• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a watch shock wheel (1) for driving a component having an unbalance with respect to a pivot axis (D) of the wheel (1), which wheel (1) comprises, one side a shaft (2) for its guidance in pivoting about said pivot axis (D), and secondly drive means (7) arranged or reported on a flange (8) that includes the wheel (1) which comprises at least one flexible element (9) between the shaft (2) and the flange (8). This flange (8) has a cylindrical bearing cooperating in centering bearing with a complementary cylindrical surface that includes the shaft (2) to ensure the perfect concentricity of the drive means (7) with the shaft (2).
    公开号:CH707590B1
    申请号:CH00434/13
    申请日:2013-02-12
    公开日:2017-08-15
    发明作者:Lagorgette Pascal；Balmer Raphaël
    申请人:Eta Sa Mft Horlogère Suisse；
    IPC主号:
    专利说明:

    Description
    FIELD OF THE DISCLOSURE [0001] The invention relates to a shockproof watch wheel for driving a component having an unbalance with respect to a pivot axis of the wheel, which wheel comprises, on the one hand, a shaft for its guidance in pivoting about the pivot axis, and secondly drive means arranged or reported on a flange that includes the wheel, which comprises at least one flexible element between said shaft and said flange.
    The invention also relates to a watch movement comprising such a wheel carrying a component having an unbalance relative to a pivot axis of the wheel.
    The invention also relates to a watch comprising at least one such watch movement.
    The invention relates to the field of protection of watches against the effects of shocks, especially when they have moving components with a large unbalance may damage a more fragile element of the drive train during an impact.
    BACKGROUND OF THE INVENTION [0005] The use of technologies making it possible to use larger imbalances of needles involves new problems: slipping of the needles onto the tubes; - breakage of cogs, or / and motor rotors in electric versions, during an impact at 5000 g, where g = 9.81 m / s2.
    This last point is by far the most critical. On some existing calibres, this kind of breakage can occur during an impact at 5000 g, where g = 9.81 m / s2, such as an accidental fall from the height of the user.
    The case no longer allows the watch to operate, which produces a strong impact on the quality perceived by the user.
    The invention aims to prevent breakage of the wheels and / or the rotor by absorbing the energy of the shock, without impacting the design of the needles. Indeed, if we can add a counterweight to the needles to reduce their imbalance, and thus reduce the torque exerted during a major shock, this type of solution alters the appearance of the needles desired by manufacturers.
    The absorption of energy shock is necessary to allow the use of needles with significant imbalance, even more common with the current trend to increase the diameter of the watches. SUMMARY OF THE INVENTION [0010] The basic principle of the invention is to absorb shock by allowing elastic torsion at a component of the gear train, and, in particular, the center wheel. This torsion is achieved by sliding between the shaft 2 of the center shaft and the flange 8. An elastic element makes it possible to absorb the impact. The sliding tube / board allows to dissipate some energy in friction. The elastic element makes it possible to modify the amplitude and duration of the shock (lower amplitude and longer duration).
    For this purpose, the invention relates to a watch shock wheel for driving a component having an unbalance relative to a pivot axis of the wheel, which wheel comprises, firstly a shaft for its guide pivotally about the pivot axis, and secondly drive means arranged or reported on a flange that includes the wheel, which wheel having at least one flexible element between the shaft and the flange, characterized in that the flange comprises a cylindrical bearing cooperating in centering bearing with a complementary cylindrical bearing surface that the shaft comprises to ensure the perfect concentricity of the drive means with the shaft.
    According to a feature of the invention, the flexible element is an interchangeable element separate from the shaft and the flange, and whose resilience is chosen according to the maximum permissible unbalance value.
    The invention also relates to a watch movement comprising such a wheel carrying a component having an unbalance relative to a pivot axis of the wheel, characterized in that this component is a needle, or an oscillating weight, or a hammer ring, or a rocker.
    The invention further relates to a watch comprising at least one such watch movement.
    BRIEF DESCRIPTION OF THE DRAWINGS [0015] Other characteristics and advantages of the invention will appear on reading the detailed description which follows, with reference to the appended drawings, in which: FIG. 1 represents, schematically and in perspective, a shockproof watch wheel in a first embodiment of the invention in which this wheel, illustrated here in the form of a minute wheel, comprises a toothed flange centered on a shaft, and fixed to this shaft by a bayonet mechanism, this flange being pivotally connected to this shaft by a flexible element which can be deformed in the event of impact, of elastomer type or the like, this flexible element is plated on an upper surface of the flange, and clipped under a lower surface of this flange; fig. 2 shows schematically and in section passing through its pivot axis, the wheel of FIG. 1; fig. 3 is a diagrammatic perspective view of the flexible element of FIG. 1; fig. 4 shows, schematically and in plan from above, this same flexible element; fig. 5 shows it in side view, FIG. 6 in partial view from below, and FIG. 7 partially in section AA of FIG. 4; fig. 8 is a diagrammatic perspective view of the shaft of FIG. 1, comprising, contiguous to a cylindrical surface provided for the centering of the flange, a radial groove provided for the axial immobilization of the flange; fig. 9 shows schematically and in perspective, the fitting, in a first relative angular position of introduction of the flange of FIG. 1 on this shaft in a bearing position in abutment, and FIG. 10 represents this flange and this shaft cooperating in a second angular position, after a rotation and a bayonet-type locking, this second angular position corresponding to a matching flange receiving housing, and complementary receiving housing that includes the shaft, to constitute together cells for the adjusted positioning of protuberances that comprises the flexible element; fig. 11 shows schematically and in perspective, the setting of the flexible element in position on an upper surface of the flange, and the cooperation of its protuberances with the positioning cells, and FIG. 12 shows the position reached after clipping clipping tabs that includes the flexible element, vi sibles in figs. 4, 6 and 7, around the flange being supported on a lower surface of the flange; figs. 13 to 15 illustrate a similar assembly of an hour wheel, the assembly being performed in the same way but with the shaft 2 reversed; figs. 16 and 17 show, similarly to FIGS. 1 and 2, a second embodiment of the invention wherein the wheel, illustrated here in the form of a minute wheel, comprises a toothed flange centered on a shaft, this flange being pivotally connected to this shaft by a flexible element deformable in case of shock, also of elastomer type or the like, this flexible element is pressed on an upper surface of the flange, and is maintained, as well as the flange, on the shaft by a locking washer driven or riveted on the shaft , the figures illustrating a version with a rivet prepared at the level of the raw shaft, and shaped after mounting the lock washer; fig. 18 is a diagrammatic perspective view of the flexible element of FIG. 16; fig. 19 shows, schematically and in plan from above, this same flexible element; fig. 20 shows it in side view, and FIG. 21 partially in the dashed section in FIG. 19; fig. 22 is a diagrammatic perspective view of the shaft of FIG. 16 having, on either side of a cylindrical surface provided for centering the flange, on the one hand a shoulder for the axial immobilization of the flange, and on the other hand a rivet for immobilizing the flange and the locking washer after being put into position; fig. 23 schematically shows in perspective, the fitting of the flange on the shaft in a abutment bearing position, in an angular position corresponding to a matching flange receiving housing, and additional receiving housing of the shaft, to form together cells for the adjusted positioning of the protuberances that comprises the flexible element; fig. 24 shows schematically in perspective the positioning of the flexible element in support on an upper surface of the flange, and the cooperation of its protuberances with the positioning cells, and FIG. 25 shows the installation of the locking washer on the flexible element by compressing it on the flange, FIG. 26 showing the final position after crimping this lock washer on the shaft; figs. 27 to 29 illustrate a similar assembly of an hour wheel, the assembly being performed in the same way but with the shaft 2 overturned; figs. 30 to 34 illustrate a third embodiment of the invention wherein the wheel, illustrated here in the form of a minute wheel, comprises a toothed flange centered on a shaft, this flange being pivotally connected to this shaft by a flexible element deformable in the event of impact, this flexible element is of spring-wire type of substantially omega shape, maintained firstly in a front groove of the shaft and secondly in a chamber of the flange, in which it is maintained substantially coplanar to the flange: FIGS. 30 and 31 represent the shaft with its front groove for receiving the spring shown in FIG. 32, the flange being shown in perspective in FIG. 33, and the assembly in FIG. 34 in top view; figs. 35 to 38 illustrate a fourth embodiment of the invention, with only two components, the shaft shown in perspective and in plan view in FIGS. 35 and 36, and the flange shown in perspective and in plan view in FIGS. 37 and 38, this flange incorporating the flexible element in the form of two blades spring in its thickness, substantially radial and reentrant, which cooperate in frictional support with a hollow eccentric cylindrical sector of the shaft; fig. 39 illustrates, in plan view, a movement with separate electric motors for the wheels minutes and hours, connected by gear wheels to the wheels according to the invention, only one of which is shown in the figure; fig. 40 represents, schematically, a watch comprising such a movement.
    DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS [0016] The invention proposes to improve the protection of watches against the effects of shocks. The effect of a large impact on a moving component with a large unbalance may damage the most fragile elements of the driveline.
    For this purpose, the invention relates to an anticorrosion watch wheel 1 for driving a component 4 having an unbalance of value B with respect to a pivot axis D of the wheel 1.
    This wheel 1 comprises, firstly a shaft 2 for its guidance in pivoting about the pivot axis D, and secondly drive means 7 arranged or reported on a flange 8 that includes the wheel 1. These drive means 7 may be a toothed sector, a belt track or chain or the like, or other.
    The wheel 1 comprises at least one flexible element 9 between the shaft 2 and the flange 8, to absorb the impact due to the shock, and dampen the effect on the other components of the watch movement 100, in which is incorporated the wheel 1 according to the invention.
    According to the invention, this flange 8 has a cylindrical bearing surface 81 cooperating in centering bearing with a complementary cylindrical surface 21 that includes the shaft 2 to ensure the perfect concentricity of the drive means 7 with the shaft 2. The geometry is thus always perfectly assured, as well as the precision of the transmission of movement. This arrangement ensures the absence of any false round, as well as any parasitic vibration due to an extremely small game.
    The figures illustrate several embodiments of the invention, in no way limiting.
    Among these illustrated modes, the first three modes, illustrated in FIGS. 1 to 34, relate to an advantageous variant of the invention, in which the flexible element 9 is an interchangeable element distinct from the shaft 2 and the flange 8. The resilience of this flexible element is chosen as a function of the maximum admissible value unbalance of value B.
    Thus, it is possible to design, for the same pair of 2-flange shaft 8, which determines the geometric interfaces with the rest of the movement, a series of flexible elements 9 of similar geometry, but different damping capacities. , making it possible to better adapt the shock wheel 1 to the context of use, and in particular to the value of the unbalance of value B, and also to the predictable shock level, which depends on the use or the destination of the watch for example for users working in constraining vibratory environment, such as public works, or for users of the sports, military, or similar. As will be seen below, the assembly of the wheel 1 is designed to be very simple, and it is therefore possible to customize a watch to its conditions of use by choosing the appropriate flexible element 9.
    Different mounting versions, not limiting, are presented here. In particular, the flexible element 9 can be mounted: - either trapped between the flange 8 and a lock washer 20 driven or crimped on the shaft 2, - is clipped on either side of an assembly area the cylindrical bearing surface 81 with the complementary cylindrical bearing surface 21, is clipped at an assembly area of the cylindrical bearing surface 81 and the complementary cylindrical bearing surface 21.
    In the first and second embodiments, the flexible elements 9 are substantially flat circular seals, and are wedged between the flange 8 and the shaft 2. The flange 8 pivots on the shaft 2. A washer in bearing on the shaft 2 and riveted on it performs an axial stop flange 8. The seals can transmit the torque between the flange 8 and the shaft 2. During an impact, these joints deform and absorb therefore some of the shock energy. When the shock is over, the flange 8 returns to its initial position relative to the shaft 2.
    In the particular case of the application of the invention to a center wheel 1 carrying a needle 5, the shock is absorbed directly at the center wheel 1. That is to say that the energy of the shock, exerted by the unbalance of the needle, is absorbed as soon as possible in the chain of transmission of the couple.
    This avoids the breakage of any workings and rotors made of plastic with small pivots, that may include a movement 100. The advantages of these plastic components are the reduced cost, the pre-lubrication, the low level of friction at the pivots. The fact of being able to keep, in a movement, such components avoids the use of metal components, synonymous with increased costs and problems of feasibility (especially for the rotor when it is an electric movement or quartz) . Absorbing the shock also prevents the needles from slipping on their shaft tube 2.
    In the first embodiment illustrated in FIGS. 1 to 15, the anti-shock wheel 1, illustrated in the form of a minute wheel, comprises a toothed flange 8 with a toothing 7, centered on a shaft 2, and fixed to this shaft 2 by a bayonet mechanism. This flange 8 is pivotally connected to this shaft 2 by a flexible element 9 which is deformable in the event of an impact, of elastomer type or the like, this flexible element 9 is pressed onto an upper lateral surface 8A of the flange 8, and clipped under a lower surface. 8B of this flange 8.
    This elastomer has a hardness close to 50 Shore A. A type of copolymer called "NBR", or butadiene-acrylonitrile, is particularly suitable. Other elastomers of similar hardness may also be suitable.
    FIG. 8 shows, on the shaft 2, contiguous to a cylindrical surface 21 provided for centering the flange 8, a radial groove 25 provided for the axial immobilization of the flange 8.
    In this embodiment, the flexible element 9 has protuberances 93 which are arranged to, in normal operation, transmit a driving torque between the shaft 2 and the flange 8, and for, during a possible shock , absorbing the torsion between the shaft 2 and the flange 8, to dissipate a portion of the energy of the impact friction, to modify the effect on the drive means 7, the amplitude and the duration of the shock , by reducing the amplitude and increasing the duration, and to constitute elastic return means reminding the flange 8 relative to the shaft 2 in a realignment position after the shock.
    These protuberances 93 are preferably connected to one another by a ring 92 of the flexible element 9, which ring 92 is arranged to bear on an upper lateral surface 8A of the flange 8.
    Preferably, these protuberances 93 are identical to each other and arranged in a regular manner around an axial direction DA around which the flexible element 9 extends.
    The flange 8 comprises housing 82 for receiving and centering the protuberances 93 of the flexible element 9.
    The shaft 2 also comprises complementary housing 22 for receiving and centering the protuberances 93.
    The shaft 2 and the flange 8 are arranged so that, in at least one angular position of the one relative to the other when they are assembled with the cylindrical bearing surface 81 cooperating in centering support with the complementary cylindrical bearing surface 21, the housing 82 and the complementary housing 22 form pairs of cells 23 for complete and complementary reception of the protuberances 93 when the flexible element 9 is pressed onto the flange 8.
    The flange 8 comprises a housing for receiving the shaft 2.
    Advantageously, the shaft 2 comprises the groove 25 arranged to receive, in a first relative angular position, a rib 85 that includes the flange 8, when the shaft 2 and the flange 8 are assembled with the cylindrical seat 81 in centering support with the complementary cylindrical bearing surface 21 and when the flange 8 is in abutment position, supported by an upper lateral surface 8A of the flange 8, against a shoulder surface 27 of the shaft 2. The groove 25 allows the bayonet pivoting of the shaft 2 relative to the flange 8 in a second angular position, wherein the housing 82 and the complementary housing 22 are aligned and form in pairs the cells 23 for the complete and complementary reception of the protuberances 93 when the flexible element 9 is pressed onto the flange 8, the protuberances 93 then ensuring the angular indexing of the flange 8 with respect to the shaft 2.
    FIG. 9 thus illustrates the fitting, in a first relative angular insertion position, of the flange 8 on the shaft 2 in a abutment bearing position. Fig. 10 shows the flange 8 and the shaft 2 cooperating in a second angular position, after a rotation and a bayonet-type locking, this second angular position corresponding to a matching of reception slots 82 of the flange 8, and housing of complementary reception 22 of the shaft 2, to constitute together the cells 23 for the adjusted positioning of the protuberances 93 that comprises the flexible element 9.
    FIG. 11 shows the placing in position of the flexible element 9 resting on an upper lateral surface 8A of the flange 8, and the cooperation of its protuberances 93 with the positioning cells 23.
    In this embodiment, the flexible element 9 has clipping tabs 94 and is clipped on either side of the assembly area of the cylindrical bearing surface 81 and the complementary cylindrical bearing surface 21.
    FIG. 12 shows the position reached after clipping of the clipping tabs 94 that includes the flexible element, visible in FIGS. 4, 6 and 7, around the flange being supported by their end 98 on the bottom surface 8B of the flange 8.
    Figs. 13 to 15 illustrate a similar assembly of an hour wheel, the assembly is performed in the same way but with the shaft 2 reversed.
    In a particular embodiment of this first embodiment, on at least part of its thickness, each protuberance 93 is symmetrical with respect to a plane passing through the axial direction DA and comprises at least two ridges 95 radiated and directed towards this direction axial DA, separated by a radially hollow 96 to absorb the compression of the protuberance 93 during an impact. In this particular case of the figures, the protuberance 93 has such a profile, still delimited laterally by radial recesses 97, of a single side 9A of the flexible element 9, and the so-called upper main surface 91, visible in FIG. 1, is intended to come above the upper lateral surface 8A of the flange 8, while, on the opposite side, the portion 9B of the protuberance 93 is substantially cylindrical, and constitutes the active surface for damping. The so-called lower surface 99 of this portion 9B is intended to be substantially flush with the lower surface 8B of the flange 8. The portion 9A thus makes it possible to hold the cylindrical portion 9B in the correct position. The protuberance 93 accepts a certain deformation, in particular twisting, of the portion 9A relative to the portion 9B, which absorbs some of the impact energy, the other part of the energy being absorbed by the compression of part 9B.
    In the second embodiment of FIGS. 16 to 29, the flexible element 9 is mounted prisoner between the flange 8 and a locking washer 20 driven or crimped onto the shaft 2.
    The minute wheel 1 comprises a toothed flange 8 centered on a shaft 2, this flange 8 being pivotally connected to the shaft 2 by a flexible element 9 deformable in case of shock, also of elastomer type or the like, this element flexible 9 is pressed on an upper lateral surface 8A of the flange 8, and is maintained, as well as the flange 8, on the shaft 2 by a blocking washer 20 driven, or preferably riveted, or the like, on the shaft. The figures show a version with a rivet 26 prepared at the level of the raw shaft 2, and which is shaped after mounting of the locking washer 20.
    The shaft 2 comprises, on either side of a cylindrical seat 21 provided for the centering of the flange 8, on the one hand a shoulder 27 for the axial immobilization of the flange 8, and secondly this rivet 26 for the immobilization of the flange 8 and the lock washer 20 after their positioning.
    FIG. 23 shows the fitting of the flange 8 on the shaft 2 in a abutment bearing position, in an angular position corresponding to a matching of the receiving housing 82 of the flange 8, and complementary receiving housing 22 of the 2, to form together cells 23 for the adjusted positioning of the protuberances 93 that comprises the flexible element 9. This preferably takes the form of a ring 92 on which are reported three bosses constituting the protuberances 93, which may be cylindrical or with a radial flat 90 for cooperation with the shaft 2.
    FIG. 24 shows the positioning of the flexible element 9 bearing on an upper lateral surface 8A of the flange 8, and the cooperation of its protuberances 93 with the positioning cells 23, and FIG. 25 shows the installation of the locking washer 20 on the flexible element 9 by compressing it on the flange 8, FIG. 26 showing the final position after crimping of this lock washer 20 on the shaft 2 by folding the rivet 26.
    Figs. 27 to 29 illustrate a similar assembly of an hour wheel, the assembly being performed in the same way but with the shaft 2 reversed.
    In the third embodiment of FIGS. 30 to 34, the flexible element 9 is a wire spring 6 of substantially omega shape, maintained firstly in a front groove 28 of the shaft 2 and secondly in a chamber 88 of the flange 8, in which the spring 6 is kept substantially coplanar with the flange 8. This shape of spring 6 is placed between the flange 8 and the shaft 2. The spring 6 can not rotate on the shaft 2. The branches 61 and 62 of the spring are preloaded on the flange 8. A washer bearing on the shaft 2, and riveted on it performs an axial stop flange 8, and allows to trap and guide the spring 6 in the plane of the flange 8. When shock, the branches 61 and 62 of the spring 6 are
    权利要求:
    Claims (23)
    [1]
    deform, absorbing some of the energy of the shock. When the impact is complete, the flange 8 returns to its initial position relative to the shaft 2. [0052] In the fourth embodiment of FIGS. 35 to 38, the flexible element 9 is integrated in the flange 8 and comprises two blades-spring 83, 84, in its thickness, substantially radial and reentrant, which cooperate in friction support with a hollow eccentric cylindrical sector 29 of the shaft 2. In another embodiment not illustrated, the flexible element 9 is constituted by an overmolding of elastomer holding together the flange 8 and the shaft 2. This overmolding relates to an elastomer with a hardness of between 20 and 70 Shore A. [0054] The invention also relates to a watch movement 100 comprising such a shockproof wheel 1, carrying such a component 4 having an unbalance of value B with respect to a pivot axis D of the wheel 1. This component 4 may be, and in no way restrictive: - a needle 5; - an oscillating weight of winding; - a striking hammer; - a rocker. In particular, as shown in FIG. 39, this watch movement 100 comprises at least one electric motor 101 for driving at least one needle 5, and comprises at least one such shock wheel 1, either carrying the needle 5, or interposed in a gear train 111 between Needle 5 and motor 101. [0056] The invention also relates to a watch 200 comprising at least one such watch movement 100. Claims
    1. Shockproof watch wheel (1) for driving a component (4) having an unbalance of value B with respect to a pivot axis (D) of said wheel (1), which wheel (1) comprises , firstly a shaft (2) for its guidance in pivoting about the pivot axis (D), and secondly drive means (7) arranged or reported on a flange (8) that comprises the wheel (1), which comprises at least one flexible element (9) between the shaft (2) and the flange (8), characterized in that the flange (8) has a cylindrical bearing surface (81) cooperating in off-center support with a complementary cylindrical surface (21) that includes the shaft (2) to ensure the perfect concentricity of these drive means (7) with the shaft (2).
    [2]
    2. Wheel (1) according to claim 1, characterized in that the flexible element (9) is an interchangeable element separate from the shaft (2) and the flange (8) and whose resilience is chosen according to the maximum permissible value of the unbalance of value B.
    [3]
    3. Wheel (1) according to claim 1 or 2, characterized in that the flexible element (9) is mounted, or trapped between the flange (8) and a locking washer (20) driven or crimped on the shaft (2) is clipped on either side of an assembly area of the cylindrical seat (81) with the complementary cylindrical surface (21).
    [4]
    4. Wheel (1) according to one of the preceding claims, characterized in that the flexible element (9) is mounted, or trapped between the flange (8) and a lock washer (20) driven or crimped on the shaft (2) is clipped at an assembly area of the cylindrical seat (81) and the complementary cylindrical seat (21).
    [5]
    5. Wheel (1) according to claim 4, characterized in that the flexible element (9) is mounted prisoner between the flange (8) and the lock washer (20) driven or crimped on the shaft (2).
    [6]
    6. Wheel (1) according to claim 3, characterized in that the flexible element (9) comprises clipping lugs (94) and is mounted clipped on either side of the assembly area of the cylindrical seat (81) and the complementary cylindrical bearing surface (21).
    [7]
    Wheel (1) according to one of the preceding claims, characterized in that the flexible element (9) has protuberances (93) arranged, in normal operation, to transmit a driving torque between the shaft (2). ) and the flange (8), and for, during a possible impact, absorb the torsion between the shaft (2) and the flange (8), to dissipate some of the energy of the impact friction, to modify the effect on the drive means (7) of the amplitude and duration of the shock by reducing the amplitude and increasing the duration, and to constitute elastic return means reminding the flange (8) relative to the shaft (2) in a realignment position after the impact.
    [8]
    8. Wheel (1) according to claim 7, characterized in that the protuberances (93) are connected by a ring (92) of the flexible element (9), which ring (92) is arranged to bear on a upper side surface (8A) of the flange (8).
    [9]
    9. Wheel (1) according to claim 7, characterized in that the flange (8) has recesses (82) for receiving and centering protuberances (93) that comprises the flexible element (9).
    [10]
    10. Wheel (1) according to claim 7, characterized in that the shaft (2) comprises complementary housing (22) for receiving and centering said protuberances (93) that comprises the flexible element (9).
    [11]
    11. Wheel (1) according to claim 7, characterized in that the protuberances (93) are identical to each other and arranged regularly around an axial direction (DA) around which extends the flexible element (9). ).
    [12]
    12. Wheel (1) according to claim 11, characterized in that each said protrusion (93) is symmetrical with respect to a plane passing through the axial direction (DA) and comprises at least two ridges (95) radiated and directed towards the axial direction (DA).
    [13]
    13. Wheel (1) according to claims 8 and 9, characterized in that the shaft (2) and the flange (8) are arranged so that in at least one particular angular position of the relative to the other when they are assembled with the cylindrical bearing surface (81) cooperating in off-center bearing with the complementary cylindrical bearing surface (21), the housings (82) and the complementary housings (22) form, in pairs, cells (23) for the complete and complementary reception of the protuberances (93) when the flexible element (9) is pressed onto the flange (8).
    [14]
    14. Wheel (1) according to claims 8 and 9, characterized in that the flange (8) has a housing for receiving the shaft (2), in that the shaft (2) has a groove (25). ) arranged to receive, in a first angular position, a rib (85) that includes the flange (8), when the shaft (2) and the flange (8) are assembled with the cylindrical bearing surface (81) in centering support with the complementary cylindrical bearing surface (21) and when the flange (8) is in abutment position, supported by an upper lateral surface (8A) of the flange (8), against a shoulder surface (27) of the shaft (2), the groove (25) allowing pivoting of the shaft (2) relative to the flange (8) to occupy an angular position in which the housing (82) and the complementary housing (22) are aligned and form two two of the cells (23) for the complete and complementary reception of the protuberances (93) when the flexible element (9) is plated on the flange (8), the protuberances (93) then ensuring the angular indexing of the flange (8) relative to the shaft (2).
    [15]
    15. Wheel (1) according to claim 1 or 2, characterized in that the flexible element (9) is a wire spring (6) of substantially omega shape, maintained firstly in a front groove (28) of the shaft (2) and secondly in a chamber (88) of the flange (8), in which the spring (6) is kept substantially coplanar with the flange (8).
    [16]
    16. Wheel (1) according to claim 1, characterized in that the flexible element (9) is integrated in said flange (8) and comprises two spring blades (83; 84) in its thickness, substantially radial and reentrant, which cooperate in frictional abutment with a hollow eccentric cylindrical sector (29) of the shaft (2).
    [17]
    Wheel (1) according to claim 1, characterized in that the flexible element (9) consists of an overmoulding of elastomer holding together the flange (8) and the shaft (2).
    [18]
    18. Watch movement (100) comprising a shockproof wheel (1) according to one of claims 1 to 17 carrying a component (4) having an unbalance of value B with respect to the pivot axis (D) of the wheel ( 1), characterized in that the component (4) is a needle (5).
    [19]
    19. Watch movement (100) comprising a wheel (1) shockproof according to one of claims 1 to 17 carrying a component (4) having an unbalance of value B with respect to the pivot axis (D) of the wheel ( 1), characterized in that the component (4) is an oscillating winding mass.
    [20]
    20. Watchmaking movement (100) comprising a shockproof wheel (1) according to one of claims 1 to 17 carrying a component (4) having an unbalance of value B with respect to the pivot axis (D) of the wheel ( 1), characterized in that the component (4) is a striking hammer.
    [21]
    Clock movement (100) comprising a shockproof wheel (1) according to one of claims 1 to 17 carrying a component (4) having an unbalance of value B with respect to the pivot axis (D) of the wheel ( 1), characterized in that the component (4) is a rocker.
    [22]
    22. Watch movement (100) comprising at least one electric motor (101) for driving at least one needle (5), characterized in that it comprises at least one wheel (1) shockproof according to one of Claims 1 to 17, either carrying the needle (5), or inserted in a gear train (111) between the needle (5) and the motor (101).
    [23]
    23. Watch (200) comprising at least one watch movement (100) according to one of claims 18 to 22.
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    EP0715695B1|1998-09-02|Flywheel particularly for motor vehicles
    FR3010162A1|2015-03-06|DAMPING DEVICE, IN PARTICULAR FOR A TRANSMISSION OF A MOTOR VEHICLE
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    WO2015162386A1|2015-10-29|Torque transmission device for a motor vehicle
    WO2014096624A1|2014-06-26|Pendular damping device
    EP1213626A1|2002-06-12|Impact resistant transmission means for driving a generator by an oscilating mass, in particular in a watch
    FR3075296B1|2019-11-22|PENDULUM DAMPING DEVICE FOR A MOTOR VEHICLE
    WO2019110310A1|2019-06-13|Pendular centrifuge damping device
    CH706795B1|2018-12-14|Mobiles, intended to be used in a precision gear, especially in a watch movement, and watch movement.
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    同族专利:
    公开号 | 公开日
    CN106919038A|2017-07-04|
    US20140226447A1|2014-08-14|
    JP5727059B2|2015-06-03|
    JP2014153367A|2014-08-25|
    CN204009381U|2014-12-10|
    CN107885073A|2018-04-06|
    CN106919038B|2019-04-02|
    CN103984219B|2017-09-26|
    CH707590A2|2014-08-15|
    CN103984219A|2014-08-13|
    US9244432B2|2016-01-26|
    EP2765462A1|2014-08-13|
    HK1252776A1|2019-05-31|
    EP2765462B1|2018-04-04|
    HK1200928A1|2015-08-14|
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    法律状态:
    2020-09-30| PL| Patent ceased|
    优先权:
    申请号 | 申请日 | 专利标题
    EP13154875.2A|EP2765462B1|2013-02-12|2013-02-12|Anti-impact centre wheel|
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