• 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 object of the invention is to provide a balance-spiral of the thermocompensated type, a movement and a timepiece that are of high quality and better in terms of thermocompensation performance. A balance-spring balance (54) of the thermocompensated type comprises a main body (62) balance spring comprising a balance shaft (61) extending along a first axis (O1) and arranged to be rotated about the first axis (O1) by the power of a hairspring (63). The balance spring balance (54) of the thermocompensated type comprising an adjustment portion (100) extending along a second axis (O2), from a position where it is in rotation symmetry around the first axle (O1) of the main balance spring body (62), allowing a positional adjustment about the second axis (O2) and comprising a bimetal piece (121) obtained by stacking together in a direction crossing the second axis (O2), materials (130, 131) having different expansion coefficients.
    公开号:CH713409A2
    申请号:CH00103/18
    申请日:2018-01-30
    公开日:2018-07-31
    发明作者:Nakajima Masahiro；Kawauchiya Takuma；koda Masayuki；Fujieda Hisashi
    申请人:Seiko Instr Inc；
    IPC主号:
    专利说明:

    Description
    BACKGROUND OF THE INVENTION
    FIELD OF THE INVENTION [0001] The present invention relates to a spiral balance-spring of the thermocompensated type, a movement and a timepiece.
    PRIOR ART [0002] A balance-spring performing the function of a regulator in a mechanical timepiece comprises a rocker shaft extending along an axis, a rocker wheel fixed to the balance shaft, and a spiral. As the hairspring expands and contracts, the balance shaft and the balance wheel perform periodic reciprocating rotational movement (oscillation) about the axis.
    With the sprung balance described above, it is important that the oscillation period is set to a prescribed predetermined value. If the oscillation period is shifted with respect to the prescribed value, the mechanical timepiece (the quantity the timepiece advances and delays) is modified.
    The oscillation period T of the spring balance is expressed by the following equation (1). In equation 1, I is the "moment of inertia" of the sprung balance and K is the "stiffness" of the hairspring.
    (1) [0005] According to equation 1, when the moment of inertia I of the sprung balance and the stiffness K of the spring are modified due to a change in temperature or the like, the oscillation period of the balance- spiral is modified. Specifically, in some cases, the balance wheel described above is made of a material whose coefficient of expansion is positive (a material expands with an increase in temperature). In this case, when the temperature increases, the balance wheel sees its diameter increase and the moment of inertia I increases. On the other hand, in some cases, the hairspring is made of a material whose thermal coefficient of the Young's modulus is negative (for example a steel). In this case, when the temperature increases, the stiffness K decreases.
    Thus, when the temperature increases, the moment of inertia I increases and the stiffness K drops, which has the consequence that the oscillation period T is longer. As a result, the oscillation period T of the sprung balance is short at a low temperature, and long at a high temperature, so that the thermal characteristic of the timepiece increases at a low temperature and falls at a high temperature.
    As a measure to overcome the fact that the oscillation period T depends on the temperature, it may be possible to use a constant modulus material (for example the co-élinvar) as a constituent material of the spiral. By using a constant modulus material, it would be possible to suppress stiffness fluctuations K with temperature changes and suppress the influence of temperature on the oscillation period T. However, to suppress the fluctuations affecting the thermal coefficient Young's modulus, a strict production management is necessary and the production of the hairspring is difficult to perform.
    On the other hand, as a measure to overcome that the oscillation period T depends on the temperature, it could be possible to provide a bi-metal part in a rotational symmetry position of the balance wheel. The bimetal piece is formed by stacking together flattened elements having different expansion coefficients.
    In this constitution, when the temperature increases, the bimetal piece undergoes a deformation, for example radially inwards, because of the difference between the expansion coefficients of the flattened elements. As a result, the average diameter of the balance wheel is decreased, whereby it is possible to reduce the moment of inertia I. It follows that it is possible to correct the thermal characteristics of the moment of inertia I, which makes it possible to suppress the influence of the temperature on the oscillation period T.
    Furthermore, for example, United Kingdom Patent No. 256,953 (Patent Document 1) mentioned below discloses a constitution in which the effective length of each bi-metal part (the amount from which there is protrusion from of the balance wheel) is modified so as to make it possible to modify the amount of correction of the thermal coefficient (the quantity of which the bimetal part changes in the radial direction due to a change of temperature). In this constitution, it must be assumed that, by adjusting the effective length of each bimetal piece as a function of the thermal coefficient of the Young's modulus, it becomes easier to compensate for the variation of the thermal coefficient of the Young's modulus thanks to the thermal characteristic of the moment of inertia I.
    However, the constitution of the aforementioned patent document 1 has a problem which is that it is difficult to make the effective lengths of the bimetal parts equal. When the effective lengths of the bimetal parts differ from each other, the center of gravity of the sprung balance is offset with respect to the axis of rotation. As a result, there is generated a balancing error affecting the sprung balance, which results in a large fluctuation affecting the oscillation period T due to the behavior of the sprung balance (a so-called behavior is generated).
    In addition, in the case where a constant modulus material is used as a constituent material of the hairspring, there is the possibility that the temperature coefficient of the Young's modulus will fluctuate more or less depending on the manufacturing conditions with which is the manufacture of the spiral (for example the dissolution and heating process).
    However, in a sprung balance comprising a conventional bimetallic piece, the thermal coefficient of the moment of inertia I (the slope of the thermal coefficient) can be adjusted only in more or less.
    SUMMARY OF THE INVENTION
    The present invention has been made in view of the problems mentioned above. An object of the present invention is to provide a thermocompensated balance spring, a movement and a timepiece which are of a high quality and better in terms of the performance of thermocompensation.
    To achieve the above purpose, according to one aspect of the present invention, there is provided a sprung balance-spring of the thermocompensated type comprising: a main body balancer-balance comprising a balance shaft extending along a first axis and configured to be rotated about the first axis by the power of a hairspring; and an adjustment portion extending along a second axis from a location where it has rotation symmetry about the first axis of the balance sprung main body, which allows positional adjustment around the second axis and which comprises a bimetal piece obtained by stacking together, in a direction crossing the second axis, materials having different coefficients of expansion.
    According to this aspect, the bimetal piece undergoes deformation during a temperature change, whereby the average diameter of the balance sprung main body is modified. As a result, it is possible to correct the thermal characteristic of the moment of inertia.
    In particular, in the present aspect, the adjustment part allows a positional adjustment around the second axis, so that it is possible to change the orientation of the bimetal part as a function of the thermal coefficient of the module. Young of the spiral. As a result, the amount of correction of the thermal coefficient effected by the bi-metal part can be modified both in the direction of an increase and in the direction of a reduction, whereby it is possible to correct the thermal coefficient of the moment of rotation. inertia of the spiral balance both in the sense of an increase and in the sense of a reduction. This means that a variation in the thermal coefficient of the Young's modulus can be easily canceled by virtue of the thermal characteristic of the moment of inertia of the balance-spring. As a result, the period of oscillation of the sprung balance can be kept constant, which makes it possible to propose a better balance-spring with regard to the property of thermocompensation.
    In addition, in the present embodiment, even if the orientation of the bimetal piece is changed, the length, in the direction of the second axis, of the adjustment portion is maintained at a fixed value. Therefore, unlike the conventional case in which the effective length of the bimetal piece is changed, it is possible to avoid a shift of the center of gravity of the sprung balance at a predetermined temperature (ambient temperature for example of the order of 23 ° C). As a result, it is possible to avoid the occurrence of a balancing error and to reduce differences in behavior.
    In the embodiment above, the main sprung balance body may comprise the balance shaft and a balance wheel which comprises a serge surrounding the balance shaft from the outer side in a first radial direction. orthogonal to the first axis and which is mounted on the balance shaft, the adjustment part extending from the serge.
    According to the present aspect, the adjustment portion is provided on the serge of the balance wheel, so that it is possible to move the adjustment part away from the first axis in the first radial direction. As a result, it is possible to increase the amount of radial deformation of the adjustment portion (the difference, in the first radial direction, between the distance between the distal end of the adjustment portion and a predefined temperature and the first axis and the distance between the distal end of the adjustment portion after a temperature change and the first axis), thereby increasing the amount of correction of the thermal coefficient due to the bi-metal part.
    In the above aspect, the adjustment portion may be disposed on the inner side of the serge, in a plan view obtained by looking from the direction of the first axis, and extending along the a tangential direction to the serge.
    According to the present aspect, it is possible to obtain the amount of radial deformation resulting from a temperature change, while avoiding an increase in the size of the sprung balance caused by the addition of the adjustment part. .
    In the aspect above, the bimetal piece can be arranged at a different position of the serge in the direction of the first axis.
    In this aspect, during a deformation, in the first radial direction, of the adjustment part because of a temperature change, it is possible to avoid interference between the serge and the part of the This adjustment makes it possible to guarantee the amount of radial deformation of the adjustment part (the adjustment part can deform radially from the desired quantity without coming up against the serge).
    In this aspect, the adjustment portion may comprise a flyweight.
    According to the present aspect, it is possible to increase the mass of the adjustment part, so that it is possible to increase the amount of correction of the thermal coefficient due to the bimetal part.
    In the above aspect, a through hole extending through the balance sprung main body in the direction of the second axis can be formed in the balance sprung main body, while the adjustment portion may comprise a fastening portion which is at one end in the direction of the second axis relative to the bi-metal piece and which fits snugly with the through-hole, and a coupling portion to which is coupled a tool can be formed in the end surface of the fixing portion facing said end in the direction of the second axis.
    In the present aspect, it is possible to couple a tool to the coupling portion of the fastening portion, through the through hole. Therefore, it is possible to easily perform the positional adjustment of the adjustment portion around the second axis. Further, the angle of rotation of the adjustment portion is changed through the attachment portion, whereby, compared to the case where the rotation angle of the adjustment portion is changed through from the distal end (the bimetal part and the flyweight), it is possible to avoid a plastic deformation of the adjustment part during the positional adjustment of the adjustment part. Therefore, it is possible to prevent a change in gait from occurring at a predetermined temperature due to plastic deformation of the adjustment portion.
    In the aspect above, the adjustment portion can extend cantilever along the second axis.
    In this aspect, it is possible to guarantee the (desired) amount of radial deformation resulting from a temperature change and increase the amount of correction of the thermal coefficient due to the bimetal part.
    In the aspect above, the spiral can be made of a constant modulus material.
    According to the present aspect, it is possible to reduce the variation of the Young's modulus caused by a temperature change and to eliminate the dependence of the oscillation period on the temperature. Furthermore, in the present aspect, it is possible to correct the variation of the thermal coefficient of the Young's modulus by means of the angle of rotation of the adjustment part, so that the production of the hairspring and the control at the moment of spiral production are facilitated. Therefore, it is possible to improve the efficiency of the production of the hairspring and to realize a cost reduction.
    In the aspect above, the center of gravity of the adjustment portion can be on the second axis.
    According to the present aspect, the center of gravity of the adjustment part is on the second axis, so that when the position of the adjustment part is adjusted around the second axis, it is possible to to prevent the center of gravity of the adjustment portion from shifting the second axis due to the rotation angle of the adjustment portion. As a result, it is possible to avoid an offset of the center of gravity of the sprung balance depending on the angle of rotation of the adjustment part, so that it is possible to reliably reduce the difference. of behavior.
    A movement according to one aspect of the present invention may comprise a sprung balance of the thermocompensated type according to the aspect above.
    [0036] A timepiece according to one aspect of the present invention may comprise a movement according to the aspect above.
    According to the present aspect, it is proposed a balance-spiral of the thermocompensated type according to the present aspect, so that it is possible to propose a movement and a timepiece which are of high quality and which imply a low variation of walking.
    According to the present invention, it is possible to propose a spiral-balance of the thermocompensated type, a movement and a timepiece which are of high quality and which are better with regard to the thermocompensation performance.
    BRIEF DESCRIPTION OF THE DRAWINGS
    [0039]
    Fig. 1 is an external view of a timepiece according to a first embodiment.
    Fig. 2 is a plan view of a movement according to the first embodiment, as seen from the front side.
    Fig. 3 is a plan view of a sprung balance according to the first embodiment as seen from the front side.
    Fig. 4 is a side view of the sprung balance according to the first embodiment.
    Fig. 5 is a sectional view along the line V-V of FIG. 3.
    Fig. 6 is a sectional view along the line VI-VI of FIG. 3.
    Fig. 7 is a partial plan view of the sprung balance for illustrating the operation of an adjustment portion.
    Fig. 8 is an enlarged sectional view of the adjustment portion, this adjustment portion being in a reference position therein.
    Fig. 9 is an enlarged sectional view of the adjustment portion, this adjustment portion being rotated at an angle of 45 °.
    Fig. 10 is an enlarged sectional view of the adjustment portion, this adjustment portion being rotated at an angle of 90 °.
    Fig. 11 is an enlarged sectional view of the adjustment portion, this adjustment portion being rotated at an angle of -45 °.
    Fig. 12 is an enlarged sectional view of the adjustment portion, this adjustment portion being rotated at an angle of -90 °.
    Fig. 13 is a graph showing the relationship between the orientation of the bimetal piece and the amount of deformation of the bimetal piece when the angle of the adjustment portion is changed in the range of -90 degrees to +90.
    Fig. 14 is a graph showing the relationship between the angle at which the adjustment portion is rotated and the amount of radial change (R).
    Fig. 15 is a graph showing the relationship between temperature (° C) and gait due to a difference in the thermal coefficient of the Young's modulus of the hairspring.
    Fig. 16 is a perspective view of a sprung balance according to a second embodiment.
    Fig. 17 is a plan view of a sprung balance according to a variant, as seen from the front side.
    Fig. 18 is a sectional view corresponding to FIG. 6, and represents a variant.
    Fig. 19 is a partial view, in plan, of a sprung balance according to a variant.
    DESCRIPTION OF THE EMBODIMENTS
    In what follows, embodiments of the present invention will be described with reference to the drawings.
    First embodiment
    Timepiece [0041] FIG. 1 is an external view of a timepiece 1. In the following, to facilitate understanding of the drawings, timepiece components are omitted and, in some cases, timepiece components are represented in a simplified form.
    As shown in FIG. 1, in the timepiece 1 of the present embodiment, a movement 2, a dial 3, different indicator hands 4 to 6, etc. are incorporated in a timepiece box 7.
    The timepiece box 7 comprises a box main body 11, a box cover (not shown) and a lid cover 12. A ring 15 is provided at the 3 o'clock position (on the right side at 1) of the lateral surface of the main body of the box 11. The crown 15 is used to actuate the movement 2 from the outside of the main body of the box 11. The crown 15 is fixed to a winding stem 19 introduced into the main body of box 11.
    FIG. 2 is a plan view of the movement 2 as seen from the front side.
    As shown in FIG. 2, in the movement 2, several mobiles, etc., are rotatably supported by a main plate 21 forming the base plate of the movement 2. In the following description, the cover ice side 12 (the dial side 3) of the timepiece box 7 with respect to the main turntable 21 will be called the "back side" of the movement 2, while the box cover side (the opposite side to the dial side 3) will be called the "front side" of the movement 2. In addition, all the mobiles described below are provided so that the anteroposterior direction of the movement 2 is their axial direction.
    The aforementioned winding rod 19 is incorporated in the main plate 21. The winding rod 19 is used to correct the date and time. The winding stem 19 is rotatable on its axis and movable in the axial direction. The position of the winding stem 19 in the axial direction is determined by a switching device comprising a pull-rod 23, a rocker 24, a rocker spring 25 and a pull-rod 26.
    When the winding stem 19 is rotated, the winding pinion 31 rotates due to the rotation of a clutch wheel (not shown). Due to the rotation of the winding pinion 31, a crown wheel 32 and a bit 33 turn next and a barrel spring (not shown) housed in the movement barrel 34 is cocked.
    The movement barrel 34 is rotatably supported between the main plate 21 and the barrel bridge 35. A center mobile 41, a mobile 42 average and a movable second 43 are rotatably supported between the platen main 21 and the gear bridge 45.
    When the movement barrel 34 is rotated by the maintenance force of the mainspring, the center mobile 41, the average mobile 42 and the second mobile 43 turn next. The movement barrel 34, the center wheel 41, the middle wheel 42 and the second wheel 43 form the front wheel.
    The minute hand 5 (see Fig. 1) is mounted on the center wheel 41 of the aforementioned front wheel. The hour hand 4 is mounted on an hour wheel (not shown) rotating with the rotation of the center wheel 41. In addition, the second hand 6 (see Fig. 1) rotates according to the rotation of the wheel. mobile 43. An exhaust regulator 51 is mounted in the movement 2.
    The exhaust regulator 51 comprises an escapement mobile 52, an anchor 53 and a sprung balance 54 (sprung-balance of the thermocompensated type).
    The escapement mobile 52 is rotatably mounted between the main plate 21 and the gear wheel 45. The escapement wheel 52 rotates with the rotation of the second wheel 43.
    The anchor 53 is supported between the main plate 21 and an anchor bridge 55 so as to be able to perform an alternating rotation movement. The anchor 53 has a pair of vanes 56a and 56b. The vanes 56a and 56b are alternately engaged with the escapement wheel 52a of the escape wheel 52 due to the reciprocating movement of the anchor 53. When one of the two vanes 56a and 56b is engaged with the escape wheel 52a, the escapement mobile 52 temporarily stops rotating. When the two vanes 56a and 56b are at a distance from the escape wheel 52a, the escape wheel 52 rotates. These operations are repeated as a result, whereby the mobile 52 rotates intermittently. Due to the intermittent rotational movement of the escapement wheel 52, the aforementioned wheel (front wheel) operates intermittently, whereby the rotation of the front wheel is controlled.
    Spiral balance [0055] FIG. 3 is a plan view of a sprung balance 54 as seen from the front side. Fig. 4 is a side view of the sprung balance 54. As shown in FIGS. 3 and 4, the sprung balance 54 controls the escapement wheel 52 (it causes the escapement wheel 52 to escape at a fixed speed). ). The spring balance 54 comprises mainly a balance shaft 61, a balance wheel 62 and a balance spring 63.
    As shown in FIG. 4, the rocker shaft 61 is supported between the main plate 21 and a cock 65 so as to be rotatable on a first axis 01. In the following description, in some cases, the direction along the first axis 01 will be called the direction of the first axis, the direction orthogonal to the first axis 01 will be called the first radial direction and the direction around the first axis 01 will be called the first peripheral direction. In this case, the direction of the first axis coincides with the anteroposterior direction.
    The balance shaft 61 performs an alternating rotational movement according to a constant oscillation cycle, on the first axis 01, because of the power received from the spiral 63. The front end, in the direction of the first axis of the balance shaft 61 is supported by the cock 65, via a bearing (not shown). The rear end in the direction of the first axis of the balance shaft 61 is supported by a bearing (not shown) formed in the main plate 21.
    A double plate 67 is fitted on the rear end, in the direction of the first axis, of the balance shaft 61. The double plate 67 is shaped like a tube arranged coaxially with the first axis 01. A Tray pin 68 is provided on a portion, in the first peripheral direction, of the double plate 67. Repeatedly, the plate pin 68 is engaged with and disengaged from the fork of the anchor 53, in a manner synchronized with the reciprocating movement of the sprung balance 54. As a result, the anchor 53 performs an alternating rotational movement, whereby the vanes 56a and 56b are repeatedly engaged with and disengaged from the escapement wheel 52.
    FIG. 5 is a sectional view along the line V-V of FIG. 3.
    As shown in Figures 3 and 5, the balance wheel 52 is fixed to the balance shaft 61, on the front of the double plate 67 in the direction of the first axis. The balance wheel 62 essentially comprises a hub 71, spokes 72 and a serge 73. In the present embodiment, the hub 71, the spokes 72 and the serge 73 are in one piece and are made of a metal (for example brass ).
    The hub 71 is fixed to the balance shaft 61 by driving or the like.
    The radius 72 protrudes outwardly in the first radial direction, from the hub 71. In the present embodiment, the spokes 72 project in the first radial direction, from opposite positions with, between them, the first axis 01 of the hub 71. The protruding positions, the number, etc. however, rays 72 may be modified as needed.
    The serge 73 has an annular shape and is disposed coaxially with the first axis 01. The serge 73 surrounds the hub 71, on the outer side in the first radial direction. On the outer side in the first radial direction, one end of the spoke 72 is connected to the inner peripheral surface of the serge 73.
    The hairspring 63 is a flat hairspring, extending in a spiral in a plan view obtained by looking from the direction of the first axis. The hairspring 63 is wound so as to extend in an Archimedean spiral. The inner end of the hairspring 63 is connected to the balance shaft 61 via a collar 75. The outer end of the hairspring 63 is connected to the cock 65 via a pin (not shown). . The hairspring 63 serves to store the transmitted power of the second wheel 43 to the escape wheel 52, and to transmit it to the balance shaft 61.
    In the present embodiment, a constant modulus material (for example co-élinvar) is suitably used for the spiral 63. The thermal characteristic of the spiral 63 is such that it has a positive Young's modulus on the temperature range of use. In this case, the thermal coefficient of the Young's modulus of the hairspring 63 is adjusted so that the oscillation period of the hairspring 54 is as fixed as possible with respect to the thermal characteristic of the moment of inertia of the hairspring. balance 62 accompanying a change of temperature. However, the hairspring 63 may be made of a material other than a constant modulus material. In this case, as a constituent material of the spiral 63, it is possible to use a general steel whose Young's modulus has a negative thermal coefficient (behavior in which the stiffness decreases during a temperature increase).
    Here, the sprung balance 54 of the present embodiment comprises two adjustment parts 100 placed in positions having a symmetry of rotation (rotation invariance of these positions) around the first axis 01 of the balance wheel 62 (2nd order symmetry in the present embodiment).
    Here, the rotation symmetry expression is an example of an expression for characterizing a figure and it is a well-known concept. More precisely, n being an integer equal to or greater than 2, the property of a figure which is superimposed on itself (invariant figure by rotation) when it is applied a rotation of 360 / n degrees around a certain center (in the case of a two-dimensional figure) or around an axis (in the case of a three-dimensional figure) is called n-symmetry or a symmetry of 360 / n degrees. For example, when n = 2, a 180-degree rotation of the figure results in it being superimposed on itself (it is unchanged), that is, there is order symmetry 2. Each adjustment portion 100 has the shape of a bar extending along the second axis 02 parallel to the tangent to the serge 73. The adjustment portions 100 are individually supported by a pair of support portions 110 provided The adjustment portions 100 have a similar construction and so are the support portions 110, so that the description which follows will focus on a single adjustment portion 100 and on a single support portion 110. In addition, in the following description, the direction along the second axis 02 will sometimes be called the direction of the second axis, and the direction orthogonal to the second axis will be called the second radial direction, while the direction around the second axis 02 will be called the second peripheral direction.
    FIG. 6 is a sectional view along the line VI-VI of FIG. 3.
    The support portion 110 forms an inward bulge, in the first radial direction, from the inner peripheral surface of the serge 73. A mounting hole 115 (through hole) is formed in the support portion. 110. It extends through the support portion 110 in the direction of the second axis. The mounting hole 115 has a round (circular) shape in a front view obtained by looking from the direction of the second axis. The shape of the mounting hole 115 is not limited to the round shape. It can also be a rectangular shape, a triangular shape, etc.
    A slot 116 communicating with the inside of the mounting hole 115 is formed in a portion of the support portion, namely in its part located on the rear side in the direction of the first axis. The slot 116 is formed in the support portion 110 from one end to the other thereof in the direction of the second axis.
    As shown in FIG. 4, an intervention hole 117 (through hole) extending through the serge 73 in the direction of the second axis is formed in the serge 73, where it passes in front of the mounting hole 115. intervention 117 allows the insertion of a tool (not shown) (for example a flat-end maneuvering tool).
    As shown in FIG. 3, the adjustment portion 100 is supported cantilevered by the support portion 110, on the inner side of the serge 73. Specifically, the adjustment portion 100 has a fixing portion 120, a piece bimetal (bimaterial) 121 and a flyweight 122, which are formed continuously from the proximal end (attachment end) to the distal end (free end) in the direction of the second axis.
    As shown lafig. 6, the fixing portion 120 is made, for example, of metal. In order to correspond to the aforementioned mounting hole 115, the fixing portion 120 is circular in a front view obtained by looking from the direction of the second axis. The fixing portion 120 is driven into the above-mentioned mounting hole 115 (which elastically retains it). The fixing portion 120 may be driven away so as to straddle the mounting hole 115 and the intervention hole 117.
    In the present embodiment, the degree of adjustment between the attachment portion 120 and the mounting hole 115 is chosen so that the adjustment portion 100 can be rotated about the second axis 02 when a pair predetermined, about the second axis 02 (second peripheral direction) is applied to the adjustment portion 100. In other words, the adjustment portion 100 of the present embodiment rotates about the second axis 02, the outer peripheral surface of the fixing portion 120 sliding on the inner peripheral surface of the mounting hole 115, whereby the position of the adjusting portion 100 about the second axis 02 can be adjusted.
    The shape of the cross section of the fastening portion 120 is not limited to the round shape. It can also be a rectangular shape, a triangular shape, etc. Further, while in the present embodiment as described above, the shape of the cross-section of the fastening portion 120 corresponds to the mounting hole 115, the fastening portion 120 and the mounting hole 115 may have different shapes since the fixing portion 120 can be rotated on the second axis 02.
    As shown in FIG. 4, a coupling portion 135 is formed on the proximal end surface, in the direction of the second axis, of the attachment portion 120. The coupling portion 135 is a groove extending linearly in the second radial direction . A tool is inserted into the coupling portion through the intervention hole 117. The coupling portion 135 is not limited to a groove since it can be coupled to a tool.
    As shown in FIG. 3, the bimetal piece 121 is bonded (for example welded or glued) to the distal end surface, in the direction of the second axis, of the fixing portion 120. The bimetal piece 121 has the shape of a plate extending linearly in the direction of the second axis, on the inner side, in the first radial direction, of the serge 73. The bimetal piece 121 is formed by stacking (mating) together, in the second radial direction, two flattened elements which differ by their coefficient of expansion (a low expansion element 130 and a high expansion element 131). In the present embodiment, invar (Ni-Fe alloy), silicon, ceramics or the like can be suitably employed as the material of the low expansion element 130. Copper, a copper alloy, the aluminum or the like may suitably be used as the material for the high expansion element 131. The low expansion element 130 and the high expansion element 131 have a similar shape (a rectangular shape in orthogonal cross-section at the second axis 02). In the example shown, the boundary zone between the low expansion element 130 and the high expansion element 131 is at the second axis 02. It is desirable that the center of gravity of each adjustment portion 100 be located at the second axis 02. Thus, the thickness of the low expansion element 130 and the thickness of the high expansion element 131 may be different from each other (the thickness may be changed as needed). In the case where the thickness of the low expansion element 130 and the thickness of the high expansion element 131 differ from each other, the boundary zone between the low expansion element 130 and the high expansion element 131 extends parallel to the second axis 02.
    The bimetal piece 121 (the element of small expansion 130 and the expansion element 131) allows a change of orientation in the second radial direction, since the adjustment portion 100 rotates about the second axis 02. The bimetal piece 121 can deform in the second radial direction during a change in temperature, which uses the difference between the expansion coefficient of the low expansion element 130 and the expansion coefficient of the high expansion element 131 The specific operation of the bimetal part 121 will be described later.
    As shown in FIG. 3, the flyweight 122 is bonded (for example welded or glued) to the distal end surface, in the direction of the second axis, of the bimetal piece 121. The flyweight 122 is made, for example, of metal. The cross section, perpendicular to the second axis 02, of the feeder 122 is of circular shape. In a front view obtained by looking from the direction of the second axis, the flyweight 122 has an outer shape larger than the bimetal part 121. The flyweight 122 can be mounted on the bimetal piece 121 so as to be removable. Temperature Correction Method [0080] A method for adjusting the amount of correction of the thermal coefficient will now be disclosed with respect to the sprung balance 54 described above. Fig. 7 is a partial plan view of the sprung balance 54 and serves to show the operation of the adjustment portion 100. In the state of FIG. 7, the low expansion element 130 and the high expansion element 131 are arranged side by side in the first radial direction, within the bimetal part 121, the low expansion element 130 on the inner side according to the first radial direction.
    As shown in FIG. 7, in the sprung balance 54 of the present embodiment, when a temperature change occurs, the bimetal piece 121 undergoes deformation, bending, due to the difference between the coefficient of expansion of the weak element. dilation 130 and the coefficient of expansion of the expansion element 131. More specifically, when the temperature increases from a predetermined temperature TO (ambient temperature, for example of the order of 23 ° C), the element of The high expansion 131 expands more than the low expansion element 130. As a result, the adjustment portion 100 is deformed to one side in the stacking direction of the low expansion element 130 and the element. high expansion 131 (the inner side in the first radial direction in Fig. 7). When the temperature decreases from the predetermined temperature TO, the high expansion element 131 contracts more than the low expansion element 130. As a result, the adjustment portion 100 undergoes deformation toward the other side according to the stacking direction (the outer side in the first radial direction in Fig. 7).
    Due to the deformation of the adjustment portion 100, the distance, in the first radial direction, between the distal end of the adjustment portion 100 and the first axis 01 is changed. More specifically, if RO is the distance, in the first radial direction, between the distal end of the adjustment portion 100 and the first axis 01 at the predetermined temperature TO and if R1 is the distance, in the first radial direction, between the distal end of the adjustment portion 100 and the first axis 01 after the temperature change, the difference between the distance RO and the distance R1 is the amount of radial change AR in the first radial direction. It is possible to increase or reduce the average diameter of the rocker wheel 62 in accordance with the amount of radial change AR, and to modify the moment of inertia, around the first axis 01, of the sprung balance 54. other words, in the case where the temperature increases, it is possible to reduce the average diameter of the balance wheel 62 to reduce the moment of inertia. In the case where the temperature has dropped, it is possible to increase the average diameter of the balance wheel 62 to increase the moment of inertia. As a result, it is possible to correct the thermal coefficient of the moment of inertia.
    In the case where, as in the present embodiment, a constant modulus material is used as a constituent material of the hairspring 63, there is the possibility that the thermal coefficient of the Young's modulus will fluctuate more or less in depending on the process conditions of the spiral production process (eg dissolution and heat treatment).
    In contrast, in the present embodiment, the orientation of the bimetal piece 121 (the rotation angle θ about the second axis 02) can be changed as a function of the thermal coefficient of the Young's modulus of the spiral 63 More specifically, a tool is coupled inside the coupling portion 135 constituting the adjustment portion 100 shown in FIG. 4, through the intervention hole 117. The tool is then rotated on the second axis 02, whereby the adjustment portion 100 rotates on the second axis 02, the outer peripheral surface of the fixing portion 120 sliding on the second axis 02. inner peripheral surface of the mounting hole 115. As a result, the rotation angle θ is changed. Figures 8 to 12 are enlarged views, in section, of the adjustment portion 100.
    In the state shown in FIG. 8, the low expansion element 130 is on the front side in the direction of the first axis, the low expansion element 130 and the high expansion element 131 being arranged side by side in the direction of the first axis. By using this state as the reference position (0 degree) of the adjustment part 100, the rotation angle θ about the second axis 02 is set. For example, in fig. 9, the adjustment portion 100 is rotated 45 degrees clockwise (+ direction) from the reference position about the second axis 02. In FIG. 10, the adjustment portion 100 is rotated 90 degrees clockwise (+ direction), from the reference position, about the second axis 02.
    In FIG. 11,1a adjustment portion 100 is rotated by -45 degrees counterclockwise (- direction) from the reference position, about the second axis 02. In FIG. 12, the adjusting portion 100 is rotated by -90 degrees counterclockwise (- direction) from the reference position about the second axis 02.
    FIG. 13 is a graph showing the relationship between the orientation of the bimetal part 121 and the amount of deformation of the bimetal part 121 when, at the same temperature (high temperature), the rotation angle θ of the adjustment part 100 is changed in the range of -90 degrees to +90. In fig. 13, the component in the first radial direction (hereinafter referred to as the X component) of the deformation vector of the bimetal piece 121 is on the abscissa. The component in the direction of the first axis (hereinafter referred to as the Y component) of the deformation vector of the bimetal piece 121 is on the ordinate. In this case, in FIG. 13, the -X direction corresponds to the inner side in the first radial direction, while the + X direction corresponds to the outer side in the first radial direction. In addition, in fig. 13, the bi-metal piece 121 at the origin represents the state at the predetermined temperature (TO) (before deformation).
    As shown in FIG. 13, when the adjustment portion 100 is at the reference position (0 degrees), the bimetal piece 121 only deforms toward the front side, in the direction of the first axis (A1 in Fig. 13). At the reference position, the Y component of the deformation vector of the bimetal piece 121 is therefore maximal and the X component of the deformation vector of the bimetal piece 121 is therefore 0. In this case, the amount of radial modification AR is 0, so that the thermal coefficient of the moment of inertia is not modified.
    When the adjustment portion 100 is rotated in the + direction from the reference position, the bimetal piece 121 also deforms towards the outer side in the first radial direction, so that the X component of the vector deformation of the bimetal piece 121 is produced (A2 and A3 in Fig. 13). By increasing the rotation angle θ in the + direction, the positive X component is gradually increased. This means that, by placing the rotation angle θ of the adjustment part 100 in the + direction from the reference position, it is possible to increase the amount of increase of the moment of inertia of the balance. -spiral 54 during a temperature increase. In addition, when the rotation angle θ is 90 degrees (A3 in Fig. 13), the bimetal piece 121 is deformed only to the outer side in the first radial direction. Therefore, in the case where the rotation angle θ is 90 degrees, the positive X component is maximum and the Y component is zero. In this way, by turning the adjustment part 100 in the + direction from the reference position, the thermal coefficient of the moment of inertia can be increased.
    On the other hand, when the adjustment portion 100 is rotated in one direction from the reference position, the bimetal piece is also deformed towards the inner side in the first radial direction, whereby the component Negative X of the deformation vector of the bimetal part 121 is produced (A4 and A5 in Fig. 13). By increasing the rotation angle in one direction, the negative X component increases. This means that, by locating the angle of rotation θ of the adjustment part 100 in one direction from the reference position, the increase in the moment of inertia of the sprung balance 54 can be suppressed. an increase in temperature. Further, in the case where the rotation angle θ is 90 degrees (A5 in Fig. 13), the bimetal piece 121 deforms only towards the inner side in the first radial direction. Therefore, in the case where the rotation angle θ is 90 degrees, the negative X component is maximum and the Y component is zero. In this way, by turning the adjustment portion 100 in the direction - from the reference position, the thermal coefficient of the moment of inertia can be reduced.
    FIG. 14 is a graph showing the relationship between the rotation angle θ of the adjustment portion 100 and the amount of radial change AR.
    As shown in FIG. 14, from the results of FIG. 13 described above, when the adjustment portion 100 is rotated in the + direction from the reference position, the amount of radial change AR increases in the + direction (to the outer side in the first radial direction). On the other hand, when the adjustment portion 100 is rotated in the direction - from the reference position, the amount of radial change AR of the adjustment portion 100 increases in the - direction (towards the inner side in the first radial direction).
    FIG. 15 is a graph showing the relationship between the temperature (° C) and the gait due to the difference in the thermal coefficient of the Young's modulus of the hairspring 63. In FIG. 15, the broken line G1 corresponds to the case where the step (the oscillation cycle of the sprung balance 54) has a negative thermal characteristic, and the dashed line G2 corresponds to the case where the step has a positive thermal characteristic.
    As G1 shows in FIG. 15, because of the relationship between the Young's modulus of the spiral 63 and the moment of inertia of the sprung balance 54, when the running has a negative thermal characteristic, the walking tends to delay when the temperature increases. In this case, the adjustment portion 100 is rotated in the direction - from the reference position. This makes it possible to obtain a quantity of radial change AR towards the inner side in the first radial direction during a temperature increase and to reduce the coefficient of the moment of inertia, so that it is possible to suppress an increase in the moment of inertia of the sprung balance 54 accompanying an increase in temperature. As a result, an adjustment is made so that the thermal coefficient of the oscillation period of the sprung balance 54 approaches 0, which makes it possible to maintain a constant step, independent of the temperature changes (see the continuous line) G3 in Fig. 15).
    On the other hand, as G2 shows in FIG. 15, because of the relationship between the Young's modulus of the spiral and the moment of inertia of the sprung balance 54, when the running has a positive thermal characteristic, walking tends to advance when the temperature increases. In this case, the adjustment portion 100 is rotated in the + direction from the reference position. This makes it possible to guarantee a quantity of radial change AR towards the outer side in the first radial direction accompanying an increase in temperature and to increase the coefficient of the moment of inertia, so that it is possible to increase the moment of inertia of the sprung balance 54 accompanying an increase in temperature. As a result, an adjustment is made so that the thermal coefficient of the oscillation period of the sprung balance 54 approaches 0, which makes it possible to maintain a constant step, independent of the temperature changes (see the continuous line) G3 in Fig. 15).
    In this way, the rotation angle θ of the adjustment portion 100 is modified according to the thermal characteristic of the step, whereby it is possible to correct the thermal coefficient of the moment of inertia of the balance- spiral 54 at the same time more and less. As a result, it is easier to suppress variations affecting the thermal coefficient of the Young's modulus, thanks to the thermal characteristic of the moment of inertia of the spring balance 54.
    In the present embodiment described above, the bimetal piece 121 is provided at a position having a symmetry of rotation, on the balance wheel 62.
    With this constitution, the bimetal piece 121 undergoes deformation during a temperature change, whereby the average diameter of the balance wheel 62 is changed. As a result, it is possible to correct the thermal characteristic of the moment of inertia.
    In particular, in the present embodiment, the position of the adjusting portion 100 about the second axis O2 can be adjusted. Therefore, it is possible to modify the orientation of the bimetal part 121 as a function of the thermal coefficient of the Young's modulus of the spiral 63. As a result, the amount of correction of the thermal coefficient of the bimetal part 121 can be changed to both in plus and minus and the thermal coefficient of the moment of inertia of the sprung balance 54 can be corrected both in addition and in less. This means that a variation affecting the thermal coefficient of the Young's modulus can be easily canceled by virtue of the thermal characteristic of the moment of inertia of the sprung balance 54. As a result, it is possible to keep constant the period of time. oscillation of the sprung balance 54, which makes it possible to propose a balance-spring balance 54 better with regard to the thermocompensation capacity.
    In addition, in the present embodiment, even if the orientation of the bimetal piece 121 is changed, the length, in the direction of the second axis 02, of the adjustment portion 100 is kept constant. Therefore, in contrast to the conventional case in which the effective length of the bimetal piece 121 is changed, it is possible to suppress that the center of gravity of the sprung balance 54 shifts to the predetermined temperature ΤΟ. As a result, it is possible to suppress the generation of a balancing error and to reduce the difference in behavior.
    In the present embodiment, the adjustment portion 100 is provided on the serge 73 of the balance wheel 62, so that it is possible to move the adjustment portion 100 away from the first axis 01, in the first radial direction. As a result, it is possible to increase the amount of radial change ÀR, which increases the amount of correction of the thermal coefficient due to the bimetal part 121.
    In the present embodiment, the adjustment portion 100 is disposed on the inner side in the first radial direction, relative to the serge 73, and extends along the tangent to the serge 73.
    In this constitution, it is possible to obtain the amount of change AR accompanying a change in temperature, while avoiding an increase in the size of the sprung balance 54 resulting from the addition of the adjustment portion 100.
    In the present embodiment, the adjustment portion 100 has the flyweight 122 at the distal end, so that it is possible to increase the weight of the distal end, which is the portion with the greatest deformation of the adjustment portion 100. Therefore, it is possible to increase the amount of correction of the thermal coefficient due to the bimetal part 121.
    In the present embodiment, the adjustment portion 100 extends cantilevered, so that it is possible to obtain the amount of a radial change AR resulting from a change of temperature and increase the amount of correction of the thermal coefficient due to the bimetal part 121.
    In the present embodiment, the intervention hole 117 is formed in the serge 73, so that it is possible to couple a tool to the coupling portion of the fixing portion 120, by the 117. Therefore, the position of the adjusting portion 100 about the second axis 02 can be easily adjusted. In addition, the rotation angle θ of the adjustment part 100 is modified via the fixing portion 120 so that, compared to the case where the rotation angle θ of the adjustment part 100 is modified through the distal end (the bimetal part 121 and the flyweight 122), it is possible to avoid a plastic deformation of the adjustment portion 100 during the positional adjustment of the adjustment portion 100. By therefore, it is possible to prevent a variation affecting the operation at the predetermined temperature TO is generated due to a plastic deformation of the adjustment portion 100. In the present embodiment, the spiral 63 is made of a constant modulus material.
    With this constitution, it is possible to reduce the change affecting the Young's modulus following a change in temperature in order to eliminate the oscillation period being dependent on the temperature. Furthermore, in the present embodiment, it is possible to correct the variations affecting the thermal coefficient of the Young's modulus, by a rotation angle θ of the adjustment part 100, so that the production and the organization at the moment of production of the hairspring 63 are facilitated. Thus, it is possible to obtain progress on the manufacturing efficiency of the hairspring 63 and to obtain a reduction in costs.
    In the present embodiment, the center of gravity of the adjustment portion 100 is on the second O2 so that when the position of the adjustment portion 100 about the second axis O2 is set, it is It is possible to prevent the center of gravity of the adjustment part 100 from being displaced away from the second axis 02 because of the rotation angle θ of the adjustment part 100. It is possible to prevent the center of gravity of the sprung balance 54 from shifting as a function of the rotation angle θ of the adjusting part 100, so that it is possible to reliably reduce a difference in behavior.
    The movement 2 and the timepiece 1 of the present embodiment are provided with the sprung balance 54 described above, so that it is possible to propose a movement 2 and a timepiece 1 having a high quality leading to slight variations in walking.
    Second Embodiment [0112] A second embodiment of the present invention will now be described. Fig. 16 is a perspective view of a sprung balance 201 according to the second embodiment. The present embodiment differs from the embodiment described above in that the support portion 202 projects in the direction of the first axis, from the serge 73. In the following description, the components which are the same as those of the mode embodiments described above are designated by the same reference numbers and a description thereof will be omitted.
    In the sprung balance 201 shown in FIG. 16, the support portions 202 are formed at positions of the serge 73 which exhibit rotational symmetry (which are invariant by rotation). Support portion 202 protrudes from serge 73 rearwardly in the direction of the first axis and extends inwardly in the first radial direction.
    In the portion of the support portion 202 that extends inwardly in the first radial direction relative to the serge 73, mounting holes 205 are formed extending through the support portion 202 in the direction of the second axis. The attachment portion 120 of the adjustment portion 100 is driven into a mounting hole 205.
    In this way, in the present embodiment, the serge 73 and the adjustment portion 100 are at different positions in the direction of the first axis. Therefore, during a deformation, in the first radial direction, of the adjustment portion 100 due to a change in temperature, it is possible to prevent interference between the serge 73 and the adjustment portion 100 and it is possible to obtain the amount of radial change AR of the adjustment portion 100.
    The technical scope of the present invention is not limited to that of the embodiments described above, but allows various modifications without departing from the scope of the present invention.
    For example, although in the embodiments described above, two adjustment portions 100 are provided at positions having rotational symmetry on the serge 73, this should not be interpreted restrictively. This means that, for example as shown in fig. 17, three adjustment portions 100 or more may be provided since the adjustment portions 100 are provided at positions having rotational symmetry, i.e. any order symmetry (these positions are invariant by rotation).
    While in the embodiments described above, the adjustment portion 100 rotates about the second axis 02, with the fact that the outer peripheral surface of the fixing portion 120 slides on the inner peripheral surface of the hole. 115, this should not be interpreted restrictively. This means that any other constitution will be suitable as soon as the position of the adjustment part 100 can be adjusted around the second axis 02. In this case, for example as shown in FIG. 18, a male spline 120a formed on the attachment portion 120 may be engaged with a female spline 115a formed in the mounting hole 115. With this constitution, the orientation of the bimetal piece 121 having been selected, the attachment portion 120 is fitly engaged in the mounting hole 115, whereby it is possible to adjust the position of the adjustment portion 100 about the second axis 02.
    After the positional adjustment of the adjustment portion 100, the adjustment portion 100 may be attached to the support portion 110 so that it can no longer be rotated. The fixing technique of the adjustment part 100 may be welding, gluing or the like, or it may be fixed by means of separate fasteners (for example a set screw).
    While in the embodiments described above, the attachment portion 120 is fitly engaged in the mounting hole 115, this should not be interpreted restrictively. The mounting technique of the adjustment portion 100 allows modifications as needed. For example, a protrusion formed on the serge 73 may be fitly engaged with a recess formed in the adjustment portion 100.
    While in the embodiments described above, the second axis 02 of the adjustment portion 100 extends along a tangent to the serge 73, this should not be interpreted restrictively. This means that any other constitution will be suitable as soon as the X component of the deformation vector of the adjustment part 100 is produced because of the deformation of the bimetal piece 121 following a change of temperature. In this case, the second axis 02 may, for example, be positioned in a direction crossing the direction of the first axis or in a direction parallel to the direction of the first axis.
    While in the embodiments described above, the adjustment portion 100 is carried by the serge 73, through the support portion 110, this should not be interpreted restrictively. This means that any other constitution will be suitable as soon as the adjustment part 100 is provided on the part (the balance sprung main body) of the sprung balance 54 rotated by the power of the spiral 63. in this case, examples of the main body of the balance spring comprise the balance shaft 61, the balance wheel 62 (the hub 71, the spokes 72, etc.), as well as the double plate 67.
    While in the embodiments described above, the low expansion element 130 and the high expansion element 131 are shaped like plates having the same shape, this should not be interpreted restrictively. For example, as shown in FIG. 19, the low expansion element 130 and the high expansion element 131 may have different thicknesses. In addition, the sections of the low expansion element 130 and the high expansion element 131 orthogonal to the second axis 02 have a shape that is not limited to the rectangular shape. This allows for modifications as needed and these sections may be triangular, semicircular or the like.
    While in the embodiments described above, the low expansion element 130 and the high expansion element 131 are stacked together in the second radial direction, this should not be interpreted restrictively. Any other constitution will be appropriate as soon as the elements are stacked together in a direction crossing the direction of the second axis. In this case, as shown for example in FIG. 19, the low expansion element 130 progressively widening towards the distal end and the high expansion element 131 gradually tapering towards the distal end can be stacked together.
    While in the embodiments described above, the adjustment portion 100 extends linearly, this should not be interpreted restrictively. The adjustment portion 100 may extend to intersect the
    权利要求:
    Claims (11)
    [1]
    direction of the second axis or can be formed according to a waveform since it allows a positional adjustment around the second axis 02. While, in the embodiments described above, the adjustment portion 100 s extends cantilevered, this should not be interpreted restrictively. It can also extend in the form of an eccentric. While, in the embodiments described above, the bimetal piece 121 extends over the entire area of the adjustment portion 100 between the support portion 110 and the counterweight 122, this should not be the case. be interpreted restrictively. Any other constitution may be suitable as soon as at least a part of the adjustment part 100 consists of the bimetal part 121. Furthermore, without departing from the scope of the present invention, the components of the Embodiments described above can be replaced by well-known components as needed. In addition, the modifications mentioned above can be combined with each other as needed. claims
    A sprung balance sprocket of the heat-compensated type, comprising: a sprung balance main body having a balance shaft extending along a first axis and configured to be rotated about the first axis by the power of a hairspring; and an adjustment portion extending along a second axis from a location where it has rotation symmetry about the first axis of the balance sprung main body, which allows positional adjustment about the second axis and which comprises a bimetal piece obtained by stacking together, in a direction crossing the second axis, materials having different coefficients of expansion.
    [2]
    2. sprung balance-spring of the heat-compensated type according to claim 1, wherein the main body balance-balance comprises: the balance shaft; and. a balance wheel which comprises a serge surrounding the balance shaft from the outer side in a first radial direction orthogonal to the first axis and which is mounted on the balance shaft; and the adjustment portion extends from the serge.
    [3]
    A thermocompensated balance sprung balance according to claim 2, wherein the adjustment portion is disposed on the inner side of the serge in a plan view obtained by looking from the direction of the first axis, the adjustment portion being extending along a direction tangential to the serge.
    [4]
    A thermocompensated type sprung balance according to claim 2 or claim 3, wherein the bimetal piece is disposed at a position different from the serge in the direction of the first axis.
    [5]
    5. Spiral balance spring of the thermocompensated type according to one of claims 1 to 4, wherein the adjustment portion comprises a feeder.
    [6]
    The thermocompensated spring-type balance spring according to one of claims 1 to 5, wherein a through-hole extending through the main body of the balance-spring in the direction of the second axis is formed in the balance main body. spiral; the adjustment portion has a fastening portion which is at one end in the direction of the second axis relative to the bimetal piece and which fits snugly with the through hole; and a coupling portion to which a tool is coupled is formed in the end surface of the fastening portion facing said end in the direction of the second axis.
    [7]
    7. Spiral spring balance of the thermocompensated type according to one of claims 1 to 6, wherein the adjustment portion extends cantilever along the second axis.
    [8]
    8. sprung balance springs of thermocompensated type according to one of claims 1 to 7, wherein the spiral is made of a constant modulus material.
    [9]
    9. sprung balance springs of thermocompensated type according to one of claims 1 to 8, wherein the center of gravity of the adjustment portion is on the second axis.
    [10]
    Movement, comprising a balance spring-balance of the thermocompensated type according to one of claims 1 to 9.
    [11]
    Timepiece, comprising a movement according to claim 10.
    类似技术:
    公开号 | 公开日 | 专利标题
    EP1612627B1|2009-05-06|Bi-material autocompensating hairspring
    EP2104006B1|2010-07-14|Single-body double spiral and method for manufacturing same
    EP2102717B1|2013-06-26|Mechanical oscillator for timepiece
    EP2407831A1|2012-01-18|Hairspring for oscillator balance of a clock piece and method for manufacturing same
    EP2196867A1|2010-06-16|Hairspring with curve elevation made from a silicon-based material
    EP2018601A2|2009-01-28|Spiral/collet assembly for a horological movement
    WO2011026725A1|2011-03-10|Spiral spring
    CH709052A2|2015-06-30|Spiral balance, movement and timepiece.
    EP2796940A2|2014-10-29|Clock component for receiving an organ by insertion
    CH707419B1|2018-12-28|Pendulum, movement of a timepiece, timepiece and method of manufacturing the pendulum.
    EP1654597B1|2009-11-11|Thermally-compensated balance wheel
    EP2917787B1|2020-08-19|Clock movement having a balance and a hairspring
    CH713409A2|2018-07-31|Spiral balance of the thermocompensated type, movement and timepiece.
    EP2753985B1|2017-03-01|Clock movement having a balance-wheel and hairspring
    CH710108A2|2016-03-15|Mechanism constant force, motion and timepiece.
    CH710603A2|2016-07-15|Clock spring spiral clock adjustable frequency.
    CH701155B1|2010-12-15|Balance spiral type mechanical oscillator for e.g. wrist watch, has balance and spiral, which are made of non-magnetic material such as diamond, where material possesses very low thermal expansion coefficient
    CH714857A2|2019-09-30|Thermocompensated balance spring, movement and timepiece.
    CH713702A2|2018-10-15|Torque compensation mechanism, constant force mechanism, timepiece movement and timepiece.
    CH715890A2|2020-08-31|Thermocompensation type sprung balance, movement and timepiece.
    EP3907563A1|2021-11-10|Timepiece mechanism comprising a pivot member
    EP3391154B1|2019-10-09|Oscillating system for timepiece
    EP3534222A1|2019-09-04|Method for producing a thermally compensated oscillator
    EP3792700A1|2021-03-17|Timepiece oscillator with flexible pivot
    CH715096A2|2019-12-30|Spiral, regulating organ, timepiece movement and timepiece.
    同族专利:
    公开号 | 公开日
    JP2018124114A|2018-08-09|
    JP6789140B2|2020-11-25|
    CN108375891B|2021-06-15|
    CN108375891A|2018-08-07|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2936572A|1957-08-12|1960-05-17|Hamilton Watch Co|Balance wheel for electric watch|
    CH511469A|1969-02-05|1971-02-26|Foerderung Forschung Gmbh|Mechanical resonator serving as a timer standard in electrical timing devices|
    JP2010230384A|2009-03-26|2010-10-14|Citizen Holdings Co Ltd|Speed governor of mechanical timepiece|
    CN202126574U|2011-06-22|2012-01-25|杭州手表有限公司|Timekeeping speed regulating mechanism of multi-hairspring watch|
    EP2613206A1|2012-01-05|2013-07-10|Montres Breguet SA|Hairspring with two spiral springs with improved isochronism|
    JP5840043B2|2012-03-22|2016-01-06|セイコーインスツル株式会社|Balance, watch movement, and watch|
    HK1178377A2|2012-07-17|2013-09-06|Master Dynamic Ltd|Hairspring design for concentricity|
    HK1186057A2|2013-01-14|2014-03-07|Master Dynamic Ltd|Stress-relief elastic structure of hairspring collet|
    CN104007650B|2013-02-25|2017-09-05|精工电子有限公司|Temperature compensating type escapement and its manufacture method, clock machine core, mechanical clock|
    CN103293938B|2013-05-31|2015-12-02|天王电子（深圳）有限公司|There is the escapement regulating inertia function and the stem-winder with this escapement|CN112859275B|2021-01-20|2021-12-14|中国科学院西安光学精密机械研究所|Cold optics self-adaptation thermal deformation compensation structure based on Archimedes spiral|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    JP2017015264A|JP6789140B2|2017-01-31|2017-01-31|Temperature-compensated balance, movement and watch|
    [返回顶部]