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 2019-07-24 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),其包括在支承件(4)和惯性元件(5)之间的具有投影相交的柔性条带的柔性轴承,该柔性轴承包括叠置的上层级(28)和下层级(29),该上层级包括在上部支承件(48)和上部惯性元件(58)之间的沿第一方向(DL1)的上部主条带(318)和沿第二方向(DL2)的上部次条带(328),该下层级包括在下部支承件(49)和下部惯性元件(59)之间的沿第一方向(DL1)的下部主条带(319)和沿第二方向(DL2)的下部次条带(329),该上层级和下层级包括在支承件(4)与上部支承件(48)或下部支承件(49)之间的平移台(308；309),其具有沿振荡平面中的一个或两个自由轴线的弹性连接件,该弹性连接件的刚度低于每个条带的刚度。(The invention relates to a mechanical timepiece oscillator (100) comprising a flexible bearing with projected intersecting flexible strips between a support (4) and an inertial element (5), the flexible bearing comprising an upper level (28) and a lower level (29) superimposed, the upper level comprising an upper main strip (318) in a first direction (DL1) and an upper secondary strip (328) in a second direction (DL2) between an upper support (48) and an upper inertial element (58), the lower level comprising a lower main strip (319) in the first direction (DL1) and a lower secondary strip (329) in the second direction (DL2) between a lower support (49) and a lower inertial element (59), the upper and lower levels comprising a translation stage (308; 309) between the support (4) and the upper support (48) or the lower support (49) with an elastic connection along one or two free axes in an oscillation plane, the stiffness of the resilient connection is lower than the stiffness of each strip.)

1. A mechanical timepiece oscillator (100) comprising a flexible bearing mechanism (200) between a first rigid support element (4) fixed directly or indirectly to a plate (900) and an inertial element (5), the flexible bearing mechanism (200) comprising at least two first flexible strips (31; 32) supporting the inertial element (5) and arranged to return the inertial element to a rest position, wherein the inertial element (5) is arranged to oscillate angularly in an oscillation plane about the rest position, the two first flexible strips (31; 32) being not in contact with each other and their projections on the oscillation plane intersect at the rest position at an intersection point (P), a rotation axis of the inertial element (5) perpendicular to the oscillation plane passing adjacent to the intersection point, characterized in that the flexible bearing mechanism (200) comprises at least one upper level (28) and at least one lower level (P) superposed on each other (29) -the upper level (28) comprises, between the upper support (48) and the inertial element (5), at least one upper main strip (318) extending in a first upper strip direction (DL1S) and at least one upper secondary strip (328) extending in a second upper strip direction (DL2S), the projections of the upper main strip (318) and the upper secondary strip (328) intersecting at an upper intersection Point (PS), -the lower level (29) comprises, between the lower support (49) and the inertial element (5), at least one lower main strip (319) extending in a first lower strip direction (DL1I) and at least one lower secondary strip (329) extending in a second lower strip direction (DL2I), the projections of the lower main strip (319) and the lower secondary strip (329) intersecting at a lower intersection Point (PI); and the upper and lower stages (28, 29) each comprise a translation stage (308; 309) between the panel (900) and the upper support (48) or lower support (49), comprising at least one elastic connection along one or two free axes in the oscillation plane, the rigidity of which is lower than that of the upper stage and also lower than that of the lower stage, to allow relative translation between the upper and lower stages, to allow adjustment of the relative position of the two points of embedment of the flexible strip (31; 32) on the side of the inertial element (5), and adjustment of the rigidity of the translation stage (308; 309) to allow adjustment of any non-isochronism.

2. The mechanical oscillator (100) of claim 1, characterized in that the elastic connection of the upper translation stage (308) or lower translation stage (309) along one or two free axes in the oscillation plane is of the form: -elastic connections along axes X and Y of bisectors of an angle formed between projections of the flexible strips of said flexible bearing means (200) on a common parallel plane.

3. The mechanical oscillator (100) according to claim 1, characterized in that in the rest position a vertex angle (α) is formed between the projections on the oscillation plane of 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) in the first rigid support element (4) and the intersection point (P), L is the total projected length of the first strip (31; 32) on the oscillation plane, and in that the centroid of the oscillator (100) in rest position is at an offset (ε) from the intersection point (P), said offset (ε) being comprised between 12% and 18% of the total projected length L ° of the first strip (31; 32) on the oscillation plane, the value of the ratio D/L is comprised between 0 and 1, said vertex angle (α) being less than or equal to said first strip direction (32), and the value of the vertex angle D/L is comprised between 0 and 15D/L for each embedding point (31; 32) and 10, 10.85/L.

4. The mechanical oscillator (100) of claim 1, wherein each of the strips (31; 32) has an aspect ratio RA ═ H/E, where H is the height of the strip (31; 32) perpendicular to the oscillation plane and to the direction of elongation of the strip (31; 32) along the length L, E is the thickness of the strip (31; 32) in the oscillation plane and perpendicular to the direction of elongation of the strip (31; 32) along the length L; for each of said strips (31; 32), said aspect ratio RA H/E is less than 10; and the total number of said flexible strips (31; 32) is strictly greater than 2.

5. The mechanical oscillator (100) of claim 4, 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.

6. The mechanical oscillator (100) of claim 5, wherein the first number N1 is equal to the second number N2.

7. The mechanical oscillator (100) of claim 5, 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.

8. The mechanical oscillator (100) of claim 7, 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.

9. The mechanical oscillator (100) of claim 5, 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 characteristics of the primary strip (31) are identical to the elastic behavior characteristics produced by the plurality of secondary strips (32) except for orientation.

10. The mechanical oscillator (100) according to claim 1, characterized in that in the rest position a vertex angle α is formed between the projections on the oscillation plane of 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) in the first rigid support element (4) and the intersection point (P), L is the total projected length of the strip (31; 32) on the oscillation plane in its direction of elongation, and the embedding point ratio (D1/L1; D2/L2) is between and including an end value, or between 0.51 and 0.85 and including an end value.

11. The mechanical oscillator (100) of claim 10, wherein the apex angle (α) is less than or equal to 50 °, and the ratio of the insertion points (D1/L1; D2/L2) is between and including 0.25 and 0.75.

12. The mechanical oscillator (100) of claim 11, wherein the apex angle (α) is less than or equal to 40 °, and the embedding point ratio (D1/L1; D2/L2) is between and including 0.30 and 0.70.

13. The mechanical oscillator (100) of claim 12, wherein the apex angle (α) is less than or equal to 35 °, and the embedding point ratio (D1/L1; D2/L2) is between and including 0.40 and 0.60.

14. The mechanical oscillator (100) of claim 10, wherein the apex angle (α) is less than or equal to 30 °.

15. The mechanical oscillator (100) of claim 10, wherein the apex angle (α) and the ratio X-D/L satisfy the relation h1(D/L) < α < 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。

16. the mechanical oscillator (100) of claim 1, wherein the flexible strip is a straight strip.

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

18. Watch (2000) comprising at least one timepiece movement (1000) according to claim 17.

Technical Field

The invention relates to a mechanical timepiece oscillator comprising a flexible bearing (flexure bearing) between a first rigid support element and a massive inertial element, said flexible bearing having at least two first flexible strips supporting the massive inertial element and arranged to return the massive inertial element to a rest position, wherein the massive inertial element is arranged to oscillate angularly in an oscillation plane about the rest position, the two first flexible strips are not in contact with each other and in the rest position their projections on the oscillation plane intersect at an intersection point, the rotation axis of the massive inertial element perpendicular to the oscillation plane is close to or passes through this intersection point, and the embedding point of the first flexible strips in the first rigid support element and the massive inertial element defines a point parallel to the intersection point At least two strip directions of 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 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 No3035127a1 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.

European patent application No.3324247A1 in the name of the same applicant, SWATCH GROUP RESEARCH & DEVELOPMENT Ltd, discloses a strip resonator for a mechanical watch movement, arranged to be fixed to or to form a main board of the movement, wherein said resonator comprises a fixed structure arranged to be fixed to or to form the main board, at least one inertia element arranged to vibrate and/or oscillate relative to the fixed structure, and said resonator comprises at least one elastic strip extending between a first anchoring point arranged on the fixed structure at a first end and a second anchoring point arranged on the at least one inertia element at a second end, and said strip is arranged to vibrate substantially in a main plane. This strip forms a bearing for the inertial element in the main plane. In order to protect the strips comprised therein from shocks, the resonator 1000 comprises at least one flat anti-shock device on the first and/or second anchor point, arranged to protect each strip from breaking in case of a shock, said flat anti-shock device comprising at least one first flexible element preloaded with a pre-stress in said main plane, said pre-stress being set at a predetermined safety stress value.

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, 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 ribbons are made thinner but of greater length. 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 the phenomenon of mutually inverse curvature (anti-curvature) is often encountered, which impairs performance.

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 specific case of a flexible bearing with strips intersecting in projection in a plane parallel to the oscillation plane, which connect a stationary mass and a moving mass, the possible angular travel θ of the pivot depends on the relation X ═ D/L, where D is the distance of the embedding point of the strip in the stationary mass on the one hand, and L is the total length l.m.h.kahrobiain team of the same strip between its two opposite embedding points along its elongation direction on the other hand, the previous work of the team shows that for a given pair of strips having a given vertex angle 83 (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.

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

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

In particular, the present invention shows that an isochronous oscillator having pivots satisfying both inequalities 0.15 ≦ (X ≦ D/L ≦ 0.85 and α ≦ 60 ° may be obtained.

Of course, configurations in which α is 0 ° are excluded, since 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 rigid support element of elongated shape for attaching the mechanical oscillator to a plate or similar of a movement, on which a massive inertia element is suspended by two separate first flexible strips, the projections of which on the oscillation plane of said inertia element intersect, said inertia element cooperating with a traditional swiss lever escapement with a standard escape wheel.

Fig. 2 shows a schematic plan 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 represents 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 including this offset 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, the ordinate being the apex angle of the intersection point of the flexible strip, the graph defining, with a dashed line, two upper and lower curves which delimit the acceptable range of these parameters in order to ensure isochronism, while the solid curve corresponds to a favourable value.

Fig. 6 shows, in a similar way to fig. 1, a second variant of the mechanical oscillator, in which a 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 being 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.

Figure 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, 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 manner to fig. 12, another flexible bearing, in which four strips are arranged alternately.

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

Fig. 15 shows, in a similar manner to fig. 12, another flexible bearing comprising six strips, of which three each overlap.

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

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

Fig. 18 shows, in a similar way to fig. 12, a further flexible bearing 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 superimposed and extend in the second direction.

Figure 19 is identical to figure 13.

Fig. 20 shows the breakdown of such a flexible bearing with four alternating strips into two pivot subunits with two strips.

Figure 21 is identical to figure 14.

Fig. 22 shows that such a flexible bearing with four strips in a two-sided arrangement is broken up into two pivot subunits with two strips.

Fig. 23 represents in a schematic way the upper and lower portions, in this case upper and lower levels, of the oscillator with such a flexible bearing broken down into several subunits, with a plurality of translation stages (translational tables) interposed between the stationary support and the support points of the strip towards the inertial element, these translation stages comprising flexible elastic bearings (bearing) in the X and Y directions along the bisectors of the projection direction of the strip.

Figure 24 is similar to figure 23 and includes a position adjustment at X on the lower rigid portion to vary the offset between the projections of the intersection of the upper and lower strips.

Figures 25 to 27 show other variants of the translation stage.

Fig. 28 represents a schematic side view of the upper and lower parts of an oscillator with a flexible bearing broken down into two subunits, in this case an upper and lower level, with a translation table interposed between the stationary support and the upper support point of the upper strip facing the inertial element.

Detailed Description

The invention concerns a mechanical timepiece oscillator 100 comprising at least one rigid support element 4, fixed directly or indirectly to a plate 900, and a massive inertial element 5. The oscillator 100 includes a compliant bearing mechanism 200 between the rigid support member 4 and the massive inertial member 5. The flexible bearing mechanism comprises at least two first flexible strips 31, 32 which support the massive inertia element 5 and are arranged to return it to the rest position. The 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 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 rigid support element 4 and a massive inertia element connected by two first flexible strips 31, 32.

The embedding points of the first flexible strips 31, 32 in the rigid support element 4 and the second massive inertia element 5 define at least 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 interposition of the first strip 31, 32 in the first rigid supporting element 4 on the oscillation plane and the point of intersection P, L is the total length of the projection of the relative strip 31, 32 on the oscillation plane, the value of the ratio D/L is between 0 and 1, and the apex angle α is less 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 mass centre of the 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 mass centre of the 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 massive inertia element 5, as shown in fig. 2 to 4.

In particular, the projection of the centroid of the massive inertial element 5 on the oscillation plane lies on the symmetry axis AA of the pivot 1 and at a non-zero distance from the intersection point P, which is 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, apex angle α is less than or equal to 50 °, alternatively less than or equal to 40 °, alternatively less than or equal to 35 °, alternatively 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 apex angle α is less than or equal to 50 °, and the ratios of insertion points 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 apex 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 apex 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 apex angle α and the ratio X ═ D/L satisfy the following relationship:

h1(D/L) < α < 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 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 in the rigid support element 4 and the third rigid element 6 define two strip directions which are parallel to the oscillation plane and which form, between their projections on the oscillation plane, an apex angle having the same bisector as the apex angle α between the projections of the first flexible strips 31, 32 on the oscillation plane, 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 mass centre of the 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 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 massive inertia element 5 and of the barycentre of the rigid support element 4 on the oscillation plane are both located on the axis of symmetry AA of the pivot 1. More specifically, the projections of the mass centre of the massive inertia element 5 and of the mass centre of the 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 mass centre of the massive inertia element 5, or at least is as close as possible to this mass centre. More particularly, this same point also corresponds to the projection of the centroid of the rigid support 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 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 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 massive inertial element 5 on the oscillation plane lies on the axis of symmetry AA of the pivot 1 and is 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 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 point of intersection P corresponding to the axis of rotation of the massive inertia 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 rigid support element 4 on the oscillation plane lies on the axis of symmetry AA of the pivot 1 and is 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, the centre of mass of the rigid support element 4 lies on the axis of symmetry AA of the pivot 1 and is 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 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 massive inertia element 5 is elongated in the direction of the axis of symmetry AA of the pivot 1, as is the case, for example, in figures 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 inertial mass, the aim being to minimize the effect of the external angular acceleration about the axis of symmetry of the pivot, since these strips have a low rotational stiffness about 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 other 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 this thus makes it possible to obtain a large angular travel: in any case greater than 30 °, even up to 50 ° or 60 °, which makes it compatible in combination with all the usual types of mechanical escapement, swiss lever, detent, coaxial or otherwise.

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, it is advantageous to subdivide the stripes longitudinally 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 limited by a threshold value. 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.

Preferably, 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:

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, etching on the front side to obtain a, etching on the back side to obtain a;

drie etching the second substrate, etching on the front side to obtain B, etching on the back side to obtain B; instead of operations b and c, the through-two layers may be etched in one operation on the first substrate and on the second substrate without performing the 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:

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.

The standard fabrication methods achieved by DRIE silicon etching also do not readily enable the fabrication of monolithic pivots with more than two different levels. Thus, it is easier to manufacture a plurality of individual components that are subsequently assembled. However, sensitivity to assembly errors requires precision greater than one micron to achieve optimal isochronism and/or positional insensitivity. To overcome this problem, it is necessary to employ the manufacturing strategy described below.

In a first step, two strips with different directions have to be assembled in a very precise manner. The present invention proposes to divide the flexible bearing or pivot into subunits consisting of a pivot with two strips, for example in the case of a flexible bearing comprising four strips as shown in fig. 19, into an upper subunit and a lower subunit, wherein four alternate strips are broken down into two pivot subunits with two strips. Fig. 21 and 22 show a similar decomposition in the case of strips having a lateral arrangement instead of an alternating arrangement. Each sub-cell is made by DRIE etching on two levels (etching the SOI wafer on both sides) to ensure sufficient alignment accuracy.

The upper sub-unit is then assembled to the lower sub-unit.

The assembly process may be carried out by any conventional method: using dowel pins and screws, or adhesive bonding, or wafer fusion, or welding, or brazing, or any other method known to those skilled in the art.

The assembly error is manifested as a small offset Δ of the rotational axes of the upper and lower subunits, such that the rotational movement of the resonator imposed by the upper subunit is not aligned with the rotational movement imposed by the lower subunit. To prevent this offset from generating excessive stress, the mechanism comprises at least one translation stage, the unrestricted movement of which is able to absorb the difference between two rotations of different axes. At least one of the translation stages must be flexible enough to prevent differences in motion from compromising isochronism. In the case of two identical translation stages, as shown in fig. 23, they must be flexible enough to prevent the difference in motion from compromising isochronism, and rigid enough to clearly determine the position of the pivot. Calculations show that these conditions are not contradictory if the offset between the rotation axes is less than 10 microns, which can be achieved by conventional assembly processes. Naturally, the accuracy of such assembly can be improved as follows: a complementary etch of the mortise and tenon type, or a plurality of mortise and tenon assemblies forming a non-zero angle therebetween, or any other arrangement known in precision machinery.

More specifically, as shown, the compliant bearing mechanism 200 includes at least one upper stage 28 and at least one lower stage 29 stacked on top of each other.

The upper subunit comprises an upper level 28, the upper level 28 comprising at least one upper main strip 318 extending in a first upper strip direction DL1S and an upper secondary strip 328 extending in a second upper strip direction DL2S between the upper support 48 and the upper inertial element 58, the projections of the upper main strip 318 and the upper secondary strip 328 intersecting at an upper intersection point PS.

Said lower subunit comprises a lower level 29, the lower level 29 comprising, between the lower support 49 and the lower inertial element 59, at least one lower main strip 319 extending in a first lower strip direction DL1I and a lower secondary strip 329 extending in a second lower strip direction DL2I, the projections of the lower main strip 319 and of the lower secondary strip 329, at rest, intersecting at a lower intersection point PI at an offset from the upper intersection point PS.

Also, at least the upper or lower stage 28, 29 comprises an upper or lower translation table 308, 309 between the plate 900 and the upper or lower support 48, 49, comprising at least one elastic connection allowing translation along one or two free axes in the oscillation plane, and having a translational stiffness along these two axes lower than that of each flexible strip 31, 32, 333, 34, 318, 319, 328, 329 comprised in the flexible bearing mechanism 200.

It should be noted that the elastic connection is not allowed to rotate around an axis parallel to the resonator axis.

It should be noted that the upper directions DL1S and DL2S of the upper level 28 do not have to be the same as the lower directions DL1I and DL2I of the lower level 29. Preferably, they have the same bisector.

More specifically, in the case where the flexible bearing mechanism 200 comprises two identical upper and lower translation stages 308 and 309, the point P through which the axis of rotation of the inertial element 5 passes is located between the upper intersection point PS and the lower intersection point PI, just in the middle. In a variant, this point P is located exactly on the lower intersection PI if the lower level 29 does not have a translation stage, or on the upper intersection PS if the upper level 28 does not have a translation stage.

Preferably, oscillator 100 includes a single massive inertial element 5 for each compliant bearing mechanism 200 included in oscillator 100. More particularly, there is only one compliant bearing mechanism 200 and only one massive inertial element 5.

Of course, the preferred configuration of the translation stages 308 and 309 shown in the figures is not limiting. These translation stages 308 and 309 can also be located between the inertial element 5 and the embedding point on the inertial element side.

If the axis of the bisector of the angle formed between the projections of the flexible strips on a common parallel plane is defined as X and Y, the combination of translation stages must be more flexible along axis X and along axis Y than the flexible pivots along the same axis. This rule works regardless of the number of levels, the combined result of all the stages combined must be more flexible than the flexible pivot in translation along axis X and along axis Y. Thus, the elastic connections of the upper translation stage 308 or of the lower translation stage 309 along one or two free axes in the oscillation plane are preferably elastic connections along these axes X and Y.

The elastic energy that is additionally stored in one or more translation stages due to the difference in motion is added to the main energy storage of the pivots and tends to break the isochronism unless the additionally stored values are much lower than the main stored values. This is why the elastic connections in the translation stage have to be much more flexible than the elastic connections of the flexible pivots.

More specifically, according to the invention, each of the upper and lower stages 28, 29 comprises, between the plate 900 and the upper or lower support 48, 49, an upper or lower translation table 308, 309 comprising at least one elastic connection along one or two free axes in the oscillation plane and having a stiffness lower than that of each flexible strip.

When each level has one translation stage, they do not have to be identical to each other.

One variation includes the use of two different translation stages, where the first translation stage is flexible so that differences in motion do not compromise isochronism, while the second translation stage is rigid to ensure the positioning of the pivot.

In another variation, one level may include a translation stage, while another level may have a rigid attachment.

Upper inertia element 58 and lower inertia element 59 form all or part of massive inertia element 5 and are rigidly connected to each other, directly or indirectly. As the case may be, the upper support 48 and the lower support 49 are connected to a rigid upper portion 480 or a rigid lower portion 490, either directly or via an upper translation stage 308 or a lower translation stage 309, the rigid upper portion 480 and the rigid lower portion 490 being rigidly connected to the rigid support element 4 or the plate 900.

Fig. 23 and 24 show an example of such a connection. The upper translation stage 308 comprises a first flexible elastic connection 78 extending in direction X between the upper support 48 and the upper intermediate mass 68, and a second flexible elastic connection 88 extending in direction Y between the upper intermediate mass 68 and the upper rigid portion 480. Similarly, the lower translation stage 309 comprises a first flexibly elastic connection 79 extending in direction X between the lower support 49 and the lower intermediate mass 69, and a second flexibly elastic connection 89 extending in direction Y between the lower intermediate mass 69 and the lower rigid portion 490.

Thus, the movement of the translation stage (or advantageously of a plurality of translation stages) is able to absorb any difference between the rotations of the upper and lower subunits. Furthermore, each translation stage helps to protect the mechanism from high accelerations, for example during a fall or impact.

Obviously, the assembly described above with reference to the first step makes any added asynchronism negligible, as long as the assembly error Δ is sufficiently small.

On the other hand, one may decide to deliberately exaggerate the assembly error Δ in order to introduce an inequality in a controlled manner, for example to compensate for losses at the escapement. It is therefore advantageous to make at least one of the insertion points in the panel movable and adjustable, in the case of the particular non-limiting variant shown, i.e. the upper support 48 and/or the lower support 49. In fact, adjusting the relative position of these two insertion points changes the stiffness of the translation stages 308, 309, which has the effect of adjusting the added inequality. This adjustment can be easily made with a cam and groove combination or by any other solution known to watchmakers.

In short, by moving the position of at least one of the insertion points in the board, as shown in fig. 24, the inequality caused by the assembly error Δ can be adjusted.

In short, this particular arrangement with at least one translation stage makes it possible to guarantee the alignment between the upper and lower levels and to avoid the high stresses to which the strip would be subjected in the case where the upper and lower levels do not follow the same trajectory.

Another alternative consists in providing the mechanism with an upper translation stage 308 and a lower translation stage 309, in which the upper support 48 and the lower support 49 are no longer rigidly connected to the rigid support element 4 or to the plate 900, but are constrained to move in relative planes in X and Y with respect to the fixed axis of the rigid support element 4 or of the plate 900, this being achieved by means of a connection device of the crank (brace) type or similar. The advantage of this solution is to allow the adjustment of the inequality without the need to slightly move the axis of rotation of the resonator.

Obviously, the translation stage forming the translating flexible bearing can be manufactured in many different ways. Examples will be found by those skilled in the art in the following references: [1] henein, concept des guidagesflexiles PPUR, [2] Larry L.Howell, Handbook of complex mechanics, WILEY), or [3] Zeyi Wu and Qingsong Xu, Actuators 2018. Some non-limiting examples are shown in fig. 25 to 27.

Fig. 28 shows a simplified example with translation stages connected via a neck portion: the upper support 48 is connected to an intermediate element 488, which intermediate element 488 is suspended by a first elastic neck portion 880 from a second intermediate element 889 having a second neck portion 890, which second neck portion 890 forms an elastic connection with a lower rigid portion 490 rigidly connected to the plate 900. In this example, upper inertia element 58 and lower inertia element 59 are connected to another intermediate element 589 to form, together with it, massive inertia element 5.