clock

Abstract

A clock that prevents loosening of the screw between the first component of the bearing that supports the rotor and the ball bearing shaft. [Solution] The clock comprises a rotor, a bearing to which the rotor is attached, and a support member that supports the bearing. The bearing has a first member having a screw hole with a female screw portion formed therein, and a second member that is rotatably supported relative to the first member and to which the rotor is attached. The support member has a bearing shaft with a male screw portion formed on its outer circumference into which the first member is screwed, and a receiving portion provided on the outer circumference of the bearing shaft and positioned to overlap the first member and the bearing shaft in the axial direction. The support member comprises an elastic member disposed between the receiving portion and the first member, which is compressed and deformed as the female screw portion is screwed into the male screw portion and the first member approaches the receiving portion.

Description

Technical Field

[0001] The present invention relates to a clock having a rotating weight.

Background Art

[0002] Clocks incorporating a rotating weight for winding a spring or generating electricity are known. For example, Patent Document 1 discloses a rotating weight for an automatic winding mechanism of a spring. This rotating weight is rotatably attached to a movement by a ball bearing. The ball bearing includes an inner ring, an outer ring, and balls disposed between the inner ring and the outer ring. The rotating weight is fixed to the outer ring, and a female thread is formed on the inner peripheral surface of the inner ring. Then, the ball bearing with the rotating weight fixed thereto is attached to the movement by screwing the female thread of the inner ring onto the male thread of a ball bearing shaft fixed to a wheel train support of the movement.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] When attaching a rotating weight with such a ball bearing, a force may be applied to the inner ring via the balls between the outer ring and the inner ring, and the inner ring may loosen with respect to the ball bearing shaft. For example, when an instantaneous force becomes large due to a disturbance such as dropping the clock, the inner ring, which is a threaded portion, may be rotated via the balls. In particular, when the rotating weight is thickened and its mass is increased to increase the winding torque of the spring, if the distance between the center of gravity position of the rotating weight and the position of the balls between the outer ring and the inner ring becomes large in the axial direction of the ball bearing, the force for rotating the inner ring via the balls may also become large. As a result, there is a risk of loosening of the threads of the inner ring and the ball bearing shaft. [Means for solving the problem]

[0005] The clock of the present disclosure comprises a rotor, a bearing to which the rotor is attached, and a support member for supporting the bearing, wherein the bearing has a first member having a screw hole with a female screw portion formed thereon, and a second member rotatably supported with respect to the first member and to which the rotor is attached, and the support member has a bearing shaft with a male screw portion formed on its outer circumference and into which the female screw portion of the first member is screwed, and a receiving portion provided on the outer circumference side of the bearing shaft and positioned to overlap the first member and the bearing shaft in the axial direction, and comprises an elastic member disposed between the receiving portion and the first member, the female screw portion being screwed into the male screw portion and the first member approaching the receiving portion to be compressed and deformed. [Brief explanation of the drawing]

[0006] [Figure 1] This is a front view showing a clock according to the first embodiment. [Figure 2] This is a rear view showing the aforementioned clock. [Figure 3] This is a cross-sectional view showing the main part of the movement of the aforementioned watch. [Figure 4] This is an enlarged cross-sectional view showing the main part of the aforementioned movement. [Figure 5] This is a plan view showing the bearing and rotary weight spacer of the above embodiment. [Figure 6] This is an enlarged cross-sectional view showing the main part of the movement of the second embodiment. [Figure 7] This is a plan view showing the main parts of the movement of the second embodiment. [Figure 8] This is an enlarged cross-sectional view showing the main part of the movement of the third embodiment. [Figure 9] This is a plan view showing a modified example of a rotor spacer. [Figure 10] This is a plan view showing other variations of the rotor spacer. [Modes for carrying out the invention]

[0007] [First Embodiment] Hereinafter, the clock 1 of the first embodiment of this disclosure will be described with reference to the drawings. Figure 1 is a front view of watch 1, and Figure 2 is a rear view of watch 1. In Figure 2, the top is the 6 o'clock position and the bottom is the 12 o'clock position. Watch 1 in this embodiment is a skeleton type watch in which the power reserve indicator hand 5 can be seen from the back. Watch 1 is a wristwatch worn on the user's wrist and has a cylindrical outer case 2, with a dial 3 positioned on the inner circumference of the outer case 2. Of the two openings in the outer case 2, the opening on the front side is covered with a cover glass, and the opening on the back side is covered with a case back 8. The case back 8 consists of a ring-shaped frame 8A and a case back glass 8B attached to the frame 8A.

[0008] The watch 1 comprises a movement 10 housed within an outer case 2, hour hands 4A, minute hands 4B, and second hands 4C that indicate the time as shown in Figure 1, and a power reserve hand 5 that indicates the remaining winding amount of the mainspring as shown in Figure 2. The dial 3 is provided with a calendar window 3A, through which the date wheel 6 can be seen.

[0009] A crown 7 is provided on the side of the outer case 2. The crown 7 can be moved from the 0th position, which is pushed in toward the center of the watch 1, to the 1st position and the 2nd position. Rotating the crown 7 to the 0 position winds the mainspring 210, which is the mechanical energy source in the movement 10. The power reserve hand 5 moves in conjunction with the winding of the mainspring 210. When crown 7 is pulled out to the first position and rotated, the gear to which the rotation of crown 7 is transmitted by the switching mechanism switches, moving the date wheel 6 and allowing the date to be set. When crown 7 is pulled out to the second position, the second hand 4C stops, and when crown 7 is rotated in the second position, the gear to which the rotation of crown 7 is transmitted by the switching mechanism switches, moving the hour hand 4A and minute hand 4B and allowing the time to be set. The configuration of the switching mechanism and the method of adjusting the date wheel 6, hour hand 4A, and minute hand 4B using crown 7 are the same as in conventional mechanical watches, so an explanation will be omitted.

[0010] [Movement] As shown in Figures 2 and 3, the movement 10 comprises a base plate 11, a gear train bridge 12, and a second bridge 13. The second bridge 13 is positioned between the base plate 11 and the gear train bridge 12. Between the base plate 11 and the gear train support 12, there is a gear train 20 for time display, a winding mechanism 30, a switching mechanism (not shown), a power reserve mechanism, and the like. The time display gear train 20 comprises a barrel wheel 21, a second wheel 22, a third wheel (not shown), and a fourth wheel 24. The barrel wheel 21 houses a mainspring 210, and the central end of the mainspring 210 is attached to the barrel arbor. A ratchet wheel that rotates integrally with the barrel arbor is attached to the barrel arbor, and by rotating the ratchet wheel, the mainspring 210, which is the source of mechanical energy, can be wound. When the barrel wheel 21 rotates due to the mechanical energy accumulated from winding the mainspring 210, the second wheel 22, third wheel, and fourth wheel 24 of the time display gear train 20 rotate in sequence. Furthermore, a barrel kana 28 is attached to the second wheel 22, and a second hand shaft 29 is attached to the fourth wheel 24. Also, a barrel wheel 27 is positioned on the outer circumference of the barrel kana 28, and the rotation of the barrel kana 28 is transmitted via a back wheel (not shown). The hour hand 4A, minute hand 4B, and second hand 4C are attached to the barrel wheel 27, barrel kana 28, and second hand shaft 29, respectively. The clock 1 in this embodiment may be a mechanical clock equipped with an escapement and speed control mechanism that includes an escape wheel, lever, balance wheel, etc., as a mechanism for regulating the rotational speed of the time display gear train 20, or it may be an electronically controlled mechanical clock equipped with a generator and speed control that has a rotor rotated by the time display gear train 20.

[0011] The winding mechanism 30 includes both an automatic winding mechanism and a manual winding mechanism. The manual winding mechanism is a common mechanism in which the mainspring 210 is wound by operating the crown 7, so its explanation will be omitted. The automatic winding mechanism comprises a rotor 31, a bearing 40, an eccentric wheel 33, a claw lever (not shown), and a transmission wheel, as shown in Figures 2 and 3. As shown in Figure 2, the rotor 31 comprises a weight portion 311 and a counterweight portion 312. The weight portion 311 is formed in a thin plate shape and comprises a central shaft portion 313 fixed to the bearing 40 and an opening 314. Because the opening 314 is formed in the weight portion 311, the power reserve needle 5 can be seen even when the rotor 31 overlaps with it. A fan-shaped scale portion 12A is provided on the back surface of the gear train bearing 12. The remaining winding amount of the mainspring can be displayed by the power reserve needle 5 pointing to this scale portion 12A. The weight portion 312 is formed continuously on the outer circumference of the weight portion 311 and is thicker than the weight portion 311. In other words, the rotor 31 is formed integrally with the weight portion 311 and the weight portion 312. The weight portion 311 overlaps the gear train bearing 12 in a plan view, but the weight portion 312 is configured not to overlap the gear train bearing 12. A plan view refers to the view of the watch 1 or movement 10 from a direction perpendicular to the dial 3, that is, from the cover glass side or the case back side.

[0012] The bearing 40 is a bearing that rotatably supports the rotor 31, and as shown in Figures 3 and 4, it comprises an inner ring 41, a retaining ring 42, an outer ring 43, balls 44, and a retainer 45. The inner ring 41 has a through-hole formed as a threaded hole on the central axis, and an internal thread portion 411 is formed on the inner peripheral surface of this through-hole. The surface of the inner ring 41 on the side of the back cover 8 is made flat, and three holes (see Fig. 2) into which a jig used when screwing in the inner ring 41 is fitted are formed. The central axis portion of the inner ring 41 on the side of the raceway receiver 12 is a protruding portion 412 protruding toward the raceway receiver 12 side. An abutting surface 413 against which the ball 44 abuts is formed on the outer peripheral portion of the inner ring 41. This abutting surface 413 is an inclined surface inclined with respect to the axial direction of the central axis of the inner ring 41 and the direction orthogonal to this axial direction.

[0013] The pressing ring 42 is formed in a substantially annular shape, and a central through-hole 421 is press-fitted into the protruding portion 412 of the inner ring 41 and integrated. The integrated inner ring 41 and pressing ring 42 constitute a first member in which the internal thread portion 411 is formed. The central axis portion of the pressing ring 42 on the inner ring 41 side is a protruding portion 422 protruding toward the inner ring 41 side. An abutting surface 423 against which the ball 44 abuts is formed on the outer peripheral portion of the pressing ring 42. This abutting surface 423 is an inclined surface similar to the abutting surface 413.

[0014] As shown in Fig. 5, the outer ring 43 is formed in a substantially ring shape and is disposed on the outer periphery of the inner ring 41 and the pressing ring 42. Note that Fig. 5 is a plan view of the bearing 40 as viewed from the raceway receiver 12 side. Teeth 431 that mesh with the eccentric wheel 33 are formed on the outer periphery of the outer ring 43. Therefore, when the outer ring 43, which is integral with the rotating weight 31, rotates, the eccentric wheel 33 rotates, and the claw lever attached to the eccentric shaft of the eccentric wheel 33 moves forward and backward to rotate the transmission wheel in one direction. The rotation of the transmission wheel is transmitted to the square hole wheel, and the spring 210 is wound up. As shown in Fig. 4, a concave groove 432 against which the ball 44 abuts is formed on the inner peripheral surface of the outer ring 43. Further, the outer ring 43 includes a fitting portion 433 into which the central axis portion 313 of the rotating weight 31 is fitted. A fitting hole formed at the center of the central axis portion 313 is fitted into the step portion between the fitting portion 433 and the teeth 431.

[0015] The balls 44 are rolling elements of the bearing 40 and are positioned between the inner ring 41 and retaining ring 42 and the outer ring 43. In this embodiment, as shown in Figure 5, seven balls 44 are arranged at equal intervals along the inner circumferential surface of the outer ring 43. The retainer 45 is a component for arranging the balls 44 at equal intervals, and is formed in a roughly disc shape with recesses on its outer circumference for holding the balls 44.

[0016] As shown in Figures 3 and 4, a bearing shaft 50 supporting a bearing 40 is fixed to the gear train support 12. The bearing shaft 50 comprises a base portion 51 and a shaft portion 52. The base portion 51 is press-fitted into a through hole formed in the gear train support 12 and fixed, and is positioned by a positioning flange 511 that abuts against the gear train support 12. A bore stone 241 that pivotally supports the fourth wheel 24 is held on the base portion 51 via a bore stone frame 242. The shaft portion 52 is formed in a substantially cylindrical shape with a through hole in its central axis, and a male threaded portion 521 is formed on its outer circumferential surface. The gear train support 12 and the bearing shaft 50 fixed to the gear train support 12 constitute a support member that supports the bearing 40. The gear train support 12, which is a support member, has a receiving portion 121 provided at a position that overlaps the first member of the bearing 40, the retaining ring 42, in the axial direction of the bearing shaft 50. The receiving portion 121 is provided on the outer circumference side of the base portion 51 of the bearing shaft 50 and has a first surface 122 that faces the retaining ring 42. The retaining ring 42 also has a second surface 424 that faces the first surface 122.

[0017] [Rotating weight spacer] An elastic rotating weight spacer 60 is positioned between the receiving portion 121 of the gear train support 12, which is a support member, and the retaining ring 42, which is the first member. As shown in Figures 4 and 5, the rotating weight spacer 60 is made of an annular film material and is positioned between the first surface 122 of the receiving portion 121 and the second surface 424 of the retaining ring 42. The rotary weight spacer 60 is composed of an elastic material such as resin or rubber. The resin includes synthetic resins and natural resins, and the rubber includes natural rubber and synthetic rubber. In this embodiment, the rotary weight spacer 60 is made of synthetic resin, and specifically, it is composed of a polyester or polyethylene film. The planar size of the rotor spacer 60 is the same as the second surface 424 of the retaining ring 42. Therefore, the outer peripheral edge 61 of the rotor spacer 60 coincides with the outer peripheral edge of the retaining ring 42. In this embodiment, the inner peripheral edge of the rotor spacer 60 is also formed to coincide with the inner peripheral edge of the retaining ring 42. The thickness dimension of the rotor spacer 60 is approximately 0.020 to 0.030 mm.

[0018] To attach a bearing 40 with this configuration to a bearing shaft 50, a rotor spacer 60 is placed between the receiving portion 121 and the retaining ring 42, and the female threaded portion 411 of the first member, consisting of the inner ring 41 and the retaining ring 42, is screwed onto the male threaded portion 521 of the bearing shaft 50. As a result, the retaining ring 42 moves closer to the receiving portion 121, causing the rotor spacer 60 to be compressed and deformed. This increases the contact between the first surface 122 of the receiving portion 121 and the rotor spacer 60, and the contact between the rotor spacer 60 and the second surface 424 of the retaining ring 42. This makes it difficult for the inner ring 41 and the retaining ring 42, which are the first members of the bearing 40, to rotate relative to the receiving portion 121, and prevents the female threaded portion 411 and the male threaded portion 521 from loosening. Furthermore, the restoring force of the compressed and deformed rotor spacer 60 applies an axial force to the retaining ring 42 and the inner ring 41, causing the female thread portion 411 and the male thread portion 521 to come into close contact, thereby preventing the female thread portion 411 and the male thread portion 521 from loosening. By placing the rotary weight spacer 60, which is an elastic member, between the receiving portion 121 and the retaining ring 42 and compressing and deforming it, it is possible to prevent the female thread portion 411 and the male thread portion 521 from loosening.

[0019] [Effects of the First Embodiment] According to the first embodiment, the following effects are obtained. Specifically, since the rotor spacer 60, which is an elastic member, is placed between the first surface 122 of the receiving portion 121 of the gear train support 12, which is a support member, and the second surface 424 of the retaining ring 42, which is a first member, the female threaded portion 411 of the inner ring 41 can be screwed onto the male threaded portion 521 of the bearing shaft 50, thereby compressing and deforming the rotor spacer 60. As a result, the contact between the rotor spacer 60 and the first surface 122 and the second surface 424 can be improved, and furthermore, the restoring force of the compressed and deformed rotor spacer 60 can apply an axial force to the retaining ring 42 and the inner ring 41, bringing the female threaded portion 411 and the male threaded portion 521 into close contact, thereby preventing loosening of the female threaded portion 411 and the male threaded portion 521. Furthermore, if adhesive is used to prevent loosening of the screw threads, workability will be reduced during reassembly in the assembly process of the movement 10, and adhesive debris may scatter when the screw threads are removed, potentially entering the movement 10 and hindering the operation of the gear train and other components. In contrast, in this embodiment, loosening of the female screw portion 411 and the male screw portion 521 can be prevented without using adhesive, thereby improving workability during reassembly and preventing debris from entering the movement 10. Furthermore, it is conceivable to increase the fastening force of the threads by increasing the engagement area of ​​the threads of the female thread portion 411 and the male thread portion 521. For example, if the engagement area of ​​the threads is increased by increasing the diameter of the female thread portion 411 and the male thread portion 521, the planar size of the bearing 40 will also increase, affecting the layout with other parts and potentially increasing the planar size of the movement 10. Moreover, if the axial length of the female thread portion 411 and the male thread portion 521 is increased, the thickness dimension of the movement 10 will increase. As a result, the size of the watch will increase. In contrast, in this embodiment, it is only necessary to place a rotor spacer 60 with a thickness dimension of 0.1 mm or less, so it is possible to prevent the size of the movement 10 from increasing. Furthermore, a method can be considered in which the inner ring of the bearing is fixed to the gear train support or the like with multiple screws, without providing a bearing shaft. In this case, the number of parts such as multiple screws increases, and the plate thickness of the threaded parts such as the gear train support needs to be increased, thus increasing the thickness of the movement. In contrast, in this embodiment, it is only necessary to add the rotor spacer 60, so the increase in the number of parts can be suppressed, and the size of the movement 10 can be prevented from becoming larger.

[0020] Since only a rotor spacer 60 is added between the retaining ring 42 and the receiving part 121, the bearing 40, bearing shaft 50, and gear train support 12 can be used as existing parts. Therefore, the diameter and thickness dimensions of the movement 10 do not increase, and it can be incorporated into the existing outer case 2. Furthermore, since the rotor spacer 60 can be positioned when screwing the bearing 40 onto the bearing shaft 50, the assembly workability of the movement 10 is not reduced, and the same level of productivity as before can be maintained. Furthermore, the rotor spacer 60 is positioned between the retaining ring 42 of the bearing 40 and the receiving portion 121 of the gear train support 12, and is not exposed to the outside of the movement 10, so it does not detract from the appearance of the watch 1 and can provide a high-quality watch 1. The rotor spacer 60 is formed in an annular shape and is positioned around the entire circumference of the second surface 424 of the retaining ring 42, thereby preventing the inner ring 41 and the retaining ring 42 from tilting when the inner ring 41 is tightened onto the bearing shaft 50.

[0021] [Second Embodiment] The second embodiment differs from the first embodiment only in that it uses a rotary weight spacer 60B, as shown in Figures 6 and 7. Therefore, components identical to those in the first embodiment are denoted by the same reference numerals and their descriptions are omitted. The rotor spacer 60B has an outer edge 61B that extends outward beyond the outer circumference of the retaining ring 42 and the inner ring 41. Therefore, as shown in Figure 7, in a plan view of the bearing 40 from the back cover side, the rotor spacer 60B can be seen through the gap between the outer surface of the inner ring 41 and the inner surface of the outer ring 43. In other words, the portion of the rotor spacer 60B that does not overlap with the balls 44 and retainer 45 is exposed and can be seen through the gap.

[0022] In the second embodiment, the same effects and advantages as in the first embodiment can be achieved. Furthermore, since the rotor spacer 60B can be seen through the gap between the inner ring 41 and the outer ring 43, after assembling the movement 10, the worker can easily confirm that the rotor spacer 60B is positioned between the retaining ring 42 and the receiving portion 121 of the gear train support 12, and can easily confirm that the rotor spacer 60B has been forgotten to be installed.

[0023] [Third Embodiment] The third embodiment differs from the first embodiment in that, as shown in Figure 8, the rotor spacer 60C is positioned between the protrusion 412 of the inner ring 41 and the base 51 of the bearing shaft 50. For this reason, components identical to those in the first embodiment are denoted by the same reference numerals and their descriptions are omitted. In the third embodiment as well, by screwing the inner ring 41 onto the bearing shaft 50, the inner ring 41 and the base 51 move closer together, causing the rotor spacer 60C to compress and deform, thus achieving the same effects as in the first embodiment. Therefore, in the third embodiment, the base 51 of the bearing shaft 50 becomes the receiving portion. Furthermore, since the rotor spacer 60C is positioned between the base 51 of the bearing shaft 50 and the inner ring 41 which is directly screwed to the bearing shaft 50, force can be directly applied to the inner ring 41 and the bearing shaft 50 by the rotor spacer 60C, effectively preventing loosening of the female thread portion 411 and the male thread portion 521. Also, the position of the rotor spacer 60C, in a plan view from the axial direction of the bearing 40, is closer to the threaded portion of the female thread portion 411 and the male thread portion 521 compared to the first and second embodiments. Therefore, force can be effectively applied to the inner ring 41 and the bearing shaft 50 by the rotor spacer 60C so that the female thread portion 411 and the male thread portion 521 are pressed together in the axial direction. For this reason, even when using a smaller rotor spacer 60C compared to the rotor spacers 60 and 60B of the first and second embodiments, loosening of the thread portion can be prevented.

[0024] [Other embodiments] It should be noted that the present invention is not limited to the embodiments described above, and various modifications can be made within the scope of the gist of the present invention. For example, the rotor spacer is not limited to an annular shape in plan view; as shown in Figure 9, it may also be an arc-shaped rotor spacer 60D in plan view. When providing one arc-shaped rotor spacer 60D, it is preferable that the central angle of the rotor spacer 60D is 180 degrees or more. Alternatively, multiple arc-shaped rotor spacers 60D with central angles of less than 180 degrees may be arranged so as not to overlap each other. Furthermore, the rotor spacer is not limited to annular or arc-shaped in plan view. For example, as shown in Figure 10, multiple rectangular rotor spacers 60E may be arranged along the circumference on the second surface 424 of the retaining ring 42. In this case, it is preferable that each rotor spacer 60E is arranged at equal intervals along the circumference. Also, the rotor spacers arranged at intervals in the circumference are not limited to a rectangular shape in plan view, but may be circular or polygonal in plan view.

[0025] The rotor spacer is not limited to being made of synthetic resin such as polyester or polyethylene, but may also be made of rubber. Furthermore, the first component and receiving portion that sandwich the rotor spacer are not limited to the configuration of the above embodiment. For example, the diameter of the base portion 51 of the bearing shaft 50 may be increased so that it faces the retaining ring 42, and the rotor spacer may be placed between the base portion 51 and the retaining ring 42. Alternatively, the receiving portion 121 of the gear train support 12 may be positioned to face the protrusion 412 of the inner ring 41, and the rotor spacer may be placed between the receiving portion 121 and the inner ring 41. In the first component and the receiving portion, the surface to which the resin or rubber rotor spacer makes contact may be a smooth surface, but the frictional force may be increased by making it a rough surface, such as by applying a textured finish. In addition, radial grooves may be machined into the second surface 424 of the retaining ring 42 of the first component. In this case as well, the frictional force between the retaining ring 42 and the rotor spacer 60 can be increased. Furthermore, in the first component and the receiving portion, the surface to which the resin or rubber rotor spacer makes contact may have steps or irregularities. In this case as well, the contact area can be secured and the frictional force increased by designing the rotor spacer to match the shape of each surface.

[0026] The rotor spacer is not limited to being made of resin or rubber; it may also be made of spring components such as spring washers or disc spring washers. Furthermore, the rotor spacer may be made of a material that is elastic after curing, and can be coated with an elastic paint or elastic adhesive onto the first components, such as the inner ring 41, retaining ring 42, receiving portion 121, and base portion 51. In this case, for example, the elastic paint or elastic adhesive can be pre-applied to the retaining ring 42 and receiving portion 121 and cured, eliminating the need to incorporate a film-like rotor spacer, thus improving the ease of bearing assembly. As described above, the rotor spacer only needs to be one that compresses and deforms when the inner ring 41, which is the first component, is screwed onto the bearing shaft 50, and that can directly or indirectly apply its restoring force to the inner ring 41 and the bearing shaft 50.

[0027] The bearing is not limited to the configuration of the embodiment described above. For example, a bearing using rollers as rolling elements may also be used. Furthermore, depending on the structure of the retainer for the rolling elements, the first member may consist only of an inner ring, and a rotor spacer may be placed between the inner ring and the receiving portion.

[0028] [Summary of this disclosure] The clock of the present disclosure comprises a rotor, a bearing to which the rotor is attached, and a support member for supporting the bearing, wherein the bearing has a first member having a screw hole with a female screw portion formed thereon, and a second member rotatably supported with respect to the first member and to which the rotor is attached, and the support member has a bearing shaft with a male screw portion formed on its outer circumference and into which the female screw portion of the first member is screwed, and a receiving portion provided on the outer circumference side of the bearing shaft and positioned to overlap the first member and the bearing shaft in the axial direction, and is characterized by comprising an elastic member disposed between the receiving portion and the first member, which is compressed and deformed when the female screw portion is screwed into the male screw portion and the first member approaches the receiving portion. According to the clock of this disclosure, since an elastic member is placed between the first member and the receiving part of the bearing that supports the rotor, when the first member is brought closer to the receiving part by screwing the female threaded part of the first member onto the male threaded part of the bearing shaft, the elastic member sandwiched between the first member and the receiving part can be compressed and deformed. The restoring force of this compressed and deformed elastic member is applied to the first member and the receiving part, which prevents the female threaded part of the first member and the male threaded part of the receiving part from loosening.

[0029] In the clock according to the present disclosure, the first member comprises an inner ring having the female thread portion on its inner circumferential surface, and a retaining ring disposed between the receiving portion and the inner ring and press-fitted and fixed to the outer circumference of the inner ring, and the elastic member may be disposed between the receiving portion and the retaining ring. According to the clock of this disclosure, since an elastic member is placed between the retaining ring, which holds rolling elements such as balls together with the inner ring, and the receiving part, the contact area between the retaining ring and the receiving part and the elastic member can be increased, the size of the elastic member can be increased, and the restoring force of the compressed and deformed elastic member can also be increased.

[0030] In the clock according to this disclosure, the first member may include an inner ring having the female threaded portion on its inner circumferential surface, and the elastic member may be disposed between the receiving portion and the inner ring. According to the clock of this disclosure, since an elastic member is placed between the inner ring and the receiving portion, the restoring force of the elastic member when compressed can be directly applied to the inner ring on which the female thread portion is formed, thereby effectively preventing loosening of the female and male thread portions.

[0031] In the clock according to the present disclosure, the bearing comprises a first member, a second member, and rolling elements disposed between the first member and the second member, wherein a portion of the elastic member preferably protrudes outward from the outer circumference of the first member in a plan view of the bearing from the axial direction and is visible from the gap between the first member and the second member. According to the clock of this disclosure, the elastic member can be seen through the gap between the first and second members, so the absence of the elastic member can be easily confirmed from the appearance of the movement.

[0032] In the watch of this disclosure, the elastic member is preferably made of resin or rubber. According to the clock of this disclosure, if the elastic member is made of resin or rubber, the adhesion between the first member and the receiving part and the elastic member can be improved. As a result, the contact area between the first member and the receiving part and the elastic member increases, and the frictional force also increases, making it more difficult for the first member to rotate relative to the receiving part, and further preventing loosening of the screw part.

[0033] In the clock of this disclosure, the elastic member may be composed of a spring member. According to the clock disclosed herein, the elastic member is composed of spring members such as spring washers and disc spring washers, which increases the restoring force when the elastic member is compressed and deformed, thereby preventing loosening of the screw threads.

[0034] In the clock according to this disclosure, the elastic members are preferably formed in an annular or arc shape in a plan view of the bearing from the axial direction, or a plurality of them are arranged along the circumferential direction. According to the clock of this disclosure, by arranging multiple elastic members in an annular, arc-shaped, or circumferential manner with spacing between them, it is possible to prevent the first bearing member from tilting relative to the receiving portion.

[0035] In the clock according to this disclosure, the elastic member may be made of a material that is applied to at least one of the receiving portion and the first member and becomes elastic after curing. According to the clock of this disclosure, the elastic member is made of a material that can be applied to at least one of the receiving part and the first member and which becomes elastic after curing, such as an elastic paint or an elastic adhesive. Therefore, the elastic member can be applied to the receiving part and the first member before the bearing is assembled into the movement. As a result, it is not necessary to assemble the bearing while arranging a sheet-like elastic member, and the bearing assembly work can be simplified.

[0036] In the clock according to this disclosure, the surface of the receiving portion and at least one of the first member that contacts the elastic member may be a rough surface. According to the clock of this disclosure, since the surface in contact with the elastic member is made rough, the frictional force between the elastic member and the rough surface can be increased, making it more difficult for the first member to rotate relative to the receiving part, and thus the effect of preventing loosening of the screw part can also be increased. [Explanation of symbols]

[0037] 1...clock, 10...movement, 12...gear train bearing, 31...rotor, 40...bearing, 41...inner ring, 42...retaining ring, 43...outer ring, 44...ball, 45...retainer, 50...bearing shaft, 51...base, 52...shaft, 60...rotor spacer, 60B...rotor spacer, 60C...rotor spacer, 60D...rotor spacer, 60E...rotor spacer, 61B...outer edge, 121...receiving part, 122...first surface, 411...female thread part, 424...second surface, 521...male thread part.

Claims

1. Rotating weight and, The bearing to which the aforementioned rotating weight is attached, The system comprises a support member that supports the bearing, The aforementioned bearing is A first member having a screw hole in which a female thread portion is formed, It comprises a second member that is rotatably supported with respect to the first member and to which the rotor weight is attached, The aforementioned support member is A bearing shaft having a male threaded portion formed on its outer circumference into which the female threaded portion of the first member is screwed, The bearing shaft has a receiving portion provided on the outer circumference side and positioned to overlap the first member and the bearing shaft in the axial direction, A clock comprising an elastic member disposed between the receiving portion and the first member, wherein the female screw portion is screwed into the male screw portion, and the first member is compressed and deformed as the first member approaches the receiving portion.

2. In the clock according to claim 1, The first member is, An inner ring having the female thread portion on its inner circumferential surface, The system includes a retaining ring positioned between the receiving portion and the inner ring, which is press-fitted and fixed to the outer circumference of the inner ring, The elastic member is a clock positioned between the receiving portion and the retaining ring.

3. In the clock according to claim 1, The first member comprises an inner ring having the female thread portion on its inner circumferential surface, The elastic member is a clock positioned between the receiving portion and the inner ring.

4. In the clock according to claim 1, The bearing comprises a first member, a second member, and rolling elements disposed between the first member and the second member. A portion of the elastic member protrudes outward from the outer circumference of the first member in a plan view of the bearing as seen from the axial direction, and is visible through the gap between the first member and the second member.

5. In the clock according to claim 1, The aforementioned elastic member is made of resin or rubber.

6. In the clock according to claim 1, The aforementioned elastic member is a clock made of a spring member.

7. In the clock according to claim 1, The aforementioned elastic members are formed in an annular or arc shape in a plan view of the bearing from the axial direction, or a plurality of them are arranged along the circumferential direction in a clock.

8. In the clock according to claim 1, The elastic member is made of a material that is applied to at least one of the receiving portion and the first member and becomes elastic after curing.

9. In the clock according to claim 1, The surface of the receiving portion and at least one of the first member that contacts the elastic member is a rough surface.

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