• 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 clockwork resonator mechanism (100) comprising a structure (1) carrying, by a flexible suspension (300), an anchoring block (30) to which is suspended an inertial element (2) oscillating according to a first degree of freedom in rotation RZ, under the action of restoring forces exerted by a flexible pivot (200) comprising first elastic blades (3) each fixed to said inertial element (2) and to said anchoring block (30) , the flexible suspension (300) being arranged to allow a certain mobility of the anchor block (30) in all the degrees of freedom other than the first degree of freedom in rotation RZ in which only the inertial element (2) is movable to prevent any disturbance of its oscillation, and the rigidity of the suspension (300) according to the first degree of freedom in rotation RZ is very much greater than the rigidity of the flexible pivot (200) according to this same first degree of freedom in rotation RZ .
    公开号:CH714922A2
    申请号:CH5182018
    申请日:2018-04-23
    公开日:2019-10-31
    发明作者:Winkler Pascal；Helfer Jean-Luc
    申请人:Eta Sa Mft Horlogere Suisse；
    IPC主号:
    专利说明:

    Description
    FIELD OF THE INVENTION The invention relates to a timepiece resonator mechanism, comprising a structure and an anchoring block from which is suspended at least one inertial element arranged to oscillate according to a first degree of freedom in rotation RZ around d a pivot axis extending in a first direction Z, said inertial element being subjected to restoring forces exerted by a flexible pivot comprising a plurality of first elastic blades each fixed, at a first end to said anchoring block, and at a second end to said inertial element, each said elastic blade being deformable essentially in an XY plane perpendicular to said first direction Z, said resonator mechanism comprising axial stop means comprising at least one first axial stop and / or a second axial stop for limit the translational travel of said inertial element at least according to said first direction Z, said axial stop means being arranged to cooperate in abutment support with said inertial element for the protection of said first blades at least against axial shocks in said first direction Z.
    The invention also relates to a clock oscillator comprising at least one such resonator mechanism.
    The invention also relates to a timepiece movement comprising at least one such oscillator and / or such a resonator mechanism.
    The invention also relates to a watch comprising such a clockwork movement, and / or such an oscillator, and / or such a resonator mechanism.
    The invention relates to the field of watchmaking resonators, and in particular those which include elastic blades acting as return means for operating the oscillator.
    BACKGROUND OF THE INVENTION Impact resistance is a delicate point for most horological oscillators, and in particular for cross-blade resonators. In fact, during out-of-plane shocks, the stress suffered by the blades quickly reaches very high values, which reduces the travel that the part can travel before yielding.
    Shock absorbers for timepieces are available in many variants. However, their main purpose is to protect the fragile pivots of the axle, and not the elastic elements, such as conventionally the spiral spring.
    Document EP 3 054 357 A1 in the name of ETA Manufacture Horlogère Suisse SA describes a horological oscillator comprising a structure and separate primary resonators, temporally and geometrically phase-shifted, each comprising a mass biased towards the structure by an elastic return means . This oscillator comprises coupling means for the interaction of the primary resonators, comprising motor means for driving in motion a mobile which comprises drive and guide means arranged to drive and guide a control means articulated with transmission means. , each articulated, at a distance from the control means, with a mass of a primary resonator. The primary resonators and the mobile are arranged in such a way that the axes of the articulations of any two of the primary resonators and the axis of articulation of the control means are never coplanar.
    Document EP 3 035 127 A1 in the name of SWATCH GROUP RESEARCH & DEVELOPMENT Ltd describes a timepiece oscillator comprising a resonator constituted by a tuning fork which comprises at least two oscillating moving parts, fixed to a connecting element by elements flexible whose geometry determines a virtual pivot axis of determined position relative to a plate, and around which oscillates the respective movable part, whose center of mass coincides in the rest position with the respective virtual pivot axis. For at least one movable part, the flexible elements consist of elastic blades crossed at a distance from each other in two parallel planes, the projections of the directions of which on one of the parallel planes intersect at the level of the pivot axis virtual part of the mobile part.
    New mechanism architectures make it possible to maximize the quality factor of a resonator, by the use of flexible guidance with the use of an anchor escapement with a very small lifting angle, according to demand. CH 01 544/16 on behalf of ETA Manufacture Horlogère Suisse and its derivatives, the teachings of which are directly usable in the present invention, and the resonator of which can be further improved with regard to its sensitivity to shocks, according to certain particular directions. It is therefore a question of protecting the blades from breaking in the event of impacts. We realize that the shockproof systems proposed to date for resonators with flexible guides, protect the blades from shocks in certain directions only, but not in all directions, or when they have the defect of letting the light move slightly. installation of the flexible pivot according to its oscillation rotation, which should be avoided as much as possible.
    权利要求:
    Claims (20)
    [1]
    Summary of the invention It is therefore a question of protecting the blades from breaking in the event of impacts. In other words, to make a good rotary resonator with flexible guidance, the latter, which constitutes a flexible pivot and defines a virtual pivot axis, must be both very flexible for the oscillation rotation according to a first degree of freedom in rotation RZ, but it must be very rigid according to the
    CH 714 922 A2 other degrees of freedom (X, Y, Z, RX, RY) so as to avoid parasitic movements of the center of mass of the resonator. Indeed, such parasitic movements can cause gait errors, if the orientation of the resonator changes in the gravity field (we speak of position error). The suspension of the pivot recess must be very rigid depending on the degree of freedom of oscillation, so as not to disturb the isochronism of the resonator, and not to dissipate energy via movements due to reaction forces.
    The invention proposes to limit the out-of-plane displacement travel of the blades of a blade resonator, and therefore to ensure better performance of the system.
    To this end, the invention relates to a reed resonator mechanism according to claim 1.
    The invention also relates to a clock oscillator comprising at least one such resonator mechanism.
    The invention also relates to a timepiece movement comprising at least one such resonator mechanism.
    The invention also relates to a watch comprising such a clockwork movement, and / or such a resonator mechanism.
    Brief description of the drawings [0017] Other characteristics and advantages of the invention will appear on reading the detailed description which follows, with reference to the accompanying drawings, where:
    fig. 1 shows, schematically, and in plan view, a resonator mechanism with elastic blades, comprising an inertial mass suspended from an anchoring block by a flexible pivot comprising two parallel levels of elastic blades, the directions in which extend these blades crossing, in projection, at the level of a virtual pivot axis of this inertial element, according to the request according to the request CH 01 544/16 in the name of ETA Manufacture Horlogère Suisse, and the lessons of which can be used in the case of the present invention;
    fig. 2 shows, schematically, and in perspective, the different degrees of freedom of the inertial mass that the resonator mechanism of FIG. 1;
    fig. 3 shows, schematically, and in section passing through the pivot axis of the inertial mass, the shock-absorbing stop system that the invention comprises, on either side of the inertial mass, and carried by a fixed structure ;
    fig. 4 shows, schematically, and in perspective, a resonator mechanism according to the invention, comprising a flexible suspension system according to 5 degrees of freedom but rigid according to the unique degree of freedom in which said pivot works, where its flexural connections in X and Y are each secured by two parallel flexible blades, the stop system in fig. 3 not shown;
    fig. 5 is a block diagram representing a watch comprising a movement with an oscillator which itself comprises a resonator mechanism according to the invention;
    fig. 6 represents, schematically, and in perspective, the inertial mass between the stops, and examples of limitation in extreme angular positions according to the degrees of freedom in rotation RX and RY;
    fig. 7 is a detail of FIG. 4 comprising only the flexible pivot and the flexible suspension, in a particular monobloc version;
    fig. 8 is a partial top view of the resonator of FIG. 4;
    fig. 9 illustrates a variant of FIG. 7, where the bending connections in X and Y are provided by more than two parallel flexible blades.
    Detailed description of the preferred embodiments The idea here is to suspend a flexible pivot 200 from a timepiece resonator 100 from a suspension system flexible according to 5 degrees of freedom but rigid according to the single degree of freedom in which said pivot works and which is that of the oscillation of at least one inertial element 2, which comprises this resonator 100. The 5 flexible degrees of freedom, which correspond to the directions in which shocks could damage the blades of the pivot, have a stroke limited by stops, against which the inertial element of the resonator comes to bear in the event of an impact.
    The present description more particularly illustrates the case of a mechanical watch movement, provided with a resonator 100 with flexible rotary guide, which constitutes a flexible pivot 200 defining a virtual pivot axis D in a first direction Z. This flexible pivot 200 is produced in this particular case on the basis of flexible blades 3, which are, according to the invention, protected from breaking in the event of impact by an anti-shock system comprising a flexible suspension,
    CH 714 922 A2 which connects the anchor of the flexible pivot 200 to a structure 1, in particular the movement plate, in combination with a set of stops which are arranged to limit the travel of the inertial element of the resonator via surfaces of support. According to the invention, this shockproof system is flexible according to 5 degrees of freedom, and rigid according to the degree of freedom corresponding to the oscillation of the resonator, here the first direction Z. And the stops allow the inertial element 2 to move freely according to the degree of freedom of oscillation of the resonator, but limit its travel for the other 5 degrees of freedom.
    The invention thus relates to a clockwork resonator mechanism 100, comprising a structure 1 and an anchoring block 30, from which is suspended at least one inertial element 2. Each inertial element 2 is arranged to oscillate according to a first degree of freedom in rotation RZ about a pivot axis D extending in a first direction Z. The center of inertia resulting from the set of inertial elements 2 is aligned on the pivot axis D.
    The invention is illustrated, without limitation, in the figures, with a single inertial element 2, those skilled in the art will be able to transpose the teachings of the present application to the case of a plurality of inertial elements, in particular bunk.
    The inertial element 2 is subjected to restoring forces exerted by a flexible pivot 200 comprising a plurality of first elastic blades 3, each fixed, at a first end to the anchoring block 30, and at a second end to the inertial element 2. Each elastic plate 3 is deformable essentially in an XY plane perpendicular to the first direction Z.
    The resonator mechanism 100 includes axial stop means, which comprise at least a first axial stop 7 and / or a second axial stop 8 to limit the translational travel of the inertial element 2, at least in the first direction Z. These axial stop means are arranged to cooperate in abutment support with the inertial element 2 for the protection of the first blades 3, at least against axial shocks in the first direction Z.
    According to the invention, the anchor block 30 is suspended from the structure 1 by a flexible suspension 300, which is arranged to allow the mobility of the anchor block 30 according to five flexible degrees of freedom of the suspension.
    These five flexible degrees of freedom of the suspension are:
    - A first degree of freedom in translation in the first direction Z;
    - A second degree of freedom in translation in a second direction X orthogonal to the first direction Z;
    a third degree of freedom in translation in a third direction Y orthogonal to the second direction X and to the first direction Z;
    - a second degree of freedom in rotation RX around an axis extending in the second direction X;
    - and a third degree of freedom in rotation RY around an axis extending in the third direction Y.
    In sum, the anchor block 30 is suspended from the structure 1 by the flexible suspension 300, in a manner suitable for allowing it a certain mobility according to all the degrees of freedom other than the first degree of freedom in rotation. > RZ according to which only the inertial element 2 must be mobile, to avoid any disturbance of its oscillation, which is essential for the invention. The anchoring block 30 carries the flexible pivot 200 to which the inertial element 2 is suspended, and the rigidity of the suspension 300 according to the first degree of freedom in rotation RZ must be very much greater than the rigidity of the flexible pivot 200 according to this same first degree of freedom in rotation RZ.
    On each of the other five flexible degrees of freedom of the suspension listed above, the condition is opposite: the rigidity of the suspension according to each of these five flexible degrees of freedom of the suspension must be much less than that of the pivot flexible 200 according to the same degree of freedom considered.
    We define here the rigidity, for a degree of freedom "i", as:
    - in rotation C, = dMoment / dAngle;
    - in translation K, = dForce / dDéplacement.
    The following matrix expresses the relative conditions between the rigidity of the suspension and that of the pivot, for each degree of freedom:
    Degree of freedom i Suspension Condition Pivot
    The essential degree of freedom of the pivot:
    RZ C RZ susp > N. C RZ pivot
    And the five flexible degrees of freedom of the suspension:
    XK x susp <1 / M. K x pivot
    YK Y susp <1 / M. K Y pivot
    CH 714 922 A2
    Z K z susp <1 / M. K z pivot RX r * suspL »RX < 1 / M. C RX pivot RY C RY susp < 1 / M. C RY pivot
    The value N is preferably chosen to be greater than or equal to 10, and in particular greater than or equal to 100 or even to 1000.
    The value Μ is preferably chosen to be greater than or equal to 10, and in particular greater than or equal to 50.
    Thus, the flexible suspension 300 is, according to the first degree of freedom in rotation RZ, at least N times, in particular 10 times, more rigid than is the flexible pivot 200 according to the first degree of freedom in rotation RZ .
    And the flexible suspension 300 is, according to the first degree of freedom in translation, the second degree of freedom in translation, the third degree of freedom in translation, the second degree of freedom in rotation RX, the third degree of freedom in rotation RY, at least Μ times, in particular 10 times, less rigid than is the flexible pivot 200 according to said first degree of freedom in translation, said second degree of freedom in translation, said third degree of freedom in translation, said second degree of freedom in rotation RX, said third degree of freedom in rotation RY.
    Therefore, the flexible suspension 300 is, according to the first degree of freedom in translation, the second degree of freedom in translation, the third degree of freedom in translation, the second degree of freedom in rotation RX, the third degree of freedom in rotation RY, at least N.Μ times, in particular 100 times, less rigid than it is according to the first degree of freedom in rotation RZ.
    More particularly, the flexible suspension 300 is, according to the first degree of freedom in rotation RZ, at least 100 times more rigid than is the flexible pivot 200 according to the first degree of freedom in rotation RZ. In other words, the rigidity according to the most rigid degree of freedom of the suspension is at least 100 times greater than the rigidity of the flexible pivot of the resonator.
    More particularly still, the flexible suspension 300 is, according to the first degree of freedom in rotation RZ, at least 1000 times more rigid than is the flexible pivot 200 according to the first degree of freedom in rotation RZ.
    More particularly, the flexible suspension 300 is, according to the first degree of freedom in translation, the second degree of freedom in translation, the third degree of freedom in translation, the second degree of freedom in rotation RX, the third degree of freedom in rotation RY, at least 50 times less rigid than is the flexible pivot 200 according to said first degree of freedom in translation, said second degree of freedom in translation, said third degree of freedom in translation, said second degree of freedom in rotation RX, said third degree of freedom in rotation RY.
    The rigidity of each of the 5 flexible degrees of freedom can be calculated according to the relationship:
    Ki = fs * mi * ari / xi where:
    - fs is a safety factor less than 1;
    - mi is the mass or inertia for the degree of freedom i;
    - ari is the acceleration according to the degree of freedom i, which would cause a rupture of the flexible pivot, according to the "direction" i;
    - xi is the distance between the stop and said resonator support surface, in other words, the travel of the resonator according to the degree of freedom i until the stop.
    In a variant, the flexible suspension 300 includes a first elastic connection, which is arranged to allow its mobility according to the first degree of freedom in translation in the first direction Z, and / or a second elastic connection arranged to allow its mobility according to the second degree of freedom in translation in the second direction X, and / or a third elastic link arranged to allow its mobility according to the third degree of freedom in translation in the third direction Y, and / or a fourth elastic link arranged to allow its mobility in rotation according to the second degree of freedom in rotation RX, and / or a fifth elastic link arranged to allow its mobility in rotation according to the third degree of freedom in rotation RY.
    Advantageously, the axial stop means are further arranged to cooperate in abutment support with the inertial element 2 for the protection of the first blades 3 in the second direction X, in the third direction Y, in the second degree of freedom in rotation RX, and according to the third degree of freedom in rotation RY. These axial abutment means comprise first bearing surfaces 79, 89, radial, which are arranged to cooperate with first complementary bearing surfaces 279,289, which comprises the inertial element 2, and second bearing surfaces 78, 88, which are arranged to cooperate with second complementary bearing surfaces 278, 288, which comprises the inertial element 2. More particularly, these abutment means are carried by the structure I. The lessons of the application CH 01 511 / 16 in the name of Swatch Group Research & Development Ltd can be used in the case of the present invention.
    As visible in Figs. 3 and 6, in a variant, the stop means comprise a first axial stop 7 and a second axial stop 8 which are cylinders in range, arranged on either side of the inertial element 2 according to
    CH 714 922 A2 the axis of oscillation of the resonator parallel to the first direction Z. And the first complementary bearing surfaces 279.289, here are bores of the inertial element 2, which extend in the first direction Z, on either side of the inertial element 2. And the second bearing surfaces 78, 88, are substantially flat, and arranged to cooperate with an edge of one of the cylinders in range during a movement according to the degree of freedom RX or RY. Fig. 6 illustrates in broken lines two configurations of angular stop in RX and in RY, respectively by contacts at points 7RX and 7RY between the first stop 7 and the inertial mass 2.
    Advantageously, the flexibility of the elastic means, which comprises the flexible suspension, is, according to the five flexible degrees of freedom of the suspension, such that the frequencies of the natural modes of vibration of the flexible suspension are, according to these five degrees of freedom, at least 10 times greater than the main oscillation frequency of the resonator during the oscillation of the inertial mass 2. More particularly, they are at least 50 times greater than the main oscillation frequency of the resonator during the 'Oscillation of the inertial mass 2. Advantageously, this main oscillation frequency of the resonator is high, greater than 10 Hz, in particular close to 20 Hz.
    It is understood that many alternative arrangements are possible to allow the bending and / or twisting of some of these elastic connections, in particular by decoupling or not the degrees of freedom, which can lead to having five different elastic connections , and four intermediate masses between the structure 1 and the anchor block 30. However, to save volume, which is always rare in a watch, it is advantageous to couple several degrees of freedom on certain links.
    In a variant, a plate, which comprises at least two flexible parallel and coplanar blades, provides the first elastic mobility link according to the first degree of freedom in translation in the first direction Z, the fourth elastic mobility link in rotation according to the second degree of freedom in rotation RX, and the fifth elastic link of mobility in rotation according to the third degree of freedom in rotation RY: it controls the flexibility according to the degrees of freedom Z, RX and RY. Figs. 4, 7, and 9 illustrate such a plate 301 with its two flexible blades 302.
    In another variant, the mobility according to the second degree of freedom in translation in the second direction X is provided by a set of flexible blades comprising at least two parallel flexible blades and not coplanar, and / or mobility according to the third degree freedom of translation in the third direction Y is ensured by a set of flexible blades comprising at least two parallel flexible blades and not coplanar.
    In yet another variant, the mobility according to the second degree of freedom in translation in the second direction X, and according to the second degree of freedom in rotation RX, is provided by a single flexible blade deformable essentially in a plane XY perpendicular to the first direction Z and arranged to tolerate a twist of +/- 10 ° relative to its longitudinal direction.
    Similarly in another variant, the mobility according to the third degree of freedom in translation in the third direction Y, and according to the third degree of freedom in rotation RY, is ensured by a single flexible blade deformable essentially in a plane XY perpendicular to the first direction Z and arranged to tolerate a twist of +/- 10 ° relative to its longitudinal direction.
    Naturally, a lower number of elastic connections can be used, if the conditions relating to the inequalities to be observed between the rigidities are met.
    Figs. 4, 7, and 8 illustrate a particular non-limiting embodiment, where a plate 301, comprising two coplanar parallel blades 302, is fixed to the structure 1, and allows a mobility along Z of a first intermediate mass 303. The latter carries two non-coplanar parallel flexible blades 304, providing X-shaped mobility to a second intermediate mass 305, which carries, through two non-coplanar parallel flexible blades 306, the anchoring block 30, allowing it mobility in Y. mobility according to RX and RY are limited, and are allowed only by the slight twist possible of blades 302, 304 and 306.
    More particularly, the elastic blades 3 of the elastic pivot 200 are straight, and the directions in which the elastic blades 3 extend are, in projection on a plane perpendicular to this pivot axis D, crossed at the pivot axis D. More particularly, these elastic blades are arranged according to the teachings of requests CH 00 111/16 in the name of ETA Manufacture Horlogère Suisse and CH 01 979/14 in the name of Swatch Group Research & Development Ltd.
    More particularly, the pivot is of the type with large angular travel, according to application CH 00 980/17 on behalf of Swatch Group Research & Development Ltd.
    In a variant not illustrated, the mechanical interaction between the axial stop means and surfaces of the inertial element 2 is supplemented by a magnetic interaction between these axial stop means and these surfaces.
    More particularly, the inertial element 2 comprises at least one counterweight 29, adjustable in position and / or orientation for the adjustment adjustment of the positioning of its center of mass and its inertia.
    Advantageously, the mass MA of the anchor block 30, like the mass of any intermediate block, such as the first intermediate mass 303 or the second intermediate mass 305, which is interposed in the flexible suspension between the anchor block 30 and the structure 1 is less than one tenth of the mass MO of the inertial element 2.
    CH 714 922 A2 The invention also relates to a clockwork oscillator mechanism 500 comprising such a clockwork resonator mechanism 100, and an escapement mechanism 400, arranged to cooperate with one another. The inertial element 2 here includes a pin 28 for this purpose.
    The invention also relates to a timepiece movement 1000 comprising at least one such oscillator mechanism 500, and / or at least one such resonator mechanism 100. This movement 1000 carries, on the structure 1, an energy source 1100 such as a barrel, powering a gear train 1200 producing the display and coupled with the escapement mechanism 400. In a variant, this movement is provided with a Swiss anchor escapement.
    In another variant, this movement is provided with a friction-rest escapement.
    In yet another variant, this movement is provided with an escapement at magnetic rest.
    [0061] FIG. 9 illustrates a variant in which the guiding in translation in X, as in Y, has more than two parallel blades, in order to increase its rigidity without increasing the maximum stress that one would have by thickening the two blades of Figs. 4, 7, and 8.
    Advantageously, the flexible pivot is made of silicon thermally compensated by a layer of silicon dioxide. In a particular embodiment, the flexible suspension 300 and the anchor block 30 constitute a one-piece assembly.
    In another particular embodiment, the flexible suspension 300 and the flexible pivot 200 constitute a one-piece assembly.
    Advantageously, the exhaust mechanism 400 includes at least one of its silicon components, or the like, to minimize its inertia, and in particular an openwork component, such as the escape wheel of FIG. Advantageously, the inertial element is an at least locally perforated lattice structure in order to minimize its mass / inertia ratio.
    The invention also relates to a watch 2000 comprising at least one such movement 1000, and / or at least one such oscillator mechanism 500, and / or at least one such resonator mechanism 100.
    The invention makes it possible to decouple the useful degree of freedom of the flexible pivot from the degrees of freedom of the suspension. In this way, the suspension protects the pivot from breaking during impacts for five degrees of freedom, without interfering with the rigidity of the useful pivot according to the degree of freedom it defines. Without this decoupling of the degrees of freedom, the suspension would allow the embedding of the blades to move, and this would result in a significant reduction in the quality factor of the resonator. If the suspension were infinitely rigid, it would result in a rupture of the pivot blades during accidental impacts. Thus, the invention makes it possible to protect the flexible pivot from rupture without altering the qualities of the resonator.
    claims
    1. Clockwork resonator mechanism (100), comprising a structure (1) and an anchoring block (30) to which is suspended at least one inertial element (2) arranged to oscillate according to a first degree of freedom in rotation RZ around a pivot axis (D) extending in a first direction Z, said inertial element (2) being subjected to restoring forces exerted by a flexible pivot (200) comprising a plurality of first elastic blades (3) each fixed, at a first end to said anchor block (30), and at a second end to said inertial element (2), each said elastic blade (3) being deformable essentially in an XY plane perpendicular to said first direction Z, said mechanism resonator (100) comprising axial stop means comprising at least a first axial stop (7) and / or a second axial stop (8) to limit the translational travel of said inertial element (2) at least according to lad ite first direction Z, said axial stop means being arranged to cooperate in abutment support with said inertial element (2) for the protection of said first blades (3) at least against axial shocks in said first direction Z, characterized in that said anchor block (30) is suspended from said structure (1) by a flexible suspension (300) arranged to allow the mobility of said anchor block (30) according to five flexible degrees of freedom of the suspension which are a first degree of freedom in translation in said first direction Z, a second degree of freedom in translation in a second direction X orthogonal to said first direction Z, a third degree of freedom in translation in a third direction Y orthogonal to said second direction X and to said first direction Z, a second degree of freedom in rotation RX about an axis extending in said second direction X, and a third degree of freedom in rotation RY about an axis extending in said third direction Y, characterized in that said flexible suspension (300) is, according to said first degree of freedom in rotation RZ, at least 10 times more rigid than is said flexible pivot (200) according to said first degree of freedom in rotation RZ, and further characterized in that said flexible suspension (300) is, according to said first degree of freedom in translation, said second degree of freedom in translation, said third degree of freedom in translation, said second degree of freedom in rotation RX, said third degree of freedom in rotation RY, at least 10 times less rigid than said flexible pivot (200) according to said first degree respectively of freedom in translation, said second degree of freedom in translation, said third degree of freedom in translation, said second degree of freedom in rotation RX, and said tr third degree of freedom in rotation RY.
    CH 714 922 A2
    [2]
    2. Resonator mechanism (100) according to claim 1, characterized in that said flexible suspension (300) is, according to said first degree of freedom in rotation RZ, at least 100 times more rigid than is said flexible pivot (200 ) according to said first degree of freedom in rotation RZ.
    [3]
    3. Resonator mechanism (100) according to claim 2, characterized in that said flexible suspension (300) is, according to said first degree of freedom in rotation RZ, at least 1000 times more rigid than is said flexible pivot (200 ) according to said first degree of freedom in rotation RZ.
    [4]
    4. Resonator mechanism (100) according to one of claims 1 to 3, characterized in that said flexible suspension (300) is, according to said first degree of freedom in translation, said second degree of freedom in translation, said third degree of freedom in translation, said second degree of freedom in rotation RX, said third degree of freedom in rotation RY, at least 50 times less rigid than is said flexible pivot (200) according to said first degree of freedom respectively in translation, said second degree of freedom in translation, said third degree of freedom in translation, said second degree of freedom in rotation RX, and said third degree of freedom in rotation RY.
    [5]
    5. Resonator mechanism (100) according to one of claims 1 to 3, characterized in that said flexible suspension (300) has a first elastic connection arranged to allow its mobility according to said first degree of freedom in translation in said first direction Z , and / or a second elastic link arranged to authorize its mobility according to said second degree of freedom in translation in said second direction X, and / or a third elastic link arranged to authorize its mobility according to said third degree of freedom in translation according to said third direction Y, and / or a fourth elastic link arranged to allow its mobility in rotation according to said second degree of freedom in rotation RX, and / or a fifth elastic link arranged to allow its mobility in rotation according to said third degree of freedom in rotation RY .
    [6]
    6. Resonator mechanism (100) according to one of claims 1 to 5, characterized in that said axial stop means are further arranged to cooperate in abutment support with said inertial element (2) for the protection of said first blades (3 ) in said second direction X, in said third direction Y, in said second degree of freedom in rotation RX, and in said third degree of freedom in rotation RY, and comprise first radial bearing surfaces (79; 89) arranged for cooperate with first complementary bearing surfaces (279; 289) that comprises said inertial element (2), and second bearing surfaces (78; 88) arranged to cooperate with second complementary bearing surfaces (278; 288 ) that includes said inertial element (2).
    [7]
    7. Resonator mechanism (100) one of claims 1 to 6, characterized in that said stop means are carried by said structure (1).
    [8]
    8. Resonator mechanism (100) according to claim 6 or 7, characterized in that said abutment means comprise a first said axial abutment (7) and a second said axial abutment (8) which are bearing cylinders arranged on one side and other of said inertial element (2) along the axis of oscillation of the resonator parallel to said first direction Z, and in that said first complementary bearing surfaces (279; 289) are bores of said inertial element (2) which extend in said first direction Z, and in that said second bearing surfaces (78; 88) are substantially planar and arranged to cooperate with an edge of one of said cylinders in range.
    [9]
    9. Resonator mechanism (100) according to one of claims 1 to 8, characterized in that the flexibility of elastic means that comprises said flexible suspension is, according to said five flexible degrees of freedom of the suspension, such that the frequencies of the modes The vibration vibration of said flexible suspension are, according to these five degrees of freedom, at least 10 times greater than the main oscillation frequency of the resonator during the oscillation of said inertial mass (2).
    [10]
    10. Resonator mechanism (100) according to claim 5 or one of claims 6 to 9when they depend on claim 5, characterized in that a plate comprising at least two parallel and coplanar flexible blades provides said first elastic mobility link according to said first degree of freedom in translation in said first direction Z, said fourth elastic link of rotational mobility according to said second degree of freedom in rotation RX, and said fifth elastic link of rotational mobility according to said third degree of freedom in rotation RY .
    [11]
    11. Resonator mechanism (100) according to claim 5 or one of claims 6 to 10 when they depend on claim 5, characterized in that the mobility according to said second degree of freedom in translation in said second direction X is ensured by a set of flexible blades comprising at least two parallel flexible blades and not coplanar, and / or in that the mobility according to said third degree of freedom in translation in said third direction Y is ensured by a set of flexible blades comprising at least two blades flexible parallel and not coplanar.
    [12]
    12. Resonator mechanism (100) according to claim 5 or one of claims 6 to 10 when they depend on claim 5, characterized in that the mobility according to said second degree of freedom in translation in said second direction X, and according said second degree of freedom in rotation RX, is provided by a single flexible blade which is deformable essentially in an XY plane perpendicular to said first direction Z and arranged to tolerate a twist of +/- 10 ° relative to its longitudinal direction.
    CH 714 922 A2
    [13]
    13. Resonator mechanism (100) according to claim 5 or one of claims 6 to 10 when they depend on claim 5, characterized in that mobility according to said third degree of freedom in translation in said third direction Y, and in said third degree of freedom in rotation RY, is ensured by a single flexible blade deformable essentially in a plane XY perpendicular to said first direction Z and arranged to tolerate a twist of +/- 10 ° relative to its longitudinal direction.
    [14]
    14. Clock mechanism resonator (100) according to one of claims 1 to 13, characterized in that said elastic blades (3) are straight, and in that the directions in which extend said elastic blades (3) are, in projection on a plane perpendicular to said pivot axis (D), crossed at said pivot axis (D).
    [15]
    15. Clock mechanism (100) according to one of claims 1 to 14, characterized in that the mechanical interaction between said axial abutment means and surfaces of said at least one inertial element (2) is supplemented by a magnetic interaction between said axial stop means and said surfaces of said at least one inertial element (2).
    [16]
    16. Clock mechanism (100) according to one of claims 1 to 15, characterized in that said inertial element (2) comprises at least one counterweight adjustable in position and / or orientation for adjusting the positioning of its center of inertia.
    [17]
    17. Clock mechanism resonator (100) according to one of claims 1 to 16, characterized in that the mass MA of said anchor block (30), like the mass of any intermediate block interposed in said flexible suspension between said anchor block (30) and said structure (1), is less than one tenth of the mass MO of said inertial element (2).
    [18]
    18. Clock oscillator mechanism (500) comprising a clock resonator mechanism (100) according to one of claims 1 to 17, and an escapement mechanism (400), arranged to cooperate with each other ,
    [19]
    19. Clock movement (1000) comprising at least one oscillator mechanism (500) according to claim 18 and / or at least one resonator mechanism (100) according to one of claims 1 to 17.
    [20]
    20. Watch (2000) comprising at least one movement (1000) according to claim 19 and / or at least one oscillator mechanism (500) according to claim 18 and / or at least one resonator mechanism (100) according to one of claims 1 to 17.
    CH 714 922 A2
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    同族专利:
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EP3839651A1|2019-12-19|2021-06-23|Patek Philippe SA Genève|Mechanical timepiece oscillator with flexible guide|CA824366A|1965-09-03|1969-10-07|Altenburger Paul|Method of assembly of resonator|
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    DE602008006057D1|2008-07-04|2011-05-19|Swatch Group Res & Dev Ltd|Coupled resonators for clock|
    EP2891930B1|2013-12-23|2018-09-19|The Swatch Group Research and Development Ltd.|Device for regulating the angular speed of a mobile in a clock movement comprising a magnetic escapement|
    WO2015104693A2|2014-01-13|2015-07-16|Ecole Polytechnique Federale De Lausanne |General 2 degree of freedom isotropic harmonic oscillator and associated time base without escapement or with simplified escapement|
    EP2894521A1|2014-01-13|2015-07-15|Ecole Polytechnique Federale de Lausanne |Isotropic harmonic oscillator and associated time base without escapement or simplified escapement|
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    EP3035127B1|2014-12-18|2017-08-23|The Swatch Group Research and Development Ltd.|Clock oscillator with tuning fork|
    CH710692B1|2015-02-03|2021-09-15|Eta Sa Mft Horlogere Suisse|Clockwork oscillator mechanism.|
    WO2016192957A1|2015-06-03|2016-12-08|Eta Sa Manufacture Horlogère Suisse|Resonator with fine adjustment by index-assembly|
    EP3356690B1|2015-09-29|2019-08-14|Patek Philippe SA Genève|Mechanical component with flexible pivot, in particular for clockmaking|
    CH713166B1|2016-11-16|2021-10-29|Swatch Group Res & Dev Ltd|Protection of the blades of a mechanical watch resonator in the event of an impact.|EP3824353A1|2018-07-16|2021-05-26|Patek Philippe SA Genève|Flexure pivot oscillator insensitive to gravity|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    EP18168765.8A|EP3561609A1|2018-04-23|2018-04-23|Shock protection of a resonator mechanism with rotatable flexible guiding|
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