Shock absorbing spring, bearing body and bearing for a timepiece

Abstract

Shock absorbing spring (1) for a timepiece (200), extending substantially in a plane (P1) and comprising a first axis of symmetry (A1) perpendicular to the plane (P1), the spring comprising at least two first spring fixing elements (11, 11', 11"), each comprising at least one first fixing surface (11a, 11b, 11a', 11b', 11a", 11b") oriented at least substantially radially with respect to the first axis (A1) and towards the first axis (A1).

Description

TECHNICAL FIELD

[0001] The invention relates to a shock absorbing spring for a timepiece. The invention relates to a bearing body for a timepiece. The invention relates to a bearing for a timepiece comprising such a shock absorbing spring and / or such a bearing body. The invention also relates to a timepiece movement comprising such a shock absorbing spring and / or such a bearing and / or such a bearing body. The invention also relates to a timepiece movement comprising such a shock absorbing spring and / or such a bearing body and / or such a bearing and / or such a movement. The invention also relates to a timepiece comprising such a shock absorbing spring and / or such a bearing body and / or such a bearing and / or such a movement and / or such a timepiece movement. BACKGROUND

[0002] There are many shock absorbing bearing solutions for timepieces, in particular those for pivoting a balance shaft. Such a bearing generally comprises a bearing body, a pierced bearing jewel, a collet, a positioning ring for positioning the jewel and the collet within the bearing body, and a spring arranged at the interface between the bearing body and the collet, so as to dampen the movement of the shaft in the event of an impact and return the shaft to its initial position after the impact.

[0003] The spring of the shock absorbing bearing may, for example, be shaped as a closed ring. It thus comprises a compression portion that projects towards the interior of the spring, in contact with the collet, and an attachment portion that projects towards the exterior of the spring, so as to be able to be housed in an internal groove of the bearing body. By way of example, the documents CH 705 583, EP 3 011 396, EP 3 220 211 disclose various alternative embodiments of such a closed ring spring.

[0004] Alternatively, the spring of the shock absorbing bearing can have an open shape. In this case, the spring has an attachment in the form of a lug arranged at one of its ends and projecting towards the exterior of the spring. By way of example, the documents EP 1 705 537, CH 708 733, EP 3 070 544 disclose various alternative embodiments of such an open ring spring. SUMMARY

[0005] The aim of the invention is to provide a shock absorbing spring and / or a bearing body and / or a bearing that makes it possible to improve the devices known in the prior art. In particular, the invention proposes a shock absorbing spring and / or a bearing body and / or a bearing that makes it possible to reduce the stiffness of the spring as much as possible and to make the load exerted on the collet as constant as possible, so as to adapt the mechanical response of the shock absorbing bearing to the stresses tolerated on the shaft, and more particularly on its pivot, in particular in the event that the materials can be modified and / or the usual dimensions of the shaft can be reduced as much as possible.

[0006] To this end, the invention provides a shock-absorbing spring for a timepiece, which extends substantially in a plane and comprises a first axis of symmetry perpendicular to said plane, said spring comprising at least two first fixing elements, each comprising at least one first fixing surface, said first fixing surface being oriented at least substantially radially with respect to said first axis of symmetry and towards said first axis of symmetry, at least one of said first fixing surfaces being located on a protrusion, said protrusion projecting towards said first axis of symmetry with respect to a respective adjacent surface, said adjacent surface being oriented at least substantially radially with respect to said first axis of symmetry and towards said first axis of symmetry, said adjacent surface being located on either side of said at least one first fixing surface along an orthogonal radial direction with respect to said first axis of symmetry, respectively.

[0007] Optionally, the spring described above has one or more of the following features:

[0008] said spring has a shape having at least substantially n-fold rotational symmetry with respect to said first axis of symmetry, where n is a natural integer, in particular where n = 2 or n = 3 or n = 4 or n = 5, and / or where said spring has the form of a closed loop which is closed on itself;

[0009] said spring comprises at least two pressing elements for pressing on a jewel element and at least two connecting elements mechanically connecting said pressing elements to said first fixing elements;

[0010] at least one portion of said at least two connecting elements extends at least substantially radially with respect to said first axis of symmetry, or at least one portion of said at least two connecting elements extends at least substantially orthoradially with respect to said first axis of symmetry.

[0011] The invention also provides a bearing body comprising a second axis of symmetry and at least two second fixing elements for fixing a spring, each comprising at least one second fixing surface, said second fixing surface being oriented at least substantially radially with respect to said second axis of symmetry and towards a direction away from said second axis of symmetry, each of said second fixing elements comprising a peg, said second fixing surface being formed on said peg.

[0012] Optionally, the bearing body described above has one or more of the following features:

[0013] said bearing body has a shape having at least substantially n-fold rotational symmetry with respect to said second axis of symmetry, where n is a natural integer, in particular where n = 2 or n = 3 or n = 4 or n = 5;

[0014] each of said pegs comprises a groove extending at least substantially radially with respect to said second axis of symmetry.

[0015] The application also provides a bearing comprising the above-mentioned bearing body and / or the above-mentioned spring.

[0016] Optionally, the bearing comprises a drilling element and / or a pivoting element and / or a positioning ring for positioning the drilling element and / or the pivoting element;

[0017] Optionally, the above-mentioned bearing comprises the above-mentioned bearing body and the above-mentioned spring, the ratio between the diameter of the larger cylinder inscribed between the first fixed surfaces and the diameter of the smaller cylinder circumscribed on the second fixed surfaces when the spring is removed or in a free or unconstrained state is less than 1 or less than 0.99 or less than 0.98.

[0018] The application also provides a timepiece movement, in particular an oscillator of the balance-spiral type, comprising the above-mentioned bearing and / or the above-mentioned spring and / or the above-mentioned bearing body.

[0019] The application also provides a timepiece movement, in particular an oscillator of the balance-spiral type, comprising the above-mentioned bearing and / or the above-mentioned spring and / or the above-mentioned bearing body.

[0020] The application also provides a timepiece, in particular a watch, comprising the above-mentioned timepiece movement and / or the above-mentioned bearing and / or the above-mentioned spring and / or the above-mentioned bearing body and / or the above-mentioned timepiece movement. BRIEF DESCRIPTION OF DRAWINGS

[0021] The attached drawings illustrate by way of example an embodiment of a timepiece.

[0022] Figure 1 An embodiment of a timepiece is depicted.

[0023] Figure 2 Is a detailed view from above of an embodiment of a bearing.

[0024] Figure 3 Is a detailed perspective view of an embodiment of a bearing.

[0025] Figure 4 Is a detailed view from above of an embodiment of a spring.

[0026] Figure 5 Is a detailed perspective view of an embodiment of a bearing body. DETAILED DESCRIPTION

[0027] The following description refers to Figures 1 to 5 An embodiment of a timepiece 200 is described.

[0028] The timepiece 200 is for example a watch, in particular a wristwatch.

[0029] The watch 200 comprises a watch movement 100. This watch movement is mounted in a watch case to protect it from the outside environment.

[0030] The watch movement 100 can be an electronic movement or a mechanical movement, in particular an automatic movement.

[0031] The watch movement comprises a watch mechanism 90.

[0032] The watch mechanism comprises a watch bearing 10. Preferably, the watch mechanism comprises two watch bearings 10, which are used to guide the element 6 at both ends of the element 6. This mechanism is for example a watch oscillator and comprises for example a balance and a spiral spring. Alternatively, this mechanism is for example an oscillator in the form of a monobloc, i.e. an inertial element formed in one piece with one or more elastic return members. Preferably, this bearing is particularly suitable for the pivoting of a shaft, in particular a shaft pivot, made of ceramic or glass. Such a shaft is for example the balance shaft 6.

[0033] The watch bearing 10 comprises a shock absorber. Thus, the watch bearing 10 is a shock absorbing bearing or a resilient bearing. This bearing is for example able to guide the rotation of a balance of a balance-spiral spring type oscillator around an axis A. This bearing is also for example able to prevent the translational movement of the balance along the axis A, in particular to limit the translational movement of the balance along the axis A. The balance comprises a shaft or a pivot, in particular the balance shaft 6.

[0034] This bearing comprises:

[0035] - a bearing body 2 comprising a through opening 20;

[0036] - a pivoting element 3, in particular a pierced jewel 3, designed to pivot the shaft 6, in particular the pivot 61 of the shaft 6;

[0037] - a setting element 4, in particular a jewel 4, designed to receive one end of the pivot 61 or to constitute a thrust bearing for one end of the pivot 61;

[0038] - a positioning ring 5 for positioning the pivoting element 3 and the setting element 4 within the opening 20 of the bearing body 2;

[0039] - a spring 1 integral with or fixed to the bearing body 2 and intended to elastically return and properly reposition the elements 3, 4, 5 within the opening 20 of the bearing body 2 after an impact on the watch 200, in particular the movement 100.

[0040] These elements are in particular visible in Figure 1 sectional view.

[0041] Preferably, the bearing body 2, and in particular the opening 20, has a geometry which is generally rotationally symmetrical about the axis A2. Preferably, the ring 5 also has a geometry which is rotationally symmetrical about the axis A5. After the ring 5 is housed in the opening 20 of the bearing body 2, the axes A2 and A5 coincide or substantially coincide. To this end, the ring 5 comprises frustoconical or inclined surfaces 53, 54 which are segmented along the axis A5 and which are intended to cooperate respectively with the segmented frustoconical or inclined surfaces 23, 24 inside the opening 20 of the bearing so as to centre the ring 5 in the bearing body 2. Here, this is a so-called "double cone" configuration.

[0042] The ring 5 comprises a through opening 50 for receiving the elements 3 and 4. More particularly, the opening 50 comprises a revolved surface 55 for receiving the axis A5 of the pivoting element 3, and a surface 56 perpendicular to the axis 5 for receiving the arbor element 4. The pivoting element 3 is in particular pinned on the surface 55. The arbor element 4 is arranged with a minimum clearance against the shoulder formed by the surface 56. The opening 50 also comprises a portion 57 for the passage of the shaft 6. The same applies to the opening 20 of the bearing body 2, which also comprises a portion 26 for the passage of the shaft 6.

[0043] After the pivoting element 3 has been assembled on the ring 5, the axis A3 of the pivoting element 3 coincides or substantially coincides with the axis A5 of the ring 5.

[0044] In an alternative configuration, the pivoting element 3 can well be made in one piece with the ring 5, so as to reduce as much as possible the number of assembly operations in the bearing 10 and the cumulative effect of the dimensions and tolerances. Furthermore, the ring 5 can be guided differently in the bearing body 2. For example, the shock absorber can be of the "reverse double cone" type, similar to the example described in document FR 1 532 798.

[0045] The shock absorbing bearing 10 is designed to be assembled on a semi-finished product 99 of a movement 100. To this end, the body 2 comprises a portion 25 which is designed to be pinned into the semi-finished product 99 of the movement 100. This semi-finished product can be a bridge, in particular a balance bridge, or can be a plate.

[0046] The function of the spring 1 is to return the elements 2, 3, 4 and 5 to Figure 1 their relative positions as shown. In particular, under the effect of an impact to which the watch is subjected, the balance, in particular the shaft 6, can move relative to the rest of the movement and in particular relative to the bearing body. It can move longitudinally relative to the axis A and / or radially relative to the axis A. The movement of the shaft 6 and the elastic return of the spring 1 imply a movement of the elements 3 and / or 4 and / or 5 relative to the body 2. After the end of the impact, the spring is able to return the elements to their positions.

[0047] The shock spring 1 preferably extends substantially in a plane P1. The spring advantageously comprises a first axis of symmetry A1 perpendicular to the plane P1. The spring comprises at least two first spring fixing elements 11, 11', 11" for fixing the spring. These first fixing elements each comprise at least one first fixing surface 11a, 11b, 11a', 11b', 11a", 11b" which is oriented at least substantially radially with respect to the first axis and which is directed towards the first axis. In particular, a vector n11 perpendicular to the first fixing surface 11a, 11b, 11a', 11b', 11a", 11b" extends substantially radially with respect to the first axis A1. The normal vector n11 can form an angle with the plane P1, in particular an angle of less than 20°, when the spring is mounted on the bearing body.

[0048] Advantageously, the first fixing surface can extend perpendicularly or substantially perpendicularly to the plane P1 when the spring is in its free state, i.e. in its unloaded state as shown, and when the spring is in its constrained state, i.e. in its preloaded state when it is mounted on the bearing body. Figure 4 Advantageously, the first fixing surface can extend perpendicularly or substantially perpendicularly to the plane P1 when the spring is in its free state, i.e. in its unloaded state as shown, and when the spring is in its constrained state, i.e. in its preloaded state when it is mounted on the bearing body.

[0049] The first fixing elements 11, 11', 11" extend at least substantially orthogonally radially with respect to the axis A1.

[0050] In addition to the first fixing elements 11, 11', 11", the spring comprises:

[0051] - at least two pressing elements 12c, 12c', 12c" for pressing against the drilling element 4; and

[0052] - at least two connecting elements 12a, 12b, 12d, 12e, 12a', 12b', 12d', 12e', 12a", 12b", 12d", 12e" mechanically connecting the pressing elements to the first fixing elements.

[0053] For example, the connecting elements are distinguished from the fixing elements by a boundary comprising a cylindrical surface C1 which is tangential to the first fixing surface (the spring being in its free state or in its constrained state mounted on the bearing body).

[0054] For example, the connecting elements are distinguished from the pressing elements by a boundary comprising a cylindrical surface C2 which is centred on the axis A1 or A2 or A3 and which has a diameter which is the same as or substantially the same as the outer diameter of the drilling element or which is the same as or substantially the same as the outer diameter of the pivoting element. Alternatively, the diameter of the cylindrical surface C2 can be less than the outer diameter of the drilling element or less than the outer diameter of the pivoting element. This configuration can increase the length of the connecting elements as much as possible.

[0055] The function of the fixing element is to fix the spring to the bearing body, in particular to fix the fixing element of the spring to the bearing body. This fixing can be achieved in particular by relative friction between the fixing element of the spring and the bearing body. Preferably, "fixing" means a complete or built-in connection between the fixing element of the spring and the fixing element of the bearing body, i.e. a connection that does not allow any degrees of freedom.

[0056] The function of the compression element is to exert a return force on the bit carrier element and / or the pivot element that can return the bit carrier element and / or the pivot element to a predetermined position, in particular to a predetermined and optimal position for the guide element 6. Preferably, the compression element is defined as an expansion of the spring that can come into contact with the bit carrier element when the bit carrier element is in its predetermined position and / or when the bit carrier element is in a position in which the spring is stressed due to an impact.

[0057] The spring preferably has a main structure in the form of a closed loop that is closed on itself. The spring can in particular have the shape of a closed loop that is closed on itself. This closed loop is preferably centered on the axis A1. Thus, the spring is formed for example from a single wire that is closed on itself. This wire can have a cross-sectional geometry that remains constant or varies along the length of the wire. Alternatively, the loop can have a cut or opening, that is to say the wire forming the loop has two ends, one on either side of the cut. The wire can in particular have a rectangular or square cross-section.

[0058] Preferably, "loop" means a wire-like geometry that has no branches or bifurcations. Preferably, this wire-like geometry does not intersect the axis A1 and / or does not cross the boundary area delimited by the cylinder C3 centered on the axis A1, the diameter of which is preferably less than 0.8 times the diameter of the cylinder C2, or less than 0.6 times the diameter of the cylinder C2. Preferably, the entirety of the loop can be traced by the curve B (shown in the figure), which can be traced by a curve with no return. Preferably, any point on this curve B can travel without return in a given direction on one and only one path along the entirety of the same curve, starting from a starting point located on this curve. Preferably, this curve is continuous. Preferably, the length of this curve B is greater than at least three times the diameter of the cylinder C1, or greater than at least four times the diameter of the cylinder C1, or greater than at least five times the diameter of the cylinder C1. Figure 4 The spring is preferably made of steel, in particular Durnico steel or Phytime or Phynox. Alternatively, the spring can be made of a metal alloy that is at least partially amorphous. Alternatively, the spring can in particular be made of nickel or a nickel-phosphorus alloy using a Liga-type process.

[0059]

[0060] ​Preferably, at least one portion 12a, 12e, 12a', 12e', 12a", 12e" of at least two connecting elements extends at least substantially radially with respect to the first axis Al.

[0061] Preferably, at least one portion 12b, 12d, 12b', 12d', 12b", 12d" of at least two connecting elements extends at least substantially orthoradially with respect to the first axis Al.

[0062] Preferably, the at least two pressing elements have a convex geometry when viewed from the inside of the spring, in particular from the first axis Al. Preferably, they each have an angular expansion with respect to the axis Al ranging between 45° and 90°, in particular when the spring has a 3-fold rotational symmetry. Preferably, more generally, when the spring has an n-fold rotational symmetry, each pressing element has an angular expansion with respect to the axis Al ranging between 270° / 2n and 270° / n.

[0063] Preferably, the at least two pressing elements each have a radial expansion with respect to the axis Al ranging between 0.25 and 0.75 times the outer radius of the collet element 4 held by said spring 1.

[0064] Each pressing element preferably mainly comprises a curved portion, in particular a circular portion 12c, 12c', 12c".

[0065] Each connecting element preferably mainly comprises:

[0066] - a first curved portion, in particular a first circular portion 12b, 12b', 12b", and a first straight portion 12a, 12a', 12a" connecting the first fixed element to the first pressing element; and

[0067] - a second curved portion, in particular a second circular portion 12d, 12d', 12d", and a second straight portion 12e, 12e', 12e" connecting the second fixed element to the relevant first pressing element.

[0068] The circular portions 12b, 12b', 12b", 12d, 12d', 12d" are convex when viewed from the outside of the spring in the plane PI.

[0069] Preferably, the at least two fixed elements extend at least substantially orthoradially with respect to the first axis Al.

[0070] Each fixed element preferably mainly comprises a curved portion, in particular a circular portion. These portions are convex when viewed from the outside of the spring in the plane PI.

[0071] Preferably, the spring has a shape which is at least substantially n-fold rotationally symmetrical or has n-fold rotational symmetry with respect to the first axis A1, wherein n is a natural integer, in particular wherein n = 2 or n = 3 or n = 4 or n = 5. In the illustrated embodiment, n = 3, which means that the spring has a trilobal geometry.

[0072] Preferably, the radially measured distance D separating the first fixing surface and the compression element is greater than 0.2 times the radius of the cylindrical surface C1, or greater than 0.3 times the radius of the cylindrical surface C1. Preferably, the radially measured distance D separating the first fixing surface and the compression element is less than 0.6 times the radius of the cylindrical surface C1, or less than 0.5 times the radius of the cylindrical surface C1.

[0073] Preferably, the first fixing surface is positioned substantially on the cylindrical surface C1, the diameter of which is equal to at least 1.5 times or at least 1.7 times the outer diameter of the collet element 4 which is pressed by the spring.

[0074] Preferably, these dimensions are determined for a spring which is not positioned or mounted on the bearing body, i.e. for a spring which is not stressed or constrained.

[0075] Advantageously, the first fixing elements each comprise at least one protrusion 1 1 c, 1 1 c', 1 1 c". The first fixing surface is preferably formed on the protrusion. The protrusions project towards the interior of the spring, i.e. they extend towards the interior of the spring. In the illustrated embodiment, each first fixing element comprises two protrusions.

[0076] Preferably, the fixing elements 1 1, 1 1 ', 1 1 " are equidistantly distributed around the axis A1 of the spring and are identical. Preferably, the compression elements 12c, 12c', 12c" are equidistantly distributed around the axis A1 of the spring and are identical. Preferably, the connection elements 12a, 12b, 12d, 12e, 12a', 12b', 12d', 12e', 12a", 12b", 12d", 12e" are equidistantly distributed around the axis A1 of the spring and are identical.

[0077] In the illustrated embodiment, the spring comprises:

[0078] - three fixing elements;

[0079] - three compression elements; and

[0080] - three connection elements.

[0081] The bearing body 2 comprises a second axis of symmetry A2 and at least two second spring fixing elements 21, 21', 21" for fixing the spring 1. These second fixing elements each comprise at least one second fixing surface 21c, 21c', 21c" which is oriented at least substantially radially with respect to the second axis and which faces away from the second axis A2. In particular, a vector n21 normal to the second fixing surface 21c, 21c', 21c" extends substantially radially with respect to the second axis A2 and projects from the fixing surface in a direction away from the second axis A2. In particular, the fixing surface 21c, 21c', 21c" is oriented towards the outside of the bearing body 2.

[0082] The second fixing elements are arranged to cooperate with the first fixing elements to fix the spring to the bearing body. In particular, the second fixing surfaces are arranged to cooperate with the first fixing surfaces to fix the spring to the bearing body. More particularly, the contact force between the first fixing surface and the second fixing surface, given or taking into account the coefficient of friction between the first fixing surface and the second fixing surface, has the same orientation or substantially the same orientation as the vectors n11 and n12. Thus, the first fixing surface exerts a force on the second surface which is directed along or substantially along the vector n11. The reaction force from the second surface towards the first surface is itself directed along or substantially along the vector n12.

[0083] The second fixing elements are respectively provided with a peg or tooth or cog 21, 21', 21" which extends mainly parallel to the axis A2. These pegs protrude from the outer peripheral surface 27 of the bearing body towards the outside of the bearing body in the radial direction of the axis A2 of the bearing body.

[0084] Preferably, the bearing body has at least substantially n-fold rotational symmetry about the second axis A2 or has n-fold rotational symmetry, where n is a natural integer, in particular where n = 2 or n = 3 or n = 4 or n = 5. In the embodiment shown, n = 3. Preferably, the second fixing elements 21, 21', 21" are equally distributed around the axis A2 of the bearing body 2 and are identical. The pegs 21, 21', 21" are separated by openings or gaps 22, 22', 22" at the surface 27 of the bearing body.

[0085] The pegs 21, 21', 21" each comprise a second fixing surface 21c, 21c', 21c". Each second fixing surface extends at the outer peripheral surface 27 of the bearing body. For example, these second fixing surfaces 21c, 21c', 21c" take the form of flat sites which are oriented radially with respect to the axis A2 and which extend orthogonally radially with respect to the axis A2.

[0086] After assembly of the spring 1 on the bearing body 2, the protrusions 11c, 11c', 11c" press against the flat portions 21c, 21c', 21c", respectively. In this configuration, the first fixing elements 11, 11', 11" of the spring 1 are positioned and held at the periphery of the second fixing elements 21, 21', 21", in particular at the periphery of the second fixing surfaces 21c, 21c', 21c".

[0087] In other words, when the spring 1 is assembled on the bearing body 2, in the radial direction with respect to one or the other of the axes Al or A2, the first fixing elements 11, 11', 11" of the spring 1 are further away from the axis Al or A2 than the second fixing elements 21, 21', 21", in particular the surfaces 21c, 21c', 21c", of the bearing body 2.

[0088] Advantageously, the ratio between the diameter of the larger cylinder inscribed between the first fixing surfaces and tangent to these first surfaces and the diameter of the smaller cylinder circumscribed on the second fixing surfaces is less than 1 or less than 0.99 or less than 0.98 (when the spring is removed or in a free or unconstrained state).

[0089] Preferably, each pin comprises two half-pins 21a, 21b, 21a', 21b', 21a", 21b". The half-pins of the same pin are separated from each other by a groove 21e, 21e', 21e" extending at least substantially radially with respect to the second axis A2. Thus, the first fixing elements 11, 11', 11" of the spring 1 each comprise a pair of protrusions 11c, 11c', 11c" which cooperate with a pair of half-pins 21a, 21b, 21a', 21b', 21a", 21b" of the second fixing elements 21, 21', 21" of the bearing body 2.

[0090] The configuration of the protrusions and flat portions allows the spring 1 to be pre-stressed so that it can be angularly held with respect to the axis A2 of the bearing body 2. Furthermore, the half-pins 21a, 21b, 21a', 21b', 21a", 21b" each comprise a shoulder 210a, 210b, 210a', 210b', 210a", 210b", i.e. a surface extending perpendicularly or substantially perpendicularly to the axis A2. Thus, this configuration of the pins allows the pairs of protrusions 11c, 11c', 11c" of the spring to be held axially.

[0091] In the figures, in particular in Figure 5In the particular embodiment of the bearing body 2 illustrated in the figures, flat portions 21c, 21c', 21c" are formed at the outer peripheral surface 27 of the bearing body 2, so that the first fixing elements 11, 11', 11" of the spring 1 are "suspended" around the bearing body 2 (after being put in place on the bearing body). In other words, the first fixing elements 11, 11', 11" of the spring 1 are positioned and held at the periphery of the bearing body 2.

[0092] Of course, it is entirely possible to construct the bearing body 2 so that it has a portion of dimensions, in particular diameter, which, when the bearing 10 is viewed from above, allows the spring 1 to be able to be contained entirely within.

[0093] The connecting elements 12a, 12b, 12d, 12e, 12a', 12b', 12d', 12e', 12a", 12b", 12d", 12e" of the spring 1 are themselves housed respectively in the openings or clearances 22, 22', 22" of the bearing body 2 provided between the pins. As seen previously, each of these connecting elements takes the form of two elastic blades 12a, 12b, 12d, 12e, 12a', 12b', 12d', 12e', 12a", 12b", 12d", 12e" comprising a plurality of substantially straight portions and curved portions.

[0094] Thanks to the manner in which the first fixing elements of the spring are arranged on the outside of the second fixing elements of the bearing body, it is possible to increase the effective length of the elastic blades as much as possible. To this end, each elastic blade can comprise, at one end and / or the other, a curved portion 12b, 12d, 12b', 12d', and 12b", 12d" which allows the effective length of each blade to be increased as much as possible.

[0095] In the particular embodiment of the spring illustrated in the figures, the cross section of the elastic blades is constant. The first fixing elements have substantially the same cross section as the elastic blades, except obviously in the region in which the protrusions extend. The boundary between the first fixing elements and the connecting elements can thus be determined by the presence or absence of the protrusions. However, the first fixing elements can be devoid of protrusions. In this case, the first fixing elements can have substantially the same cross section as the connecting elements. Alternatively, the protrusions can be replaced by notches designed to cooperate with the protrusions formed on each pin of the bearing body.

[0096] After the spring 1 is mounted on the bearing body 2, the compression elements 12c, 12c', 12c" are in contact with the retaining element 4 and exert on it a substantially axial return force, which is determined in particular by the level of preloading in the spring 1, which is defined in particular by the overall construction of the spring, in particular by the first and second fixed elements of the spring, and by the construction of the bearing body. This is achieved by the mobility of the compression elements and of the connecting elements with respect to the first fixed elements 11, 11', 11". More particularly, the construction of the spring, in particular of the leaves 12a, 12b, 12d, 12e, 12a', 12b', 12d', 12e', 12a", 12b", 12d", 12e", allows the connecting elements and the compression elements to move substantially rotationally about the axes A12, A12', A12" which are at least substantially radially orthogonal to the axes A1 and A2 and which extend at the interface between the fixed elements and the connecting elements. These axes A12, A12', A12" are shown in Figure 3 Figure 8. Thus, the compression elements 12c, 12c', 12c" can move outside the plane passing through the first fixed elements 11, 11', 11".

[0097] Thus, when the element 6 or the pivot 61 of the element 6 is impacted, each compression element and each connecting element of the spring 1 can exert an elastic return force on the elements 3, 4, 5 inside the bearing body 2, and this is achieved by the mobility of the compression elements and of the connecting elements with respect to the first fixed elements.

[0098] The effective length of the elastic leaves 12a, 12b, 12d, 12e, 12a', 12b', 12d', 12e', 12a", 12b", 12d", 12e", in combination with the cross section of the elastic leaves, can reduce the stiffness of the spring 1 as much as possible with respect to the dimensions of the bearing body 2, in particular the dimensions or the diameter along which the second fixed surface 21c, 21c', 21c" extends.

[0099] Furthermore, the elastic leaves 12a, 12b, 12d, 12e, 12a', 12b', 12d', 12e', 12a", 12b", 12d", 12e" can comprise more curved portions to increase their effective length as much as possible.

[0100] The bearing body 2 advantageously comprises a mechanism for mounting the spring 1 therein. It comprises in particular at each end of the pin or half-pin a chamfer 28 to help the passage of the first fixed elements under the shoulder 210a, 210b, 210a', 210b', 210a", 210b" of each pin or half-pin.

[0101] The bearing body 2 advantageously comprises mechanisms 21 d, 21 d', 21 d" for handling the spring. These mechanisms 21 d, 21 d', 21 d" comprising knurling allow the insertion of a tool for handling the spring into the region of its first fixing element, in particular between each of the protrusions provided on the first fixing element.

[0102] Of course, it is entirely possible to provide each first fixing element of the spring with a single independent protrusion. The same applies to the second fixing elements of the bearing body, which can each comprise a single independent solid pin, instead of two half-pins.

[0103] In a particular design of the bearing 10, the assembly of the spring on the bearing body can be of the "bayonet" type. In a first angular position of the spring relative to the bearing body, determined by the axis Al or A2, the spring can be detached from the bearing body, while in a second angular position of the spring relative to the bearing body, determined by the axis Al or A2, the spring can be fixed to the bearing body.

[0104] Preferably, the cross-section of the blades 12a, 12b, 12d, 12e, 12a', 12b', 12d', 12e', 12a", 12b", 12d", 12e" has a height measured parallel to the axis Al which is greater than a width measured in a plane perpendicular to the axis Al. Alternatively, the cross-section of the blades 12a, 12b, 12d, 12e, 12a', 12b', 12d', 12e', 12a", 12b", 12d", 12e" has a height measured parallel to the axis Al which is less than a width measured in a plane perpendicular to the axis Al.

[0105] Preferably, the second fixing surface is positioned substantially on a cylindrical surface having a diameter equal to at least 1.5 times or at least 1.6 times or at least 1.8 times the outer diameter of the collet element 4 held by the spring 1.

[0106] The solution described above makes it possible to reduce the stiffness of the spring as much as possible, in particular for a given cross-section and a given material of the spring. In particular, thanks to the solution described, the stiffness of the spring can be less than 4 N / mm or less than 3 N / mm. To achieve this, the particular construction of the spring comprises elastic portions in the form of blades whose effective length is as large as possible for a given size of bearing body. The blades have the particular feature of extending both inside and outside the bearing body. This is achieved by the first fixing element of the spring being positioned abutting the outside of the second fixing element provided, for example, on the outer periphery of the bearing body. In particular, the first fixing element of the spring extends radially at least substantially orthogonally to the axis of the spring or of the bearing body outside the second fixing element of the bearing body.

[0107] In particular, the above solution concerns a spring comprising at least two elastic portions extending at least substantially radially with respect to the axis of the spring or bearing body and formed in continuation of a first attachment or fixing portion extending at least substantially orthogonally radially with respect to the axis of the spring or bearing body and externally of a second attachment or fixing portion of the damper body, on both sides.

[0108] The advantage of this solution of a damper bearing is to provide a mechanical response optimized for a given geometry and / or a given material of the swing axle. It is possible in particular to reduce as much as possible the stiffness of such a spring and to make it as constant as possible regardless of the movement of the axle. Finally, the mounting / demounting of such a spring within the bearing body is particularly simple, thus simplifying the assembly plan and the after-sales service operations related to such a damper bearing.

[0109] Throughout the document, the orientation of a surface of a solid element is defined as the orientation of the vector normal to this surface, the normal vector emerging from the solid element at this surface.

[0110] Throughout the document, "fixed surface" preferably means a surface that makes permanent contact between the spring and the bearing body when the spring is mounted on the bearing body and as long as the spring is mounted on the bearing body. This contact is broken when the spring is removed.

[0111] Throughout the document, "at least substantially perpendicular" means "perpendicular or substantially perpendicular".

[0112] Throughout the document, "at least substantially parallel" means "parallel or substantially parallel".

[0113] Throughout the document, "at least substantially radially" means "radially or substantially radially".

[0114] Throughout the document, "at least substantially orthogonally radially" means "orthogonally radially or substantially orthogonally radially".

Claims

1. A shock-absorbing spring (1) for a watch (200), extending substantially in a plane (P1) and including a first axis of symmetry (A1) perpendicular to said plane (P1), said spring including at least two first fixing elements (11, 11', 11”), each of the first fixing elements including at least one first fixing surface (11a, 11b, 11a', 11b', 11a”, 11b”), the first fixing surface being at least substantially radially oriented relative to and toward the first axis of symmetry (A1). At least one of the first fixing surfaces is located on the protrusion, the protrusion protruding toward the first axis of symmetry relative to a corresponding adjacent surface, the adjacent surface being oriented at least substantially radially toward the first axis of symmetry, and the adjacent surface being located on both sides of at least one of the first fixing surfaces along an orthogonal radial direction relative to the first axis of symmetry.

2. The spring according to claim 1, wherein, The spring has a shape with at least n-order rotational symmetry about the first axis of symmetry (A1), where n is a natural integer, and / or the spring has the form of a self-closing closed loop.

3. The spring according to claim 1, wherein, The spring has a shape with at least n-order rotational symmetry about the first axis of symmetry (A1), where n = 2, n = 3, n = 4, or n = 5.

4. The spring according to any one of claims 1 to 3, wherein, The spring includes at least two clamping elements (12c, 12c', 12c”) for pressing against the drill element (4) and at least two connecting elements (12a, 12b, 12d, 12e, 12a', 12b', 12d', 12e', 12a”, 12b”, 12d”, 12e”) for mechanically connecting the clamping elements to the first fixing element.

5. The spring according to claim 4, wherein, At least one portion (12a, 12e, 12a', 12e', 12a”, 12e”) of the at least two connecting elements extends at least substantially radially relative to the first axis of symmetry (A1).

6. The spring according to claim 4, wherein, At least one portion (12b, 12d, 12b', 12d', 12b”, 12d”) of the at least two connecting elements extends at least substantially orthogonally radially relative to the first axis of symmetry (A1).

7. A bearing body (2) comprising a second axis of symmetry (A2) and at least two second fixing elements (21, 21', 21”) for fixing a spring (1), each of the second fixing elements comprising at least one second fixing surface (21c, 21c', 21c”), the second fixing surface being at least substantially radially oriented relative to the second axis of symmetry and toward a direction away from the second axis of symmetry, each of the second fixing elements comprising a pin, the second fixing surface being formed on the pin.

8. The bearing body according to claim 7, wherein, The bearing body has a shape with at least substantially n-order rotational symmetry about the second axis of symmetry (A2), where n is a natural integer.

9. The bearing body according to claim 8, wherein, n = 2 or n = 3 or n = 4 or n = 5.

10. The bearing body according to claim 7, wherein, Each of the said pins includes a groove that extends at least substantially radially relative to the second axis of symmetry.

11. A bearing comprising a bearing body according to any one of claims 7 to 10 or a spring according to any one of claims 1 to 6.

12. The bearing according to claim 11, wherein, The bearing includes a drill support element (4) and / or a pivot element (3) and / or a positioning ring (5) for positioning the drill support element and / or the pivot element.

13. A bearing comprising a bearing body according to any one of claims 7 to 10 and a spring according to any one of claims 1 to 6.

14. The bearing according to claim 13, wherein, When the spring is removed or in a free or unrestrained state, the ratio between the diameter of the larger cylinder inscribed between the first fixed surfaces and the diameter of the smaller cylinder inscribed on the second fixed surface is less than 1, less than 0.99, or less than 0.

98.

15. A watch mechanism (90) comprising a bearing according to any one of claims 11 to 14 and / or a spring according to any one of claims 1 to 6 and / or a bearing body according to any one of claims 7 to 10.

16. The watch mechanism according to claim 15, wherein, The clock mechanism is an oscillator of the balance wheel-hairspring type.

17. A watch movement (100) comprising a bearing according to any one of claims 11 to 14 and / or a spring according to any one of claims 1 to 6 and / or a bearing body according to any one of claims 7 to 10 and / or a watch mechanism according to claim 15 or 16.

18. A watch (200) comprising a watch movement according to claim 17 and / or a bearing according to any one of claims 11 to 14 and / or a spring according to any one of claims 1 to 6 and / or a bearing body according to any one of claims 7 to 10 and / or a watch mechanism according to claim 15 or 16.

19. The clock according to claim 18, wherein, The clocks and watches include wristwatches.

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