EP4224257A1 - Monolithische spiralfeder-spiralrolle-anordnung - Google Patents

Monolithische spiralfeder-spiralrolle-anordnung Download PDF

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Publication number
EP4224257A1
EP4224257A1 EP23173087.0A EP23173087A EP4224257A1 EP 4224257 A1 EP4224257 A1 EP 4224257A1 EP 23173087 A EP23173087 A EP 23173087A EP 4224257 A1 EP4224257 A1 EP 4224257A1
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EP
European Patent Office
Prior art keywords
ferrule
balance shaft
monolithic
assembly
parts
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
EP23173087.0A
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English (en)
French (fr)
Inventor
Jérôme Daout
Richard Bossart
Jean-Marc Bonard
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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
Publication of EP4224257A1 publication Critical patent/EP4224257A1/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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/32—Component parts or constructional details, e.g. collet, stud, virole or piton
    • G04B17/34—Component parts or constructional details, e.g. collet, stud, virole or piton for fastening the hairspring onto the balance
    • G04B17/345—Details of the spiral roll
    • 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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/14—Mainsprings; Bridles therefor
    • 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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/14—Mainsprings; Bridles therefor
    • G04B1/145—Composition and manufacture of the springs
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49579—Watch or clock making

Definitions

  • the invention relates to a ferrule.
  • the invention also relates to a monolithic single or double spiral spring assembly - unsplit ferrule, intended to be driven onto a balance shaft, in particular a monolithic assembly including a ferrule according to the invention.
  • the invention also relates to a monolithic spiral spring-shell assembly comprising at least two stages as well as to a method of manufacturing such an assembly.
  • One of the critical points for the use of a hairspring in a high-precision watch movement is the reliability of the attachments (embeddings) of the hairspring to the balance shaft and to the balance bridge.
  • the attachment of the hairspring to the balance shaft is generally done by a ferrule, which was originally a small split cylinder intended to be driven onto the balance shaft and pierced laterally to receive the end interior of the spiral spring itself.
  • micro-fabrication techniques such as DRIE processes for silicon, quartz and diamond or UV-Liga for Ni and NiP, open up possibilities in terms of the shapes and geometries used.
  • Silicon is a very interesting material for making watch hairsprings, and microfabrication techniques make it possible to make the ferrule monolithically and come from manufacture with the hairspring.
  • a potential problem is that silicon does not have a plastic deformation domain. The ferrule can thus quickly break if the stresses exceed the stress allowable maximum and/or the elastic limit of the material. It is thus necessary to take care to dimension the ferrule both to maintain the spiral spring on the axis of the balance during the operation of the oscillator (minimum tightening torque) and also to be able to assemble the ferrule with axes whose diameters present fluctuations and this, without breaking or undergoing plastic deformation if the diameter of the balance shaft remains within a given tolerance interval.
  • EP 1 826 634 offers on his figure 4 in connection with line 34 of column 3, a ferrule comprising elastic zones consisting of curved arms. This document does not indicate where the hairspring must be fixed.
  • EP 1 513 029 And EP 2 003 523 offer ferrules having a triangular opening.
  • the balance spring is fixed at a point of attachment (reference 3 in the figures of these documents) located at one of the vertices of the triangles.
  • the ferrule is made up of an external stiffening structure to which are attached flexible arms which deform to accommodate the balance shaft.
  • the object of the invention is to propose new shell geometries giving full satisfaction, that is to say making it possible to obtain the highest possible tightening torque on the balance shaft and a stress in the material the most possible low.
  • these ferrules must be as balanced as possible so as not to cause unbalance, which would degrade the chronometric properties of the hairspring.
  • the invention relates to a monolithic single or double spiral spring-shroud assembly, the latter possibly being split or not.
  • This assembly has the particularity of comprising at least two levels (or stages or parts), the spiral spring being located on a different level from that where the support surfaces of the ferrule for the balance shaft are located.
  • This feature is particularly advantageous because it makes it possible to best optimize the holding torque of the ferrule on the balance staff without having to increase its size in the plane of the hairspring.
  • this characteristic makes it possible to bring the point of attachment of the spiral spring closer to the axis of the balance wheel, without being limited by the periphery of the ferrule.
  • the invention also relates to a process for the manufacture of a monolithic spiral spring - ferrule, split or not, in which the balance spring is produced on a level different from that where the bearing surfaces of the ferrule are located for the balance shaft.
  • the invention applies both to assemblies with a single hairspring and to those with a double hairspring. However, it is for the latter that it is best suited.
  • double hairspring it is meant here a hairspring comprising two blades wound in the same direction, but with an offset of 180 degrees, as described in the application EP 2 151 722 A1 .
  • the respective inner ends of these blades are integral with the ferrule and their respective attachment points are arranged symmetrically on opposite sides of the periphery of the ferrule.
  • the "attachment point” or “embedding point” of the hairspring is generally well defined in the case of a hairspring assembled on a ferrule made of a material other than the hairspring.
  • the point of Embedment can be defined as the point where the local stiffness along the neutral fiber reaches a value which is 10x higher than the stiffness of the hairspring blade.
  • the minimum value of the local stiffness along the blade will be considered.
  • the local stiffness is equivalent to the bending stiffness, determined during the bending of the blade or the operation of the hairspring, over a portion of given length, for example 1 ⁇ m.
  • the corresponding embedding points 10,11 are indicated by way of example on the ferrule-spiral assemblies of the figures 21 and 22 . In the case of the figure 21 (which corresponds to the ferrule geometry of the figure 12 ), we see that the embedding point is located on the extension of the outer contour or periphery 32 of the ferrule.
  • the embedding point is located in the immediate vicinity of the balance shaft, closer to the central opening of the ferrule than is the contour 33 of the level of the ferrule which does not include the spiral.
  • the ferrules according to the invention are dimensioned both to hold the hairspring on the balance shaft during operation of the oscillator, and also to be able to be assembled with shafts whose diameter shows a certain dispersion (no breakage or plastic deformation on driving out for a shaft diameter within a given tolerance interval).
  • These shells normally have at least 2, and preferably 4, bearing surfaces for the balance shaft.
  • the precise shape of the connecting parts is not crucial, as long as they manage to deform elastically, in particular in bending, during the driving out of a balance shaft.
  • the receiving parts are therefore rigid or non-deformable parts and the connecting parts, deformable parts, in particular deformable in bending or flexible.
  • the flexibility of the latter comes from the fact that they are thinned with respect to the reception parts.
  • the deformable parts have sections with smaller areas than the non-deformable parts. This thinning is achieved, according to the invention, by providing the deformable parts less wide than the receiving parts.
  • width is meant here the thickness measured in the plane of the ferrule, in other words, the distance between the contour of the ferrule and the contour of its central opening (for example, the minimum width e or e' or the width halfway between the rigid receiving parts b or b' on the figures 12 and 13 ).
  • junctions between the receiving parts and the connecting parts are generally located substantially at the base of a support surface (see below, as well as at as examples, the figure 18 , or the figure 5 where they can be located each time on one side of the curved part 14).
  • it is sought to maximize the length of the connecting parts, therefore to maximize the angular sector that they occupy.
  • FIG. 4 represents the central part of an example of a monolithic double spiral spring/unsplit ferrule assembly according to the invention.
  • the shell 1, in particular the receiving parts 17,18 comprises two pairs of support points 2,3 and 4,5 located on substantially flat arms 6,7 and 8,9 which are not elastic and are placed two by two close to the attachment points 10,11 of the blades 12,13 of the double hairspring.
  • the non-elastic arms of the same pair protrude into the central opening of the ferrule and they form between them an angle ⁇ which is preferably less than 170 degrees, more preferably greater than 90 degrees and less than 170 degrees, and is here about 120 degrees.
  • Each arm 6,7,8 or 9 has a free end.
  • the V-shape of the pairs of rigid arms has the effect of better wedging the balance shaft than a single fulcrum would do.
  • the important thing is in fact that the ferrule-axle embedding is as rigid as possible, so that the points of contact between the ferrule and the balance shaft do not move under the effect of the torque developed by the balance spring during operation in motion, that is to say during oscillations of the balance-spring once the balance-spring assembly - ferrule has been driven out or assembled on the axis of a balance wheel.
  • the geometry with two reception parts facing each other (in particular at 180° from each other) and each comprising a pair of surfaces support can act as a vice held by the flexible connecting parts.
  • the connecting parts exert elastic return actions bringing the receiving parts towards each other and each in contact against the balance shaft.
  • a single point of support such as for example a flat, convex or concave contact surface with a radius of curvature greater than the radius which is provided for the axis of the balance.
  • the arms 6,7,8 and 9 and the corresponding support surfaces 2,3,4 and 5 are flat, that is to say that their radius of curvature on the side of the central opening 26 is infinite.
  • the support surfaces can also be convex, that is to say that their radius of curvature can be negative on the side of the central opening 26, or concave, that is to say that their radius of curvature can be positive on the side of the central opening 26.
  • the positive radius of curvature is strictly greater than 0.51 times the diameter d max of the largest circle that can be traced inside the contour of the central opening (when the ferrule n is not deformed, in particular when it is not mounted on the balance shaft), a circle which is also called an “inscribed circle” in the remainder of the description.
  • the positive radius of curvature is greater than 0.62 times the diameter d max , which makes it possible to define a single point of contact between the support part and the balance shaft.
  • a radius of curvature greater than 0.75 times, or even 1 time, the diameter d max of the inscribed circle is also suitable.
  • the shaft diameter is slightly greater than d max , for example included in a tolerance interval between 1.01 and 1.02 d max .
  • the shroud 1 has rotational symmetry of order 2, and has two axes of symmetry in reflection, one being formed by the bisector of the angle ⁇ , the other being perpendicular to the latter and located at an equal distance from the intersection of the arms. It can be considered that it comprises two rigid balance shaft receiving parts connected by two flexible connecting parts, as can be seen in the figure 18 which will be detailed below.
  • the rigid parts 17 and 18 are those from which leave both the arms 6.7 and 8.9 and the blades 12 and 13 of the double hairspring.
  • the flexible parts 15 and 16 (in gray on the figure 18 ) are connecting parts symmetrically connecting the rigid parts, so as to form the shell 1 with its central opening.
  • the symmetry of the geometry of the ferrule of the figure 4 aims to obtain a balance so as not to create any imbalance.
  • the non-circular central opening of the ferrule may be defined as including a central recess 26 for receiving the balance shaft, substantially delimited by the 4 bearing surfaces 2,3,4 and 5, and two peripheral recesses 27,28 formed substantially and symmetrically between the arms 6,8, on the one hand and 7, 9 on the other hand, and the elastic parts 15 and 16.
  • the recesses 27 and 28 are symmetrical to each other with respect to the bisector of the angle ⁇ .
  • the geometry makes it possible to precisely define the support points, four in number in the case of the figure 4 .
  • the arms 6 to 9 make it possible to precisely define the bearing points of the ferrule on the balance shaft, while maximizing the length of the flexible elastic parts. On the other hand, these arms 6 to 9 do not flex or flex negligibly and cannot be considered as elastic arms.
  • the ferrule is thus formed of two rigid balance shaft reception parts 17,18 symbolized in black on the figure 18 , connected to each other by two flexible or elastic connecting parts 15,16, symbolized in gray on the figure 18 .
  • the advantage of this arrangement is to maximize the length of the flexible connecting parts, while guaranteeing a sufficient holding torque on the balance shaft, with a level of stress clearly lower than the maximum allowable stress for the material.
  • the simulations show that the shroud according to the invention makes it possible to obtain a holding torque (M) on the axis that is higher than with flexible arms located inside a closed contour (for the same size).
  • M holding torque
  • the flexible parts occupy about 70% of the total length of the outline.
  • the flexible parts occupy 50% or more of the total length of the outline, in particular between 50% and 90%, more preferably between 60 and 80%.
  • the angle sectors measured from the center of the ferrule (which corresponds to the center of the circle inscribed in the central opening) and occupied respectively by a rigid receiving part and by a flexible connecting part are approximately 54° and 126°.
  • the angle sector measured from the center of the shroud and occupied by a flexible connecting part is greater than or equal to 50°, in particular between 90° and 160°, more preferably between 110° and 145°.
  • This angle sector is for example defined as the smallest continuous angle sector between two reception parts where there is a zone where the stress in the material is greater than 50% of the maximum stress reached following the driving out of the axis.
  • the shell comprises only one pair of non-elastic arms 2.3.
  • a domed part 14 Opposite the V formed by the latter, on the other side of the non-circular central opening, is a domed part 14 intended to serve as a third support surface for the balance staff.
  • the geometry here comprises only a symmetry of reflection around the bisector of the angle ⁇ (if the point of attachment of the blades of the hairspring is not taken into account).
  • the shape and dimensions of the domed part 14 are chosen so as to balance the ferrule as much as possible.
  • the third bearing surface can also be flat or even concave, with a radius of curvature strictly greater than 0.51 times, preferably greater than 0.62, 0.75 or 1 time the inscribed diameter d max .
  • the ferrule according to the invention is particularly suitable for attaching a double hairspring to a balance staff. Indeed, most of the ferrules known from the state of the art do not deform symmetrically with respect to the attachment points. With a ferrule like the one shown on the figure 1 , one of the blades would be fixed at the same point as the blade of the simple hairspring represented, ie at the top of the triangle formed by the stiffening structure. The second blade must have an attachment point located 180° from the first, or opposite, in the middle of one side of the triangle. The displacement of the attachment points following the driving in with respect to the center of the hairspring and/or to the external attachments would therefore not be equivalent for the two attachment points, which would degrade the chronometric performance. In addition, the embedding point of the second blade would be liable to deform during the expansion and contraction of the hairspring, which would also adversely affect chronometric performance.
  • the invention relates to a shell having at least two levels or stages or parts.
  • the point of attachment or anchoring of the hairspring (or the points of attachment in the case of a double hairspring) is then located on a level different from that where the major part, or even all of the surfaces of the spring are located. support. This is particularly applied to a monolithic spiral spring-shell assembly.
  • the inventors have in fact discovered that it was possible to maximize the torque resistance of the ferrule, while minimizing its bulk, by lengthening the ferrule in the plane perpendicular to the hairspring. This makes it possible to separate the function of attaching the hairspring to the shaft via the ferrule (first level, in the plane of the hairspring) from that of holding the shaft, in particular holding the ferrule on the shaft (first and second level, and preferably exclusively on the second level, outside the plane of the hairspring), while distributing the elastic stress in the most balanced way possible along the flexible parts.
  • a monolithic spiral spring-shell assembly corresponding to that of the figure 4 built on 2 levels is represented in front and rear perspectives on the figures 9 and 10 .
  • the sides are not perfectly superimposed, they have a shift of a few microns between the first and the second layer.
  • FIG 11 represents the entire spring-spring assembly according to the figures 9 and 10 , with the outer ends of the blades of the double hairspring which are integral with a fixing element intended to be connected to the movement of a timepiece.
  • the ferrule or the spiral-ferrule assembly can be manufactured according to known methods, such as that forming the subject of patent application no. EP 1 655 642 .
  • the ferrule or the spiral spring-ferrule assembly according to the second aspect of the invention can be manufactured according to known methods, such as those forming the subject of patent applications no. EP 1 835 339 Or EP 2 104 007 .
  • the starting substrate used is a slice (“wafer” in English) of the “SOI” (“Silicon-on-Insulator”) type, composed of two parts of monocrystalline Si separated by a thin layer of silicon oxide, SiO 2 ( figure 8a , with monocrystalline Si in white and SiO 2 in oblique hatching).
  • SOI Silicon-on-Insulator
  • the wafer is oxidized to form a layer of SiO 2 on the surface on either side of the substrate ( figure 8b ) which will serve as a mask for deep etching by reactive ions (“Deep Reactive Ion Etching”, “DRIE” in English).
  • a photolithography is then carried out on a first face to define a first pattern in photoresist ( figure 8c , resin shown in hatched right) and this pattern is reproduced in the underlying oxide layer by dry etching ( figure 8d ).
  • photolithography is used to define a second pattern in photosensitive resin ( figure 8f ), which is reproduced in the underlying oxide layer by dry etching ( figure 8g ).
  • a deep DRIE etching step is then performed on the second side to etch the pattern in the second Si layer ( figure 8 o'clock ). Then, a deep DRIE etch is performed on the first layer ( figure 8i ).
  • the exposed parts of SiO 2 (outer layers and central layer) are finally dissolved by BHF attack (buffered HF, ie a mixture of HF and NH 4 F which serves as a buffer to stabilize the attack rate; figure 8d ).
  • the ferrule has at least two levels, and the point of attachment or embedding of the hairspring (or the points of attachment in the case of a double hairspring) is located on a level different from that where the support surfaces are located and at a distance from the center of the ferrule less than the distance between the center of the ferrule and its contour or periphery.
  • the shell 100 comprises a bore 101 intended to receive the balance shaft, as well as at least a first part 102 and a second part 103.
  • the first and second parts are separated by a plane 104 perpendicular to the axis 107 of the bore, this axis also representing the center of the ferrule.
  • the element(s) 105 for attaching the ferrule to a spiral spring are located exclusively on the first part.
  • the element 106 for connecting the ferrule to the balance shaft for example formed from bearing surfaces, is essentially, preferably exclusively, located on the second part.
  • an element connecting the ferrule to the balance shaft is essentially located on the second part”, it is meant that more than half of the forces connecting the ferrule to the balance staff are applied at the level of the second part.
  • the bore 101 forms a central opening intended to receive the balance shaft.
  • an SOI wafer is used to produce such a ferrule or a monolithic ferrule-hairspring assembly including such a ferrule, the first and the second part being made of silicon and separated by a layer of silicon oxide.
  • the use of SOI wafers where the internal layer of SiO 2 separating the two layers of Si is thick, even very thick (for example 2-3 microns as usual, but preferentially of thickness greater than 5, even than 10 microns) makes it possible to produce a flexible shell superimposing the turns as shown in the figure 19 , which shows such a monolithic double spiral spring assembly - ferrule made on 2 levels.
  • the flexible shell is in all respects similar to that of the figure 4 .
  • the attachment points of the hairspring are not located on the contour as on the figure 21 , but as close as possible to the central opening of the ferrule and therefore to the balance staff, as in the example of the figure 22 .
  • the blades of the hairspring are thus partially superimposed on the ferrule, over a little less than 180° in the example of the figure 19 (corresponding to a little less than half a winding turn of the hairspring blade).
  • the two-level manufacturing process makes it possible to produce this kind of structure, because the dissolution attack of the SiO 2 ( figure 8j ) will also attack the oxide which secures the blades to the shell if the attack time is sufficient, thus releasing the latter.
  • the attachment element of the hairspring to the ferrule or the embedding point 10, 11 is at a distance D1 of the axis of the bore 107 less than half the diameter D2 of a cylinder in which the second part fits, in particular at a distance D1 less than or equal to the average of half the diameter D2 and half the diameter of the inscribed circle dmax.
  • D1 is 0.330mm
  • D2 is 1.180mm
  • the embedding point is closer to the central opening than is the outline 33 of the ferrule.
  • a ferrule as described above can in particular be included in a monolithic spiral spring-ferrule assembly.
  • this type of approach is not limited to a double hairspring, but is also perfectly suitable for a single hairspring, and is not limited to a closed contour ferrule, but is also suitable for a split ferrule. Any combination of ferrule and hairspring can be obtained in this way, resulting in a balance spring-ferrule assembly with significantly improved chronometric properties.
  • the layer height of the hairspring (first part) is 150 microns and the layer height of the level bearing the support surfaces (second part) is 500 microns.
  • the balance shafts have a tolerated diameter of between 0.5 and 0.506 mm, with a nominal value of 0.503 mm.
  • the graph of the figure 14 shows the evolution of the simulated holding torque M of the ferrule as a function of the diameter of the balance shaft for each of the hairspring/ferrule assemblies of the figures 12, 13 And 3 , respectively.
  • the minimum holding torque is indicated on the figure 14 through the interrupted line.
  • the graph of the figure 15 shows the evolution of the stress s of the ferrule as a function of the diameter of the balance shaft for each of the hairspring/ferrule assemblies of the figures 12, 13 And 3 , respectively.
  • the maximum allowable stress for the material is indicated by the broken line.
  • the advantage of the ferrule of the figure 13 is that it is more flexible, that its level of stresses is lower and that the slope of the couple according to the diameter of the axis is weaker than for the ferrule of the figure 12 . As a corollary, the holding torque is lower.
  • the stress very quickly exceeds the maximum allowed value. It can therefore be seen that this type of ferrule is not suitable for assembly by driving in. In fact, such a geometry of the contour does not make it possible to ensure both good hold and deformation without breakage of the ferrule following the driving in of the balance shaft.
  • the inscribed diameter is only 0.2 micron less than the lower limit of the tolerance so that the stresses are lower than the maximum allowable stress for the lower limit of the tolerance, which requires extremely precise manufacturing tolerances.
  • This example illustrates the advantage of a closed-contour ferrule, with rigid receiving parts connected by flexible connecting parts.
  • This difference in stiffness can be estimated as a first approximation by the theory of beams with small deformations: for a beam, the stiffness k of an element of width e, thickness h and length L is proportional to e 3 ⁇ h/ L 3 .
  • a k r /k f ratio greater than 10, more preferably greater than 50, even more preferably greater than 100 is chosen.
  • the difference in width between the rigid receiving parts and the flexible connecting parts is preferable to obtain a lower rigidity on the connecting parts than on the receiving parts.
  • the average width of the connecting parts can be preferentially lower than the average width of the receiving parts, more preferably less by a factor of two than the average width of the receiving parts.
  • the two connecting parts have a minimum width and/or a width at mid-distance of the receiving parts that is less than the maximum width of the receiving parts.
  • the minimum width e of the connecting parts is then preferably less than 0.5 ⁇ a, even more preferably equal to or less than 0.3 ⁇ a, where a is the maximum width of the receiving parts.
  • the width in the middle of the connecting parts, halfway between the receiving parts is preferably less than 0.7 ⁇ a, even more preferably equal to or less than 0.5 ⁇ a.
  • the height is determined by the dimensions of the hairspring, among other things by the torque required and the size (diameter).
  • the height of the ferrule, and therefore of the arms carrying the bearing surfaces and flexible parts, will necessarily be fixed by the height of the hairspring and cannot be freely adjusted.
  • the holding torque values are lower by a ratio of 500/150 compared to a multilayer assembly equipped with a hairspring of the same height (150 microns), since the holding is performs on 150 microns instead of 500 microns. As a result, these holding torque values would be lower than the minimum value (broken line on fig. 14 ) required for shaft diameters close to the minimum tolerance (0.5 micron).
  • one way of increasing the holding torque of a single layer or stage ferrule is to increase the torque developed by the flexible parts without increasing the stress, which implies a larger diameter of the ferrule. This has the consequence that the point of attachment of the blades of the hairspring must be far from the balance axis, which degrades the chronometric properties.
  • a monolithic hairspring/ferrule assembly with at least two levels offers the possibility of maximizing the holding torque by optimizing its size, that is to say by avoiding increasing the diameter of the ferrule.
  • a shroud in which the second part 103 extends, along the axis of the bore 107, over a length greater than once the thickness E of the spiral spring, or even greater than 3 times the thickness E of the spiral spring, is therefore particularly suitable, in particular for forming a monolithic hairspring-shell assembly.
  • the monolithic 2-stage hairspring/ferrule assembly of the figure 7 has flexible parts that are not symmetrical.
  • Thermo-compensation of the hairspring of the single or double hairspring-shroud assembly is carried out by known means. It is for example possible to use a layer of material on the surface of the turns which compensates for the first thermal coefficient of the Young's modulus of the base material. In the case of an Si hairspring, a suitable material for the layer is SiO 2 .
  • each connecting part is mainly stressed in bending, once the monolithic assembly is mounted on the balance shaft.
  • mainly stressed in bending it is meant that, in each connecting part, one can identify a neutral fiber oriented substantially in a direction along which extends the connecting part and separating a zone stressed in tension, from a zone stressed in compression.
  • each connecting part has a portion remote from the balance shaft by at least 0.5 times the radius of the balance shaft, or even by at least 0.9 times the radius of the balance shaft, once the assembly is mounted on the balance shaft.
  • the receiving parts and the connecting parts form an element capable of continuously surrounding the balance shaft, that is to say capable of surrounding the shaft without topological interruption. of pendulum. They thus form a closed ferrule, as opposed to a split ferrule.
  • non-deformable part or “rigid part” means a part which does not deform or substantially does not deform during operation or during assembly of the monolithic assembly on the balance shaft or a part whose deformation is not desired and/or does not perform any function during operation or during assembly of the monolithic assembly.
  • deformable part means a part that deforms elastically during operation or during mounting of the monolithic assembly on the balance shaft or a part whose elastic deformation is sought or performs a function during operation or during assembly of the monolithic assembly.
EP23173087.0A 2011-09-29 2012-10-01 Monolithische spiralfeder-spiralrolle-anordnung Pending EP4224257A1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP11405332 2011-09-29
PCT/EP2012/069372 WO2013045706A2 (fr) 2011-09-29 2012-10-01 Ensemble monolithique ressort spiral-virole
EP12766973.7A EP2761380B1 (de) 2011-09-29 2012-10-01 Einteilige anordnung aus einer spiralfeder und spannzange

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EP12766973.7A Division EP2761380B1 (de) 2011-09-29 2012-10-01 Einteilige anordnung aus einer spiralfeder und spannzange

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EP4224257A1 true EP4224257A1 (de) 2023-08-09

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EP12766973.7A Active EP2761380B1 (de) 2011-09-29 2012-10-01 Einteilige anordnung aus einer spiralfeder und spannzange
EP23173087.0A Pending EP4224257A1 (de) 2011-09-29 2012-10-01 Monolithische spiralfeder-spiralrolle-anordnung

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EP12766973.7A Active EP2761380B1 (de) 2011-09-29 2012-10-01 Einteilige anordnung aus einer spiralfeder und spannzange

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US (1) US9411314B2 (de)
EP (2) EP2761380B1 (de)
JP (1) JP6301834B2 (de)
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WO2013045706A2 (fr) 2013-04-04
US9411314B2 (en) 2016-08-09
JP2014528572A (ja) 2014-10-27
WO2013045706A3 (fr) 2013-05-30
EP2761380B1 (de) 2023-05-31
CN103930837A (zh) 2014-07-16
JP6301834B2 (ja) 2018-03-28
EP2761380A2 (de) 2014-08-06
US20150023140A1 (en) 2015-01-22
CN103930837B (zh) 2017-05-03

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