous over the drive member to improve the efficiency of transmission as well as to reduce production costs, in particular 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 clearly less than the circumference of the driven element, like the flange 3, which makes it possible to save elastomeric material, and also simplifies the machining of the movable element 31 as well as of the central barrel 2.
  • the ratio of the circumferences of the driving element relative to the driven element makes it possible to define a continuous gear ratio, unlike a ratio between the numbers of teeth between a mobile leading and a driven mobile, which is a function of discrete values.
  • the proposed solution also dispenses with a very precise positioning of the relative mutual axes of rotation of the parts, also often called “center distance”, these positioning clearances being able to be recovered thanks to the plastic properties of the elastomer drive roller 25 which will then be more or less compressed against the running surface of the mobile to be driven in rotation.
  • the assembly of the control device is thus simplified, which allows additional productivity gains.
  • the control crown 1 is a crown having only one axial position vis-à-vis the middle part, which comprises a cover 11 projecting out of the middle part 5 and which can be actuated in rotation by the user of the watch.
  • a screw-down crown could however be used within the framework of the invention without this affecting the particular transmission device proposed.
  • the cover 11 is mounted above a tube 13, here provided with a thread 131 for its assembly by screwing to the middle 5 in the first threaded through hole 51 in which is inserted a central cylinder 12 integral with the cover 11, 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 part 21.
  • the central barrel 2 thus forms a first movable element of the control member what constitutes crown 1; it is movable in rotation with respect to the tube 13 screwed to the middle part 5 and it is at its proximal end, that is to say the tapped lower part 23 for the possible addition of a control rod - not shown - that is arranged the drive roller 25 of elastomeric material, replacing an end pinion as on traditional crowns.
  • the drive roller 25 formed here by a first O-ring which is arranged in a groove delimited by two axial stops 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 may be integral with the central barrel 2 or consist of washers mounted on the latter.
  • a second seal 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 on the 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 in order to increase the actuation torque of the crown 1, is thus to avoid imposing any parasitic movement on the flange 3.
  • the ring friction 14 is here maintained axially between the shoulder 22 of the central barrel 2, which can also be formed by a washer, possibly even the other side of the washer used as an axial stop 24 for the drive roller 25, and the the lower end 132 of the tube 13 screwed to the middle part 5.
  • this friction ring allows therefore to make it more difficult to activate the crown 1 in rotation, and therefore more effectively secures the angular position of the flange 3.
  • this friction ring 14 is interposed e between the tube 13 and a part of the central barrel 2, here the shoulder 22, so that the friction is arranged in planes perpendicular to the first axis of rotation 10 of the crown 1. This type of friction can be qualified as axial friction.
  • a friction ring 14 directly inside the tube 13 of the crown, in a groove arranged directly on the central barrel 2, so that the friction is no longer axial, but radials.
  • the advantage of using an axial friction ring 14, like the one shown in figure 4 is that it makes it possible to dispense with substantial wall thicknesses in order to be able to arrange therein a sufficiently deep groove and to house the friction element therein. It is thus compatible with crown tubes having parts terminals of reduced diameter, and with a low wall below the threaded part for assembly to the caseband, such as that of the tube 13 shown, which makes it possible in particular to center, if necessary, a casing circle for the movement.
  • the protruding part of the crown 1 outside the middle 5 shows an enlarged view of the detail of the elements illustrated on figure 3B , namely a threaded central cylinder 12 connected to the central barrel 2, the axial skirt 111 and the cover 112 of the bonnet, as well as the sealing elements of the crown head vis-à-vis the inside of the middle part, that is to say a third O-ring 16, covered by a deckring 15, and moreover maintained axially by means of a spacer 17.
  • These elements however have no influence on the gear mechanism hybrid proposed in the context of the present invention, and in particular on the arrangement of the drive roller 25.
  • the drive roller 25 of elastomeric material cooperates with a rolling toothing 32 arranged on the underside of a flange body 3.
  • 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 teeth 32, partially covering the edge of the dial 4, and which is provided with a peripheral rim 37 annular on which is mounted a Teflon washer 33 in order to minimize friction with the bezel 6, which is also covered with the crystal 7 and mounted in a notch on the caseband 5.
  • a seal formed by a fourth O-ring 61 is arranged between the bezel 6 and the middle 5, and similarly, a fifth O-ring 81 is interposed between the bottom 8 and the middle 5.
  • the rolling teeth 32 extend essentially in a parallel gear plane. to the first axis of rotation 10 of the crown 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 reference without requiring the use of inclined teeth to save space in height.
  • a hybrid gear device comprising an oblique rolling toothing 32, in particular at 45 degrees relative to the axis of rotation of the driven or driving body, to effect a 90-degree return, or even arrange a rolling toothing 32 extending no longer in a plane but in a cylindrical portion at the periphery of a mobile cooperating with a mobile rotating about a parallel axis, in order to ensure the transmission in rotation to a second mobile rotating about a parallel axis of rotation.
  • the figure 5 shows the detail of a rolling toothing 32 according to a preferred embodiment, where it is arranged on the underside of the second mobile 31 of the flange and extends along an annular surface located in a plane perpendicular to the second axis rotation 30, i.e. the gear plane 35, referenced on the figure 3B .
  • the rolling teeth 32 is formed here of a flat toothing 36, the tooth profile of which is greater than 90 degrees, and preferably between 100 and 130 degrees, here 120 degrees on the figure 5 .
  • Such a profile would not be suitable for a mutual gearing of toothings on adjacent moving parts because of the risk of slipping, but is perfectly suited here to limit the bulk and guarantee the transmission of the rotation by rolling of the drive roller 25 in elastomeric material, slightly compressed in the hollows of this flat toothing 36.
  • a knurling formed for example by oblique ridges extending in a single direction or two symmetrically opposite directions, the difference with the flat teeth corresponding to a shallower depth of the indentations formed on the rolling teeth 32, thus allowing a slight additional gain in height.
  • the depth of the toothings or indentations will preferably not exceed a quarter of a millimeter (i.e. 0.25mm), and depending on 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)

Description

La présente invention concerne une pièce d'horlogerie munie d'un réhaut tournant.The present invention relates to a timepiece provided with a rotating flange.

Dans le domaine de l'horlogerie, on connaît depuis longtemps les réhauts, qui consistent en une pièce annulaire disposée en périphérie d'un cadran, et qui recouvrent partiellement le bord de ce dernier. Ils peuvent être solidaires ou non d'une lunette à laquelle est ajustée la glace de la montre. Certains réhauts sont mobiles en rotation indépendamment de la lunette, et situés intégralement sous la glace. Pour commander de tels réhauts tournants, le système de commande le plus usuel consiste à utiliser une couronne pourvue d'un pignon terminal à son extrémité, qui engrène avec un crantage agencé sur une surface inférieure du réhaut pour entraîner ce dernier en rotation. Le brevet FR1027587 décrit par exemple un tel système de commande par coopération de dentures du réhaut et d'un pignon de couronne, où l'engrenage n'est possible que dans une position de travail tirée de la couronne, et un pointeau monté sur ressort agit comme élément d'indexation pour les positions angulaires du réhaut.In the field of watchmaking, highlights have long been known, which consist of an annular part arranged at the periphery of a dial, and which partially cover the edge of the latter. They may or may not be integral with a bezel to which the watch crystal is fitted. Some flanges are movable in rotation independently of the bezel, and located entirely under the glass. To control such rotary flanges, the most common control system consists of using a ring gear provided with an end pinion 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 describes for example such a control system by cooperation of teeth of the flange and a crown pinion, where the gear is only possible in a working position pulled from the crown, and a needle mounted on spring acts as an element index for the angular positions of the flange.

Un inconvénient de ce type de système de commande est qu'il requiert une denture relativement profonde pour assurer l'encliquetage entre la denture du pignon terminal de la couronne et le crantage du réhaut. Par conséquent, l'encombrement en hauteur est assez important et augmente la taille du boîtier permettant de loger un tel système assurant la transmission entre la rotation de la couronne et celle du réhaut. Par ailleurs, la coopération mutuelle des deux dentures impliquées dans le mécanisme d'engrenage rend ce système de transmission d'une part assez bruyant, et d'autre part relativement malcommode pour des réglage fins. En effet, la l'indexation angulaire du réhaut suite à l'actionnement de la couronne est conditionnée par le nombre de dents du pignon terminal de cette dernière, dont le diamètre est en général nettement inférieur à celui du réhaut. Or il est difficile d'usiner un grand nombre de dents sur une pièce de petite taille, et le nombre de dents de cette pièce influence considérablement les rapports d'engrenage, c'est à dire la démultiplication de la course angulaire du réhaut par rapport à celle de la couronne.A drawback of this type of control system is that it requires relatively deep teeth to ensure the engagement between the teeth of the terminal pinion of the crown and the notching of the flange. Consequently, the overall height is quite large and increases the size of the case making it possible to accommodate such a system ensuring the transmission between the rotation of the crown and that of the flange. Furthermore, the mutual cooperation of the two toothings 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 following the actuation of the crown is conditioned by the number of teeth of the terminal pinion of the latter, the diameter of which is generally markedly 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 considerably influences the gear ratios, that is to say the reduction of the angular travel of the flange in relation to to that of the crown.

Pour l'engrenage d'autres type de pièces d'horlogerie, notamment à bas coûts, on connaît par ailleurs des mécanismes d'entraînement par friction. Le document CH691199 divulgue par exemple une couronne de commande agencée pour actionner, dans une position de travail axiale prédéfinie, en rotation une tige pourvue d'un pommeau terminal dépourvu de dents coopérant par friction avec un bourrelet périphérique d'une roue de minuterie, et par suite tout le rouage de minuterie lors d'une remise à l'heure.For the gearing of other types of timepieces, in particular at low cost, friction drive mechanisms are also known. The document CH691199 discloses for example a control ring arranged to actuate, in a predefined axial working position, in rotation a rod provided with a terminal knob devoid of teeth cooperating by friction with a peripheral bead of a timer wheel, and consequently all the timer cog when setting the time.

L'inconvénient de ce type d'engrenage est qu'il présente toutefois un degré de fiabilité moindre, et un moins bon rendement de transmission en rotation, notamment sur la durée en raison de l'abrasion progressive des surfaces de contact des pièces d'engrenage. Cette détérioration des surfaces résulte en une diminution de l'intensité des forces de friction et provoque, à terme, de forts glissements mutuels plutôt qu'une transmission de roulement entre les pièces d'engrenageThe drawback of this type of gear is that it has, however, a lower degree of reliability, and a poorer transmission efficiency in rotation, in particular over time due to the progressive abrasion of the contact surfaces of the parts of the gear. gear. This deterioration of the surfaces results in a decrease in the intensity of the frictional forces and ultimately causes strong mutual slippage rather than a rolling transmission between the gear parts.

On connaît aussi le document JP201039460 , qui décrit une pièce d'horlogerie selon le préambule de la revendication 1 annéxée.We also know the document JP201039460 , which describes a timepiece according to the preamble of appended claim 1.

Un but de la présente invention est par conséquent de proposer une solution alternative pour un système de commande, notamment d'un réhaut, et plus généralement d'un organe tournant pour pièce d'horlogerie, dépourvue de ces limitations connues.An aim of the present invention is consequently to propose an alternative solution for a control system, in particular of a flange, and more generally of a rotating member for a timepiece, devoid of these known limitations.

A cet effet, l'invention a pour objet une pièce d'horlogerie telle que définie dans la revendication indépendante 1. Des réalisations préférées sont définies dans les revendications dépendantes.To this end, the invention relates to a timepiece as defined in independent claim 1. Preferred embodiments are defined in the dependent claims.

Un premier avantage de la solution proposée est de conférer un gain significatif d'encombrement en hauteur grâce au profil aplati de la surface de roulement du mobile menant ou du mobile mené du dispositif d'engrenage hybride décrit, sans toutefois diminuer la qualité de la transmission ni sa fiabilité sur la durée.A first advantage of the proposed solution is that it gives a significant gain in overall height thanks to the flattened profile of the running surface of the driving wheel set or of the driven wheel body of the hybrid gear device described, without however reducing the quality of the transmission. nor its reliability over time.

Un autre avantage de la solution proposée est qu'elle confère un caractère silencieux mécanisme d'engrenage grâce au galet d'entraînement en matériau élastomère, dont la souplesse évite tout à-coups et bruit de cliquetis d'engrenage, contrairement à la coopération mutuelle de dentures des mobiles menant et mené d'une solution connue de l'art antérieur.Another advantage of the proposed solution is that it confers a silent character of the gear mechanism thanks to the drive roller made of elastomeric material, the flexibility of which avoids jolts and rattling noise of the gear, unlike mutual cooperation. teeth of the moving and driven moving parts of a solution known from the prior art.

Encore un autre avantage de la solution proposée est qu'elle permet une réduction des coûts grâce à l'économie à la fois de l'usinage complexe d'une denture d'un mobile de petit diamètre, comme typiquement un pignon d'entraînement, et gain de matière grâce à l'aplanissement des crans d'entraînement, typiquement sur un mobile mené de plus gros diamètre.Yet another advantage of the proposed solution is that it allows a reduction in costs thanks to the economy both of the complex machining of a toothing of a small-diameter mobile, such as typically a drive pinion, and saving in material thanks to the flattening of the drive notches, typically on a driven mobile of larger diameter.

Encore un autre avantage de la solution proposée est qu'elle facilite le positionnement mutuel de l'organe de commande et de l'organe tournant, notamment dans un boîtier, car les propriétés élastiques du galet d'entraînement en matériau élastomère permettent de récupérer des jeux de positionnement pour les axes respectifs des éléments mobiles menants et menés impliqués dans le dispositif d'engrenage proposé.Yet another advantage of the proposed solution is that it facilitates the mutual positioning of the control member and the rotating member, in particular in a housing, since the elastic properties of the drive roller made of elastomeric material make it possible to recover positioning clearances for the respective axes of the driving and driven movable elements involved in the proposed gear device.

D'autres caractéristiques et avantages de la présente invention apparaîtront dans la description suivante d'un mode de réalisation préféré concernant un réhaut entraîné par une couronne de commande, présenté à titre d'exemple non limitatif en référence aux dessins annexés, dans lesquels:

  • les figure 1A, 1B et 1C montrent respectivement une vue de dessus, en coupe et en trois dimensions d'une carrure destinée à loger le système de commande pour réhaut tournant selon un mode de réalisation préférentiel de l'invention;
  • les figures 2A, 2B et 2C montrent respectivement une vue de dessus, en coupe et en trois dimensions d'un réhaut tournant selon un mode de réalisation préférentiel de l'invention;
  • les figure 3A, 3B et 3C montrent respectivement une vue de profil, en coupe et en trois dimensions d'une couronne de commande selon un mode de réalisation préférentiel de l'invention;
  • la figure 4 est une vue en coupe du système de commande pour réhaut tournant selon un mode de réalisation préférentiel de l'invention, intégré dans une montre bracelet;
  • la figure 5 est une vue de détail de la surface de roulement utilisée pour le réhaut selon le mode de réalisation préférentiel des figures 2A,2B et 2C.
Other characteristics and advantages of the present invention will appear in the following description of a preferred embodiment relating to a flange driven by a control ring, presented by way of non-limiting example with reference to the accompanying drawings, in which:
  • the figure 1A, 1B and 1C respectively show a top view, in section and in three dimensions of a middle part intended to house the control system for a rotating flange according to a preferred embodiment of the invention;
  • the figures 2A, 2B and 2C respectively show a top view, in section and in three dimensions of a rotating flange according to a preferred embodiment of the invention;
  • the figure 3A, 3B and 3C respectively show a side view, in section and in three dimensions of a control ring according to a preferred embodiment of the invention;
  • the figure 4 is a sectional view of the control system for a rotating flange according to a preferred embodiment of the invention, integrated in a wristwatch;
  • the figure 5 is a detail view of the running surface used for the flange according to the preferred embodiment of the figures 2A, 2B and 2C .

Selon le vocabulaire horloger usuel, un galet est une pièce formée traditionnellement par un rouleau en acier, et qui vise à remplacer le frottement de glissement par un frottement de roulement (voir le dictionnaire professionnel illustré de l'horlogerie de G-A. Berner, p.518, référence 2221 ). On se référera donc, dans le cadre de la présente demande, par extension à un galet d'entraînement pour une pièce ayant pour vocation de transmettre un mouvement de rotation par frottement de roulement avec une autre pièce mobile.According to the usual watchmaking vocabulary, a roller is a part traditionally formed by a steel roller, and which aims to replace sliding friction by rolling friction (see GA Illustrated Professional Dictionary of Watchmaking. Berner, p.518, reference 2221 ). Reference will therefore be made, in the context of the present application, by extension to a drive roller for a part intended to transmit a rotational movement by rolling friction with another moving part.

Les figures 1A, 1B et 1C montrent respectivement une vue de dessus, en coupe et en trois dimensions d'une carrure 5 destinée à recevoir le système de commande selon l'invention, formé par une couronne 1 et un réhaut 3, illustrés sur les figures 2A,B,C et 3A,B,C qui suivent. La carrure 5 comprend deux paires de cornes 53 d'attache pour bracelet, ainsi qu'une portée 50 formant une surface d'appui pour le réhaut 3 tournant. Dans la carrure sont percés un premier trou traversant taraudé 51 ainsi qu'un deuxième trou traversant taraudé 52, de préférence pour le montage de tubes de couronne. Au niveau de chacun de ces trous taraudés sont disposées respectivement une première échancrure 501 et une deuxième échancrure 502, visibles sur la figure 1A. Ces échancrures permettent de passer une clef pour le montage ou le changement de divers éléments constitutifs de la couronne 1 assemblée à la carrure 5 lors d'un service après-vente, et notamment galet d'entraînement 25 sur son axe.The figures 1A, 1B and 1C respectively show a top view, in section and in three dimensions of a middle part 5 intended to receive the control system according to the invention, formed by a crown 1 and a flange 3, illustrated on figures 2A, B, C and 3A, B, C that follow. The middle 5 comprises two pairs of strap attachment horns 53, as well as a bearing surface 50 forming a bearing surface for the rotating flange 3. A first threaded through hole 51 and a second threaded through hole 52 are drilled in the middle part, preferably for mounting crown tubes. At the level of each of these threaded holes are respectively arranged a first notch 501 and a second notch 502, visible on the figure 1A . These notches make it possible to pass a key for mounting or changing various constituent elements of the crown 1 assembled to the middle 5 during after-sales service, and in particular drive roller 25 on its axis.

La figure 1B montre une vue en coupe de la carrure 5 selon le premier axe de coupe B-B de la figure 1A, traversant le premier trou traversant taraudé 51, sur laquelle on peut voir l'épaisseur de la portée 50, tandis que sur la figure 1C on distingue les mêmes éléments que sur la figure 1A, hormis les première et deuxième échancrures 501,502.The figure 1B shows a sectional view of the middle 5 along the first cutting axis BB of the figure 1A , passing through the first threaded through hole 51, on which we can see the thickness of the seat 50, while on the figure 1C we distinguish the same elements as on the figure 1A , except for the first and second indentations 501,502.

La figure 2A montre une vue de dessus du réhaut 3 destiné à être monté sur la carrure 5 des figures 1A, 1B, et 1C précédentes, sur lequel on distingue sa face supérieure, consistant en une surface oblique d'affichage 34, ici dépourvue d'éléments d'affichage, mais que l'on peut discerner plus loin sur la figure 4, ainsi que la surface supérieure 371 d'un rebord périphérique 37, destinée à fournir une surface d'appui pour un élément annulaire disposé à sa périphérie. La figure 2B montre le réhaut 3 selon le deuxième axe de coupe C-C de la figure 2A, et met en évidence le rebord périphérique 37, et la surface supérieure 371 ainsi que la surface inférieure 372 de celui-ci, la surface oblique d'affichage 34, mais surtout la denture de roulement 32 qui coopère avec le galet d'entraînement 25, visible sur les figures 3A, 3B et 3C suivantes de la couronne. Cette denture de roulement 32, visant à transmettre le mouvement de rotation de la couronne 1 lorsque cette dernière est actionnée par l'utilisateur de la montre, s'étend le long d'une face inférieure de forme annulaire du réhaut 3, et on peut constater que cette denture de roulement 32 se situe dans un plan d'engrenage 35 perpendiculaire au deuxième axe de rotation 30 du réhaut 3. Cette denture de roulement 32 est formée de préférence par une denture plate, comme illustrée plus loin sur la figure 5, mais on pourrait envisager d'employer, à titre d'alternative, un autre type de surface de roulement comme un moletage voire même une matériau présentant une rugosité suffisante pour garantir la transmission du roulement du galet d'entraînement 25 en évitant tout glissement. La figure 2C illustre les mêmes éléments constitutifs du réhaut 3 que la figure 2A décrite précédemment, à savoir la surface oblique d'affichage 34, ainsi que le rebord périphérique 37 et sa surface supérieure 371.The figure 2A shows a top view of the flange 3 intended to be mounted on the middle 5 of the figures 1A, 1B, and 1C previous ones, on which we can distinguish its upper face, consisting of an oblique display surface 34, here devoid of display elements, but which can be discerned later on the figure 4 , as well as the upper surface 371 of a peripheral rim 37, intended to provide a bearing surface for an annular element disposed at its periphery. The figure 2B shows flange 3 along the second cutting axis CC of the figure 2A , and highlights the peripheral rim 37, and the upper surface 371 as well as the lower surface 372 thereof, the oblique display surface 34, but above all the rolling teeth 32 which cooperates with the drive roller 25 , visible on figures 3A, 3B and 3C following the crown. This rolling toothing 32, aimed at transmitting the rotational movement of the crown 1 when the latter is actuated by the user of the watch, extends along an annular lower face of the flange 3, and it is possible to note that this rolling toothing 32 is located in a gear plane 35 perpendicular to the second axis of rotation 30 of the flange 3. This rolling toothing 32 is preferably formed by a flat toothing, as illustrated later on figure 5 , but one could consider using, as an alternative, another type of rolling surface such as knurling or even a material having sufficient roughness to guarantee the transmission of the roller bearing. drive 25 avoiding any slippage. The figure 2C illustrates the same components of flange 3 as the figure 2A described above, namely the oblique display surface 34, as well as the peripheral rim 37 and its upper surface 371.

La figure 3A illustre une vue de profil d'une couronne 1 selon un mode de réalisation préférentiel de l'invention. Bien qu'il s'agisse d'une couronne non vissée ne présentant qu'une seule position axiale par rapport à la carrure, on comprendra que le système d'engrenage hybride ainsi que la disposition d'un galet d'entraînement 25 sur une couronne est indépendant de la structure de couronne employée, et qu'ainsi une couronne du type vissée pourrait tout à fait être employée également sans sortir du cadre de l'invention ni imposer de limites structurelles au mécanisme d'engrenage hybride proposé entre le galet d'entraînement 25 et la denture de roulement 32 du réhaut 3.The figure 3A illustrates a profile view of a crown 1 according to a preferred embodiment of the invention. Although this is an unscrewed crown having only one axial position relative to the caseband, it will be understood that the hybrid gear system as well as the arrangement of a drive roller 25 on a crown is independent of the crown structure employed, and that thus a crown of the screwed type could quite well also be used without departing from the scope of the invention nor imposing structural limits on the hybrid gear mechanism proposed between the roller d 'drive 25 and the rolling teeth 32 of the flange 3.

La couronne 1, mobile autour d'un premier axe de rotation 10, est composée classiquement d'un tube 13, destiné à être monté à la carrure 5 par chassage ou vissage, au-dessus duquel est agencé un capot 11 actionnable par l'utilisateur de la montre. Au niveau de l'extrémité proximale de la couronne, sur la gauche des figures 3A, 3B, et 3B, est agencé le galet d'entraînement 25, sous la forme d'un premier joint torique du type O-ring ou d'un joint surmoulé. L'avantage d'utiliser un joint de type O-Ring est de pouvoir utiliser le galet d'entraînement 25 comme pièce d'usure, remplaçable indépendamment du reste de la couronne 1. Le galet d'entraînement 25 est réalisé en matériau élastomère précisément pour augmenter les forces de frottement et améliorer la qualité de la transmission du roulement, à la manière d'un pneu d'un véhicule sur le revêtement d'une route. Entre l'organe de transmission, solidaire en rotation de la couronne 1 sur laquelle est agencé le galet d'entraînement 25, et le tube 13, est agencé de préférence une bague de friction 14, qui se présente sous la forme d'un deuxième joint de section de préférence rectangulaire afin de maximiser la surface de frottement avec chacune des pièces. Les surfaces de friction se présentent alors sous une forme annulaire dans chacun des plans de friction. On pourrait toutefois également envisager un joint de forme torique de type O-ring ou également consister en un autre joint surmoulé, ce nécessiterait néanmoins une compression axiale plus importante du joint pour garantir les mêmes forces de frottement. Cette bague de friction 14, vise à augmenter le couple de mise en rotation du réhaut 3 et éliminer ainsi les mouvements parasites et involontaires du réhaut 3 lors des manipulations de la couronne 1. Bien que selon le mode de réalisation préférentiel illustré, la couronne 1 ne soit pas une couronne vissée, une telle bague de friction 14 est particulièrement avantageuse pour une couronne vissée ayant plusieurs position axiales, notamment lors de la transition d'une position verrouillée ou vissée « T0 » à une position tirée ou dévissée « T1 » de réglage. En effet, dans le cadre d'une montre de plongée par exemple, l'avantage d'une couronne vissée consisterait à bloquer à la demande et par vissage la rotation du réhaut 3, afin d'en éviter tout déplacement accidentel. Ceci s'avère indispensable pour des raisons de sécurité, car des indications temporelles critiques pour une plongée, comme par exemple un temps restant avant d'effectuer un palier de décompression, ne doivent en aucun cas pouvoir être modifiés. Parallèlement au verrouillage par vissage, la bague de friction 14 demeure dans ce cas indispensable pour empêcher toute rotation accidentelle du réhaut 3 précisément lors des opérations de dévissage, et surtout de revissage de la couronne 1.The crown 1, movable around 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 11 operable by the watch user. At the level of the proximal end of the crown, to the left of the figures 3A, 3B, and 3B , is arranged the drive roller 25, in the form of a first O-ring type O-ring or an overmolded seal. The advantage of using an O-ring type seal is to be able to use the drive roller 25 as a wearing part, replaceable independently of the rest of the ring 1. The drive roller 25 is made of precisely elastomeric material. to increase frictional forces and improve the quality of rolling transmission, much like a vehicle tire on a road surface. Between the transmission member, integral in rotation with the ring 1 on which the drive roller 25 is arranged, and the tube 13, is preferably arranged a friction ring 14, which is in the form of a second preferably section seal rectangular in order to maximize the friction surface with each part. The friction surfaces are then present in an annular shape in each of the friction planes. However, it would also be possible to envisage an O-ring-shaped seal of the O-ring type or also consist of another overmolded seal, this would nevertheless require greater axial compression of the seal in order to guarantee the same frictional forces. This friction ring 14 aims to increase the torque for setting the flange 3 in rotation and thus eliminate the parasitic and involuntary movements of the flange 3 during handling of the crown 1. Although according to the preferred embodiment illustrated, the crown 1 is not a screwed crown, such a friction ring 14 is particularly advantageous for a screwed crown having several axial positions, in particular during the transition from a locked or screwed position "T0" to a pulled or unscrewed position "T1" of setting. In fact, in the context of a diving watch for example, the advantage of a screw-down crown would consist in blocking the rotation of the flange 3 on demand and by screwing in, in order to avoid any accidental displacement thereof. This is essential for safety reasons, since time-critical indications for a dive, such as for example a time remaining before performing a decompression stop, must not be able to be modified under any circumstances. In parallel with the screw-locking, the friction ring 14 remains in this case essential to prevent any accidental rotation of the flange 3 precisely during unscrewing operations, and especially when screwing the crown 1 back on.

La figure 3B montre une vue en coupe selon le troisième axe de coupe A-A de la figure 3A, ou l'on peut voir, en plus des autres éléments déjà décrits sur la figure 3A, un cylindre central 12 taraudé pour être relié à une tige de commande, ainsi que la jupe axiale 111 et le couvercle 112 du capot 11. On peut également distinguer par ailleurs les éléments d'étanchéité de la tête de couronne vis-à-vis de l'intérieur de la carrure, c'est-à-dire un troisième joint 16, également de forme torique, recouvert par un deckring 15. Le troisième joint torique 16 est par ailleurs maintenu axialement à l'aide d'une entretoise 17. Sur la figure 3C, les éléments de la couronne 1 illustrés sont similaires à ceux déjà décrits au vu de la figure 3A, c'est-à-dire le galet d'entraînement 25, la bague de friction 14 et le tube 13; néanmoins, on peut distinguer un logo « H » sur la face externe 113 du capot 11, et mieux visualiser le moletage sur le pourtour de la jupe axiale 111 du capot 11, prévu pour faciliter la préhension et la manipulation de la couronne par l'utilisateur.The figure 3B shows a sectional view along the third cutting axis AA of the figure 3A , where we can see, in addition to the other elements already described on the figure 3A , a central cylinder 12 threaded to be connected to a control rod, as well as the axial skirt 111 and the cover 112 of the cover 11. One can also distinguish, moreover, the sealing elements of the crown head vis-à-vis from the inside of the caseband, that is to say a third seal 16, also of O-ring shape, covered by a deckring 15. The third O-ring 16 is also maintained axially using a spacer 17. On the figure 3C , the elements of the crown 1 illustrated are similar to those already described in view of the figure 3A , that is to say the drive roller 25, the friction ring 14 and the tube 13; nevertheless, we can distinguish an "H" logo on the external face 113 of the cover 11, and better visualize the knurling on the periphery of the axial skirt 111 of the cover 11, provided to facilitate the gripping and handling of the crown by the user.

La figure 4 montre une vue en coupe du détail du mécanisme de commande selon le mode de réalisation préférentiel de l'invention, où le réhaut 3 et la couronne de commande 1 illustrées séparément par les figures 2 et 3 précédentes sont désormais intégrés dans la carrure 5 d'une montre.The figure 4 shows a sectional view of the detail of the control mechanism according to the preferred embodiment of the invention, where the flange 3 and the control ring 1 illustrated separately by the figures 2 and 3 previous ones are now integrated into the middle 5 of a watch.

Selon l'invention, le dispositif d'engrenage hybride du système de commande pour organe tournant proposé concerne la transmission d'un mouvement de rotation entre un premier élément mobile et un deuxième élément mobile autour de leur axe de rotation respectif à l'aide d'un engrenage par frottement de roulement entre les deux pièces mobiles, l'une étant équipée sur son pourtour d'un matériau élastomère de préférence lisse et l'autre d'un matériau plus dur, comme par exemple du métal ou de l'acier, et présentant de préférence une denture. L'engrenage utilisé dans le cadre de la présente invention est ainsi qualifié d' « hybride » non seulement pour cette première raison d'inadéquation potentielle entre les deux matériaux responsables de la transmission, mais également parce qu'il est possible de faire coopérer des surfaces de nature différente, tel qu'un crantage, un moletage et ou encore une surface rugueuse avec une surface lisse, comme celle du galet d'entraînement 25. La coopération d'éléments de nature différente, c'est-à-dire dont les matériaux et les profils de surface sont hétérogènes, est inhabituelle pour un mécanisme de transmission par engrenage traditionnel horloger où en général la denture en métal d'un premier mobile sont prévues pour coopérer avec une autre denture en métal d'un autre mobile. Alternativement, dans le cadre d'engrenage par friction, aucune denture n'est jamais employée non plus comme surface de roulement.According to the invention, the hybrid gear device of the proposed rotary member control system relates to the transmission of a rotational movement between a first movable member and a second movable member about their respective axis of rotation by means of 'a gear by rolling friction between the two moving parts, one being equipped on 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 teeth. The gear used in the context of the present invention is thus qualified 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 make surfaces of a different nature, such as a notch, a knurling and or even a rough surface with a smooth surface, such as that of the drive roller 25. The cooperation of elements of a different nature, that is to say of which the materials and surface profiles are heterogeneous, is unusual for a traditional watchmaking gear transmission mechanism where in general the metal teeth of a first mobile are provided to cooperate with another metal teeth of another mobile. Alternatively, in the frame friction gear, no toothing is ever used as a running surface either.

Selon le mode de réalisation préférentiel décrit où l'organe tournant est un réhaut 3 et l'organe de commande est une couronne 1, le deuxième élément mobile 31 peut être considéré comme le corps du réhaut 3, référencé sur la figure 4, alors que le réhaut 3 comprend ici par ailleurs une rondelle en téflon 33 agencée au-dessus de son rebord périphérique 37. Cette rondelle en téflon 33 vient en appui sur la surface supérieure 371 de celui-ci, afin de minimiser les frottements avec la lunette 6. Le premier élément mobile, qui est solidaire en rotation du galet d'entraînement 25, est formé ici par le canon central 2 de la couronne 1, solidaire également en rotation du capot 11 de la couronne 1 suite au vissage de sa partie supérieure filetée 21 dans le trou borgne taraudé 121 du cylindre central 12.According to the preferred embodiment described where the rotating member is a flange 3 and the control member is a ring 1, the second movable element 31 can be considered as the body of the flange 3, referenced on the figure 4 , while the flange 3 here further comprises a Teflon washer 33 arranged above its peripheral rim 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 crown 1, also integral in rotation with the cover 11 of the crown 1 following the screwing of its part. upper thread 21 in the threaded blind hole 121 of the central cylinder 12.

Selon le mode de réalisation préférentiel décrit, on pourra noter que le galet d'entraînement 25 est agencé sur un élément menant, c'est-à-dire le canon central 2 solidaire en rotation de la couronne 1, tandis que la denture de roulement 32 est agencée sur un élément mené, c'est-à-dire le 2e élément mobile 31 du réhaut 3. Un tel agencement du galet d'entraînement 25 en matériau élastomère est avantageux sur l'élément menant pour améliorer l'efficacité de la transmission ainsi que de diminuer les coûts de production, notamment lorsque la circonférence de celui-ci, en l'occurrence voisine de celle de sa partie inférieure 23 - taraudée pour la fixation éventuelle d'une tige de commande - est nettement inférieure à la circonférence de l'élément mené, comme le réhaut 3, ce qui permet d'économiser de la matière élastomère, et simplifie par ailleurs l'usinage de l'élément mobile 31 ainsi que du canon central 2. Par ailleurs, alors que l'engrenage s'effectue par frottement de roulement mutuel, on pourra remarquer que le rapport des circonférences de l'élément menant par rapport à l'élément mené permet de définir un rapport d'engrenage continu, contrairement à un ratio entre des nombres de dents entre un mobile menant et un mobile mené, qui est fonction de valeurs discrètes. On se dispense parallèlement de denture pointues et profondes traditionnelles et ainsi de tout à-coup d'indexation. Par ailleurs, la solution proposée dispense également d'un positionnement très précis des axes de rotation relatifs mutuel des pièces, aussi souvent appelé « entraxe », ces jeux de positionnement pouvant être récupérés grâce aux propriétés plastiques du galet d'entraînement 25 en élastomère qui sera alors plus ou moins comprimé contre la surface de roulement du mobile à entraîner en rotation. Le montage du dispositif de commande en est ainsi simplifié, ce qui permet des gains de productivité additionnels.According to the preferred embodiment described, it may be noted that the drive 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. such an arrangement of the drive roller 25 of elastomeric material is advantageous over the drive member to improve the efficiency of transmission as well as to reduce production costs, in particular 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 clearly less than the circumference of the driven element, like the flange 3, which makes it possible to save elastomeric material, and also simplifies the machining of the movable element 31 as well as of the central barrel 2. Furthermore, while the gearing takes place by mutual rolling friction , it will be noted that the ratio of the circumferences of the driving element relative to the driven element makes it possible to define a continuous gear ratio, unlike a ratio between the numbers of teeth between a mobile leading and a driven mobile, which is a function of discrete values. At the same time, we dispense with traditional sharp and deep toothing and thus suddenly indexing. Furthermore, the proposed solution also dispenses with a very precise positioning of the relative mutual axes of rotation of the parts, also often called “center distance”, these positioning clearances being able to be recovered thanks to the plastic properties of the elastomer drive roller 25 which will then be more or less compressed against the running surface of the mobile to be driven in rotation. The assembly of the control device is thus simplified, which allows additional productivity gains.

Sur la figure 4, la couronne de commande 1 est une couronne n'ayant qu'une seule position axiale vis-à-vis de la carrure, qui comporte un capot 11 saillant hors de la carrure 5 et qui peut être actionné en rotation par l'utilisateur de la montre. On pourrait toutefois utiliser une couronne vissée dans le cadre de l'invention sans que cela n'affecte le dispositif de transmission particulier proposé. Le capot 11 est monté au-dessus d'un tube 13, ici pourvu d'un filetage 131 pour son assemblage par vissage à la carrure 5 dans le premier trou traversant 51 taraudé dans lequel est introduit un cylindre central 12 solidaire du capot 11, et qui est pourvu à son extrémité d'un trou borgne taraudé 121 pour l'assemblage à un canon central 2, présentant pour sa part une partie supérieure filetée 21. Le canon central 2 forme ainsi un premier élément mobile de l'organe de commande que constitue la couronne 1; il est mobile en rotation par rapport au tube 13 vissé à la carrure 5 et c'est au niveau de son extrémité proximale, c'est-à-dire la partie inférieure taraudée 23 pour l'adjonction éventuellement d'un tige de commande - non représentée - qu'est agencé le galet d'entraînement 25 en matériau élastomère, en remplacement d'un pignon terminal comme sur des couronnes traditionnelles. Le galet d'entraînement 25 formé ici par un premier joint torique qui est disposé dans une rainure délimitée par deux butées axiales 24, agencées dans un plan perpendiculaire au premier axe de rotation 10 de la couronne, qui est aussi celui du canon central 2 et qui peuvent venir de matière avec le canon central 2 ou consister en des rondelles montées sur ce dernier.On the figure 4 , the control crown 1 is a crown having only one axial position vis-à-vis the middle part, which comprises a cover 11 projecting out of the middle part 5 and which can be actuated in rotation by the user of the watch. A screw-down crown could however be used within the framework of the invention without this affecting the particular transmission device proposed. The cover 11 is mounted above a tube 13, here provided with a thread 131 for its assembly by screwing to the middle 5 in the first threaded through hole 51 in which is inserted a central cylinder 12 integral with the cover 11, 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 part 21. The central barrel 2 thus forms a first movable element of the control member what constitutes crown 1; it is movable in rotation with respect to the tube 13 screwed to the middle part 5 and it is at its proximal end, that is to say the tapped lower part 23 for the possible addition of a control rod - not shown - that is arranged the drive roller 25 of elastomeric material, replacing an end pinion as on traditional crowns. The drive roller 25 formed here by a first O-ring which is arranged in a groove delimited by two axial stops 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 may be integral with the central barrel 2 or consist of washers mounted on the latter.

Selon le mode de réalisation préférentiel illustré par la figure 4, on peut constater qu'un deuxième joint, de section de préférence rectangulaire ou carrée, est agencé autour du canon central 2, venant en appui sur un épaulement 22. Ce deuxième joint constitue la bague de friction 14, déjà visible sur les figures 3A,3B et 3C précédemment décrites, et qui est agencée entre le canon central 2 et le tube 13 vissé à la carrure 5 afin d'augmenter le couple d'actionnement de la couronne 1, est ainsi éviter d'imposer tout mouvement parasite au réhaut 3. La bague de friction 14 est ici maintenue axialement entre l'épaulement 22 du canon central 2, qui peut également être formé par une rondelle, même éventuellement l'autre face de la rondelle utilisée comme butée axiale 24 pour le galet d'entraînement 25, et l'extrémité inférieure 132 du tube 13 vissé à la carrure 5. Légèrement comprimée entre l'extrémité inférieure 132 du tube 13, fixe par rapport à la carrure, et l'épaulement 22 solidaire en rotation du canon central 2, cette bague de friction permet donc de rendre plus difficile l'actionnement en rotation de la couronne 1, et par suite sécurise plus efficacement la position angulaire du réhaut 3. Selon le mode de réalisation préférentiel décrit, on pourra constater que cette bague de friction 14 est interposée entre le tube 13 et une partie du canon central 2, ici l'épaulement 22, de telle sorte que les frottements sont agencés dans des plans perpendiculaires au premier axe de rotation 10 de la couronne 1. On pourra qualifier ce type de frottement comme des frottements axiaux. Selon une variante, on pourrait toutefois envisager agencer une telle bague de friction 14 directement à l'intérieur du tube 13 de la couronne, dans une gorge aménagée directement sur le canon central 2, de telle sorte que les frottements ne soient plus axiaux, mais radiaux. L'avantage d'utiliser une bague de friction 14 axiale, comme celle représentée sur la figure 4, est qu'elle permet de s'affranchir d'épaisseurs de parois substantielles pour pouvoir y agencer une rainure suffisamment profonde et y loger l'élément de friction. Elle est ainsi compatible avec des tubes de couronne présentant des parties terminales de diamètre réduit, et à faible paroi en dessous de la partie filetée pour l'assemblage à la carrure, comme celle du tube 13 représenté, ce qui permet notamment de centrer au besoin un cercle d'emboîtage du mouvement.According to the preferred embodiment illustrated by figure 4 , we can see that a second seal, 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 on the 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 in order to increase the actuation torque of the crown 1, is thus to avoid imposing any parasitic movement on the flange 3. The ring friction 14 is here maintained axially between the shoulder 22 of the central barrel 2, which can also be formed by a washer, possibly even the other side of the washer used as an axial stop 24 for the drive roller 25, and the the lower end 132 of the tube 13 screwed to the middle part 5. Slightly compressed between the lower end 132 of the tube 13, fixed with respect to the middle part, and the shoulder 22 integral in rotation with the central barrel 2, this friction ring allows therefore to make it more difficult to activate the crown 1 in rotation, and therefore 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 e between the tube 13 and a part of the central barrel 2, here the shoulder 22, so that the friction is arranged in planes perpendicular to the first axis of rotation 10 of the crown 1. This type of friction can be qualified as axial friction. According to a variant, one could however envisage arranging such a friction ring 14 directly inside the tube 13 of the crown, in a groove arranged directly on the central barrel 2, so that the friction is no longer axial, but radials. The advantage of using an axial friction ring 14, like the one shown in figure 4 , is that it makes it possible to dispense with substantial wall thicknesses in order to be able to arrange therein a sufficiently deep groove and to house the friction element therein. It is thus compatible with crown tubes having parts terminals of reduced diameter, and with a low wall below the threaded part for assembly to the caseband, such as that of the tube 13 shown, which makes it possible in particular to center, if necessary, a casing circle for the movement.

La partie saillante de la couronne 1 hors de la carrure 5 montre une vue agrandie du détail des éléments illustrés à la figure 3B, à savoir un cylindre central 12 taraudé relié au canon central 2, la jupe axiale 111 et le couvercle 112 du capot, ainsi que les éléments d'étanchéité de la tête de couronne vis-à-vis de l'intérieur de la carrure, c'est-à-dire un troisième joint 16 torique, recouvert par un deckring 15, et maintenu par ailleurs axialement à l'aide d'une entretoise 17. Ces éléments n'ont toutefois pas d'influence sur le mécanisme d'engrenage hybride proposé dans le cadre de la présente invention, et en particulier sur l'agencement du galet d'entraînement 25.The protruding part of the crown 1 outside the middle 5 shows an enlarged view of the detail of the elements illustrated on figure 3B , namely a threaded central cylinder 12 connected to the central barrel 2, the axial skirt 111 and the cover 112 of the bonnet, as well as the sealing elements of the crown head vis-à-vis the inside of the middle part, that is to say a third O-ring 16, covered by a deckring 15, and moreover maintained axially by means of a spacer 17. These elements however have no influence on the gear mechanism hybrid proposed in the context of the present invention, and in particular on the arrangement of the drive roller 25.

Comme on peut le voir sur la figure 4, le galet d'entraînement 25 en matériau élastomère coopère avec une denture de roulement 32 agencée sur la face inférieure d'un corps de réhaut 3.As can be seen on the figure 4 , the drive roller 25 of elastomeric material cooperates with a rolling toothing 32 arranged on the underside of a flange body 3.

Le réhaut 3 est composé d'un deuxième élément mobile 31, c'est-à-dire le corps du réhaut sur lequel est agencée la denture de roulement 32, recouvrant partiellement le bord du cadran 4, et qui pourvu d'un rebord périphérique 37 annulaire sur lequel est montée une rondelle en téflon 33 afin de minimiser les frottements avec la lunette 6, qui est par ailleurs recouverte de la glace 7 et montée à cran sur la carrure 5. Afin de garantir l'étanchéité vers l'intérieur la carrure, un joint d'étanchéité formé par un quatrième joint 61 torique est agencé entre la lunette 6 et la carrure 5, et similairement, un cinquième joint 81 torique est interposé entre le fond 8 et la carrure 5.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 teeth 32, partially covering the edge of the dial 4, and which is provided with a peripheral rim 37 annular on which is mounted a Teflon washer 33 in order to minimize friction with the bezel 6, which is also covered with the crystal 7 and mounted in a notch on the caseband 5. In order to guarantee the seal inwardly the middle, a seal formed by a fourth O-ring 61 is arranged between the bezel 6 and the middle 5, and similarly, a fifth O-ring 81 is interposed between the bottom 8 and the middle 5.

Selon le mode de réalisation préférentiel illustré appliqué à l'entraînement en rotation d'un réhaut 3 par une couronne, la denture de roulement 32 s'étend essentiellement dans un plan d'engrenage parallèle au premier axe de rotation 10 de la couronne 1, c'est-à-dire perpendiculairement au deuxième axe de rotation 30 du réhaut 3. Par conséquent, le mécanisme d'engrenage hybride fait office de renvoi sans nécessiter l'emploi de dentures inclinées pour gagner de la place en hauteur. On comprendra toutefois qu'il serait possible d'agencer un dispositif d'engrenage hybride selon l'invention comprenant une denture de roulement 32 oblique, notamment à 45 degrés par rapport à l'axe de rotation du mobile mené ou menant, pour effectuer un renvoi à 90 degrés, ou encore agencer une denture de roulement 32 s'étendant non plus dans un plan mais dans une portion cylindrique en périphérie d'un mobile coopérant avec un mobile tournant selon un axe parallèle, afin d'assurer la transmission en rotation à un deuxième mobile tournant selon un axe de rotation parallèle.According to the preferred embodiment illustrated applied to the rotational drive of a flange 3 by a crown, the rolling teeth 32 extend essentially in a parallel gear plane. to the first axis of rotation 10 of the crown 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 reference without requiring the use of inclined teeth to save space in height. It will be understood, however, that it would be possible to arrange a hybrid gear device according to the invention comprising an oblique rolling toothing 32, in particular at 45 degrees relative to the axis of rotation of the driven or driving body, to effect a 90-degree return, or even arrange a rolling toothing 32 extending no longer in a plane but in a cylindrical portion at the periphery of a mobile cooperating with a mobile rotating about a parallel axis, in order to ensure the transmission in rotation to a second mobile rotating about a parallel axis of rotation.

La figure 5 montre le détail d'une denture de roulement 32 selon un mode de réalisation préférentiel, où elle est agencée sur la face inférieure du deuxième mobile 31 du réhaut et s'étend le long d'une surface annulaire située dans un plan perpendiculaire au deuxième axe de rotation 30, c'est à dire le plan d'engrenage 35, référencé sur la figure 3B. La denture de roulement 32 est formée ici d'une denture plate 36, dont le profil de denture est supérieur à 90 degrés, et de préférence entre 100 et 130 degrés, ici 120 degrés sur la figure 5. Un tel profil ne serait pas adapté pour un engrenage mutuel de dentures sur des mobiles adjacents en raison du risque de glissement, mais est parfaitement adapté ici pour limiter l'encombrement et garantir la transmission de la rotation par roulement du galet d'entraînement 25 en matériau élastomère, légèrement comprimé dans les creux de cette denture plate 36. A titre d'alternative, on pourrait employer un moletage, formé par exemple par des stries obliques s'étendant dans une direction unique ou deux directions symétriquement opposées, la différence avec la denture plate correspondant à une profondeur moins importante des empreintes formées sur la denture de roulement 32, permettant ainsi un léger gain en hauteur additionnel. Il est également possible de remplacer la denture plate 36 ou le moletage par une surface plane très rugueuse afin de permettre la transmission du roulement dans risque de glissement; néanmoins une telle alternative présenterait le risque d'user rapidement le galet d'entraînement 25 en arrachant du matériau élastomère en raison du caractère très abrasif qui serait requis pour garantir la qualité de la transmission, et nécessiter ainsi fréquemment le son remplacement. En tout état de cause, si une denture plate 36 est utilisée ou un moletage, la profondeur des dentures ou des empreintes n'excédera de préférence pas un quart de millimètre (c'est-à-dire 0.25mm), et selon le mode de réalisation préférentiel décrit, cette profondeur est de préférence comprise entre 0.05 et 0.20mm, afin de gagner le maximum de hauteur possible par rapport à un mécanisme d'engrenage classique.The figure 5 shows the detail of a rolling toothing 32 according to a preferred embodiment, where it is arranged on the underside of the second mobile 31 of the flange and extends along an annular surface located in a plane perpendicular to the second axis rotation 30, i.e. the gear plane 35, referenced on the figure 3B . The rolling teeth 32 is formed here of a flat toothing 36, the tooth profile of which is greater than 90 degrees, and preferably between 100 and 130 degrees, here 120 degrees on the figure 5 . Such a profile would not be suitable for a mutual gearing of toothings on adjacent moving parts because of the risk of slipping, but is perfectly suited here to limit the bulk and guarantee the transmission of the rotation by rolling of the drive roller 25 in elastomeric material, slightly compressed in the hollows of this flat toothing 36. As an alternative, one could use a knurling, formed for example by oblique ridges extending in a single direction or two symmetrically opposite directions, the difference with the flat teeth corresponding to a shallower depth of the indentations formed on the rolling teeth 32, thus allowing a slight additional gain in height. It is also possible to replace the flat toothing 36 or the knurling by a surface very rough plane in order to allow the transmission of the bearing in the risk of slipping; nevertheless, such an alternative would present the risk of rapidly wearing out the drive roller 25 by tearing the elastomeric material because of the very abrasive nature which would be required to guarantee the quality of the transmission, and thus frequently necessitating its replacement. In any event, if flat toothing 36 is used or knurling, the depth of the toothings or indentations will preferably not exceed a quarter of a millimeter (i.e. 0.25mm), and depending on 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.

Claims (6)

  1. Timepiece including:
    - a flange (3) positioned between a dial (4) and a glass (7) of the timepiece, completely covered by the glass (7), said flange (3) comprising a body (31) movable in rotation about a second rotation axis (30) independently of a bezel (6) of the timepiece on which the glass (7) is fitted, said body (31) being provided with rolling teeth (32)
    - a control system for said flange (3), comprising
    ∘ a control element (11) for actuating said flange (3), and
    ∘ a transmission device between said control element and said flange (3), characterised in that said transmission device is a hybrid gearing device comprising a first element (2), which is movable around a first rotation axis (10) provided with a drive runner (25) made from elastomeric material, said drive runner (25) cooperating with said rolling tooth system (32) by friction.
    characterised in that the first rotation axis (10) of the first element (2) is perpendicular to the second rotation axis (30) of the body (31) of the flange (3), and in that the first element (2) passes through a middle part (5) of the timepiece, said middle part (5) being separate from the bezel (6).
  2. Timepiece according to claim 1, characterised in that said rolling tooth system (32) is formed by a flat toothing system (36), the depth of which is in the range of between 0.05 and 0.20 mm.
  3. Timepiece according to one of the preceding claims, characterised in that said drive runner (25) made from elastomeric material is formed by a first ring seal.
  4. Timepiece according to any of the preceding claims, said drive runner (25) cooperating by friction with said rolling tooth system (32) essentially in a meshing plane (35) perpendicular to said second rotation axis (30) of said body (31).
  5. Timepiece according to one of the preceding claims, characterised in that said control element is a crown (1).
  6. Timepiece according to claim 5, characterised in that it additionally comprises a friction ring (14) formed by a second seal of rectangular cross-section, which is movable around said first rotation axis (10) of said crown (1).
EP15708215.7A 2014-03-26 2015-03-06 Timepiece comprising a turning collar Active EP3123251B1 (en)

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PCT/EP2015/054744 WO2015144423A1 (en) 2014-03-26 2015-03-06 Control system for a timepiece

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WO2015144423A1 (en) 2015-10-01
CN106133619B (en) 2019-12-03
CN106133619A (en) 2016-11-16
US10018963B2 (en) 2018-07-10
US20170123377A1 (en) 2017-05-04
EP3123251A1 (en) 2017-02-01
JP6262364B2 (en) 2018-01-17

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