JP6650010B2 - Return spring, train wheel mechanism, watch movement and mechanical watch - Google Patents

Description

  The present invention relates to a return spring, a train wheel mechanism, a movement for a timepiece, and a mechanical timepiece.

In a timepiece movement, a mode in which the transmission of power (rotational torque) between the first vehicle and the second vehicle is allowed by oscillating the oscillating vehicle disposed between the first vehicle and the second vehicle. It is known to switch between a mode in which power transmission between a first vehicle and a second vehicle is interrupted.
In this case, for example, in a state where the rocking vehicle is meshed with the first vehicle, the rocking vehicle is rockably arranged between a meshing position meshing with the second vehicle and a release position where the meshing with the second vehicle is released. Have been. When the oscillating vehicle is located at the meshing position, the power transmitted from the first vehicle can be transmitted to the second vehicle via the oscillating vehicle. On the other hand, when the rocking vehicle is located at the release position, it is possible to prevent the power transmitted from the first vehicle from being transmitted to the second vehicle via the rocking vehicle.

In the case of using this kind of rocking vehicle, there is known a technique of using a lateral contact spring to bias the rocking vehicle from the release position side to the meshing position side along the in-plane direction of the movement (eg, for example). Patent Document 1). Examples of the horizontal contact spring include a leaf spring, a U-shaped spring, and a wire spring.
There is also known a technique of using a swinging lever to swingably hold a swinging wheel between a meshing position and a release position, and positioning the swinging wheel at a meshing position (for example, Patent Document 2, 3).
Furthermore, there is also known a technique in which a rocking wheel is pressed in the thickness direction of the movement by using a pressing spring or a needle seat, so that the rocking wheel is rockably positioned at a meshing position between a meshing position and a release position. ing.

JP-A-2006-114509 JP 2014-41124 A JP-A-215-236236

In the case of the above-mentioned conventional horizontal contact spring, if the spring force (urging force) for urging the rocking vehicle is large, the rocking vehicle strongly presses against the second vehicle, so that a large load is applied to the rocking vehicle. For example, wear and the like easily occur in the meshing portion. Further, since the swinging vehicle becomes difficult to swing from the meshing position side to the release position side, it is easy to hinder proper swinging of the swinging vehicle.
Therefore, in the case of a horizontal contact spring, it is desired to reduce the spring force for urging the rocking wheel. However, in this case, it is necessary to form the side contact spring long to secure a long spring length, and it is necessary to ensure a large plane space for installing the side contact spring. However, in a movement in which a large number of timepiece components are densely arranged, it is difficult to secure a sufficient plane space for installing a horizontal contact spring, and there is room for improvement.

  On the other hand, in the case of the above-mentioned conventional swing lever, the required plane space can be reduced as compared with the horizontal contact spring. However, since the swing lever is not biased toward the meshing position, it is necessary to automatically return the swing lever toward the meshing position after swinging from the meshing position to the release position. And there was room for improvement.

  For example, in the case where the second vehicle is a square wheel that can wind up a mainspring housed inside a barrel car, and the rocking vehicle is a rocking transmission vehicle that transmits the rotational torque from the winding stem to the square wheel, If the rocking transmission wheel is left at the release position by the rocking lever, the engagement between the square wheel and the rocking transmission wheel is released. In this state, if, for example, the spring is disengaged from the square wheel to perform the unwinding operation of the mainspring, there is a possibility that the mainspring may be unwound vigorously. Therefore, there is room for improvement as described above.

Furthermore, in the case of the above-mentioned conventional holding spring or needle seat, the required flat space can be reduced as compared with the horizontal contact spring, similarly to the swing lever, but the swing wheel is released from the meshing position. After swinging to the position, the swinging vehicle cannot be automatically returned to the meshing position side, and there is room for improvement.
In addition, it is necessary to assemble the holding spring or the needle seat in the direction of the thickness of the movement with respect to the swinging wheel. Easy to separate in the thickness direction. Therefore, the assemblability is poor and there is room for improvement.

  The present invention has been made in view of such circumstances, and an object of the present invention is to mount the swinging vehicle in one direction while suppressing a load applied to the swinging vehicle while being able to be mounted without requiring a large plane space. It is an object of the present invention to provide a return spring, a train wheel mechanism, a movement for a timepiece, and a mechanical timepiece that can be biased to a force.

(1) A return spring according to the present invention directs an oscillating vehicle, which is swingably disposed between a first position and a second position along a swing direction, from a first position side to a second position side. A fixed frame portion, a connection end portion having a base end portion connected to the fixed frame portion, and a free end portion having a tip end contactable with the rocking vehicle. An elastically deformable cantilever spring body, wherein the free end can contact the rocking vehicle in a state where the rocking vehicle is biased toward the second position. The spring body is spaced from the free end to the connection end in a radial direction intersecting with the center axis of the rocking wheel when viewed from the axial direction of the rocking wheel. It is formed opposing portions adjacent open curved which has at least two or more stages, the spring body, or outside in the radial direction of the swing car It is formed in a spiral shape surrounding the multi-stage.

  According to the return spring according to the present invention, when the swing vehicle swings from the second position side to the first position side, the spring body is elastically deformed in the radial direction according to the swing of the swing vehicle. At this time, the spring main body is elastically deformed so that opposing portions that are adjacent to each other in the radial direction at an interval approach or separate from each other in the swinging direction. Thus, the rocking wheel can be urged from the first position side to the second position side via the free end by utilizing the elastic restoring force of the spring body, and the rocking wheel returns to the second position. Can be done.

In particular, since the spring body is formed in a curved shape having at least two or more adjacent opposing portions spaced apart in the radial direction from the free end to the connection end, the spring body is connected from the free end. The spring can be made small in plan while sufficiently securing the effective length of the spring up to the end.
Since the spring effective length of the spring main body can be sufficiently ensured, it is possible to reduce the urging force (spring force using the elastic restoring force) by which the spring main body urges the oscillating vehicle, and it is possible to apply to the oscillating vehicle. The rocking vehicle can be biased in one direction toward the second position while the load is suppressed. Further, since the spring body can be formed small in a plane, the return spring can be mounted without requiring a large plane space. Therefore, it is possible to mount the return spring in a smaller space than the conventional horizontal contact spring.
Further, since the spring main body is formed in a spiral shape, the effective length of the spring from the free end to the connection end of the spring main body can be further increased, and the spring main body can be further reduced in plan.

(2) The free end may be arranged closer to the first position than the rocking vehicle, and may be capable of contacting the rocking vehicle from the first position.

  In this case, the swing vehicle can be urged toward the second position while the free end of the swing vehicle is in contact with the swing vehicle from the first position side. Therefore, the return spring can be combined with the rocking vehicle with a simple configuration in which, for example, the free end is pressed against the rocking vehicle from the first position side. Therefore, the return spring can be easily attached.

(3) The spring body is provided on the opposite side to the biasing direction from the center axis of the rocking wheel, in each of the intervals along the rocking direction formed between the opposing portions adjacent to each other. At least one portion is formed wider on the biasing direction side than the center axis of the rocking wheel than each interval along the rocking direction formed between the opposing portions adjacent to each other. Is also good.

In this case, the spring main body is not formed in a spiral shape in which the intervals between the opposing portions adjacent to each other are, for example, equal, but on the side opposite to the biasing direction with respect to the center axis of the rocking wheel. The spiral shape is such that at least one interval between the opposing portions is wider than each interval between the opposing portions on the biasing direction side of the center axis of the rocking wheel.
When the swinging wheel swings from the second position side to the first position side against the elastic force (that is, the urging force) of the spring body, the spring body moves with the swinging wheel. The opposing portions are elastically deformed such that the opposing portions are closer to each other on the side opposite to the biasing direction than the center axis, and the opposing portions are separated from each other on the biasing direction side of the center axis of the rocking vehicle. As described above, since the spring body is formed with at least one space wider on the side opposite to the biasing direction than the center axis of the rocking wheel, it is difficult to bring the opposing portions into contact with each other by that much. it can. Therefore, the spring body can be more elastically deformed while preventing contact between the opposing portions of the spring body. Therefore, the spring effective length of the spring body can be further secured, and the spring body can be formed to be smaller in plan.
Further, since the spring body can be more elastically deformed while preventing the opposing portions of the spring body from contacting with each other, the swing wheel can be swung between the first position and the second position with a larger stroke. And the swinging vehicle can be used effectively.

(4) The spring body includes a curved portion curved along an Archimedes curve centered on the center axis of the rocking wheel, and a linear portion extending linearly along the rocking direction. It may be formed in a spiral shape alternately arranged in the longitudinal direction of the main body.

  In this case, since the spring body is formed in a spiral shape having a linear portion extending linearly along the swing direction, when the swinging wheel swings from the second position side to the first position side. In addition, it is easy to positively elastically deform the entire spring body in the swinging direction. Thereby, the rocking vehicle can be effectively biased in the direction from the first position side to the second position side along the rocking direction, and even when the biasing force of the spring main body on the rocking wheel is small. Accordingly, the rocking vehicle can be appropriately biased toward the second position.

(5) The connection end portion is disposed at a position that passes through the center axis of the rocking vehicle and deviates from an imaginary axis line extending along the rocking direction, and the spring body connects the connection end portion. As a base point, the whole may be elastically displaceable in the swing direction.

  In this case, when the swinging wheel swings from the second position to the first position, the spring body is elastically deformed in the radial direction, and the entire spring body is further swung about the connection end. It can be elastically displaced toward the first position side along the direction. Therefore, even if the urging force of the spring main body with respect to the rocking vehicle is small, the rocking vehicle can be efficiently urged toward the second position.

(6) The free end may be formed in an annular shape surrounding the axle of the rocking wheel from the outside in the radial direction.

In this case, since the free end of the spring body is formed in an annular shape surrounding the axle of the rocking wheel, the simple and simple method of inserting the axle inside the annular free end, for example, is reliable and easy. The rocking wheel and the return spring can be combined while the free end is in contact with the rocking wheel. Therefore, the return spring can be more easily attached.
Further, since the free end is formed in an annular shape, the free end is attached to the surrounding structure when the return spring is assembled, as compared with a case where the free end is formed in a simple plate-like shape or a rod shape, for example. On the other hand, inconveniences such as sudden contact or catching are unlikely to occur, and inconveniences such as bending of the free end by unintentional crushing are unlikely to occur. Also in this respect, the return spring can be easily attached.

(7) The fixed frame portion may be formed in an annular shape surrounding the spring main body from a radial outside.

  In this case, since the fixed frame portion is formed in an annular shape, the spring main body can be stably supported in a cantilever shape with little rattling, and the above-described operation and effect using the spring main body can be more appropriately performed. Can be successful. Further, since the fixed frame surrounds the spring body, it is unlikely that the spring body interferes with other timepiece parts. Therefore, the reliability of the operation of the spring body can be improved.

(8) The wheel train mechanism according to the present invention includes the return spring.

  In this case, since the return spring is provided, the wheel train mechanism can be configured using a small plane space.

(9) A transmission wheel that transmits power to a round wheel that rotates by rotating the winding stem, a square wheel that winds up the mainspring inside the barrel car by rotation, the round wheel and the transmission wheel. Wherein the power is transmitted from the round wheel to the transmission wheel and the rocking wheel is urged by the return spring. The engagement of the moving vehicle is released, and a release position is provided for interrupting the transmission of the power from the round wheel to the transmission vehicle through the rocking vehicle, and the second position is relative to the transmission vehicle. The rocking wheel is engaged with the wheel and the transmission wheel is allowed to transmit the power from the round wheel to the transmission wheel through the rocking wheel. The rocking wheel includes the release position and the meshing position. Can swing along the swing direction between Together are, by the return spring may be biased towards the engagement position.

  In this case, since the rocking wheel is urged by the return spring to the meshing position where the rocking wheel meshes with the transmission wheel, by rotating the winding stem in a predetermined direction, the swinging wheel is rotated from the round hole wheel side through the rocking wheel. Power (rotational torque) can be transmitted to the transmission vehicle side, whereby the power can be transmitted to the square wheel. As a result, the mainspring housed inside the barrel car can be wound up.

  On the other hand, when the mainspring is wound, for example, when the winding stem is rotated in the direction opposite to the predetermined direction, the power in the opposite direction acts on the rocking wheel via the round hole wheel. The rotation of the square wheel in the unwinding direction of the mainspring is regulated. Accordingly, the rotation of the transmission wheel in the unwinding direction of the mainspring is also correspondingly regulated. Therefore, the rocking vehicle cannot transmit the power transmitted to itself to the power transmitting vehicle, and rocks from the meshing position to the release position while rotating in a direction opposite to, for example, the time of winding the mainspring. Thus, transmission of power from the round wheel to the transmission wheel via the rocking wheel can be cut off, and the power can be prevented from being transmitted to the square wheel. Thereafter, by stopping the rotation operation of the winding stem in the reverse direction, the swinging wheel can be automatically returned from the release position side to the meshing position side by the biasing force of the return spring.

  Thus, a wheel train mechanism suitable for winding a mainspring utilizing a return spring can be provided. In particular, since the return spring is used, it is possible to suppress the rocking vehicle from strongly pressing the transmission wheel, so that the load applied to the meshing portion between the transmission wheel and the rocking vehicle can be suppressed. Further, since the urging force of the return spring can be reduced, it is easy to swing the rocking vehicle smoothly to the release position.

(10) A timepiece movement according to the present invention includes the above-described wheel train mechanism.
(11) A mechanical timepiece according to the present invention includes the timepiece movement described above.

  In this case, since the wheel train mechanism itself can be configured using a small plane space, a timepiece movement and a mechanical timepiece that can be easily further reduced in size and thickness can be provided.

  ADVANTAGE OF THE INVENTION According to this invention, it can attach, without requiring a large planar space, and can urge a rocking vehicle in one direction in the state which suppressed the load to a rocking vehicle.

BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows 1st Embodiment which concerns on this invention, and is an external view of a timepiece. FIG. 2 is an enlarged perspective view of a portion around a hoisting wheel train mechanism in the movement shown in FIG. 1. FIG. 3 is a longitudinal sectional view of the hoist train wheel mechanism shown in FIG. 2. FIG. 3 is a perspective view showing a state in which the rocking vehicle shown in FIG. 2 has rocked from a meshing position to a release position. FIG. 3 is a plan view of the return spring shown in FIG. 2 and is a plan view of the return spring in a state where an oscillating vehicle is located at a meshing position. FIG. 5 is a plan view of the return spring illustrated in FIG. 4, and is a plan view of the return spring in a state where an oscillating vehicle is located at a release position. It is a top view showing the modification of a return spring. It is a top view which shows another modification of a return spring. It is a top view which shows another modification of a return spring. It is a top view which shows another modification of a return spring. It is a top view which shows another modification of a return spring. It is a figure showing a 2nd embodiment concerning the present invention, and is a perspective view which expanded a peripheral part of a hoisting wheel train mechanism. It is a longitudinal cross-sectional view of the hoist wheel train mechanism shown in FIG. FIG. 13 is a perspective view showing a state in which the rocking vehicle shown in FIG. 12 has rocked from a meshing position to a release position. FIG. 13 is a plan view of the return spring shown in FIG. 12, and is a plan view of the return spring in a state where the swinging wheel is located at the meshing position. FIG. 16 is a plan view showing a natural state of the return spring in the state shown in FIG. 15. FIG. 15 is a plan view of the return spring shown in FIG. 14, and is a plan view of the return spring in a state where the rocking wheel is located at a release position.

(1st Embodiment)
Hereinafter, a first embodiment according to the present invention will be described with reference to the drawings.
Generally, a mechanical body including a driving part of a timepiece is referred to as a “movement”. A state in which a dial and hands are attached to this movement and put in a watch case to make a finished product is called "complete" of the watch. The side with the glass of the watch case (that is, the side with the dial) of the two sides of the main plate constituting the base plate of the timepiece is referred to as the “back side” of the movement. Also, of the two sides of the main plate, the side with the case back of the watch case (that is, the side opposite to the dial) is referred to as the “front side” of the movement.
In the present embodiment, the direction from the dial to the case back is described as the upper side, and the opposite side is described as the lower side.

  As shown in FIG. 1, a mechanical timepiece 1 of this embodiment stores a movement (timepiece movement according to the present invention) 10 and at least information on time in a timepiece case made of a case back and a glass 2 (not shown). The dial 3 includes a dial 3 having a scale indicating the scale, and hands indicating the scale (that is, an hour hand 4 indicating the hour, a minute hand 5 indicating the minute, and a second hand 6 indicating the second).

As shown in FIGS. 2 and 3, the movement 10 includes a base plate 11 constituting a substrate, and a train wheel bridge 12 disposed on the front side of the base plate 11. Note that illustration of the train wheel bridge 12 is omitted in FIG.
The dial 3 is arranged on the back side of the main plate 11. Between the train wheel bridge 12 and the main plate 11, a front train wheel, an escapement for controlling the rotation of the front train wheel, and a speed governor for controlling the escapement are mainly provided. A hoisting wheel train mechanism 15 (a wheel train mechanism according to the present invention) for winding up a mainspring 14 housed inside 13 is provided. In each of the drawings, the illustration of the front train wheel, the escapement, and the governor is omitted.

A winding stem guide hole 11a is formed in the base plate 11, and a winding stem 20 is incorporated in the winding stem guide hole 11a so as to be rotatable around the first axis O1. The crown 21 shown in FIG. 1 is connected to the winding stem 20. Thereby, the winding stem 20 can be rotated around the first axis O1 via the crown 21.
In the present embodiment, a so-called manual winding mechanical timepiece 1 in which the winding stem 20 is manually rotated to wind the mainspring 14 will be described as an example.

  The position of the winding stem 20 in the axial direction is determined by a switching device (not shown) having a setting, a latch, a latch spring, and the like. To the guide shaft portion of the winding stem 20, a wheel 22 is attached so as to be rotatable with respect to the winding stem 20 and immovable in the axial direction. A pinwheel (not shown) is attached to a portion of the winding stem 20 that is located closer to the tip end than the wheel 22 so as to be non-rotatable with respect to the winding stem 20 and movable in the axial direction.

  For example, when the winding stem 20 is set at the winding stem position (zero position) closest to the movement 10 along the axial direction, the wheel 22 and the continuous wheel can mesh with each other. Therefore, by rotating the winding stem 20 via the crown 21 in this state, it is possible to rotate the wheel 22 around the first axis O1 coaxial with the winding stem 20 via the pinwheel. ing.

  The square wheel 23 can be rotated via the hoist train wheel mechanism 15 by rotating the wheel 21. Further, by rotating the square wheel 23, it is possible to wind up the mainspring 14, which is a power source housed in the barrel barrel 13.

  The mainspring 14 can be wound by rotating the winding stem 20 around the first axis O1 in a predetermined first rotation direction M1. Further, when the winding stem 20 is rotated around the first axis O1 in the second rotation direction M2 opposite to the first rotation direction M1, the swinging stem 32 described later causes the winding stem 20 to rotate from the winding stem 20. The power transmission path to the square wheel 23 is configured to be cut off.

  The front train wheel mainly includes a barrel wheel 13, a second wheel, a third wheel, and a fourth wheel. In each of the drawings, the illustration of the second wheel, the third wheel, and the fourth wheel is omitted. The second wheel, the third wheel, and the fourth wheel rotate sequentially with the rotation of the barrel wheel 13 that is rotated by the elastic restoring force of the wound mainspring 14.

  In addition, the second hand 6 shown in FIG. 1 rotates based on the rotation of the fourth wheel and rotates at a rotation speed controlled by the escapement and the speed governor, that is, one rotation per minute. The minute hand 5 rotates based on the rotation of the center wheel or the rotation of a minute wheel (not shown) that rotates with the rotation of the center wheel, and the rotation speed adjusted by the escapement and the governor, that is, 1 One revolution in time. The hour hand 4 rotates via a minute wheel (not shown) based on the rotation of an hour wheel (not shown) that rotates with the rotation of the second wheel and a rotation speed controlled by an escapement and a speed governor. One revolution at the speed, ie 12 hours or 24 hours.

  The escapement is equipped with an escape wheel that meshes with the fourth wheel and rotates by the power transmitted from the mainspring 14 and an pallet that escapes the escape wheel and rotates it regularly. Control the train wheel. The speed governor is provided with a balance that reciprocates (forward / reverse rotation) at a steady amplitude (swing angle) corresponding to the output torque of the barrel car 13 using a hairspring (not shown) as a power source.

  As shown in FIG. 3, the barrel car 13 is combined with a barrel barrel (not shown) rotatably supported by the main plate 11 and the train wheel bridge 12 so as to be relatively rotatable with respect to the barrel barrel. And a barrel case 13a to be accommodated. The barrel case 13a is provided with a barrel gear 13b that meshes with the second wheel & pinion.

  The mainspring 14 is housed in the barrel case 13a while being spirally wound around the barrel true. The mainspring 14 is wound up by the rotation of the barrel true, and rotates the barrel case 13a by an elastic restoring force when unwound, and transmits power (rotation torque) to the front wheel train via the center wheel.

  As shown in FIGS. 2 and 3, the square wheel 23 is disposed between the barrel case 13a and the train wheel bridge 12, and is fixed to the barrel true by, for example, press fitting. The square wheel 23 has a square gear 23a that meshes with a second transmission gear 36d of a second transmission wheel 36, which will be described later. It is possible to rotate integrally. Thus, the mainspring 14 can be wound up through the barrel case by rotation of the hour wheel 23 in the third rotation direction M3.

  As shown in FIG. 2, a hammer 24 that regulates reverse rotation of the hour wheel 23 is engaged with the hour wheel 23 in order to prevent the wound mainspring 14 from being unwound. By means of this spring 24, rotation of the square wheel 23 in the third rotation direction M3 is permitted, and rotation in the opposite fourth rotation direction M4 is restricted. In FIG. 2, the illustration of each gear is simplified.

(Wheel train mechanism)
As shown in FIGS. 2 and 3, the hoist train wheel mechanism 15 includes a round wheel 30 that rotates by rotation of the winding stem 20 and a swing wheel 32, and the power is transmitted from the round wheel 30 to the square wheel 23. And a return spring 33 for urging the swinging wheel 32 in one direction.

The round wheel 30 is arranged between the winding stem 20 and the train wheel bridge 12, and is supported by the train wheel bridge 12 via a guide ring 40 so as to be rotatable around the second axis O2.
The train wheel bridge 12 is formed with a screw hole 41 formed so as to penetrate the train train bridge 12 up and down, and a cylindrical guide tube 42 is formed so as to project downward. I have. The screw hole 41 and the guide cylinder 42 are formed coaxially with the second axis O2.

The guide ring 40 is arranged coaxially with the second axis O <b> 2, and is integrally combined with the train wheel bridge 12 by the connecting screw 43 in a state of being fitted to the outside of the guide cylinder 42 from below the train wheel bridge 12. .
The connection screw 43 includes a head portion 43a that comes into contact with the guide ring 40 from below, and a screw shaft portion 43b that is screwed into the screw hole 41, and sandwiches the guide ring 40 between the train wheel bridge 12. The gear train 12 is connected to the train wheel bridge 12 in a slid state.

  The round wheel 30 is attached to the outside of the guide ring 40 so as to be relatively rotatable around the second axis O2 with respect to the guide ring 40. The round wheel 30 has a round gear 30 a that meshes with the wheel 22. Thereby, the round wheel 30 can rotate around the second axis O2 with the rotation of the wheel 22.

  When the mainspring 14 is wound, the winding stem 20 and the wheel 22 rotate clockwise in the first rotation direction M1 around the first axis O1 when the mainspring 14 is wound up, so that the wheel 30 is rotated from above (case back lid side). As seen, it rotates clockwise (hereinafter simply referred to as clockwise) as shown by the arrow in FIG. Therefore, when the winding stem 20 and the stop wheel 22 are rotated around the first axis O1 in the second rotation direction M2 opposite to the first rotation direction M1, the round wheel 30 rotates counterclockwise ( (Hereinafter, simply referred to as counterclockwise.)

  The manual wheel train 31 includes a first transmission wheel (transmission wheel according to the present invention) 35 disposed between the main plate 11 and the wheel train receiver 12, and a second transmission wheel (in the present invention) in addition to the swing wheel 32. The transmission vehicle 36 is further provided. The first transmission wheel 35 is rotatable around the third axis O3. The second transmission wheel 36 is rotatable around the fourth axis O4.

The first transmission wheel 35 has a lower tenon 35 a supported by a first tenon hole 45 a of a first bearing 45 held by the main plate 11, and a second tenon 35 b held by the train wheel bridge 12. The bearing 46 is pivotally supported by a second mortise 46a. In addition, as the first bearing 45 and the second bearing 46, for example, a pit stone made of ruby or the like can be used.
The first transmission wheel 35 includes a first transmission gear 35c that meshes with a later-described oscillation gear 32c of the oscillation wheel 32. Thus, the first transmission wheel 35 is rotatable around the third axis O3 with the rotation of the swing wheel 32.

The second transmission wheel 36 is rotatably supported by a third tenon hole 47 a of a third bearing 47 held by the main plate 11, and a fourth tenon 36 b held by the train wheel bridge 12. The bearing 48 is pivotally supported by a fourth tenon 48a. The third bearing 47 and the fourth bearing 48 include, for example, a pit stone formed of ruby or the like.
The second transmission wheel 36 includes a second transmission pinion 36c that meshes with the first transmission gear 35c, and a second transmission gear 36d that meshes with the square gear 23a of the square wheel 23. Thus, the second transmission wheel 36 is rotatable around the fourth axis O4 with the rotation of the first transmission wheel 35, and is also capable of rotating the square wheel 23.

  When the mainspring 14 is wound up, the first transmission wheel 35 rotates the clockwise around the second axis O2 when the mainspring 14 is wound up. Rotate clockwise around O3. Thus, when the mainspring 14 is wound up, the second transmission wheel 36 rotates counterclockwise around the fourth axis O4 as shown by the arrow in FIG. Accordingly, when the mainspring 14 is wound, as described above, the square wheel 23 is rotated in the third rotation direction M3 with the rotation of the second transmission wheel 36, and the mainspring 14 can be wound.

(Swinging car)
The swing wheel 32 is disposed between the main plate 11 and the train wheel bridge 12 so as to be located between the round wheel 30 and the first transmission wheel 35, and is rotatable around the fifth axis O5. .
The rocking wheel 32 is moved along the first rocking hole 50 and the second rocking hole 51 formed in the base plate 11 and the train wheel bridge 12, each having a slot shape in plan view, along with the release position shown in FIG. The first position P1 and a meshing position (a second position according to the present invention) P2 shown in FIG. 2 are swingable.

  The release position P1 is a position at which the engagement of the rocking wheel 32 with the first transmission wheel 35 is released and the transmission of power from the round wheel 30 to the first transmission wheel 35 via the rocking wheel 32 is interrupted. Have been. The meshing position P2 is a position at which the rocking wheel 32 meshes with the first transmission wheel 35 and allows transmission of power from the round wheel 30 to the first transmission wheel 35 via the rocking wheel 32. I have.

  As shown in FIGS. 3 and 5, the first swing hole 50 is formed in the main plate 11 so as to extend along the circumferential direction of the round wheel 30. The second swing hole 51 is formed in the train wheel bridge 12 so as to correspond to the first swing hole 50, and extends along the circumferential direction of the wheel 30. Accordingly, the swing direction L of the swing wheel 32 along the first swing hole 50 and the second swing hole 51 is along the circumferential direction of the round wheel 30. In addition, in each of the drawings including FIG. 5, since the curvature of the swinging wheel 32 in the swinging direction L is slight, it is schematically illustrated in a straight line.

As shown in FIGS. 2 and 3, a swing ring 55 is fitted into the first swing hole 50 so as to be relatively movable along the swing direction L. The lower tenon portion 32a of the axle of the oscillating wheel 32 is fixed inside the oscillating ring 55 with a predetermined interference, for example, by driving. Further, the upper tenon portion 32b of the axle of the rocking wheel 32 is supported inside the second rocking hole 51 formed in the train wheel bridge 12 so as to be relatively movable along the rocking direction L.
Therefore, the axle of the rocking wheel 32 and the rocking ring 55 are integrally movable in the rocking direction L along the first rocking hole 50 and the second rocking hole 51.

The swing wheel 32 further includes a swing gear 32c that can mesh with the round gear 30a of the round wheel 30 and the first transmission gear 35c of the first transmission wheel 35. The swing gear 32c is connected to the axle on which the lower tenon portion 32a and the upper tenon portion 32b are formed so as to be relatively rotatable around a fifth axis O5.
Thereby, the rocking wheel 32 can rock in the rocking direction L along the first rocking hole 50 and the second rocking hole 51 in a state where the rocking gear 32c is rotatable around the fifth axis O5. ing. In the present embodiment, the rotation of the swing gear 32c around the fifth axis O5 is simply referred to as the rotation of the swing wheel 32.

The oscillating gear 32c meshes with the first transmission gear 35c when the oscillating wheel 32 is located at the meshing position P2, as shown in FIG. 2, and as shown in FIG. When it is located at P1, it is separated from the first transmission gear 35c and disengaged.
However, in the present embodiment, as shown in FIGS. 2 and 4, the swing gear 32c is always meshed with the round gear 30a regardless of the swing position of the swing wheel 32.

Thus, the swing wheel 32 can swing along the swing direction L between the release position P1 and the meshing position P2 in a state where the swing wheel 32 is engaged with the round wheel 30.
Therefore, when the rocking wheel 32 is located at the meshing position P2, the oscillating wheel 32 can transmit the power from the round wheel 30 to the first transmission wheel 35 and at the same time is located at the releasing position P1. By separating the power transmission path from the round wheel 30 to the first transmission wheel 35, the transmission of power to the first transmission wheel 35 can be cut off.
When the mainspring 14 is wound up, the swing wheel 32 rotates counterclockwise around the fifth axis O5 as shown by an arrow in FIG. 2 by rotating the round wheel 30 clockwise around the second axis O2. I do.

  The swinging wheel 32 configured as described above is constantly urged from the release position P1 side to the meshing position P2 side by the return spring 33 shown in FIG.

(Return spring)
As shown in FIGS. 2, 3, and 5, in a state where the return spring 33 is housed inside the concave portion 60 formed in the main plate 11, the return wheel 33 connects the swing wheel 32 via the swing ring 55 to the meshing position P 2. The oscillating wheel 32 is pressed against the first transmission wheel 35 by being urged toward the side. The first swing hole 50 is formed in the bottom wall of the recess 60.
In a plan view as viewed from the direction of the fifth axis O5, which is the center axis of the rocking wheel 32, a direction intersecting the fifth axis O5 is referred to as a radial direction, and a direction orbiting around the fifth axis O5 is referred to as a circumferential direction.

  The return spring 33 has an annular fixed frame portion 70 fixed inside the recessed portion 60, and is disposed inside the fixed frame portion 70 and is elastically deformed supported in a cantilever manner with respect to the fixed frame portion 70. And a possible spring body 71.

The spring body 71 is a thin plate spring made of a metal such as iron or nickel. The spring body 71 has a base end serving as a connection end 72 connected to the fixed frame 70 and a tip end swinging via the swing ring 55. A free end 73 is provided which can contact the moving vehicle 32.
The spring body 71 is formed in a curved shape having at least two or more adjacent opposing portions spaced apart in the radial direction from the free end 73 to the connection end 72. In the present embodiment, the spring body 71 is formed in a spiral shape along the Archimedes curve in a polar coordinate system centered on the fifth axis O5 of the swinging wheel 32 located at the meshing position P2 (origin). Thus, the spring body 71 is wound with a plurality of turns so as to be adjacent to each other at substantially equal intervals in the radial direction.

Specifically, the spring main body 71 is formed in a spiral shape surrounding the swinging wheel 32 in four stages (multistage) from the outside in the radial direction.
As shown in FIG. 5, the spring body 71 includes a free end portion 73 and is located at the radially innermost innermost peripheral spring portion 75, and a first intermediate portion surrounding the innermost peripheral spring portion 75 from the radially outer side. A spring portion 76, a second intermediate spring portion 77 surrounding the first intermediate spring portion 76 from the radial outside, and a connection end portion 72, and surrounding the second intermediate spring portion 77 from the radial outside, and a radially outermost portion. Are formed in a spiral shape that is continuously connected along the Archimedes curve.

  Note that the innermost peripheral spring portion 75, the first intermediate spring portion 76, the second intermediate spring portion 77, and the outermost peripheral spring portion 78 function as the above-described opposing portions, respectively. Therefore, the spring main body 71 of the present embodiment is formed in a spiral shape having four stages of opposing portions.

Further, the spring body 71 is connected to the fixed frame 70 via the connection end 72 so that the free end 73 urges the swinging wheel 32 toward the meshing position P2. Specifically, the spring body 71 is connected such that the free end 73 is disposed closer to the release position P1 than the rocking wheel 32 and contacts the rocking wheel 32 via the rocking ring 55 from the release position P1 side. It is connected to the fixed frame 70 via the end 72.
Further, the connecting end 72 is disposed at a position off the imaginary axis V extending through the fifth axis O5 and along the swing direction L in plan view as viewed from the direction of the fifth axis O5. As a result, the spring body 71 is connected to the fixed frame 70 so that the entire spring body 71 can be elastically deformed in the swing direction L with the connection end 72 as a base point.

The fixed frame portion 70 is formed in an annular shape surrounding the spring body 71 from the outside in the radial direction. In the present embodiment, the fixed frame portion 70 is formed in an annular shape along the side wall portion 61 that defines the recessed portion 60 formed in the base plate 11, and is disposed inside the side wall portion 61.
A plurality of protrusions 79 slightly bulging toward the side wall 61 are formed on the fixed frame 70 at intervals along the fixed frame 70. The plurality of protrusions 79 are, for example, in close contact with the side wall 61. Thus, the fixed frame portion 70 is disposed in the recessed portion 60 in a state of being fitted inside the side wall portion 61 via the plurality of protrusion portions 79.

(Operation of mechanical watch)
Next, the operation of the mechanical timepiece 1 including the hoisting train wheel mechanism 15 including the return spring 33 configured as described above will be described.

  In the mechanical timepiece 1 of the present embodiment, when manually winding the mainspring 14, the winding stem 20 is moved in the direction of the first axis O <b> 1 via the crown 21 to move the winding stem 20 toward the movement 10. Set to the closest winding true position (0-step position). As a result, the wheel & pinion 22 and the continuous wheel can be meshed. Therefore, as shown in FIG. 2, by rotating the winding stem 20 around the first axis O1 in the first rotation direction M1 at the 0-stage position, the round hole wheel 30 And the wheel 30 can be rotated clockwise about the second axis O2.

  Since the swinging wheel 32 is urged to the meshing position P2 by the return spring 33, it is in a state of meshing with both the round wheel 30 and the first transmission wheel 35. Accordingly, the swing wheel 32 can be rotated counterclockwise around the fifth axis O5 with the rotation of the round wheel 30 and the first transmission wheel 35 is moved along the third axis with the rotation of the swing wheel 32. It can be rotated clockwise around O3. Thus, the power transmitted to the round wheel 30 can be transmitted to the first transmission wheel 35 via the swing wheel 32.

By rotating the first transmission wheel 35, the second transmission wheel 36 can be rotated counterclockwise around the fourth axis O4, and with the rotation of the second transmission wheel 36, the square wheel 23 is moved. It can be rotated in the third rotation direction M3. Thus, the power transmitted to the first transmission wheel 35 can be transmitted to the square wheel 23 via the second transmission wheel 36.
By rotating the square wheel 23 in the third rotation direction M3, the mainspring 14 housed inside the barrel wheel 13 can be wound up through the barrel barrel.

  By the way, as shown in FIG. 4, when the mainspring 14 is wound, when the winding stem 20 is rotated in a second rotation direction M2 opposite to the first rotation direction M1 determined in advance, And the power in the opposite direction acts on the round wheel 30 via the wheel 22. Thereby, the round wheel 30 rotates counterclockwise around the second axis O2 as indicated by the arrow shown in FIG. Therefore, the power in the opposite direction acts on the swing wheel 32 from the round wheel 30.

  Here, since the rotation of the square wheel 23 in the fourth rotation direction M4 that is the unwinding direction of the mainspring 14 is regulated by the hammer 24, the first transmission wheel 35 and the second transmission wheel are correspondingly provided. 36 also restricts the rotation of the mainspring 14 in the unwinding direction. That is, the first transmission wheel 35 is restricted from rotating counterclockwise around the third axis O3, and the second transmission wheel 36 is restricted from rotating clockwise around the fourth axis O4. .

Therefore, the rocking wheel 32 cannot transmit the power transmitted from the round wheel 30 to the first transmission wheel 35. The power transmitted from the round wheel 30 to the rocking wheel 32 acts in a direction to separate the rocking wheel 32 from the first transmission wheel 35.
From these facts, the swing wheel 32 swings from the meshing position P2 to the release position P1 along the swing direction L while rotating around the fifth axis O5 in a clockwise direction opposite to the time when the mainspring 14 is wound up. I do. Accordingly, it is possible to prevent the power from the winding stem 20 from being transmitted to the square wheel 23.

  Thereafter, by stopping the rotation of the winding stem 20 in the second rotation direction M2, the swinging wheel 32 is automatically returned from the release position P1 toward the meshing position P2 by the urging force of the return spring 33. be able to. Therefore, as shown in FIG. 2, the swing wheel 32 can be returned to a state in which the swing wheel 32 is engaged with both the round wheel 30 and the first transmission wheel 35 again.

The return spring 33 will be described in detail.
When the swing wheel 32 swings from the meshing position P2 shown in FIGS. 2 and 5 to the release position P1 shown in FIGS. 4 and 6, the free end 73 is released to the swing wheel 32 via the swing ring 55. With the spring body 71 in contact with the position P1 side, the spring body 71 is elastically deformed in the radial direction according to the swing of the swing wheel 32. At this time, the opposing portions that are radially adjacent to each other with an interval therebetween (that is, the innermost peripheral spring portion 75, the first intermediate spring portion 76, the second intermediate spring portion 77, and the outermost peripheral spring portion 78). Are elastically deformed so as to approach or separate from each other in the swing direction L.

By using the elastic restoring force of the spring body 71, the swing wheel 32 is moved from the release position P1 shown in FIGS. 4 and 6 toward the meshing position P2 shown in FIGS. Can be biased through.
As a result, the rocking wheel 32 can be returned to the meshing position P2.

  In particular, the spring main body 71 has a curved shape having at least two or more adjacent opposing portions spaced apart in the radial direction from the free end portion 73 to the connection end portion 72, specifically, the innermost portion. It is formed in a spiral shape having four-stage opposing portions of a peripheral spring portion 75, a first intermediate spring portion 76, a second intermediate spring portion 77, and an outermost peripheral spring portion 78. Therefore, the spring main body 71 can be formed to be small in plan while sufficiently securing the effective spring length of the spring main body 71 from the free end 73 to the connection end 72.

Since the spring effective length of the spring main body 71 can be sufficiently ensured, the urging force (spring force using the elastic restoring force) by which the spring main body 71 urges the oscillating wheel 32 can be reduced. The swing wheel 32 can be urged in one direction toward the meshing position P2 with the load applied to the swing wheel 32 suppressed.
Furthermore, since the spring main body 71 can be formed small in a plane, the return spring 33 can be attached without requiring a large plane space. Therefore, it is possible to mount the return spring 33 in a smaller space than the conventional lateral contact spring.

  As described above, according to the return spring 33 of the present embodiment, it is possible to mount the return spring 33 without requiring a large plane space, and to move the swing wheel 32 toward the meshing position P2 while suppressing the load on the swing wheel 32. Can be biased in one direction.

  In particular, in the return spring 33 of the present embodiment, since the spring body 71 is formed in a spiral shape, the effective spring length from the free end 73 to the connection end 72 of the spring body 71 can be further increased. In addition, it can be formed smaller in plan view.

Further, as shown in FIG. 5, the connecting end 72 is disposed at a position deviated from the virtual axis V, and the entire spring body 71 can be elastically displaced in the swing direction L with the connecting end 72 as a base point. ing. Therefore, as shown in FIG. 6, when the swinging wheel 32 swings toward the release position P <b> 1, the spring body 71 is elastically deformed in the radial direction, and the entire spring body 71 is moved from the connection end 72 to the base point. The elastic displacement can be performed toward the release position P1 along the swing direction L. Therefore, even if the urging force of the spring main body 71 on the rocking wheel 32 is small, the rocking wheel 32 can be urged efficiently toward the meshing position P2.
Further, since the fixed frame portion 70 is formed in an annular shape, the spring main body 71 can be stably supported in a cantilever shape with little rattling, and the above-described operation and effect using the spring main body 71 is more appropriately performed. Can be successful.

  Further, since the hoist train wheel mechanism 15 of the present embodiment includes the above-described return spring 33, the hoist wheel train mechanism 15 itself can be configured using a small plane space as shown in FIG. it can. Further, since the return spring 33 is used, it is possible to suppress the rocking vehicle 32 from strongly pressing the first transmission wheel 35, so that the load applied to the meshing portion between the first transmission wheel 35 and the rocking wheel 32 is reduced. Can be suppressed. Further, since the urging force of the return spring 33 can be reduced, the swing wheel 32 can be smoothly swung to the release position P1.

  Furthermore, according to the movement 10 and the mechanical timepiece 1 of the present embodiment, the hoist train wheel mechanism 15 itself can be configured using a small plane space, so that the movement can be further reduced in size and thickness. And a mechanical timepiece.

(Modification of First Embodiment)
In the first embodiment, as shown in FIG. 5, the free end portion 73 is disposed closer to the release position P1 than the rocking wheel 32, and the free end portion 73 contacts the rocking wheel 32 via the rocking ring 55 from the release position P1 side. By doing so, the rocking wheel 32 was urged toward the meshing position P2, but the invention is not limited to this.
For example, in FIG. 5, the free end 73 is disposed closer to the meshing position P2 than the swing wheel 32, and the free end 73 is integrally fixed to the swing ring 55 by welding or the like, or integrally connected by engagement or the like. You may. Thus, the swing wheel 32 can be urged by the free end portion 73 via the swing ring 55 so as to be pulled toward the meshing position P2. Therefore, even in this case, the same operation and effect can be achieved.
In any case, as long as the swinging wheel 32 can be biased toward the meshing position P2, the relative positional relationship of the free end portion 73 to the swinging wheel 32 may be changed as appropriate. However, in the case of the configuration as in the first embodiment, a simple configuration in which the free end portion 73 is pressed against the rocking wheel 32 from the release position P1 side, and the return spring 33 is Can be combined, so that the return spring 33 can be easily attached.

Further, the shape of the return spring 33 is not limited to the shape of the first embodiment.
For example, as shown in FIG. 7, the shape of the fixed frame portion 81 may be a return spring 80 formed in an elliptical shape in a plan view that is long in the swinging direction L. In this case, since the size of the fixed frame portion 81 itself can be easily reduced, the return spring 80 can have a smaller planar shape. The shape of the fixed frame portion 81 may be, for example, a circular shape or a square shape in plan view.
Further, for example, instead of forming the fixed frame portion 91 in a ring shape as shown in FIG. 8, a return spring 90 having a fixed frame portion 91 formed so as to partially surround the spring body 71 from the radial outside may be used. I do not care.
As described above, in the present invention, the shape of the fixed frame portion is not limited to a specific shape, and may be appropriately changed according to, for example, the shape of the base plate 11 or the shape of the depression 60 formed in the base plate 11. I don't care.

Further, as shown in FIG. 9, a curved portion 102 curved along an Archimedes curve centered on the fifth axis O5 (origin) of the rocking wheel 32 located at the meshing position P2, and a straight line along the rocking direction L The return spring 100 may include a spiral spring main body 101 in which the linear portions 103 extending in a spiral shape are alternately arranged.
In this case, the innermost peripheral spring portion 75, the first intermediate spring portion 76, the second intermediate spring portion 77, and the outermost peripheral spring portion 78 are formed by combining the curved portion 102 and the straight portion 103, respectively.

  In the case of the return spring 100 configured as described above, since the spring main body 101 is formed in a spiral shape having the linear portion 103 extending linearly in the swing direction L, the swing wheel 32 meshes. When the spring body 101 swings from the position P2 side to the release position P1 side, it is easy to positively elastically deform the entire spring body 101 in the swing direction L. Thereby, the rocking wheel 32 can be effectively biased in the direction from the release position P1 side to the meshing position P2 side along the rocking direction L, and the biasing force of the spring body 101 on the rocking wheel 32 is small. However, the swing wheel 32 can be appropriately biased toward the meshing position P2.

  Further, as shown in FIG. 10, the return spring 110 may be a combination of the fixed frame portion 81 shown in FIG. 8 and the spring main body 101 shown in FIG.

Further, as shown in FIG. 11, a return spring 120 in which a fixed frame portion 121 having a shape obtained by extending the outermost peripheral spring portion 78 may be combined with the spring main body 101 shown in FIG.
The return spring 120 shown in FIG. 11 includes a third intermediate spring portion 122 between the second intermediate spring portion 77 and the outermost peripheral spring portion 78, and the number of turns of the spring body 101 is larger by one turn. 120. In the case of the return spring 120 configured as described above, the entire shape of the return spring 120 including the fixed frame portion 121 can be formed in a spiral shape. can do.

(2nd Embodiment)
Next, a second embodiment according to the present invention will be described with reference to the drawings. In the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.

  In the first embodiment, the swing wheel 32 is disposed so as to be located between the round wheel 30 and the first transmission wheel 35. In the present embodiment, the swing wheel 32 is connected to the first transmission wheel 35 and the second transmission wheel 35. It is arranged so as to be located between the transmission wheel 36. Furthermore, in the first embodiment, the return spring 33 wound with a plurality of turns so that the spring main bodies 71 are adjacent to each other at substantially equal intervals in the radial direction has been described as an example, but in the present embodiment, the return springs 33 are adjacent to each other. The return spring in which the spring body is formed so that the interval between the opposing portions becomes uneven will be described as an example.

  As shown in FIGS. 12 and 13, in the hoisting wheel train mechanism (wheel train mechanism according to the present invention) 130 of the present embodiment, the swinging wheel 32 is provided between the first transmission wheel 35 and the second transmission wheel 36. It is configured to be arranged. The first transmission wheel 35 is arranged to mesh with the round wheel 30, and the second transmission wheel 36 is arranged to mesh with the square wheel 23.

  In the first transmission wheel 35 of the present embodiment, the first transmission gear 35 c meshes with the round gear 30 a of the round wheel 30. Thus, the first transmission wheel 35 is rotatable around the third axis O3 with the rotation of the round wheel 30. When the mainspring 14 is wound up, the first transmission wheel 35 rotates clockwise around the second axis O2 as shown by the arrow in FIG. 12 when the round wheel 30 is rotated in the third direction as shown by the arrow in FIG. It rotates counterclockwise around the axis O3.

  The rocking wheel 32 moves along the first rocking hole 50 and the second rocking hole 51 formed in the main plate 11 and the train wheel bridge 12, respectively, and the meshing position P2 shown in FIGS. It can swing between the release position P1.

  As shown in FIG. 14, at the release position P <b> 1, the engagement of the rocking wheel 32 with the second transmission wheel 36 is released, and the second transmission from the round wheel 30 via the first transmission wheel 35 and the rocking wheel 32. The position is such that the transmission of power to the vehicle 36 is interrupted. As shown in FIG. 12, the meshing position P2 is such that the swinging wheel 32 meshes with the second transmission wheel 36 and the second transmission wheel 36 via the first transmission wheel 35 and the rocking wheel 32 from the round wheel 30 side. This position allows power transmission to the side.

As shown in FIGS. 12 and 13, the oscillating gear 32 c of the present embodiment has a structure in which the oscillating gear 32 c is provided with respect to the first transmission gear 35 c of the first transmission wheel 35 and the second transmission pinion 36 c of the second transmission wheel 36. Are engaged with each other. In particular, the oscillating gear 32c meshes with the second transmission pinion 36c when the oscillating wheel 32 is located at the meshing position P2, and the second transmission pinion when the oscillating wheel 32 is at the release position P1. 36c is disengaged.
However, as shown in FIGS. 12 and 14, the swing gear 32c always meshes with the first transmission gear 35c regardless of the swing position of the swing wheel 32.

Thus, the rocking wheel 32 can rock along the rocking direction L between the release position P1 and the meshing position P2 in a state in which the rocking wheel 32 is meshed with the first transmission wheel 35.
Accordingly, when the rocking wheel 32 is located at the meshing position P2, the power from the round wheel 30 via the first transmission wheel 35 can be transmitted to the second transmission wheel 36, and the rocking wheel 32 can be released. When it is located at P1, the power transmission path from the round wheel 30 through the first transmission wheel 35 to the second transmission wheel 36 is cut off, and the transmission of power to the second transmission wheel 36 is performed. It is possible to shut off.

  When the mainspring 14 is wound up, the first transmission wheel 35 rotates counterclockwise around the third axis O3 when the mainspring 14 is wound up, thereby turning clockwise around the fifth axis O5 as shown by an arrow in FIG. Rotate. Thus, when the mainspring 14 is wound up, the second transmission wheel 36 rotates counterclockwise around the fourth axis O4 as indicated by an arrow in FIG. Therefore, when the mainspring 14 is wound, the square wheel 23 is rotated in the third rotation direction M3 with the rotation of the second transmission wheel 36, and the mainspring 14 can be wound.

  The rocking wheel 32 configured as described above is constantly urged from the release position P1 side to the meshing position P2 side by the return spring 140 shown in FIG.

(Return spring)
As shown in FIGS. 12, 13, and 15, the return spring 140 is housed inside a spring recess 135 formed in the main plate 11. Then, the return spring 140 urges the rocking wheel 32 toward the meshing position P2 via the rocking ring 55, and presses the rocking wheel 32 against the second transmission wheel 36. The first swing hole 50 is formed in the bottom wall of the spring recess 135.

  The base plate 11 is formed so that a plurality of other housing recesses are connected to the spring recesses 135. One of the plurality of accommodation recesses is formed, for example, deeper than the spring recess 135, and is used to set the return spring 140 into the spring recess 135 or to remove the return spring 140 from the spring recess 135. 136.

  The return spring 140 has an annular fixed frame 141 fixed inside the spring recess 135, and is disposed inside the fixed frame 141 and elastically supported in a cantilever manner with respect to the fixed frame 141. And a deformable spring body 142.

  The fixed frame 141 is formed in an annular shape surrounding the spring body 142 from the outside in the radial direction. The fixed frame portion 141 is formed in an annular shape along the side wall portion 135a that defines the spring recess 135, and is at least partially fitted inside the side wall portion 135a. As a result, the return spring 140 is housed without dropping out of the spring recess 135.

  The fixed frame portion 141 is integrally formed with a flange portion 143 that enters the setting concave portion 136. As described above, since the setting recess 136 is formed deeper than the spring recess 135, the gap along the fifth axis O5 direction is provided between the bottom wall of the setting recess 136 and the flange 143. Are formed. This allows a fingertip, a tool, or the like, for example, to enter under the flange portion 143 using this gap, and the return spring 140 can be pushed upward through the flange portion 143. Thereby, the return spring 140 can be easily removed from the inside of the spring recess 135.

The spring main body 142 is a thin plate spring made of a metal such as iron or nickel, for example, and has a base end serving as a connection end 145 connected to the fixed frame 141 and a tip end swinging through the swing ring 55. The free end 146 is capable of contacting the moving vehicle 32.
The spring main body 142 is formed in a curved shape having at least two or more adjacent opposing portions spaced apart in the radial direction from the free end 146 to the connection end 145. In the present embodiment, the spring body 142 is formed in a spiral shape that surrounds the swinging wheel 32 in four stages (multi-stages) from the outside in the radial direction.

The free end 146 is formed in an annular shape that surrounds the axle of the rocking wheel 32 from the outside in the radial direction. Specifically, the free end 146 is formed in a ring shape whose inner diameter is slightly larger than the outer diameter of the swing ring 55, and surrounds the axle of the swing wheel 32 via the swing ring 55.
In the illustrated example, the free end 146 is shown to be in contact with the outer peripheral surface of the swing ring 55 without any gap, but a slight gap is formed between the free end 146 and the swing ring 55. It may be formed.

  As shown in FIG. 15, the spring body 142 includes a free end 146 and is located at the radially innermost inner spring portion 150, and a first intermediate portion surrounding the innermost peripheral spring portion 150 from the radial outside. A spring portion 151, a second intermediate spring portion 152 surrounding the first intermediate spring portion 151 from the radial outside, and a connection end portion 145, and surrounding the second intermediate spring portion 152 from the radial outside, and a radially outermost portion. And an outermost peripheral spring portion 153, which is formed in a continuous spiral shape.

  Note that the innermost peripheral spring portion 150, the first intermediate spring portion 151, the second intermediate spring portion 152, and the outermost peripheral spring portion 153 function as the above-described facing portions. Therefore, the spring body 142 of the present embodiment is formed in a spiral shape having four steps of opposing portions, in combination with the fact that the free end portion 146 is formed in an annular shape.

  The spring body 142 is connected to the fixed frame 141 via the connection end 145 such that the free end 146 urges the swinging wheel 32 toward the meshing position P2. The connection end 145 is disposed at a position off the imaginary axis V extending through the fifth axis O5 and along the swing direction L in plan view as viewed from the direction of the fifth axis O5. As a result, the spring body 142 is connected to the fixed frame 141 so that the whole body can be elastically deformed in the swing direction L with the connection end 145 as a base point.

As described above, the spring body 142 of the present embodiment is formed such that the intervals between the opposing portions adjacent to each other are unequal.
More specifically, the spring main body 142 is opposed to each other adjacent to each other on the side opposite to the biasing direction (ie, the side opposite to the direction from the release position P1 to the engagement position P2) with respect to the fifth axis O5 of the rocking wheel 32. Intervals (H1, H2, H3) along the swinging direction L formed between the portions (the innermost peripheral spring portion 150, the first intermediate spring portion 151, the second intermediate spring portion 152, and the outermost peripheral spring portion 153). At least one of the opposing portions (the innermost peripheral spring portion 150, adjacent to each other) in the biasing direction (that is, the direction from the release position P1 toward the meshing position P2) with respect to the fifth axis O5 of the rocking wheel 32. The gaps H4, H5, H6 along the swing direction L formed between the first intermediate spring portion 151, the second intermediate spring portion 152, and the outermost peripheral spring portion 153) are formed wider.

In the interval between the innermost peripheral spring portion 150 and the first intermediate spring portion 151 along the swing direction L, the interval between portions located on the side opposite to the biasing direction with respect to the fifth axis O5 is different. The interval H1 is set, and the interval between portions located on the biasing direction side of the fifth axis O5 is set as the interval H4.
Among the intervals along the swing direction L between the first intermediate spring portion 151 and the second intermediate spring portion 152, the interval between portions located on the opposite side to the biasing direction with respect to the fifth axis O5 is the interval H2. The interval between portions located on the biasing direction side of the fifth axis O5 is set as an interval H5.
Among the intervals along the swing direction L between the second intermediate spring portion 152 and the outermost peripheral spring portion 153, the interval between portions located on the side opposite to the biasing direction with respect to the fifth axis O5 is equal to the interval H3. The interval between portions located on the biasing direction side of the fifth axis O5 is set as an interval H6.

In the present embodiment, the spring main body 142 is formed such that each of the intervals H1, H2, and H3 is wider than the intervals H4, H5, and H6. However, the present invention is not limited to this case, and at least one of the intervals H1, H2, and H3 may be formed so as to be wider than the intervals H4, H5, and H6.
It should be noted that the relationship between these intervals is naturally maintained from the stage of the natural state of the spring body 142 before the swing wheel 32 is combined with the spring body 142, as shown in FIG. The spring body 142 is stationary at a position slightly closer to the biasing direction side than the first swing hole 50 in the natural state. Therefore, by combining the spring body 142 and the rocking wheel 32 as shown in FIG. 15, the spring body 142 urges the rocking wheel 32 toward the meshing position P2 while maintaining the above-described relationship between the intervals. It is possible.

(Operation of mechanical watch)
Next, even in the case of the mechanical timepiece 1 including the hoisting wheel train mechanism 130 including the return spring 140 configured as described above, the same operation and effect as those of the first embodiment can be achieved.
That is, when the mainspring 14 is manually wound up, the winding stem 20 is rotated in the first rotation direction M1 via the crown 21 as shown in FIG. The wheel 30 is rotated clockwise around the second axis O2.

Since the swing wheel 32 is urged to the meshing position P2 by the return spring 140, it is in a state of meshing with both the first transmission wheel 35 and the second transmission wheel 36. Therefore, the first transmission wheel 35 can be rotated counterclockwise around the third axis O3 with the rotation of the round wheel 30 and the rocking wheel 32 is rotated clockwise around the fifth axis O5. Thus, the second transmission wheel 36 can be rotated counterclockwise around the fourth axis O4 with the rotation of the rocking wheel 32. Then, with the rotation of the second transmission wheel 36, the square wheel 23 can be rotated in the third rotation direction M3.
Thus, the power transmitted to the round wheel 30 can be transmitted to the second transmission wheel 36 via the first transmission wheel 35 and the rocking wheel 32, and further, the square wheel wheel via the second transmission wheel 36. 23. By rotating the square wheel 23 in the third rotation direction M3, the mainspring 14 housed inside the barrel wheel 13 can be wound up through the barrel barrel.

  When the mainspring 14 is wound up, as shown in FIG. 14, when the winding stem 20 is rotated in a second rotation direction M2 opposite to the first rotation direction M1 determined in advance, a round hole wheel is used. Numeral 30 rotates counterclockwise around the second axis O2 as indicated by the arrow shown in FIG. Therefore, the power in the reverse direction acts on the first transmission wheel 35 from the round wheel 30 and the first transmission wheel 35 rotates clockwise around the third axis O3 as indicated by the arrow shown in FIG. I do.

  On the other hand, the rotation of the square wheel 23 in the fourth rotation direction M4, which is the unwinding direction of the mainspring 14, is regulated by the hammer 24, and accordingly, the second transmission wheel 36 is also wound around the mainspring 14. The rotation in the unwinding direction is regulated. That is, the second transmission wheel 36 is restricted from rotating clockwise around the fourth axis O4.

Therefore, the rocking vehicle 32 cannot transmit the power transmitted from the first transmission wheel 35 to the second transmission wheel 36. Further, the power transmitted from the first transmission wheel 35 to the rocking wheel 32 acts in a direction to separate the rocking wheel 32 from the second transmission wheel 36.
From these facts, the swing wheel 32 is rotated from the meshing position P2 along the swing direction L in FIGS. 14 and 17 while rotating around the fifth axis O5 in the clockwise direction opposite to the time when the mainspring 14 is wound up. It swings toward the release position P1. Accordingly, it is possible to prevent the power from the winding stem 20 from being transmitted to the square wheel 23.

  Thereafter, by stopping the rotation of the winding stem 20 in the second rotation direction M2, the swinging wheel 32 is automatically returned from the release position P1 toward the meshing position P2 by the urging force of the return spring 140. be able to. Therefore, as shown in FIG. 12, it is possible to return the swinging vehicle 32 to a state in which both the first transmission wheel 35 and the second transmission wheel 36 are meshed again.

In particular, according to the return spring 140 of the present embodiment, in addition to achieving the same operation and effect as the first embodiment, the following operation and effect can be further achieved.
When the swinging wheel 32 swings from the meshing position P2 shown in FIGS. 12 and 15 toward the release position P1 shown in FIGS. 14 and 17 against the elastic force (biasing force) of the spring body 142, the spring body 142 Is elastically deformed in the radial direction according to the swing of the swing wheel 32. At this time, the opposing portions that are radially adjacent to each other with an interval between them (that is, the innermost peripheral spring portion 150, the first intermediate spring portion 151, the second intermediate spring portion 152, and the outermost peripheral spring portion 153). Are elastically deformed so as to approach or separate from each other in the swing direction L.

  Specifically, the opposing portions (the innermost peripheral spring portion 150, the first intermediate spring portion 151, the second intermediate spring portion 152, and the outermost peripheral spring) are located on the opposite side of the biasing direction of the fifth axis O5 of the rocking wheel 32. Parts 153) approach each other, and are opposed to each other (the innermost peripheral spring part 150, the first intermediate spring part 151, the second intermediate spring part 152, and the outermost part) on the biasing direction side of the fifth axis O5 of the rocking wheel 32. The outer peripheral spring portions 153) are elastically deformed so as to be separated from each other.

At this time, as shown in FIG. 15, the spring main body 142 has opposing portions (the innermost peripheral spring portion 150, the first intermediate spring portion 151, and the Since the intervals H1, H2, and H3 between the two intermediate spring portions 152 and the outermost peripheral spring portions 153 are formed widely, as shown in FIG. 17, the facing portions (the innermost peripheral spring portions 150 and the The first intermediate spring portion 151, the second intermediate spring portion 152, and the outermost peripheral spring portion 153) can be made difficult to contact each other.
Therefore, the spring body 142 is made larger while preventing the opposing portions (the innermost peripheral spring portion 150, the first intermediate spring portion 151, the second intermediate spring portion 152, and the outermost peripheral spring portion 153) of the spring body 142 from contacting each other. It can be elastically deformed. Therefore, the spring effective length of the spring main body 142 can be further secured, and the spring main body 142 can be formed smaller in plan view.

  Further, the spring body 142 is made larger while preventing the opposing portions (the innermost spring portion 150, the first intermediate spring portion 151, the second intermediate spring portion 152, and the outermost spring portion 153) of the spring body 142 from contacting each other. Since the rocking wheel 32 can be elastically deformed, the rocking wheel 32 can be rocked with a larger stroke, and the rocking wheel 32 can be used effectively.

  Furthermore, since the free end 146 of the spring body 142 of the present embodiment is formed in a ring shape surrounding the axle of the swing wheel 32 via the swing ring 55, for example, the free end 146 is provided inside the ring-shaped free end 146. The rocking wheel 32 and the return spring 140 can be combined with the rocking wheel 32 reliably and easily by bringing the free end 146 into contact with the rocking wheel 32 by a simple method of merely inserting the axle. Therefore, the return spring 140 can be more easily attached.

  In addition, since the free end 146 is formed in a ring shape, the free end 146 can be formed when the return spring 140 is assembled, as compared with a case where the free end 146 is formed in a simple plate-like shape or a rod shape, for example. Inconveniences such as sudden contact with or hooking on a peripheral structure (for example, the first swing hole 50 or the like) are unlikely to occur, and the free end 146 is unintentionally crushed, for example, to bend and deform. Such inconvenience is unlikely to occur. Also in this respect, the return spring 140 can be easily attached.

  Although the embodiments of the present invention have been described above, these embodiments are presented as examples and are not intended to limit the scope of the invention. The embodiment can be implemented in other various forms, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. The embodiment and its modified examples include, for example, those easily conceivable by those skilled in the art, those substantially the same, those in an equivalent range, and the like.

  For example, in each of the above embodiments, a so-called manual winding mechanical timepiece has been described as an example.However, the present invention is not limited to this case. For example, a mechanical timepiece corresponding to both manual winding and automatic winding is used. No problem. In this case, for example, at the time of automatic winding utilizing the rotating torque of the rotating weight, the swinging wheel may swing from the meshing position side to the release position side against the urging force of the return spring.

Further, in each of the above-described embodiments, the case has been described as an example in which the swinging wheel constituting the hoisting train train mechanism is biased in one direction using the return spring. It is not limited to use.
The return spring only needs to be able to bias a rocking wheel that rocks between the first position and the second position along the rocking direction, and can be used for various wheel train mechanisms.

Furthermore, in each of the above embodiments, the spring main body is formed in a spiral shape, but is not limited to the spiral shape. For example, a bellows-shaped spring main body in which at least two or more opposing portions are arranged at intervals in the radial direction by bending a plurality of times may be used. Even in this case, the same function and effect as the spiral shape can be achieved.
In any case, the spring body may be formed in a curved shape having at least two or more adjacent opposing portions spaced apart in the radial direction from the free end to the connection end.

L: swing direction V: virtual axis line O5: fifth axis line (center axis of rocking vehicle)
P1: Release position (first position)
P2: meshing position (second position)
1 ... mechanical watch 10 ... movement (movement for watch)
13 ... barrel car 14 ... spring 15, 130 ... winding wheel train mechanism (wheel train mechanism)
Reference numeral 20: Makima 23: Square hole wheel 30: Round hole wheel 32: Swing wheel 33, 80, 90, 100, 110, 120, 140 ... Return spring 35: First transmission wheel (transmission wheel)
36 Second transmission vehicle (transmission vehicle)
70, 81, 91, 121, 141 ... fixed frame part 71, 101, 142 ... spring body 72, 145 ... connecting end 73, 146 ... free end 75, 150 ... innermost peripheral spring part (opposed part of spring body) )
76, 151 ... 1st intermediate spring part (opposite part of a spring main body)
77, 152: second intermediate spring portion (opposing portion of the spring body)
78, 153... Outermost peripheral spring portion (opposing portion of spring body)
102: curved portion 103: linear portion

Claims (11)

A return spring for urging a rocking vehicle arranged to be rockable between a first position and a second position along a rocking direction from a first position side to a second position side,
A fixed frame part,
An elastically deformable cantilevered spring body, a base end of which is a connection end connected to the fixed frame portion, and a tip end of which is a free end which can contact the rocking vehicle; With
The free end is capable of contacting the rocking vehicle in a state where the rocking vehicle is biased toward the second position side,
The spring body is adjacent to the free end portion at a distance in a radial direction intersecting a center axis of the rocking wheel when viewed from an axial direction of the rocking wheel, from the free end portion to the connection end portion. It is formed in a curved shape having at least two or more opposing portions ,
The return spring , wherein the spring main body is formed in a spiral shape surrounding the swinging wheel in multiple stages from the outside in the radial direction . The return spring according to claim 1,
A return spring, wherein the free end is disposed closer to the first position than the rocking vehicle and is capable of contacting the rocking vehicle from the first position. The return spring according to claim 1 or 2 ,
The spring body is
At least one of the intervals along the rocking direction formed between the opposing portions adjacent to each other on the side opposite to the biasing direction with respect to the center axis of the rocking wheel is the rocking motion. A return spring, which is formed wider on the biasing direction side than the center axis of the moving vehicle than each interval along the swing direction formed between the opposing portions adjacent to each other. The return spring according to any one of claims 1 to 3 ,
The spring body has a curved portion curved along an Archimedes curve centered on the central axis of the rocking wheel, and a linear portion extending linearly along the rocking direction, and has a longitudinal length of the spring body. A return spring formed in a spiral shape alternately arranged in the direction. The return spring according to any one of claims 1 to 4 ,
The connection end portion is disposed at a position off the imaginary axis passing through the center axis of the rocking vehicle and extending along the rocking direction,
A return spring, wherein the spring body is entirely elastically displaceable in the swing direction with the connection end as a base point. The return spring according to any one of claims 1 to 5 ,
A return spring, wherein the free end is formed in an annular shape surrounding the axle of the rocking wheel from the radial outside. The return spring according to any one of claims 1 to 6 ,
A return spring, wherein the fixed frame portion is formed in an annular shape surrounding the spring body from a radial outside. A wheel train mechanism comprising the return spring according to any one of claims 1 to 7 . The train wheel mechanism according to claim 8 ,
A round hole wheel that rotates by rotating the winding stem,
A transmission wheel that transmits power to a square hole wheel that rotates the mainspring inside the barrel car by rotation,
The swing wheel, which is disposed between the round wheel and the transmission wheel, transmits the power from the round wheel to the transmission wheel, and is urged by the return spring.
The first position is a release position where the engagement of the rocking vehicle with the transmission wheel is released and the transmission of the power from the round hole wheel side to the transmission wheel side via the rocking wheel is interrupted. ,
The second position is a meshing position at which the rocking wheel meshes with the transmission wheel and allows transmission of the power from the round wheel side to the transmission wheel side via the rocking wheel,
A wheel train that is swingable along the swing direction between the release position and the meshing position along the swing direction, and is urged toward the meshing position by the return spring; mechanism. A timepiece movement comprising the wheel train mechanism according to claim 8 or 9 . A mechanical timepiece comprising the timepiece movement according to claim 10 .

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