CN118584778A - Watch movements and watches - Google Patents

Abstract

Provided is a timepiece movement capable of suppressing excessive torque of a mainspring from being transmitted to an escapement/speed regulating mechanism and suppressing wear of parts without deteriorating the appearance of the movement. The movement comprises: a large steel wheel (30) which is arranged in a manner capable of winding up a mainspring; a barrel splint (12) which supports the large steel wheel (30) in a manner capable of rotating around a rotation axis (O); a slider seat (41) which is arranged in a manner capable of not being displaced relative to the barrel splint (12) and is provided with a guide groove (43) extending in a circumferential direction around the rotation axis (O); a pin (50) which has a center axis (P) extending in an axial direction along the rotation axis (O), is inserted into the guide groove (43), and is displaced along the guide groove (43) around the rotation axis (O); a slider (60) which is arranged along the slider seat (41) and holds the pin (50); and a pawl body (70) which is supported on the pin (50), is arranged in a manner capable of rotating relative to the barrel splint (12) around the center axis (P), and has a pawl portion (72) which engages with the large steel wheel (30).

Description

Watch movements and watches

Technical Field

The invention relates to a watch movement and a watch.

Background Art

In the past, the movement of a mechanical watch was equipped with a barrel wheel that accommodates a power spring, a large steel wheel that winds up the spring, and a winding wheel train that rotates the large steel wheel. In order to prevent the wound spring from unwinding, a ratchet that limits the reverse rotation of the large steel wheel is engaged with the large steel wheel. Furthermore, in order to suppress the excessive torque of the spring from being transmitted to the escapement/speed regulating mechanism, the movement is sometimes provided with a mechanism that, when the rotation of the large steel wheel that winds up the spring is stopped, the large steel wheel is reversed to some extent to loosen the spring (for example, refer to Patent Document 1). Patent Document 1 discloses the following spring winding mechanism: the ratchet that meshes with the large steel wheel is made to be a gear that swings along a long hole formed in the main plate or the splint by the rotation of the large steel wheel, and when the large steel wheel rotates in one direction, the ratchet stops rotating by a stopper at the single-side swinging end.

Prior Art Literature

Patent Literature

Patent document 1: Japanese Utility Model Application Laid-Open No. 52-166555.

Summary of the invention

Problems to be solved by the invention

However, in the spring winding mechanism disclosed in Patent Document 1, when the ratchet moves along the long hole due to the rotation of the large steel wheel, it slides at high speed on the side wall surface of the long hole, so there is a possibility of wear on the side wall surface of the long hole. On the other hand, if the main plate or the splint formed with the long hole is subjected to a surface treatment to improve the wear resistance, there is a possibility that the appearance of the movement will deteriorate. Therefore, in a watch movement that can suppress the excessive torque of the spring from being transmitted to the escapement/speed regulating mechanism, there is a problem of suppressing the wear of parts without deteriorating the appearance of the movement.

Therefore, the present invention provides a timepiece movement and a timepiece equipped with the same, which can suppress the excessive torque of the mainspring from being transmitted to the escapement/speed regulating mechanism and suppress the wear of parts without deteriorating the appearance of the movement.

Solutions to Solve Problems

The watch movement involved in the first scheme of the present invention comprises: a large steel wheel, which is arranged in a manner capable of winding up a mainspring; a barrel splint, which supports the aforementioned large steel wheel in a manner capable of rotating around a rotation axis; a sliding member seat, which is configured in a manner unable to be displaced relative to the aforementioned barrel splint, and is formed with a guide groove extending in a circumferential direction around the aforementioned rotation axis as the center; a pin, which has a center axis extending in an axial direction along the aforementioned rotation axis, is inserted into the aforementioned guide groove, and is displaced along the aforementioned guide groove around the aforementioned rotation axis as the center; a sliding member, which is configured along the aforementioned sliding member seat to hold the aforementioned pin; and a pawl body, which is supported on the aforementioned pin, is configured in a manner capable of rotating relative to the aforementioned barrel splint around the aforementioned center axis as the center, and has a pawl portion that meshes with the aforementioned large steel wheel.

According to the first scheme, when the mainspring is wound up, if the large steel wheel is rotated, a force in the rotation direction of the large steel wheel is applied to the pawl body through the claw portion. Here, the pawl body is supported by the pin, and thus rotates around the rotation axis in the same direction as the large steel wheel together with the pin guided by the guide groove and moving in the guide groove. If the winding of the mainspring is stopped, a torque in the opposite direction to the rotation direction during winding acts on the large steel wheel due to the restoring force of the unwinding of the mainspring. Then, the large steel wheel starts to reverse. At this time, the pawl body rotates around the rotation axis in the same direction as the large steel wheel together with the pin as the large steel wheel reverses. In this way, when the winding of the mainspring is stopped, the length of the guide groove is allowed to rotate with the rotation of the pawl body and the reversal of the large steel wheel, thereby preventing the excessive torque of the mainspring from being transmitted to the escapement/speed regulating mechanism.

Furthermore, a guide groove for guiding the rotation of the pawl body around the axis of rotation is formed on the slider seat, thereby preventing the pawl body and the pin from sliding in contact with the barrel bridge when the pawl body and the pin rotate around the axis of rotation. Therefore, the wear resistance of the watch movement against the rotation of the pawl body around the axis of rotation can be improved without changing the material or performing surface treatment on the barrel bridge. Furthermore, the slider holding the pin is arranged along the slider seat, thereby preventing the pin from tilting relative to the slider seat, preventing the pawl body supported by the pin from accidentally sliding in contact with the barrel bridge. Therefore, in a watch movement that can prevent excessive torque of the mainspring from being transmitted to the escapement/speed regulating mechanism, wear of parts can be suppressed without deteriorating the appearance of the watch movement.

Furthermore, since the slider seat, the pin, the slider and the pawl body can be made into a unit, when the unit is worn out, the worn parts can be replaced by replacing the unit without replacing the barrel bridge, thereby improving after-sales serviceability.

A timepiece movement according to a second aspect of the present invention may be the timepiece movement according to the first aspect, wherein the slider is disposed between the barrel bridge and the slider seat.

According to the second embodiment, the portion where the slider slides relative to the barrel bridge and the slider seat as the pin rotates is located between the barrel bridge and the slider seat. Thus, even if oil is injected into the sliding portion between the barrel bridge and the slider and the sliding portion between the slider seat and the slider, it is possible to prevent oil from seeping out onto the outer surface of the watch movement. Therefore, it is possible to prevent the appearance of the watch movement from deteriorating.

A timepiece movement according to a third aspect of the present invention may be the timepiece movement according to the first or second aspect, wherein the pawl body is rotatably supported by the pin.

According to the third embodiment, the sliding portion generated when the pawl body rotates around the central axis of the pin is generated at the contact portion between the pawl body and the pin. As a result, the sliding portion generated when the pawl body rotates around the rotation axis and the sliding portion generated when the pawl body rotates around the central axis of the pin can be separated. Therefore, the sliding portion generated during the operation related to winding up the mainspring can be dispersed to suppress wear of parts.

The watch movement involved in the 4th scheme of the present invention may also be a watch movement involved in any one of the above-mentioned 1st scheme to 3rd scheme, wherein a secondary guide groove extending along the aforementioned guide groove as viewed from the aforementioned axial direction is formed in one of the aforementioned barrel splint and the aforementioned sliding member seat, and the aforementioned sliding member has a stopper capable of being inserted into the aforementioned secondary guide groove and displaced along the extension direction of the aforementioned guide groove on the inner side of the aforementioned secondary guide groove, and the displacement of the aforementioned secondary guide groove in the width direction is restricted by the aforementioned stopper, and when the aforementioned pin is displaced around the aforementioned rotation axis, the rotation around the aforementioned center axis is restricted.

According to the fourth scheme, when the pin rotates around the rotation axis, the slider can be prevented from rotating around the central axis of the pin. As a result, the slider can be rotated around the rotation axis in a desired posture. Therefore, during the action related to the winding of the mainspring, the occurrence of unexpected sliding parts can be prevented.

A timepiece movement according to a fifth aspect of the present invention may be the timepiece movement according to the fourth aspect, wherein the pawl body is provided in a non-rotatable manner relative to the slider.

According to the fifth aspect, when the pin rotates around the rotation axis, the pawl body can be prevented from rotating about the pin. Thus, the pawl body can be prevented from contacting surrounding parts with a force greater than necessary and causing wear due to the pawl body rotating about the pin at an unnecessary time.

A timepiece movement according to a sixth aspect of the present invention may be the timepiece movement according to any one of the first to fifth aspects, wherein the pin is formed integrally with the slider.

According to the sixth aspect, compared with a configuration in which the pin and the slider are provided separately, the number of parts can be reduced, and the assemblability of the timepiece movement can be improved.

The timepiece movement according to a seventh aspect of the present invention may be the timepiece movement according to any one of the first to sixth aspects, wherein the yield stress of the slider seat is greater than the yield stress of the barrel bridge.

According to the seventh scheme, the slider seat can be made harder than the barrel bridge and less prone to wear. Thus, compared with a configuration in which a groove for guiding the rotation of the guide pin around the rotation axis is formed on the barrel bridge instead of the slider seat, the wear resistance of the watch movement against the rotation of the pawl body around the rotation axis can be improved.

The watch movement involved in the 8th scheme of the present invention may also be a watch movement involved in any one of the above-mentioned 1st to 7th schemes, wherein the pin abuts against the sliding member seat at the end of the guide groove in the circumferential direction and is restricted from moving in the circumferential direction.

According to the eighth aspect, the rotation range of the pawl body around the rotation axis can be defined by the pin and the slider seat without using other parts. Therefore, a watch movement can be obtained that suppresses the increase in the number of parts and the deterioration of assembly performance while achieving the above-mentioned effects.

The watch movement involved in the 9th scheme of the present invention may also be the watch movement involved in any one of the above-mentioned schemes 1 to 8, further comprising: a pawl spring, which is arranged on the outside of the aforementioned pawl body and is set in a manner capable of pressing the aforementioned pawl body to apply force to the aforementioned pawl portion toward the aforementioned large steel wheel; and a positioning portion, which limits the aforementioned pawl spring from approaching the aforementioned pawl body side, the aforementioned pawl spring is cantilevered, and the aforementioned positioning portion has a limiting portion extending in a direction orthogonal to the aforementioned axial direction to limit the displacement of the aforementioned pawl spring in the aforementioned axial direction.

According to the ninth embodiment, by making the pawl spring always contact the positioning portion in a force-applying state, the deviation of the gap between the pawl spring and the pawl body can be suppressed, and the movement of the pawl body can be stabilized. Furthermore, when the pawl spring supported by the cantilever is about to bend due to an impact such as falling, the displacement of the pawl spring can be limited by the limiting portion. Therefore, the pawl spring can be suppressed from deviating from a predetermined position relative to the pawl body.

The timepiece movement according to a tenth aspect of the present invention may be the timepiece movement according to any one of the first to ninth aspects, further comprising a first spacer inserted outside the pin and interposed between the pin and the pawl body.

According to the tenth embodiment, compared with a structure in which the pawl body and the pin are in sliding contact, the sliding resistance accompanying the rotation of the pawl body around the central axis can be reduced. Therefore, the pawl body can be moved smoothly. In addition, the wear of the pin and the pawl body can be suppressed.

The timepiece movement according to the eleventh aspect of the present invention may be the timepiece movement according to any one of the first to tenth aspects, further comprising a second spacer inserted outside the pin inside the guide groove.

According to the eleventh aspect, when the pawl body rotates around the rotation axis together with the pin, the spacer can slide in contact with the wall surface of the guide groove, thereby suppressing wear of the pin and the slider seat compared to a configuration in which the pin directly slides in contact with the wall surface of the guide groove.

A timepiece according to a twelfth aspect of the present invention includes the timepiece movement according to any one of the first to eleventh aspects.

According to the twelfth aspect, it is possible to provide a timepiece having excellent appearance and precision and having high reliability with suppressed wear of parts.

Effects of the Invention

According to the present invention, a timepiece movement and a timepiece equipped with the same can be provided, wherein the timepiece movement can suppress the transmission of excessive torque of a mainspring to an escapement/speed regulating mechanism and suppress wear of parts without deteriorating the appearance of the movement.

BRIEF DESCRIPTION OF THE 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 as viewed from above.

FIG. 3 is a cross-sectional view taken along line III-III of FIG. 2 .

FIG. 4 is an exploded perspective view of the barrel bridge and the pawl unit according to the first embodiment.

FIG. 5 is a perspective view of the pawl unit according to the first embodiment.

FIG. 6 is an exploded perspective view of the pawl unit according to the first embodiment.

FIG. 7 is a plan view of the movement showing the periphery of the large steel wheel according to the first embodiment in an enlarged manner.

FIG. 8 is a cross-sectional view taken along line VIII-VIII of FIG. 7 .

FIG. 9 is a plan view of the movement showing the operation of the pawl unit according to the first embodiment.

10 is a longitudinal sectional view of a slider and a pin body according to a second embodiment.

FIG. 11 is a cross-sectional view of a movement according to the third embodiment, and is an enlarged view of a cross section corresponding to FIG. 3 .

FIG. 12 is a plan view showing a slider seat according to a third embodiment.

FIG. 13 is a plan view of a movement showing an enlarged view of the periphery of a large steel wheel according to the third embodiment.

FIG. 14 is a cross-sectional view of a movement according to a fourth embodiment, and is an enlarged view of a cross section corresponding to FIG. 3 .

FIG. 15 is a cross-sectional view showing a part of the pawl unit according to the fifth embodiment.

FIG. 16 is a cross-sectional view showing a pawl unit according to a sixth embodiment.

FIG. 17 is a cross-sectional view showing a part of the pawl unit according to the seventh embodiment.

DETAILED DESCRIPTION

Hereinafter, an embodiment of the present invention will be described based on the accompanying drawings. In addition, in the following description, the same reference numerals are used for components having the same or similar functions. Moreover, repeated descriptions of these components are sometimes omitted. In this embodiment, a mechanical clock is described as an example of a clock.

In general, the mechanical body including the driving part of the watch is called the "movement". The state in which the dial and the hands are installed on the movement and placed in the watch case to become a finished product is called the "finished product" of the watch. The direction of the axis of rotation of the needle is called the axial direction. The axial direction is described as the direction from the main board, which is the substrate of the watch, toward the back cover of the case as the upper side and the opposite side as the lower side. The direction orthogonal to the axial direction is called the planar direction. In addition, in this embodiment, the rotation direction of the component displaced around the axis along the axial direction is described as the direction observed from the upper side.

[First embodiment]

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

As shown in FIG1 , the finished product of the clock 1 of the present embodiment includes a movement 9 (clock movement), a dial 4, and hands including an hour hand 5, a minute hand 6, and a second hand 7 in a clock case 3 composed of a case back cover and a glass 2 (not shown). The clock 1 can wind up a mainspring 23 (see FIG3 ) manually, and the mainspring 23 is wound up via a manual winding wheel train by rotating a turning handle 8.

Fig. 2 is a top view of the movement of the first embodiment as viewed from above. Fig. 3 is a cross-sectional view taken along line III-III of Fig. 2 .

As shown in Fig. 2 and Fig. 3, the movement 9 includes a support member 10, a barrel wheel 20, a large steel wheel 30, a pawl unit 40, a pawl spring 80, and a positioning portion 90. In addition, the movement 9 includes a barrel wheel 20 or a front side wheel train including a second wheel, a third wheel, a fourth wheel, etc., and an escapement/speed regulating mechanism including a balance spring mechanism or an escapement wheel, an escapement fork, etc., but detailed description is omitted.

The support component 10 is a so-called main board 11 and a splint. The support component 10 supports the rotating body of the movement 9. The rotating body includes a barrel wheel 20 or a front-side wheel train, an escapement/speed regulating mechanism, etc. The support component 10 includes a main board 11 and a barrel splint 12 arranged on the upper side (case back cover side) than the main board 11. The main board 11 and the barrel splint 12 support the barrel wheel 20 in a manner that can rotate around a rotation axis O extending in the axial direction. The main board 11 and the barrel splint 12 are formed of a metal material. In the present embodiment, the main board 11 and the barrel splint 12 are formed of brass.

FIG. 4 is an exploded perspective view of the barrel bridge and the pawl unit according to the first embodiment.

As shown in FIG4 , a recessed portion 13 recessed downward and a through portion 14 penetrating the barrel splint 12 are formed on the upper surface of the barrel splint 12. The recessed portion 13 includes: a large steel wheel accommodating portion 13a, which accommodates the large steel wheel 30; and a pawl accommodating portion 13b, which is connected to the large steel wheel accommodating portion 13a and accommodates the pawl body 70 described later. The through portion 14 penetrates the barrel splint 12 in the axial direction. The through portion 14 opens at the bottom surface of the pawl accommodating portion 13b.

The barrel splint 12 is provided with a guide pin 16 and a cylindrical screw 17. The guide pin 16 and the cylindrical screw 17 are arranged at a position closer to the outer periphery of the movement 9 than the large steel wheel accommodating portion 13a and closer to the clockwise direction around the rotation axis O than the through portion 14. The guide pin 16 and the cylindrical screw 17 are respectively provided separately from the barrel splint 12 and are retained in the pin hole formed in the barrel splint 12. However, the guide pin 16 and the cylindrical screw 17 can also be formed integrally with the barrel splint 12. The guide pin 16 is formed in a cylindrical shape. The guide pin 16 and the cylindrical screw 17 protrude from the barrel splint 12 to the upper side along the axial direction. The guide pin 16 is arranged relative to the cylindrical screw 17 in a clockwise direction around the rotation axis O. The upper end edge of the cylindrical screw 17 is located lower than the upper end edge of the guide pin 16. The stop screw 18 is threadedly engaged with the cylindrical screw 17 from the upper side.

As shown in FIG3 , the barrel wheel 20 has a barrel shaft 21, a barrel 22 mounted on the barrel shaft 21, and a spring 23 accommodated in the barrel 22. The barrel shaft 21 is supported by the main board 11 and the barrel splint 12 in a manner that can rotate around the rotation axis O. The barrel 22 is arranged between the main board 11 and the barrel splint 12. The barrel 22 is supported on the barrel shaft 21 in a manner that can rotate. The inner end of the spring 23 is connected to the barrel shaft 21. The outer end of the spring 23 is connected to the inner circumferential surface of the barrel 22. The spring 23 is wound up by the rotation of the barrel shaft 21. The barrel 22 rotates by the restoring force when the spring 23 is unwound, driving the front side wheel train.

As shown in FIGS. 2 and 3 , the large steel wheel 30 is arranged on the same axis as the barrel wheel 20. The large steel wheel 30 is arranged on the barrel shaft 21 in a manner that allows it to rotate as a whole. The large steel wheel 30 is supported on the barrel splint 12 in a manner that allows it to rotate via the barrel shaft 21. The large steel wheel 30 is arranged on the side opposite to the barrel 22 (i.e., the upper side) by clamping the barrel splint 12. The large steel wheel 30 is arranged in the large steel wheel accommodating portion 13a. The large steel wheel 30 rotates integrally with the barrel shaft 21 in the clockwise direction to wind up the mainspring 23 accommodated in the barrel 22. Due to the restoring force when the mainspring 23 is unwound, a torque in the counterclockwise direction acts on the large steel wheel 30. Teeth 31 are formed on the outer periphery of the large steel wheel 30. A manual winding wheel train is connected to the large steel wheel 30. In the illustrated example, the intermediate wheel 29 that transmits the rotation of the small steel wheel of the manual winding train to the large steel wheel 30 is meshed with the large steel wheel 30 .

Fig. 5 is a perspective view of the pawl unit according to the first embodiment. Fig. 6 is an exploded perspective view of the pawl unit according to the first embodiment.

As shown in FIGS. 5 and 6 , the pawl unit 40 includes a slider seat 41 , a pin 50 , a slider 60 , and a pawl body 70 .

The slider seat 41 is provided separately from the support member 10. The slider seat 41 is formed in a plate shape with the front and back faces in the axial direction. The slider seat 41 is arranged on the side opposite to the large steel wheel 30, sandwiching the barrel splint 12. The slider seat 41 is arranged between the main board 11 and the barrel splint 12. The slider seat 41 is arranged in a manner overlapping with the barrel wheel 20 when viewed from the axial direction. The slider seat 41 is arranged in a recess formed on the lower surface of the barrel splint 12 in a manner not protruding further below than the barrel splint 12. The slider seat 41 is arranged in a manner that cannot be displaced relative to the support member 10. The slider seat 41 is fastened to the barrel splint 12 by screws 42 inserted through from the bottom (refer to Figure 4).

The slider seat 41 is provided with a guide groove 43 extending in a circumferential direction (hereinafter referred to as the circumferential direction) centered on the rotation axis O and a secondary guide groove 44 extending along the guide groove 43 when viewed in the axial direction. The guide groove 43 and the secondary guide groove 44 are respectively opened in the upper surface of the slider seat 41. In the present embodiment, the guide groove 43 and the secondary guide groove 44 respectively penetrate the slider seat 41 in the axial direction.

The guide groove 43 extends with a certain width. The guide groove 43 overlaps with the through-portion 14 of the barrel bridge 12 when viewed from the axial direction. The entire guide groove 43 is located on the inner side of the side wall surface of the through-portion 14 when viewed from the axial direction. The auxiliary guide groove 44 is located at a position that does not overlap with the through-portion 14 of the barrel bridge 12 when viewed from the axial direction. The auxiliary guide groove 44 has an inner auxiliary guide groove 44a that is closer to the rotation axis O than the guide groove 43 and an outer auxiliary guide groove 44b that is located on the opposite side of the inner auxiliary guide groove 44a with the guide groove 43 sandwiched therebetween. The inner auxiliary guide groove 44a and the outer auxiliary guide groove 44b are formed at intervals relative to the guide groove 43, respectively. The inner auxiliary guide groove 44a and the outer auxiliary guide groove 44b extend in the circumferential direction with a certain width, respectively. The side wall surfaces of the guide groove 43 and the auxiliary guide groove 44 are respectively smoothly formed in a continuous manner throughout the entire circumference.

The pin 50 has a central axis P extending in the axial direction. The pin 50 passes through the through portion 14 of the barrel bridge 12. The pin 50 is inserted into the guide groove 43 of the slider seat 41 from above. The pin 50 is arranged so as not to protrude downward from the slider seat 41. The pin 50 can move in the guide groove 43 along the extension direction of the guide groove 43 and rotate along the guide groove 43 around the rotation axis O. The pin 50 is restricted from moving in the circumferential direction by abutting against the slider seat 41 at the end portion of the guide groove 43 in the circumferential direction. The pin 50 includes a pin body 51 and a ratchet screw 53 screwed to the pin body 51.

The pin body 51 passes through the through-portion 14 of the barrel splint 12, and has an upper end located above the barrel splint 12 and a lower end located below the barrel splint 12. The pin body 51 does not contact the side wall surface of the through-portion 14 of the barrel splint 12. The pin body 51 is formed in a cylindrical shape. A female thread is formed on the inner circumferential surface of the pin body 51. The lower end of the pin body 51 is inserted into the guide groove 43 of the slider seat 41. The lower end of the pin body 51 can be displaced along the guide groove 43. At the lower end of the pin body 51, a flange 52 is formed that protrudes outward in the radial direction and extends continuously throughout the entire circumference. The flange 52 is formed in an annular shape centered on the central axis P. The flange 52 is located on the inner side of the guide groove 43. The outer diameter of the flange 52 is substantially consistent with the width of the guide groove 43. The flange 52 has a certain thickness throughout the entirety.

The pawl screw 53 is inserted into the inner side of the pin body 51 from the opposite side of the slider seat 41 while clamping the barrel bridge 12. The pawl screw 53 has a head 54 and a shaft 55. A male thread that is threadedly engaged with the female thread of the pin body 51 is formed at the lower part of the shaft 55. A support shaft portion 55a is formed between the male thread and the head 54. The support shaft portion 55a is located above the upper end surface of the pin body 51. The support shaft portion 55a is formed coaxially with the center axis P. The support shaft portion 55a has a smooth outer peripheral surface. The outer diameter of the support shaft portion 55a is smaller than the outer diameter of the upper end portion of the pin body 51 and the outer diameter of the head 54.

The slider 60 is arranged along the slider seat 41. The slider 60 is arranged between the barrel bridge 12 and the slider seat 41. The slider 60 has a plate-shaped slider body 61 and a rotation stopper 63 provided to protrude from the slider body 61.

The slider body 61 is formed in a plate shape with the front and back faces facing the axial direction. The slider body 61 overlaps with the barrel bridge 12 and the slider seat 41 when viewed from the axial direction. The slider body 61 is formed with a pin hole 62 through which the pin 50 is inserted. The pin hole 62 penetrates the slider body 61 in the axial direction. The slider body 61 is pressed into the pin hole 62 by the pin 50, and the pin 50 is held in a manner that cannot be relatively displaced. The slider body 61 contacts the upper surface of the flange 52 of the pin 50. The slider body 61 is formed in a semicircular shape with the pin hole 62 as the center when viewed from the axial direction, and has a shape in which a portion in the counterclockwise direction is cut off. Thus, the slider body 61 is formed in a manner that extends from the pin hole 62 at least to the clockwise direction and the rotation axis O side. When the pin hole 62 is used as a reference, the clockwise direction and the rotation axis O side coincide with the meshing portion side of the pawl body 70 and the large steel wheel 30 when viewed from the axial direction. The slider body 61 is formed in the following manner: when the pin 50 is located at the end of the guide groove 43 in the clockwise direction, the portion located on the meshing side of the pawl body 70 and the large steel wheel 30 overlaps with the slider seat 41 based on the pin hole 62 when viewed from the axial direction. The upper surface and the lower surface of the slider body 61 are each chamfered. The type of chamfer is not particularly limited, and for example, it may be a chamfer or a rounded corner. Ideally, the curvature of the chamfered portion is greater than 0 [1/mm] and is less than 20 [1/mm].

The stopper 63 protrudes from the slider body 61 toward the slider seat 41. In the present embodiment, the stopper 63 is provided separately from the slider body 61, and is supported on the slider body 61 in a manner that cannot be relatively displaced by being pressed into a through hole formed in the slider body 61. In this case, the stopper 63 is arranged so as not to protrude from the slider body 61 toward the barrel bridge 12. The stopper 63 is provided in a one-to-one correspondence with each of the auxiliary guide grooves 44. The stopper 63 is inserted into the auxiliary guide groove 44. The stopper 63 is arranged so as not to protrude downward from the slider seat 41.

The stopper 63 is formed in a cylindrical shape. The outer diameter of the stopper 63 is smaller than the width of the auxiliary guide groove 44. When the slide seat 41 and the pin 50 are displaced integrally with each other as the pin 50 is displaced in the circumferential direction along the guide groove 43 of the slide seat 41, the stopper 63 can be displaced in the extension direction of the guide groove 43 inside the auxiliary guide groove 44. The stopper 63 limits the displacement in the width direction of the auxiliary guide groove 44 by contacting the side surface of the auxiliary guide groove 44, and always limits the rotation of the slide 60 and the pin 50 around the central axis P. Thus, the stopper 63 allows the pin 50 and the slide 60 to move parallel to each other in the circumferential direction. When the pin 50 is located at the end of the guide groove 43 in the circumferential direction, the stopper 63 is located at the end of the auxiliary guide groove 44 in the circumferential direction, and further displacement in the circumferential direction is limited. However, the stopper 63 slightly allows the pin 50 and the slide 60 to rotate around the central axis P within the range in which the stopper 63 can be displaced within the width of the auxiliary guide groove 44. In addition, in the present embodiment, parallel movement along the circumferential direction and rotational movement around the rotation axis O are substantially synonymous.

The pawl body 70 is arranged on the same side as the large steel wheel 30 in the axial direction relative to the barrel splint 12. The pawl body 70 is formed with an axial hole 71 for inserting the pin 50. The pawl body 70 is rotatably supported on the support shaft portion 55a of the pawl screw 53. Thus, the pawl body 70 is arranged in a manner that allows it to rotate relative to the slider 60 around the central axis P of the pin 50. The pawl body 70 tilts from a predetermined posture together with the pin 50 and the slider 60, and does not contact the barrel splint 12 when the slider 60 is in contact with at least one of the lower surface of the barrel splint 12 and the upper surface of the slider seat 41 and is restricted from further tilting.

FIG. 7 is a plan view of the movement showing the periphery of the large steel wheel according to the first embodiment in an enlarged manner.

As shown in FIG. 7 , the pawl body 70 extends from the central axis P of the pin 50 to both sides in the circumferential direction. The pawl body 70 includes a claw portion 72 and an abutment portion 73. The claw portion 72 meshes with the large steel wheel 30. The claw portion 72 is arranged in a clockwise direction more than the pin 50. The claw portion 72 protrudes toward the rotation axis O side. The claw portion 72 tapers at the end when viewed from the axial direction in such a manner that it enters the tooth groove between a pair of teeth 31 of the large steel wheel 30. The abutment portion 73 is the end face of the pawl body 70 in the counterclockwise direction. The abutment portion 73 is formed in the following manner: when the pin 50 is located near the end of the guide groove 43 in the counterclockwise direction, the abutment portion 73 makes surface contact with the side wall surface of the pawl accommodation portion 13b. When the pawl body 70 is pressed in the counterclockwise direction, the abutment portion 73 makes surface contact with the side wall surface of the pawl accommodation portion 13b, thereby limiting the rotation of the pawl body 70 centered on the pin 50.

Ideally, the slider seat 41, the slider body 61 and the pawl body 70 are formed of a material having a higher yield stress than the barrel splint 12. Ideally, the yield stress of the slider seat 41 is 500 MPa or more, more preferably, 1000 MPa or more. For example, the slider seat 41, the slider body 61 and the pawl body 70 are formed of a metal material such as iron or stainless steel. Furthermore, ideally, a treated layer having a higher wear resistance than its base material is provided on the outer surface of the component that comes into sliding contact with the barrel splint 12. In addition, the slider seat 41, the slider body 61 and the pawl body 70 may also be formed of ceramics.

The pawl spring 80 is arranged in a manner that can press the pawl body 70 to apply the pawl portion 72 of the pawl body 70 toward the large steel wheel 30. The pawl spring 80 is arranged on the same side (upper side) as the pawl body 70 in the axial direction relative to the barrel splint 12. The pawl spring 80 is cantilever-supported on the barrel splint 12. The pawl spring 80 includes a fixing portion 81 fixed to the barrel splint 12 and a spring portion 86 extending from the fixing portion 81 and formed in a manner that can be flexibly deformed, which are formed integrally. The fixing portion 81 is arranged at a position in the clockwise direction relative to the pawl body 70. In the fixing portion 81, a first pin hole 82 for inserting the guide pin 16 and a second pin hole 83 for inserting the stop screw 18 are formed. The fixing portion 81 is restricted from being separated from the barrel splint 12 by the seat surface of the stop screw 18.

The spring portion 86 extends from the fixing portion 81 toward the pawl body 70 in the counterclockwise direction. The distal end of the spring portion 86 is arranged on the side opposite to the large steel wheel 30, sandwiching the pawl body 70. The distal end of the spring portion 86 has a sliding contact surface 87 facing the large steel wheel 30. The sliding contact surface 87 extends in the circumferential direction. The sliding contact surface 87 approaches the rotation axis O side as it moves from its end in the counterclockwise direction toward the clockwise direction. The sliding contact surface 87 has a gap of a degree that allows it to contact the pawl body 70 that swings around the pin 50.

FIG. 8 is a cross-sectional view taken along line VIII-VIII of FIG. 7 .

As shown in FIGS. 7 and 8 , the positioning portion 90 is provided on the barrel bridge 12. The positioning portion 90 is arranged on the side opposite to the guide pin 16 with respect to the cylindrical screw 17 in the circumferential direction. The positioning portion 90 is provided separately from the barrel bridge 12 and is formed in a cylindrical shape. The positioning portion 90 is pressed into a circular hole formed in the barrel bridge 12 and coaxial with the positioning portion 90. The positioning portion 90 protrudes from the barrel bridge 12 to the same side as the pawl spring 80. The positioning portion 90 contacts the spring portion 86 of the pawl spring 80 from the large steel wheel 30 side. The positioning portion 90 contacts a portion of the spring portion 86 of the pawl spring 80 that is closer to the fixing portion 81 side than the terminal portion. The elastic restoring force of the spring portion 86 acts on the positioning portion 90. The positioning portion 90 restricts the terminal end of the spring portion 86 from approaching the pawl body 70 side due to the elastic restoring force of the spring portion 86.

The positioning portion 90 includes a limiting portion 91 extending in a planar direction. The limiting portion 91 is opposed to the spring portion 86 of the pawl spring 80 from the side opposite to the barrel bridge 12. The limiting portion 91 limits the displacement of the spring portion 86 in the axial direction. In the example shown in the figure, the limiting portion 91 abuts against a limiting wall 19 erected on the barrel bridge 12 from the upper side. The limiting wall 19 is formed in a manner covering the shaft portion of the positioning portion 90 from the side opposite to the spring portion 86. The positioning portion 90 is positioned in the up-and-down direction relative to the barrel bridge 12 by the limiting portion 91 abutting against the limiting wall 19.

FIG. 9 is a plan view of the movement showing the operation of the pawl unit according to the first embodiment.

The operation of the pawl body 70 will be described with reference to Fig. 7 and Fig. 9. In the following description, the movement of the pawl body 70 about the pin 50 is referred to as swinging, and the movement of the pawl body 70 about the rotation axis O is referred to as turning.

When the mainspring 23 is wound up, if the large steel wheel 30 is rotated in the clockwise direction, a force in the clockwise direction is applied to the pawl body 70 via the claw portion 72. At this time, if the pawl body 70 attempts to disengage the claw portion 72 from the tooth groove of the large steel wheel 30 and swings in the counterclockwise direction, the pawl body 70 contacts the pawl spring 80 and is pressed toward the large steel wheel 30. Therefore, the claw portion 72 maintains a state of meshing with the large steel wheel 30.

Here, the pawl body 70 is supported by the pin 50, and thus rotates in the clockwise direction together with the pin 50 which is guided by the guide groove 43 of the slider seat 41 and moves in the guide groove 43. At this time, the outer peripheral surface of the pin 50 (the outer peripheral surface of the flange 52 of the pin body 51) slides on the side wall surface of the guide groove 43. The pawl body 70 does not contact the barrel bridge 12 when rotating.

If the pin 50 reaches the vicinity of the end of the guide groove 43 in the clockwise direction as the large steel wheel 30 rotates in the clockwise direction, the clockwise rotation of the pawl body 70 is restricted. In this state, if the large steel wheel 30 is further rotated in the clockwise direction, the pawl body 70 swings in the counterclockwise direction so that the claw portion 72 is disengaged from the tooth groove of the large steel wheel 30. On the other hand, if the pawl body 70 swings in the counterclockwise direction, the pawl spring 80 contacts the pawl body 70 and presses the pawl body 70 toward the large steel wheel 30. Therefore, if the claw portion 72 passes over the tooth top of the large steel wheel 30, the pawl body 70 swings in the clockwise direction so that the claw portion 72 enters the tooth groove. In this way, if the large steel wheel 30 is rotated in the clockwise direction, the pawl body 70 swings back and forth so that the teeth 31 of the large steel wheel 30 pass over the claw portion 72 one by one (refer to Figure 9). Thus, when the pawl body 70 swings, the inner peripheral surface of the shaft hole 71 of the pawl body 70 slides on the outer peripheral surface of the support shaft portion 55 a of the pawl screw 53 .

The pawl spring 80 contacts the pawl body 70 when the claw portion 72 swings to pass over the teeth 31 of the large steel wheel 30, regardless of the circumferential position of the pawl body 70. In addition, the pawl spring 80 has a gap relative to the pawl body 70 in at least a portion of the state in which the claw portion 72 is engaged with the large steel wheel 30 and the pawl body 70 rotates. In the present embodiment, the pawl spring 80 has a gap relative to the pawl body 70 when the pawl body 70 is located at the end of the rotation range in the counterclockwise direction and the claw portion 72 is engaged with the large steel wheel 30 (refer to FIG. 7). The pawl spring 80 has a gap relative to the pawl body 70 when the pawl body 70 is located at the end of the rotation range in the clockwise direction and the claw portion 72 is engaged with the large steel wheel 30 (refer to FIG. 9). That is, the pawl body 70 has a gap relative to the pawl spring 80 during the entire process of rotating the claw portion 72 in engagement with the large steel wheel 30. However, the pawl body 70 may transition from a state in which it is allowed to separate from the pawl spring 80 to a state in which it is forcibly in contact with the pawl spring 80 during the process of rotating in the clockwise direction by engaging the pawl portion 72 with the large steel wheel 30 .

If the winding of the mainspring 23 is stopped, the restoring force of the unwinding of the mainspring 23 causes a counterclockwise torque to act on the large steel wheel 30. As a result, the large steel wheel 30 begins to reverse in the counterclockwise direction. At this time, the pawl body 70 maintains the state of engagement between the pawl portion 72 and the large steel wheel 30 by the pawl spring 80, similarly to when the mainspring 23 is wound, and thus rotates in the counterclockwise direction together with the pin 50 and the slider 60 as the large steel wheel 30 reverses.

If the pin 50 reaches the vicinity of the counterclockwise end of the guide groove 43 as the large steel wheel 30 reverses in the counterclockwise direction, the contact portion 73 of the pawl body 70 makes surface contact with the side wall surface of the pawl accommodation portion 13b. At this time, the contact portion 73 is pressed against the side wall surface of the pawl accommodation portion 13b by the large steel wheel 30 in the counterclockwise direction, so that the pawl body 70 is restricted from swinging. As a result, the pawl portion 72 maintains a state of meshing with the large steel wheel 30, thereby restricting the counterclockwise rotation of the large steel wheel 30.

As described above, the movement 9 of this embodiment includes: the slider seat 41, which is arranged in a manner that cannot be displaced relative to the barrel bridge 12, and is formed with the guide groove 43 extending in the circumferential direction with the rotation axis O as the center; the pin 50, which has the center axis P extending in the axial direction, is inserted into the guide groove 43, and is displaced along the guide groove 43 with the rotation axis O as the center; the slider 60, which is arranged along the slider seat 41 and holds the pin 50; and the pawl body 70, which is supported by the pin 50, is arranged in a manner that can rotate relative to the barrel bridge 12 with the center axis P as the center, and has the claw portion 72 that meshes with the large steel wheel 30. According to this structure, when the mainspring 23 is wound up, if the large steel wheel 30 is rotated, the pawl body 70 is applied with a force in the rotation direction of the large steel wheel 30 via the claw portion 72. Here, the pawl body 70 is supported by the pin 50, and thus rotates in the same direction as the large steel wheel 30 together with the pin 50 guided by the guide groove 43 and moving in the guide groove 43 around the rotation axis O. If the winding of the mainspring 23 is stopped, a torque in the direction opposite to the rotation direction during winding acts on the large steel wheel 30 due to the restoring force of the unwinding of the mainspring 23. Then, the large steel wheel 30 starts to reverse. At this time, the pawl body 70 rotates in the same direction as the large steel wheel 30 around the rotation axis O together with the pin 50 as the large steel wheel 30 reverses. In this way, when the winding of the mainspring 23 is stopped, the length of the guide groove 43 is allowed to rotate with the rotation of the pawl body 70 and the reversal of the large steel wheel 30, so that the excessive torque of the mainspring 23 can be suppressed from being transmitted to the escapement/speed regulating mechanism.

Furthermore, a guide groove 43 for guiding the rotation of the pawl body 70 around the rotation axis O is formed in the slider seat 41, thereby preventing the pawl body 70 and the pin 50 from sliding in contact with the upper surface of the barrel bridge 12 when the pawl body 70 and the pin 50 rotate around the rotation axis O. Therefore, the wear resistance of the movement 9 against the rotation of the pawl body 70 around the rotation axis O can be improved without changing the material or performing surface treatment on the barrel bridge 12. Furthermore, the slider 60 for holding the pin 50 is arranged along the slider seat 41, thereby preventing the pin 50 from tilting relative to the slider seat 41, and preventing the pawl body 70 supported by the pin 50 from accidentally sliding in contact with the upper surface of the barrel bridge 12. Therefore, in the movement 9 that can prevent the excessive torque of the mainspring 23 from being transmitted to the escapement/speed regulating mechanism, the wear of the parts can be suppressed without deteriorating the appearance of the movement.

Furthermore, since the slider seat 41, the pin 50, the slider 60 and the pawl body 70 can be made into a unit, when the unit is worn, the worn parts can be replaced by replacing the unit without replacing the barrel bridge 12. Therefore, after-sales serviceability can be improved.

The slider 60 is disposed between the barrel bridge 12 and the slider seat 41. According to this configuration, the portion where the slider 60 slides relative to the barrel bridge 12 and the slider seat 41 as the pin 50 rotates is located between the barrel bridge 12 and the slider seat 41. Thus, even if oil is injected into the sliding portion between the barrel bridge 12 and the slider 60 and the sliding portion between the slider seat 41 and the slider 60, it is possible to suppress oil from seeping out onto the outer surface of the movement 9. Therefore, it is possible to suppress deterioration of the appearance of the movement 9.

Furthermore, the slider seat 41 is disposed on the lower side of the barrel bridge 12. According to this configuration, the portion where the slider 60 slides relative to the barrel bridge 12 and the slider seat 41 as the pin 50 rotates is located on the lower side of the barrel bridge 12. Thus, it is possible to prevent the oil injected into the sliding portion of the slider 60 from seeping out to the surface side of the barrel bridge 12 on the appearance of the movement 9. Therefore, it is possible to prevent the appearance of the movement 9 from deteriorating.

The pawl body 70 is rotatably supported on the pin 50. According to this configuration, a sliding portion generated when the pawl body 70 rotates around the central axis P of the pin 50 is generated at a contact portion between the pawl body 70 and the pin 50. Thus, the sliding portion generated when the pawl body 70 rotates around the rotation axis O and the sliding portion generated when the pawl body 70 rotates around the central axis P of the pin 50 can be separated. Therefore, the sliding portion generated during the operation related to the winding of the mainspring 23 can be dispersed to suppress the wear of the parts.

The slider seat 41 is provided with a secondary guide groove 44 extending along the guide groove 43 when viewed from the axial direction. The slider 60 has a stopper 63 that can be inserted into the secondary guide groove 44 and displaced along the extension direction of the guide groove 43 on the inner side of the secondary guide groove 44. The slider 60 is restricted from displacement in the width direction of the secondary guide groove 44 by the stopper 63, and is restricted from rotating around the center axis P when the pin 50 is displaced around the rotation axis O. According to this configuration, when the pin 50 rotates around the rotation axis O, the slider 60 can be prevented from rotating around the center axis P. As a result, the slider 60 can be rotated around the rotation axis O in a desired posture. Therefore, during the action related to the winding of the mainspring 23, the occurrence of an unexpected sliding portion can be prevented.

The yield stress of the slider seat 41 is greater than the yield stress of the barrel bridge 12. According to this structure, the slider seat 41 can have a higher hardness than the barrel bridge 12 and is less likely to wear. As a result, compared with a structure in which a groove or a long hole for guiding the rotation of the guide pin 50 around the rotation axis O is formed in the barrel bridge 12 instead of the slider seat 41, the wear resistance of the movement 9 against the rotation of the pawl body 70 around the rotation axis O can be improved.

The pin 50 is restricted from moving in the circumferential direction by abutting against the slider seat 41 at the circumferential end of the guide groove 43. According to this configuration, the rotation range of the pawl body 70 around the rotation axis O can be defined by the pin 50 and the slider seat 41 without using other parts. Therefore, the movement 9 can be obtained while suppressing the increase in the number of parts and the deterioration of the assembly performance and achieving the above-mentioned effects.

The slider 60 extends from the pin hole 62 to the meshing portion side of the pawl body 70 and the large steel wheel 30 in a manner overlapping with the slider seat 41 when viewed from the axial direction. According to this configuration, in a state where the end of the pin 50 in the clockwise direction of the guide groove 43 abuts against the slider seat 41, when the pawl body 70 is pulled by the large steel wheel 30, the portion of the slider 60 extending from the pin hole 62 to the meshing portion side of the pawl body 70 and the large steel wheel 30 abuts against the slider seat 41, and the slider 60 can be suppressed from tilting. Therefore, it is also possible to suppress the pin 50 and the pawl body 70 from tilting from a predetermined posture, and it is possible to suppress the pawl body 70 from contacting the barrel bridge 12.

The movement 9 also includes a positioning portion 90 that limits the pawl spring 80 from approaching the pawl body 70. The pawl spring 80 is supported by a cantilever, and the positioning portion 90 includes a limiting portion 91 that extends in a plane direction to limit the displacement of the pawl spring 80 in the axial direction. According to this structure, by making the pawl spring 80 always contact the positioning portion 90 in a force-applied state, the deviation of the gap between the pawl spring 80 and the pawl body 70 can be suppressed, and the movement of the pawl body 70 can be stabilized. Furthermore, in the case where the pawl spring 80 supported by the cantilever is about to bend due to an impact such as falling, the displacement of the pawl spring 80 can be limited by the limiting portion 91. Therefore, the pawl spring 80 can be suppressed from deviating from a predetermined position relative to the pawl body 70.

The upper edge of the cylindrical screw 17 is located below the upper edge of the guide pin 16. According to this configuration, when the click spring 80 is assembled to the barrel bridge 12, when the click spring 80 is tilted so that the spring portion 86 is inserted into the lower side of the limiting portion 91 of the positioning portion 90, the positions of the upper edges of the cylindrical screw 17 and the guide pin 16 can be matched with the tilt of the click spring 80. That is, the upper edge of the cylindrical screw 17 arranged closer to the fixing portion 81 than the guide pin 16 with respect to the upper edge of the guide pin 16 is arranged on the lower side, and thus the upper edges of the cylindrical screw 17 and the guide pin 16 are arranged along the lower surface of the click spring 80 tilted in such a way that the spring portion 86 is located below the fixing portion 81. As a result, when the click spring 80 is assembled to the barrel bridge 12, the angle at which the click spring 80 is tilted can be suppressed from becoming larger. Therefore, the movement 9 that is easy to assemble can be obtained.

Furthermore, the timepiece 1 of the present embodiment includes the above-described movement 9 and can therefore be a highly reliable timepiece having excellent appearance and precision and with suppressed wear of parts.

[Second embodiment]

Next, the second embodiment will be described with reference to FIG. 10 . In the first embodiment, the pin 50 and the slider 60 are provided separately. In contrast, in the second embodiment, the pin 150 and the slider 160 are formed integrally, which is different from the first embodiment. In addition, the configuration other than that described below is the same as that of the first embodiment.

10 is a longitudinal sectional view of a slider and a pin body according to a second embodiment.

As shown in FIG. 10 , the ratchet unit 40 includes a slider 160 and a pin 150 instead of the slider 60 and the pin 50 of the first embodiment. The slider 160 includes a slider body 161 and a stopper 163 formed integrally with each other, which is equivalent to a configuration in which the slider body 61 and the stopper 63 of the first embodiment are integrated. The pin 150 includes a pin body 151 formed integrally with the slider body 161. The pin body 151 is equivalent to a configuration in which the pin body 51 of the first embodiment and the slider body 161 are integrated. The ratchet screw 53 is threadedly fixed to the pin body 151.

In this embodiment, the same effects as those of the first embodiment are achieved. In addition, according to this embodiment, the pin 150 and the slider 160 are integrally formed, so the number of parts can be reduced compared to a configuration in which the pin and the slider are separately provided, and the assemblability of the movement 9 can be improved.

[Third Embodiment]

Next, the third embodiment will be described with reference to Fig. 11 to Fig. 13. In the first embodiment, the pin 50 supports the pawl body 70 in a rotatable manner. In contrast, the third embodiment is different from the first embodiment in that the pin 350 supports the pawl body 70 in a non-rotatable manner. In addition, the configuration other than that described below is the same as that of the first embodiment.

FIG. 11 is a cross-sectional view of a movement according to the third embodiment, and is an enlarged view of a cross section corresponding to FIG. 3 .

As shown in Fig. 11, the pawl unit 40 includes a slider seat 341 and a pin 350 instead of the slider seat 41 and the pin 50 of the first embodiment. The pin 350 is fixed by sandwiching a pawl body 70 between the upper end surface of the pin body 51 and the head 54 of the pawl screw 53. That is, the pawl body 70 is provided in a manner that cannot rotate relative to the slider 60.

FIG. 12 is a plan view showing a slider seat according to a third embodiment.

As shown in FIG12 , an inner auxiliary guide groove 344a is formed in the slider seat 341 instead of the inner auxiliary guide groove 44a of the first embodiment. The inner auxiliary guide groove 344a extends further in the clockwise direction than the position where the stopper 63 is located when the pin 350 is located at the end of the guide groove 43 in the clockwise direction when the pawl body 70 and the large steel wheel 30 are meshed. In addition, in FIG12 , the pin 350 and the stopper 63 are shown by imaginary lines when the pin 350 is located at the end of the guide groove 43 in the clockwise direction when the pawl body 70 and the large steel wheel 30 are meshed.

FIG. 13 is a plan view of a movement showing an enlarged view of the periphery of a large steel wheel according to the third embodiment.

As shown in FIG. 13 , if the large steel wheel 30 is further rotated in the clockwise direction while the pin 350 is located near the end of the guide groove 43 in the clockwise direction, the ratchet body 70 is intended to swing in the counterclockwise direction together with the slider 60 in such a manner that the claw portion 72 is disengaged from the tooth groove of the large steel wheel 30. At this time, the stopper 63 inserted into the inner auxiliary guide groove 344a is further displaced in the clockwise direction along the circumferential direction in the inner auxiliary guide groove 344a, and the stopper 63 inserted into the outer auxiliary guide groove 44b is displaced in the counterclockwise direction along the circumferential direction in the outer auxiliary guide groove 44b, so that the slider 60 rotates in the counterclockwise direction with the pin 350 and the ratchet body 70 around the central axis P. That is, in the present embodiment, when the pin 350 is displaced about the rotation axis O, the stopper 63 contacts the side surfaces of the auxiliary guide grooves 344 a and 44 b to restrict displacement in the width direction of the auxiliary guide groove 44 , thereby restricting the slider 60 and the pin 350 from rotating about the central axis P. On the other hand, when the pin 350 is located at the end of the guide groove 43 in the clockwise direction, the stopper 63 allows the slider 60 and the pin 350 to swing.

In this embodiment, the same effects as those of the first embodiment are achieved. In addition, according to this embodiment, the pawl body 70 is arranged in a manner that cannot rotate relative to the slider 60, so when the pin 350 rotates around the rotation axis O, the pawl body 70 can be suppressed from rotating around the pin 350. As a result, the pawl body 70 can be suppressed from contacting with surrounding parts such as the pawl spring 80 with a force greater than necessary due to the rotation around the pin 350 at unnecessary times such as when the pawl body 70 is displaced around the rotation axis O, thereby suppressing the occurrence of wear.

In addition, in the present embodiment, the pawl body 70 is fixed to the pin 350 by the pawl screw 53, but the fixing method of the pawl body is not limited thereto. For example, the pawl body may be driven into the pin to be fixed, or may be set in a manner that cannot rotate relative to the pin by an angle guide. In addition, the pawl body may be bonded to the pin.

[Fourth embodiment]

Next, the fourth embodiment will be described with reference to FIG. 14. In the first embodiment, the auxiliary guide groove 44 for inserting the anti-rotation member 63 is formed in the slider seat 41. In contrast, the fourth embodiment is different from the first embodiment in that the auxiliary guide groove 15 for inserting the anti-rotation member 463 is formed in the barrel bridge 12. In addition, the configuration other than that described below is the same as that of the first embodiment.

FIG. 14 is a cross-sectional view of a movement according to a fourth embodiment, and is an enlarged view of a cross section corresponding to FIG. 3 .

As shown in FIG. 14 , a secondary guide groove 15 is formed on the lower surface of the barrel splint 12. The secondary guide groove 15 does not penetrate the barrel splint 12. The secondary guide groove 15 is formed away from the through portion 14. The secondary guide groove 15 has an inner secondary guide groove 15a that is closer to the rotation axis O than the through portion 14, and an outer secondary guide groove 15b that is located on the opposite side of the inner secondary guide groove 15a across the through portion 14. The inner secondary guide groove 15a and the outer secondary guide groove 15b are formed at intervals relative to the through portion 14. The inner secondary guide groove 15a and the outer secondary guide groove 15b extend in the circumferential direction with a certain width. In the present embodiment, the shape of the secondary guide groove 15 is consistent with the shape of the secondary guide groove 44 of the first embodiment when viewed from the axial direction.

The pawl unit 40 includes a slider seat 441 and a slider 460 instead of the slider seat 41 and the slider 60 of the first embodiment. The slider seat 441 is formed in the same manner as the slider seat 41 of the first embodiment except that the auxiliary guide groove is not formed. The slider 460 includes a stopper 463 instead of the stopper 63 of the first embodiment. The stopper 463 protrudes from the slider body 61 toward the barrel bridge 12 side. In the present embodiment, the stopper 463 is provided separately from the slider body 61, and is supported by the slider body 61 in a manner that cannot be relatively displaced by being pressed into a through hole formed in the slider body 61. In this case, the stopper 463 is arranged so as not to protrude from the slider body 61 toward the slider seat 441 side. The stopper 463 is provided in a one-to-one correspondence with each auxiliary guide groove 15. The stopper 463 is inserted into the auxiliary guide groove 15.

In this embodiment, the stopper 463 makes the pin 50 and the slider 460 move in parallel along the circumferential direction, thereby achieving the same effect as in the first embodiment. In addition, according to this embodiment, the slider seat 441 is not provided with a secondary guide groove, thereby improving the strength of the slider seat 441.

[Fifth embodiment]

Next, the fifth embodiment will be described with reference to FIG15. In the first embodiment, the pawl body 70 is directly supported on the pin 50. In contrast, the fifth embodiment is different from the first embodiment in that the pawl body 70 is supported on the pin 50 via the spacer 558 (first spacer). In addition, the configuration other than that described below is the same as that of the first embodiment.

FIG. 15 is a cross-sectional view showing a part of the pawl unit according to the fifth embodiment.

As shown in FIG. 15 , the pawl unit 40 further includes a spacer 558. The spacer 558 is formed of a metal material. The spacer 558 is formed in a cylindrical shape. The inner circumference and the outer circumference of the spacer 558 extend in the axial direction at a certain diameter. The spacer 558 is inserted outside the support shaft portion 55a of the pawl screw 53, and is interposed between the outer circumference of the pawl screw 53 and the inner circumference of the shaft hole 71 of the pawl body 70. The spacer 558 can rotate relative to at least one of the pin 50 and the pawl body 70.

In this embodiment, the same effects as those of the first embodiment are achieved. In addition, in this embodiment, compared with the configuration in which the pawl body 70 is in sliding contact with the pin, the sliding resistance accompanying the rotation of the pawl body 70 around the central axis P can be reduced. Therefore, the pawl body 70 can be operated smoothly. In addition, the wear of the pin 50 and the pawl body 70 can be suppressed.

In addition, the spacer 558 does not need to be formed of a metal material, but may be a gemstone such as ruby or zirconium oxide. In this way, the same effects as those of the fifth embodiment described above are achieved.

[Sixth embodiment]

Next, the sixth embodiment will be described with reference to FIG. 16. In the first embodiment, the pin 50 is in sliding contact with the side wall surface of the guide groove 43 of the slider seat 41. In contrast, the sixth embodiment is different from the first embodiment in that the spacer 658 (second spacer) externally inserted into the pin 50 is in sliding contact with the side wall surface of the guide groove 43. In addition, the configuration other than that described below is the same as that of the first embodiment.

FIG. 16 is a cross-sectional view showing a pawl unit according to a sixth embodiment.

As shown in FIG. 16 , the pawl unit 40 includes a pin body 651 instead of the pin body 51 of the first embodiment. The lower end of the pin body 651 includes a flange 52 located inside the guide groove 43 and a protrusion 656 adjacent to the lower side of the flange 52 and protruding radially outward from the flange 52. The outer diameter of the flange 52 is smaller than the width of the guide groove 43. The protrusion 656 is located below the guide groove 43. The protrusion 656 is formed in an annular shape extending continuously around the entire circumference with the central axis P as the center. The outer diameter of the protrusion 656 is larger than the width of the guide groove 43.

The pawl unit 40 also includes a spacer 658. The spacer 658 is formed of a metal material. The spacer 658 is formed in a cylindrical shape. The inner circumferential surface and the outer circumferential surface of the spacer 658 extend in the axial direction at a certain diameter. The spacer 658 is externally inserted into the flange 52 of the pin body 651. The spacer 658 is supported on the pin body 651 in a rotatable manner. The outer diameter of the spacer 658 is substantially consistent with the width of the guide groove 43. The spacer 658 is located on the inner side of the guide groove 43 and is seated on the protrusion 656 of the pin body 651. The outer circumferential surface of the spacer 658 is directly opposite to the side wall surface of the guide groove 43 and is in sliding contact with the side wall surface of the guide groove 43. The inner diameter of the spacer 658 is smaller than the width of the guide groove 43.

In this embodiment, the same effect as in the first embodiment is achieved. In addition, in this embodiment, when the pin 50 is displaced in the circumferential direction in the guide groove 43, the spacer 658 inserted into the pin body 651 can be made to slide in contact with the side wall surface of the guide groove 43, and the spacer 658 can be made to rotate and roll on the side wall surface of the guide groove 43. As a result, compared with the structure in which the pin body and the side wall surface of the guide groove 43 are in direct sliding contact, the sliding resistance accompanying the displacement of the pin 50 in the circumferential direction can be reduced. Therefore, the pawl body 70 can be made to move smoothly. In addition, the wear of the pin 50 and the slider seat 41 can be suppressed.

In addition, the spacer 658 may not be formed of a metal material, but may be a gemstone such as ruby or zirconium oxide. In this case, the spacer 658 may be pressed into the flange 52 of the pin body 651 and supported on the pin body 651 in a non-rotatable manner. By making the spacer 658 a gemstone, when the pin 50 is displaced in the circumferential direction in the guide groove 43, the gemstone inserted into the pin body 651 can be in sliding contact with the side wall surface of the guide groove 43. As a result, compared with the configuration in which the pin body and the side wall surface of the guide groove 43 are in direct sliding contact, the wear of the pin 50 and the slider seat 41 can be suppressed.

[Seventh embodiment]

Next, the seventh embodiment will be described with reference to FIG17 . In the first embodiment, the pawl spring 80 is provided separately from the pawl unit 40. In contrast, the seventh embodiment is different from the first embodiment in that the pawl spring 780 is incorporated into the pawl unit 40. In addition, the configuration other than that described below is the same as that of the first embodiment.

FIG. 17 is a cross-sectional view showing a part of the pawl unit according to the seventh embodiment.

17, the pawl spring 780 directly urges the pawl body 70 relative to the pin 50. The pawl spring 780 is interposed between the upper end surface of the pin body 51 and the lower surface of the pawl body 70. The pawl spring 780 is a torsion coil spring having one end engaged with the pin body 51 and the other end engaged with the pawl body 70.

In this embodiment, the same effect as in the first embodiment is achieved. In addition, in this embodiment, the pawl spring 80 can be omitted, and the grinding of the pawl spring 80 and the pawl body 70 caused by the sliding of the pawl spring 80 and the pawl body 70 will not occur, and the pawl body 70 can be always pressed to apply force to the claw portion 72 of the pawl body 70 toward the large steel wheel 30.

In addition, the present invention is not limited to the above-mentioned embodiment described with reference to the drawings, and various modifications are conceivable within the technical scope of the present invention.

For example, in the above-described embodiment, the guide groove 43 penetrates the slider seat 41 in the axial direction, but the guide groove may not penetrate the slider seat. The same is true for the auxiliary guide groove formed in the slider seat.

In the above embodiment, the large steel wheel 30 is arranged on the upper side of the barrel splint 12, but the large steel wheel may be arranged on the lower side of the barrel splint. In this case, even if the slider seat and the slider are arranged on the upper side of the barrel splint, since the sliding contact part of the slider is located on the lower side of the slider seat, it is possible to prevent the oil injected into the sliding part of the slider from seeping out to the surface side of the slider seat on the appearance of the movement. Therefore, it is possible to prevent the deterioration of the appearance of the movement.

In the above embodiment, the pin 50 supports the pawl body 70 by screwing the pawl screw 53 to the pin body 51 , but the present invention is not limited to this configuration. For example, a member replacing the pawl screw 53 may be press-fitted into the inside of the pin body 51 .

In the above embodiment, the pawl body 70 is supported by the pawl screw 53 of the pin 50, but the present invention is not limited to this structure. The pawl body may be externally inserted into the pin body and supported by the pin body.

In the above-mentioned embodiment, the slider 60 is formed in a semicircular shape when viewed from above, but the shape of the slider is not particularly limited. For example, the slider can also be formed in a rectangular shape when viewed from above. However, it is ideal that the slider is formed in a manner that extends from the pin hole 62 at least in the clockwise direction and on the side of the rotation axis O, regardless of its shape when viewed from above. Thus, when the pawl body 70 is pulled by the large steel wheel 30, the slider abuts against the slider seat 41, which can suppress the slider from tilting. Therefore, it is also possible to suppress the pin 50 and the pawl body 70 from tilting from a predetermined posture, and it is possible to suppress the pawl body 70 from contacting the barrel splint 12.

In the above embodiment, the positioning portion 90 includes the restricting portion 91 extending in the planar direction, but the present invention is not limited to this configuration. The positioning portion may not include the restricting portion 91. In this case, the positioning portion may be formed integrally with the barrel bridge 12.

In the above-mentioned embodiment, the positioning portion 90 is formed coaxially with the circular hole formed in the barrel splint 12, but is not limited to this configuration. The positioning portion may also be an eccentric pin. That is, the positioning portion may also include an eccentric shaft portion that is eccentric with respect to the central axis of the circular hole of the barrel splint 12. In this case, by making the spring portion 86 abut against the outer peripheral surface of the eccentric shaft portion, the amount of flexural deformation of the spring portion 86 can be adjusted according to the angle of the positioning portion relative to the barrel splint 12. Therefore, the position of the sliding contact surface 87 of the spring portion 86 relative to the pawl body 70 can be easily adjusted.

Furthermore, components in the above-described embodiments may be appropriately replaced with well-known components without departing from the spirit of the present invention, and the above-described embodiments and modifications may be appropriately combined.

Description of Reference Numerals

1...Watch 9...Movement (watch movement) 12...Barrel bridge 15, 44...Auxiliary guide groove 23...Spring 30...Large steel wheel 41, 341, 441...Slider seat 43...Guide groove 50, 150, 350...Pin 60, 160, 460...Slider 70...Pawl body 72...Pawl portion 80...Pawl spring 90...Positioning portion 91...Restricting portion 558...Spacer (1st spacer) 658...Spacer (2nd spacer) O...Rotation axis P...Center axis.

Claims (12)

1. A watch movement, comprising: A large steel wheel, which is arranged in such a way that the mainspring can be wound up tightly; a barrel bridge which supports the large steel wheel in a manner rotatable about a rotation axis; a slider seat arranged in a manner that cannot be displaced relative to the barrel bridge, and having a guide groove formed therein extending in a circumferential direction centered on the rotation axis; a pin having a central axis extending in the axial direction of the rotation axis, inserted into the guide groove, and displaced along the guide groove with the rotation axis as the center; a slider disposed along the slider seat and holding the pin; and The pawl body is supported by the pin, is disposed so as to be rotatable about the central axis relative to the barrel bridge, and has a pawl portion that meshes with the large steel wheel. 2. The watch movement according to claim 1, wherein: The slider is disposed between the barrel bridge and the slider seat. 3. The watch movement according to claim 1, wherein: The pawl body is rotatably supported by the pin. 4. The timepiece movement according to claim 1, wherein: A secondary guide groove extending along the guide groove as viewed in the axial direction is formed in one of the barrel bridge and the slider seat, The sliding member has a stopper that can be inserted into the secondary guide groove and displaced along the extension direction of the guide groove on the inner side of the secondary guide groove. The displacement in the width direction of the secondary guide groove is restricted by the stopper, and when the pin is displaced around the rotation axis, the rotation around the center axis is restricted. 5. The timepiece movement according to claim 4, wherein: The pawl body is arranged in a non-rotatable manner relative to the sliding member. 6. The timepiece movement according to claim 1, wherein: The pin is integrally formed with the slider. 7. The timepiece movement according to claim 1, wherein: The yield stress of the slider seat is greater than the yield stress of the barrel bridge. 8. The timepiece movement according to claim 1, wherein: The pin abuts against the slider seat at an end portion of the guide groove in the circumferential direction, and movement in the circumferential direction is restricted. 9. The timepiece movement according to claim 1, further comprising: a ratchet spring disposed on the outer side of the ratchet body and arranged in a manner capable of pressing the ratchet body to force the pawl portion toward the large steel wheel; and a positioning portion that limits the pawl spring from approaching the pawl body side, The pawl spring is supported by a cantilever, The positioning portion includes a restricting portion that extends in a direction orthogonal to the axial direction to restrict displacement of the click spring in the axial direction. 10. The timepiece movement according to claim 1, wherein: The invention further includes a first spacer which is inserted outside the pin and interposed between the pin and the pawl body. 11. The timepiece movement according to claim 1, wherein: A second spacer is further provided which is inserted outside the pin inside the guide groove. 12 . A timepiece comprising the timepiece movement according to claim 1 .