CN108375891A - Temperature compensating type hair-spring balance, movement and clock and watch - Google Patents

Abstract

It is excellent that the present invention provides temperature compensating type hair-spring balance, movement and clock and watch, temperature-compensating performance.Temperature compensating type hair-spring balance has：Hair-spring balance main body has the balance staff (61) extended along the 1st axis (O1), and is rotated around the 1st axis (O1) by the power of balance spring (63)；With adjustment section (100), it is extended around the position of the 1st axis (O1) rotational symmetry respectively along the 2nd axis (O2) from hair-spring balance main body, and adjustment is configured to around the position of the 2nd axis (O2), the adjustment section is with bimetal leaf (121) made of the different material of coefficient of thermal expansion is laminated on the direction intersected with the 2nd axis (O2).

Description

Temperature-compensated balance-spring balances, movements and timepieces

technical field

The invention relates to a temperature-compensated balance with hairspring, a movement and a timepiece.

Background technique

A balance with hairspring that functions as a governor of a mechanical timepiece includes: a balance shaft extending along an axis; a balance wheel fixed to the balance shaft; and a hairspring. The balance shaft and the balance wheel periodically rotate (vibrate) forward and backward around the axis as the balance spring expands and contracts.

For the above-mentioned balance with hairspring, it is important to set the vibration period within a predetermined value. If the vibration period deviates from the specified value, the rate of the mechanical timepiece (the speed of the timepiece) will change.

The vibration period T of the balance with hairspring is expressed by the following equation (1). In formula (1), I represents the "moment of inertia" of the balance with hairspring, and K represents the "spring constant" of the hairspring.

【Equation 1】

According to the formula (1), when the moment of inertia I of the balance with hairspring or the spring constant K of the balance with hairspring changes due to temperature change, etc., the vibration period T of the balance with hairspring changes. Specifically, there are cases where the above-mentioned balance wheel is formed of a material with a positive coefficient of thermal expansion (a material that expands due to an increase in temperature). In this case, when the temperature rises, the diameter of the balance wheel expands, and the moment of inertia I increases. On the other hand, there are cases where the hairspring is formed of a material having a negative temperature coefficient of Young's modulus (for example, a steel material). In this case, when the temperature rises, the spring constant K decreases.

Therefore, as the temperature rises, the moment of inertia I increases or the spring constant K decreases, whereby the vibration period T becomes longer. As a result, the vibration period T of the balance with hairspring becomes shorter at low temperature and longer at high temperature, whereby the temperature characteristic of the timepiece becomes faster at low temperature and slower at high temperature.

Therefore, as a measure for improving the temperature dependence of the oscillation period T, it may be considered to use a constant elastic material (for example, a cobalt-Ellingval constant elastic alloy, etc.) for the material of the hairspring. It is considered that by using a constant elastic material, fluctuations in the spring constant K accompanying temperature changes can be suppressed, thereby suppressing the temperature dependence of the vibration period T. However, in order to suppress fluctuations in the temperature coefficient of Young's modulus, strict manufacturing control is required, and there is a problem that it is difficult to manufacture the hairspring.

On the other hand, as a measure for improving the temperature dependence of the vibration period T, a configuration in which a bimetal is provided at a rotationally symmetrical position on the balance wheel may also be considered. Bimetal sheets are formed by laminating sheets with different thermal expansion rates.

According to this configuration, when the temperature rises, the bimetal is deformed, for example, radially inward due to the difference in the coefficients of thermal expansion of the plates. As a result, the average diameter of the balance wheel is reduced, and the moment of inertia I can be reduced. As a result, the temperature characteristic of the moment of inertia I can be corrected, and the temperature dependence of the vibration period T can be suppressed.

Furthermore, for example, Patent Document 1 below discloses a structure in which the effective length of each bimetal (the amount of protrusion from the balance wheel) can be changed to change the temperature coefficient correction amount (the current diameter of the bimetal against a change in temperature). upward change). According to this configuration, it is considered that by adjusting the effective length of each bimetal according to the temperature coefficient of Young's modulus, it is easy to eliminate the variation in the temperature coefficient of Young's modulus according to the temperature characteristic of moment of inertia I.

Patent Document 1: Specification of British Patent No. 256953

However, in the structure of the above-mentioned patent document 1, there exists a problem that it is difficult to make the effective length of each bimetallic piece uniform. If the effective lengths of the individual bimetallic plates are different, the center of gravity of the balance with hairspring is offset relative to the axis of rotation. As a result, the balance with hairspring is biased (piece weight り), and the fluctuation of the vibration period T due to the posture of the balance with hairspring becomes large (a so-called posture difference occurs).

In addition, when a constant elastic material is used as the material of the hairspring, the temperature coefficient of Young's modulus may fluctuate to be positive or negative depending on processing conditions in the hairspring manufacturing process (for example, melting or heat treatment).

However, in the conventional balance with hairspring including a bimetallic piece, the temperature coefficient of the moment of inertia I (inclination of the temperature characteristic) can only be adjusted to either positive or negative.

Contents of the invention

The present invention has been made in consideration of the above circumstances, and an object of the present invention is to provide a high-quality temperature-compensated balance with hairspring, a movement, and a timepiece excellent in temperature compensation performance.

In order to solve the above-mentioned problems, a temperature-compensated balance with hairspring according to an aspect of the present invention includes: a balance with hairspring main body having a balance shaft extending along a first axis and rotating about the first axis by power of a hairspring; and Adjusting parts extending from positions on the body of the balance with hairspring that are rotationally symmetrical about the first axis along the second axis respectively, and configured to be capable of adjusting positions around the second axis, the adjusting parts It has a bimetal sheet formed by laminating materials with different coefficients of thermal expansion in a direction intersecting the second axis.

According to this aspect, the average diameter of the main body of the balance with hairspring changes due to the deformation of the bimetallic piece as the temperature changes. Thereby, the temperature characteristic of the moment of inertia can be corrected.

In particular, in this aspect, since the position of the adjustment part is adjustable around the second axis, the orientation of the bimetal strip can be changed in accordance with the temperature coefficient of Young's modulus of the hairspring. Thereby, the temperature coefficient correction amount of the bimetal strip can be changed to both positive and negative, and the temperature coefficient of the moment of inertia of the balance with hairspring can be corrected to both positive and negative. That is, it is easy to eliminate the variation in the temperature coefficient of Young's modulus according to the temperature characteristic of the moment of inertia of the balance with hairspring. As a result, the vibration period of the balance with hairspring can be kept constant, and a balance with hairspring excellent in temperature compensation characteristics can be provided.

Furthermore, in this form, even if the orientation of the bimetal is changed, the length of the adjustment part in the second axis direction is maintained constant. Therefore, it is possible to prevent the center of gravity of the balance with hairspring from shifting at a predetermined temperature (ordinary temperature (for example, about 23° C.)) unlike conventionally changing the effective length of the bimetallic strip. As a result, it is possible to suppress the occurrence of biased weighting and reduce the difference in posture.

In the above aspect, the balance wheel body with hairspring may include: the balance shaft; and a balance wheel attached to the balance shaft, which has The rim portion of the balance shaft, the adjustment portion is extended from the rim portion.

According to this aspect, since the adjustment part is provided on the rim part of the balance, the adjustment part can be separated from the first axis in the first radial direction. Thus, the amount of radial deformation of the adjustment portion (in the first radial direction, the distance between the end portion of the adjustment portion and the first axis at a predetermined temperature, and the distance between the end portion of the adjustment portion and the first axis when the temperature changes) can be increased. 1 axis distance difference), so that the temperature coefficient correction amount based on the bimetal can be increased.

In the above aspect, the adjustment portion may be arranged inside the rim portion in a plan view viewed from the first axis direction, and may extend along a tangential direction of the rim portion.

According to this aspect, not only can the enlargement of the balance with hairspring accompanying the addition of the adjustment part be suppressed, but also the amount of radial deformation accompanying the temperature change can be ensured.

In the above aspect, the bimetal may be arranged at a position different from that of the rim portion in the first axis direction.

According to this aspect, when the adjustment part deforms in the first radial direction due to temperature changes, interference between the rim part and the adjustment part can be suppressed, and the amount of radial deformation of the adjustment part can be ensured.

In the above aspect, the adjustment part may include a weight part.

According to this aspect, since the weight of the adjustment part can be increased, the temperature coefficient correction amount by a bimetal can be increased.

In the above aspect, a through hole may be formed in the main body of the balance wheel with hairspring, the through hole passing through the main body of the balance wheel with hairspring in the direction of the second axis, the adjustment part may include a fixing part, and the fixing part may be provided with a fixing part. The part is located on one side of the second axis direction with respect to the bimetal, and is fitted in the through hole, and the side of the fixing part facing the one side in the second axis direction A locking portion for tool locking is formed on the end surface.

According to this aspect, the tool can be passed through the through hole and locked to the locking part of the fixing part. Therefore, the position adjustment of the adjustment part around the second axis can be easily performed. In addition, by changing the rotation angle of the adjustment part through the fixed part, it is possible to prevent the adjustment part from being damaged when the position of the adjustment part is adjusted, compared with the case where the rotation angle of the adjustment part is changed through the terminal part (bimetal or weight part). Plastic deformation of the adjustment part. Therefore, it is possible to suppress occurrence of variation in differential rate at a predetermined temperature due to plastic deformation of the adjustment portion.

In the above aspect, the adjustment portion may extend in a cantilever manner along the second axis.

According to this aspect, the amount of radial deformation accompanying a temperature change can be ensured, and the amount of temperature coefficient correction by the bimetal can be increased.

In the above manner, the hairspring may be formed of a constant elastic material.

According to this aspect, it is possible to reduce the change in Young's modulus accompanying the temperature change, thereby suppressing the temperature dependence of the vibration cycle. Furthermore, in this form, since the variation in the temperature coefficient of Young's modulus can be corrected by using the rotation angle of the adjustment part, the manufacturing management at the time of manufacturing the hairspring becomes easy. Therefore, not only can the manufacturing efficiency of the hairspring be improved, but also the cost can be reduced.

In the above aspect, the center of gravity of the adjustment unit may be located on the second axis.

According to this aspect, since the center of gravity of the adjustment part is located on the second axis, when the position of the adjustment part around the second axis is adjusted, it is possible to prevent the center of gravity of the adjustment part from shifting from the second axis according to the rotation angle of the adjustment part. Offset situation. As a result, it is possible to prevent the center of gravity of the balance with hairspring from being shifted in accordance with the rotation angle of the adjustment unit, so that the posture difference can be reliably reduced.

A movement according to one aspect of the present invention may include the temperature-compensated balance with hairspring of the above-mentioned aspect.

A timepiece according to one aspect of the present invention may include the movement of the above-mentioned aspect.

According to this aspect, since the above-mentioned temperature-compensated balance with hairspring according to this aspect is provided, it is possible to provide a high-quality movement and timepiece with less variation in the differential rate.

According to the present invention, it is possible to provide a high-quality temperature-compensated balance with hairspring, a movement, and a timepiece excellent in temperature compensation performance.

Description of drawings

FIG. 1 is an external view of a timepiece according to a first embodiment.

Fig. 2 is a plan view of the movement of the first embodiment seen from the front side.

3 is a plan view of the balance with hairspring according to the first embodiment viewed from the front side.

Fig. 4 is a side view of the balance with hairspring according to the first embodiment.

Fig. 5 is a sectional view corresponding to line V-V in Fig. 3 .

Fig. 6 is a cross-sectional view along line VI-VI of Fig. 3 .

Fig. 7 is a partial plan view of the balance with hairspring for explaining the operation of the adjustment unit.

FIG. 8 is an enlarged cross-sectional view showing the adjustment unit in a state where the adjustment unit is at a reference position.

FIG. 9 is an enlarged cross-sectional view showing the adjustment unit in a state where the rotation angle θ of the adjustment unit is 45 (deg).

FIG. 10 is an enlarged cross-sectional view showing the adjustment unit in a state where the rotation angle θ of the adjustment unit is 90 (deg).

Fig. 11 is an enlarged cross-sectional view showing the adjustment unit in a state where the rotation angle θ of the adjustment unit is -45 (deg).

Fig. 12 is an enlarged cross-sectional view showing the adjustment unit in a state where the rotation angle θ of the adjustment unit is -90 (deg).

13 is a graph showing the relationship between the orientation of the bimetal and the amount of deformation of the bimetal when the rotation angle θ of the adjustment part is changed between -90 (deg) to 90 (deg). picture.

14 is a graph showing the relationship between the rotation angle θ of the adjustment unit and the amount of change in radius ΔR.

15 is a graph showing the relationship between temperature (° C.) and differential rate when the temperature coefficients of Young's modulus of hairsprings are different.

Fig. 16 is a perspective view of a balance with hairspring according to a second embodiment.

Fig. 17 is a plan view of a balance with hairspring according to a modified example viewed from the front side.

FIG. 18 is a cross-sectional view corresponding to FIG. 6 of a modified example.

Fig. 19 is a partial plan view of a balance with hairspring according to a modified example.

Label description

1: Clock;

2: movement;

54: balance with hairspring;

61: swing shaft;

62: balance wheel;

73: rim portion;

100: adjustment department;

115: mounting hole (through hole);

117: working hole (through hole);

120: fixed part;

121: bimetallic sheet;

122: Weight Department;

135: locking department;

202: supporting part;

205: installation hole (through hole).

Detailed ways

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(first embodiment)

[clock]

FIG. 1 is an external view of a timepiece 1 . In addition, in each of the figures shown below, in order to make the drawings easier to see, the illustration of some of the timepiece components is omitted, and each of the timepiece components is shown in simplified form.

As shown in FIG. 1 , a timepiece 1 according to the present embodiment is constituted by incorporating a movement 2 or a dial 3 , various hands 4 to 6 , and the like into a timepiece case 7 .

The timepiece case 7 includes a case body 11 , a case cover (not shown), and a cover glass 12 . A crown 15 is provided at the 3 o'clock position (right side in FIG. 1 ) on the side of the case main body 11 . The crown 15 is used to operate the movement 2 from the outside of the case main body 11 . The crown 15 is fixed to an arbor 19 , and the arbor 19 is inserted into the case main body 11 .

[movement]

FIG. 2 is a plan view of the movement 2 viewed from the front side.

As shown in FIG. 2 , the movement 2 is configured by rotatably supporting a plurality of gear bodies and the like on a bottom plate 21 constituting a base plate of the movement 2 . In addition, in the following description, with respect to the bottom plate 21, the cover glass 12 side (dial 3 side) of the timepiece case 7 is referred to as the "back side" of the movement 2, and the case cover side (opposite to the dial 3 side) is referred to as "back side" of the movement 2. side) is referred to as the "front side" of the movement 2. In addition, each gear body described below is provided with the front and back directions of the movement 2 as the axial direction.

The above-mentioned stem 19 is assembled on the bottom plate 21 . Stem 19 is used for date or time correction. The stem 19 is rotatable about its axis and movable in the axial direction. The position of the handle shaft 19 in the axial direction is determined by a switching device, and the switching device has a pull gear 23 , a clutch lever 24 , a clutch lever spring 25 and a pull lever compression spring 26 .

When the stem 19 is rotated, the vertical wheel 31 is rotated by the rotation of a clutch wheel (not shown). With the rotation of the vertical wheel 31 , the small steel wheel 32 and the large steel wheel 33 rotate sequentially, thereby winding up a mainspring (not shown) accommodated in the barrel wheel 34 .

The barrel wheel 34 is rotatably supported between the bottom plate 21 and the barrel support 35 . The second wheel 41 , the third wheel 42 , and the fourth wheel 43 are rotatably supported between the base plate 21 and the wheel train support 45 .

When the barrel 34 is rotated by the restoring force of the mainspring, the second wheel 41 , the third wheel 42 , and the fourth wheel 43 are sequentially rotated due to the rotation of the barrel 34 . The barrel wheel 34 , the second wheel 41 , the third wheel 42 and the fourth wheel 43 constitute a front wheel train.

The minute hand 5 (see FIG. 1 ) is attached to the second wheel 41 of the above-mentioned front wheel train. The above-mentioned hour hand 4 is attached to an hour wheel (not shown) that rotates with the rotation of the second wheel 41 . In addition, the second hand 6 (see FIG. 1 ) is configured to rotate based on the rotation of the fourth wheel 43 .

A speed regulating escapement 51 is mounted on the movement 2 .

The governor escapement 51 has an escape wheel 52 , a pallet fork 53 , and a balance with hairspring (temperature compensation type balance with hairspring) 54 .

The escape wheel 52 is rotatably supported between the bottom plate 21 and the train wheel support 45 . The escape wheel 52 rotates with the rotation of the fourth wheel 43 .

The pallet fork 53 is supported reciprocally and rotatably between the bottom plate 21 and the pallet fork bridge 55 . The pallet fork 53 includes a pair of pallet stones 56a, 56b. The pallet stones 56a and 56b alternately engage with the escape gear 52a of the escape wheel 52 as the pallet 53 reciprocates. When one of the pair of pallet stones 56a, 56b engages with the escape gear 52a, the escape wheel 52 temporarily stops rotating. In addition, when the pair of pallet stones 56a, 56b are disengaged from the escape gear 53a, the escape wheel 52 rotates. By continuously repeating these operations, the escape wheel 52 rotates intermittently. Then, the above-mentioned gear train (front side gear train) is intermittently operated by the intermittent rotational movement of the escape wheel 52, thereby controlling the rotation of the front side gear train.

＜Balance with Hairspring＞

FIG. 3 is a plan view of the balance with hairspring 54 viewed from the front side. FIG. 4 is a side view of the balance with hairspring 54 .

As shown in Fig. 3 and Fig. 4, the balance wheel 54 with hairspring regulates the speed of the escape wheel 52 (makes the escape wheel 52 escape at a fixed speed.). The balance with hairspring 54 mainly has a balance shaft 61 , a balance 62 and a hairspring 63 .

As shown in FIG. 4 , the balance shaft 61 is rotatably supported between the bottom plate 21 and the balance bridge 65 around the first axis O1. In the following description, there are cases where the direction along the first axis O1 is referred to as the first axis direction, the direction perpendicular to the first axis O1 is referred to as the first radial direction, and the direction that rotates around the first axis O1 The direction is called the first circumferential direction. In this case, the first axis direction coincides with the front and back directions.

The balance shaft 61 rotates forward and backward at a fixed vibration cycle around the first axis O1 by power transmitted from the hairspring 63 . The end portion on the front side in the first axis direction of the balance shaft 61 is supported by the balance bridge 65 via a bearing (not shown). The rear side end in the first axial direction of the balance shaft 61 is supported by a bearing (not shown) formed on the bottom plate 21 .

A double disc 67 is fitted on the back side end portion of the balance shaft 61 in the first axis direction. The double disc 67 is formed in a cylindrical shape arranged coaxially with the first axis O1. A disc nail 68 is provided on a part of the double disc 67 in the first circumferential direction. The disc pin 68 repeatedly engages and disengages from the pallet case of the pallet 53 in synchronization with the reciprocating rotation of the balance with hairspring 54 . Accordingly, by reciprocating the pallet fork 53 , the pallet stones 56 a , 56 b are repeatedly engaged and disengaged from the escape wheel 52 .

Fig. 5 is a sectional view corresponding to line V-V in Fig. 3 .

As shown in FIGS. 3 and 5 , the balance wheel 62 is fixed on the front side in the first axis direction with respect to the double disk 67 on the balance shaft 61 . The balance wheel 62 mainly includes a hub portion 71 , spoke portions (みみだ portion) 72 , and a rim portion 73 . In this embodiment, the hub portion 71, the spoke portion 72, and the rim portion 73 are integrally formed of a metal material (for example, brass or the like).

The hub portion 71 is fixed to the balance shaft 61 by press fitting or the like.

The spoke portion 72 is provided to protrude outward in the first radial direction from the hub portion 71 . In the present embodiment, the spoke portion 72 is protrudingly provided from a position where the first axis O1 in the hub portion 71 is sandwiched and opposed in the first radial direction. However, the protruding position, the number, and the like of the spoke portions 72 can be changed appropriately.

The rim portion 73 is formed in an annular shape arranged coaxially with the first axis O1. The rim portion 73 surrounds the hub portion 71 from the outside in the first radial direction. The outer end portion in the first radial direction of the spoke portion 72 is connected to the inner peripheral surface of the rim portion 73 .

The balance spring 63 is a spiral balance spring in a plan view viewed from the first axis direction. The hairspring 63 is wound along the Archimedes curve. The inner end of the balance spring 63 is connected to the balance shaft 61 via a collet 75 . The outer end of the balance spring 63 is connected to the balance bridge 65 through a stud (not shown). The hairspring 63 plays a role of accumulating power transmitted from the fourth wheel 43 to the escape wheel 52 and transmitting the power to the balance shaft 61 .

In the present embodiment, a constant elastic material (for example, cobalt-Ellingval constant elastic alloy, etc.) is suitably used for the balance spring 63 . The Young's modulus of the hairspring 63 in the operating temperature range is a positive temperature characteristic. In this case, the temperature coefficient of the Young's modulus of the hairspring 63 is adjusted so that the vibration period of the balance with hairspring 54 becomes as constant as possible with respect to the temperature characteristic of the moment of inertia of the balance 62 accompanying temperature changes. However, the hairspring 63 may also be formed of a material other than the constant elastic material. In this case, a general steel material having a Young's modulus with a negative temperature coefficient (a property in which the spring constant decreases due to an increase in temperature) can be used as the hairspring 63 .

Here, the balance with hairspring 54 of this embodiment has a pair of adjustment parts 100 at positions on the balance 62 that are rotationally symmetrical about the first axis O1 (in this embodiment, quadratically symmetrical).

In addition, the object of rotation mentioned here is an example of an expression for giving characteristics to figures, and the following properties as well-known concepts are called n-fold symmetry, n-phase symmetry, or (360/n)-degree symmetry, etc., wherein the Specifically, the property is a property that coincides with itself when n is an integer of 2 or greater and rotates (360/n)° around a certain center (in the case of a 2-dimensional figure) or an axis (in the case of a 3-dimensional figure). For example, in the case of n=2, it becomes a double symmetry that overlaps with itself when rotated by 180°. Each adjustment portion 100 is formed in a rod shape extending along a second axis O2 parallel to a tangent to the rim portion 73 . Each adjustment part 100 is supported by a pair of support parts 110 connected to the rim part 73, respectively. Since each adjustment part 100 and support part 110 are mutually equivalent structures, in the following description, one adjustment part 100 and support part 110 are demonstrated as an example. In addition, in the following description, there are cases where the direction along the second axis O2 is referred to as the second axis direction, the direction perpendicular to the second axis O2 is referred to as the second radial direction, and the direction around the second axis O2 is referred to as the second radial direction. The direction of rotation is called the second circumferential direction.

FIG. 6 is a cross-sectional view along line VI-VI of FIG. 3 .

The support portion 110 bulges inward in the first radial direction from the inner peripheral surface of the rim portion 73 . An attachment hole (through hole) 115 penetrating through the support portion 110 in the second axis direction is formed in the support portion 110 . The attachment hole 115 is formed in a circular shape (perfect circular shape) in plan view viewed from the second axis direction. Furthermore, the shape of the mounting hole 115 is not limited to a circular shape, and may be a rectangular shape, a triangular shape, or the like.

A slot 116 communicating with the inside of the attachment hole 115 is formed in a portion of the support portion 110 located on the back side in the first axial direction. The slit 116 is formed over the entire support portion 110 in the second axis direction.

As shown in FIG. 4 , in the rim portion 73 , a working hole (through hole) 117 penetrating the rim portion 73 in the second axis direction is formed at a portion overlapping the mounting hole 115 when viewed from the second axis direction. The working hole 117 is configured so that a tool not shown (for example, a flat-head screwdriver, etc.) can be inserted.

As shown in FIG. 3 , the adjustment unit 100 is cantilever-supported by the support unit 110 inside the rim portion 73 . Specifically, the adjustment part 100 is formed such that the fixed part 120 , the bimetal 121 and the weight part 122 are sequentially connected from the base end side (fixed end side) to the distal end side (free end side) in the second axis direction.

As shown in FIG. 6 , the fixing portion 120 is formed of, for example, a metal material. The fixing portion 120 is formed in a circular shape in a plan view viewed from the second axis direction corresponding to the above-mentioned attachment hole 115 . The fixing portion 120 is press-fitted (elastically held) into the aforementioned mounting hole 115 . In addition, the fixing portion 120 may be press-fitted so as to straddle the mounting hole 115 and the working hole 117 .

In this embodiment, the amount of interference between the fixing portion 120 and the mounting hole 115 is set to such an extent that when a predetermined rotation is applied to the adjustment portion 100 about the second axis O2 (in the second circumferential direction), In the case of torque, the adjustment unit 100 can rotate around the second axis O2. That is, the adjustment unit 100 of the present embodiment is configured to be able to adjust the adjustment unit by rotating the adjustment unit around the second axis O2 while sliding the outer peripheral surface of the fixing unit 120 on the inner peripheral surface of the attachment hole 115 . The position around the second axis O2.

In addition, the cross-sectional shape of the fixing part 120 is not limited to a circular shape, and may be a rectangular shape, a triangular shape, or the like. In addition, in this embodiment, the case where the cross-sectional shape of the fixing part 120 is formed corresponding to the mounting hole 115 has been described, however, as long as the fixing part 120 is configured to be rotatable around the second axis O2, the fixed The portion 120 and the mounting hole 115 may have different shapes from each other.

As shown in FIG. 4 , a locking portion 135 is formed on a proximal end surface in the second axial direction of the fixing portion 120 . The locking portion 135 is a groove extending linearly along the second radial direction. A tool is inserted into the locking portion through the working hole 117 . In addition, the locking part 135 is not limited to a groove as long as it can be locked with a tool.

As shown in FIG. 3 , the bimetal 121 is joined (for example, welded or bonded) to the end surface of the fixing portion 120 in the direction of the second axis. The bimetal 121 is formed in a plate shape linearly extending in the second axial direction on the inside of the rim portion 73 in the first radial direction. The bimetallic sheet 121 is formed by superimposing two plate materials (low expansion member 130 and high expansion member 131 ) having different coefficients of thermal expansion in the second radial direction. In the present embodiment, for the low expansion member 130, invar (Ni—Fe alloy), silicon, ceramics, or the like is appropriately used. For the high expansion member 131, copper or a copper alloy, aluminum, or the like is suitably used. The low-expansion member 130 and the high-expansion member 131 are formed in the same shape (the cross-sectional shape perpendicular to the second axis O2 is rectangular). In the illustrated example, the boundary portion between the low-expansion member 130 and the high-expansion member 131 is located on the second axis O2. Furthermore, it is preferable that the center of gravity of each adjustment part 100 is located on the second axis O2, respectively. Therefore, the plate thicknesses of the low-expansion member 130 and the high-expansion member 131 may be different from each other (the plate thickness can be appropriately changed). When the plate thicknesses of the low expansion member 130 and the high expansion member 131 are different, the boundary portion between the low expansion member 130 and the high expansion member 131 extends parallel to the second axis O2.

The bimetal 121 (the low-expansion member 130 and the high-expansion member 131 ) is configured such that the orientation of the bimetal in the second radial direction can be changed as the adjustment unit 100 rotates around the second axis O. The bimetal 121 is configured to be deformable in the second radial direction as the temperature changes by utilizing the difference in thermal expansion coefficient between the low-expansion member 130 and the high-expansion member 131 . In addition, the specific operation of the bimetal 121 will be described later.

As shown in FIG. 3 , the weight portion 122 is joined (for example, welded or bonded) to the end surface of the bimetal 121 in the direction of the second axis. The weight portion 122 is formed of, for example, a metal material. The weight portion 122 has a circular cross-sectional shape perpendicular to the second axis O2. The outer shape of the weight part 122 is larger than that of the bimetal 121 in a front view viewed from the direction of the second axis. Furthermore, the weight portion 122 may be detachably attached to the bimetal 121 .

[temperature correction method]

Next, a method of adjusting the temperature coefficient correction amount in the balance with hairspring 54 described above will be described. FIG. 7 is a partial plan view of the balance with hairspring 54 for explaining the operation of the adjustment unit 100 . In the state of FIG. 7 , the low expansion member 130 and the high expansion member 131 are aligned in the first radial direction with the low expansion member 130 located inside the bimetal 121 in the first radial direction.

As shown in FIG. 7 , in the balance with hairspring 54 of this embodiment, when a temperature change occurs, the bimetal 121 bends and deforms due to the difference in thermal expansion coefficient between the low-expansion member 130 and the high-expansion member 131 . Specifically, when a temperature rise occurs from a predetermined temperature T0 (normal temperature (for example, about 23° C.)), the high expansion member 131 expands more than the low expansion member 130 . As a result, the adjustment unit 100 is deformed toward one side in the lamination direction of the low-expansion member 130 and the high-expansion member 131 (inward in the first radial direction in FIG. 7 ). When the temperature drops from the predetermined temperature T0, the high-expansion member 131 contracts more than the low-expansion member 130 . As a result, the adjustment unit 100 is deformed to the other side in the stacking direction (the first radial direction outer side in FIG. 7 ).

By deforming the adjustment part 100, the distance between the tip part of the adjustment part 100 and the first axis O1 in the first radial direction changes. Specifically, when a predetermined temperature T0 is set, the distance between the end portion of the adjustment unit 100 and the first axis O1 in the first radial direction is R0, and when the temperature changes, the distance between the end portion of the adjustment unit 100 and the first axis O1 is R0. When the distance of O1 in the first radial direction is R1, the difference between the distance R0 and the distance R1 becomes the radius change amount ΔR in the first radial direction. In addition, the average diameter of the balance wheel 62 can be reduced or increased in accordance with the amount of change in radius ΔR, whereby the moment of inertia about the first axis O1 of the balance wheel with hairspring 54 can be changed. That is, when the temperature rises, the average diameter of the balance wheel 62 can be reduced to reduce the moment of inertia. When the temperature is lowered, the average diameter of the balance wheel 62 can be enlarged to increase the moment of inertia. Accordingly, the temperature coefficient of the moment of inertia can be corrected.

However, when a constant elastic material is used for the hairspring 63 as in the present embodiment, the temperature coefficient of Young's modulus may vary positively or negatively depending on the processing conditions in the hairspring manufacturing process (for example, melting or heat treatment). possibility.

In contrast, in the present embodiment, the orientation of the bimetal 121 (rotation angle θ around the second axis O2 ) can be changed in accordance with the temperature coefficient of Young's modulus of the hairspring 63 . Specifically, a tool is passed through the working hole 117 and locked in the locking portion 135 of the adjustment unit 100 shown in FIG. 4 . Then, by rotating the tool around the second axis O2, the adjustment part 100 is rotated around the second axis O2 while sliding the outer peripheral surface of the fixing part 120 on the inner peripheral surface of the attachment hole 115 . Thus, the rotation angle θ is changed.

8 to 12 are enlarged cross-sectional views of the adjustment unit 100 .

In the state shown in FIG. 8 , the low-expansion member 130 is located on the front side in the first axial direction in a state where the low-expansion member 130 and the high-expansion member 131 are aligned in the first axial direction. Using this state as the reference position (0 (deg)) of the adjustment unit 100 , the rotation angle θ around the second axis O2 is adjusted. For example, in FIG. 9 , the adjustment unit 100 is rotated by 45 (deg) in the clockwise direction (+ direction) around the second axis O2 from the reference position. In FIG. 10 , the adjustment unit 100 is rotated by 90 (deg) in the clockwise direction (+ direction) around the second axis O2 from the reference position.

In FIG. 11 , the adjuster 100 is rotated by -45 (deg) in the counterclockwise direction (-direction) around the second axis O2 from the reference position. In FIG. 12 , the adjuster 100 is rotated by -90 (deg) in the clockwise direction (-direction) around the second axis O2 from the reference position.

FIG. 13 shows the orientation of the bimetal 121 and the relationship between the orientation of the bimetal 121 and the rotation angle θ of the adjustment part 100 in the range of -90 (deg) to 90 (deg) at the same temperature (at high temperature). 121 is a graph of the relationship between the amount of deformation. In FIG. 13 , the X axis represents a component along the first radial direction (hereinafter, referred to as an X component) of the deformation vector of the bimetal 121 . In addition, the Y axis represents a component (hereinafter, referred to as a Y component) along the first axis direction of the deformation vector of the bimetal 121 . In this case, in FIG. 13 , the -X direction coincides with the inner side of the first radial direction, and the +X direction coincides with the outer side of the first radial direction. In addition, in FIG. 13 , the bimetal 121 located at the origin shows the state at a predetermined temperature T0 (before deformation).

As shown in FIG. 13 , when the adjustment unit 100 is at the reference position (0 (deg)), the bimetal 121 deforms only toward the front side in the first axis direction (A1 in FIG. 13 ). Therefore, at the reference position, the Y component of the deformation vector of the bimetal 121 becomes the largest, and the X component becomes zero. In this case, the radius change amount ΔR is 0, so the temperature coefficient of the moment of inertia does not change.

When the adjusting part 100 is rotated in the + direction from the reference position, the bimetal 121 is also deformed outward in the first radial direction, thereby generating a +X component (A2, A2 in FIG. 13 , A3). And, by increasing the rotation angle θ in the + direction, the +X component gradually becomes larger. That is, by displacing the rotation angle θ of the adjustment unit 100 in the + direction from the reference position, it is possible to increase the amount of increase in the moment of inertia of the balance with hairspring 54 when the temperature rises. Furthermore, when the rotation angle θ is 90 (deg) (A3 in FIG. 13 ), the bimetal 121 deforms only outward in the first radial direction. Therefore, when the rotation angle θ is 90 (deg), the +X component becomes the largest, and the Y component becomes 0. In this way, the temperature coefficient of the moment of inertia can be increased by rotating the adjustment unit 100 in the + direction from the reference position.

On the other hand, when the adjusting part 100 is rotated from the reference position to the − direction, the bimetal 121 is also deformed inward in the first radial direction, thereby generating a −X component in the deformation vector of the bimetal 121 ( FIG. 13 ). in A4, A5). And, by increasing the rotation angle θ in the - direction, the -X component becomes larger. That is, by displacing the rotation angle θ of the adjustment unit 100 in the − direction from the reference position, it is possible to suppress an increase in the moment of inertia of the balance with hairspring 54 when the temperature rises. Furthermore, when the rotation angle θ is 90 (deg) (A5 in FIG. 13 ), the bimetal 121 deforms only inward in the first radial direction. Therefore, when the rotation angle θ is 90 (deg), the −X component becomes the largest and the Y component becomes 0. In this way, by rotating the adjustment unit 100 from the reference position in the − direction, the temperature 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 unit 100 and the amount of change in radius ΔR.

As shown in FIG. 14 , based on the above-mentioned results in FIG. 13 , when the adjustment unit 100 is rotated in the + direction from the reference position, the radius change ΔR of the adjustment unit 100 becomes larger in the + direction (outside the first radial direction). . On the other hand, when the adjustment unit 100 is rotated in the - direction from the reference position, the radius change ΔR of the adjustment unit 100 becomes larger in the - direction (inward in the first radial direction).

FIG. 15 is a graph showing the relationship between temperature (° C.) and differential rate when the temperature coefficient of Young's modulus of hairspring 63 is different. In FIG. 15 , a dotted line G1 indicates a case where the differential (vibration period of the balance with hairspring 54 ) has a negative temperature characteristic, and a dotted line G2 indicates a case where the differential has a positive temperature characteristic.

As shown in G1 of FIG. 15 , according to the relationship between the Young's modulus of the hairspring 63 and the moment of inertia of the balance with hairspring 54, in the case where the differential has a negative temperature characteristic, the differential has a change as the temperature rises. slow tendency. In this case, the adjustment unit 100 is rotated in the - direction from the reference position. As a result, the amount of change in radius ΔR toward the inner side in the first radial direction accompanying the temperature rise can be ensured, and the temperature coefficient of the moment of inertia can be reduced. Therefore, the decrease in the moment of inertia of the balance with hairspring 54 accompanying the temperature rise can be suppressed. increase. As a result, the temperature coefficient of the vibration period of the balance with hairspring 54 is adjusted toward zero, thereby maintaining the differential rate constant regardless of temperature changes (see solid line G3 in FIG. 15 ).

On the other hand, as shown in G2 of FIG. 15 , according to the relationship between the Young's modulus of the hairspring 63 and the moment of inertia of the balance with hairspring 54, when the differential rate has a positive temperature characteristic, as the temperature rises, The difference rate has a tendency to become faster. In this case, the adjustment unit 100 is rotated in the + direction from the reference position. As a result, the amount of change in radius ΔR toward the outer side in the first radial direction accompanying the temperature rise can be ensured, and the temperature coefficient of the moment of inertia can be increased. Therefore, the moment of inertia of the balance with hairspring 54 can be increased due to the temperature rise. increase. As a result, the temperature coefficient of the vibration period of the balance with hairspring 54 is adjusted toward zero, thereby maintaining the differential rate constant regardless of temperature changes (see solid line G3 in FIG. 15 ).

By thus changing the rotation angle θ of the adjuster 100 according to the temperature characteristic of the differential rate, the temperature coefficient of the moment of inertia of the balance with hairspring 54 can be corrected to both positive and negative. This makes it easy to eliminate variations in the temperature coefficient of Young's modulus according to the temperature characteristics of the moment of inertia of the balance with hairspring 54 .

As described above, according to the present embodiment, the bimetal 121 is provided at a rotationally symmetrical position on the balance wheel 62 .

According to this structure, the bimetal 121 deforms according to the temperature change, thereby changing the average diameter of the balance wheel 62 . Thereby, the temperature characteristic of the moment of inertia can be corrected.

In particular, in the present embodiment, the adjustment unit 100 is configured to be capable of position adjustment around the second axis O2. Therefore, the orientation of the bimetal strip 121 can be changed according to the temperature coefficient of Young's modulus of the hairspring 63 . Accordingly, the temperature coefficient correction amount of the bimetal 121 can be changed to both positive and negative, and the temperature coefficient of the moment of inertia of the balance with hairspring 54 can be corrected to both positive and negative. That is, it is easy to eliminate the variation in the temperature coefficient of Young's modulus according to the temperature characteristic of the moment of inertia of the balance with hairspring 54 . As a result, the vibration cycle of the balance with hairspring 54 can be kept constant, and the balance with hairspring 54 excellent in temperature compensation characteristics can be provided.

Furthermore, in this embodiment, even if the orientation of the bimetal 121 is changed, the length of the adjustment part 100 in the direction of the second axis O2 is maintained constant. Therefore, unlike the conventional case where the effective length of the bimetal 121 is changed, it is possible to suppress the shift of the center of gravity of the balance with hairspring 54 at the predetermined temperature T0. As a result, it is possible to suppress the occurrence of biased weighting and reduce the difference in posture.

In the present embodiment, since the adjustment part 100 is provided on the rim part 73 of the balance 62, the adjustment part 100 can be moved away from the first axis O1 in the first radial direction. Accordingly, the radial deformation amount ΔR can be increased, and the temperature coefficient correction amount by the bimetal 121 can be increased.

In the present embodiment, the adjustment unit 100 is configured to be disposed inside the rim portion 73 in the first radial direction and to extend along a tangent to the rim portion 73 .

According to this structure, not only can the enlargement of the balance with hairspring 54 accompanying the addition of the adjustment part 100 be suppressed, but also the amount of radial deformation ΔR accompanying the temperature change can be ensured.

In this embodiment, since the adjustment part 100 has the weight part 122 in the terminal part, the weight of the terminal part which is the largest deformation part in the adjustment part 100 can be increased. Therefore, the temperature coefficient correction amount by the bimetal 121 can be increased.

In the present embodiment, the adjustment unit 100 extends in a cantilever manner, so the radial deformation amount ΔR accompanying the temperature change can be ensured, thereby increasing the temperature coefficient correction amount by the bimetal 121 .

In the present embodiment, since the working hole 117 is formed in the rim portion 73 , a tool can be passed through the working hole 117 and locked to the locking portion of the fixing portion 120 . Therefore, the position adjustment of the adjustment part 100 around the 2nd axis line O2 can be performed easily. Furthermore, by changing the rotation angle θ of the adjustment unit 100 through the fixing unit 120, compared with the case where the rotation angle θ of the adjustment unit 100 is changed through the terminal part (bimetal 121 or weight part 122), it is possible to suppress the Plastic deformation of the adjustment unit 100 when the position of the adjustment unit 100 is adjusted. Therefore, it is possible to suppress occurrence of variation in differential rate at a predetermined temperature T0 due to plastic deformation of the adjustment unit 100 .

In the present embodiment, the balance spring 63 is formed of a constant elastic material.

According to this configuration, it is possible to reduce the change in Young's modulus accompanying the temperature change, thereby suppressing the temperature dependence of the vibration period. Furthermore, in the present embodiment, since the variation in the temperature coefficient of Young's modulus can be corrected by using the rotation angle θ of the adjustment unit 100 , the manufacturing management at the time of manufacturing the hairspring 63 becomes easy. Therefore, not only the manufacturing efficiency of the hairspring 63 can be improved, but also the cost can be reduced.

In this embodiment, since the center of gravity of the adjustment unit 100 is located on the second axis O2, when the position of the adjustment unit 100 around the second axis O2 is adjusted, it is possible to prevent the center of gravity of the adjustment unit 100 from being adjusted by the adjustment unit 100. The case where the rotation angle θ deviates from the second axis O2. As a result, it is possible to prevent the center of gravity of the balance with hairspring 54 from shifting in accordance with the rotation angle θ of the adjustment unit 100 , so that the posture difference can be reliably reduced.

The movement 2 and the timepiece 1 according to the present embodiment include the above-mentioned balance with hairspring 54 , and therefore, it is possible to provide a high-quality movement 2 and the timepiece 1 with less variation in the differential rate.

(second embodiment)

Next, a second embodiment of the present invention will be described. FIG. 16 is a perspective view of a balance with hairspring 201 according to the second embodiment. This embodiment differs from the above-described embodiment in that the support portion 202 protrudes from the rim portion 73 in the first axis direction. In the following description, the same components as those in the above-mentioned embodiment are denoted by the same reference numerals and descriptions thereof are omitted.

In the balance with hairspring 201 shown in FIG. 16 , support portions 202 are formed at rotationally symmetrical positions of the rim portion 73 . The support portion 202 protrudes from the rim portion 73 toward the back side in the first axial direction, and protrudes inward in the first radial direction. A mounting hole 205 penetrating through the support portion 202 in the second axial direction is formed in a portion of the support portion 202 protruding inwardly in the first radial direction relative to the rim portion 73 . The fixing part 120 of the adjustment part 100 is press-fitted into each mounting hole 205, respectively.

Thus, in the present embodiment, the rim portion 73 and the adjustment portion 100 are arranged at different positions in the first axial direction. Therefore, when the adjustment part 100 deforms in the first radial direction due to temperature changes, the interference between the rim part 73 and the adjustment part 100 can be suppressed, and the radial deformation amount ΔR of the adjustment part 100 can be ensured.

In addition, the technical scope of the present invention is not limited to the above-described embodiments, and various changes can be added within a range not departing from the gist of the present invention.

For example, in the above-mentioned embodiment, the configuration in which the two adjustment parts 100 are provided at rotationally symmetrical positions of the rim part 73 has been described, but the configuration is not limited to this configuration. That is, as long as each adjustment unit 100 is installed at a rotationally symmetrical position, three or more adjustment units 100 may be provided, for example, as shown in FIG. 17 .

In the above-mentioned embodiment, the configuration in which the adjustment part 100 is rotated around the second axis O2 while sliding the outer peripheral surface of the fixing part 120 on the inner peripheral surface of the attachment hole 115 has been described, but the configuration is not limited to this configuration. That is, the adjustment unit 100 may be configured so as to be capable of position adjustment around the second axis O2. In this case, for example, as shown in FIG. 18 , a configuration may be adopted in which an external spline 120 a formed in the fixing portion 120 engages with an internal spline 115 a formed in the mounting hole 115 . According to this structure, the position of the adjustment part 100 can be adjusted around the 2nd axis|shaft O2 by fitting the fixed part 120 in the attachment hole 115 after aligning the direction of the bimetal 121.

In addition, after the position adjustment of the adjustment part 100 is performed, the adjustment part 100 may be fixed so that it cannot rotate with respect to the support part 110. As shown in FIG. As a fixing method of the adjusting part 100, welding or bonding may be used, and other fastening members (for example, fastening screws, etc.) may be used for fixing.

In the above-mentioned embodiment, the structure in which the fixing portion 120 is fitted into the mounting hole 115 has been described, but the present invention is not limited to this structure, and the method of mounting the adjustment portion 100 can be appropriately changed. For example, a convex portion formed on the rim portion 73 and a concave portion formed on the adjustment portion 100 may be fitted together.

In the above-described embodiment, the configuration in which the second axis O2 of the adjustment unit 100 extends along the tangent to the rim portion 73 has been described, but the configuration is not limited to this configuration. That is, any configuration is sufficient as long as the X component is generated in the deformation vector of the adjustment unit 100 by the deformation of the bimetal 121 accompanying the temperature change. In this case, the second axis O2 may be set to a direction intersecting the first axis direction, a direction parallel to the first axis direction, or the like.

In the above-mentioned embodiment, the structure in which the adjustment part 100 is supported by the rim part 73 via the support part 110 was demonstrated, but it is not limited to this structure. That is, what is necessary is just to install the adjustment part 100 on the part (balance body with hairspring) of the balance with hairspring 54 which rotates by the power of the hairspring 63. As shown in FIG. In this case, examples of the main body of the balance with hairspring include the balance shaft 61 or the balance 62 (the hub portion 71 or the spoke portion 72 , etc.), the double disc 67 , and the like.

In the above-mentioned embodiment, the case where the low-expansion member 130 and the high-expansion member 131 are formed of the same-shaped plate material was demonstrated, but it is not limited to this structure. For example, as shown in FIG. 19 , the low-expansion member 130 and the high-expansion member 131 may have different thicknesses from each other. In addition, the cross-sectional shape of the low-expansion member 130 and the high-expansion member 131 perpendicular to the second axis O2 is not limited to a rectangular shape, and may be appropriately modified such as a triangular shape or a semicircular shape.

In the above-mentioned embodiment, the structure in which the low-expansion member 130 and the high-expansion member 131 are stacked in the second radial direction has been described, but it is not limited to this structure. However, in this case, for example, as shown in FIG. 19 , the low-expansion member 130 which becomes thicker toward the distal end and the high-expansion member 131 which gradually becomes thinner toward the distal end may be laminated.

In the above-mentioned embodiment, the configuration in which the adjustment unit 100 extends linearly has been described, but the configuration is not limited to this configuration. As long as the adjustment unit 100 is configured to be positionally adjustable around the second axis O2, it may extend to cross the second axis direction or be formed in a corrugated shape.

In the above-mentioned embodiment, the structure in which the adjustment part 100 is extended like a cantilever has been described, but it is not limited to this structure, and the structure supported at both ends may be sufficient.

In the above-mentioned embodiment, the case where the bimetal 121 is formed over the whole between the support part 110 and the weight part 122 in the adjustment part 100 was demonstrated, but it is not limited to this structure. It is only necessary that at least a part of the adjustment unit 100 is constituted by the bimetal 121 .

In addition, the constituent elements in the above-described embodiments can be appropriately replaced with known constituent elements within the range not departing from the gist of the present invention, and the above-described modification examples can also be appropriately combined.

Claims (11)

1. a kind of temperature compensating type hair-spring balance, which is characterized in that

The temperature compensating type hair-spring balance has：

Hair-spring balance main body has the balance staff extended along the 1st axis, and turns around the 1st axis by the power of balance spring It is dynamic；With

Adjustment section, from the hair-spring balance main body around the position of the 1st Axial-rotational Symmetry respectively along the 2nd axis It is extended, and is configured to adjust around the position of the 2nd axis, the adjustment section has coefficient of thermal expansion is different Material on the direction of the 2nd Axis Cross be laminated made of bimetal leaf.

2. temperature compensating type hair-spring balance according to claim 1, which is characterized in that

The hair-spring balance main body has：

The balance staff；With

It is installed on the balance wheel of the balance staff, has from the vertical with the 1st axis the 1st radial outside and surrounds the balance staff Rim part,

The adjustment section is extended from the rim part.

3. temperature compensating type hair-spring balance according to claim 2, which is characterized in that

The adjustment section in the inside for being configured in the rim part from the vertical view from the 1st axis direction, and along The tangential direction of the rim part extends.

4. temperature compensating type hair-spring balance according to claim 2, which is characterized in that

The bimetal leaf is configured on the 1st axis direction at the position different with the rim part.

5. temperature compensating type hair-spring balance according to claim 1, which is characterized in that

The adjustment section, which has, applies weight portion.

6. temperature compensating type hair-spring balance according to claim 1, which is characterized in that

Through hole is formed in the hair-spring balance main body, the through hole penetrates through the balance spring pendulum on the 2nd axis direction Wheel body,

The adjustment section has fixed part, and the fixed part is located at the one of the 2nd axis direction relative to the bimetal leaf Side, and be embedded in the through hole,

In the fixed part towards being formed with for the locking card of tool on the end face of the side on the 2nd axis direction Determine portion.

7. temperature compensating type hair-spring balance according to claim 1, which is characterized in that

The adjustment section extends in a cantilever fashion along the 2nd axis.

8. temperature compensating type hair-spring balance according to claim 1, which is characterized in that

The balance spring is formed by parelinvar.

9. temperature compensating type hair-spring balance according to claim 1, which is characterized in that

The center of gravity of the adjustment section is located on the 2nd axis.

10. a kind of movement, which is characterized in that

The movement has the temperature compensating type hair-spring balance described in any one in claim 1 to claim 9.

11. a kind of clock and watch, which is characterized in that

The clock and watch have movement according to any one of claims 10.