JP2017146219A - Balance wheel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a balance wheel which has a high rigidity, does not easily deform by impact, and has a small number of small members, without increasing the size of a timepiece.SOLUTION: The balance wheel includes: a connection part 3 inserted in a balance staff member 2; an arm 4 connected to the connection part 3; and a rim 1 connected to the arm 4, the arm 4 having a first arm 41 and a second arm 42 in the form of truss structure.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a ten wheel used in a mechanical timepiece. More specifically, the present invention relates to a structure of a ten wheel provided with a mechanism for preventing deformation when a large impact is applied.

  As a speed control device for a mechanical timepiece, a ten wheel that performs reciprocating rotational vibration in combination with a balance spring is used. The normal structure of the ten wheel will be described below. A ring-shaped member called a rim is the main body, the rim coincides with the central axis and serves as a support shaft for the rotational reciprocating motion, and an arm formed integrally with the rim and arranged along the diameter of the rim. It is fixedly connected by a long and thin member called a flat plate. The arm is molded thinner than the thickness of the rim in order to reduce the weight of the ten wheel as much as possible by concentrating it on the rim.

  In such a normal structure, the ten wheel is likely to be deformed when a strong impact is applied particularly in the true axial direction (which is also a direction perpendicular to the ring surface of the rim). That is, as a result of the impact, there is a drawback that the flat arm may be plastically deformed into a mountain shape. When such a deformation occurs, the ten wheel is displaced and interferes (contacts) with other components that are close to each other in the timepiece movement, so that free vibration movement cannot be performed, and the timepiece may stop.

  Patent Document 1 is known as a structure capable of mitigating such an impact in the true axial direction. In Patent Document 1, the ten wheel is arranged so as to be sandwiched between two spring members, and the spring member has a circular flat plate shape larger than the diameter of the ten wheel, and is arranged radially in the radial direction. In addition, it is configured to be connected by thin members called many blades. A buffering effect is exhibited by the flexibility of the blade.

JP 2004-294438 A (page 4, FIG. 6)

  However, in the buffer structure as described in Patent Document 1, the buffer member is large, and the thickness of the timepiece increases when the spring member is placed on top and bottom of the ten wheel. Further, since the balance spring is located between the two buffer members, the structure is difficult to operate the slow and quick needles.

  In addition to the one described in Patent Document 1, in the conventional configuration, the inertia ratio of the ten wheel is determined by the initial design. Changing conditions such as the gear ratio of the train wheel and the number of beats requires a balance with a different frequency. In such cases, conventionally, a balance spring with a different size is used or a different inertia ratio is given to the balance wheel. However, it was necessary to go through troublesome procedures such as redesigning the dimensions.

  A main object of the present invention is to constitute a ten wheel having a high rigidity and being difficult to be deformed by an impact, without increasing the timepiece, with a small number of members reduced in size. Also, a secondary object is to provide a ten wheel that can adjust the inertia ratio without changing the design of the parts.

  The ten wheel of the present invention employs the following configuration in order to achieve the above object.

  A ten wheel having a connecting portion to be inserted into the tenth, an arm connected to the connecting portion, and a rim connected to the arm, wherein the arm includes a first arm and a second arm forming a truss structure. And an arm.

  By configuring in this way, the rigidity of the arm is improved by the truss structure, and deformation of the ten wheel when subjected to an impact is suppressed.

  Further, the arm may be connected to each of the rim and the connecting portion so as to be rotatable.

  By comprising in this way, the concrete truss structure which improved the rigidity of the arm can be provided.

  The rim may have a plurality of divided rims, and each of the divided rims may be connected to the arm.

  With this configuration, a basic configuration for changing the inertia ratio of the ten wheel can be obtained.

  The connecting portion has a first connecting portion and a second connecting portion that are slidable along the tenth, and the first connecting portion is connected to the first arm and is connected to the second connection. The part may be connected to the second arm.

  By configuring in this way, a more detailed configuration for changing the inertia ratio of the ten wheel can be obtained.

  By using a small number of miniaturized members, it is possible to configure a ten wheel that is highly rigid and difficult to be deformed by impact without increasing the timepiece. In addition, it is possible to provide a ten wheel capable of adjusting the inertia ratio without changing the design of the parts.

It is a perspective view of the principal part of 1st Embodiment of this invention. It is the perspective view which decomposed | disassembled a part of 1st Embodiment. FIG. 3A shows a second embodiment of the present invention, FIG. 3A is a plan view, and FIG. 3B is a cross-sectional view taken along line AA in FIG. It is a perspective view in case the 3rd Embodiment of this invention is shown and it exists in a 1st state. It is a perspective view in case the 3rd Embodiment of this invention is shown and it exists in a 2nd state.

  The present invention is to provide a ten ring having high rigidity and difficult to be deformed by an impact without providing a separate member. The ten ring includes a connecting portion to be inserted into the ten and an arm connected to the connecting portion. A rim connected to the arm, the arm having a first arm and a second arm forming a truss structure.

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

<Structure of principal part of first embodiment FIGS. 1 and 2>
A tenth embodiment of a ten wheel according to the present invention will be described with reference to FIGS. 1 and 2. FIG. 1 is a perspective view of a completed ten wheel. The rim 1 is a ring-shaped member that gives a principal inertia ratio to the ten wheel. The tenth true 2 becomes the rotation axis of the ten wheel. The upper end and the lower end are usually processed to be thin to reduce rotational friction to form a tenon, the tenon is inserted into a hole stone that is a radial bearing, and the tip is received by a stone that is a thrust bearing. In the figures of the present specification, the tenth 2 shows only the cylindrical part of the barrel.

  A connecting portion 31 and a connecting portion 32 that form two connecting portions 3 are fitted into the cylindrical portion of the tenth true 2 while maintaining an appropriate distance. The rim 1 has rim-side projections 11 at two positions symmetrical with respect to the central axis of the inner periphery (which is also the axis of the tenth true stem 2). Each of the connection portions 31 and 32 has a pair of connection portion side protrusions 30 at symmetrical positions on the outer peripheral side surface.

  Two rim-side projections 11 are provided with rim-side joints 12, two connection-portion-side projections 30 of connection portions 31 are provided with connection-portion-side joints 33, and two connection-portion 32 are similarly connected. The connecting portion side protrusion 30 is provided with a connecting portion side joint 34. The end portions of the arms 4 are coupled to the six joints.

  The arm 4 includes a first arm 41 coupled to the connection portion side joint 33 and the rim side joint 12, and a second arm coupled to the connection portion side joint 34 and the rim side joint 12. It has a triangular truss structure with the joints 33 and 34 and the rim side joint 12 as vertices.

  As a material for the rim 1 and the arm 4, a general structural material such as brass or stainless steel can be used.

  FIG. 2 is a perspective view of the ten wheel in which a part of the first arm 41 and the second arm 42 is exploded to show details of the structure of the joint portion. A pin 5 is implanted in each of the rim side protrusion 11 and the connection side joints 33, 34, and joint holes 411, 412, 421, 422 provided at the ends of the first arm 41 and the second arm 42 are , Respectively, are fitted with the pins 5. The first arm 41 extends to the connection portion 31 toward the upper side of the plane of the rim 1, and the second arm 42 extends to the connection portion 32 toward the lower side of the plane of the rim 1.

  With such a structure, the three elements that connect the first arm 41, the second arm 42, and the connecting portion 3 are positions corresponding to the two hypotenuses and the base of one triangle that is turned sideways. Will be almost occupied. Thereby, a truss structure is realized. In the truss structure, the force acting on any vertex of the triangle has little effect of bending the member that forms any side of the triangle, and mainly exerts tension or compression, so it forms any side. Even if the member to be made is thin and lightweight, it is difficult to be deformed, and there is an advantage that high rigidity and strength can be obtained. The members forming the two sides of the triangle of the truss structure are said to rotate at the joint point, but the case where they are rigidly joined is also included in the truss structure.

  As described above, the structure of the first embodiment uses a relatively small number of light-weight and small parts and symmetrically forms two truss structures on both sides of the tenth true 2, so that the tenth true 2 particularly in the axial direction. In addition to improving the rigidity of the acting force without taking an excessively complicated structure, a tenn wheel in which the weight balance around the tenth true axis was maintained was realized.

If the first arm 41 and the second 42 are respectively fixed by the joints 12, 33, and 34, the highest rigidity can be obtained. In order to obtain a fixed structure, an adhesive may be used, welding may be applied, or the pin may be crushed and assembled after assembling. On the other hand, if each arm can be rotated by each joint, for example, when an impact force with rotation is applied, a part of the force can be released by the rotation action of the joint, so that the resistance to destruction can be increased. There may be cases. In order to be able to rotate, the pin 5 and the joint holes 411, 412, 4
21 and 422 to adjust the degree of fitting.

  It is desirable from the viewpoint of the timepiece mechanism that the positions of the connecting portions 31 and 32 on the shaft of the tenth truth 2 do not move once the positions are determined. In order to fix the members to each other, application of an adhesive, welding, caulking that applies a force to the tenth true 2 from the outer side surface of the connection portions 31 and 32, or a horizontal screw (not shown) (the cylindrical surface of the connection portions 31 and 32) It is good to carry out any of the fixing by the above. When there is no need to change the distance between the connecting portions 31 and 32 as in a third embodiment described later, the connecting portion may be integrated as the connecting portion 3 without being divided into two members.

<Main part structure of 2nd Embodiment FIG. 3 (a), (b)>
A first embodiment of a ten wheel according to the present invention will be described with reference to FIGS. 3A is a plan view of the ten wheel, and FIG. 3B is an AA cross-sectional view of the arm. In the present embodiment, the rim 1 and the tenth stem 2 are substantially the same as those in the first embodiment, but the forms of the connecting portion and the arm are different. The connecting portion 3 fitted to the tenth 2 is provided with shelf portions 301, 302, and 303 protruding at different heights in the axial direction.

  Three arms 43, 44, 45 are provided on one side of the tenth truth 2. The three arms are formed, for example, by punching a thin plate-like remaining member formed by turning the rim 1 from both sides, and have a shape gathered close to each other at the arm coupling portion 13 on the rim 1 side. . As shown in FIG. 3B, each arm is bent up and down appropriately and has terminal portions 431, 441, and 451 that are slightly swollen to the side of the tenth stem 2, and each of the shelf portions 301, 302, and 303 It is fixed to the upper surface by spot welding, adhesive, fitting, screwing with a screw member, or the like.

  As shown in FIG. 3 (b), the terminal portions 431 and 451 on the side of the tenth are as shown in FIG. 3 (a) on the shelves 301 and 303 formed at the same height as the connecting portion 3. As shown in FIG. 3B, the terminal portion 441 is welded on the shelf 302 formed on the upper side of the connecting portion 3. On the other hand, the rim 1 side ends of the three arms 43, 44, 45 are close to each other at the arm coupling portion 13. Therefore, the arms 43, 44, and 45 can be regarded as forming a three-dimensional truss having a shape close to a tetrahedron along with the tenth truth 2 by being arranged along three ridges of an approximate triangular pyramid. At this time, the arm 44 can be regarded as a first arm, and the arms 43 and 45 can be regarded as a second arm.

  The three-dimensional truss structure has a characteristic that resistance to deformation is large even when an external force is applied in a direction not parallel to any of the triangular surfaces. Therefore, the structure of 2nd Embodiment has the characteristic that high rigidity is acquired with respect to the impact force from arbitrary directions by having the characteristic of a solid truss structure.

  In the present embodiment, the three arms are described as being formed by punching a thin plate-like remaining member formed by turning the rim 1 from both sides, and fixed by performing spot welding or the like with the connecting portion. However, as in the first embodiment, the rim 1 and the connection portion 3 may be provided with a rim side joint and a connection portion side joint, respectively, and the arms 43, 44, 45 may be coupled.

<Description of Third Embodiment FIG. 4 and FIG. 5>
The structure used in the first embodiment and applying the structure other than impact resistance can be described as a third embodiment, which will be described with reference to FIGS. 4 and 5. The main effect of the new is to make it possible to change or adjust the value of the inertia ratio of the ten wheel. In the present embodiment, the structure of the first embodiment is that the connecting portion is divided into a first connecting portion 31 and a second connecting portion 32, and each of them can be slid in the axial direction on the tenth, and both The interval h can be changed, and the rim 1 is previously cut along the diameter with a predetermined width and separated into divided rims 1a and 1b.

  FIG. 4 shows a state in which the third embodiment is in the first state, that is, a state in which the inertia performance factor of the ten wheel is minimized. The connecting portion 31 and the connecting portion 32 are separated from each other as much as possible on the cylindrical portion of the tenth truth, and the distance h between them is maximized. In this way, the angle formed by the arms 41 and 42 is opened, and the distance s between the divided rims 1a and 1b is minimized. Since the respective masses of the split rims 1a and 1b are close to the central axis, the inertia ratio of the ten wheels is minimized. The center of gravity of the ten wheel is kept on the central axis.

  FIG. 5 shows a state where the third embodiment is in the second state, that is, a state in which the inertia ratio of the ten wheel is maximized. The connecting portion 31 and the connecting portion 32 are made as close as possible on the cylindrical portion of the tenth true square, and the distance h between them is minimized. At this time, the angle formed by the arms 41 and 42 is reduced, and the distance s between the divided rims 1a and 1b is maximized. The respective masses of the divided rims 1a and 1b are moved away from the central axis by the same distance, and the inertia ratio of the ten wheel is maximized.

  4 and 5 show a case where the value of the inertial performance ratio of the ten wheel is the minimum and maximum extremes, but of course, it can be adjusted to an arbitrary value between the two. In order to keep the value from shifting after adjusting the inertia ratio, make sure that the sliding friction between the tenshin 2 and the connecting portions 31 and 32 is sufficiently large, and a fixing mechanism after the slide is prepared. It is sufficient to use a means (such as a horizontal screw) or adhesion after adjustment.

  For the balance spring having a constant spring constant, the cycle of the reciprocating rotational vibration becomes longer when the inertia ratio of the ten wheel is increased, and the cycle is shortened when it is decreased. The merit of being able to change the inertia ratio of the balance wheel obtained by the third embodiment is that the vibration period error caused by the variation in the machining accuracy of each part of the mechanical watch including the balance spring can be reduced between the balance wheel and the balance spring. It can be corrected after assembly.

  In addition, since the inertia ratio can be changed, the same ten wheel can be used without changing the design of the ten wheel when changing the reduction ratio, balance spring, and beat number of the train wheel of the watch. Furthermore, other ten wheels can be used for repairing the watch.

<Description of Fourth Embodiment FIG. 3B>
Based on the structure of the second embodiment described with reference to FIG. 3, it is possible to change the inertia ratio of the ten wheel. In the second embodiment, the connecting portion 3 is integrated, but as shown in FIG. 3B, the connecting portion 3 is connected to the first portion on the boundary of a one-point difference line PP parallel to the ring surface of the rim 1. By dividing the rim 1 into a divided rim as described in the third embodiment and dividing the rim 1 into a structure that can adjust the inertia ratio of the ten wheel, the rim 1 can be deformed. . In addition, what is necessary is just to change the bending angle of arms 43, 44, 45, when changing an inertial rate.

<Description of Fifth Embodiment>
In the first embodiment, since the rim-side protrusion 11 and the connection portion-side protrusion 30 are provided symmetrically on the opposite side of the rotation axis of the ten wheel, a triangular shape parallel to one plane including the rotation axis of the ten wheel is provided. A pair of planar truss structures are obtained. On the other hand, the rim side protrusions and the connection part side protrusions are arranged in three directions every 120 ° or four directions every 90 ° with respect to the rotation axis of the ten wheel, and the number of arms corresponding to the arrangement is arranged. If added, three or more truss structures such as three or four around the rotation axis of the ten wheel can be provided. By doing so, it is possible to increase the rigidity and strength against impact forces in all directions.

  In the above-described embodiment, the description has been given assuming that the truss structure is close to an isosceles triangle in which the arms are arranged in the upward direction and the downward direction with respect to the ring plane of the rim 1. For example, the first arm is the rim. It is also possible to have a truss structure with an unequal triangular shape parallel to the ring plane. As a result, the degree of freedom in designing the ten wheel can be increased.

  In addition, it is possible to obtain further different embodiments by extracting and combining the features of the above-described embodiments, or by adding other requirements.

  The present invention has great industrial applicability because the rigidity can be improved, impact resistance can be increased, and a configuration of a ten wheel that can adjust the inertial performance ratio can be provided.

DESCRIPTION OF SYMBOLS 1 Rim 11 Rim side protrusion 12 Rim side joint 1a, 1b Split rim 2 Ten true 3, 31, 32 Connection part 30 Connection part side protrusion 33, 34 Connection part side joint 301,302,303 Shelf part 4,43,44, 45 Arm 41 1st arm 42 2nd arm 411, 412, 421, 422 Joint hole 4a Arm coupling part 431, 441, 451 Arm terminal part 5 Pin h Distance between split connection parts s Distance between split rims

Claims (4)

A ten wheel having a connecting portion to be inserted into the tenth, an arm connected to the connecting portion, and a rim connected to the arm,
The tenter wheel, wherein the arm includes a first arm and a second arm forming a truss structure. The ten wheel according to claim 1, wherein the arm is rotatably connected to each of the rim and the connection portion. The rim has a plurality of divided rims;
Each of the said division | segmentation rim is connected with the said arm. The ten wheel of Claim 1 or 2 characterized by the above-mentioned. The connecting portion has a first connecting portion and a second connecting portion that are slidable along the tenth,
The first connecting portion is connected to the first arm;
The ten wheel according to claim 3, wherein the second connection portion is connected to the second arm.

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