JP2017138286A - Gear, wheel train mechanism, movement, and watch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gear, a wheel train mechanism, a movement, and a watch that can save a space and reduce the adverse effect of a backlash.SOLUTION: There is provided a gear body 41 having coaxial gears 61 and 62. The gears 61 and 62 can dependently rotate in the circumferential direction of the shaft center. The gear 61 has a first base body 63 and a first elastic arm part 64 integrally formed with the first base part 63. The first elastic arm part 64 is connected to the gear 62, is bending-elastically deformed according to the position of the gears 61 and 62 in the circumferential direction, and oppositely energizes the gears 61 and 62 into the circumferential direction according to the amount of the bending elastic deformation.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a gear, a gear train mechanism, a movement, and a timepiece.

A so-called “backlash”, which is a gap intentionally provided in the rotation direction, is set between gears that transmit power from a power source and mesh with each other and rotate. In the gear train in which the backlash is set, the friction between the tooth surfaces of the meshing gears is moderately suppressed.
For example, in a mechanism that transmits the rotational force of the crown with a gear train and rotates the shaft provided with an electrical contact and a display means for displaying the function on the dial, the gear has backlash. There may be a deviation in operation before the rotational force is transmitted to the final stage. When the deviation of this operation is large, the operator feels uncomfortable. Since the crown performs forward rotation and reverse rotation, the displacement of the operation is likely to increase, and a difference in operation is likely to occur between the display and the display means.
The problem of misalignment of operation is the same for the second hand, minute hand, and hour hand constituting the tooth wheel train, and the second hand or the like is not driven immediately after the start of driving, so that the operation of the second hand or the like may be delayed.
If there are few gears that make up the gear train, the effect of backlash can be reduced by that amount, but depending on the arrangement space of the gears, it may be necessary to transmit the rotational force by increasing the number of gears. The effect of rush increases and the deviation of operation increases.

  As a mechanism for suppressing the deviation of operation, for example, a mechanism has been proposed in which a sliding resistance (braking force) is applied to the pointer wheel by pressing the pointer wheel in the radial direction with a pressing spring ( For example, see Patent Document 1).

JP 2006-242793 A

However, in the configuration described in Patent Document 1, since a mechanism for applying a braking force to the pointer wheel is provided, the structure is complicated, and it is necessary to secure a space for the mechanism. There was room for improvement.
An object of the present invention is to provide a gear, a gear train mechanism, a movement, and a timepiece that can reduce the adverse effects of backlash and can save space.

The present invention has a plurality of coaxial gears, and at least two gears adjacent to each other in the axial direction among the plurality of gears can rotate independently of each other in a circumferential direction around the axis. One of the gears has a first base and a first elastic arm portion formed integrally with the first base, and the first elastic arm portion is connected to the other gear of the two gears. And providing a gear body that undergoes bending elastic deformation in accordance with the circumferential position of the two gears and biases the two gears in the circumferential direction opposite to each other in accordance with the amount of bending elastic deformation.
According to this configuration, the gear body can be meshed with another gear while suppressing unnecessary rotation (rattle) in the gap set as backlash by the biasing force of the first elastic arm portion. . Therefore, it is possible to reduce adverse effects such as a shift in operation caused by backlash.
Unlike the conventional product that uses a presser spring, the gear body does not require a separate member outside the gear body, so that space can be saved. Therefore, the size of the timepiece can be reduced. In addition, since a dedicated component as the separate member is unnecessary, the cost can be reduced.
The gear body has a small number of parts because the first elastic arm portion is formed integrally with the first base. Therefore, the manufacturing can be facilitated and the manufacturing cost can be suppressed.
Further, in the gear body, since the two gears are biased in opposite directions, for example, when the pitch of the tooth portion becomes non-uniform or the distance from other gears fluctuates due to manufacturing reasons. Also, unnecessary rotation (rattle) in the gap set as backlash can be suppressed. Therefore, a constant rotational force can be transmitted between the other gears.

In the gear body, the other of the two gears has a second base and a second elastic arm portion formed integrally with the second base, and the second elastic arm portion is the one of the ones. A configuration is adopted in which the two gears are bent elastically deformed according to the circumferential position of the two gears, and the two gears are biased in the opposite circumferential directions according to the amount of the bending elastic deformation. May be.
According to this configuration, not only the two gears are biased in opposite directions by the first elastic arm portion, but also the two gears are biased in opposite directions by the second elastic arm portion. The applied urging force can be increased. For this reason, it is possible to reliably reduce adverse effects such as displacement of operation caused by backlash.

In the gear body, a configuration may be adopted in which the one gear is provided with a support shaft portion that rotatably supports the other gear in the circumferential direction.
According to this configuration, two gears can be easily assembled. Moreover, the center alignment of the two gears can be performed easily and accurately.

In the gear body, the other gear is provided with the other side locking receiving portion, and the first elastic arm portion has a first locking portion that is locked to the other side locking receiving portion by unevenness. Then, a configuration may be adopted in which the first locking portion is connected to the other gear by being locked to the other side locking receiving portion.
According to this configuration, the first elastic arm portion can be connected to the other gear by an easy operation.

The gear body may adopt a configuration in which a first hole portion is formed in the first base body, and the first elastic arm portion is formed to extend into an internal space of the first hole portion. Good.
According to this configuration, the one gear can be formed thin. Therefore, the gear body can be thinned.

In the gear body, the first elastic arm portion may adopt a configuration formed along the circumferential direction of the one gear.
According to this configuration, a large urging force can be applied to the two gears by elastically bending and deforming the first elastic arm portion so that the bending radius changes.

The gear train mechanism of the present invention includes the gear body.
According to this configuration, it is possible to provide a gear train mechanism that can reduce adverse effects such as a shift in operation caused by backlash and can save space.

The movement of the present invention includes the gear body.
According to this configuration, it is possible to provide a movement that can reduce adverse effects such as a shift in operation caused by backlash and can save space.

The timepiece of the present invention includes the movement.
According to this configuration, it is possible to provide a timepiece that can reduce adverse effects such as displacement of operation due to backlash and can save space.

According to the present invention, the gear body can be meshed with another gear while suppressing unnecessary rotation (rattle) in the gap set as the backlash by the biasing force of the first elastic arm portion. . Therefore, it is possible to reduce adverse effects such as a shift in operation caused by backlash.
Unlike the conventional product that uses a presser spring, the gear body does not require a separate member outside the gear body, so that space can be saved. Therefore, the size of the timepiece can be reduced. In addition, since a dedicated component as the separate member is unnecessary, the cost can be reduced.
The gear body has a small number of parts because the first elastic arm portion is formed integrally with the first base. Therefore, the manufacturing can be facilitated and the manufacturing cost can be suppressed.
In the gear body, since the two gears are biased in opposite directions to each other, for example, when the pitch of the tooth portion becomes uneven or the distance from other gears fluctuates due to manufacturing reasons, Unnecessary rotation (rattle) in the gap set as backlash can be suppressed. Therefore, a constant rotational force can be transmitted between the other gears.

It is a figure which shows embodiment which concerns on this invention, Comprising: It is an external view of a timepiece. It is a figure which shows a part of movement of the timepiece shown in FIG. 1, Comprising: (a) is a top view, (b) is sectional drawing. It is a top view which expands and shows a part of movement of the timepiece shown in FIG. It is a perspective view showing the gear body concerning a 1st embodiment of the present invention. It is a top view which shows the gear body of FIG. FIG. 5 is an exploded perspective view showing the gear body of FIG. 4. It is a top view which shows the 1st gearwheel of the gear body of FIG. It is a top view which shows the 2nd gearwheel of the gear body of FIG. It is the perspective view which looked at the 2nd gear of the gear body of Drawing 4 from the inner surface side. FIG. 5 is a plan view showing a first gear and a second gear of the gear body of FIG. 4. It is a top view which shows an example of the use condition of the gear body of FIG. It is a top view which shows the other example of the use condition of the gear body of FIG. It is a top view which shows the gear body which concerns on 2nd Embodiment of this invention. It is a disassembled perspective view which shows the gear body of a previous figure. It is a top view which shows the gear body which concerns on 3rd Embodiment of this invention. It is a disassembled perspective view which shows the gear body of a previous figure. It is a top view which shows the gear body which concerns on the modification of 2nd Embodiment of this invention. It is a disassembled perspective view which shows the gear body of a previous figure. It is a top view which shows a part of other example of the movement using the gear body of FIG. It is a top view which shows a part of other example of the movement using the gear body of FIG.

Embodiments of the present invention will be described with reference to the drawings. In the present embodiment, an analog quartz watch will be described as an example.
[First Embodiment]
(clock)
In general, a machine body including a driving part of a timepiece is referred to as a “movement”. A state in which a dial and a pointer are attached to the movement, and the dial is put into a watch case to form a finished product is referred to as “complete” of the watch.
Of the both sides of the base plate constituting the base of the watch, the side of the watch case with the glass, that is, the side with the dial is referred to as the “back side” of the movement. Of the two sides of the main plate, the side of the watch case with the case back, that is, the side opposite to the dial is referred to as the “front side” of the movement.

FIG. 1 is an external view showing a timepiece according to the first embodiment.
As shown in FIG. 1, the complete watch 1 includes a movement 10, a dial 11, and hands 12 to 14 inside a watch case 3 having a case back (not shown) and a glass 2.
The dial plate 11 has at least a scale indicating information about time. The hands 12 to 14 include an hour hand 12 indicating the hour, a minute hand 13 indicating the minute, and a second hand 14 indicating the second.

(Movement, train wheel mechanism)
2A and 2B are views showing a part of the movement 10 according to the first embodiment, wherein FIG. 2A is a plan view and FIG. 2B is a cross-sectional view. FIG. 3 is an enlarged plan view showing a part of the movement 10.
As shown in FIGS. 2 and 3, the movement 10 includes a main plate 20 and a train wheel bridge 29.
The main plate 20 constitutes the base of the movement 10. As shown in FIG. 1, a winding stem 24 is rotatably incorporated into the movement 10 through a winding stem guide hole (not shown) formed in the main plate 20. The winding stem 24 is used for time adjustment for rotating the minute hand 13 and the hour hand 12 to correct the time display (hour and minute display). A crown 53 located on the side of the watch case 3 is attached to the tip of the winding stem 24.

On the back side of the base plate 20, the dial plate 11 is disposed so as to be visible through the glass 2.
On the front side of the main plate 20, a battery (not shown), a crystal unit (not shown), a circuit board (not shown), a step motor 35 (power source), a train wheel mechanism 23, and the like are arranged.

  As shown in FIG. 2, the step motor 35 is disposed in a coil block (not shown), a stator 31 disposed so as to contact both end portions of the magnetic core of the coil block, and a rotor hole 31 a of the stator 31. And a rotor 32.

The rotor 32 is rotatably supported with respect to the main plate 20 and the train wheel bridge 29. That is, the upper shaft portion of the rotor 32 is pivotally supported by the bearing portion of the train wheel bridge 29, and the lower shaft portion of the rotor 32 is pivotally supported by the bearing portion of the main plate 20.
The rotor 32 rotates one step every second, and applies a rotational force to the fifth wheel & pinion 40 via the rotor pinion 32d.

The wheel train mechanism 23 includes a fifth wheel 40 that rotates based on the rotation of the rotor 32, a fourth wheel 41 that rotates based on the rotation of the fifth wheel 40, and a third wheel that rotates based on the rotation of the fourth wheel 41. A second wheel (not shown), a second wheel 43 that rotates based on the rotation of the third wheel, a minute wheel that rotates based on the rotation of the second wheel 43 (not shown), and the second wheel An hour wheel 44 that rotates based on the rotation of the car.
The train wheel mechanism 23 is a first embodiment of the train wheel mechanism of the present invention.
In the following description, the direction of the axis O1 of the fourth wheel & pinion 41 may be referred to as the axial direction, and the train wheel bridge 29 side (front side) along the axial direction may be referred to as the upper side, and the main plate 20 side (back side) may be referred to as the lower side. The direction orthogonal to the axis O1 is the radial direction. The axis O1 of the fourth wheel & pinion 41 coincides with the axis of the axle 60.

  The fifth wheel & pinion 40 has a fifth gear 40 a and a fifth upper pinion 40 b and is rotatably supported by the main plate 20 and the train wheel bridge 29. That is, the upper shaft portion 40 c of the fifth wheel & pinion 40 is pivotally supported by the bearing portion of the train wheel bridge 29, and the lower shaft portion 40 d of the fifth wheel & pinion 40 is pivotally supported by the bearing portion of the main plate 20. The fifth gear 40 a meshes with the rotor pinion 32 d of the rotor 32. Thereby, the fifth wheel & pinion 40 rotates as the rotor 32 rotates.

  The second wheel & pinion 43 is disposed coaxially with the axis O <b> 1 of the fourth wheel & pinion 41 and is rotatably attached to a cylindrical part 52 formed integrally with the main plate 20. The second wheel & pinion 43 has a second gear 43a that meshes with the third wheel & pinion. Thereby, the center wheel & pinion 43 rotates along with the rotation of the center wheel & pinion.

The center wheel 43 is disposed inside a cylindrical portion 52 formed integrally with the main plate 20 and is rotatably mounted on the upper opening end of the cylindrical portion 52. Thereby, the center wheel & pinion 43 can be rotated stably.
The center wheel & pinion 43 is configured to rotate once per hour, and a minute hand 13 is attached to the lower end (see FIG. 1).

The hour wheel 44 is arranged coaxially with the axial center O <b> 1 of the fourth wheel 41, is rotatably attached to the cylindrical member 52, and is located on the back side of the cylindrical member 52. The hour wheel 44 has a cylindrical gear 44a that meshes with the center wheel & pinion 43 via the minute wheel and the like. Thereby, the hour wheel 44 rotates based on the minute wheel.
The hour wheel 44 is configured to rotate once in 12 hours, and the hour hand 12 is attached (see FIG. 1).

The winding stem 24 is a timepiece part used for time adjustment for correcting the time display (hour and minute display) by rotating the minute hand 13 and the hour hand 12, and is positioned at one side of the watch case 3 at the side of the timepiece case 3. A crown 53 is attached (see FIG. 1).
As described above, the winding stem 24 is rotatably supported by the winding stem guide hole formed in the main plate 20 and can be pulled out in the axial direction. The axial position of the winding stem 24 is determined by a switching device (not shown) such as a setting lever, a crown, a crown spring and the like arranged on the front side of the main plate 20.

  On the front side of the main plate 20, the above-mentioned minute wheel is arranged that rotates through a pinion wheel (not shown) or the like when the winding stem 24 is rotated in the pulled-out state. As the minute wheel rotates, the second wheel 43 and the hour wheel 44 rotate. Thereby, time adjustment becomes possible.

(No. 4 car)
Next, the fourth wheel 41 will be described with reference to FIGS. The fourth wheel & pinion 41 is the first embodiment of the gear body of the present invention.
As shown in FIGS. 2 and 3, the fourth wheel 41 is a wheel disposed between the fifth wheel 40 and the third wheel, and is fixed to the axle 60 that is rotatable around the axis O <b> 1. The first fourth gear 61 and the second fourth gear 62 rotatably attached to the first fourth gear 61 are provided.
The first fourth gear 61 is an example of a first gear according to the present invention. The second fourth gear 62 is an example of a second gear according to the present invention. In the illustrated example, the second fourth gear 62 is positioned above the first fourth gear 61.

  As shown in FIG. 2, the axle 60 is inserted through the insertion hole inside the center wheel & pinion 43. Further, the upper shaft portion 60 a of the axle 60 is pivotally supported by the bearing portion of the train wheel bridge 29. As a result, the fourth wheel 41 can be rotated stably. The lower shaft portion 60b of the axle 60 protrudes toward the glass 2 with respect to the center wheel 43, and the second hand 14 is attached to the protruding portion (see FIG. 1).

  FIG. 4 is a perspective view showing the fourth wheel & pinion 41. FIG. 5 is a plan view showing the fourth wheel & pinion 41. FIG. 6 is an exploded perspective view showing the fourth wheel & pinion 41. FIG. 7 is a plan view showing the first fourth gear 61 of the fourth wheel 41. FIG. 8 is a plan view showing the second fourth gear 62. FIG. 9 is a perspective view of the second fourth gear 62 viewed from the inner surface side.

As shown in FIGS. 6 and 7, the first fourth gear 61 includes a first base 63, a first elastic arm portion 64 formed integrally with the first base 63, and an opposing surface 63 a of the first base 63. And a support shaft portion 65 protruding from the (upper surface).
On the outer peripheral edge of the first base 63, a plurality of tooth portions 61 a that mesh with the fifth upper pinion 40 b of the fifth wheel & pinion 40 are formed over the entire circumference. In the illustrated example, the number of teeth of the tooth portion 61a is 30. The facing surface 63a is a surface on the second fourth gear 62 side.

The first base 63 has a central hole 66 formed at a central position including the axis O1, and a first elongated hole 67 (first hole) and a first engagement at a position away from the axis O1. A hole 68 (one side latch receiving portion) is formed.
The central hole 66 is formed so as to penetrate in the thickness direction of the first base 63, and the shape in plan view is, for example, a circle.

The first elongated hole portion 67 is formed so as to penetrate in the thickness direction, and the shape in plan view is, for example, an arc shape along the direction around the axis O1 (the circumferential direction of the first base 63). Assuming a sector shape formed by the first elongated hole portion 67 and the axis O1, the central angle is, for example, 90 to 300 °. In the illustrated example, the central angle is about 270 °. The width of the first long hole portion 67 (the dimension in the radial direction of the first base 63) is preferably substantially constant over the entire length. The width of the first elongated hole portion 67 is larger than the outer diameter of the second movement restricting convex portion 79.
The one end portion 67a of the first elongated hole portion 67 is preferably a curved concave shape, for example, a semicircular shape in plan view. The radius of curvature of the one end portion 67a is preferably larger than the radius of curvature of the outer peripheral edge of the second movement restricting convex portion 79 in plan view.

The first locking hole 68 is a hole that is locked by a second locking projection 74d described later, and is formed so as to penetrate in the thickness direction. The shape in plan view is, for example, a circle. The first locking hole 68 is formed at a different position from the first elongated hole 67 in the circumferential direction of the first base 63.
In the first locking hole 68, the second locking projection 74d of the second elastic arm 74 is inserted and locked. As a result, the second elastic arm portion 74 is connected to the first fourth gear 61.

  A first movement restricting convex portion 69 is formed on the facing surface 63 a of the first base 63. The first movement restricting convex portion 69 has, for example, a circular shape in plan view, and is formed to protrude upward from the facing surface 63a. The 1st movement control convex part 69 is formed so that insertion in the 2nd long hole part 77 mentioned later is possible. The first movement restricting convex portion 69 is formed in a different position in the circumferential direction of the first base 63 from the first elongated hole portion 67 and the first locking hole portion 68.

The first elastic arm portion 64 extends into the internal space of the first long hole portion 67 from the other end portion 67b of the first long hole portion 67 toward the one end portion 67a.
The first elastic arm portion 64 includes an extension portion 64a extending from the other end portion 67b along the length direction of the first elongated hole portion 67, and a tip end portion 64b formed at the tip of the extension portion 64a. Have.
The planar view shape of the extending portion 64a is, for example, an arc shape along the direction around the axis O1 (the circumferential direction of the first base 63). The width of the extending portion 64a is, for example, constant in the length direction.
The facing surface 64c (the surface on the second fourth gear 62 side) of the extending portion 64a is flush with the facing surface 63a of the first base 63 (on the same virtual plane). It is preferable that the extension portion 64 a has the same thickness as the first base 63.

  The tip end portion 64b is, for example, cylindrical, and the upper portion thereof is a first locking convex portion 64d (first locking portion) formed so as to protrude upward with respect to the facing surface 64c of the extending portion 64a. The outer diameter of the distal end portion 64b is preferably larger than the width of the extending portion 64a.

As shown in FIG. 6, the support shaft portion 65 includes a plurality of latch portions 70 and a plurality of holding wall portions 71.
The latch part 70 has a plate-like latch body 70a and a locking claw part 70b.
The plan view shape of the latch body 70a is, for example, an arc shape along the direction around the axis O1 (the circumferential direction of the first base 63). The latch body 70a is formed to protrude upward with respect to the facing surface 63a. The latch body 70a can be elastically bent and deformed so that the locking claw portion 70b approaches and separates from the axis O1. The latch body 70 a can be inserted into the central hole 76 of the second fourth gear 62.

  The locking claw portion 70b is formed so as to protrude radially outward from the outer surface of the distal end portion of the latch body 70a. The locking claw portion 70b is formed at a position higher than the facing surface 63a. The locking claw portion 70b is formed so as to be able to restrict the movement of the second fourth gear 62 in the direction away from the first fourth gear 61 (upward).

  The plurality of latch portions 70 are formed at intervals in the direction around the axis O1 (the circumferential direction of the first base 63). In the illustrated example, the number of latch units 70 is three, and these latch units 70 are provided at equal intervals.

The holding wall portion 71 is formed to protrude upward with respect to the facing surface 63a. The planar view shape of the holding wall portion 71 is, for example, an arc shape along the direction around the axis O1 (the circumferential direction of the first base 63). The outer diameter of the holding wall 71 is substantially the same as the outer diameter of the latch body 70a, for example.
The holding wall portion 71 is formed between the adjacent latch portions 70. In the illustrated example, the number of holding wall portions 71 is 3, and these holding wall portions 71 are provided at equal intervals.
The holding wall 71 can be inserted into the central hole 76 of the second fourth gear 62.

The support shaft portion 65 is inserted through the central hole 76 of the second fourth gear 62 and can support the second fourth gear 62 so as to be rotatable around the axis O1.
A through hole 72 that penetrates the first base 63 is formed in the first base 63 adjacent to the radially outer side of the latch body 70a. Through the through hole 72, the latch body 70a is easily deformed radially outward.

As shown in FIGS. 4 to 6, 8, and 9, the second fourth gear 62 includes a second base 73 and a second elastic arm 74 formed integrally with the second base 73. .
The second fourth gear 62 is rotatably attached to the first fourth gear 61 in a state where it overlaps the upper side of the first fourth gear 61. Therefore, the second fourth gear 62 can be rotated around the axis O <b> 1 independently of the first fourth gear 61.

The outer diameter of the second fourth gear 62 is preferably the same as the outer diameter of the first fourth gear 61.
On the outer peripheral edge of the second base 73, a plurality of tooth portions 62a that engage with the fifth upper pinion 40b of the fifth wheel & pinion 40 are formed over the entire circumference. The number of teeth 62 a of the second fourth gear 62 is preferably the same as the number of teeth 61 a of the first fourth gear 61. In the illustrated example, the number of teeth of the tooth portion 62a is 30. The pitch of the tooth portions 62a (the circumferential distance between the adjacent tooth portions 62a) is preferably the same as the pitch of the tooth portions 61a of the first fourth gear 61.
The opposing surface 73a (lower surface) (see FIG. 9) of the second base 73 is a surface on the first fourth gear 61 side. The facing surface 73 a may be in contact with the facing surface 63 a of the first fourth gear 61.

The second base 73 has a central hole 76 formed at a central position including the axis O1, and a second elongated hole 77 (second hole) and a second locking portion at a position away from the axis O1. A hole 78 (the other side latch receiving portion) is formed.
The central hole 76 is formed so as to penetrate in the thickness direction of the second base 73, and the planar view shape is, for example, a circle. The central hole portion 76 allows the support shaft portion 65 (the latch body 70a and the holding wall portion 71) of the first fourth gear 61 to be inserted.
The inner diameter of the central hole 76 is substantially the same as the outer diameter of the latch main body 70a and the holding wall 71 so that the second fourth gear 62 rotates smoothly with respect to the first fourth gear 61, or the latch main body. 70a and the outer diameter of the holding wall 71 are preferably slightly larger.

The second elongated hole portion 77 is formed so as to penetrate in the thickness direction, and the shape in plan view is, for example, an arc shape along the direction around the axis O1 (the circumferential direction of the second base body 73). Assuming a sector shape formed by the second elongated hole portion 77 and the axis O1, the central angle is, for example, 90 to 300 °. In the illustrated example, the central angle is about 270 °. The width of the second elongated hole portion 77 (the dimension in the radial direction of the second base 73) is preferably substantially constant over the entire length. The width of the second elongated hole portion 77 is larger than the outer diameter of the first movement restricting convex portion 69.
The one end 77a of the second elongated hole 77 is preferably a curved concave shape, for example, a semicircular shape in plan view. The radius of curvature of the one end 77a is preferably larger than the radius of curvature of the outer peripheral edge of the first movement restricting convex portion 69 in plan view.

The second locking hole 78 is a hole that is locked by the first locking protrusion 64d, and is formed so as to penetrate in the thickness direction. The shape in plan view is, for example, a circle. The second locking hole 78 is formed at a different position from the second elongated hole 77 in the circumferential direction of the second base 73.
The first locking projection 64d of the first elastic arm portion 64 is inserted into the second locking hole 78 and locked. As a result, the first elastic arm portion 64 is connected to the second fourth gear 62.

  A second movement restricting convex portion 79 is formed on the facing surface 73 a of the second base 73. The second movement restricting convex portion 79 has, for example, a circular shape in plan view, and is formed to protrude downward from the facing surface 73a. The second movement restricting convex portion 79 is formed so as to be insertable into the first long hole portion 67 of the first fourth gear 61. The second movement restricting convex portion 79 is formed in a different position in the circumferential direction of the second base 73 from the second elongated hole portion 77 and the second locking hole portion 78.

The second elastic arm portion 74 extends into the internal space of the second long hole portion 77 from the other end portion 77b of the second long hole portion 77 toward the one end portion 77a.
The second elastic arm portion 74 includes an extension portion 74a extending from the other end portion 77b along the length direction of the second long hole portion 77, and a tip portion 74b formed at the tip of the extension portion 74a. Have.
The planar view shape of the extending portion 74a is, for example, an arc shape along the direction around the axis O1 (the circumferential direction of the second base 73). The width of the extending portion 74a is, for example, constant in the length direction.
The opposing surface 74c (the surface on the first fourth gear 61 side) of the extending portion 74a is flush with the opposing surface 73a of the second base 73 (on the same virtual plane). The thickness of the extending portion 74 a is preferably the same as the thickness of the second base 73.

  The distal end portion 74b is, for example, a cylindrical shape, and a lower portion thereof is a second locking convex portion 74d (second locking portion) formed to protrude downward with respect to the facing surface 74c of the extending portion 74a. The outer diameter of the tip portion 74b is preferably larger than the width of the extending portion 74a.

  As shown in FIG. 6, the extending direction of the second elastic arm portion 74 is opposite to the extending direction of the first elastic arm portion 64 of the first fourth gear 61. In the illustrated example, the extension direction of the first elastic arm portion 64 is clockwise with respect to the axis O1, as viewed from above, whereas the extension direction of the second elastic arm portion 74 is: This is a counterclockwise direction with respect to the axis O1.

As shown in FIG. 10, when the first fourth gear 61 and the second fourth gear 62 are overlapped in a state where the first elastic arm portion 64 and the second elastic arm portion 74 are not elastically deformed, the first elastic arm The first locking convex portion 64 d of the tip end portion 64 b of the portion 64 does not coincide with the second locking hole portion 78 of the second fourth gear 62 in the circumferential direction. In the illustrated example, the first locking convex portion 64 d is in a position shifted in the clockwise direction with respect to the second locking hole portion 78.
The second locking projection 74 d of the tip 74 b of the second elastic arm 74 does not coincide with the first locking hole 68 of the first fourth gear 61 in the circumferential direction. In the illustrated example, the second locking projection 74 d is at a position shifted in the counterclockwise direction with respect to the first locking hole 68.

  As shown in FIGS. 4 to 6, in the fourth wheel & pinion 41, the first locking projection 64 d is inserted into the second locking hole 78, and the second locking projection 74 d is the first locking hole 68. In this state, the first fourth gear 61 and the second fourth gear 62 are combined. In this state, the first elastic arm portion 64 and the second elastic arm portion 74 are elastically bent and deformed in a direction in which the radius of curvature decreases.

  Since the first elastic arm portion 64 and the second elastic arm portion 74 are in an elastically deformed state, the first fourth gear 61 and the second fourth gear 62 are the first elastic arm portion 64 and the second elasticity. The arms 74 are biased in opposite directions by the elastic force of the arms 74. In the illustrated example, the first fourth gear 61 is urged counterclockwise by the second elastic arm portion 74, and the second fourth gear 62 is urged clockwise by the first elastic arm portion 64. . The first elastic arm portion 64 and the second elastic arm portion 74 have a function of urging the gears 61 and 62 in opposite directions by their elastic force.

  In the example shown in the figure, the first elastic arm portion 64 and the second elastic arm portion 74 are elastically bent and deformed in the direction in which the bending radius decreases, but are elastically bent in the direction in which the bending radius increases. An urging force may be applied to the first fourth gear 61 and the second fourth gear 62 by deforming.

  The first movement restricting convex portion 69 of the first fourth gear 61 is inserted into the second long hole 77 of the second fourth gear 62. The first fourth gear 61 is restricted from moving in the urging direction by the second elastic arm portion 74 when the first movement restricting convex portion 69 is engaged with the one end portion 77 a of the second elongated hole portion 77. In the illustrated example, the first movement restricting convex portion 69 is engaged with the one end 77 a of the second long hole portion 77, whereby the movement of the first fourth gear 61 in the counterclockwise direction is restricted.

  The second movement restricting convex portion 79 of the second fourth gear 62 is inserted into the first long hole portion 67 of the first fourth gear 61. The second fourth gear 62 is restricted from moving in the urging direction by the first elastic arm portion 64 when the second movement restricting convex portion 79 is engaged with the one end portion 67 a of the first elongated hole portion 67. In the illustrated example, the second movement restricting convex portion 79 is engaged with the one end portion 67 a of the first elongated hole portion 67, whereby the clockwise movement of the second fourth gear 62 is restricted.

  Since the first fourth gear 61 and the second fourth gear 62 can rotate independently of each other, the second movement restricting convex portion 79 is separated from the one end 67a of the first elongated hole portion 67, and the first movement restricting portion The first fourth gear 61 and the second fourth gear 62 can be arranged so that the convex portion 69 is in a state of being separated from the one end portion 77 a of the second elongated hole portion 77. In this state, the first fourth gear 61 and the second fourth gear 62 are urged in opposite directions by the elastic forces of the first elastic arm portion 64 and the second elastic arm portion 74, and It can move in either direction.

  The relative rotation width of the first fourth gear 61 and the second fourth gear 62 is at least half the pitch of the tooth portions 61a and 62a (preferably one pitch or more of the tooth portions 61a and 62a). preferable. For example, the first fourth gear 61 and the second fourth gear 62 are in a state in which the circumferential positions of the tooth portions 61a and 62a coincide with each other and the circumferential positions of the tooth portions 61a and 62a are shifted by a half pitch or more. It can be movable relative to each other.

The support shaft portion 65 of the first fourth gear 61 is inserted into the central hole 76 of the second fourth gear 62. The second fourth gear 62 is rotatably supported by the support shaft portion 65 with respect to the first fourth gear 61.
The movement of the second fourth gear 62 in the direction away from the first fourth gear 61 (upward) is restricted by the locking claw portion 70b.

(Clock action)
Next, the operation of the timepiece 1 configured as described above will be described.
As shown in FIG. 2, in the movement 10, when the crystal unit in the crystal unit oscillates at a predetermined frequency, the oscillation unit built in the integrated circuit outputs a reference signal based on the vibration of the crystal unit. The frequency divider divides the output signal from the oscillator.
Thus, the driving unit outputs a motor driving signal for driving the step motor 35 based on the output signal of the frequency dividing unit. When this motor drive signal is input to the coil block, the stator 31 is magnetized to rotate the rotor 32. At this time, the rotor 32 continues to rotate, for example, while rotating 180 degrees every second.

  The rotational force of the rotor 32 is transmitted to the fourth wheel 41 via the fifth wheel 40, and the fourth wheel 41 rotates once per minute. Thereby, the second hand 14 can be rotated once per minute. Further, the rotational force transmitted to the fourth wheel 41 is transmitted to the third wheel, the second wheel 43 and the hour wheel 44, and these vehicles rotate. At this time, the center wheel 43 rotates once per hour, and the hour wheel 44 rotates once per 12 hours. Thereby, the minute hand 13 can be rotated once per hour, and the hour hand 12 can be rotated once per 12 hours.

The transmission of rotational force from the fifth wheel 40 to the fourth wheel 41 will be described in detail.
As shown in FIG. 3, the tooth portions 61 a and 62 a of the first fourth gear 61 and the second fourth gear 62 can be in a state where the phases are shifted in the circumferential direction. A clearance in the circumferential direction between the tooth portion 61a of the first fourth gear 61 and the tooth portion 62a of the second fourth gear 62 is referred to as “H1”. The first fourth gear 61 and the second fourth gear 62 are urged in the direction in which the gap H1 is reduced by the elastic force of the first elastic arm portion 64 and the second elastic arm portion 74.

The tooth portion 40b1 of the fifth upper pinion 40b in the fifth wheel & pinion 40 is in the tooth portion (at least one of the tooth portion 61a and the tooth portion 62a) of the fourth wheel & pinion 41 in a state of entering the gap H1 between the tooth portions 61a and 62a. Engage. Therefore, when the fifth upper kana 40b rotates in the CCW direction (counterclockwise direction) based on the rotation of the rotor 32, for example, the rotational force is transmitted to the tooth portion (tooth portion 61a or tooth portion 62a) of the fourth wheel & pinion 41. .
Since the first fourth gear 61 and the second fourth gear 62 are urged to each other, the first fourth gear 61 and the second fourth gear 62 rotate together in the CW direction (clockwise). Thereby, the whole fourth wheel 41 can be rotated in the CW direction.

The first fourth gear 61 and the second fourth gear 62 are urged by the first elastic arm portion 64 and the second elastic arm portion 74 in the direction in which the gap H1 becomes smaller. Unnecessary rotation (rattle) of the fourth wheel & pinion 41 in a gap set as backlash with the vehicle 41 can be suppressed.
In the example shown in FIG. 3, the tooth portion 40 b 1 of the fifth upper pinion 40 b is sandwiched between the tooth portion 61 a of the first fourth gear 61 and the tooth portion 62 a of the second fourth gear 62.
Note that the tooth portion 40b1 of the fifth upper kana 40b may not be sandwiched between the tooth portions 61a and 62a, and may be separated from the tooth portion 61a or the tooth portion 62a, for example.

In the process in which the fifth upper kana 40b and the fourth wheel 41 rotate while the tooth portion 40b1 of the fifth upper kana 40b enters the gap H1, the tooth portion 40b1 of the fifth upper kana 40b A force for expanding the gap H1 may be applied to at least one of the tooth portions 61a and 62a.
In the fourth wheel 41, the first fourth gear 61 and the second fourth gear 62 can be rotated independently, so that the clearance is resisted against the urging force of the first elastic arm portion 64 and the second elastic arm portion 74. It can rotate in the direction in which H1 spreads.
In the illustrated example, when a force in the CW direction (clockwise direction) is applied to the tooth portion 61a of the first fourth gear 61 by the tooth portion 40b1 of the fifth upper pinion 40b rotating in the CCW direction (counterclockwise direction), The second fourth gear 62 can rotate in the opposite direction (CCW direction) relative to the first fourth gear 61 (arrow F1 direction) while rotating in the CW direction as a whole.
Therefore, it is possible to reliably secure a gap H1 between the tooth portions 61a and 62a of the fourth wheel 41 so that the tooth portion 40b1 of the fifth upper pinion 40b can enter.

Thus, the fourth wheel 41 can mesh with the fifth wheel 40 while suppressing unnecessary rotation (rattle) in the gap set as backlash. Therefore, the second hand 14 can be advanced while reducing adverse effects such as a shift in operation caused by backlash.
Unlike the conventional product that uses a presser spring, the fourth wheel 41 does not need to be provided with a separate member outside the fourth wheel 41, so that space can be saved. Therefore, the timepiece 1 can be downsized. In addition, since a dedicated component as the separate member is unnecessary, the cost can be reduced.

The fourth wheel 41 has a small number of parts because the first elastic arm portion 64 is formed integrally with the first base 63. Therefore, the manufacturing can be facilitated and the manufacturing cost can be suppressed.
Further, in the fourth wheel 41, the first fourth gear 61 and the second fourth gear 62 are urged in directions opposite to each other. For example, the shape and pitch of the tooth portions 61a and 62a are reduced due to manufacturing reasons. Even when the distance between the fourth wheel 41 and the fifth wheel 40 fluctuates, an unnecessary rotation (rattle) in the gap set as the backlash can be suppressed. Therefore, a constant rotational force can be transmitted to the fifth wheel & pinion 40.

In the fourth wheel 41, the rotational load applied to the fourth wheel 41 can be reduced as compared with the conventional product using the pressing spring. Therefore, an increase in rotational torque for rotating the fourth wheel & pinion 41 can be suppressed, and the power consumption of the step motor 35 can be reduced.
Furthermore, since the fourth wheel 41 can suppress an increase in rotational torque, the tooth portion 40b1 of the fifth upper pinion 40b, the tooth portion 61a of the first fourth gear 61, and the tooth portion 62a of the second fourth gear 62 , The wear of the contact surface can be prevented and the durability can be enhanced. Therefore, the lifetime of the fifth wheel 40 and the fourth wheel 41 can be increased.

  In the fourth wheel 41, the first elastic arm portion 64 of the first fourth gear 61 not only biases the gears 61 and 62 in the opposite directions but also the second elastic arm portion 74 of the second fourth gear 62. Since the gears 61 and 62 are urged in the opposite directions, the urging force acting on the gears 61 and 62 can be increased. For this reason, it is possible to reliably reduce adverse effects such as displacement of operation caused by backlash.

The first fourth gear 61 is provided with a support shaft portion 65 that rotatably supports the second fourth gear 62.
According to this configuration, the first fourth gear 61 and the second fourth gear 62 can be easily assembled by inserting the support shaft portion 65 through the central hole 76 of the second fourth gear 62. Further, the axial alignment of the first fourth gear 61 and the second fourth gear 62 can be easily and accurately performed.

In the fourth wheel 41, the first elastic arm portion 64 is engaged with the first elastic arm portion 64 by the first locking convex portion 64 d of the first elastic arm portion 64 being locked in the second locking hole portion 78 of the second fourth gear 62. 2 is connected to the fourth gear 62. Therefore, the 1st elastic arm part 64 can be connected to the 2nd 4th gearwheel 62 by easy operation.
Similarly, when the second locking projection 74 d of the second elastic arm 74 is locked in the first locking hole 68 of the first fourth gear 61, the second elastic arm 74 is moved to the first fourth. Since it is connected to the gear 61, the second elastic arm portion 74 can be connected to the first fourth gear 61 by an easy operation.

  In the fourth wheel 41, the first elastic arm portion 64 is formed so as to extend into the internal space of the first long hole portion 67 of the first fourth gear 61, so that the first fourth gear 61 is formed thin. Can do. Further, since the second elastic arm portion 74 is formed so as to extend into the internal space of the second elongated hole portion 77 of the second fourth gear 62, the second fourth gear 62 can be formed thin. Therefore, the fourth wheel 41 can be reduced in thickness.

  Since the first elastic arm portion 64 and the second elastic arm portion 74 are shaped along the direction around the axis O1 (the circumferential direction of the first base 63), they are elastically bent and deformed so that the bending radius changes. By doing so, a large urging force can be applied to the first fourth gear 61 and the second fourth gear 62.

FIG. 11 is a diagram illustrating an example of a usage state of the gear body 81 having the same structure as the fourth wheel & pinion 41.
As shown in FIG. 11, the gear body 81 can be used in mesh with the gear 82. The gear 82 is a general-purpose gear having no structure such as an elastic arm. The gear 82 has the same number of teeth 82a as the number of teeth 61a, 62a.

FIG. 12 is a diagram illustrating another example of the usage state of the gear body 81.
As shown in FIG. 12, the gear body 81 can be used in mesh with a gear body 81 having the same structure.

[Second Embodiment]
(Gear body)
FIG. 13 is a plan view showing a gear body 91 according to the second embodiment of the present invention. FIG. 14 is an exploded perspective view showing the gear body 91.
As shown in FIGS. 13 and 14, the gear body 91 includes a first fourth gear 61 </ b> A and a second fourth gear 92.
In addition, about the structure similar to 1st Embodiment, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

The first fourth gear 61A has the same configuration as the first fourth gear 61 shown in FIGS. 6 and 7 except that the first locking hole 68 is not provided.
The second fourth gear 92 includes a second base body 93 having a plurality of tooth portions 92a formed on the entire outer periphery.
The second fourth gear 92 is rotatably attached to the first fourth gear 61A in a state where it overlaps the upper side of the first fourth gear 61A. Therefore, the second fourth gear 92 is rotatable around the axis O1 independently of the first fourth gear 61A.

The outer diameter of the second fourth gear 92 is preferably the same as the outer diameter of the first fourth gear 61A.
The number of teeth 92a of the second fourth gear 92 is preferably the same as the number of teeth 61a of the first fourth gear 61A. In the illustrated example, the number of teeth of the tooth portion 92a is 30. The pitch of the tooth portions 92a is preferably the same as the pitch of the tooth portions 61a.

A central hole 96 is formed in the second base 93 at a central position including the axis O1, and a second movement restricting hole 97 and a second locking hole 98 (on the other side) are located away from the axis O1. Locking receiving portion).
The central hole 96 is formed so as to penetrate in the thickness direction of the second base body 93, and the shape in plan view is, for example, a circle. The support shaft portion 65 of the first fourth gear 61A can be inserted through the center hole portion 96.

  The second movement restricting hole 97 is formed to penetrate in the thickness direction, and the shape in plan view is, for example, a circle. The inner diameter of the second movement restricting hole 97 is sufficiently larger than the outer diameter of the first movement restricting convex portion 69. As a result, the first movement restricting projection 69 inserted into the second movement restricting hole 97 can move in the second movement restricting hole 97 in the direction around the axis O1 (the circumferential direction of the second base body 93). Become.

The second locking hole 98 is a hole that the first locking projection 64d locks, and is formed so as to penetrate in the thickness direction. The shape in plan view is, for example, a circle. The second locking hole 98 is formed at a different position from the second movement restricting hole 97 in the circumferential direction of the second base body 93.
In the second locking hole 98, the first locking projection 64d of the first elastic arm 64 is inserted and locked. As a result, the first elastic arm portion 64 is connected to the second fourth gear 92.

In the gear body 91, the first fourth gear 61 </ b> A and the second fourth gear 92 are combined in a state where the first locking projection 64 d is inserted into the second locking hole 98. The first elastic arm portion 64 is elastically bent and deformed in a direction in which the bending radius decreases.
The first fourth gear 61 </ b> A and the second fourth gear 92 are urged in opposite directions by the elastic force of the first elastic arm portion 64.

The first movement restricting convex portion 69 of the first fourth gear 61 </ b> A is inserted into the second movement restricting hole 97 of the second fourth gear 92. In the first fourth gear 61 </ b> A, the movement in the urging direction by the first elastic arm portion 64 is restricted by the first movement restricting convex portion 69 being engaged with the peripheral edge portion 97 a of the second movement restricting hole portion 97. .
The relative rotational width of the first fourth gear 61A and the second fourth gear 92 is preferably at least half the pitch of the tooth portions 61a and 92a.

The support shaft portion 65 of the first fourth gear 61 </ b> A is inserted into the central hole portion 96 of the second fourth gear 92. The second fourth gear 92 is rotatably supported by the support shaft portion 65 with respect to the first fourth gear 61A.
The movement of the second fourth gear 92 in the direction away from the first fourth gear 61A (upward) is restricted by the locking claw portion 70b.

Since the first fourth gear 61A and the second fourth gear 92 are urged by the elastic force of the first elastic arm portion 64 in the direction in which the gap between the tooth portions 61a and 92a is reduced, the gear body 91 is It is possible to mesh with other gears while suppressing unnecessary rotation (rattle) in the gap set as rush. Therefore, it is possible to reduce adverse effects such as a shift in operation caused by backlash.
The gear body 91 can save space compared to a conventional product that uses a holding spring. Therefore, the timepiece 1 can be downsized. Moreover, since a separate member is unnecessary, cost reduction is possible.
The gear body 91 has a small number of parts because the first elastic arm portion 64 is formed integrally with the first base 63. Therefore, the manufacturing can be facilitated and the manufacturing cost can be suppressed.
In the gear body 91, since the first fourth gear 61A and the second fourth gear 92 are urged in opposite directions, the shapes and pitches of the tooth portions 61a and 92a are not uniform, Even when the distance fluctuates, unnecessary rotation (rattle) in the gap set as backlash can be suppressed. Therefore, a constant rotational force can be transmitted between the other gears.

Since the gear body 91 can reduce the rotational load, the power consumption of the step motor 35 can be reduced.
Furthermore, since the gear body 91 can suppress an increase in rotational torque, wear of the contact surface of the tooth portion can be prevented. Therefore, durability can be improved and lifetime can be extended.

[Third Embodiment]
(Gear body)
FIG. 15 is a plan view showing a gear body 101 according to the third embodiment of the present invention. FIG. 16 is an exploded perspective view showing the gear body 101.
As shown in FIGS. 15 and 16, the gear body 101 includes a first fourth gear 111 and a second fourth gear 112 that is rotatably attached to the first fourth gear 111. .
In addition, about the structure similar to 1st Embodiment or 2nd Embodiment, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

The first fourth gear 111 includes a first base 113 and a support shaft portion 65 that protrudes from the facing surface 113 a (upper surface) of the first base 113.
On the outer peripheral edge of the first base 113, a plurality of tooth portions 111a are formed over the entire circumference. The number of teeth 111a of the first fourth gear 111 is preferably the same as the number of teeth 62a of the second fourth gear 112. In the illustrated example, the number of teeth of the tooth portion 111a is 30. The facing surface 113a is a surface on the second fourth gear 112 side.
The outer diameter of the first fourth gear 111 is preferably the same as the outer diameter of the second fourth gear 112. The pitch of the tooth portions 111a is preferably the same as the pitch of the tooth portions 62a.

In the first base 113, a central hole 66 is formed at a central position including the axis O1, and a first locking hole 68 is formed at a position away from the axis O1. A first movement restricting convex portion 69 is formed on the facing surface 113 a of the first base 113.
The second fourth gear 112 has the same configuration as the second fourth gear 62 shown in FIGS. 8 and 9 except that the second locking hole 78 and the second movement restricting convex portion 79 are not provided.

As shown in FIG. 15, in the gear body 101, the first fourth gear 111 and the second fourth gear 112 are combined with the second locking projection 74d inserted into the first locking hole 68. Has been. The second elastic arm portion 74 is elastically bent and deformed in a direction in which the radius of curvature decreases.
The first fourth gear 111 and the second fourth gear 112 are urged in opposite directions by the elastic force of the second elastic arm portion 74.

The first movement restricting convex portion 69 of the first fourth gear 111 is inserted into the second long hole 77 of the second fourth gear 112. In the first fourth gear 111, the movement in the urging direction by the second elastic arm portion 74 is restricted by the first movement restricting convex portion 69 being engaged with the one end portion 77 a of the second elongated hole portion 77. In the illustrated example, the first movement restricting convex portion 69 is locked to the one end 77 a of the second elongated hole portion 77, thereby restricting the movement of the first fourth gear 111 in the counterclockwise direction.
The relative rotation width of the first fourth gear 111 and the second fourth gear 112 is preferably at least half the pitch of the tooth portions 111a and 62a.

In the gear body 101, the first fourth gear 111 and the second fourth gear 112 are urged in the direction in which the gap between the tooth portions 111a and 62a is reduced by the elastic force of the second elastic arm portion 74. It is possible to mesh with other gears while suppressing unnecessary rotation (rattle) due to the gap set as rush. Therefore, it is possible to reduce adverse effects such as a shift in operation caused by backlash.
The gear body 101 can save space compared to a conventional product that uses a holding spring. Therefore, the timepiece 1 can be downsized. Moreover, since a separate member is unnecessary, cost reduction is possible.
The gear body 101 has a small number of parts because the second elastic arm portion 74 is formed integrally with the second base 73. Therefore, the manufacturing can be facilitated and the manufacturing cost can be suppressed.
In the gear body 101, since the first fourth gear 111 and the second fourth gear 112 are biased in opposite directions, the shapes and pitches of the tooth portions 111a and 62a are not uniform, Even when the distance fluctuates, unnecessary rotation (rattle) in the gap set as backlash can be suppressed. Therefore, a constant rotational force can be transmitted between the other gears.

[Modification of Second Embodiment]
(Gear body)
FIG. 17 is a plan view showing a gear body 121 according to a modification of the second embodiment of the present invention. FIG. 18 is an exploded perspective view showing the gear body 121.
As shown in FIGS. 17 and 18, the gear body 121 includes a first fourth gear 61 </ b> A and a second fourth gear 122.
In addition, about the structure similar to 1st Embodiment, 2nd Embodiment, or 3rd Embodiment, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

The second fourth gear 122 has the same configuration as the second fourth gear 92 shown in FIGS. 13 and 14 except that the shape of the second movement restricting hole 127 in plan view is an oval.
The second movement restricting hole 127 includes, for example, a side peripheral edge 127a on the inner peripheral side, a side peripheral edge 127b on the outer peripheral side, and an end peripheral edge 127c on one end side of the side peripheral edges 127a and 127b in plan view, It is an oval formed of an end peripheral edge portion 127d on the other end side of the side peripheral edge portions 127a and 127b. The side peripheral edge portions 127a and 127b are, for example, arcs along the direction around the axis O1 (the circumferential direction of the second base body 93). The end peripheral portions 127c and 127d have, for example, a curved convex shape (for example, a semicircle).

  The first movement restricting convex portion 69 of the first fourth gear 61 </ b> A is inserted into the second movement restricting hole 127 of the second fourth gear 122. In the first fourth gear 61A, the movement of the first elastic arm portion 64 in the urging direction is restricted by the first movement restricting convex portion 69 being engaged with the end peripheral edge portion 127c of the second movement restricting hole portion 127. The

Since the first fourth gear 61A and the second fourth gear 122 are biased in the direction in which the gap between the tooth portions 61a and 92a is reduced by the elastic force of the first elastic arm portion 64, the gear body 121 is It is possible to mesh with other gears while suppressing unnecessary rotation (rattle) in the gap set as rush. Therefore, it is possible to reduce adverse effects such as a shift in operation caused by backlash.
Since the second movement restricting hole 127 of the second fourth gear 122 has an oval shape along the direction around the axis O1 (the circumferential direction of the second base body 93), the gear body 121 has the first fourth gear 61A and the first gear A large rotation width in the circumferential direction with the second gear 122 can be secured.

FIG. 19 is a configuration diagram showing a part of another example of a movement using a gear body having the same structure as that of the fourth wheel & pinion 41.
The structure shown in FIG. 19 is used to rotate the winding stem 24 that rotates based on the rotation of the crown (not shown), the first intermediate wheel 131 that rotates based on the rotation of the winding stem 24, and the first intermediate wheel 131. A second intermediate wheel 132 that rotates based on the rotation of the second intermediate wheel 132, a display gear 134 that rotates based on the rotation of the third intermediate wheel 133, and a display gear 134. The display wheel 135 that rotates based on the rotation of the display wheel 135 and the jump spring 136 that presses the side surface of the display wheel 135 are provided.
In this structure, a gear body having the same structure as the fourth wheel & pinion 41 is used as the second intermediate wheel 132.

According to this structure, in the second intermediate wheel 132, the first fourth gear 61 and the second fourth gear 62 are connected by the elastic force of the first elastic arm portion 64 and the second elastic arm portion 74 to the tooth portions 61a, It is urged in the direction in which the gap 62a becomes smaller. Therefore, it is possible to mesh with other gears (first intermediate wheel 131 and third intermediate wheel 133) while suppressing unnecessary rotation (rattle) in the gap set as backlash.
Therefore, the deviation between the operation of the winding stem 24 due to the rotation of the crown and the operation of the display means by the display wheel 135 can be reduced. Accordingly, it is possible to reduce adverse effects such as a shift in operation caused by backlash and improve operability.

FIG. 20 is a configuration diagram showing a part of still another example of a movement using a gear body having the same structure as that of the fourth wheel & pinion 41.
The structure shown in FIG. 20 is the same as the structure shown in FIG. 19 except that a third intermediate wheel 137 made of a gear body having the same structure as the fourth wheel 41 is used instead of the third intermediate wheel 133. It is.

According to this structure, since the second intermediate wheel 132 and the third intermediate wheel 137 use the same gear body as the fourth wheel 41, the first intermediate wheel 131 and the second intermediate wheel 132 In the meantime, between the second intermediate wheel 132 and the third intermediate wheel 137 and between the third intermediate wheel 137 and the display gear 134, adverse effects such as displacement of operation caused by backlash can be reduced. .
In a structure in which a large number of gears are arranged in series, the displacement of operation due to backlash tends to be large, but in the structure shown in FIG. 20, a gear body (second intermediate wheel) having the same structure as the fourth wheel 41 is used. By using a plurality of 132 and the third intermediate wheel 137), unnecessary rotation (rattle) between the gears can be suppressed, so that adverse effects of backlash can be reduced.

The technical scope of the present invention is not limited to the above embodiment, and various modifications can be made without departing from the spirit of the present invention.
The fourth wheel 41 shown in FIG. 4 and the like is composed of two gears (a first fourth gear 61 and a second fourth gear 62), but the gear body of the present invention may be composed of three or more gears. Good. In that case, at least two gears adjacent to each other in the axial direction among the three or more gears can be rotated around the axis center independently of each other. For example, the gear body of the present invention has a configuration in which a third gear is superimposed on the second fourth gear 62 in addition to the first fourth gear 61 and the second fourth gear 62 shown in FIG. May be. The number of gears constituting the gear body of the present invention may be an arbitrary number of 2 or more.

In the fourth wheel 41, a first elongated hole portion 67 (first hole portion) is formed in the first fourth gear 61, and the first elastic arm portion 64 extends into the internal space of the first elongated hole portion 67. However, the first fourth gear may not have the first elongated hole portion (first hole portion). In that case, the first elastic arm portion is formed to extend to the outside of the first fourth gear.
Further, in the fourth wheel 41, a second elongated hole portion 77 (second hole portion) is formed in the second fourth gear 62, and the second elastic arm portion 74 is formed in the internal space of the second elongated hole portion 77. Although formed so as to extend, the second fourth gear may not have the second long hole (second hole). In that case, the second elastic arm portion is formed to extend to the outside of the second fourth gear.

  In the fourth wheel 41, the first elongated hole portion 67 of the first fourth gear 61 is formed so as to penetrate the first base 63 in the thickness direction, but the first elongated hole portion (first hole portion). May be a groove formed on the surface of the first substrate. The second elongated hole 77 of the second fourth gear 62 is formed so as to penetrate the second base 73 in the thickness direction. The second elongated hole (second hole) is the surface of the second base. The groove part formed in this may be sufficient.

  In the fourth wheel & pinion 41, the first elastic arm portion 64 and the second elastic arm portion 74 are formed in an arc shape, but the shapes of the first elastic arm portion 64 and the second elastic arm portion 74 are not limited thereto. The shape of the first elastic arm portion and the second elastic arm portion may be, for example, a polygonal line shape combining a plurality of linear portions in plan view.

  In the fourth wheel 41, the first locking convex portion 64 d of the first elastic arm portion 64 is inserted and locked in the second locking hole portion 78 of the second fourth gear 62, but conversely, the first elasticity You may employ | adopt the structure which the latching convex part of a 2nd 4th gearwheel is inserted in the latching hole part formed in the arm part, and latches. Similarly, in the fourth wheel 41, the second locking convex portion 74d of the second elastic arm portion 74 is inserted and locked in the first locking hole portion 68 of the first fourth gear 61. You may employ | adopt the structure where the latching convex part of a 1st 4th gearwheel is inserted and latched in the latching hole part formed in the 2nd elastic arm part.

  In the fourth wheel 41, the first fourth gear 61 is provided on the support shaft portion 65, but the first fourth gear 61 may be configured without the support shaft portion 65. In this case, for example, the second fourth gear may be attachable to the axle 60.

  In the fourth wheel 41, the case where the gear body according to the present invention is applied to the fourth wheel 41 to which the second hand 14 is attached has been described as an example. However, the gear body according to the present invention meshes with the fourth wheel 41, for example. It may be applied to the third wheel. Even in this case, it is possible to reduce the adverse effects of backlash.

The gear body according to the present invention may be applied to a mechanical timepiece instead of the quartz type timepiece 1. In this case, for example, it can be suitably used for a gear to which a chronograph second in which hand movement unevenness is conspicuous is attached.
In the fourth wheel 41, the second fourth gear 62 is disposed on the upper side of the first fourth gear 61. However, the vertical relationship between the first fourth gear 61 and the second fourth gear 62 is opposite to the illustrated example. It may be.

DESCRIPTION OF SYMBOLS 1 ... Clock 10 ... Movement 23 ... Wheel train mechanism 41 ... Fourth wheel (gear body)
81, 91, 101, 121 ... gear body 61, 61A, 111 ... 1st fourth gear (first gear)
61a, 111a ... tooth portion of the first fourth gear 62, 92, 112, 122 ... second fourth gear (second gear)
62a, 92a ... tooth portion of the second fourth gear 64d first locking projection (first locking portion)
67 1st slot (1st hole)
78 Second locking hole (other side locking receiving portion)
O1 ... axis

Claims (9)

A plurality of coaxial gears,
Of the plurality of gears, at least two gears adjacent to each other in the axial direction are rotatable independently of each other in the circumferential direction around the axis,
One of the two gears includes a first base and a first elastic arm portion formed integrally with the first base,
The first elastic arm portion is connected to the other gear of the two gears, undergoes bending elastic deformation according to the circumferential position of the two gears, and the 2 according to the amount of bending elastic deformation. A gear body characterized in that two gears are biased in the circumferential direction opposite to each other. The other of the two gears has a second base and a second elastic arm portion formed integrally with the second base,
The second elastic arm portion is connected to the one gear, and undergoes bending elastic deformation according to the circumferential position of the two gears, and the two gears oppose each other according to the amount of bending elastic deformation. The gear body according to claim 1, wherein the gear body is biased in the circumferential direction.   The gear body according to claim 1 or 2, wherein a support shaft portion that rotatably supports the other gear in the circumferential direction is provided on the one gear. On the other gear, the other side latch receiving portion is formed,
The first elastic arm portion has a first engagement portion that is engaged with the other side engagement receiving portion by unevenness, and the first engagement portion is engaged with the other side engagement receiving portion. The gear body according to any one of claims 1 to 3, connected to the other gear. A first hole is formed in the first base,
The gear body according to any one of claims 1 to 4, wherein the first elastic arm portion is formed to extend into an internal space of the first hole portion.   The gear body according to any one of claims 1 to 5, wherein the first elastic arm portion is formed along the circumferential direction of the one gear.   A gear train mechanism comprising the gear body according to any one of claims 1 to 6.   A movement comprising the gear body according to any one of claims 1 to 6.   A timepiece comprising the movement according to claim 7.

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