• 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:
    It is proposed a thermocompensated balance-spring balance, a movement and a timepiece for simply adjusting, with high precision, a quantity of thermal coefficient correction and having an excellent thermal compensation performance with a high quality. A thermocompensated balance-spring balance according to the present application comprises: a balance spring body which comprises a balance shaft (61) extending along a first axis (O1) and which rotates about the first axis (O1) by the power a hairspring (63); and an adjusting unit (100) which comprises at least two bimaterial pieces (121) which extend respectively along second axes (O2), from symmetrical positions by rotation about the first axis (O1) on the body of sprung balance. In each bimaterial part (26) materials (130, 131) having different thermal expansion coefficients are brought together in a direction intersecting the respective second axis (O2), as well as a counterweight portion (122) which is attached to the bimaterial part (121) so as to be displaceable in a second axial direction along the second axis (O2).
    公开号:CH714857A2
    申请号:CH00310/19
    申请日:2019-03-14
    公开日:2019-09-30
    发明作者:Nakajima Masahiro；Kawauchiya Takuma；Fujieda Hisashi；Ito Kengo
    申请人:Seiko Instr Inc；
    IPC主号:
    专利说明:

    The present invention relates to a thermocompensated balance spring, a movement and a timepiece.
    2. Description of the Related Prior Art A balance-spring which fulfills the function of a speed regulator of a mechanical timepiece comprises a balance shaft extending along an axis, a balance wheel attached to the balance shaft, as well as a hairspring. The balance shaft and balance wheel rotate in and out of the axis (oscillate) periodically, depending on the expansions and contractions of the balance spring.
    In the balance spring described above, it is considered important that the oscillation period is set to a specified predetermined value. If the oscillation period deviates from the specified value, the running of the mechanical timepiece (the degree of delay or advance of the timepiece) changes.
    The oscillation period T of the balance spring is given by equation (1) below. In equation (1), I is the "moment of inertia" of the balance spring and K is the "stiffness of the balance spring".
    E | equation (1) : [0005] On the basis of equation (1), if the moment of inertia I of the balance-spring and the stiffness K of the balance-spring change as a function of a change in temperature or the like, the oscillation period T of the balance spring changes. In particular, in some cases, the above-mentioned balance wheel is made of a material having a positive coefficient of expansion (a material which expands for an increase in temperature). In this case, if the temperature increases, the diameter of the balance wheel increases and the moment of inertia I increases. On the other hand, in some cases, the hairspring is made of a material (for example steel) having a Young's modulus with a negative thermal coefficient. In this case, if the temperature increases, the stiffness K decreases.
    For this reason, when the temperature increases, the moment of inertia I increases and the stiffness K decreases, so that the oscillation period T sees its duration increase. As a result, the oscillation period T of the balance spring becomes shorter at a low temperature and becomes longer at a high temperature, so that the thermal behavior (thermal characteristic) of the timepiece is to advance at low temperatures and delay at high temperatures.
    Here, as a corrective measure to improve the dependence of the oscillation period T on the temperature, it is conceivable to use a material of constant elasticity (for example Coelinvar or the like) as material constituting the hairspring. By using a constant elastic material, it is understood that the variation of the stiffness K as a function of a temperature change can be eliminated and that the dependence of the oscillation period T on the temperature can be eliminated. However, to suppress the variations of the thermal coefficient of the Young's modulus, there is a problem which is that a mastery of a precise manufacturing is required and that it is difficult to manufacture the balance spring.
    Furthermore, as a corrective measure to improve the dependence of the period of oscillation T on the temperature, a constitution in which the bimetal parts constituting the balance wheel are provided in symmetrical positions by rotation (invariance by rotation) is also possible (see, for example, document JP-B-43-26 014 (patent document 1)). The bimetal part is produced by stacking plate materials having different coefficients of expansion.
    With this constitution, when the temperature increases, the bimetal part is deformed, for example inwards in a radial direction, depending on the difference between the coefficients of expansion of the respective plate materials. Therefore, by reducing the average diameter of the balance wheel, the moment of inertia I can be reduced. As a result, it is conceivable that the thermal behavior (thermal characteristic) of the moment of inertia I can be corrected and that the dependence of the oscillation period T on the temperature can be eliminated.
    However, in the constitution described above proposed in patent document 1, in the case of an adjustment of the degree of correction of the thermal coefficient (the degree of deformation of the bimetal part in the radial direction, depending temperature change) by each of the bimetal pieces, it is necessary to attach a screw or the like separately to the bimetal piece and to detach that screw or the like from the bimetal piece. For this reason, it is complicated to adjust the degree of correction of the thermal coefficient and it is difficult to make an adjustment with high precision.
    CH 714 857 A2 In addition, for example, in the case where each of the bimetal parts is not produced to the desired shape due to a manufacturing fluctuation or the like, the degrees of thermal coefficient corrections by the bimetal parts tend to be variable. In the case where the degrees of the thermal coefficient corrections differ between the different bimetal parts, the center of gravity of the balance spring is offset relative to the axis of rotation. As a result, it is possible that the balance-spring has an unbalance and that the variation of the oscillation period T according to the orientation of the balance-spring becomes greater (commonly called the difference due to the orientation).
    SUMMARY OF THE INVENTION One aspect of the present application is to propose a thermocompensated balance-spring, a movement and a timepiece making it possible to simply adjust, with high precision, the importance of the correction of thermal coefficient and obtaining excellent performance in terms of thermal compensation, with high quality.
    One aspect of the present application is to provide a thermocompensated balance spring comprising: a balance spring body which comprises a balance shaft extending along a first axis and which rotates around the first axis by the power of 'a hairspring; and an adjustment unit which comprises bimaterial parts which extend respectively along second axes, from symmetrical positions by rotation around the first axis on the balance-spring body, and in which materials having coefficients of expansion different thermal are joined in a direction intersecting the second axis, as well as a weight forming part which is attached to the bimaterial part so as to be movable in a second axial direction along the second axis.
    According to the present aspect, because the bi-material part deforms as a function of a temperature change, an average diameter of the balance-spring body is changed. Therefore, it is possible to correct the thermal characteristic of the moment of inertia.
    In particular, in the present aspect, by adjusting the position of the counterweight part in the second axial direction relative to the bi-material part, it is possible to modify the position of the center of the counterweight part in the second direction axial. Therefore, it is possible to continuously adjust the thermal coefficient of the moment of inertia of the balance spring. Therefore, it is possible to adjust in a simple manner, with high precision, the degree of correction of the thermal coefficient, compared to the constitution of the prior art in which separate components such as screws and the like are attached and detached.
    In the aspect, the balance-spring body may include the balance shaft, and a balance wheel which includes a clamp surrounding the balance shaft from an outside in a first radial direction orthogonal to the first axis and which is attached to the balance shaft, the adjustment unit being able to extend from the clamp.
    According to the present aspect, as the adjustment unit equips the twill, it is possible to keep the adjustment unit at a distance from the first axis in the first radial direction. As a result, it becomes possible to increase the radius variation (the difference in distance between the distance from a tip end of the adjusting unit to the first axis at a predetermined temperature and the distance from the tip end of the adjustment unit at the first axis after a temperature change, in the first radial direction) of the adjustment unit and it is possible to increase the importance of the correction of thermal coefficient by the bimaterial part.
    In appearance, the counterweight part may include a fixed part which is fixed to the bi-material part, and a movable part which is attached to the fixed part, so as to be movable in the second axial direction.
    According to the present aspect, by moving only the displaceable part of the counterweight part relative to the fixed part and the bi-material part, the effective length is not modified (the length of the exposed segment of the bi-material part, in the 'adjustment unit) of the bimaterial part with a displacement of the movable part. In other words, since it is possible to modify only the position of the center of the counter-forming part (the quantity by which the bi-material part is deformed as a function of a temperature variation is not changed), it is possible to adjust in an even simpler way the importance of the correction of thermal coefficient.
    In appearance, the bimaterial part can extend in overhang from the balance-spring body, the part forming a counterweight being able to be attached to an end end of the bimaterial part.
    According to the present aspect, as the adjustment units extend in overhang, it is possible to guarantee the variation in radius as a function of the variation in temperature and it is possible to increase the quantity the thermal coefficient is corrected by the bi-material part.
    In addition, as the weight forming part is attached to the tip end of the bimaterial piece, it is possible to increase the mass of the tip end, which is the part of the adjustment unit. more distorted. For this reason, it is possible to increase the quantity whose thermal coefficient is corrected by the bi-material part. In addition, by attaching the counterweight portion to the tip end of the bimetal piece, it is possible to have one base end of the adjustment unit held securely in the balance-spring body. Therefore, it is possible to prevent the entire adjustment unit from jerking according to an adjustment of the counterweight portion and it is possible to adjust the amount of the thermal coefficient correction with even higher precision.
    CH 714 857 A2 In the aspect, the adjustment unit can be carried by the balance-spring body so as to have an adjustable orientation around the second axis.
    According to the present aspect, as the orientation of the adjustment unit around the second axis can be adjusted, it is possible to modify the orientation of the bimaterial part as a function of the thermal coefficient of the Young's modulus of the hairspring . Consequently, the degree of correction of the thermal coefficient by the bimaterial part can be modified to be both positive and negative, and the thermal coefficient of the moment of inertia of the balance-spring can be corrected so as to be both positive and negative. . In other words, it becomes easy to compensate for a change in the thermal coefficient of Young's modulus by a thermal characteristic of the moment of inertia of the balance-spring. In particular, as in the present aspect, by adjusting the moment of inertia of the balance-spring by the orientation of the bi-material part in addition to the position of the counterweight part, it is possible to adjust with higher precision l importance of thermal coefficient correction. As a result, the period of oscillation of the balance spring can be constant and that a balance spring having excellent thermal compensation can be proposed.
    In addition, in this aspect, even if the orientation of the bimaterial part is changed, the length of the adjustment unit in the second axial direction remains the same. For this reason, unlike in the case of a change in the effective length of the bimetal part that we have in the prior art, it is possible to prevent the center of gravity of the balance spring from being offset at temperature predetermined (normal temperature (for example around 23 ° C)). As a result, it is possible to avoid the appearance of an imbalance and to reduce the difference due to the orientation.
    In appearance, the hairspring can be made of a constant elastic material.
    According to the present aspect, it is possible to reduce the variation of the Young's modulus as a function of a temperature change and to remove a dependence of the period of oscillation on the temperature. Furthermore, in the present aspect, since a variation of the thermal coefficient of the Young's modulus can be corrected by the pivoting angle of the adjustment unit, the management of the production of the balance spring becomes easy. For this reason, it is possible to improve the efficiency of the production of the balance spring and reduce costs.
    In appearance, a center of the bimaterial part can be positioned on the second axis.
    According to the present aspect, as the center of the adjustment unit is positioned on the second axis, it is possible to prevent the center of the adjustment unit from being offset out of the second axis by the position of the weight-forming part in the case of an adjustment of the position of the weight-forming part in the second axial direction. As a result, since it is possible to prevent the center of gravity of the balance-spring from being offset as a function of the pivoting angle of the adjustment unit, it is possible to surely reduce the difference due to the orientation.
    A movement according to another aspect of the present application may [0031] A timepiece according to yet another aspect of the present application may include a balance-spring according to the aspect.
    According to the present aspect, as the thermocompensated balance-spring of the aspect is incorporated, it is possible to propose a movement and a timepiece of high quality, with a small variation affecting walking.
    According to the present application, it is possible to propose a thermocompensated balance-spring, a movement and a timepiece making it possible to easily adjust the importance of the correction of thermal coefficient, with high precision, and obtaining a performance excellent for thermal compensation, with high quality.
    BRIEF DESCRIPTION OF THE FIGURES [0034]
    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, namely the plan view obtained when looking from the front side.
    Fig. 3 is a plan view of a balance spring according to the first embodiment, namely the plan view obtained when looking from the front side.
    Fig. 4 is a side view of the balance spring according to the first embodiment.
    Fig. 5 is a sectional view along the line V-V present in FIG. 3.
    Fig. 6 is an exploded perspective view of an adjustment unit according to the first embodiment.
    Fig. 7 is a sectional view along line VII-VII shown in FIG. 6.
    Fig. 8 is a sectional view similar to FIG. 7.
    CH 714 857 A2
    Fig. 9 is a partial plan view of the balance spring to explain the operation of the adjustment unit. Fig. 10 is a sectional view showing the enlarged adjustment unit, in a state where the adjustment unit is in a reference position. Fig. 11 is a sectional view showing the enlarged adjustment unit, in a state where a pivoting angle θ of the adjustment unit is 45 degrees. Fig. 12 is a sectional view showing the enlarged adjustment unit, in a state where the swivel angle θ of the adjustment unit is 90 degrees. Fig. 13 is a sectional view showing the enlarged adjustment unit, in a state where the swivel angle of this adjustment unit is -45 degrees. Fig. 14 is a sectional view showing the enlarged adjustment unit, in a state where the pivot angle θ of this adjustment unit is -90 degrees. Fig. 15 is a diagram illustrating the relationship between the orientation of the bimaterial part and the amount of deformation of the bimaterial part in the case where the pivoting angle θ of the adjustment unit is varied from -90 degrees to 90 degrees. Fig. 16 is a graph representing the relationship between the swivel angle θ and the variation of radius AR of the adjustment unit. Fig. 17 is a graph representing the relationship between temperature (° C) and walking, as a function of a difference on the thermal coefficient of the Young's modulus of a hairspring. Fig. 18 is a perspective view of an adjustment unit according to a second embodiment. Fig. 19 is a sectional view along line XIX-XIX present in FIG. 18. Fig. 20 is a perspective view of an adjustment unit according to a third embodiment. Fig. 21 is a sectional view along the line XXI-XXI present in FIG. 20. Fig. 22 is a plan view of a balance spring according to an exemplary variant, namely the plan view obtained when looking from the front side. Fig. 23 is a partial plan view of the balance spring according to the variant example.
    DESCRIPTION OF THE EMBODIMENTS In the following, we will describe embodiments of the present invention with reference to the drawings. The components which correspond to each other in the embodiments described below are designated by the same reference numbers and, in certain cases, their description will be omitted.
    First embodiment
    Timepiece [0036] FIG. 1 is an external view of a timepiece 1. In order to make the drawings easy to understand, in each of the drawings seen below, part of the components of the timepiece are omitted and each of the components of the timepiece watchmaking is represented in a simplified manner in certain cases.
    As shown in fig. 1, the timepiece 1 of this embodiment is obtained by mounting a movement 2, a dial 3, various hands 4 to 6, and so on in a timepiece box 7.
    The timepiece box 7 comprises a box body 11, a box cover (not shown) and a cover glass 12. A crown 15 is provided in the position at 3 o'clock (right side in fig . 1), on a lateral surface of the box body 11. The crown 15 is designed to maneuver movement 2 from outside the box body 11. The crown 15 is fixed to a winding rod 19 inserted in the body of box 11.
    Movement [0039] FIG. 2 is a plan view of movement 2 as seen from the front side.
    As shown in fig. 2, the movement 2 is constituted so that several rotating objects (mobile or the like) are rotatably mounted on a plate 21 forming a frame of the movement 2. In the following description, the
    CH 714 857 A2 side of plate 21 with the cover glass 12 of the timepiece box 7 (the side with the dial 3) is called the "rear side" of movement 2 and the side of plate 21 with the box cover (the side opposite to the dial 3) is called the "front side" of movement 2. In addition, each of the rotating objects described below has, as axial direction, the anteroposterior direction of movement 2.
    The winding stem 19 mentioned above is mounted in the plate 21. The winding stem 19 is used to correct the date or the time. The winding stem 19 is rotatable on an axis of the winding stem 19 and it is movable in an axial direction. The winding stem 19 is positioned in the axial direction by means of a switching device comprising a pull tab 23, a rocker 24, a rocker spring 25, as well as a pull jumper 26.
    When the winding stem 19 is rotated, a winding pinion 31 rotates by means of the rotation of a sliding pinion (not shown). Due to the rotation of the winding pinion 31, a crown wheel 32 and a röchet 33 rotate in succession and a barrel spring (not shown) housed in a movement barrel 34 is armed.
    The movement barrel 34 is mounted between the plate 21 and a barrel bridge 35 so as to be rotatable. A second mobile 41, a third mobile 42 and a fourth mobile 43 are mounted between the plate 21 and a gear train 45 so as to be rotatable.
    When the movement barrel is rotated by a restoring force produced by the barrel spring, the second mobile 41, the third mobile 42 and the fourth mobile 43 are rotated in succession by the rotation of the movement barrel 34. The movement barrel 34, the second mobile 41, the third mobile 42 and the fourth 43 form a front wheel train.
    In the front train described above, the minute hand 5 (see Fig. 1) is subject to the second mobile 41. The hour hand 4 mentioned above is attached to an hour wheel (not shown) which rotates according to the rotation of the second mobile 41. In addition, the second hand 6 (see fig. 1) is arranged to rotate on the basis of the rotation of the fourth mobile 43.
    A speed control exhaust 51 is mounted in movement 2.
    The speed regulation exhaust 51 includes an exhaust mobile 52, an anchor 53 and a balance-spring 54 (thermocompensated balance-spring).
    The exhaust mobile 52 is mounted between the plate 21 and the gear train 45 so as to be rotatable. The exhaust mobile 52 is rotated by a rotation of the fourth mobile 43.
    The anchor 53 is mounted between the plate 21 and an anchor bridge 55 so as to be able to oscillate. The anchor 53 includes a pair of pallets 56a and 56b. The pallets 56a and 56b are alternately engaged with an escape wheel 52a of the exhaust mobile 52, due to the oscillation of the anchor 53. The exhaust mobile 52 stops rotating temporarily when one of the pallets 56a and 56b is engaged with the escape wheel 52a. In addition, the exhaust mobile 52 rotates when the paddles 56a and 56b are away from the exhaust wheel 52a. By continuously repeating these operations, the exhaust mobile 52 is rotated intermittently. Due to the intermittent rotation of the exhaust mobile 52, the train (the front train) operates intermittently, so that the rotation of the front train is controlled.
    Spiral balance [0050] FIG. 3 is a plan view of the balance spring 54 as seen from the front side. Fig. 4 is a side view of the balance spring 54.
    As shown in Figures 3 and 4, the balance spring 54 regulates the speed of the exhaust mobile 52 (it makes this mobile 52 is released at a constant rate). The balance spring 54 mainly comprises a balance shaft 61, a balance wheel 62 and a balance spring 63.
    As shown in fig. 4, the balance shaft 61 is retained between the plate 21 and a balance bridge 65 so as to be rotatable on a first axis 01. In the description which follows, in certain cases, the direction along the first axis 01 is called the first axial direction, a direction orthogonal to the first axis 01 is called a first radial direction and a direction rotating around the first axis 01 is called a first circumferential direction. In the present case, the first axial direction coincides with the anteroposterior direction.
    The balance shaft 61 swings back and forth around the first axis 01, with a constant oscillation period, due to the power transmitted from the barrel spring 63. One end of the balance shaft 61, namely its front end in the first axial direction, is retained by the balance bridge 65, by means of a bearing (not shown). One end of the balance shaft 61, namely its rear end in the first axial direction, is retained by a bearing (not shown) formed in the plate 21.
    A double plate 67 is adapted externally on the end of the balance shaft 61 which is the rear end in the first axial direction. The double plate 67 has a tubular shape arranged so as to be coaxial with the first axis 01. A plate pin 68 is provided on a part of the double plate 67 in the first circumferential direction. The plateau pin 68 repeats the actions of engaging and freeing itself from the
    CH 714 857 A2 fork of the anchor 53 synchronized with the movements of the balance-spring 54. Consequently, the anchor 53 moves back and forth, so that the pallets 56a and 56b repeat the operations of engaging and releasing the exhaust mobile 52.
    As shown in fig. 3, the balance wheel 62 is fixed to the front side of the double plate 67 in the balance shaft 61 in the first axial direction. The balance wheel 62 mainly 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 made of a metal (for example brass or the like) , in a single piece.
    The hub 71 is fixed to the balance shaft 61 by driving or the like.
    The spoke 72 protrudes from the hub 71, outward in the first radial direction. In the present embodiment, it is possible to appropriately modify the position of the spoke 72 in the first circumferential direction, the number of spokes 72 and so on.
    The serge 73 has an annular shape arranged so as to be coaxial with the first axis 01 as a whole, since the two ends of a pair of serge portions 75, in the first circumferential direction, are connected one to the other. The serge 73 surrounds the hub 71, from the outside in the first radial direction. One end of the spoke 72, namely its outer end in the first radial direction, is connected to an internal peripheral surface of the serge 73.
    Each of the portions of twill 75 is formed so as to be symmetrical by rotation (symmetry of order 2 in the present embodiment) around the first axis 01. A rotation target is an example of an expression to characterize a figure and it is a known concept. For example, if n is an integer greater than or equal to 2 and when a rotation target overlaps itself when it is rotated 360 / n degrees around a certain center (for the case of a figure in two dimensions) or an axis (in the case of a three-dimensional shape), this characteristic is called n-order symmetry, n-phase symmetry, 360 / n degree symmetry or the like. For example, in the case where n = 2, when it is rotated by 180 °, the rotation target overlaps itself and it has a symmetry of order 2.
    Each of the twill portions 75 comprises a circular arc portion 76, a first bent portion 77 and a second bent portion 78.
    The respective circular arc portions 76 have arc shapes having the same radius of curvature around the first axis 01 as the center.
    The first bent portion 77 is connected to a first end of the circular arc portion 76 in the first circumferential direction. The first bent portion 77 is bent from a circular arc portion 76, towards the first axis 01, along a tangential direction of the serge 73.
    The second bent portion 78 is connected to a second end of a circular arc portion 76 in the first circumferential direction. The second bent portion 78 is bent from a circular arc portion 76, toward the first axis 01, along a tangential direction of the serge 73.
    The first bent portion 77 of a portion of twill 75 from the respective portions of twill 75 is connected to the second bent portion 78 of the other portion of twill 75. The second bent portion 78 of a portion of twill 75 among the respective portions of twill 75 is connected to the first bent portion 77 of the other portion of twill 75. Consequently, the twill 77 is in one piece, of annular shape. In the present embodiment, the first angled portion 77 of a portion of twill 75 (or of the other portion of twill 75) and the second bent portion 78 of the other portion of twill 75 (or said one portion of serge 75) are perpendicular to each other.
    Spiral 73 is a flat spiral in the form of a spiral when it is seen in a plan view in the first axial direction. Spiral 63 is wound along an Archimedes curve. An inner end of the balance spring 63 is connected to the balance shaft 61 by means of a ferrule 79. An external end of the balance spring 63 is connected to the balance bridge 63 by means of a stud (not shown). The hairspring 63 has the role of storing energy transmitted from the fourth mobile 43 to the exhaust mobile 52 and to transmit this power to the balance shaft 61.
    In the present embodiment, a constant elastic material (for example Coelinvar or the like) is suitably used for the hairspring 63. The hairspring 63 has a positive thermal characteristic of the Young's modulus over the temperature range use. In this case, the thermal coefficient of the Young's modulus of the balance spring 63 is chosen so as to make the oscillation period of the balance spring 54 as constant as possible for a thermal characteristic of the moment of inertia of the wheel. pendulum 62 with temperature change. At the same time, the hairspring 63 can be made of a material other than a constant elastic material. In this case, for hairspring 63, it is possible to use a general steel having a negative thermal coefficient (a characteristic according to which the stiffness increases with an increase in temperature) of the Young's modulus.
    Adjustment unit Here, an adjustment unit 100 is carried by the first bent portion 77 of each portion of twill 75 described above, in overhang. The adjustment unit 100 has the form of a bar extending along a second axis 02 parallel to a tangent of the serge 73, inside this serge 73. In the following, in some cases, a direction according to
    CH 714 857 A2 second axis 02 is called a second axial direction, a direction orthogonal to the second axis 02 is called a second radial direction, and a direction rotating around the second axis 02 is called a second circumferential direction. In the present embodiment, the adjustment units 100 have rotational symmetry about the first axis 01. For this reason, in the description which follows, an adjustment unit 100 will be described by way of example.
    FIG. 5 is a sectional view along the line V-V of FIG. 3.
    As shown in fig. 5, a mounting hole 101 passing through the first bent portion 77 in the second axial direction is formed in this first bent portion 77. The mounting hole 101 is circular in shape (a perfect circular shape) when viewed in a front view in the second axial direction. The shape of the mounting hole 101 is not limited to the circular shape and may be a rectangular shape, a triangular shape and the like.
    Slots 102 are formed respectively in the first bent portion 77, on both sides of the mounting hole 101 in the second radial direction. Each of the slots 102 extends in the second radial direction and an inner end in the second radial direction communicates with the mounting hole 101. Each of the slots 102 passes through the first bent portion 77 in the second axial direction.
    As shown in fig. 3, the adjustment unit 100 is formed by assembling a support portion 120, a bimaterial part 121 and a weight forming part 122, from a retained end side (fixed end side) to a tip end side (end side free) in the second axial direction.
    [0072] FIG. 6 is an exploded perspective view of the adjustment unit.
    As shown in figs. 3 and 6, the support portion 120 is made, for example of a metal. The support portion 120 has a tubular shape at the bottom, open towards the end end side of the adjustment unit 100 in the second axial direction. The support portion 120 has a shape which is circular as seen in a plan view in the second axial direction and which corresponds to the mounting hole 101 described above. The support portion 120 is forcibly mounted (elastic resistance) in the mounting hole 101.
    As shown in fig. 5, the difference in width between the support portion 120 and the mounting hole 101 is chosen to a value such that the adjustment unit 100 can rotate around the second axis 02 in the case where a predetermined torque around the second axis 02 (second circumferential direction) is applied to the adjustment unit 100. In other words, since an external circumferential surface of the support portion 120 rotates around the second axis 02 by sliding on an internal peripheral surface of the mounting hole 101, the adjustment unit 100 of the present embodiment is such that the pivot angle can be adjusted on the second axis 02. The shape of the cross section of the support portion 120 is not limited to the circular shape and it can be a rectangular shape, a triangular shape, or the like. Further, in the present embodiment, the case where the shape of the cross section of the support portion 120 corresponds to the mounting hole 101 is described, but the support portion 120 and the mounting hole 101 may have shapes different from each other when the support portion 120 is shaped so as to be rotatable on the second axis 02.
    As shown in fig. 3, a base end of the support portion 120 in the second axial direction protrudes from the first bent portion 77, towards the outside of the twill 73. Specifically, the base end of the support portion 120 is found in an area delimited by the first bent portion 77 of one of the portions of serge 75 and the second bent portion 78 of the other portion of serge 75 belonging to serge 73.
    As shown in fig. 4, a coupling portion 126 is formed on a base end surface of the support portion 120. The coupling portion 126 is a groove extending in the second radial direction, with a linear shape. A tool can be engaged with the coupling portion 126. In other words, the adjustment unit 100 is provided to be able to be pivoted on the second axis 02 by means of a tool engaged with the portion d 'coupling 126. As soon as the coupling portion 126 has a shape allowing it to be engaged with a tool, this coupling portion 126 is not limited to a groove.
    As shown in figs. 3 and 5, the bimaterial part 121 is fixed in the support portion 120. For example, the bimaterial part 121 is force-fitted or inserted into the support portion 120 and fixed to this support portion 120 by means of an adhesive or the like. The bimaterial part 121 is in the form of a plate extending linearly in the second axial direction.
    The bi-material part 121 is formed by overlapping two plate materials (a low expansion element 130 and a high expansion element 131) having different coefficients of thermal expansion, in the second radial direction. In the present embodiment, invar (Ni-Fe alloy), silicon, ceramics or the like is suitably used for the low expansion element 130. Copper, a copper-based alloy, aluminum or the like is suitably used for the high expansion element 131. The low expansion element 130 and the high expansion element 131 have equivalent shapes to each other (a shape of the cross section perpendicular to the second axis 02 is rectangular). In the example shown, the border area between the low expansion element 130 and the high expansion element 131 is positioned on the second axis 02. It is preferable that the center of the adjustment unit 100 is positioned on the second axis 02. For this reason, the plate thicknesses of the low expansion element 130 and of the high expansion element 131 may be different from each other
    CH 714 857 A2 (plate thickness can be changed as appropriate). In the case where the plate thicknesses of the low expansion element 130 and the high expansion element 131 differ from one another, the border area between the expansion element 130 and the expansion element high 131 extends parallel to the second axis 02.
    The bimaterial part 121 (the low expansion element 130 and the high expansion element 131) is arranged so that its orientation in the second radial direction can be modified according to a pivoting of the unit. adjustment 100 on the second axis 02. The bimaterial part 121 is designed to deform in the second radial direction as a function of a temperature change, using the difference between the coefficients of thermal expansion of the low expansion element 130 and of the high expansion element 131. A specific operation of the bimaterial part 121 will be described below.
    FIG. 7 is a sectional view along line VII-VII shown in FIG. 6. Fig. 8 is a sectional view which corresponds to FIG. 7.
    As shown in figs. 6 to 8, the counterweight portion 122 comprises a fixed part 140 and a movable part 141. In the present embodiment, the fixed part 140 and the movable part 141 are both made of metal.
    The fixed part 140 has a tubular shape arranged so as to be coaxial with the second axis 02. A through hole 143 in the fixed part 140 has a shouldered shape so that its internal diameter decreases towards the end end side in the second axial direction. Specifically, the through hole 143 comprises a large diameter portion 143a positioned on the base end side in the second axial direction, a small diameter portion 143b positioned end side end in the second axial direction, as well as a shoulder 143c connecting the large diameter portion 143a and the small diameter portion 143b.
    One end of the bimaterial part 121 is fixed in the large diameter portion 143a. For example, the bimaterial part 121 is force-fitted or inserted into the fixed part 140 and fixed to the fixed part 140 by means of an adhesive or the like. The end end surface of the bimaterial part 121 is close to or in contact with the shoulder 143c in the second axial direction, in the large diameter portion 143a. Consequently, the positioning of the fixed part 140 in the second axial direction is carried out on the bimaterial part 121.
    A thread is formed in the internal peripheral surface of the portion of small diameter 143b. It is possible to suitably modify the internal diameter of the through hole 143. For example, the internal diameter of the through hole 143 may be constant over the entire second axial direction.
    The movable part 141 has the shape of a screw. A thread is formed in a rod 141 a of the displaceable part 141. The rod 141 a is screwed into the small diameter portion 143b.
    A head 141b of the movable part 141 projects outwards in the second radial direction, from an end end of the rod 141 a in the second axial direction. The head 141b has a polygonal shape as seen in a plan view in the second axial direction. In the present embodiment, a portion of maximum external diameter of the head 141b coincides with an external diameter of the fixed part 140. At the same time, it is possible to appropriately modify the shape or the external diameter of the head 141 b as seen in a plan view.
    As shown in fig. 8, when the movable part 141 is rotated in the screwing direction relative to the fixed part 140, this movable part 141 moves towards the base end side of the fixed part 140 and the bimaterial part 121 in the second direction axial. Consequently, the center (center of gravity) of the counterweight portion 122 moves towards the base end side in the second axial direction. On the other hand, as shown in fig. 7, when the movable part 141 is rotated in the direction of unscrewing relative to the fixed part 140, this movable part 141 moves towards the end end side of the fixed part 140 and of the bimaterial part 121 according to the second axial direction. Therefore, the center of the counterweight portion 122 moves to the tip end side in the second axial direction.
    In this way, the counterweight portion 122 of the present embodiment is such that the position of its center in the second axial direction can be adjusted by means of a displacement of the movable portion 141 in the second direction. axial with respect to the fixed part 140 and the bi-material part 121.
    Temperature Correction Method Now, we will describe a method of adjusting the importance of the correction of thermal coefficient in the balance-spring 54. First, a thermal correction method based on the orientation of the bi-material part 121 will be described. Fig. 9 is a partial plan view which represents the balance spring 54 and which is intended to explain an operation of the adjustment unit 100.
    In the state shown in FIG. 9, the low expansion element 130 and the high expansion element 131 in the bimaterial part 121 are aligned in the first radial direction in a state where the low expansion element 130 is placed inside in the first direction radial.
    In the balance spring 54 of this embodiment, when there is a change in temperature, the bimaterial part 121 bends and deforms as a function of the difference between the coefficients of thermal expansion
    CH 714 857 A2 of the low expansion element 130 and the high expansion element 131. In particular, in the case where the temperature increases with respect to a predetermined temperature T0 (normal temperature (for example around 23 ° C.) ), the high expansion element 131 expands more than the low expansion element 130. Consequently, the adjustment unit 100 is deformed to one side (the inner side in the first radial direction in FIG. 9) of the low expansion element 130 and of the high expansion element 131, in the stacking direction. In the case where the temperature decreases with respect to the predetermined temperature TO, the high expansion element 131 contracts more than the low expansion element 131. Consequently, the adjustment unit 100 is deformed towards the other side (the outer side in the first radial direction in fig. 9) in the stacking direction.
    By means of the deformation of the adjustment unit 100, the distance between the tip end of the adjustment unit 100 and the first axis 01 in the first radial direction is modified. In particular, in the case where the distance between the tip end of the adjustment unit 100 and the first axis 01 in the first radial direction at the predetermined temperature TO is a distance RO and where the distance between the end of end of the adjustment unit 100 and the first axis 01 in the first radial direction after a temperature change is a distance R1, the difference between the distance RO and the distance R1 is a variation of radius AR in the first radial direction. An average diameter of the balance wheel 62 can be reduced or increased as a function of the variation in radius AR, and the moment of inertia of the balance spring 54 around the first axis 01 can be modified. In other words, in the case where the temperature increases, it is possible to decrease the moment of inertia by decreasing the average diameter of the balance wheel 62. In the case where the temperature decreases, it is possible to increase the moment of inertia by increasing the mean diameter of the balance wheel 62. Consequently, it is possible to correct the thermal coefficient of the moment of inertia.
    By the way, in the case where a constant elastic material is used for the hairspring 63 as in the present embodiment, it is possible that the thermal coefficient of the Young modulus varies positively or negatively depending on the manufacturing conditions in the manufacturing process (eg dissolution or heat treatment) of the hairspring.
    Conversely, in the present embodiment, it is possible to modify the orientation (the pivot angle θ on the second axis 02) of the bimaterial part 121 as a function of the thermal coefficient of the module Young of hairspring 63. In particular, a tool is engaged in the coupling portion 126 of the adjustment unit 100 shown in FIG. 4. When the tool is rotated on the second axis 02, the adjustment unit 100 rotates on the second axis 02 while the external circumferential surface of the support portion 120 slides on the internal peripheral surface of the mounting hole 101 Consequently, the pivot angle θ is modified.
    Figs. 10 to 14 are sectional views showing the enlarged adjustment unit 100.
    In the state shown in FIG. 10, the low expansion member 130 and the high expansion member 131 are aligned in the first axial direction in a state where the expansion member 130 is placed on the front side in the first axial direction. This state is chosen as the reference position (0 degree) of the adjustment unit 100, the pivot angle θ on the second axis 02 is adjusted. For example, in fig. 11, the adjustment unit 100 is pivoted 45 degrees clockwise (+ direction), on the second axis 02, from the reference position. In fig. 12, the adjustment unit 100 is pivoted 90 degrees clockwise (+ direction), on the second axis 02, from the reference position.
    In FIG. 13, the adjustment unit 100 is pivoted by -45 degrees anti-clockwise (direction -), on the second axis 02, from the reference position. In fig. 14, the adjustment unit 100 is pivoted by -90 degrees anticlockwise (direction -), on the second axis 02, from the reference position.
    [0098] FIG. 15 is a diagram illustrating the relationship between the orientation of the bimaterial part 121 and the amount of deformation of the bimaterial part 121 in the case where the pivot angle θ of the adjustment unit 100 is changed from -90 degrees to at 90 degrees, the temperature being the same (high temperature). In fig. 15, the X axis represents the component (hereinafter called the X component) in the first radial direction of the deformation vector of the bimaterial part 121. In addition, the Y axis represents the component (hereinafter called the component Y) in the first axial direction of the deformation vector of the bimaterial part 121. In this case, in FIG. 15, the direction -X corresponds to the interior in the first radial direction, and the direction + X corresponds to the exterior in the first radial direction. Furthermore, in FIG. 15, the bimaterial part 121 positioned at the level of the origin represents the state observable at the predetermined temperature TO (before deformation).
    As shown in fig. 15, in the case where the adjustment unit 100 is at the reference position (0 degrees), the bimaterial part 121 is deformed only towards the front side in the first axial direction (A1 in fig. 15). For this reason, at the reference position, the Y component of the deformation vector of the bimaterial part 121 reaches a maximum and the X component of the deformation vector of the bimaterial part 121 is equal to 0. In this case, as the variation of radius AR is equal to 0, the thermal coefficient of the moment of inertia is not modified.
    When the adjustment unit 100 is pivoted in the + direction from the reference position, this bimaterial part 121 also deforms outwards in the first radial direction, so that a + X component of the vector of deformation of the bimaterial part 121 exists (A2 and A3 in fig. 15). When increasing the pivot angle 9 in
    CH 714 857 A2 the + direction, the + X component is gradually increased. In other words, by moving the pivoting angle θ of the adjustment unit 100 in the + direction from the reference position, it is possible to increase the quantity by which the moment of inertia of the balance increases -spiral 54 during a temperature increase. In addition, in the case where the pivot angle θ is equal to 90 degrees (A3 in fig. 15), the bimaterial part 121 only deforms outwards in the first radial direction. For this reason, in the case where the pivot angle θ is equal to 90 degrees, the component + X reaches a maximum and the component Y is equal to 0. In this way, by pivoting the adjustment unit 100 in the sense + from the reference position, it is possible to increase the thermal coefficient of the moment of inertia.
    On the other hand, when the adjustment unit 100 is pivoted in the direction - from the reference position, the bimaterial part 121 also deforms inwards in the first radial direction, so that 'a component -X of the deformation vector of the bimaterial part 121 exists (A4 and A5 in fig. 15). When the pivot angle θ is increased in the - direction, the -X component is increased. In other words, by moving the pivoting angle θ of the adjustment unit 100 in the direction - from the reference position, it is possible to prevent the moment of inertia of the balance spring 54 increases with a rise in temperature. In addition, in the case where the pivot angle θ is equal to - 90 degrees (A5 in fig. 15), the bimaterial part 121 deforms only inwards in the first radial direction. For this reason, in the case where the pivot angle θ is equal to -90 degrees, the component -X reaches a maximum and the component Y is equal to 0. In this way, by turning the adjustment unit 100 in the direction - from the reference position, it is possible to decrease the thermal coefficient of the moment of inertia.
    [0102] FIG. 16 is a graph representing the relationship between the pivot angle θ and the variation in radius AR of the adjustment unit 100.
    As shown in fig. 16 according to the results of fig. 15 described above, when the adjustment unit 100 is pivoted in the + direction from the reference position, the variation in radius AR of the adjustment unit 100 is increased in the + direction (outwards according to the first radial direction). On the other hand, when the adjustment unit 100 is turned in the direction-from the reference position, the variation in radius AR of the adjustment unit 100 is increased in the direction - (inward in the first radial direction).
    [0104] FIG. 17 is a graph representing the relationship between temperature (° C) and walking as a function of the difference on the thermal coefficient of the Young's modulus of hairspring 63. In fig. 17, the broken line G1 represents a case in which the step (the period of oscillation of the balance-spring 54) has a negative thermal characteristic, and the dashed line G2 represents a case in which the step has a characteristic positive thermal.
    As illustrated by G1 in FIG. 17, according to the relationship between the Young's modulus of the balance spring 63 and the moment of inertia of the balance spring 54, in the case where the step has a negative thermal characteristic, the step resulting from an increase in temperature tends to be delayed. In this case, the adjustment unit 100 is turned in the direction - from the reference position. Consequently, since it is possible to set the variation of radius AR inwards in the first radial direction as a function of an increase in temperature and to reduce the thermal coefficient of the moment of inertia, it is possible to prevent that the moment of inertia of the balance spring increases with an increase in temperature. It follows that the thermal coefficient of the period of oscillation of the balance-spring 54 is adjusted to approach 0 and the walking is kept constant whatever the temperature change (see the solid line G3 in fig. 17) .
    On the other hand, as shown by G2 in fig. 17, according to the relationship between the Young's modulus of the balance spring 63 and the moment of inertia of the balance spring 54, in the case where the step has a positive thermal characteristic, the step resulting from an increase in temperature tends to advance . In this case, the adjustment unit 100 is pivoted in the + direction from the reference position. Consequently, as it is possible to set the variation of radius AR inwards in the first radial direction as a function of an increase in temperature and to increase the thermal coefficient of the moment of inertia, it is possible to increase the quantity by which the moment of inertia of the balance spring is increased as a function of the temperature increase. It follows that the thermal coefficient of the period of oscillation of the balance-spring 54 is adjusted to approach 0 and the walking is kept constant whatever the temperature change (see the solid line G3 in fig. 17) .
    We will now describe a temperature correction method using the feeder portion 122. The feeder portion 122 of this embodiment is such that the movable portion 141 is movable relative to the fixed portion 140 and the bimaterial part 121 in the second axial direction. In this case, in order to decrease the thermal coefficient of the moment of inertia, as shown in fig. 7, the movable part 141 is rotated in the screwing direction. Then, the movable part 141 moves towards the base end of the fixed part 140 and the bimaterial part 121, in the second axial direction. In other words, since the length of the counterweight portion 122 in the second axial direction (the length of a projecting portion of the first bent portion 77) is reduced, the center (center of gravity) of the unit of adjustment 100 is moved towards the base end in the second axial direction. Consequently, it is possible to reduce the thermal coefficient of the moment of inertia of the adjustment unit 100.
    CH 714 857 A2 [0109] On the other hand, in order to increase the thermal coefficient of the moment of inertia, as shown in fig. 8, the movable part 141 is rotated in the unscrewing direction. Then, the movable part 141 moves towards the end end side of the fixed part 140 and of the bimaterial part 121 in the second axial direction. In other words, as the length of the counterweight portion 122 in the second axial direction is increased, the center of the adjustment unit 100 is moved to the tip end side in the second axial direction. Therefore, it is possible to increase the thermal coefficient of the moment of inertia of the adjustment unit 100.
    In this embodiment, when changing the pivot angle change (orientation of the bimaterial part 121) of the adjustment unit 100 and the length (the position of the movable part 141) of the part forming flyweight 122 as a function of the thermal characteristic of the step, the thermal coefficient of the moment of inertia of the sprung balance 54 can be corrected to be positive as well as negative. Consequently, it becomes easy to compensate for a variation in the thermal coefficient of Young's mobile with a thermal characteristic of the moment of inertia of the balance-spring 54.
    As described above, the present embodiment presents a constitution in which the adjustment units 100 comprising the bi-material parts 121 are provided in symmetrical positions by rotation in the balance wheel 62.
    With this constitution, due to the fact that the bimaterial part 121 deforms as a function of the temperature change, the mean diameter of the balance wheel is modified. Therefore, it is possible to correct the thermal characteristic of the moment of inertia.
    Here, in the present embodiment, the adjustment unit 100 is constituted so as to include the bi-material part 121 and the counterweight part 122 attached to the bi-material part 121 movable in the second axial direction.
    With this constitution, by adjusting the position of the counterweight portion 122 in the second axial direction relative to the bi-material part 121, it is possible to change the position of the center of the counterweight portion 122 in the second axial direction . Consequently, it is possible to continuously adjust the thermal coefficient of the moment of inertia of the balance spring 54. Consequently, it is possible to adjust in a simple manner, with high precision, the degree of correction of the compared thermal coefficient to the constitution of the prior art in which separate components such as a screw and the like are attached and detached.
    In the present embodiment, since the adjustment unit 100 is provided on the serge 73 of the balance wheel 62, it is possible to keep the adjustment unit 100 away from the first pivot axis 01 according to the first radial direction. Consequently, it is possible to increase the variation of radius AR and it is possible to increase the quantity of which the thermal coefficient is corrected by the bimaterial part 121.
    The present embodiment has a constitution in which the counterweight portion 122 is attached to the fixed part 140 so as to be displaceable in the second axial direction, relative to the fixed part 140.
    With this constitution, when only the displaceable part 141 of the counterweight portion 122 is displaced relative to the fixed part 140 and to the bimaterial part 121, no change in the effective length (the length of the portion discovered at from the support portion 120 or from the counterweight portion 122) of the bimaterial part 121 does not result from a displacement of the displaceable portion 141. In other words, since it is possible to modify only the position of the center of the weight forming part 122 (the degree of deformation of the bimaterial part 121 as a function of a temperature change is not modified), it is possible to adjust in a simpler way the quantity of which the thermal coefficient is corrected.
    In the present embodiment, the bimaterial part 121 extends in overhang from the serge 73 and the weight forming part 122 is attached to an end of the bimaterial part 121.
    With this constitution, since the adjustment unit 100 extends overhang, it is possible to guarantee a variation of radius AR with a change in temperature and it is possible to increase the quantity of which the thermal coefficient is corrected by the bimaterial part 121.
    In addition, since the weight forming part 122 is attached to the tip end of the bimaterial piece 121, it is possible to increase the mass of the tip end which is the most deformed part within the adjustment unit 100. For this reason, it is possible to increase the quantity whose thermal coefficient is corrected by the bimaterial part 121. In addition, by attaching the weight forming part 122 to the end of the part bimaterial 121, one base end of the adjustment unit 100 can be held stably in the rim 73. Therefore, it is possible to prevent the entire adjustment unit 100 from wobbling depending on the setting of the weight forming part 122 and it is possible to adjust with an even higher precision the quantity with which the thermal coefficient is corrected.
    In the present embodiment, the adjustment unit 100 is such that the orientation of the adjustment unit 100 can be adjusted around the second axis 02 (its pivot angle on the second axis 02).
    With this constitution, it is possible to change the orientation of the bimaterial part 121 as a function of the thermal coefficient of the Young's modulus of the hairspring 63. Consequently, the importance of the correction of thermal coefficient by the bimaterial part 121 can be modified to be both positive and negative and the thermal coefficient of the moment of inertia of the balance spring 54 can be corrected to be both positive and negative. In other words, it becomes easy
    CH 714 857 A2 to compensate for a variation in the thermal coefficient of the Young's modulus by a thermal characteristic of the moment of inertia of the balance-spring 54. In particular, as in the present embodiment, by adjusting the moment of inertia of the balance-spring 54 with the pivoting angle θ of the adjustment unit 100 in addition to the position of the counterweight portion 122, it is possible to adjust with greater precision the quantity by which the thermal coefficient is corrected. As a result, the oscillation period of the balance spring 54 can be constant and that the balance spring 54 with an excellent thermal compensation characteristic can be proposed.
    In addition, in the present embodiment, even if the orientation of the bimaterial part 121 is modified, the length of the adjustment unit 100 in the second axial direction 02 remains constant. For this reason, contrary to the case of a modification of the effective length of the bimaterial part 121 of the relative prior art, it is possible to prevent the center (center of gravity) of the balance spring from being offset at temperature. ΤΟ. As a result, it is possible to prevent an imbalance from appearing and to reduce a difference due to the orientation.
    In this embodiment, the adjustment unit 100 is placed inside the serge 73 in the first radial direction and it extends along a tangent line of the serge 73.
    With this constitution, it is possible to guarantee the variation of radius AR with a change in temperature while preventing the balance-spring 54 from being made wider because of the addition of the adjustment unit 100.
    In the present embodiment, as the coupling portion 126 is formed on the base end (the support portion 120) of the adjustment unit 100, it is possible to simply adjust the the orientation of the adjustment unit around the second pivot axis via the support portion 120. In addition, by changing the pivot angle θ of the adjustment unit 100 via the support portion 120, it is possible to prevent plastic deformation when adjusting the orientation of the adjustment unit 100, compared with the case where the change in the pivoting angle θ of the adjustment unit 100 would take place via the tip end (the bimaterial part 121 or the counterweight part 122). For this reason, it is possible to avoid a change in the rate of operation occurring at the predetermined temperature TO by a plastic deformation of the adjustment unit 100.
    In the present embodiment, the hairspring 63 is made of a constant elastic material.
    With this constitution, it is possible to reduce the change in the Young's modulus as a function of temperature variations and to remove the dependence of the oscillation period on the temperature. Furthermore, in the present embodiment, since the variations in the thermal coefficient of the Young's modulus can be corrected by the adjustment unit 100, the management of the manufacture during the manufacture of the hairspring 63 becomes easy. For this reason, it is possible to improve the manufacturing efficiency of hairspring 63 and reduce costs.
    In the present embodiment, since the center of the adjustment unit 100 is placed on the second axis 02, it is possible to prevent the center of the adjustment unit 100 from being offset from the second axis 02 by the pivoting angle θ of the adjustment unit 100 or the position of the counterweight portion 122 in the second axial direction. As a result, it is possible to adjust with greater precision the quantity with which the thermal coefficient is corrected.
    As the movement 2 and the timepiece 1 of this embodiment include the balance spring 54 described above, it is possible to propose a movement 2 of high quality and a timepiece 1 having a step having a small variation.
    Second embodiment [0131] Now, a second embodiment of the present invention will be described. Fig. 18 is a perspective view of an adjustment unit 100 according to the second embodiment. Fig. 19 is a sectional view along the line XIX-XIX present in FIG. 18.
    As shown in figs. 18 and 19, the adjustment unit 100 of this embodiment differs from the first embodiment described above in that the counterweight portion 122 is screwed directly onto the bimaterial part 121.
    A thread is formed on the outer circumferential surface of the tip end of the bimaterial part 121.
    The weight portion 122 has a tubular shape arranged so as to be coaxial with the second axis 02. A thread is formed on the internal peripheral surface of the weight portion 122. Consequently, the weight portion 122 is screwed on the tip end of the bimaterial part 121.
    In the present embodiment, when the part forming the counterweight 122 is turned in the screwing direction relative to the bimaterial part 121, the part forming the counterweight 122 moves towards the base end side of the bimaterial part 121 in the second axial direction. Consequently, the center of the adjustment unit 100 moves towards the base end side in the second axial direction. On the other hand, when the weight forming part 122 is rotated in the direction of unscrewing relative to the bimaterial part 121, the weight forming part 122 moves towards the end end side of the bimaterial part 121 in the second direction axial.
    In the present embodiment, for example, the following actions and effects are obtained in addition to the same operation and the same effects as the embodiment described above.
    CH 714 857 A2 [0137] According to the present embodiment, the effective length of the bimaterial part 121 changes when the weight forming part 122 is moved. Consequently, it is possible to increase the degree of modification of the moment of inertia of the balance-spring 54 using the quantity of which the weight-forming part 122 is adjusted in the second axial direction.
    Third embodiment [0138] Now, a third embodiment of the present invention will be described. Fig. 20 is a perspective view of the adjustment unit 100 according to the third embodiment. Fig. 21 is a sectional view along the line XXI-XXI shown in FIG. 20.
    As shown in figs. 20 and 21, in the present embodiment, the counterweight portion 122 comprises a tubular portion 200 and a counterweight body 201.
    The tubular portion 200 is arranged so as to be coaxial with the second axis 02. A slot 202 which is open at a base end surface in the second axial direction is formed in the tubular portion 200 The slot 202 extends in the second axial direction and ends at an intermediate portion of the tubular portion 200. In the present embodiment, the slots 202 form a pair in a portion of the tubular portion 200, opposite in the second radial direction. A portion of the tubular portion 200 positioned between the slots 202 in the second circumferential direction is formed so as to be elastically deformable in the second radial direction. It is possible to appropriately change the position, number, size and the like of the slots 202.
    The counterweight body 201 is fixed to the end end of the tubular portion 200. It is possible to appropriately change the size and the like of the counterweight body 201.
    In the present embodiment, the bimaterial part 121 is force-fitted (elastic retention) in the tubular portion 200, from an open portion on the base end side. The interference between the bimaterial part 121 and the tubular portion 200 (the difference between their widths) is adjusted so that the counterweight portion 122 is movable in the second axial direction in the case where an external force is applied to the tubular portion 200 in the second axial direction.
    In the present embodiment, by sliding the weight-forming part 122 in the second axial direction relative to the bimaterial part 121, it is possible to change the position of the center of the weight-forming part 122 according to the second axial direction. In other words, by moving the counterweight portion 122 towards the end end side of the bimaterial part 121 in the second axial direction, the center of the counterweight portion 122 is moved towards the end end side in the axial direction . On the other hand, by moving the weight forming part 122 towards the base end side of the bimaterial part 121 in the second axial direction, the center of the weight forming part 122 is moved towards the base end side according to the second axial direction.
    In the present embodiment, the following actions and effects are obtained in addition to the same operation and the same effects as the second embodiment described above.
    Without applying a particular method to the bimaterial part 121, it is possible to subject the counterweight part 122 to the bimaterial part 121 so that the counterweight part 122 is movable in the second axial direction. Consequently, it is possible to avoid a decrease in manufacturing efficiency and an increase in manufacturing costs in connection with the addition of the counterweight portion 122.
    Other examples of a variant [0146] The technical scope of the present invention is not limited to the embodiments described above and various modifications may be possible without departing from the spirit of the present invention.
    For example, in the embodiment described above, the arrangement described is that in which two adjustment units 100 are provided in symmetrical positions by rotation on the serge 73, but the embodiment is not limited to this single arrangement. In other words, as shown in fig. 22 for example, three or more than three adjustment units 100 can be provided as long as the respective adjustment units 100 are provided in symmetrical positions by rotation.
    After the orientation of the adjustment unit 100 around the second axis 02 has been adjusted, the adjustment unit 100 can be fixed to the first bent portion 77 so that it cannot be turned. As a method of fixing the adjustment unit 100, welding, an adhesive, or the like can be used, or a separate fastener (e.g. a pressure screw or the like) can be used for fixing.
    In the embodiment described above, the constitution described is that allowing adjustment of the moment of inertia of the balance-spring 54 by the pivot angle θ of the bimaterial part 121 and the position of the counterweight part 122 in the second axial direction, but the embodiment is not limited to this single constitution. The adjustment unit 100 is such that at least the counterweight portion 122 is movable relative to the bimaterial part 121 in the second axial direction.
    CH 714 857 A2 [0150] In the embodiment described above, the constitution has been described in which the weight-forming part 122 is secured to the tip end of the bimaterial part 121, but the weight-forming part 122 can be attached in any position on the bimaterial part 121 as soon as the weight forming part 122 can be moved in the second axial direction relative to the bimaterial part 121.
    In the embodiment described above, the constitution has been described in which the adjustment unit 100 is placed in the same plane as the serge 73, but the embodiment is not limited to this single constitution . In other words, the adjustment unit 100 and the twill 73 can be placed in positions offset in the first axial direction.
    In the embodiment described above, there has been described the constitution in which the second axis 02 of the adjustment unit 100 extends along a tangent line of the serge 73, but the embodiment does not is not limited to this one constitution. In other words, any arrangement can be used as soon as the X component of the deformation vector of the regulagelOO unit is generated as a function of the deformation of the bimaterial part as a function of the temperature change. In this case, the second axis 02 can be adjusted to a direction intersecting the first axial direction, to a direction parallel to the first axial direction, or the like.
    In the embodiment described above, there has been described the constitution in which the adjustment unit 100 is carried by the serge 73 via a support portion 120, but the embodiment does not is not limited to this one constitution. In other words, in the balance spring 54, the adjustment unit 100 can be provided at a part (balance spring body) driven in rotation by the power of the spring 63. In this case, as balance-spring body, balance shaft 61, balance wheel 62 (hub 71, spoke 72, or the like), the double plate 67, or the like is used.
    In the embodiment described above, there has been described the constitution in which the low expansion element 130 and the high expansion element 131 are formed of plate materials having the same shapes, but the embodiment is not limited to this one constitution. For example, as shown in fig. 23, the thicknesses of the low expansion member 130 and the high expansion member 131 may be different from each other. In addition, the shape of the cross section of the low expansion member 131 and the high expansion member 131 orthogonal to the second axis 02 is not limited to a rectangular shape, so that the shape of the cross section can be appropriately changed to a triangular shape, a semi-circular shape, or the like.
    In the embodiment described above, the constitution has been described in which the low expansion element 130 and the high expansion element 131 are stacked in the second radial direction, but the embodiment is not not limited to this one constitution. The low expansion element 130 and the high expansion element 131 can be stacked in a direction intersecting the second axial direction. In this case, as shown in fig. 23 for example, the low dilation element 130 gradually thickening towards the tip end and the high dilation element 131 gradually thinning towards the tip end can be joined.
    In the embodiment described above, the constitution has been described in which the adjustment unit 100 extends in a linear form, but the embodiment is not limited to this single constitution. As soon as it is possible to adjust the pivoting angle of the adjustment unit 100 on the second axis 02, the adjustment unit 100 can extend by cutting the second axial direction or can have a wavy shape.
    In the embodiment described above, the constitution has been described in which the adjustment unit 100 extends in overhang, but the embodiment is not limited to this single constitution and may have a double pinch constitution.
    In the embodiment described above, the case has been described where the entire portion between the support portion 120 and the counterweight portion 122 is constituted by the bimaterial part 121 in the adjustment unit 100, but the embodiment is not limited to this single constitution. At least part of the adjustment unit 100 can be formed by the bimaterial part 121.
    In addition, within the scope not departing from the spirit of the present invention, it is possible to appropriately replace components of the embodiments described above by known components, and the different Examples of variants described above can be combined as appropriate.
    claims
    权利要求:
    Claims (9)
    [1]
    1. Thermocompensated balance spring, comprising:
    a balance-spring body which comprises a balance shaft extending along a first axis and which rotates around the first axis by the power of a balance spring; and an adjustment unit which comprises bimaterial parts which extend respectively along second axes, from symmetrical positions by rotation around the first axis on the balance-spring body, and in which materials having coefficients of expansion different thermal are joined in a direction intersecting the second axis, as well as a weight forming part which is attached to the bimaterial part so as to be movable in a second axial direction along the second axis.
    CH 714 857 A2
    [2]
    2. Thermocompensated balance spring according to claim 1, in which the balance spring body comprises the balance shaft, and a balance wheel which comprises a serge surrounding the balance shaft from an exterior in a first orthogonal radial direction. to the first axis and which is attached to the balance shaft, the adjustment unit extending from the clamp.
    [3]
    3. Thermocompensated balance spring according to claim 1 or 2, in which the counterweight part comprises a fixed part which is fixed to the bi-material part, and a movable part which is attached to the fixed part, so as to be movable according to the second axial direction.
    [4]
    4. Thermocompensated balance spring according to one of claims 1 to 3, in which the bimaterial part extends in cantilever from the balance spring body, the weight forming part being attached to one end of the end of the bi-material part.
    [5]
    5. Thermocompensated balance spring according to one of claims 1 to 4, in which the adjustment unit is carried by the balance spring body so as to have an adjustable orientation around the second axis.
    [6]
    6. Thermocompensated balance spring according to one of claims 1 to 5, wherein the balance spring is made of a constant elastic material.
    [7]
    7. Thermocompensated balance spring according to one of claims 1 to 6, in which a center of the bimaterial part is positioned on the second axis.
    [8]
    8. Movement comprising a thermocompensated balance-spring according to one of claims 1 to 7.
    [9]
    9. Timepiece comprising a balance-spring according to claim 8.
    类似技术:
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    同族专利:
    公开号 | 公开日
    JP2019158844A|2019-09-19|
    CN110275419A|2019-09-24|
    CN110275419B|2022-02-08|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US168583A|1875-08-11|1875-10-11|Improvement in compensation-balances for watches |
    GB256953A|1925-08-13|1927-02-17|Paul Ditisheim|Improvements in regulating-devices for clockwork mechanism|
    CH691748A5|2000-11-16|2001-09-28|Leschot Sa|Barrel ratchet drive mechanism for watch has moving intermediate pinion to disengage wolf's teeth wheel from barrel during manual winding|
    EP1805565B1|2004-10-26|2010-09-15|TAG Heuer SA|Wristwatch regulating member and mechanical movement comprising one such regulating member|
    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|
    EP3217229B1|2016-03-07|2020-01-01|Montres Breguet S.A.|Adjustable auxiliary thermal compensation system|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    JP2018050030A|JP2019158844A|2018-03-16|2018-03-16|Temperature compensating balance, movement, and watch|
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