阅读说明：本技术 包括具有长角向行程的柔性轴承的钟表振荡器 (Timepiece oscillator comprising a flexible bearing with a long angular travel ) 是由 G·迪多梅尼科 P·屈赞 J-L·黑尔费尔 A·甘德尔曼 P·温克勒 B·伊诺 D·莱乔 于 2019-06-24 设计创作，主要内容包括：本发明涉及一种机械钟表振荡器(100),包括在第一元件(4)和第二惯性元件(5)之间的两个或以上不同的柔性条带(31；32),其将惯性元件(5)返回到振荡平面中的休止位置,其中这些条带的投影在交叉点(P)处彼此交叉,第二惯性元件(5)的枢转轴线穿过该交叉点,并且对于每个条带(31；32),高度与厚度的纵横比小于10。(The invention relates to a mechanical timepiece oscillator (100) comprising two or more distinct flexible strips (31; 32) between a first (4) and a second (5) inertia element, which return the inertia elements (5) to a rest position in an oscillation plane, wherein the projections of the strips cross each other at a point of intersection (P) through which the pivot axis of the second inertia element (5) passes, and wherein for each strip (31; 32) the aspect ratio of height to thickness is less than 10.)

1. Mechanical timepiece oscillator (100) comprising a flexible bearing between a first rigid support element (4) and a second massive inertial element (5), the flexible bearing comprising at least two first flexible strips (31; 32) supporting the second massive inertial element (5) and arranged to return the latter to a rest position, wherein the second massive inertial element (5) is arranged to oscillate angularly in an oscillation plane about the rest position, the two first flexible strips (31; 32) are not in contact with each other and their projections on the oscillation plane intersect at the rest position, the rotation axis of the second massive inertial element (5) perpendicular to the oscillation plane is adjacent to or passes through the intersection, and the first flexible strips (31; 32) are at the intersection of the first rigid support element (4) and the second massive inertial element (5) The embedding points define two strip directions (DL1, DL2) parallel to the oscillation plane, each of the strips (31; 32) having an aspect ratio RA H/E, where H is the height of the strip (31; 32) perpendicular to the oscillation plane and perpendicular to the elongation of the strip (31; 32) along the length L, and E is the thickness of the strip (31; 32) in the oscillation plane and perpendicular to the elongation of the strip (31; 32) along the length L, characterized in that, for each of the strips (31; 32), the aspect ratio RA H/E is less than 10.

2. The mechanical oscillator (100) of claim 1, wherein the oscillator (100) comprises a first number N1 of the first stripes, called primary stripes (31), extending in a first stripe direction (DL1), and a second number N2 of the first stripes, called secondary stripes (32), extending in a second stripe direction (DL2), the first number N1 and the second number N2 each being greater than or equal to 2.

3. The mechanical oscillator (100) of claim 2, wherein the first number N1 is equal to the second number N2.

4. The mechanical oscillator (100) of claim 2, comprising at least one pair of strips formed by one said primary strip (31) extending in a first strip direction (DL1) and one said secondary strip (32) extending in a second strip direction (DL2), and in each pair of strips, the primary strip (31) is identical to the secondary strip (32) except for its orientation.

5. The mechanical oscillator (100) of claim 4, comprising only a plurality of said pairs of strips each formed by one said primary strip (31) extending in a first strip direction (DL1) and one said secondary strip (32) extending in a second strip direction (DL2), and in each pair, the primary strip (31) is identical to the secondary strip (32) except for orientation.

6. The mechanical oscillator (100) of claim 2, comprising at least one set of strips formed by one said primary strip (31) extending in a first strip direction (DL1) and a plurality of said secondary strips (32) extending in a second strip direction (DL2), and in each set of strips, the elastic behavior of the primary strip (31) is identical to the elastic behavior produced by the plurality of secondary strips (32), except for orientation.

7. The mechanical oscillator (100) of claim 1, wherein the first strip (31; 32) is a straight strip.

8. Mechanical timepiece oscillator (100) according to claim 1, wherein in the rest position an apex angle a is formed between the projections on the oscillation plane of the two strip directions (DL 1; DL2) parallel to the oscillation plane, the position of the intersection point (P) being defined by the ratio X ═ D/L, where D is the distance between the projection on the oscillation plane of one of the embedding points of the first strip (31; 32) on the first rigid support element (4) and the intersection point (P), L is the total length of the projection on the oscillation plane of the strip (31; 32) in its direction of elongation, and the embedding point ratio (D1/L1; D2/L2) is between 0.15 and 0.49 inclusive, or between 0.51 and 0.85 inclusive.

9. The mechanical oscillator (100) of claim 8, wherein the apex angle (a) is less than or equal to 50 °, the ratio of insertion points (D1/L1; D2/L2) being between 0.25 and 0.75 inclusive.

10. The mechanical oscillator (100) of claim 9, wherein the apex angle (a) is less than or equal to 40 °, and the embedding point ratio (D1/L1; D2/L2) is between 0.30 and 0.70, inclusive.

11. The mechanical oscillator (100) of claim 10, wherein the apex angle (a) is less than or equal to 35 °, and the embedding point ratio (D1/L1; D2/L2) is between 0.40 and 0.60, inclusive.

12. The mechanical oscillator (100) of claim 1, wherein the apex angle (a) is less than or equal to 30 °.

13. The mechanical oscillator (100) of claim 1, wherein the apex angle (a) and the ratio X ═ D/L satisfy the relation h1(D/L) < a < h2(D/L), wherein

For X <0.5 > 0.2 ≦ X:

h1(X)＝116-473*(X+0.05)+3962*(X+0.05)³-6000*(X+0.05)⁴，

h2(X)＝128-473*(X-0.05)+3962*(X-0.05)³-6000*(X-0.05)⁴，

for 0.5< X ≦ 0.8:

h1(X)＝116-473*(1.05-X)+3962*(1.05-X)³-6000*(1.05-X)⁴，

h2(X)＝128-473*(0.95-X)+3962*(0.95-X)³-6000*(0.95-X)⁴。

14. the mechanical oscillator (100) of claim 1, wherein the centroid of the oscillator (100) in its rest position is separated from the intersection point (P) by an interval (ε) of 10% to 20% of the total length (L) of the projection of the strips (31; 32) on the oscillation plane.

15. The mechanical oscillator (100) of claim 14, wherein the spacing (ε) is 12% to 18% of a total length (L) of projections of the strips (31; 32) on the oscillation plane.

16. The mechanical oscillator (100) of claim 1, wherein the first strip (31; 32) and its embedding point jointly define a pivot (1), the projection of the pivot (1) on the oscillation plane being symmetrical with respect to a symmetry axis (AA) passing through the intersection point (P).

17. The mechanical oscillator (100) according to claim 16, characterized in that, in the rest position, a projection of the centre of mass of the second massive inertial element (5) on the oscillation plane is located on the symmetry axis (AA) of the pivot (1).

18. The mechanical oscillator (100) according to claim 17, characterized in that the projection of the centroid of the second massive inertia element (5) on the oscillation plane is located at a non-zero distance from the intersection point (P) corresponding to the rotation axis of the second massive inertia element (5), the non-zero distance being comprised between 0.1 and 0.2 times the total length (L) of the projection of the strip (31; 32) on the oscillation plane.

19. Timepiece movement (1000) comprising at least one mechanical oscillator (100) according to claim 1.

20. Watch (2000) comprising at least one timepiece movement (1000) according to claim 19.

Technical Field

The invention relates to a mechanical timepiece oscillator comprising a first rigid support element, a second massive inertia element (solid inertial element), and at least two first flexible strips between the first rigid support element and the second massive inertia element, the at least two first flexible strips supporting the second massive inertia element and being arranged to return the second massive inertia element to a rest position, wherein the second massive inertia element is arranged to oscillate angularly in an oscillation plane around the rest position, the two first flexible strips are not in contact with each other and their projections on the oscillation plane intersect at an intersection point at the rest position, the rotation axis of the second massive inertia element perpendicular to the oscillation plane is immediately adjacent to or passes through the intersection point, and the insertion points of the first flexible strips in the first rigid support element and the second massive inertia element define an insertion point Two strip directions are parallel to the oscillation plane.

The invention also relates to a timepiece movement including at least one such mechanical oscillator.

The invention also relates to a watch comprising such a timepiece movement.

The invention relates to the field of mechanical oscillators for timepieces, comprising a flexible bearing (flexible bearing) with a flexible strip that performs the function of holding and returning a movable element.

Background

The use of flexible bearings, in particular with flexible strips, in mechanical timepiece oscillators can be achieved by processes such as MEMS, LIGA and the like for the development of micro-machined materials, such as silicon and silicon oxide, which allow the highly reproducible manufacture of components with constant elastic properties over time and which are highly insensitive to external factors such as temperature and humidity. Flexible pivots, such as those disclosed in european patent application EP1419039 or EP16155039 by the same applicant, may in particular replace the traditional balance pivot and the balance spring normally associated therewith. Eliminating pivot friction also significantly increases the quality factor of the oscillator. However, the flexible pivots generally have a limited angular travel of about 10 ° to 20 °, which is very low compared to the usual 300 ° amplitude of the balance/balance spring, which means that they cannot be directly combined with traditional escapements, in particular with the usual stop members such as swiss levers or the like, which require a large angular travel to ensure correct operation.

The m.h. kahrobaian team first proposed this increase in angular travel in the article "Gravity sensitive flexible pivots for watchoscillators" in the international horological convention held by monterelle, switzerland at 28 and 29 in 2016, the complex solution envisaged is not isochronous.

EP patent application No 3035127a1 in the name of the same applicant, SWATCH GROUP reset & DEVELOPMENT Ltd, discloses a timepiece oscillator comprising a time base having at least one resonator formed by a tuning fork comprising at least two oscillating kinematic components, wherein said kinematic components are fixed to a connecting element included in said oscillator by flexible elements, the geometry of said flexible elements determining a virtual pivot axis having a determined position with respect to said connecting element, said respective kinematic components oscillating around said virtual pivot axis, and the centre of mass of said kinematic components coinciding, in a rest position, with said respective virtual pivot axis. For at least one of the moving parts, the flexible elements are formed by intersecting elastic strips extending at a distance from each other in two parallel planes, and the directions of their projections on one of the parallel planes intersect at the virtual pivot axis of the moving part concerned.

U.S. patent application No.3628781A in the name of GRIB discloses a tuning fork in the form of a double cantilever structure for imparting a protruding rotational motion to a pair of movable elements relative to a stationary reference plane comprising: a first resiliently deformable body having at least two similar elongate resiliently flexible portions, the ends of each of said flexible portions being respectively integral with enlarged rigid portions of said member, a first of said rigid portions being fixed to define a reference plane and the second being resiliently supported for projecting rotational movement relative to the first; a second elastically deformable body substantially identical to the first elastically deformable body; and means for rigidly securing a first one of said respective rigid portions of said elastically deformable body in spaced relation to provide a tuning fork configuration, wherein each tine of the tuning fork comprises a free end of one of said elastically deformable bodies.

EP patent application No 2911012a1 in the name of CSEM discloses a rotary oscillator for a timepiece comprising a supporting element for allowing the oscillator to be assembled in the timepiece, a balance, a plurality of flexible bands connecting the supporting element to the balance and able to exert a return torque on the balance, and a rim mounted integrally with the balance. The plurality of flex strips includes at least two flex strips, a first strip disposed in a first plane perpendicular to the oscillator plane, and a second strip disposed in a second plane perpendicular to the oscillator plane and intersecting the first plane. The first and second strips have the same geometric shape, and the geometric oscillation axis of the oscillator is defined by the intersection of the first plane and the second plane, which intersects the first and second strips at 7/8 of their respective lengths.

EP patent application No.2998800A2 in the name of PATEK PHILIPPE discloses a timepiece component with a flexible pivot comprising a first monolithic part defining a first rigid portion and a second rigid portion connected by at least one first elastic band, and a second monolithic part defining a third rigid portion and a fourth rigid portion connected by at least one second elastic band, wherein the first and second monolithic parts are assembled to each other so that the first and third rigid portions are integral with each other and the second and fourth rigid portions are integral with each other. The at least one first elastic strip and the at least one second elastic strip cross without contact and define a virtual axis of rotation for the second and fourth rigid portions with respect to the first and third rigid portions. The timepiece component comprises a bearing integral with the second and fourth rigid portions and intended to guide the rotation of an element moving about an axis different from and substantially parallel to the virtual axis of rotation.

European patent application No. ep3130966a1 in the name of ETA Manufacture Horlog de, switzerland discloses a mechanical timepiece movement comprising at least one barrel, a set of gears driven at one end by the barrel, and an escapement with a local oscillator of a resonator in the form of a balance/balance spring and a feedback system for the timepiece movement. The escapement is driven at the other end of the set of gears. The feedback system includes at least one precision reference oscillator combined with a rate comparator to compare the rates of the two oscillators, and a mechanism for adjusting the local oscillator resonator to slow or speed up the resonator based on the comparison of the rate comparator.

ETA SA manual horloge surise swiss patent application No. ch709536a2 discloses a timepiece speed regulating mechanism comprising: an escape wheel mounted for at least pivotal movement relative to the plate, the escape wheel being arranged to receive a drive torque through a gear train; and a first oscillator comprising a first rigid structure connected to said plate by a first elastic return means. The regulating mechanism comprises a second oscillator comprising a second rigid structure connected to said first rigid structure by second elastic return means and comprising bearing means arranged to cooperate with complementary bearing means comprised in said escape wheel, so as to synchronize said first oscillator and said second oscillator by means of said gear train.

European patent application No. ep17183666 to the same applicant, which is incorporated herein by reference, discloses a pivot with a large angular travel. By using an angle between the strips of about 25 ° to 30 ° and an intersection point located at about 45% of their length, and by offsetting the resonator's center of mass relative to the axis of rotation, good isochronism and positional insensitivity can be achieved simultaneously over large angular strokes (up to 40 ° or more). To maximize angular travel while maintaining good out-of-plane stiffness, the straps are made thinner but with greater height. The use of high aspect ratio values, i.e. the ratio of the height of the strip to its thickness, is theoretically advantageous, but in practice, with large angular amplitudes, a suppression of the inverse back curvature (anti-back curvature) is observed, which impairs the isochronous properties of the resonator.

Disclosure of Invention

The present invention proposes to develop a mechanical oscillator with a flexible bearing whose angular travel is compatible with existing escapement mechanisms and whose behavior behaves in a regular manner despite any deformation.

Such a resonator with a rotary flexible bearing must have the following characteristics:

-a high quality factor;

-a large angular travel;

good isochronism;

high spatial insensitivity.

Considering the particular case of a flexible bearing with strips intersecting in projection in a plane parallel to the oscillation plane, where said strips connect a stationary mass and a moving mass, the possible angular travel θ of the pivot depends on the relation X ═ D/L, where on the one hand D is the distance of the embedding point of the strip in the stationary mass from the intersection point and on the other hand L is the total length L of the same strip in its direction of elongation between its two opposite embedding points. The aforementioned work by the m.h. kahrobaiyan team shows that for a given pair of strips having a given apex angle α (here 90 °) at the intersection point, the possible angular travel θ is maximum at X ═ D/L ═ 0.5 and decreases rapidly away from this value in a substantially symmetrical curve. However, such cross-strap pivots are not isochronous at X-D/L-0.5 and α -90 °.

The invention therefore explores the range of advantageous combinations between the value of the apex angle α at the strip intersection and the value of the ratio X ═ D/L to obtain an optimum value of the isochronous pivot axis and of the aspect ratio of each strip.

To this end, the invention relates to a mechanical oscillator according to claim 1.

In particular, the invention shows that it is possible to obtain an isochronous oscillator having pivots satisfying two inequalities simultaneously: 0.15 ≤ (X ═ D/L) 0.85, and α ≤ 60 °.

Of course, configurations in which α is 0 ° are excluded, because the strips no longer intersect in the projection, but are parallel to each other.

The invention also relates to a timepiece movement including at least one such mechanical oscillator.

The invention also relates to a watch comprising such a timepiece movement.

Drawings

Other features and advantages of the present invention will become apparent upon reading the following detailed description and upon reference to the drawings in which:

fig. 1 shows a schematic perspective view of a first variant of a mechanical oscillator comprising a first rigid support element of elongate shape for attaching the mechanical oscillator to a plate or similar of a movement, on which a second massive inertia element is suspended by two unconnected flexible strips, the projections of which on the oscillation plane of said second inertia element intersect, said second inertia element cooperating with a traditional swiss lever escapement with a standard escape wheel.

Fig. 2 shows a schematic perspective view of the oscillator of fig. 1.

Fig. 3 shows a schematic cross-sectional view of the oscillator of fig. 1 through the crossing axes of the strips.

Fig. 4 shows a schematic view of a detail of fig. 2, showing the offset between the intersection of the strips and the projection of the centroid of the resonator, which detail can be applied in the same way to the different variants described below.

Fig. 5 is a graph, the abscissa being the ratio X ═ D/L between the distance D of the insertion point and the intersection point of the strip in the static mass on the one hand and the total length L of the same strip between its two opposite insertion points on the other hand, and the ordinate being the apex angle of the intersection point of the flexible strip, the graph defining, in dashed lines, the upper and lower two curves which delimit the acceptable range of these parameters in order to ensure isochronism. The solid curve shows favorable values.

Fig. 6 shows, in a similar way to fig. 1, a second variant of the mechanical oscillator, in which a first rigid supporting element of elongated shape is also movable with respect to the stationary structure and is carried by a third rigid element by means of a second set of flexible strips arranged in a similar way to the first flexible strips, a second inertial element also arranged in cooperation with a conventional escapement mechanism (not shown).

Fig. 7 shows a schematic plan view of the oscillator of fig. 6.

Fig. 8 shows a schematic cross-sectional view of the oscillator of fig. 1 through the crossing axes of the strips.

Figure 9 is a block diagram representing a watch comprising a movement with such a resonator.

Fig. 10 shows in schematic perspective a bearing with projected intersecting flexible strips between a stationary structure and an inertial element.

Fig. 11 shows, in a similar way to fig. 10, a theoretical compliant bearing, wherein each strip has a higher aspect ratio than the strip of fig. 10.

Fig. 12 shows, in a similar way to fig. 10, a compliant bearing according to the invention, which is comparable to the theoretical bearing of fig. 11 in terms of elastic return, but with a greater number of strips, each having an aspect ratio of less than 10. In this variant, two elementary strips of the first type overlap in the first direction and the projection intersects two elementary strips of the second type, which also overlap and extend in the second direction.

Fig. 13 shows, in a similar way to fig. 12, another flexible bearing according to the invention, in which four strips are arranged alternately.

Fig. 14 shows, in a similar way to fig. 12, a further flexible bearing according to the invention, in which the four strips comprise two elementary strips of the first type in the first direction, which are located on either side of two elementary strips of the second type that are superimposed and extend in the second direction.

Figure 15 shows, in a similar way to figure 12, another flexible bearing according to the invention, comprising six strips, of which three each overlap.

Fig. 16 shows, in a similar way to fig. 13, another flexible bearing according to the invention, in which six strips are arranged alternately.

Fig. 17 shows, in a similar way to fig. 14, another flexible bearing according to the invention, in which eight strips comprise a first and a second superposition of two elementary strips of a first type in a first direction, which are located on either side of four elementary strips of a second type that are superimposed and extend in a second direction.

Fig. 18 shows, in a similar way to fig. 12, a further flexible bearing according to the invention with an odd number of strips, wherein five strips comprise two elementary strips of the first type in the first direction, on either side of three elementary strips of the second type which are superposed and extend in the second direction.

Detailed Description

The invention therefore concerns a mechanical timepiece oscillator 100 comprising at least a first rigid support element 4 and a second massive inertial element 5. The oscillator 100 comprises at least two first flexible strips 31, 32 between the first rigid support element 4 and the second massive inertia element 5, which support the second massive inertia element 5 and are arranged to return it to the rest position. The second massive inertia element 5 is arranged to oscillate angularly in an oscillation plane around said rest position.

The two first flexible strips 31 and 32 are not in contact with each other, and in the rest position their projections on the oscillation plane intersect at an intersection point P, next to which or passing through the rotation axis of the second massive inertia element 5 perpendicular to the oscillation plane is located. Unless otherwise stated, all geometric elements described hereinafter should be considered to be in the rest position of the stopped oscillator.

Fig. 1 to 4 show a first variant with a first rigid support element 4 and a second massive inertial element connected by two first flexible strips 31, 32.

The embedding points of the first flexible strips 31, 32 in the first rigid supporting element 4 and in the second massive inertial element 5 define two strip directions DL1, DL2 which are parallel to the oscillation plane and which form an apex angle α between their projections on the oscillation plane.

The position of the point of intersection P is defined by the ratio X ═ D/L, where D is the distance between the projection of one of the points of insertion of the first strip 31, 32 in the first rigid support element 4 on the oscillation plane and the point of intersection P, and L is the total length of the projection of the relative strip 31, 32 on the oscillation plane. The ratio D/L has a value between 0 and 1 and a vertex angle α smaller than or equal to 70 °.

Advantageously, the apex angle α is less than or equal to 60 °, while the embedding point ratio D1/L1, D2/L2 is between 0.15 and 0.85, inclusive, for each first flexible strip 31, 32.

In particular, as shown in fig. 2 to 4, the centroid of the oscillator 100 in its rest position is separated from the intersection point P by an offset epsilon which represents between 10% and 20% of the total length L of the projection of the strips 31, 32 on the oscillation plane. More particularly, the offset epsilon amounts to 12% to 18% of the total length L of the projection of the strips 31, 32 on the oscillation plane.

More specifically, as shown, the first strips 31, 32 define, with their points of embedment, a pivot 1, the projection of which pivot 1 on the oscillation plane is symmetrical with respect to a symmetry axis AA passing through the point of intersection P.

More specifically, when the pivot 1 is symmetrical about the axis of symmetry AA, in the rest position the projection of the centre of mass of the second massive inertia element 5 on the oscillation plane is located on the axis of symmetry AA of the pivot 1. In projection, the centroid may or may not coincide with the intersection point P.

More particularly, the centroid of the second massive inertia element 5 is located at a non-zero distance from the point of intersection P corresponding to the axis of rotation of the second massive inertia element 5, as shown in fig. 2 to 4.

In particular, the projection of the centroid of the second massive inertia element 5 on the oscillation plane is located on the symmetry axis AA of the pivot 1 and at a non-zero distance from the point of intersection P comprised between 0.1 and 0.2 times the total length L of the projection of the strips 31, 32 on the oscillation plane.

More specifically, the first strips 31 and 32 are straight strips.

More particularly, the apex angle α is less than or equal to 50 °, or less than or equal to 40 °, or less than or equal to 35 °, or less than or equal to 30 °.

More specifically, the embedding point ratios D1/L1, D2/L2 are between 0.15 and 0.49 inclusive, or between 0.51 and 0.85 inclusive, as shown in FIG. 5.

In a variant, more particularly according to the embodiment of fig. 5, the vertex angle α is less than or equal to 50 °, and the insertion point ratios D1/L1, D2/L2 are between 0.25 and 0.75, inclusive.

In a variant, more particularly according to the embodiment of fig. 5, the vertex angle α is less than or equal to 40 °, and the embedding point ratios D1/L1, D2/L2 are between 0.30 and 0.70, inclusive.

In a variant, more particularly according to the embodiment of fig. 5, the vertex angle α is less than or equal to 35 °, and the embedding point ratios D1/L1, D2/L2 are between 0.40 and 0.60, inclusive.

Advantageously, as shown in fig. 5, the vertex angle α and the ratio X ═ D/L satisfy the following relationship:

h1(D/L) < alpha < h2(D/L), wherein,

for X <0.5 > 0.2 ≦ X:

h1(X)＝116-473*(X+0.05)+3962*(X+0.05)³-6000*(X+0.05)⁴，

h2(X)＝128-473*(X-0.05)+3962*(X-0.05)³-6000*(X-0.05)⁴，

for 0.5< X ≦ 0.8:

h1(X)＝116-473*(1.05-X)+3962*(1.05-X)³-6000*(1.05-X)⁴，

h2(X)＝128-473*(0.95-X)+3962*(0.95-X)³-6000*(0.95-X)⁴。

more specifically, and in particular in the non-limiting embodiment shown in the figures, the first flexible strips 31 and 32 have the same length L and the same distance D.

More specifically, between their embedding points, these first flexible strips 31 and 32 are identical.

Fig. 6 to 8 show a second variant of the mechanical oscillator 100, in which the first rigid support element 4 is also directly or indirectly movable with respect to a stationary structure comprised in the oscillator 100 and is carried by the third rigid element 6 by means of two second flexible strips 33, 34, these two flexible strips 33, 34 being arranged in a similar manner to the first flexible strips 31, 32.

More specifically, in the non-limiting embodiment shown in the figures, the projections of first flex strips 31, 32 and second flex strips 33, 34 on the oscillation plane intersect at the same intersection point P.

In another particular embodiment (not shown), in the rest position, the projections of the first flexible strips 31, 32 and of the second flexible strips 33, 34 on the oscillation plane, when projected on the oscillation plane, intersect at two different points, both of which lie on the symmetry axis AA of the pivot 1 when the pivot 1 is symmetrical about the symmetry axis AA.

More specifically, the points of embedding of the second flexible strips 33, 34 with the first and third rigid supporting elements 4, 6 define two strip directions which are parallel to the oscillation plane and which, between their projections on the oscillation plane, form a vertex angle having the same bisector as the vertex angle α between the first flexible strips 31, 32. More specifically, the two directions of the second flexible strips 33, 34 have the same apex angle α as the first flexible strips 31, 32.

More specifically, in the non-limiting example in the figures, the second flexible strips 33, 34 are identical to the first flexible strips 31, 32.

More specifically, when the pivot 1 is symmetrical about the axis of symmetry AA, in the rest position the projection of the centre of mass of the second massive inertia element 5 on the oscillation plane is located on the axis of symmetry AA of the pivot 1.

Similarly, in particular when the pivot 1 is symmetrical about the axis of symmetry AA, in the rest position the projection of the centre of mass of the first rigid supporting element 4 on the oscillation plane is located on the axis of symmetry AA of the pivot 1.

In a particular variant, when the pivot 1 is symmetrical about the axis of symmetry AA, in the rest position, the projections of the barycentre of the second massive inertia element 5 and of the barycentre of the first rigid supporting element 4 on the oscillation plane are both located on the axis of symmetry AA of the pivot 1. More specifically, the projection of the centroid of the second massive inertia element 5 and of the centroid of the first rigid support element 4 on the axis of symmetry AA of the pivot 1 coincide.

One particular configuration for such multiple overlapping pivots shown in the figures is such that: wherein the projections of the first and second flexible strips 31, 32, 33, 34 on the oscillation plane intersect at the same intersection point P, which also corresponds to the projection of the centroid of the second massive inertial element 5, or at least is as close as possible to this centroid. More particularly, this same point also corresponds to the projection of the centroid of the first rigid supporting element 4. More particularly, this same point also corresponds to the projection of the centroid of the entire oscillator 100.

In one particular variant of this superimposed pivot configuration, when the pivot 1 is symmetrical about the axis of symmetry AA, in the rest position the projection of the centroid of the second massive inertia element 5 on the oscillation plane is located on the axis of symmetry AA of the pivot 1 and at a non-zero distance from the intersection point corresponding to the axis of rotation of the second massive inertia element 5, this non-zero distance being between 0.1 and 0.2 times the total length L of the projections of the strips 33, 34 on the oscillation plane, and the offset is similar to the offset epsilon of fig. 2 to 4.

Similarly and in particular, when the pivot 1 is symmetrical about the axis of symmetry AA, the projection of the centroid of the second massive inertial element 5 on the oscillation plane is located on the axis of symmetry AA of the pivot 1 and at a non-zero distance from the intersection point corresponding to the axis of rotation of the rigid support element 4, this non-zero distance being comprised between 0.1 and 0.2 times the total length L of the projections of the strips 31, 32 on the oscillation plane.

Similarly and in particular, when the pivot 1 is symmetrical about the axis of symmetry AA, the projection of the centre of mass of the first rigid support element 4 on the oscillation plane is located on the axis of symmetry AA of the pivot 1 and at a non-zero distance from the point of intersection P corresponding to the axis of rotation of the second massive inertial element 5. In particular, this non-zero distance is comprised between 0.1 and 0.2 times the total length L of the projection of the strips 33, 34 on the oscillation plane.

Similarly and in particular, when the pivot 1 is symmetrical about the axis of symmetry AA, the projection of the centroid of the first rigid support element 4 on the oscillation plane lies on the axis of symmetry AA of the pivot 1 and at a non-zero distance from the intersection point corresponding to the axis of rotation of the first rigid support element 4, this non-zero distance being comprised between 0.1 and 0.2 times the total length L of the projections of the strips 31, 32 on the oscillation plane.

Similarly and in particular, the centroid of the first rigid supporting element 4 lies on the symmetry axis AA of the pivot 1 and is at a non-zero distance from the point of intersection P, which is comprised between 0.1 and 0.2 times the total length L of the projection of the strips 33, 34 on the oscillation plane.

More specifically, and as shown in the variant in the figure, when the pivot 1 is symmetrical about the axis of symmetry AA, the projection of the centre of mass of the oscillator 100 in its rest position on the oscillation plane lies on the axis of symmetry AA.

More specifically, when the pivot 1 is symmetrical about the axis of symmetry AA, the second massive inertia element 5 is elongated in the direction of the axis of symmetry AA of the pivot 1. This is the case, for example, in fig. 1 to 4, in which the inertia element 5 comprises a base on which a conventional balance is fixed, the long arm of which is provided with an arc-shaped rim portion or inertia mass. The aim is to minimize the influence of external angular accelerations around the axis of symmetry of the pivot, since these strips have a low rotational stiffness around this axis due to the small angle α.

The invention is well suited to integrated embodiments of these strips and the massive parts to which they are attached, made of micromachinable or at least partially amorphous material by MEMS or LIGA or similar processes. In particular, in the case of a silicon embodiment, oscillator 100 is advantageously temperature compensated by adding silicon dioxide to the flexible silicon strip. In one variation, the strips may be assembled (e.g., embedded) in a groove or similar structure.

When there are two pivots in series, as in the case of fig. 6 to 9, the centroid can be set on the axis of rotation, with the arrangement chosen so that the undesired movements are offset with respect to each other, which constitutes an advantageous but non-limiting variant. It should be noted, however, that this arrangement need not be chosen and that the oscillator operates with two pivots in series rather than having to locate the center of mass on the axis of rotation. Of course, although the illustrated embodiment corresponds to a particular geometric alignment or symmetrical configuration, it is clear that it is also possible to place one pivot on top of the other, the two pivots being different or having different points of intersection or having non-aligned centres of mass, or to implement a greater number of sets of tandem strips with intermediate masses to further increase the amplitude of oscillation of the balance.

In the variant shown, all the pivot axes, the strap intersections and the centroids are coplanar, which is a particularly advantageous but non-limiting case.

It will be appreciated that the invention makes it possible to obtain a long angular travel: in any case greater than 30 °, up to 50 ° or even 60 °, which makes it compatible with all the usual types of mechanical escapement, swiss lever, detent, coaxial or other.

This is also a problem to determine a practical solution, equivalent to the theoretical application of high aspect ratio values for the strip.

To this end, the invention longitudinally subdivides a stripe by replacing a single stripe with a plurality of base stripes whose combined behavior characteristics are identical, and in which each base stripe has an aspect ratio that is limited by a threshold. Thus, the aspect ratio of each base strip is reduced compared to a single reference strip to achieve optimal isochronism and position insensitivity.

Each strip 31, 32 has an aspect ratio RA ═ H/E, where H is the height of the strip 31, 32, both perpendicular to the plane of oscillation and to the direction of elongation of the strip 31, 32 along the length L, and where E is the thickness of the strip 31, 32 in the plane of oscillation, perpendicular to the direction of elongation of the strip 31, 32 along the length L.

According to the invention, for each strip 31, 32, the aspect ratio RA H/E is less than 10. More specifically, the aspect ratio is lower than 8. And the total number of flexible strips 31, 32 is strictly greater than 2.

More particularly, the oscillator 100 comprises a first number N1 of first stripes, called primary stripes 31, extending in a first stripe direction DL1, and a second number N2 of first stripes, called secondary stripes 32, extending in a second stripe direction DL2, the first number N1 and the second number N2 each being higher than or equal to 2.

More specifically, the first number N1 is equal to the second number N2.

More particularly, the oscillator 100 comprises at least one strip pair formed by one main strip 31 extending in a first strip direction DL1 and one secondary strip 32 extending in a second strip direction DL 2. Also, in each stripe pair, the primary stripes 31 are identical to the secondary stripes 32 except for orientation.

In one particular variant, the oscillator 100 comprises only a plurality of pairs of strips each formed by one primary strip 31 extending in the first strip direction DL1 and one secondary strip 32 extending in the second strip direction DL2, and in each pair of strips, the primary strip 31 is identical to the secondary strip 32, except for the orientation.

In another variant, the oscillator 100 comprises at least one set of strips formed by one main strip 31 extending along the first strip direction DL1 and a plurality of secondary strips 32 extending along the second strip direction DL 2. Also, in each case, in each set of strips, the elastic behavior of the primary strips 31 is identical to that produced by the combination of the plurality of secondary strips 32, except for the orientation.

It should also be noted that while the behavior of a flexible strip depends on its aspect ratio RA, it also depends on the value of the curvature imparted to the flexible strip. The bending/deflection curve (deflected curve) of the flex ribbon depends on both the aspect ratio value and the local curvature radius value, especially at the embedding point. This is why a symmetrical arrangement of the strips in the planar projection is preferred.

The invention concerns a timepiece movement 1000 comprising at least one such mechanical oscillator 100.

The invention also relates to a watch 2000 comprising at least one such timepiece movement 1000.

One suitable manufacturing method includes: the following operations are performed for the following various types of pivots:

for an AABB type pivot according to the diagram of fig. 12:

a. using a substrate having at least four layers, such as but not limited to resulting from the assembly of two SOI wafers;

b. front side etching by DRIE process to obtain AA, especially integrally etching both layers;

c. back etching by DRIE process to obtain BB, especially integrally etching both layers;

d. the four layers are partially separated by etching the buried oxide.

The high accuracy of the DRIE (deep reactive ion etching) process ensures very high positioning and alignment accuracy of less than or equal to 5 microns due to the optical alignment system which ensures very good edge-to-edge alignment. Of course, similar processes may be implemented depending on the materials selected.

Substrates with more layers, in particular six available layers, can be realized, for example by assembling two DSOI, to obtain an AAABBB type structure.

One variant for obtaining the same AABB type pivot comprises:

a. two standard SOI substrates with two layers are used;

drie etching the first substrate to obtain a on the front side and a on the back side;

drie etching the second substrate to obtain B on the front side and B on the back side; instead of operations b and c, etching through both layers may be performed in one step on the first substrate and on the second substrate without performing front and back side etching.

d. Wafer-wafer bonding of two substrates or component-component assembly of the respective assemblies is performed to obtain the AABB. At this point, the correct alignment of the geometry is associated with the specifications of the wafer-wafer bonding machine or the component-component assembly process in a manner well known to those skilled in the art.

For ABAB type pivots according to the diagram of fig. 13:

a. two standard SOI substrates with two layers are used;

drie etching the first substrate to obtain a on the front side and B on the back side;

drie etching the second substrate to obtain a on the front side and B on the back side;

d. wafer-wafer bonding of the two substrates or component-component assembly of the respective assemblies is performed to obtain ABAB. As above, the correct alignment of the geometry is now associated with the specifications of the wafer-wafer bonding machine or the component-component assembly process.

Many other variations of this method can be implemented depending on the number of strips and the available equipment.