JP2019132652A - Wind-up force transmission mechanism, movement and mechanical timepiece - Google Patents

Abstract

To provide a wind-up force transmission mechanism capable of effectively reducing energy loss during automatic winding-up, and also to provide a movement and a mechanical timepiece.SOLUTION: A wind-up force transmission mechanism includes: an oscillation transmission wheel 33 which is meshed with a round hole wheel 20 rotated by operation of a winding stem 17; an oscillating wheel 34 meshed with the oscillation transmission wheel 33, provided swingably around a shaft center C of the oscillation transmission wheel 33 and moving between a meshing position meshed with a square hole wheel 14 and a retracted position where meshing with the square hole wheel 14 is released; and a swing lever 40 capable of holding the oscillating wheel 34 at the retracted position.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a hoisting force transmission mechanism, a movement, and a mechanical timepiece.

A mechanical timepiece that uses a mainspring as an energy source for driving a train wheel may use both a manual winding mechanism that operates a winding stem and an automatic winding mechanism that rotates a rotating weight as a mechanism for winding the mainspring. .
The manual hoisting mechanism manually rotates the crown integrated with the winding stem, and transmits the rotation from the continuous wheel to the transmission wheel via the chichi-car, round-hole wheel, and transmission intermediate wheel. Then, the square hole wheel meshed with the transmission wheel is rotated to wind up the mainspring.
On the other hand, the automatic hoisting mechanism transmits the rotation of the rotary weight from the outer ring (the first car) integrated with it to the first transmission wheel, drives the feeding member with the first wheel, and drives the transmission wheel by driving the feeding member. Rotate in one direction. Thereby, the square hole wheel meshed with the transmission wheel is rotated to wind up the mainspring.

  Here, in the automatic winding mechanism, the transmission wheel is rotated in one direction by the feed member, and the transmission intermediate wheel of the manual winding mechanism is engaged with the transmission wheel. In such a configuration, the rotational energy of the rotary weight in the automatic winding mechanism is not consumed only for winding the mainspring, but the transmission intermediate wheel, round hole wheel, and chichi wheel of the manual winding mechanism are rotated. Will be consumed. For this reason, a technique has been proposed in which the transmission intermediate wheel is made swingable and the engagement between the transmission intermediate wheel and the transmission wheel is released when the automatic winding mechanism is operated.

  In addition, this has a spring-like holding member for maintaining the meshing state between the transmission intermediate wheel and the transmission wheel during automatic winding. Thereby, at the time of manual winding, the meshing state of the transmission intermediate wheel and the transmission wheel is maintained. On the other hand, at the time of automatic winding, the transmission intermediate wheel and the transmission wheel are disengaged against the spring force of the holding member, and the transmission intermediate wheel, the round hole wheel, and the chisel wheel are not rotated. As a result, the energy loss of the automatic winding mechanism is reduced.

JP 2003-279667 A

  However, in the above-described prior art, it is necessary to operate the automatic winding mechanism against the spring force of the holding member during automatic winding. For this reason, it is difficult to effectively solve the energy loss of the automatic winding mechanism.

  Accordingly, the present invention provides a hoisting force transmission mechanism, a movement, and a mechanical timepiece that can effectively reduce energy loss during automatic winding.

  In order to solve the above-described problems, a hoisting force transmission mechanism according to the present invention is engaged with a swing transmission wheel meshed with a round hole wheel that is rotated by a winding stem operation, and meshed with the swing transmission wheel. A swing wheel provided so as to be swingable about the rotation center of the swing transmission wheel and moving to a meshing position meshed with the square hole wheel and a retreat position where meshing with the square hole wheel is released; And a retracted position holding means capable of holding the rocking wheel at the retracted position.

  In this way, the swinging wheel is held at the retracted position where the meshing with the square hole wheel is released by the retracted position holding means. That is, when rotating the square hole wheel during automatic winding, the square hole wheel and the rocking wheel are not meshed, and the state is maintained. For this reason, it is possible to prevent the rotation of the square hole wheel from being transmitted to the swing transmission wheel or the round hole wheel without applying an extra load to the square hole wheel. Therefore, the energy loss at the time of automatic winding can be reduced effectively.

  The hoisting force transmission mechanism according to the present invention is characterized in that it includes meshing position holding means capable of holding the rocking wheel at the meshing position.

  With this configuration, the swing wheel and the square hole wheel can be engaged with each other during manual winding. For this reason, the frequency | count of the sound and impact which generate | occur | produce at the time of mesh | engagement of a rocking wheel and a square hole wheel can be reduced as much as possible. For this reason, an easy-to-use hoisting force transmission mechanism can be provided.

  A hoisting force transmission mechanism according to the present invention includes a rocking support that supports the rocking wheel and has an opening formed along a rocking locus of the rocking wheel. It is fixed to one end of the inserted swing axle, and a flange portion that contacts the swing receiver is provided at the base end of the swing receiver of the swing axle so that the retracted position is maintained. The means and the meshing position holding means are elastic bodies that bias a force that presses the flange portion against the swinging receiver.

  With this configuration, the rocking wheel can be held at the retracted position or the meshing position by using frictional resistance generated when the flange portion is pressed against the rocking receiver. For this reason, the retracted position holding means and the meshing position holding means can be reduced in size as much as possible with a simple structure.

  In the hoisting force transmission mechanism according to the present invention, the elastic body is a leaf spring having a distal end interposed between the swing receiver and the swing wheel, and a base end of the leaf spring is the swing member. The transmission wheel is supported so as to be rotatable about the rotation center of the transmission wheel.

  With such a configuration, the elastic body can be disposed in a space-saving manner, so that the hoisting force transmission mechanism can be further downsized.

  In the hoisting force transmission mechanism according to the present invention, the elastic body includes a C-shaped support portion formed so as to surround a periphery of a support shaft that supports the round hole wheel, and both ends of the support portion. And a lever portion extending to the rocking wheel, wherein the lever portion is elastically tiltable with respect to the support portion in the axial direction of the rocking wheel shaft.

  By comprising in this way, an elastic body can be arrange | positioned by a simple structure and space saving. Further, by adjusting the bending angle between the support portion and the lever portion, the urging force for pressing the flange portion of the swing axle can be easily adjusted. For this reason, a hoisting force transmission mechanism that is small and easy to use can be provided.

  A movement according to the present invention is characterized by including the hoisting force transmission mechanism described above.

  By comprising in this way, the movement which can reduce effectively the energy loss at the time of automatic winding can be provided.

  A mechanical timepiece according to the present invention includes the above-described movement.

  By comprising in this way, the mechanical timepiece which can reduce the energy loss at the time of automatic winding effectively can be provided.

  According to the present invention, the rocking wheel is held at the retracted position where the meshing with the square hole wheel is released by the retracted position holding means. That is, when rotating the square hole wheel during automatic winding, the square hole wheel and the rocking wheel are not meshed, and the state is maintained. For this reason, it is possible to prevent the rotation of the square hole wheel from being transmitted to the swing transmission wheel or the round hole wheel without applying an extra load to the square hole wheel. Therefore, the energy loss at the time of automatic winding can be reduced effectively.

1 is an external plan view of a mechanical timepiece according to an embodiment of the present invention. It is the top view which looked at the movement in the embodiment of the present invention from the front side. It is the top view which looked at the detail of the periphery of the winding stem and hoisting force transmission mechanism in embodiment of this invention from the front side. It is sectional drawing which follows the II line | wire of FIG. It is a top view of the rocking lever in the embodiment of the present invention. It is a side view in the natural body of the rocking lever in the embodiment of the present invention. It is explanatory drawing which shows the behavior at the time of attaching the rocking | fluctuation lever of a natural body to the movement in embodiment of this invention.

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

(Mechanical watch)
FIG. 1 is an external plan view of a mechanical timepiece 1.
In general, a machine body including a drive portion of the mechanical timepiece 1 is referred to as a “movement 10”. A state in which the dial 4 and the hands (hour hand 5, minute hand 6, second hand 7) are attached to the movement 10 and put into the watch case 3 to make a finished product is referred to as “complete” of the mechanical timepiece. Of the two sides of the base plate 11 constituting the substrate of the mechanical timepiece 1, the side with the glass 2 (the side with the dial) of the timepiece case 3 is referred to as the “back side” of the movement 10. Further, of the both sides of the main plate 11, the side of the timepiece case 3 with the case back cover (the side opposite to the dial) is referred to as the “front side” of the movement 10. Each vehicle described below is provided with the front and back surfaces of the movement 10 as the rotation axis direction.

  As shown in FIG. 1, a complete timepiece 1 includes a movement 10 and a dial 4 having a scale indicating at least time information in a timepiece case 3 including a case back cover and a glass 2 (not shown). A pointer including an hour hand 5 indicating the hour, a minute hand 6 indicating the minute, and a second hand 7 indicating the second. The mechanical timepiece 1 is a so-called self-winding wristwatch. At the time of automatic winding, the mechanical timepiece 1 is a power source (not shown) that is a power source via an automatic winding wheel train (including a square wheel 14 described later) by rotating a rotating weight (not shown) by a user's movement. The mainspring is rolled up. Further, the mechanical timepiece 1 can manually wind up the mainspring (not shown) via the square wheel 14 even manually. At the time of manual winding, the mechanical timepiece 1 rotates the crown 8 to wind up the mainspring 23 via a hoisting force transmission mechanism 30 (manual winding wheel train) described later (the hoisting force transmission mechanism 30). Detailed operation will be described later).

(Movement)
FIG. 2 is a plan view of the movement 10 as seen from the front side.
As shown in FIG. 2, the movement 10 includes a base plate 11, a winding stem 17 provided on the base plate 11, a train wheel bridge 12 disposed on the front side of the base plate 11, and a winding provided on the train wheel bridge 12. An upper force transmission mechanism 30, a barrel wheel 13 that is rotatably supported between the main plate 11 and the train wheel bridge 12, a square wheel 14 arranged coaxially with the barrel wheel 13, and a front wheel (not shown) And the escapement / regulation mechanism 18 and the like. The front wheel train (not shown) is a power transmission mechanism that transmits the power of the barrel complete 13 to the escapement / regulation mechanism 18 and has a second wheel, a third wheel, a fourth wheel (all not shown), and the like. doing. The escapement / regulation mechanism has a balance 15 and a escape wheel 16 and the like, and vibrates at a constant cycle by the power of the barrel complete 13 transmitted through the front wheel train.

FIG. 3 is a plan view of the details of the periphery of the winding stem 17 and the hoisting force transmission mechanism 30 as viewed from the front side, and shows a state where the main plate 11 and the train wheel bridge 12 of FIG. 2 are removed.
The winding stem 17 is provided on the main plate 11 so as to be slidable and rotatable in a direction orthogonal to the rotation axis direction of the front train wheel. The axial position of the winding stem 17 is determined by a switching mechanism (not shown) having a setting lever, a spring, a spring and the like. A chisel wheel 18 is provided on the guide shaft portion of the winding stem 17 so as to be rotatable with respect to the winding stem 17 and not movable in the axial direction.

The crown 8 is integrally provided at the base end of the winding stem 17. When the crown 8 is rotated, the winding stem 17 is rotated.
Further, a pinion wheel 19 is provided on the tip side of the winding stem 17 of the winding stem 17 so as to be movable in the axial direction with respect to the winding stem 17 and non-rotatable. The hour wheel 18 and the pinion wheel 19 are provided so as to be able to mesh with each other. In addition, the pinion wheel 19 is configured to be able to mesh with a small iron wheel (not shown) used when time is set. On the other hand, a round hole wheel 20 is engaged with the chichi wheel 18. The round hole wheel 20 is rotatably supported by a round hole axle 22 (see FIG. 4) provided in the train wheel bridge 12.

  Under such a configuration, when the mechanical timepiece 1 is manually wound up, the winding stem 17 is moved to the first winding stem position (0th stage) closest to the inside of the movement 10 along the axial direction. Set to. At the first winding stem position, the hour wheel 18 and the clutch wheel 19 are engaged with each other. When the winding stem 17 is rotated in this state, the hour wheel 18 is rotated through the rotation of the clutch wheel 19. And, when this hour wheel 18 rotates, the round hole wheel 20 that meshes with it rotates. And when this round hole wheel 20 rotates, the square hole wheel 14 rotates via the hoisting force transmission mechanism 30. By rotating the square wheel 14, the mainspring (not shown) accommodated in the barrel complete 13 is wound up.

4 is a cross-sectional view taken along the line II of FIG.
As shown in FIG. 4, the barrel 13 includes a barrel 21 in which a mainspring (not shown) is stored, a barrel barrel that is rotatably supported by a base plate 11 and a barrel holder (not shown), and the like. . Then, when the square wheel 14 is rotated, the barrel complete is rotated and the mainspring is wound up. The barrel 21 is rotated by the spring force when the mainspring is unwound to drive the front train wheel.

(Hoisting force transmission mechanism)
As shown in FIGS. 3 and 4, the hoisting force transmission mechanism 30 is supported on the front side of the train wheel bridge 12 via a fixed screw 31 and rotatably supported by the rocking receiver 32. The swing transmission wheel 33 that is supported, the swing wheel 34 that is swingably supported by the swing receiver 32, and the swing lever 40 that causes the swing wheel 34 to generate a frictional resistance against the swing receiver 32. Is the main component.

  The swing receiver 32 is a plate-like member that extends from the position slightly spaced from the round hole wheel 20 to the outer peripheral part of the round hole wheel 20 in the outer peripheral portion of the barrel 21. The base end side of the swing receiver 32 located on the outer peripheral side of the barrel 21 in the longitudinal direction is fixed to the train wheel bridge 12 by a fixing screw 31. The swing receiver 32 is formed with a through hole 32a into which the cylindrical portion 35 of the train wheel bridge 12 can be inserted on the distal end side located on the round hole wheel 20 side in the longitudinal direction.

  The cylindrical portion 35 of the train wheel bridge 12 is formed to protrude toward the front side. The tip of the cylindrical portion 35 is inserted into the through hole 32 a of the swing receiver 32. A support screw 36 is inserted into the cylindrical portion 35. The head 36a of the support screw 36 is formed in a disc shape. The tip of the support screw 36 opposite to the head 36a is inserted from the front side of the cylindrical portion 35 so that the head 36a and the swing receiver 32 come into contact with each other. Is fixed to the tip side.

  The inner peripheral surface of the flanged bush 37 is fitted on the outer peripheral surface of the cylindrical portion 35 between the train wheel bridge 12 and the swing receiver 32. The flanged bush 37 is arranged with the outer flange portion 37a facing the swing receiver 32 side. The flanged bush 37 secures a gap between the train wheel bridge 12 and the swing receiver 32. The swing transmission wheel 33 is rotatably supported on the outer peripheral surface of the flanged bushing 37 except the outer flange portion 37a. The swing transmission wheel 33 is meshed with the round hole wheel 20.

Further, an opening 38 is formed in the swing receiver 32 approximately in the middle between the fixed screw 31 and the support screw 36. The opening 38 is formed in an arc shape centered on the axis C of the support screw 36 when viewed from the front side. A swing axle 39 is inserted through the opening 38.
The swing axle 39 has a shaft main body 41 and a disk-shaped head portion 42 that is integrally formed on the proximal end side of the shaft main body 41. The opening 38 has an opening width in the short direction so that the shaft main body 41 can be inserted and the head 42 cannot be inserted. Then, the front end of the swing axle 39 opposite to the head 42 is inserted from the front side of the swing receiver 32, and the head 42 is brought into contact with the front surface 32 b of the swing receiver 32. Therefore, the swing axle 39 can swing along the opening 38, that is, swing about the axis C of the support screw 36.

  Further, the shaft main body 41 is formed with a constricted portion 43 whose entire circumference is reduced in diameter by a step at substantially the center in the axial direction. The width W between the constricted portion 43 and the head portion 42 is set to be slightly larger than the plate thickness of the swing receiver 32. The rocking wheel 34 is fitted and fixed to the distal end side of the constricted portion 43 of the shaft main body 41. For this reason, the oscillating wheel 34 rotates integrally with the oscillating wheel shaft 39.

The swing wheel 34 is meshed with the swing transmission wheel 33. Since the swing wheel 34 is integrated with a swing wheel shaft 39 that swings along the opening 38 of the swing receiver 32, the swing wheel 34 swings while maintaining meshing with the swing transmission wheel 33.
Further, the swinging direction of the swing wheel 34 is a direction approaching and separating from the square wheel 14. The rocking wheel 34 is formed so as to be able to mesh with the square hole wheel 14. For this reason, the rocking wheel 34 is engaged with the square wheel 14 or is disengaged with the rocking.

FIG. 5 is a plan view of the swing lever 40.
As shown in FIGS. 3 to 5, the swing lever 40 is disposed along the swing receiver 32 at a position corresponding to the constricted portion 43 of the swing axle 39.
The swing lever 40 is a leaf spring formed of an elastic metal plate. The swing lever 40 has a support portion 44 slidably fitted to the outer peripheral surface of the outer flange portion 37 a of the flanged bush 37. The support portion 44 is formed in a C shape when viewed from the front side, and is arranged with the opening directed toward the rocking axle 39. A pair of lever portions 45 a and 45 b that extend toward the swing axle 39 are integrally formed at both ends of the support portion 44.

The distal ends of these lever portions 45 a and 45 b are attached to the constricted portion 43 of the swing axle 39. In the lever portions 45a and 45b, concave portions 46a and 46b that can receive the constricted portion 43 are formed at positions corresponding to the constricted portion 43, respectively. The recesses 46a and 46b are formed in a substantially arc shape when viewed from the front side. The curvature radii of the concave portions 46 a and 46 b are set to be substantially equal to the radius of the constricted portion 43.
The lever portions 45 a and 45 b are formed such that the gap K excluding the recesses 46 a and 46 b is smaller than the shaft diameter of the swing axle 39. By the lever portions 45a and 45b formed in this way, the constricted portion 43 of the swing axle 39 is sandwiched from the outside in the radial direction.

  Furthermore, inclined portions 47a and 47b are formed at the ends of the lever portions 45a and 45b so that the distance between the lever portions 45a and 45b gradually increases toward the tip at the sides facing each other. These inclined portions 47a and 47b function as guides when the swing axle 39 is inserted from the tip side of the lever portions 45a and 45b.

  That is, when the swing axle 39 is inserted between the lever portions 45a and 45b, the swing axle 39 is smoothly guided between the lever portions 45a and 45b by the inclined portions 47a and 47b. Further, when the lever portions 45 a and 45 b are pushed toward the swing axle 39, the lever portions 45 a and 45 b are pushed and expanded by the swing axle 39 while being elastically deformed. Thereafter, when the swing axle 39 reaches the recesses 46a and 46b of the lever portions 45a and 45b, the lever portions 45a and 45b approach each other due to the restoring force of the lever portions 45a and 45b. In this way, the lever portions 45a and 45b sandwich the swing axle 39 so as to be snap-fit fixed.

FIG. 6 is a side view of a natural body (hereinafter simply referred to as a natural body) before being assembled to the constricted portion 43 of the swing lever 40. FIG. 7 is an explanatory diagram showing the behavior when the natural rocking lever 40 is assembled to the mechanical timepiece 1 (movement 10).
Here, as shown in FIG. 6, the rocking lever 40 is bent so that the lever portions 45 a and 45 b have a predetermined angle θ with respect to the support portion 44 in the natural body.

  As shown in FIG. 7, when the swing lever 40 is assembled to the mechanical timepiece 1 (movement 10), first, the lever portions 45 a and 45 b of the swing lever 40 are sandwiched between the swing axle 39. In other words, the lever portions 45 a and 45 b are interposed between the swing receiver 32 and the swing wheel 34. At this time, the swing lever 40 is assembled to the lever portions 45a and 45b so that the support portion 44 is separated from the swing receiver 32. Thereafter, the swing lever 40 is elastically deformed to raise the support portion 44 toward the swing receiver 32. And it is made for the support part 44 and lever part 45a, 45b to be on the same plane (refer arrow Y1 in FIG. 7).

  Then, the rocking wheel 34 is pressed to the back side (lower side in FIG. 7) by the restoring force of the rocking lever 40 (see arrow Y2 in FIG. 7). And the rocking axle 39 to which the rocking wheel 34 is fixed is also pressed to the back side. When the swing axle 39 is pressed, the head portion 42 of the swing axle 39 is pressed against the front surface 32 b of the swing receiver 32. For this reason, the frictional resistance between the front surface 32 b of the swing receiver 32 and the head portion 42 of the swing axle 39 is increased.

(Operation of hoisting force transmission mechanism)
Next, the operation of the hoisting force transmission mechanism 30 will be described based on FIG.
First, manual winding will be described.
At the time of manual winding, the winding stem 17 is set at the first winding stem position (0th stage) closest to the inside of the movement 10 along the axial direction. At the first winding stem position, the hour wheel 18 and the clutch wheel 19 are engaged with each other. When the winding stem 17 is rotated in this state, the hour wheel 18 is rotated through the rotation of the clutch wheel 19. Then, by rotating the hour wheel 18, the round hole wheel 20 that meshes with the wheel rotates in the counterclockwise direction in FIG. 3 (in the direction of arrow Y 3 in FIG. 3).

  Then, the swing transmission wheel 33 of the hoisting force transmission mechanism 30 meshed with the round hole wheel 20 rotates in the clockwise direction in FIG. 3 (arrow Y4 direction in FIG. 3). Subsequently, the swing wheel 34 meshed with the swing transmission wheel 33 rotates in the counterclockwise direction in FIG. 3 (the direction of arrow Y5 in FIG. 3).

  Here, the swing wheel 34 is supported so as to be swingable with respect to the swing receiver 32 via a swing axle 39. That is, the swing wheel 34 swings along a direction approaching and separating from the square hole wheel 14. Further, when the rotational force is transmitted from the swing transmission wheel 33, the swing wheel 34 is urged toward the direction toward the square wheel 14 by this rotational force (see arrow Y6 in FIG. 3).

Further, the swing lever 40 of the hoisting force transmission mechanism 30 has a support portion 44 slidably fitted to the outer flange portion 37 a of the flanged bush 37. Therefore, the oscillating wheel 34 moves in a direction approaching the square hole wheel 14, and the oscillating lever 40 also follows the oscillating wheel 34 and rotates around the axis C of the support screw 36. Thereby, the rocking wheel 34 is meshed with the square hole wheel 14 (meshing position).
Then, the square wheel 14 rotates in the clockwise direction in FIG. 3 (the direction of the arrow Y7 in FIG. 3). By rotating the square wheel 14, the mainspring (not shown) accommodated in the barrel complete 13 is wound up.

  By the way, in the hoisting force transmission mechanism 30, the frictional resistance between the front surface 32 b of the swing receiver 32 and the head portion 42 of the swing axle 39 is increased by the elastic force of the swing lever 40. Due to this frictional resistance, the swing wheel 34 is held at the meshing position with the square hole wheel 14 during manual winding. That is, during the manual winding operation, the engagement between the square wheel 14 and the rocking wheel 34 is not released, and the manual winding operation is performed smoothly.

Next, the automatic winding will be described.
At the time of automatic winding, the winding stem 17 is set at the first winding stem position (0th stage), and the chime wheel 18 and the clutch wheel 19 are engaged with each other.
In this state, a rotational force is applied to the square wheel 14 via the outer ring (both not shown) by the rotating weight. Then, the square hole wheel 14 rotates in the clockwise direction in FIG. 3 (the direction of the arrow Y7 in FIG. 3). By rotating the square wheel 14, the mainspring (not shown) accommodated in the barrel complete 13 is wound up.

  At this time, the rotational force of the square hole wheel 14 is transmitted to the swing wheel 34 meshed with the square hole wheel 14. The rotational force urges the swing wheel 34 in a direction away from the square wheel 14 (see arrow Y8 in FIG. 3). Therefore, the oscillating wheel 34 moves in a direction away from the square wheel 14, and the oscillating lever 40 also follows the oscillating wheel 34 and rotates around the axis C of the support screw 36. As a result, the engagement between the square hole wheel 14 and the swing wheel 34 is released (retracted position).

  Even at the retracted position of the swing wheel 34, the elastic force of the swing lever 40 of the hoisting force transmission mechanism 30 is acting. In other words, a frictional resistance acts between the front surface 32 b of the swing receiver 32 and the head portion 42 of the swing axle 39. For this reason, at the time of automatic winding, once the swing wheel 34 moves to the retracted position, the swing wheel 34 is held at the retracted position. Therefore, during the automatic winding operation, the square hole wheel 14 and the swing wheel 34 are not engaged with each other, and the automatic winding operation is performed smoothly.

Thus, the above-described hoisting force transmission mechanism 30 is engaged with the swing transmission wheel 33 meshed with the round hole wheel 20 and the swing transmission wheel 33, and the rotation center (support) of the swing transmission wheel 33 is supported. A swing wheel 34 that is swingable about the axis C) of the screw 36 and moves between a meshing position and a retracted position; a swing lever 45 that can hold the swing wheel 34 at the meshing position and the retracted position; It has.
For this reason, at the time of manual winding, the square wheel 14 and the rocking wheel 34 can be meshed. Therefore, it is possible to reduce the number of sounds and impacts generated when the square wheel 14 and the rocking wheel 34 are engaged with each other, and it is possible to provide an easy-to-use hoisting force transmission mechanism 30.

  For example, it is assumed that the swing wheel 34 is constantly urged to either the meshing position or the retracted position. In such a case, the square wheel 14 and the oscillating wheel 34 are engaged each time the winding operation is performed, either during manual winding or during automatic winding. As a result, a collision sound and an impact at the time of meshing between the square hole wheel 14 and the rocking wheel 34 are generated each time. However, in this embodiment, the rocking wheel 34 is held at the meshing position or the retracted position by the hoisting force transmission mechanism 30, so the number of sounds and impacts generated when the square wheel 14 and the rocking wheel 34 are meshed with each other. Can be reduced as much as possible.

  Further, when the square wheel 14 is rotated during automatic winding, the square wheel 14 and the rocking wheel 34 are not meshed with each other and the state is maintained. For this reason, it is possible to prevent the rotation of the square hole wheel 14 from being transmitted to the swing transmission wheel 33 and the round hole wheel 20 without applying an extra load on the square hole wheel 14. Therefore, the energy loss at the time of automatic winding can be reduced effectively.

  Further, when the swing wheel 34 is held at the meshing position and the retracted position, a disk-shaped head 42 is provided on the swing wheel shaft 39 that fixes the swing wheel 34, and the head 42 is elastically supported by the swing lever 45. Is pushing. Thereby, a frictional resistance is generated between the swing receiver 32 and the head 42. Then, using this frictional resistance, the rocking wheel 34 is held at the meshing position and the retracted position. Thus, the rocking wheel 34 can be held at the meshing position and the retracted position with a simple structure, and the hoisting force transmission mechanism 30 can be miniaturized as much as possible.

  The swing lever 40 is a leaf spring formed of a metal plate having elasticity. And the support part 44 is fitted to the outer peripheral surface of the outer flange part 37a of the bush 37 with a flange so that sliding is possible. For this reason, it is possible to arrange a structure for generating a frictional resistance between the swing receiver 32 and the head portion 42 of the swing axle 39 in a narrow space, and to make the swing lever 40 follow the swing of the swing wheel 34. Can do. For this reason, it is not necessary to provide an elastic body for pressing the swing axle 39 at each of the meshing position and the retracted position of the swing wheel 34. Therefore, the hoisting force transmission mechanism 30 can be more reliably downsized.

Further, the swing lever 40 includes a C-shaped support portion 44 and lever portions 45 a and 45 b extending from both ends of the support portion 44. In the natural body, the swing lever 40 is bent with respect to the support portion 44 so that the lever portions 45a and 45b have a predetermined angle θ. Such a swing lever 40 is elastically deformed so that the support portion 44 and the lever portions 45a and 45b are on the same plane, and the hoisting force transmission mechanism 30 is assembled. A frictional resistance is generated between the swing receiver 32 and the head 42.
Thus, a frictional resistance can be generated between the swing receiver 32 and the head 42 with a simple structure and a small space. Further, by adjusting the bending angle θ between the support portion 44 and the lever portions 45a and 45b in the natural body, the urging force of the head portion 42 on the swing receiver 32 can be easily adjusted. That is, the magnitude of the frictional resistance between the swing receiver 32 and the head 42 can be easily adjusted. For this reason, the hoisting force transmission mechanism 30 that is small and easy to use can be provided.

The present invention is not limited to the above-described embodiment, and includes various modifications made to the above-described embodiment without departing from the spirit of the present invention.
For example, in the above-described embodiment, the case where the rocking wheel 34 is held by the rocking lever 40 in both the meshing position and the retracted position with respect to the square wheel 14 has been described. However, the present invention is not limited to this, as long as it can be held at least in the retracted position. By comprising in this way, the energy loss at the time of automatic winding can be reduced reliably.

  In the above-described embodiment, the case where the swing lever 40 that is a leaf spring is provided as a means for holding the meshing position and the retracted position of the swing wheel 34 has been described. However, the present invention is not limited to this, and the hoisting force transmission mechanism 30 may be configured to hold the rocking wheel 34 at the meshing position or the retracted position. For example, instead of the swing lever 40, a coil spring may be provided at a position corresponding to the meshing position or the retracted position. With this coil spring, the head 42 of the swing axle 39 is elastically pressed toward the swing receiver 32, whereby the swing wheel 34 can be held at the meshing position or the retracted position.

  In the above-described embodiment, the case where the swing receiver 32 is fixed to the train wheel bridge 12 and the swing transmission wheel 33 and the swing wheel 34 are rotatably supported by the swing receiver 32 has been described. However, the present invention is not limited to this, and the train wheel bridge 12 can also rotatably support the swing transmission wheel 33 and the swing wheel 34. In this case, the opening 38 of the swing receiver 32 may be formed in the train wheel bridge 12.

DESCRIPTION OF SYMBOLS 1 ... Mechanical type watch, 10 ... Movement, 14 ... Square hole wheel, 17 ... Winding stem, 20 ... Round hole wheel, 30 ... Hoisting force transmission mechanism, 32 ... Swing receiver, 33 ... Swing transmission wheel, 34 ... Oscillating wheel, 38 ... opening, 39 ... oscillating axle, 40 ... oscillating lever (retracting position holding means, meshing position holding means), 41 ... shaft main body, 42 ... head (flange), 44 ... support part, 45a, 45b ... lever part, C ... shaft center (rotation center)

Claims (7)

A swing transmission wheel meshed with a round hole wheel rotating by a winding stem operation;
Engaged with the oscillating transmission wheel and oscillated around the center of rotation of the oscillating transmission wheel, the meshing position meshed with the square hole wheel and the retraction where the meshing with the square hole wheel is released A rocking wheel that moves to a position;
Retraction position holding means capable of holding the rocking wheel at the retraction position;
A hoisting force transmission mechanism characterized by comprising:   The hoisting force transmission mechanism according to claim 1, further comprising a meshing position holding unit capable of holding the rocking wheel at the meshing position. A swing receiver that supports the swing wheel and has an opening formed along a swing locus of the swing wheel;
The swing wheel is fixed to one end of a swing axle inserted through the opening,
At the base end of the swing axle of the swing axle, a flange portion that contacts the swing receiver is provided,
The hoisting force transmission mechanism according to claim 2, wherein the retracted position holding unit and the meshing position holding unit are elastic bodies that urge a force that presses the flange portion against the swing receiving member. . The elastic body is a leaf spring having a tip interposed between the swing receiver and the swing wheel,
4. The hoisting force transmission mechanism according to claim 3, wherein a base end of the leaf spring is supported so as to be rotatable around a rotation center of the swing transmission wheel. The elastic body is
A C-shaped support part formed so as to surround the periphery of the support shaft supporting the round hole wheel;
Lever portions extending from both ends of the support portion to the swing wheel;
Have
The hoisting force transmission mechanism according to claim 4, wherein the lever portion is elastically tiltable with respect to the support portion in an axial direction of the swing axle.   A movement comprising the hoisting force transmission mechanism according to any one of claims 1 to 5.   A mechanical timepiece comprising the movement according to claim 6.

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