• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The watch movement comprising a pivoting element (24), a bearing (28) for a pivot of this pivoting element and an anti-shock device (30) associated with this bearing and comprising an elastic member (32) arranged to exert a restoring force on at least one counter pivoting stone (36). The anti-shock device further comprises a magnetic system (40) formed of two magnets and a high magnetic permeability element (46) arranged between these two magnets and integral with one of them, the two magnets being respectively fixed to a support of the shockproof device and the elastic member and arranged to generate between them, in association with the high magnetic permeability element, a global magnetic attraction force on a first section of a possible displacement distance for the counter-pivot stone in the event of impact and a global repulsion magnetic force on a second section of this displacement distance corresponding to distances greater than those of the first section.
    公开号:CH712502A2
    申请号:CH00522/17
    申请日:2017-04-19
    公开日:2017-11-30
    发明作者:Lenoir Deirdré；Sarchi Davide；Légeret Benoît
    申请人:Montres Breguet Sa；
    IPC主号:
    专利说明:

    Description
    Field of the Invention [0001] The present invention relates to horological shock devices. Such shockproof devices are generally associated with bearings that guide rotation of the pivoting elements of the watch movement, in particular rockers. We also speak of shock absorbers, bumpers or shock absorbers. The invention relates more particularly to the damping of axial shocks undergone by pivoting elements and the mechanical stresses experienced by the pivots during such axial shocks.
    BACKGROUND OF THE INVENTION [0002] A conventional horological shock-absorbing device comprises an elastic member which carries or exerts a pressure against at least one stone against the pivot of the bearing equipped with this shock-proof device, this counter-pivot stone forming a stop for the pivot inserted in this bearing in the direction of the axis of rotation of the pivoting element considered. This shockproof device is arranged so as to generate, via the counter-pivot stone, a restoring force on the pivot in question when the pivot presses in case of impact against the stone against pivot. By "pivoting stone" is meant any structure, in any suitable material, which defines an axial bearing surface for the pivot.
    Such anti-shock devices generally comprise mechanical springs which are dimensioned empirically, following practical rules such as that of the best compromise between mechanical stability during operation and elastic resistance to mechanical deformations. Indeed, it is desirable to have a relatively rigid damper which does not generate axial movements of the pivoting element at each small impact, while ensuring the function of shock absorber for violent shocks generating large axial accelerations (positive or negative) for this pivoting element that could damage its pivots.
    In particular, the conventional shock devices of the spring balance, the parachutes (also called fall arrestors) and the lyres, are dimensioned not to be activated until relatively large shock accelerations (between 200 g and 500 g). g, g being the terrestrial acceleration), thanks to a prestressing of the spring forming these parachutes and lyres which defines a threshold value. Beyond this threshold value, it is expected that the spring deforms and absorbs some of the energy of the shock. However, because of the low mechanical damping of the metal blades used, most of the energy is returned to the pendulum. The local deformation of the pendulum pivot is therefore very likely, already for relatively small shocks. Such deformation, which has a considerable impact on the chronometric accuracy of the watch, is generally neglected because the certified chronometer standard is not very severe for the chronometric stability of a watch as a result of a shock of a watch. meter (60 s / day difference). SUMMARY OF THE INVENTION The object of the present invention is to provide a watch movement equipped with at least one effective anti-shock device which provides a solution to the problem of deterioration of the pivots of a pivoting element in the event of shocks, even in case of strong shocks.
    For this purpose, the present invention relates to a watch movement as defined in claim 1.
    Thanks to the features of the invention, which will be described in detail later, the shockproof device has a lower resistance for relatively strong shocks while ensuring good stability for less shock. Indeed, the rigidity of the anti-shock device according to the invention no longer behaves like a mechanical spring which generates a restoring force substantially proportional to the axial displacement of the stone against pivot. On the contrary, it exerts a relatively large force when the displacement is zero, which then decreases at least on an initial portion of the shock-absorbing path that can cross the stone against pivot.
    In a main embodiment, the first and second magnets and the high magnetic permeability element are aligned in a direction substantially parallel to the axis of rotation of the pivoting element, the first and second magnets having polarities. opposite in this direction.
    In a preferred embodiment, the high magnetic permeability element is attached to the first magnet.
    BRIEF DESCRIPTION OF THE DRAWINGS [0010] The invention will be described below with the aid of the accompanying drawings, given by way of non-limiting examples, in which:
    Fig. 1 is a perspective view from below of an anti-shock device according to a first embodiment of the invention;
    Fig. 2 is a partial sectional view of a watch movement incorporating the anti-shock device of FIG. 1, carried out through this shockproof device;
    Fig. 3 is a side view, partly in section, of a magnetic system similar to that incorporated in the anti-shock device of the invention;
    Fig. 4 shows the graph of the overall magnetic force exerted on a moving magnet as a function of its distance from a ferromagnetic disk for the magnetic system of FIG. 3;
    Fig. 5 shows the graph of the elastic force exerted by the flat spring of the anti-shock device of FIG. 1 on the pivot of a pivoting element and the graph of the total force exerted by the anti-shock device as a function of the displacement of this pivot, bearing against a counter-pivot stone, along its axis of rotation;
    Fig. 6 is a top view of an anti-shock device according to a second embodiment of the invention;
    Fig. 7 is a partial sectional view of a watch movement incorporating the anti-shock device of FIG. 6, performed through this shockproof device;
    Fig. 8 shows the graph of the elastic force exerted by the lyre spring of the anti-shock device of FIGS. 6 and 7 on the pivot of a pivoting element and the graph of the total force exerted by the anti-shock device as a function of the displacement of this pivot, bearing against a counter-pivot stone, along its axis of rotation.
    Detailed Description of the Invention [0011] Using FIGS. 1 to 5, will be described below a first embodiment of a watch movement 22 incorporating a pivoting element 24, a bearing 28 in which is arranged a pivot 26 of the pivoting element and an anti-shock device 30 associated with this bearing.
    In general, the shockproof device 30 comprises an elastic member 32 which exerts a force on a counter-pivot stone 36, which forms a stop for the pivot 26 in the direction of the axis of rotation of the pivoting member . This shockproof device is arranged in such a way as to be able to generate, by means of the counter-pivot stone, a restoring force on the pivot 26 when this pivot presses, in the event of an impact, against this counter-pivoting stone. According to the invention, the anti-shock device further comprises a magnetic system 40 formed of two magnets 42, 44 and a high magnetic permeability element 46 arranged between these two magnets and integral with one of them. These two magnets are respectively fixed to a support 48 of the shock-proof device and to the elastic member 32, so as to be able to present a relative movement between them over a certain relative distance D (referenced in FIG. undergoes, especially in the event of a certain shock, momentarily elastic deformation under a certain pressure exerted by the pivot against the stone against pivot. More particularly, the magnet 44, integral with the elastic member, is arranged to undergo, in case of relatively strong axial shocks for the pivoting element, a reciprocating movement symbolized in FIG. 2 by a two-way arrow. In the absence of shock, the elastic member is in a specific rest position and the magnet that it also carries. Note that in this rest position, the elastic member may have an initial elastic deformation. In the latter case, it is said that the elastic member is prestressed.
    [0013] Remarkably and very advantageously, as will be explained below with reference to FIGS. 3 and 4, the two magnets 42 and 44 are arranged to generate between them, in association with the high magnetic permeability element 46, a global magnetic attraction force on a first section of the aforementioned relative distance and a force overall magnetic repulsion on a second section of this relative distance, this second section corresponding to distances (referenced E in Figure 3) between the first and second magnets which are greater than the distances corresponding to the first section. In addition, the magnetic system 40 and the elastic member 32 are arranged so that the total force exerted in case of shock by the shockproof device on the pivot 26 remains a restoring force for the integer of the relative distance.
    Particular variants of the first embodiment, all shown in FIG. 2, are the following: the element with high magnetic permeability 46 is fixed to the magnet 42 integral with the support 48; - The element with high magnetic permeability is formed by a wafer having a central axis which is substantially coincident with the magnetization axis of the magnet 42; - When the elastic member is in its rest position, the two magnets 42, 44 and the high magnetic permeability element 46 are aligned in a direction substantially parallel to the axis of rotation 50 of the pivoting member 24; - The magnets 42 and 44 have polarities opposite in the direction of their alignment.
    In particular, according to the variant shown in FIGS. 1 and 2, the two magnets are cylindrical and the wafer is in the form of a disc made for example of a ferromagnetic material.
    With reference to FIGS. 3 and 4, the magnetic system 40 and its operation will be described below. For this purpose, it is shown in FIG. 3 a magnetic system 52 similar to the magnetic system 40. Thus, the magnetic system 52 comprises a first magnet 4, a high magnetic permeability element 6 which is integral with the first magnet, and a second magnet 8 which is movable, along an axis of displacement, relative to the assembly formed by the first magnet 4 and the element 6. As indicated above, the element 6 is arranged between the first magnet and the second magnet, in contact or close to the first magnet. In particular, the element 6 is glued to the first magnet as shown in FIG. 3. In another variant, the first magnet can be driven into the element with high magnetic permeability which then for example has the shape of a cylindrical box open at one end to receive the first magnet. In a preferred variant, the distance between the element 6 and the magnet 4 integral with this element is less than or substantially equal to one-tenth of the length of this magnet along its axis of magnetization. The first magnet 4 and the element 6 form a first part of the magnetic system and the second magnet 8 forms a second part of this system. The element 6 consists for example of a carbon steel, tungsten carbide, nickel, FeSi or FeNi, or other alloys with cobalt such as Vacozet® (CoFeNi) or Vacoflux® (CoFe). In an advantageous variant, this element with high magnetic permeability consists of a metal glass based on iron or cobalt. Element 6 is characterized by a saturation field Bs and a permeability u. The magnets 4 and 8 are for example ferrite, FeCo or PtCo, rare earths such as NdFeB or SmCo. These magnets are characterized by their remanent field Br1 and Br2.
    The high magnetic permeability element 6 has a central axis 10 which is substantially coincident with the magnetization axis of the first magnet 4 and also with the magnetization axis of the second magnet 8. The magnetization senses respective magnets 4 and 8 are opposite. These first and second magnets therefore have opposite polarities and they are likely to undergo a relative movement between them over a certain relative distance D. In the example shown in FIG. 3, the magnet 4 is fixed and the magnet 8 is movable so that the relative movement between them has a direction substantially along the central axis 10 which then defines the axis of displacement. It will be noted that the axis 10 is linear, but this is a non-limiting variant. In the context of the first embodiment of the invention, the axis of displacement is substantially circular arc, the central axis of the element 46 being substantially tangential to this axis of displacement curve. In such a case, as a first approximation, the behavior of the magnetic system 40 is similar to that of the magnetic system 52. This is all the more true that the radius of curvature is large relative to the maximum possible distance between the element 46 and the magnet 44, as is the case in the first embodiment of the invention. In a preferred variant, as shown in FIG. 3, the element 6 has dimensions in a plane orthogonal to the central axis 10 which are greater than those of the first magnet 4 and those of the second magnet in projection in this orthogonal plane. It will be noted that, in the case where the second magnet abuts against the element 6 at the end of the magnetic attraction stroke, this second magnet advantageously has a hardened surface or a thin layer of hard material on its surface.
    The two magnets 4 and 8 are arranged in magnetic repulsion so that, in the absence of the element with high magnetic permeability 6, a repulsion force tends to move these two magnets away from each other. Surprisingly, however, the arrangement between these two magnets of the element 6 reverses the direction of the magnetic force between the first and second parts of the magnetic system when they are at a short distance from each other. so that a global force of magnetic attraction is then generated between these two parts. Fig. 4 is a graph whose curve 54 represents the magnetic interaction force between the first and second parts of the magnetic system 52 as a function of the distance E between the two magnets, respectively from the relative distance D between the moving magnet 8 and the element with high magnetic permeability 6. It is observed that the magnet 8 undergoes, on a first section D1 of the relative distance, generally a magnetic attraction force which tends to maintain the magnet 8 against the element 6 or to bring him back to him in case of removal. Then, the element 6 and the two magnets are arranged so that the second magnet undergoes, on a second section D2 of the aforementioned relative distance, globally a magnetic repulsion force. This second section corresponds to distances between the first and second parts, and therefore at distances D between the element 6 and the magnet 8, which are greater than the distances corresponding to the first section of the relative distance. The second section is limited by a maximum distance Dmax which is generally defined by a stop limiting the distance of the moving magnet.
    The overall magnetic force is a continuous function of the distance between the components and it has a zero value at the distance Dinv. Thus, when the distance between the magnet 8 and the element 6 is greater than a distance Dinv, this magnet is subjected to a global magnetic repulsion force which tends to move it away from the element 6. On the other hand, when the distance between the element 6 and the movable magnet 8 is smaller than the distance Dinv, the magnet 8 is subjected to a global magnetic attraction force which tends to approach the element 6 and, if nothing opposes it, putting it in contact with that element, and then keeping it in that position. This is a remarkable operation of the magnetic system 52 which is used in the anti-shock device according to the invention. The inversion distance Dinv is determined by the geometry of the three magnetic parts forming the magnetic system and their magnetic properties.
    Hereinafter will be described in more detail the anti-shock device 30 according to the first embodiment and its behavior resulting from the incorporation, according to the invention, of the magnetic system 40. The elastic member 32 is formed by a spring flat having a first end 56 and a second end 58, the first end being fixed to the support 48 by means of a screw 60 and the second end carrying the second magnet 44. According to an advantageous variant, the counter-pivoting stone 36 is located , in projection in a general plane of the flat spring, between the first and second ends. The bearing 28 comprises a base 62 fixedly arranged in an opening of the support 48. In a conventional manner, this base has at its center a hole through which the pivot 26 passes. The pivoting element 24, here the shaft of a balance ( not shown) has a bearing 70 which classically limits the movement of this element along the axis 50, this bearing abutting against a surface defined by the base to the device of the hole. The bearing 28 further comprises a kitten 64 in which is inserted the counter pivot stone 36. In the variant shown, it is a magnetic bearing. Thus, the kitten still supports a magnet 66 and a closing stone 68. This kitten also participates in the anti-shock device. It is arranged in a housing formed by the base 62 and a closure plate 72 fixed to the support 48, so as to be able to undergo an axial movement at least over a distance corresponding to the maximum displacement that can undergo in case of impact the pivot 26 when the span 70 abuts against the base. A short tube 74 is fixed to the flat spring 32 at its end end 58 so as to bear against the kitten or the closure stone. The anti-shock device acts on the integral assembly of the counter-pivot stone via this tube. It should be noted that the invention is not limited to a magnetic bearing. Thus, in another variant, there is a conventional bearing with a kitten incorporating a pierced stone and a counter-pivot stone, the latter may have a flat surface opposite the pivot.
    The magnetic system and the elastic member are arranged so that, in a rest position of the shock-proof device, the counter-pivot stone or a kitten to which it is attached is held (e) in abutment against the support of the bearing or against a base of this bearing as long as the force exerted by the pivot considered against the counter pivot stone is less than a limit value, the latter being preferably provided greater than the gravitational force acting on the pivoting element, in particular the balance -spiral. In a particular variant, the elastic element is prestressed in the rest position of the shock-proof device, so that the counter-pivot stone remains immobile over a larger range of values of the force exerted by the mobile element undergoing axial acceleration. in case of shock.
    In FIG. FIG. 5 shows the graph of the elastic force exerted by the flat spring 32 and the graph of the total force exerted by the shockproof device 30 as a function of the displacement DP of the counter-pivot stone and thus of the pivot 26, bearing against this stone. counter-pivot, along its axis of rotation 50. It will be noted that there is a linear relationship (as a first approximation) between the displacement DP and the distance D of the magnetic system 40 described above. In a known manner, the elastic force varies proportionally with the displacement DR. Its graph is an affine line 76 in broken lines. The graph of the total force exerted by the anti-shock device on the assembly carrying the counter-pivot stone, and through it on the pivot 26 bearing against this stone, according to its displacement DP is given by the curve 78 which corresponds to the sum of the elastic force and the overall magnetic force generated by the magnetic system 40. It is observed that this total force (restoring force) is greater than the elastic force on a first section DP1 between a distance DPR, corresponding to the rest position of the anti-shock device, and a distance DPinv corresponding to a position of the pivot-against stone for which the overall magnetic force exerted on the magnet 44 is zero. Then, between the distance DPinv and a distance DPmax, for which the shaft 24 of the balance is in abutment against the peripheral surface of the hole in the base of the bearing, the total force is less than the elastic force because the global magnetic force s' then opposes the elastic force, which decreases the total force exerted on the pivot of the rotating element.
    The shockproof device according to the invention has a remarkable behavior as shown by the curve 78. The force exerted on the pivot bearing against the stone against pivot, at least for a displacement distance of this stone less than DPinv, is maximum for the idle distance DPr of the shockproof device. As soon as the force applied by the pivot to the counter-pivot stone rises above the maximum value occurring for the rest position of the anti-shock device, the counter-pivot stone moves away from its rest position and then the total force against the pivot 26 decreases relatively quickly, which directly ensures a relatively large movement of the stone against pivot and a good shock damping to the stop position. In the example given in fig. 5, the flat spring has a rigidity close to a standard stiffness but its preload is reduced, compared to a standard prestress, by a factor of about 30% to 40%, while having a usual stability for the shock-proof device in his rest position.
    The dependence of the total force on the pivot as a function of the axial displacement of the balance and the corresponding displacement of the shockproof device allows the following operation (for a variant with a balance having a weight of about 40 mg and a material element ferromagnetic between the two magnets of the magnetic system): 1) For an acceleration shock of less than 400 g, the shockproof device remains stationary due to the magnetic attraction force and the prestressing of the spring which is seated. 2) For a shock that exceeds 400 g, in particular 1000 g, the movable magnet carried by the spring is detached from the ferromagnetic element and the magnetic force decreases rapidly and then reverses, opposing the elastic force applied by the spring. Once the activation threshold force of an axial movement of the shock device has been exceeded, the resulting total force decreases at least over a major part of the possible displacement for the pivot, the deformation of the shock becoming immediately very important and allowing the pendulum to arrive quickly in mechanical stop. This makes it possible to absorb the kinetic energy of the balance by limiting the force applied on the pivot over the entire shock absorption path.
    Once the shock is complete, the shock device can return to its original position, because it is expected that the total force remains positive (restoring force) and exceeds the friction forces. The inversion of the magnetic force, which takes place when the moving magnet is sufficiently close to the ferromagnetic element, simultaneously ensures the absolute absence of mechanical hysteresis and the re-centering of the bearing after an impact.
    The following advantages arise from the characteristics of the shockproof device according to the invention: - The shockproof device works as a real shock absorber (unlike traditional shockproof); - Ability to dimension the shockproof device by optimizing the preload (thus the operation for small shocks where stability of the bearing is desired) and the shock absorber response for large shocks; - After a great shock, repositioning the shockproof device in its given rest position and refocusing the kitten (defining the axis of rotation of the balance) provided by the magnetic attraction force; - The force experienced by the pendulum pivot during the great impact is reduced, the maximum force being preferably the total force of the shock device intervening in its rest position.
    [0027] Referring to FIGS. 6-8, will be described hereinafter a watch movement 82 incorporating a second embodiment of an anti-shock device according to the invention. The bearing and the shock device 86 which is. Associated are arranged in an opening of a plate 84. The resilient member 88 is a lyre spring having two branches 89 and 90 arranged to exert pressure on the pivoting stone 36A. In a variant (not shown), the two branches press on a kitten which is fixed against the pivot stone. The anti-shock device comprises a first magnetic system 40A and a second magnetic system 40B each similar to the magnetic system 40 described in the first embodiment. Thus, the remarkable operation of these two magnetic systems will not be described again here.
    The two magnetic systems are respectively associated with two structures 92 and 94 which are respectively fixed to the two branches 89 and 90 substantially in their central zone. These two structures respectively carry two magnets 44A and 44B each forming the moving magnet of the respective magnetic system. Thus, the two branches are respectively associated with the first and second magnetic systems and carry, through the structures 92 and 94, each a movable magnet 44A, respectively 44B which cooperates with a fixed magnet 42A, respectively 42B. Each magnetic system further comprises a high magnetic permeability element 46A, respectively 46B, which is integral with the fixed magnet of the respective magnetic system.
    It will be noted that each of the legs 89, 90 of the lyre-spring, conventionally, is retained axially at its two ends by angularly projecting portions of an upper ring of the base 62A of the bearing. Thus, it is in the median zone of these branches that the lyre spring undergoes in the event of stress a maximum elastic deformation. It should also be noted that each branch substantially presses in the middle on the counter-pivot stone. Preferably, but in a nonlimiting manner, the two structures 92 and 94 are integral with the lyre spring and have a greater rigidity than that of the respective branches, in particular by a greater thickness as shown in the figures. However, in another variant, the structures have the same thickness as the branches of the lyre spring to facilitate manufacture, but have larger sections. However, in another variant, the rigidity of the supporting structures of the moving magnets is not greater than those of the branches, the mobile magnets performing in case of large shocks longer courses than the counter-pivot stone.
    The arrangement of two magnetic systems symmetrically associated respectively with the two elastic branches of the lyre spring is advantageous because it results from such an arrangement the same pressure of each branch on the counter-pivot stone, or more generally on the mobile assembly 96 of the bearing, for the same elastic deformation of the two branches. This maintains a uniform behavior of the anti-shock device and in particular the counter-pivot stone 36A in a general plane perpendicular to the axis of rotation of the balance in the event of axial shocks.
    FIG. 8 shows the curve 76A of the elastic force applied by the spring-lyre to the stone against pivot, and thus on the pivot 26 bearing against it, depending on the axial displacement of the stone against the pivot, and the curve 100 of the total force exerted by the anti-shock device 86 on the pivot as a function of said axial displacement. It will be noted that the variant shown is particular in that no mechanical prestressing of the anti-shock device is provided in the rest position, only the magnetic attraction force ensuring the immobility of the anti-shock device in its static operating range ( idle position here corresponding to a displacement DP equal to zero) up to a certain maximum static force of this shockproof device. The preponderance of the magnetic force in the rest position makes it possible to reduce the total restoring force well below the maximum force of the static situation as soon as the shockproof device enters its dynamic operating range and is therefore armed. . This ensures that the maximum force applied to the pivot, in abutment against the counter-pivot stone is that of the shock device in non-armed condition. Thus, during a sudden movement of the pivot due to a large axial shock, the balance moves with less resistance until it meets the stop formed by the base of the bearing. Note that this stop, by acting on an annular bearing shaft 24 of the balance, protects the pendulum pivot in case of violent shocks.
    Finally, the rigidity of the lyre spring and the sizing of the two magnetic systems are provided in such a way that the total resulting force applied by the shockproof remains a greater restoring force to the friction forces to ensure, after a shock generating a force greater than the maximum force intervening for the static situation on the mobile assembly 96 of the bearing, the return of the shockproof device in its initial position and a good refocusing of this mobile assembly (crucial property to ensure good chronometry of the watch movement).
    Note that, advantageously in the context of the second embodiment, the two bearings of a sprung balance are equipped with a shock absorber device of the type described above.
    权利要求:
    Claims (11)
    [1]
    claims
    1. A watch movement (22; 82) comprising a pivoting element (24), a bearing (28) in which a pivot (26) of this pivoting element is arranged and an anti-shock device (30; 86) associated with this bearing, the anti-shock device comprising an elastic member (32; 88) arranged to be able to exert pressure on at least one counter-pivoting stone (36; 36A) forming an abutment for said pivot in the direction of the axis of rotation (50) of the pivoting element, this shockproof device being arranged in such a way as to be able to generate, by means of the counter-pivot stone, a restoring force on said pivot when this pivot presses, in the event of an impact, against the counter-stone pivot; characterized in that the anti-shock device further comprises a magnetic system (40; 40A, 40B) formed of two magnets (42,44) and a high magnetic permeability element (46) arranged between these two magnets and integral with the magnet. one of them, the first and second magnets being respectively fixed to a support (48) of the shockproof device and to the elastic member so as to be able to present a relative movement between them over a certain relative distance when the elastic member undergoes , in the event of an impact, an elastic deformation under a pressure exerted by said pivot against said counter pivot stone; in that said first and second magnets are arranged to generate between them, in association with said high magnetic permeability element, a global magnetic attraction force on a first section of said relative distance and a global magnetic force of repulsion on a second section of this relative distance, this second section corresponding to distances between the first and second magnets which are greater than the distances corresponding to the first section; and in that said magnetic system and said elastic member are arranged so that the total force exerted in the event of shock by the shockproof device on said pivot remains a restoring force for the integer of said relative distance.
    [2]
    2. watch movement according to claim 1, characterized in that the first and second magnets and said high magnetic permeability element are aligned in a direction substantially parallel to the axis of rotation (50) of said pivoting element, the first and second magnets having polarities opposite in this direction.
    [3]
    3. watch movement according to claim 2, characterized in that said element with high magnetic permeability is formed by a wafer having a central axis which is substantially coincident with the magnetization axis of the first magnet.
    [4]
    4. Watchmaking movement according to claim 2 or 3, characterized in that the distance between the element with high magnetic permeability and the magnet secured to this element is less than or substantially equal to one tenth of the length of the magnet along its axis. magnetization.
    [5]
    5. Watchmaking movement according to any one of the preceding claims, characterized in that said element with high magnetic permeability is attached to the first magnet.
    [6]
    6. Watchmaking movement according to claim 5, characterized in that the magnetic system and the elastic member are arranged so that, in a rest position of the shockproof device, the resilient member maintains the counter-pivot stone or a kitten to which is fixed this counter-pivot stone bearing against said support or against a base integral with the support as long as the force exerted by said pivot against the counter-pivot stone is less than a limit value, this limit value being greater than the force gravitational acting on said pivoting element.
    [7]
    7. Watch movement according to claim 6, characterized in that said elastic element (32) is prestressed in said rest position of said shockproof device.
    [8]
    8. Horological movement according to any one of the preceding claims, characterized in that the element with high magnetic permeability consists of a metal glass based on iron or cobalt.
    [9]
    Clock movement according to one of the preceding claims, characterized in that said elastic member is a flat spring (32) having a first end and a second end, the first end being fixed to said support and the second end (58). carrying the second magnet, said counter pivot stone being located, in projection in a general plane of the flat spring, between the first and second ends.
    [10]
    10. watch movement according to any one of claims 1 to 8, characterized in that said elastic member is a lyre spring (88) having two legs (89, 90) arranged to exert pressure on the stone against pivot or on a kitten to which is fixed this stone against pivot; in that said magnetic system defines a first magnetic system and the shockproof device further comprises a second magnetic system as defined in any one of claims 1 to 8, said two branches respectively being associated with the first and second magnetic systems and carrying each a magnet, corresponding to said second magnet, which cooperates with a respective magnet, corresponding to said first magnet, fixed to said support of the shockproof device.
    [11]
    11. Watch movement according to any one of the preceding claims, characterized in that said pivoting element is a pendulum.
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    同族专利:
    公开号 | 公开日
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    JP6340114B2|2018-06-06|
    HK1245425A1|2018-08-24|
    US20170336761A1|2017-11-23|
    CN107402511B|2019-08-09|
    JP2017207485A|2017-11-24|
    CN107402511A|2017-11-28|
    EP3246764B1|2019-01-23|
    引用文献:
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    DE2541124A1|1975-09-16|1977-03-24|Rheinfelder Uhrteile Fab|Timepiece balance shaft shock absorbing bearing - has apertured inner jewel and flat outer jewel fitting into slip ring|
    US4308605A|1980-02-12|1981-12-29|Ayer Henry E|Balance wheel assembly|
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    EP2469357B2|2010-12-21|2016-06-29|The Swatch Group Research and Development Ltd.|Shock-absorbing bearing for a rotating mobile of a clock movement|
    JP2015152402A|2014-02-13|2015-08-24|セイコーインスツル株式会社|Magnet bearing structure, movement, and watch|
    EP3081997A1|2015-04-16|2016-10-19|Montres Breguet S.A.|Magnetic shock-absorber for timepiece arbour|
    EP3106934A1|2015-06-16|2016-12-21|Montres Breguet S.A.|Magnetic device for pivoting an arbour in a clock movement|
    EP3106933B1|2015-06-16|2018-08-22|Montres Breguet S.A.|Magnetic pivoting device for an arbour in a clock movement|EP3671369A1|2018-12-18|2020-06-24|ETA SA Manufacture Horlogère Suisse|Device for geometric control for timepiece wheels|
    法律状态:
    2020-09-15| AZW| Rejection (application)|
    优先权:
    申请号 | 申请日 | 专利标题
    CH6392016|2016-05-18|
    EP16170213|2016-05-18|
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