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EP3916489A1 - Dämpfungsfeder, lagerkörper und lager für uhr - Google Patents

Dämpfungsfeder, lagerkörper und lager für uhr Download PDF

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Publication number
EP3916489A1
EP3916489A1 EP20177619.2A EP20177619A EP3916489A1 EP 3916489 A1 EP3916489 A1 EP 3916489A1 EP 20177619 A EP20177619 A EP 20177619A EP 3916489 A1 EP3916489 A1 EP 3916489A1
Authority
EP
European Patent Office
Prior art keywords
spring
axis
bearing
bearing body
fixing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP20177619.2A
Other languages
English (en)
French (fr)
Inventor
Éric JOLIDON
Daniel Moille
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Rolex SA
Original Assignee
Rolex SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Rolex SA filed Critical Rolex SA
Priority to EP20177619.2A priority Critical patent/EP3916489A1/de
Priority to US17/327,965 priority patent/US12038723B2/en
Priority to JP2021086712A priority patent/JP2021192032A/ja
Priority to CN202110592507.0A priority patent/CN113791530A/zh
Publication of EP3916489A1 publication Critical patent/EP3916489A1/de
Pending legal-status Critical Current

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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B31/00—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor
    • G04B31/02—Shock-damping bearings
    • G04B31/04—Shock-damping bearings with jewel hole and cap jewel
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B31/00—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor
    • G04B31/02—Shock-damping bearings

Definitions

  • the invention relates to a shock absorber 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 damper spring and / or such a bearing body.
  • the invention also relates to a watch mechanism comprising such a damper spring and / or such a bearing and / or such a bearing body.
  • the invention also relates to a watch movement comprising such a damper spring and / or such a bearing body and / or such a bearing and / or such a mechanism.
  • the invention also relates to a timepiece comprising such a damper spring and / or such a bearing body and / or such a bearing and / or such a mechanism and / or such a watch movement.
  • shock-absorbing bearing solutions for a timepiece in particular those provided for pivoting a balance axis.
  • These bearings usually include a bearing body, a drilled bearing stone, a counter-pivot, a ring for positioning the stone and the counter-pivot within the bearing body, as well as a spring arranged at the interface of the bearing. bearing body and the counter-pivot, so as to damp the movement of the axis in the event of an impact that the timepiece would be liable to undergo, and to return the axis to its initial position after the impact.
  • the spring of the damper bearing may for example have a closed loop conformation. It then comprises bearing portions, in contact against the counter-pivot, projecting inwardly of the spring, as well as attachment portions projecting outwardly of the spring, so that the latter can fit into an internal groove of the bearing housing.
  • the documents CH705583 , EP3011396 , EP3220211 disclose different variant embodiments of such a closed loop spring.
  • the spring of the damper bearing may have an open configuration.
  • the spring has fasteners in the form of tabs arranged at its ends, projecting outwardly from said spring.
  • the documents EP1705537 , CH708733 , EP3070544 disclose different variant embodiments of such an open loop spring.
  • the aim of the invention is to provide a shock absorber spring and / or a bearing body and / or a bearing making it possible to improve the devices known from the prior art.
  • the invention proposes a shock absorber spring and / or a bearing body and / or a bearing making it possible to minimize the stiffness of the spring, and to make the force applied to the counter-pivot as constant as possible, so as to so as to adapt the mechanical response of the damper bearing to the admissible stresses on the axis and more particularly on its pivots, in particular in the case of figure where the materials are required to be modified and / or the conventional dimensions of the axis are brought to be minimized.
  • a shock absorber spring according to the invention is defined by claim 1.
  • a shock absorber bearing body according to the invention is defined by claim 6.
  • a bearing according to the invention is defined by claim 10.
  • a horological mechanism according to the invention is defined by claim 13.
  • a watch movement according to the invention is defined by claim 14.
  • a timepiece according to the invention is defined by claim 15.
  • the timepiece 200 is for example a watch, in particular a wristwatch.
  • the timepiece 200 comprises a timepiece movement 100.
  • the timepiece movement is intended to be mounted in a timepiece case in order to protect it from the external environment.
  • the watch movement 100 can be an electronic movement or a mechanical movement, in particular an automatic movement.
  • the watch movement includes a 90 watch mechanism.
  • the clockwork mechanism comprises a clockwork bearing 10.
  • the clockwork mechanism comprises two clockwork bearings 10 intended to guide an element 6 at its two ends.
  • the mechanism is for example a horological oscillator and comprises for example a balance and a spiral spring.
  • the mechanism is, for example, an oscillator in the form of a monolithic structure, namely an element of inertia formed integrally with one or more elastic return members.
  • the bearing is particularly suitable for the pivoting of an axis, in particular of an axis pivot, made of ceramic or glass. This axis is for example an axis 6 of the balance.
  • the watchmaking bearing 10 includes a damper.
  • the watchmaking bearing 10 is therefore a damping bearing or an elastic bearing.
  • the bearing makes it possible, for example, to guide in rotation, around an axis A, the balance of an oscillator of the sprung balance type.
  • the bearing for example also makes it possible to stop in translation, along the axis A, the balance, in particular to limit the movements in translation along the axis A, of the balance.
  • the balance comprises an axis or shaft, in particular an axis 6 of the balance.
  • the bearing body 2, in particular the opening 20, generally has a geometry of revolution about an axis A2.
  • the ring 5 also has a geometry of revolution about an axis A5.
  • the ring 5 comprises frustoconical or inclined surfaces 53, 54 stepped along the axis A5, which are provided to cooperate respectively with frustoconical or inclined surfaces 23, 24 stepped within the opening 20 of the bearing. , so as to center the ring 5 in the bearing body 2. This is a so-called “double cone” construction.
  • the ring 5 comprises a through opening 50 provided so as to receive the elements 3 and 4. More particularly, the opening 50 comprises a surface 55 of revolution of axis A5, which is provided to receive the pivot element 3, thus a surface 56 perpendicular to the axis A5, which is provided to receive the counter-pivot element 4.
  • the pivot element 3 is in particular driven against the surface 55.
  • the counter-element pivot 4 is arranged with less clearance against a bearing surface formed by the surface 56.
  • the opening 50 further comprises a portion 57 provided for the passage of the pin 6. The same is true of the opening 20 of the bearing body 2, which also comprises a portion 26 for passing through the pin 6.
  • the axis A3 of the pivot element 3 coincides or substantially coincides with the axis A5 of the ring 5.
  • the pivot element 3 could very well be manufactured in one piece with the ring 5, so as to minimize the number of assemblies within the bearing 10 and to reduce the chains of dimensions and tolerances.
  • the ring 5 could be guided differently within the bearing body 2.
  • the shock absorber could be “inverted double cone”, as in the example described in the document FR1532798 .
  • the damper bearing 10 is designed to be assembled on a blank 99 of the movement 100.
  • the body 2 comprises a portion 25 intended to be driven into the blank 99 of the movement 100.
  • This blank can be a bridge, in particular a balance bridge, or a plate.
  • the function of the spring 1 is to return the elements 2, 3, 4 and 5 to their relative positions shown on the figure 1 .
  • the balance, in particular the axis 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 displacements of the axis 6, as well as the elastic return of the spring 1 involve displacements of the elements 3 and / or 4 and / or 5 relative to the body 2.
  • the spring allows the elements to be returned to their positions once the impact has passed.
  • the shock absorber spring 1 preferably extends substantially along 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 elements 11, 11 ', 11 "for fixing said spring.
  • These first fixing elements each comprise at least one first fixing surface 11a, 11b, 11a', 11b ', 11a", 11b "oriented at least substantially radially relative to the first axis and towards the first axis.
  • the vectors n11 normal to the first fixing surfaces 11a, 11b, 11a ', 11b', 11a ", 11b” extend substantially radially relative to the first axis A1
  • the normal vectors n11 can form an angle with the plane P1, in particular an angle less than 20 °, when the spring is mounted on the bearing body.
  • the first fixing surfaces can extend perpendicularly or substantially perpendicularly to the plane P1 when the spring is in its free state, that is to say in a non-prestressed state as shown in Figure. figure 4 .
  • the first surfaces can extend perpendicularly or substantially perpendicularly to the plane P1 when the spring is in its stressed state, that is to say in a prestressed state where it is mounted on the bearing body.
  • the first fixing elements 11, 11 ', 11 "extend at least substantially orthoradially relative to the axis A1.
  • the connecting elements are distinguished from the fixing elements by a border formed by a cylindrical surface C1 tangent to the first fixing surfaces (the spring being in its free state or in its stressed state, mounted on the bearing body) .
  • the connecting elements are distinguished from the support elements by a border formed by a cylindrical surface C2 centered on the axis A1 or A2 or A3 and having the same diameter or substantially the same diameter as the outside diameter of the counter-pivot member or having the same diameter or substantially the same diameter as the outside diameter of the pivot member.
  • the diameter of the cylindrical surface C2 may be less than the outside diameter of the counter-pivot element or the outside diameter of the pivot element. Such a conformation would make it possible to maximize the length of the connecting elements.
  • the function of the fixing elements is to fix the spring to the bearing body, and in particular to fix said fixing elements of the spring to the bearing body.
  • This fixing can in particular be obtained by relative friction between said fixing elements of the spring and the bearing body.
  • fixing we preferably mean a complete bond or a recess connection, namely a connection allowing no degree of freedom between the fixing elements of the spring and the fixing elements of the bearing body.
  • the function of the support elements is to exert on the counter-pivot element and / or on the pivot element a return force making it possible to return the counter-pivot element and / or the pivot element in a predefined position, in particular a predefined and optimum position for guiding the element 6.
  • the support elements are defined as the extents of the spring on which the counter-pivot element can come into contact while the The counter-pivot member is in its predefined position and / or while the counter-pivot member is in a position stressing the spring due to an impact.
  • the spring preferably has a main structure in the form of a closed loop on itself.
  • the spring may in particular have the form of a closed loop on itself. This closed loop is preferably centered on the axis A1.
  • the spring is thus for example formed by a single wire closed on itself.
  • the wire may have a cross section of constant or changing geometry throughout the length of the wire.
  • the loop may have a cut or an opening, that is to say that the wire forming the loop has two ends on either side of the cut.
  • the wire may in particular have a cross section of rectangular shape or of square shape.
  • loop is preferably understood to mean a wire-frame geometry without branching or bifurcation.
  • a wireframe geometry does not intersect the axis A1 and / or does not cross a border zone delimited by a cylindrical surface C3 centered on the axis A1, the diameter of the cylindrical surface C3 preferably being less than 0.8 times the diameter of the cylindrical surface C2, or even less than 0.6 times the diameter of the cylindrical surface C2.
  • the whole loop can be described by a curve B (shown in the figure 4 ) which can be described by a curvilinear abscissa, without a cusp.
  • any point of this curve B can traverse the whole of this same curve along one and the same course in a given direction, without cusp, from an origin point disposed on the curve.
  • this curve is continuous.
  • the length of such a curve B is greater than at least three times the diameter of the cylindrical surface C1, or even greater than at least four times the diameter of the cylindrical surface C1, or even greater than at least five times the diameter. of the cylindrical surface C1.
  • the spring is preferably made of steel, in particular of Durnico steel, or of Phytime or else of Phynox.
  • the spring can be made of an at least partially amorphous metal alloy.
  • the spring can be made of Nickel or else of a Nickel-Phosphorus alloy, in particular by a Liga type technology.
  • At least one portion 12a, 12e, 12a ', 12e', 12a ", 12e" of the at least two connecting elements extend at least substantially radially relative to the first axis A1.
  • At least one portion 12b, 12d, 12b ', 12d', 12b ", 12d" of the at least two connecting elements extend at least substantially orthoradially relative to the first axis A1.
  • the at least two support elements have a convex geometry seen from the inside of the spring, in particular from the first axis A1.
  • they each have angular extents around the axis A1 of between 45 ° and 90 ° (in particular when the spring exhibits rotational symmetry of order 3).
  • each support element has an angular extent around the axis A1 of between 270 ° / 2n and 270 ° / n.
  • the at least two support elements each have radial extents relative to the axis A1 of between 0.25 times and 0.75 times the outer radius of the counter-pivot element 4, the counter-pivot element on which said spring 1 is intended to support.
  • Each support element preferably consists mainly of a curved portion, in particular a portion of a circle 12c, 12c ', 12c ".
  • the circle portions 12b, 12b ', 12b ", 12d, 12d', 12d" are convex seen from the outside of the spring in the plane P1.
  • the at least two fixing elements extend at least substantially orthoradially relative to the first axis A1.
  • Each fastening element preferably consists mainly of a curved portion, in particular a portion of a circle. These portions are convex seen from the outside of the spring in the plane P1.
  • the distance D measured radially separating the first fixing surfaces and the bearing elements is greater than 0.2 times the radius of the cylindrical surface C1, or even greater than 0.3 times the radius of the cylinder C1.
  • the distance D measured radially separating the first fixing surfaces and the bearing elements 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.
  • the first fixing surfaces are substantially arranged on the cylindrical surface C1 having a diameter equal to at least 1.5 times or at least 1.7 times the outer diameter of the counter-pivot element 4, the counter-pivot element on which the spring is intended to support.
  • these dimensions are established for a spring which is not positioned or not mounted on a bearing body, that is to say for an unstressed or unstressed spring.
  • the first fixing elements each comprise at least one lobe 11c, 11c ', 11c ".
  • the first fixing surfaces are preferably produced on the lobes.
  • the lobes project towards the inside of the spring, that is to say that is, extend towards the interior of the spring
  • each first fixing element comprises two lobes.
  • the fixing elements 11, 11 ', 11 are evenly distributed around the axis A1 of the spring and are identical.
  • the support elements 12c, 12c', 12c" are evenly distributed around the axis A1 of the spring and are identical.
  • the connecting elements 12a, 12b, 12d, 12e, 12a ', 12b', 12d ', 12e', 12a ", 12b", 12d ", 12e” are evenly distributed around the axis A1 of the spring and are identical.
  • the bearing body 2 comprises a second axis of symmetry A2 and at least two second elements 21, 21 ', 21 "for fixing the spring 1.
  • These second fixing elements each comprise at least one second fixing surface 21c, 21c', 21c "oriented at least substantially radially relative to the second axis and in a direction opposite to the second axis A2.
  • the vectors n21 normal to the second fixing surfaces 21c, 21c ', 21c extendend substantially radially relative to the second axis A2 and exit from these fixing surfaces in a direction opposite to the second A2.
  • the fixing surfaces 21c, 21c ', 21c are oriented towards the outside of the bearing body 2.
  • the second fixing elements are arranged so as to cooperate with the first fixing elements to ensure the fixing of the spring on the bearing body.
  • the second fixing surfaces are arranged so as to cooperate with the first fixing surfaces to ensure the fixing of the spring on the bearing body.
  • the contact forces between the first and the second fixing surfaces have the same orientations or substantially the same orientations as those of the vectors n11 and n21, except for the coefficient of friction between the first and the second fixing surfaces.
  • the first fixing surface exerts a force against the second surface, which is oriented or oriented substantially along the vector n11.
  • a reaction force from the second surface to the first surface is for its part oriented or oriented substantially according to the vector n12.
  • the second fasteners are respectively provided with studs or teeth or crenellations 21, 21 ', 21 "extending mainly parallel to the axis A2. These studs protrude outwardly of the bearing body from a peripheral surface 27 of the bearing housing. bearing body, in a direction radial to the axis A2 of the bearing body.
  • n 3.
  • the second fixing elements 21, 21 ', 21 "are evenly distributed around the axis A2 of the bearing body 2, and are identical.
  • the studs 21, 21', 21" are separated by openings or voids. 22, 22 ', 22 "at the surface 27 of the bearing body.
  • Each stud 21, 21 ', 21 “comprises a second fixing surface 21c, 21c', 21c".
  • Each second fixing surface extends at the level of the peripheral surface 27 of the bearing body.
  • these second fixing surfaces 21c, 21c ', 21c are in the form of flats oriented radially relative to the axis A2 and extending orthoradially relative to the axis A2.
  • the lobes 11c, 11c ', 11c "bear respectively against the flats 21c, 21c', 21c".
  • the first fixing elements 11, 11 ', 11 "of the spring 1 are arranged and held on the outer periphery of the second fixing elements 21, 21', 21", in particular on the outer periphery of the second fixing surfaces 21c, 21c ', 21c ".
  • the first fasteners 11, 11 ', 11 "of the spring 1 are further from the axis A1 or A2 than are the second fasteners.
  • each stud comprises two half-studs 21a, 21b, 21a ', 21b', 21a ", 21b".
  • the half-studs of the same stud are separated from one another by a groove 21e, 21e ', 21e "extending at least substantially radially relative to the second axis A2.
  • each first fixing element 11, 11 ', 11 "of the spring 1 comprises a pair of lobes 11c, 11c', 11c" cooperating with a pair of half-studs 21a, 21b, 21a ', 21b', 21a ", 21b” of a second fixing element 21, 21 ', 21 "of the bearing body 2.
  • each half-stud 21a, 21b, 21a ', 21b', 21a ", 21b” comprises a bearing 210a, 210b, 210a ', 210b', 210a ", 210b", namely a surface extending perpendicularly or substantially perpendicular to the axis A2.
  • Such a conformation of the pads thus allows the axial retention of the pairs of lobes 11c, 11c ', 11c "of the spring.
  • the flats 21c, 21c ', 21c are formed at the level of the peripheral surface 27 of the bearing body 2, so that the first fixing elements 11, 11', 11" of the spring 1 (once placed on the bearing housing) “overhang” around the bearing housing 2.
  • the first fixing elements 11, 11 ', 11 "of the spring 1 are arranged and held at the outer periphery of the bearing body 2.
  • the bearing body 2 it is quite possible to shape the bearing body 2 so that it has a portion whose dimensions, in particular the diameter, make it possible to contain the entire spring 1, from a top view of the bearing. 10.
  • the connecting elements 12a, 12b, 12d, 12e, 12a ', 12b', 12d ', 12e', 12a ", 12b", 12d “, 12e” of the spring 1 are, for their part, intended to be housed respectively in the openings or voids 22, 22 ', 22 "of the bearing body 2 which are provided between the studs.
  • each of these connecting elements is in the form of two elastic strips 12a, 12b, 12d, 12e, 12a ', 12b', 12d ', 12e', 12a ", 12b", 12d ", 12e” comprising several substantially rectilinear and curved parts.
  • each elastic blade can include, at one and / or the other of its ends, curved parts 12b, 12d, 12b ', 12d', and 12b ", 12d" which make it possible to maximize the length. active of each of the blades.
  • the elastic leaves have a constant section.
  • the first fastening elements have substantially the same section as that of the elastic blades, with the notable exception of the zones within which the lobes extend.
  • the boundaries between the first fasteners and the connecting elements can be determined by the presence or absence of lobes.
  • the first fasteners may be devoid of lobes.
  • the first fastening elements may have substantially the same section as the connecting elements.
  • the lobes can be replaced by notches provided to cooperate with projections formed on each of the pads of the bearing body.
  • the support elements 12c, 12c ', 12c are in contact with the counter-pivot element 4 and apply an essentially axial return force to it, which is in particular determined by the level of preload of the spring 1, defined in particular by the general conformation of the spring and in particular by the conformations of the respective first and second fixing elements of the spring and of the bearing body. This is made possible by the mobility of the elements bearing and connecting elements facing the first fixing elements 11, 11 ', 11 ".
  • the conformation of the spring in particular of the leaves 12a, 12b, 12d, 12e, 12a ', 12b', 12d ', 12e', 12a ", 12b", 12d “, 12e” allows, by elastic deformation of the spring , a substantially rotational movement of the connecting elements and the bearing elements about an axis A12, A12 ', A12 "at least substantially orthoradial to the axes A1 and A2 and extending at the level of the interfaces between the fixing elements and the connecting elements.
  • These axes A12, A12 ', A12 are represented on the figure 3 .
  • the support elements 12c, 12c ', 12c are thus movable outside a plane passing through the first fixing elements 11, 11', 11".
  • each support element and each connecting element of the spring 1 is thus capable of providing an elastic return force against the elements. 3, 4, 5 within the bearing body 2, thanks to the mobility of the bearing elements and of the connecting elements facing the first fixing elements.
  • the active length of the elastic blades 12a, 12b, 12d, 12e, 12a ', 12b', 12d ', 12e', 12a ", 12b", 12d ", 12e” combined with the section of the elastic blades, make it possible to minimize the stiffness of the spring 1 with respect to the dimensions of the bearing body 2, and in particular the dimension or the diameter over which the second fixing surfaces 21c, 21c ', 21c "extend.
  • the resilient blades 12a, 12b, 12d, 12e, 12a ', 12b', 12d ', 12e', 12a ", 12b", 12d ", 12e” can include more curved parts so as to maximize their active length. .
  • the bearing body 2 advantageously comprises means for mounting the spring 1 within it. It comprises in particular a chamfer 28 at the level of each of the ends of the studs or half-studs so as to facilitate the passage of the first fixing elements under the spans. 210a, 210b, 210a ', 210b', 210a ", 210b" of each of the studs or half-studs.
  • the bearing body 2 advantageously comprises means 21d, 21d ', 21d "for handling the spring.
  • These means comprise countersinks 21d, 21d', 21d" allowing the passage of a tool provided for handling the spring at its first level. fixing elements, in particular between each of the lobes provided on the first fixing elements.
  • the assembly of the spring on the bearing body could be of the "bayonet" type. According to a first angular position of the spring relative to the bearing body, determined by the axis A1 or A2, the spring could be detached from the bearing body, while in a second angular position of the spring relative to the bearing body, determined by the axis A1 or A2, the spring could be secured to the bearing body.
  • the blades 12a, 12b, 12d, 12e, 12a ', 12b', 12d ', 12e', 12a ", 12b", 12d “, 12e” have a section whose height measured parallel to the axis A1 is greater than the width measured along a plane perpendicular to the axis A1.
  • the blades 12a, 12b, 12d, 12e, 12a ', 12b', 12d ', 12e', 12a ", 12b", 12d “, 12e” have a section whose height measured parallel to the axis A1 is more smaller than the width measured along a plane perpendicular to the axis A1.
  • the second fixing surfaces are substantially arranged on a cylindrical surface having a diameter of at least 1.5 times or at least 1.6 times or at least 1.8 times the outer diameter of a counter-pivot element 4, counter-element. pivot on which said spring 1 is intended to press.
  • the solutions described above make it possible to minimize the stiffness of the spring for in particular a given section and material of said spring.
  • the stiffness of the spring can be less than 4 N / mm or less than 3 N / mm.
  • a specific spring configuration comprises elastic portions in the form of leaves, the active lengths of which are maximized for a given dimension of the bearing body.
  • the blades have the particularity of extending both inside the bearing body and outside the bearing body. This is made possible by the fact that the leaves adjoin first fixing elements of the spring, which are arranged outside second fixing elements arranged, for example, on the outer periphery of the bearing body.
  • the first fixing elements of the spring extend at least substantially orthoradially relative to the axis of the spring or of the bearing body, outside of second fixing elements of the bearing body.
  • the solution relates to a spring comprising at least two elastic portions extending at least substantially radially relative to the axis of the spring or of the bearing body, which are formed right through in the continuity of first attachment portions. or attachment extending at least substantially orthoradially relative to the axis of the spring or of the bearing body and extending outside of second attachment or attachment portions of the shock absorber body.
  • Such a damper bearing solution has the advantage of having an optimized mechanical response for a given geometry and / or a given balance axle material.
  • the stiffness of such a spring can in particular be minimized and made as constant as possible whatever the displacement of the axis.
  • the assembly / disassembly of such a spring within the bearing body is particularly simple, which facilitates the assembly ranges and after-sales service operations of such a damping bearing.
  • orientation of a surface of a solid element is defined as being the orientation of a vector normal to this surface, the normal vector leaving the solid element at the level of this surface.
  • mounting surface is preferably meant a surface on which there is permanent spring-bearing body contact when the spring is mounted on the bearing body and as long as the spring is mounted on the bearing. bearing body. When the spring is removed, this contact is broken.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Springs (AREA)
EP20177619.2A 2020-05-29 2020-05-29 Dämpfungsfeder, lagerkörper und lager für uhr Pending EP3916489A1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP20177619.2A EP3916489A1 (de) 2020-05-29 2020-05-29 Dämpfungsfeder, lagerkörper und lager für uhr
US17/327,965 US12038723B2 (en) 2020-05-29 2021-05-24 Shock absorber spring, bearing body and bearing for timepiece
JP2021086712A JP2021192032A (ja) 2020-05-29 2021-05-24 時計用緩衝器ばね、軸受本体、及び軸受
CN202110592507.0A CN113791530A (zh) 2020-05-29 2021-05-28 用于钟表的避震弹簧、轴承主体和轴承

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20177619.2A EP3916489A1 (de) 2020-05-29 2020-05-29 Dämpfungsfeder, lagerkörper und lager für uhr

Publications (1)

Publication Number Publication Date
EP3916489A1 true EP3916489A1 (de) 2021-12-01

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20177619.2A Pending EP3916489A1 (de) 2020-05-29 2020-05-29 Dämpfungsfeder, lagerkörper und lager für uhr

Country Status (4)

Country Link
US (1) US12038723B2 (de)
EP (1) EP3916489A1 (de)
JP (1) JP2021192032A (de)
CN (1) CN113791530A (de)

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR909574A (fr) * 1943-11-03 1946-05-13 Dispositif pare-choc pour palier de mobile d'horlogerie
CH272618A (fr) * 1949-02-05 1950-12-31 Erismann Gerard Dispositif pare-chocs.
FR1532798A (fr) 1967-07-21 1968-07-12 Palier amortisseur de chocs pour mobile d'horlogerie
EP1705537A1 (de) 2005-03-23 2006-09-27 Rolex S.A. Stoßdämpfende Lagerung für Uhren
CH705583A2 (fr) 2011-10-14 2013-04-15 Seiko Instr Inc Palier amortisseur de chocs pour pièce d'horlogerie.
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EP3011396A2 (de) 2013-06-21 2016-04-27 ETA SA Manufacture Horlogère Suisse Stossdämpfungssystem mit sicherer montage
EP3070544A1 (de) 2015-03-20 2016-09-21 Manufacture et fabrique de montres et chronomètres Ulysse Nardin Le Locle SA Lager für eine uhr
EP3220211A1 (de) 2016-03-14 2017-09-20 ETA SA Manufacture Horlogère Suisse Stosssicherungssystem mit rotationssperre

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EP1705537A1 (de) 2005-03-23 2006-09-27 Rolex S.A. Stoßdämpfende Lagerung für Uhren
CH705583A2 (fr) 2011-10-14 2013-04-15 Seiko Instr Inc Palier amortisseur de chocs pour pièce d'horlogerie.
EP3011396A2 (de) 2013-06-21 2016-04-27 ETA SA Manufacture Horlogère Suisse Stossdämpfungssystem mit sicherer montage
CH708733A2 (fr) 2013-10-21 2015-04-30 Kif Parechoc Sa Dispositif antichoc.
EP3070544A1 (de) 2015-03-20 2016-09-21 Manufacture et fabrique de montres et chronomètres Ulysse Nardin Le Locle SA Lager für eine uhr
EP3220211A1 (de) 2016-03-14 2017-09-20 ETA SA Manufacture Horlogère Suisse Stosssicherungssystem mit rotationssperre

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US12038723B2 (en) 2024-07-16
CN113791530A (zh) 2021-12-14
JP2021192032A (ja) 2021-12-16

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