JP2019060661A - Movement for timepieces and timepiece - Google Patents

Abstract

To provide a movement for timepieces and a timepiece with which it is possible to easily increase the magnitude of a spring force of an hour jumper.SOLUTION: The movement for timepieces comprises a scoop wheel 70, a reverse wheel for the day, a winding stem, and a time difference correction wheel row that rotates in linkage with the winding stem. The scoop wheel 70 comprises a barrel gear 71 that rotates in linkage with the reverse wheel for the day, an hour jumper 72 composed of a plurality of hour jumper bodies stacked one on another in the axial direction of the barrel gear 71, an hour jumper kana 73 that engages with the plurality of hour jumper bodies, and a scoop wheel body, provided with an hour needle, that rotates in linkage with the barrel gear 71 via the hour jumper 72 and the hour humper kana 73 and rotates in linkage with the time difference correction wheel row.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a watch movement and a watch.

Conventionally, for example, there is a timepiece provided with a time difference correction mechanism capable of correcting "time" indicated by the hour hand when correcting a time difference with movement between regions (see, for example, Patent Document 1).
In the watch of Patent Document 1, the hour wheel has a cylindrical gear (first gear portion) that rotates in conjunction with a sun wheel, a jumper kana (star wheel) when it rotates integrally with the cylindrical gear, and an hour jumper kana When engaged, it has a jumper and an hour hand attached, and it has a tubular body (cylinder) that rotates integrally with the jumper. With this configuration, the cylinder body rotates in conjunction with the cylinder gear. Further, the cylinder body rotates in conjunction with the time difference correction wheel train that rotates in conjunction with the winding stem.
In this watch, when rotating the time difference correction wheel train by operating the winding stem and rotating the cylinder body, the rotation of the cylinder gear is restricted by the minute wheel of the day, so when the jumper bends, the jumper kana and the hour The jumper is disengaged. For this reason, the cylinder body rotates with the cylindrical gear stopped, and the "hour" indicated by the hour hand can be corrected.

JP, 2016-57269, A

  By the way, in a timepiece provided with a date indicator, for example, there is a case where an instantaneous date feeding mechanism for instantaneously sending the date indicator is provided, and the instantaneous date feeding mechanism is driven by the cylinder body. In such a case, the torque required to drive the cylinder body increases. For this reason, when rotating the cylinder body in conjunction with the cylindrical gear, it is necessary to further increase the spring force of the hour jumper so that the engagement of the hour jumper kana and the hour jumper is not released.

  An object of the present invention is to provide a watch movement and watch that can easily increase the spring force of the jumper.

  The watch movement according to the present invention includes an hour wheel, a minute wheel, a winding stem, and a time difference correction wheel train that rotates in conjunction with the winding stem, and the hour wheel includes the hour wheel. When composed of a cylindrical gear that rotates in conjunction with a plurality of jumpers stacked in the axial direction of the cylindrical gear, a jumper, a jumper kana when engaged with the plurality of jumpers, and an hour hand It is characterized in that it comprises a cylinder car body attached and rotated in conjunction with the cylinder gear via the hour jumper and the hour jumper kana, and rotated in conjunction with the time difference correction wheel train.

According to the present invention, since the jumper is composed of a plurality of stacked jumpers, the spring force of the jumper is greater than when the jumper is configured of one jumper. it can.
Here, for example, even when the jumper is composed of one jumper body, the spring force may be increased by increasing the thickness dimension along the axial direction of the cylindrical gear in the one jumper body. it can. However, when the ratio of the thickness dimension to the width dimension of the jump portion of the jumper body increases, it may be difficult to form the jumper body in press working, and the jumper body may not be easily manufactured. On the other hand, according to the present invention, since it is not necessary to increase the thickness of the individual jumper body, it is possible to form the jumper body each time using pressing, and the jumper can be easily manufactured. .
Also, for example, the spring force can be increased by changing the shape of the one time jumper body as viewed in the axial direction of the cylindrical gear, but in this case, per unit area per hour when the jumper is used. The applied force increases and wear resistance decreases, and it is also necessary to redesign the jumper body. On the other hand, according to the present invention, since the force applied per unit area to the jumper jumper does not change, the wear resistance can be maintained, and the shape of the jumper body does not have to be changed each time, The time required to design the jumper can be shortened.

  In the watch movement of the present invention, preferably, the plurality of jumper bodies have the same shape and size as viewed in the axial direction, and the thickness dimensions along the axial direction are the same. .

  According to the present invention, since it is not necessary to manufacture a plurality of types of jumper bodies, management of manufacturing processes and parts can be simplified. In addition, each time the number of jumpers is increased, the spring force can be increased to twice, three times, four times, etc., the spring force when one jumper body is used, so that the spring force is adjusted. easy.

  In the watch movement of the present invention, it is preferable that the plurality of jumper bodies have at least one of a shape, a size, and a thickness dimension along the axial direction as viewed from the axial direction.

  According to the present invention, for example, since the spring force can be changed for each jumper body, when compared with the case where the shapes, sizes and thickness dimensions of the plurality of jumper bodies are the same as each other, The spring force can be finely adjusted. Also, for example, the mounting structure can be changed for each jumper body.

  In the watch movement of the present invention, the plurality of hour jumpers are fixed to the cylindrical gear and rotate integrally with the cylindrical gear, and the jumper kana is fixed to the cylindrical car body and integrated with the cylindrical car body. It is preferable to rotate at.

  The stop position of the cylinder body at the time of the time difference correction is determined by the teeth provided on the hour jumper kana. For this reason, when the jumper kana is fixed to the cylinder body and the cylinder body rotates integrally with the jumper kana, for example, when the jumper is fixed to the cylinder body and the jumper kana is fixed to the cylinder gear In comparison with the above, it is possible to suppress that the stop position of the cylinder body deviates. Thereby, it is possible to reduce the deviation of the indicated position of the hour hand at the time of time difference correction.

  In the watch movement of the present invention, the cylindrical gear has an annular shape surrounding the outer periphery of the jumper kana, protrudes in the axial direction from the inner peripheral edge, and has an arc portion having an arc shape seen from the axial direction. The plurality of hour jumpers each have a jumper body main portion when guided by the arc portion, and a jump control claw portion extending from the time jumper body main portion and engaged with the jumper kana It is preferable to have a jump control unit.

  According to the present invention, since the jumper body can be reliably aligned at each time by the arc portion, it is possible to suppress the fluctuation of the spring force when the position of the hour jumper body is shifted.

  In the watch movement of the present invention, it is preferable that a 24-hour hand be attached and a 24-hour hand wheel that rotates in conjunction with the cylindrical gear.

  According to the present invention, when the time difference correction wheel train is rotated by operating the winding stem, the engagement of the hour jumper and the hour jumper is released, and the cylinder body rotates with the cylinder gear stopped. For this reason, the "hour" indicated by the hour hand can be corrected without changing the "hour" indicated by the 24 hour hand attached to the 24-hour hand wheel linked to the cylindrical gear.

  A watch according to the present invention is characterized by comprising the watch movement and the hour hand.

  According to the watch movement, since the spring force can be easily increased, the types of mechanisms driven by the cylinder body can be increased. For this reason, according to the watch provided with the watch movement, it is possible to easily manufacture different types of watches.

The top view of the timepiece in the embodiment of the present invention. Sectional drawing of the movement of embodiment. Sectional drawing of the movement of embodiment. The elements on larger scale of FIG. The perspective view of the hour wheel (except cylinder body) of an embodiment. The top view of the movement of embodiment. The top view of the movement (except for a date wheel etc.) of embodiment. The perspective view which looked at the date sending part of embodiment from the surface side. The perspective view which looked at the date sending part of embodiment from the back side. The figure explaining the date sending operation of embodiment. The figure explaining the date sending operation of embodiment. The graph which shows the load torque of the cylinder body of embodiment. FIG. 7 is a diagram for explaining a date feeding operation of Modification 1 of the present invention. FIG. 7 is a diagram for explaining a date feeding operation of Modification 1 of the present invention.

Hereinafter, embodiments according to the present invention will be described based on the drawings.
[Clock configuration]
FIG. 1 is a plan view showing a timepiece 1 which is an electronic timepiece.
The timepiece 1 has a cylindrical outer case 11, and a disc-shaped dial 12 is disposed on the inner peripheral side of the outer case 11. Of the two openings of the exterior case 11, the opening on the watch front side (hereinafter simply referred to as the front side) is closed by the cover glass 14 through the annular bezel 13 and the back face of the watch The opening (hereinafter simply referred to as the back side) is closed by a back cover not shown. Here, the outer case 11 and the back cover constitute a case.

The timepiece 1 includes a movement 2 (see FIGS. 2 and 3) housed in a case, a second hand 21, a minute hand 22, an hour hand 23, a 24-hour hand 24, and a date wheel 25 as a calendar wheel.
The respective hands 21 to 24 are disposed on the front side of the dial 12, and the movement 2 is disposed on the rear side of the dial 12. The respective hands 21 to 24 are attached to coaxially provided axles 411, 421, 741, 451 (see FIG. 4) included in the movement 2 and driven by the movement 2.
In the timepiece 1, when the 24-hour hand 24 designates the 24-hour scale provided on the bezel 13, it is possible to display the time having a time difference different from the time displayed by the hour hand 23. For example, when in a foreign country, the hour hand 23 can indicate the time of the local time, and the 24-hour hand 24 can indicate the time of the Japanese time.

Further, the calendar small window 12A is provided on the dial 12, and the number of the date indicator 25 is visible from the calendar small window 12A. The number of the date wheel 25 represents the "day" of the date.
Further, a crown 15 attached to a winding stem 39 (see FIG. 6) included in the movement 2 is provided on the side surface of the exterior case 11 and operated when correcting the time and date.

[Structure of Movement]
2 and 3 are cross-sectional views of the movement 2, and FIG. 4 is a partially enlarged view of FIG.
As shown in FIG. 2 and FIG. 3, the movement 2 as a watch movement moves from the dial 12 to the back cover side, the calendar base plate 31, the base plate 32, the second support 33 (minute hand carriage), and the train wheel bridge It has 34.
In addition, a winding stem 39 on which the crown 15 is attached is incorporated in the movement 2. The winding stem 39 is configured to be able to draw two steps from the pushed-in position in the axial direction.
Furthermore, the movement 2 includes a wheel train mechanism 40 that displays hours, minutes, and seconds, a date shift mechanism 50 that displays a date, and a time difference correction mechanism 60 that corrects the time difference of the hour hand 23.

[Configuration of wheel train mechanism]
The wheel train mechanism 40 is a fifth wheel (not shown), a fourth wheel 41, a third wheel (not shown), a second wheel 42, a sun wheel, which rotates in conjunction with a rotor of a motor (not shown). 43, an hour wheel 70, and a 24 hour middle wheel 44, a 24 hour hour wheel 45 are provided.

[Fourth car configuration]
As shown in FIG. 4, the fourth wheel & pinion 41 (second hand wheel) includes an axle 411 (second hand shaft) to which the second hand 21 is attached, and a fourth gear 412 and a fourth kana 413 provided on the axle 411. . The fourth gear 412 meshes with the fifth wheel, and the fourth kana 413 meshes with the third wheel.
The end on the back cover side of the axle 411 is guided by a perforator 341 provided on the train wheel bridge 34.
The cover glass side end of the axle 411 is located closer to the cover glass than the dial 12. Further, the axle 411 is provided with a projecting portion 411 </ b> A that protrudes outward on the cover glass side of the dial 12.

Here, the second bearing 33 is provided with a second axle 331 (first guide portion). The secondary axle 331 is formed in a cylindrical shape, and is provided coaxially with the axis O1 of the axle 411. The cover glass side end of the secondary axle 331 is positioned closer to the cover glass than the dial 12, and constitutes a guide portion 331A that protrudes inward and outward. Further, on the rear cover side of the surface of the main plate 32, the second axle 331 is provided with a guide portion 331B that protrudes outward.
The axle 411 is inserted into the secondary axle 331, and the protrusion 411 </ b> A of the axle 411 is guided by the guide portion 331 </ b> A of the secondary axle 331. In this manner, the axle 411 is guided by the second axle 331.
The fourth gear 412 and the fourth pinion 413 are provided between the gear train 34 and the second bearing 33.

[Configuration of the second car]
The second wheel & pinion 42 (minute hand wheel) includes an axle 421 (minute hand shaft) to which the minute hand 22 is attached, and a second wheel 422 and a second kana 423 provided on the axle 421. The second gear 422 meshes with the third wheel and the second pinion 423 meshes with the sun wheel 43.
The axle 421 is formed in a cylindrical shape having a larger diameter than the axle 411, and is provided coaxially with the axis O1. The end on the back lid side of the axle 421 is located between the second bearing 33 and the base plate 32 in the axial direction, and the end on the cover glass side is located closer to the cover glass than the dial 12.
The axle 411 and the secondary axle 331 are inserted into the axle 421, and the guide portions 331A and 331B of the secondary axle 331 guide the inner circumferential surface of the axle 421. Thus, the axle 421 is guided by the secondary axle 331.
The second gear 422 and the second pinion 423 are provided between the second bearing 33 and the main plate 32.

[Configuration of an hour wheel]
FIG. 5 is a perspective view of the hour wheel 70 (hour hand wheel). In FIG. 5, the cylinder body 74 is not shown.
As shown in FIG. 4 and FIG. 5, the hour wheel 70 is provided on the surface side of the main plate 32, and includes the cylindrical gear 71, the hour jumper 72, the hour jumper kana 73, and the cylinder body 74 (first day intermediate wheel). Have.

As shown in FIG. 4, the cylinder body 74 is formed in a cylindrical shape having a larger diameter than the axle 421, and an axle 741 provided coaxially with the axis O1 and a cylinder body gear 742 integrally formed on the axle 741. And have.
As shown in FIGS. 4 and 5, the hour jumper kana 73 is formed in a cylindrical shape having a larger diameter than the axle 421 of the center wheel & pinion 42, and is provided coaxially with the axis O1. The hour jumper kana 73 is fitted on the back side of the cylinder body 74 and rotates integrally with the cylinder body 74. That is, the axle shaft 741 and the hour jumper kana 73 constitute a pointer shaft (hour hand shaft) of the hour wheel 70. Furthermore, twelve teeth 731 are provided on the outer peripheral surface of the hour jumper 73 along the outer periphery. The hour jumper kana 73 may also be referred to as a star wheel.

  The cylindrical gear 71 has an annular shape surrounding the outer periphery of the hour jumper kana 73, and the outer peripheral surface is provided with a tooth 711 meshing with the minute wheel 44 and the intermediate wheel 24 (see FIG. 3). . Further, the cylindrical gear 71 is provided with an arc portion 712 which protrudes from the inner peripheral edge to the surface side and has an arc shape as viewed from the surface side. The arc portion 712 surrounds the outer circumference of the hour jumper kana 73 by half or more.

The hour jumper 72 is provided on the surface side of the cylindrical gear 71. In this embodiment, to be described later in detail, in order to increase the torque of the hour jumper 72, the hour jumper 72 includes two hour jumpers 721 and 722 stacked in the axial direction. The jumpers 721 and 722 are formed by pressing.
The jumper body 721 is formed in an arc shape centering on the axis O1 when viewed from the front surface side, and guided by the arc portion 712 of the jumper kana 73 when the jumper body body portion 721A and the jumper body body portion 721A. And a jump control portion 721B having elasticity extending from an end in the circumferential direction. The jump control portion 721 B has a jump control claw portion 721 C engaged with the teeth 731 of the jumper jumper 73 at the tip, and can bend in the direction away from the jumper jumper 73.

The jumper body 722 has the same planar shape, size and thickness as the jumper body 721 and, like the jumper body 721, is guided by the arc portion 712 when the jumper body 722A, and the jumper kana 73 A jump control portion 722B provided with a jump control claw portion 722C engaged with the teeth 731 of FIG. And, when viewed from the front side, it is fixed at the same rotational position as the jumper body 721 and completely overlaps with the jumper body 721.
The hour jumper body portions 721A and 722A are fixed to the cylindrical gear 71 by two fixing pins 723 and the hour jumper 72 rotates integrally with the cylindrical gear 71. The fixing pin 723 may be formed integrally with the cylindrical gear 71.

Here, as shown in FIG. 4, the base plate 32 is provided with a central pipe 321 (second guide portion). The central pipe 321 is formed in a cylindrical shape and provided coaxially with the axis O1. In the central pipe 321, the axle 411 of the fourth wheel 41, the second axle 331, and the axle 421 of the second wheel 42 are inserted. The end by the side of the cover glass of central pipe 321 is located in the cover glass side rather than the back of date dial holder 35 mentioned below. Further, the end on the cover glass side of the central pipe 321 constitutes a guide portion 321A that protrudes outward. Further, the central pipe 321 is provided with a guiding portion 321B that protrudes outward on the back cover side of the guiding portion 321A.
The axle 411, the secondary axle 331, the axle 421, and the central pipe 321 are inserted into the axle 741 and the jumper jumper 73 of the cylinder body 74, and the guide portion 321A of the central pipe 321 guides the inner peripheral surface of the axle 741. The guide portion 321B of the central pipe 321 guides the inner peripheral surface of the jumper kana 73. Thus, the hour wheel 70 is guided by the central pipe 321.

In the hour wheel 70 having such a configuration, when the minute wheel 43 rotates in conjunction with the rotation of the rotor, the cylindrical gear 71 and the hour jumper 72 integrally rotate in conjunction with the minute wheel 43. At this time, since the jump restraint claws 721 C and 722 C press the jumper jumper 73, they engage with the teeth 731 of the jumper jumper 73, and the jumper jumper 73 rotates in conjunction with the jumper 72. The cylinder body 74 rotates integrally with the jumper jumper 73.
On the other hand, when the cylinder body 74 is rotated by the time difference correction mechanism 60 described later, the jumper jumper 73 rotates integrally with the cylinder body 74. At this time, since the rotation of the jumper 72 is restricted by the back wheel 43 of the day meshing with the cylindrical gear 71, the jump control parts 721B and 722B are pushed by the teeth 731 of the jumper jumper 73 and flexed, The engagement between the portions 721C and 722C and the teeth 731 is released. Thus, the cylinder body 74 can be rotated while the hour jumper 72 is stopped.

Here, as shown in FIG. 6, the movement 2 is provided with a date dial holder 35 that regulates the axial movement of the date dial 25. FIG. 6 is a plan view of the movement 2 as viewed from the front side.
As shown in FIG. 4, the date dial presser 35 is provided on the surface side of the cylinder body gear 742. The date indicator holder 35 includes a circular opening 351 centered on the axis O1, and a cylindrical portion 352 (third guide) which protrudes from the outer periphery of the opening 351 to the surface side. The cylindrical portion 352 is provided coaxially with the axis O1. In the cylindrical portion 352, an axle 411, a secondary axle 331, an axle 421, and an axle 741 are inserted. The tip of the cylindrical portion 352 is located closer to the cover glass than the back surface of the dial 12.
A ring-shaped needle seat 36 (hour hand seat) is provided between the cylinder body gear 742 and the date hand holder 35. The hour wheel 70 is biased by the main plate 32 by the needle 36.

  Further, in the present embodiment, a part of the guide portion 321A for guiding the cylinder body 74 in the central pipe 321 and the contact portion of the cylinder body gear 742 and the needle seat 36 are located on the same plane orthogonal to the axial direction. ing. As a result, while the inclination of the hour wheel 70 is suppressed, the hour wheel 70 can be biased by the needle seat 36.

[Composition of 24 hour train]
As shown in FIG. 4, the 24-hour hour wheel 45 (24-hour hand wheel) is formed in a cylindrical shape, and integrally formed with an axle 451 (24-hour hand shaft) coaxially provided with the axis O1 and the axle 451. And a 24-hour cylindrical gear 452. The 24-hour cylindrical gear 452 meshes with the 24-hour intermediate wheel 44 (see FIG. 3) and rotates in conjunction with the hour wheel 70. The 24-hour cylindrical gear 452 rotates 1⁄2 each time the hour wheel 70 rotates.

The axle 451 is provided on the cover glass side of the first cylindrical portion 451A formed to have a first diameter and the cover glass of the first cylindrical portion 451A, and is formed to have a second diameter smaller than the first diameter. And a second cylindrical portion 451B.
The axle 411 of the fourth wheel 41, the second axle 331, the axle 421 of the second wheel 42, the axle 741 of the cylinder body 74, and the tubular portion 352 of the date wheel retainer 35 are inserted into the first tubular portion 451A. A part (guide portion) of the cylindrical portion 352 guides the inner peripheral surface of the first cylindrical portion 451A. Thus, the axle 451 is guided by the tubular portion 352. The axle 411, the second axle 331, the axle 421, and the axle 741 are inserted into the second tubular portion 451B.

The 24-hour cylindrical gear 452 is provided between the date dial holder 35 and the dial 12.
And, between the 24 o'clock cylindrical gear 452 and the dial 12, there is provided a needle seat 37 (24 o'clock hand seat) formed in an annular shape. The 24-hour hour wheel 45 is biased by the date wheel holder 35 by the needle 37.

  Further, in the present embodiment, a part of the guide portion for guiding the 24-hour hour wheel 45 in the cylindrical portion 352 of the date dial holder 35 and the contact portion of the 24-hour cylindrical gear 452 and the needle seat 37 have an axial direction It is located on the same plane which intersects perpendicularly. As a result, the 24-hour hour wheel 45 can be biased by the needle seat 37 while suppressing the inclination of the 24 hour hour wheel 45.

[Configuration of date sending mechanism 50]
FIG. 7 is a plan view of the movement 2 with the date wheel holder 35, the date indicator guide plate, the date wheel 25 and the 24 hour hour wheel 45 removed from the front side.
As shown in FIG. 7, the date feeding mechanism 50 (calendar feeding mechanism) is provided on the surface side of the calendar base plate 31 (see FIG. 2), and includes a correction wheel 51, a second date turning intermediate wheel 52, and a date feeding unit 80. Is equipped.
The correction wheel 51 meshes with the cylinder body gear 742 of the cylinder body 74 and rotates in conjunction with the cylinder body 74. The second date intermediate wheel 52 meshes with the correction wheel 51 and rotates in conjunction with the correction wheel 51. The correction wheel 51 and the second date turning intermediate wheel 52 constitute an intermediate train wheel.

[Configuration of the date sending unit]
FIG. 8 is a perspective view of the date feeder 80 as viewed from the front side. FIG. 9 is a perspective view of the date feeder 80 as viewed from the back side.
As shown in FIGS. 2, 8 and 9, the date feeder 80 is rotatable relative to the support 85 provided on the calendar base 31, the axle 86 supported by the support 85, and the axle 86. A date turning gear 81 attached, a date turning claw 82 pivotally supported on an axle 86 and integrally rotating, a date turning cam 83, and a date turning lever 84 engaged with the date turning cam 83 are provided. The date feed lever 84 is pivotally supported by a pin 322 (see FIG. 7) provided on the main plate 32, and is positioned in the thickness direction by the calendar main plate 31.

The date rotation gear 81 as a calendar rotation gear meshes with the second date rotation intermediate wheel 52 and rotates in conjunction with the second date rotation intermediate wheel 52. The date gear 81 is provided with an arc-shaped opening 811 (see FIG. 10) centered on the axle 86.
In the present embodiment, when the correction wheel 51, the second date turning intermediate wheel 52, and the date turning gear 81 are driven in the forward rotation direction, a force is exerted in the direction in which the meshing separates, and when driven in the reverse direction. The force is arranged to work in the meshing direction.

The date feed claw 82 as a calendar feed claw is provided on the surface side of the date rotation gear 81, and is formed in a substantially disk shape. The date feed claw 82 is provided with a claw portion 821 projecting from the outer peripheral surface and an engagement hole 822.
Here, as shown in FIG. 6, 31 teeth 251 are formed on the inner peripheral side of the date wheel 25, and the date feed claw 82 rotates the teeth 251 by the claw portion 821 every rotation. Send one. As a result, the date wheel 25 rotates by one day, and the number of the date wheel 25 visually recognized from the calendar small window 12A is advanced by one.

  The date feed cam 83 as a calendar feed cam is provided on the back surface side of the date rotation gear 81, and is formed in a substantially fan shape centering on an axle 86. The date feeding cam 83 has a protrusion 831 on the surface side, and the protrusion 831 is inserted into the opening 811 of the date turning gear 81 and engaged with the engagement hole 822 of the date feeding claw 82.

  The date feed lever 84 as a calendar feed lever has elasticity, and has a pin 322 (see FIG. 7) provided on the main plate 32 as a rotation axis, and a tip 841 (see FIG. 9) of the date feed lever 84 has a side surface , And abut on the date feeding cam 83, and the side surface is provided with two projecting portions 842 and 843.

[Day advance operation]
FIG. 10 and FIG. 11 are transition diagrams for explaining the date feeding operation. FIG. 10 is a view from which the date feed claw 82 is removed.
Before the date is fed, as shown in the state 1 of FIGS. 10 and 11, the projecting portion 842 of the date lever 84 is in contact with the arc portion 832 of the outer circumferential surface of the date feeding cam 83. At this time, the claw portion 821 of the date feed claw 82 is not in contact with the teeth 251 of the date dial 25.
In this state, when the date rotation gear 81 rotates counterclockwise in conjunction with the second date rotation intermediate wheel 52, the projection 831 of the date passing cam 83 is formed on the inner surface of the opening 811 of the date rotation gear 81. As it is pushed, the date feed cam 83 rotates. As a result, when the arc portion 832 of the date feeding cam 83 pushes the projecting portion 842 of the date sending lever 84, the date sending lever 84 is gradually bent. Further, the date feed claw 82 also rotates counterclockwise integrally with the date feed cam 83. The date gear 81 causes the date lever 84 to bend in approximately one turn.

  When the date feeding cam 83 further rotates, as shown in the state 2 of FIGS. 10 and 11, the arc portion 832 of the date feeding cam 83 does not abut on the projecting portion 842 of the date sending lever 84. Due to the spring force of the lever 84, the projecting portion 842 of the date lever 84 pushes the radial portion 833 of the outer peripheral surface of the date cam 83, and the date cam 83 is vigorously pivoted counterclockwise. That is, the date feeding cam 83 rotates at a speed faster than the date turning gear 81. At this time, since the projection 831 of the date feeding cam 83 moves in the opening 811 of the date turning gear 81, the rotation of the date feeding cam 83 is not restricted by the date turning gear 81. In addition, the date feed claw 82 also pivots counterclockwise in unison with the date feed cam 83.

  Then, when the date feeding cam 83 rotates by a predetermined angle, as shown in the state 3 of FIGS. 10 and 11, the claw portion 821 hits the tooth 251 of the date dial 25 and the date dial 25 is pushed by the claw portion 821 One tooth rotates around, and one day to be visually recognized from the calendar small window 12A of the dial 12 is sent.

Furthermore, when the date feeding cam 83 is rotated, as shown in the state 4 of FIGS. 10 and 11, the projection 831 of the date feeding cam 83 abuts on the inner surface opposite to the opening 811 of the date turning gear 81 The rotation of the feed cam 83 is stopped. At this time, since the date feeding cam 83 abuts on the projecting portion 843 of the date feeding lever 84, the date feeding lever 84 also stops the rotation of the date feeding cam 83.
In addition, the date wheel 25 tries to rotate counterclockwise in a counterclockwise direction even after it is sent by the date feed claw 82 and stops contacting the claw portion 821 of the date feed claw 82. The teeth 251 adjacent to the teeth 251 in the clockwise direction of the teeth 251 sent by the claws 821 of the date feed claw 82 hit the claws 821, whereby it is possible to restrict the date wheel 25 to rotate more than one day.

  Thus, according to the date feeding unit 80, as shown in the state 2 to the state 4 of FIGS. 10 and 11, the date indicator 25 is rotated by rotating the date feeding cam 83 by the restoring force of the date sending lever 84. Can be turned instantly for one day. That is, the number of the date indicator 25 visually recognized from the calendar small window 12A is instantaneously changed. Therefore, the date sending mechanism 50 may be referred to as an instantaneous date sending mechanism. As a result, the user can reliably view the number of the date indicator 25 from the calendar small window 12A even at around 12 o'clock on the night when the date changes.

[Configuration of the time difference correction mechanism]
As shown in FIGS. 3 and 7, the time difference correction mechanism 60 includes a clutch wheel 62 (see FIG. 3) provided on the winding stem 39, and in the case where the winding stem 39 is pulled by one stage, A first correction intermediate wheel 63 (see FIG. 3) that rotates in conjunction with 62, a second correction intermediate wheel 64 that rotates in conjunction with the first correction middle wheel 63, and a rotation in conjunction with the second correction intermediate wheel 64 The correction car 51 is provided. The correction wheel 51 constitutes a part of the date shift mechanism 50 and a part of the time difference correction mechanism 60. That is, the clutch wheel 62, the first correction intermediate wheel 63, the second correction intermediate wheel 64, and the correction wheel 51 constitute a time difference correction wheel train that rotates in conjunction with the winding stem 39.

When the winding stem 39 is rotated by one step, the first correction intermediate wheel 63, the second correction intermediate wheel 64, and the correction wheel 51 are interlocked to rotate in conjunction with the clutch wheel 62. Thereby, the time when the cylinder body 74 rotates and the hour hand 23 displays is corrected.
At this time, although the jumper jumper 73 is rotated integrally with the cylinder body 74, as described above, the rotation of the jumper 72 is restricted by the rear wheel 43 of the day meshing with the cylinder gear 71. , 722B, and the engagement between the teeth 731 of the jumper jumper 73 and the jump control claws 721C, 722C is released. Thereby, the cylinder body 74 rotates in a state where the hour jumper 72 and the cylinder gear 71 are stopped. Therefore, among the times displayed by the second hand 21, the minute hand 22, and the hour hand 23, the 24 hour hand 24 can be corrected only when the hour hand 23 is displayed. In addition, since 12 teeth 731 are provided at equal intervals on the jumper jumper 73, the cylinder body is rotated each time the winding stem 39 is rotated to release the engagement between the teeth 731 and the jump control claws 721C and 722C. 74 can be rotated for one hour. That is, the time displayed by the hour hand 23 can be corrected one hour at a time.

[When the torque of the jumper]
In this embodiment, since it is necessary to bend the date turning lever 84 of the date turning mechanism 50 by the rotation of the cylinder body 74, compared to the case where a general date turning mechanism without the date turning lever 84 is provided, The torque required to rotate the cylinder body 74 is increased.
FIG. 12 is a graph showing the torque (load torque) required to rotate the cylinder body 74 according to the display time. A two-dot chain line P1 indicates the maximum value of load torque (forward rotation) by the date shift mechanism 50, and a solid line P2 indicates an average value of load torque (forward rotation) by the date shift mechanism 50. The alternate long and short dash line P3 indicates the maximum value of the load torque (reverse rotation) by the date shift mechanism 50, and the solid line P4 indicates the average value of the load torque (reverse rotation) by the date shift mechanism 50. The dotted line P5 shows the maximum value of the load torque (forward rotation) by the day jumper 87 (see FIG. 6, FIG. 7), and the solid line P6 shows the average value of the load torque (forward rotation) by the day jumper 87. The solid line P7 indicates the maximum value of the load torque (reverse rotation) by the day jumper 87, and the dotted line P8 indicates the average value of the load torque (reverse rotation) by the day jumper 87. An alternate long and short dash line P9 indicates the total value of the load torque. FIG. 12 shows a graph in the case where the hour jumper 72 is constituted by one hour jumper body. If the time jumper 72 is composed of two time jumper bodies, the torque is doubled.
As apparent from FIG. 12, in the present embodiment, the date passing mechanism 50 is configured such that the torque required for forward rotation is smaller than that for reverse rotation.

  Further, the dotted line P10 in FIG. 12 indicates the minimum value of the torque of the hour jumper 72, and the alternate long and short dash line P11 indicates the average value of the torque of the hour jumper 72. The torque of the hour jumper 72 needs to be larger than the load torque of the cylinder body 74 in order to rotate the cylinder body 74. That is, it is necessary to make the spring force of the hour jumper 72 larger than the load torque of the cylinder body 74. For this reason, in the present embodiment, as described above, the jumper 72 is composed of two jumper bodies 721 and 722 to increase the torque, and as indicated by the dotted line P10, the minimum value of the torque of the jumper 72 However, it is made to become larger than the load torque of the cylinder body 74 shown by each line P1-P9. In this embodiment, the thickness dimensions (dimensions in the direction along each pointer axis) of the hour jumper 72 are set to the fourth gear 412, the second gear 422, the cylindrical gear 71, the cylindrical body gear 742, and the date gear 81. It is set to 1.5 times (or twice) or more of the thickness dimension.

[Operation and effect of this embodiment]
In the watch 1, since the secondary axle 331 is provided between the axle 411 of the fourth wheel 41 and the axle 421 of the second wheel 42, contact between the axle 411 and the axle 421 can be suppressed. Rotation of the axle 421 can be suppressed. In addition, it is possible to suppress the rotation of the axle 421 through oil injected between the axles as the axle 411 rotates.
Further, in the timepiece 1, since the central pipe 321 is provided between the axle 421 and the axle 741 and the jumper jumper 73 of the cylinder body 74, contact between the axle 421 and the axle 741 and the jumper jumper 73 is required. It is possible to suppress the rotation of the axle 741 and the jumper jumper 73 when the axle 421 rotates. In addition, it is possible to suppress that the axle 741 and the hour jumper kana 73 rotate through the oil injected between the axles as the axle 421 rotates. Further, at the time of the time difference correction, it is possible to suppress the rotation of the axle 421 of the center wheel & pinion 42 and the axle 451 of the 24 hour hour wheel 45 along with the rotation of the axle 741 of the cylinder body 74.
Further, in the timepiece 1, since the cylindrical portion 352 of the date dial holder 35 is provided between the axle 741 and the axle 451 of the 24 hour hour wheel 45, contact between the axle 741 and the axle 451 can be suppressed. The rotation of the axle 451 can be suppressed as the axle 741 rotates. In addition, it is possible to suppress the rotation of the axle 451 through the oil injected between the axles as the axle 741 rotates.
As described above, according to the timepiece 1, it is possible to suppress that each pointer shaft is rotated with the rotation of another pointer shaft.

In the timepiece 1, the guide portion provided between the axle 741 of the cylinder body 74 and the axle 451 of the 24 hour hour wheel 45 is constituted by the cylindrical portion 352 which is a part of the date dial holder 35, so There is no need to separately provide the parts that constitute the guide part, and the number of parts can be reduced.
Moreover, since the said guide part is comprised by a part of date dial holder 35, the date dial holder 35 can be arrange | positioned in the position near the cylinder body 74, and the needle seat 36 is the cylinder body 74 and date dial holder. It can be provided between 35. According to this configuration, it is possible to restrict movement of the hour wheel 70 in the axial direction by the needle seat 36.
In addition, a part of the guide portion 321A for guiding the cylinder body 74 in the central pipe 321 and the contact portion of the cylinder body gear 742 and the needle seat 36 are located on the same plane orthogonal to the axial direction. The needle seat 36 can restrict movement of the hour wheel 70 in the axial direction while suppressing the vehicle 70 from tilting.

  In the timepiece 1, since the secondary axle 331 is provided on the secondary bearing 33, there is no need to separately provide a member for fixing the secondary axle 331. Further, since the central pipe 321 is provided on the base plate 32, there is no need to separately provide a member for fixing the central pipe 321. By these, the number of parts can be reduced.

  In the watch 1, since the axle 411 of the fourth wheel & pinion 41 is guided by the train wheel carrier 34 and the second axle 331 provided on the second bearing 33, the axle 411 is not inclined. Can guide you.

  In the timepiece 1, since the needle seat 37 is provided between the 24-hour cylinder gear 452 and the dial 12, the needle seat 37 can restrict movement of the 24-hour hour wheel 45 in the axial direction. Further, a part of the guiding portion for guiding the 24 hour hour wheel 45 in the cylindrical portion 352 of the date dial holder 35, and the contact portion of the 24 hour cylindrical gear 452 and the needle seat 37 are on the same plane orthogonal to the axial direction. Since the 24 hour cylinder 45 is prevented from being inclined, the needle seat 37 can restrict the movement of the 24 hour cylinder 45 in the axial direction.

In the watch 1, since the jumper 72 is composed of a plurality of jumper bodies 721 and 722, the torque of the jumper 72, ie, when the jumper 72 is composed of a single jumper body, ie , Can increase the spring force.
Here, for example, even if the hour jumper 72 is formed of one hour jumper body, the spring force can be increased by increasing the thickness dimension of the one hour jumper body. However, when the ratio of the thickness dimension to the width dimension of the jump portion of the jumper body increases, it may be difficult to form the jumper body by press processing, and the jumper body may not be easily manufactured. On the other hand, according to the watch 1, since it is not necessary to increase the thickness dimensions of the individual jumpers 721 and 722, the jumpers 721 and 722 can be formed each time using pressing. The jumper 72 can be easily manufactured.
Also, for example, the spring force can be increased by changing the planar shape of the one jumper body, but in this case, the force applied per unit area to the jumper jumper 73 is increased. Wear resistance is reduced, and it is necessary to redesign the jumper body when. On the other hand, according to the watch 1, since the force applied per unit area to the jumper jumper 73 does not change, the wear resistance can be maintained, and it is necessary to change the shape of the jumpers 721 and 722 each time The time required to design the jumper 72 can be reduced because there is no
As described above, according to the timepiece 1, since the torque of the jumper 72 can be easily increased, the types of mechanisms driven by the cylinder body 74 can be increased, and different types of timepieces can be easily manufactured.

  In the timepiece 1, the hour jumpers 721 and 722 have the same planar shape, size, and thickness. Therefore, it is not necessary to manufacture a plurality of types of jumper bodies, and the management of manufacturing processes and parts can be simplified.

  The stop position of the cylinder body 74 at the time of the time difference correction is determined by the teeth 731 provided on the hour jumper kana 73. For this reason, when the jumper kana 73 is fixed to the cylinder body 74 and the cylinder body 74 integrally rotates with the jumper kana 73, for example, the hour jumper 72 is fixed to the cylinder body 74 and As compared with the case where the kana 73 is fixed, the stop position of the cylinder body 74 can be suppressed from shifting. Thereby, the deviation of the designated position of the hour hand 23 at the time of time difference correction can be reduced.

  In the timepiece 1, the hour jumpers 721 and 722 are guided by the circular arc portion 712 provided on the cylindrical gear 71, respectively. The position of the jumpers 721 and 722 can be offset, and fluctuations in the torque of the jumper 72 can be suppressed.

  According to the timepiece 1, when the winding stem 39 is operated to rotate the time difference correction wheel train, the engagement of the hour jumper 72 and the hour jumper kana 73 is released, and the cylinder body 74 is in a state where the cylinder gear 71 is stopped. Rotate. For this reason, the "hour" indicated by the hour hand 23 can be corrected without changing the "hour" indicated by the 24-hour hand 24 attached to the 24-hour hour wheel 45 interlocked with the cylinder gear 71.

According to the timepiece 1, the date rotation gear 81 rotates in conjunction with the cylinder body 74, the date rotation cam 83 rotates in linkage with the date rotation gear 81, and the date rotation lever 84 gradually bends. Then, when the date feeding cam 83 turns to a predetermined position, the date feeding cam 83 vigorously turns by the spring force of the bent date sending lever 84 and turns integrally with the date feeding cam 83. The nail 82 sends the date wheel 25. As a result, it is possible to send the day instantaneously in the timepiece 1 provided with the time difference correction function.
Further, according to the timepiece 1, since the date rotation gear 81 rotates in conjunction with the cylinder body 74, the hour hand 23 is operated by rotating the time difference correction wheel train by operating the winding stem 39 and rotating the cylinder body 74. Not only the "time" instructed by the can be corrected simultaneously, but the convenience can be improved as compared with the case where the "time" correction and the day correction are separately performed.

In the timepiece 1, the thickness dimension of the hour jumper 72 is, for example, larger than the thickness dimension of the cylindrical gear 71 (in the embodiment, 1.5 to 2 times). According to this configuration, when compared with the case where the thickness dimension of the jumper 72 is the same as the thickness dimension of the cylindrical gear 71, for example, the jumper 72 bends in the direction orthogonal to the bending direction (direction along the rotation axis of the hour wheel 70). Can be controlled. That is, it can be suppressed that the jumper 72 is twisted. As a result, the spring force in the bending direction of the jumper 72 can be stabilized, and the torque of the jumper 72 can be stabilized.
In addition, by making the thickness dimension of the jumper 72 larger than the thickness dimension of the cylindrical gear 71, the dimension of the portion where the jumper 72 and the jumper jumper 73 engage (along the axial direction of the jumper jumper 73) The dimension can be made larger than half of the combined thickness dimension of the cylindrical gear 71 and the hour jumper 72. Thereby, compared with the case where the thickness dimensions of the hour jumper 72 and the cylindrical gear 71 are the same, it is possible to suppress the tilting of the hour jumper 72 and the cylindrical gear 71 at the time difference correction or the like.

  In the watch 1, the date rotation gear 81 rotates in conjunction with the cylinder body 74 via the intermediate train (the correction wheel 51 and the second date rotation intermediate wheel 52). According to this configuration, as compared with the case where the cylinder body 74 and the date gear 81 are directly meshed, there are more meshing points of the gear, so when the force by the impact is applied to the movement 2, the force can be easily released . Thereby, it can suppress that the position of the cylinder body 74 or the date gear 81 shifts | deviates by the said force. In addition, it is possible to adjust the rotation direction of the date gear 81 relative to the rotation direction of the cylinder body 74 and the position of the date gear 81 relative to the cylinder body 74.

  In the timepiece 1, the correction wheel 51 is used for the time difference correction wheel train and also for the middle train wheel of the date feeding mechanism 50. That is, one gear of the time difference correction wheel train and one gear of the intermediate train wheel are common gears. According to this, the number of gears can be reduced and the number of parts can be reduced, as compared with the case where the gears of the middle train wheel and the gears of the time difference correction train wheel are separately provided. Note that the number of gears in common may be two or more.

In the timepiece 1, the hour wheel 70 is provided on the surface side of the main plate 32, and the correction wheel 51, the second date turning intermediate wheel 52, and the date feeding unit 80 are provided on the surface side of the calendar ground plate 31. That is, the axial position of the hour wheel 70 is determined by the base plate 32, and the axial position of the correction wheel 51, the second date intermediate wheel 52, and the date feeding unit 80 is determined by the calendar base plate 31.
According to this configuration, as compared with the case where the correction wheel 51, the second date turning intermediate wheel 52, and the date feeding unit 80 are provided on the surface side of the main plate 32 similarly to the hour wheel 70, the correction wheel 51, the second date turning Positioning in the axial direction of the intermediate wheel 52 and the date feeding unit 80 is facilitated, and variations in the axial position can be suppressed.
In addition, since the correction wheel 51, the second date turning intermediate wheel 52, and the date turning gear 81 can be positioned on substantially the same plane, each car can be driven even if a force is applied to it during the time difference correction. It can control tilting. For this reason, by increasing the torque of the jumper 72, the force required to rotate the cylinder body 74 at the time of the time difference correction becomes large, and the time difference correction can be appropriately performed even if the force applied to each vehicle becomes large. Can.

[Other embodiments]
Note that the present invention is not limited to the above-described embodiment, and modifications, improvements, and the like as long as the object of the present invention can be achieved are included in the present invention.

[Modification 1]
In the said embodiment, although the date sending mechanism 50 is rotating the date indicator 25, it is not limited to this. For example, if the watch 1 is equipped with a day wheel, the day wheel may also be rotated by the date shift mechanism. FIG. 13 and FIG. 14 are transition diagrams for explaining the date shift operation in this case. FIG. 14 is a diagram excluding the date feed claw 82.
As shown in the state 1 of FIG. 14, in the date feeding mechanism 50A of this modification, the date feeding claw 82A is used in addition to the claw portion 821 to send two teeth 261 of the teeth 261 of the hour gear 26 provided on the drive. The units 823 and 824 are provided. The tooth gear 26 is provided with fourteen teeth 261. That is, when the day gear 26 is fed by two teeth, the day is fed by one day.

Just before the day of the week is fed, the date feed cam 83 rotates counterclockwise in conjunction with the date rotation gear 81 similarly to the embodiment, and the arc portion 832 of the date feed cam 83 is a protrusion of the date feed lever 84 By pushing 842, the date advance lever 84 is gradually bent.
Furthermore, when the date feeding cam 83 is rotated, as shown in the state 1 of FIGS. 13 and 14, the arc portion 832 of the date feeding cam 83 does not contact the projection 842 of the date sending lever 84. By the restoring force of the feed lever 84, the projecting portion 842 of the date feed lever 84 pushes the radial portion 833 of the outer circumferential surface of the date feed cam 83, and the date feed cam 83 is vigorously pivoted counterclockwise. At this time, since the projection 831 of the date feeding cam 83 moves in the opening 811 of the date turning gear 81, the rotation of the date feeding cam 83 is not restricted by the date turning gear 81. In addition, the date feed claw 82 also pivots counterclockwise in unison with the date feed cam 83.

Then, when the date feeding cam 83 rotates by a predetermined angle, as shown in the state 2 of FIGS. 13 and 14, the claw portion 823 contacts the tooth 261 of the drive gear 26 and the drive gear 26 is pushed by the claw portion 823. Rotate one tooth clockwise.
Furthermore, when the date feed claw 82A rotates, as shown in state 3 of FIGS. 13 and 14, the claw portion 821 hits the tooth 251 of the date dial 25, and the date dial 25 is pushed by the claw portion 821 to rotate counterclockwise. Rotate one tooth (for one day) to
Further, when the date feed claw 82A is rotated, as shown in state 4 of FIGS. 13 and 14, the claw portion 824 abuts the tooth 261 of the drive gear 26, and the drive gear 26 is pushed by the claw portion 824 to rotate clockwise. And rotate one more tooth. As a result, a day drive is sent for one day.
Further, when the date feed claw 82A is rotated, the projection 831 of the date feed cam 83 abuts against the inner surface on the opposite side of the opening 811 of the date rotation gear 81 as shown in state 5 of FIGS. The rotation of the feed cam 83 is stopped. At this time, since the date feeding cam 83 abuts on the projecting portion 843 of the date feeding lever 84, the date feeding lever 84 also stops the rotation of the date feeding cam 83.
Thus, according to the date feeding mechanism 50A, as shown in the state 2 to the state 4 of FIGS. 13 and 14, the date dial 25 is rotated by rotating the date feeding cam 83 by the spring force of the date feeding lever 84. And you can rotate the drive wheel instantly for one day.
In the first modification, the date feeding mechanism is an example of rotating the date indicator 25 and the day wheel, but the date feeding mechanism may be configured to rotate only the day wheel.

[Modification 2]
In the embodiment, the guide portion provided between the axle 741 of the cylinder body 74 and the axle 451 of the 24 hour hour wheel 45 is constituted by the cylindrical portion 352 which is a part of the date dial holder 35, It is not limited to this.
For example, it may be configured by a part of a date indicator guide plate that guides the date indicator 25. Or you may comprise by components provided separately, such as a center pipe.

[Modification 3]
In the said embodiment, although the center axle 331 is provided in the center bearing 33 and the center pipe 321 is provided in the ground plate 32, it is not limited to this.
That is, the center axle 331 and the center pipe 321 may be provided on the support plate provided in the movement 2.

[Modification 4]
In the said embodiment, although the time jumper 72 is comprised by two time jumper body 721, 722, it is not limited to this.
That is, depending on the torque required to rotate the cylinder body 74, three or more hour jumpers may be used. Here, when the planar shape, size, and thickness dimensions of the respective jumpers constituting the jumper 72 are made the same, when the number of the jumpers is increased, the torque of the jumper 72 is 1 when the jumper is 1 The torque can be increased by two times, three times, four times ... in one case, and the torque of the jumper 72 can be easily adjusted.
Also, the hour jumper 72 may be configured as a single time jumper body whose thickness dimension is increased. If the ratio of the width dimension to the thickness dimension of the jump portion of the jumper body is in the range of 0.2 to 0.5, the jumper body can be manufactured by processing such as laser cutting or wire cutting.

In addition, the plurality of hour jumpers constituting the hour jumper 72 may be different from each other in planar shape, size, or thickness dimension.
For example, by changing at least one of the planar shape, the size, and the thickness dimension of the jump portion for each jumper body, it is possible to change the torque for each jumper body. For this reason, the torque of the hour jumper 72 can be finely adjusted as compared with the case where the planar shape, size and thickness of the jump portion are the same.
Also, for example, the mounting structure (fixed structure) for the cylindrical gear 71 is set for each of the jumper bodies by changing at least one of the planar shape, size, and thickness dimensions of the body of the jumper body for each jumper body. it can.

[Modification 5]
In the embodiment described above, the jumpers 721 and 722 are fixed at the same rotational position when viewed from the front side when the hour jumper 72 is configured, but the present invention is not limited thereto.
That is, the hour jumpers 721 and 722 may be fixed at different rotational positions. That is, the jump restraint claws 721 C and 722 C may engage with the different teeth 731 of the hour jumper can 73. For example, the hour jumpers 721 and 722 may be fixed at a rotational position shifted by 180 degrees. In this case, the center of gravity of the hour jumper 72 can be overlapped with the rotation center of the cylindrical gear 71, and the cylindrical gear 71 can be prevented from tilting. Further, in the hour jumper kana 73, the portions pressed by the jump control claws 721C and 722C can be dispersed in the circumferential direction. In addition, since the spring force of the jump control claw portion 721C and the spring force of the jump control claw portion 722C work to cancel each other, the inclination of the cylindrical gear 71 can be suppressed.

[Modification 6]
In the embodiment, although the cylinder body 74 and the hour jumper kana 73 are fixed and the cylinder gear 71 and the hour jumper 72 are fixed, the present invention is not limited to this.
For example, the cylinder body 74 and the hour jumper 72 may be fixed, and the cylinder gear 71 and the hour jumper kana 73 may be fixed.
However, in this case, since it is necessary to match the size of the cylinder body 74 to the size of the hour jumper 72, the size of the cylinder body 74 is increased. In this case, it is necessary to increase the size of the date gear 81 whose speed reduction ratio is determined to be 1/2 with respect to the cylinder body 74, and the size of the movement 2 is increased.
Further, the cylinder body 74 is preferably formed of non-metal in view of the attachment of the hour hand 23. For this reason, when fixing the cylinder body 74 and the hour jumper 72, welding can not be used.
Further, since the cylinder body 74 and the jumper kana 73 are not fixed when determining the stop position of the cylinder body 74 at the time of the time difference correction, the stop position of the cylinder body 74 at the time of the time difference correction may be shifted.
From the above reasons, as in the embodiment, it is preferable that the cylinder body 74 and the hour jumper kana 73 be fixed and the cylinder gear 71 and the hour jumper 72 be fixed.

[Modification 7]
In the above embodiment, the second date turning intermediate wheel 52 rotates in conjunction with the cylinder body gear 742 of the cylinder body 74 via the correction wheel 51 which is a part of the time difference correction wheel train, but is not limited to this. . For example, the cylindrical body gear 742 may be configured to rotate in conjunction with the cylindrical body gear 742 via a separately provided gear.

[Modification 8]
In the embodiment, the date gear 81 rotates in conjunction with the cylindrical body gear 742 via the intermediate gear train (the correction wheel 51 and the second date rotation intermediate wheel 52), but is not limited thereto. For example, the date gear 81 may be directly meshed with the cylindrical body gear 742. In this configuration, it is possible to reduce the torque required to rotate the date gear 81.

[Modification 9]
Although the said embodiment is an example which applied this invention to the electronic timepiece, this invention is applicable also to a mechanical timepiece.

  DESCRIPTION OF SYMBOLS 1 ... clock 2 ... movement (movement for watch) 12 ... dial plate, 21 ... second hand, 22 ... minute hand, 23 ... hour hand, 24 ... 24 hour hand, 25 ... sun wheel, 26 ... day gear, 31 ... calendar base plate, 32: ground plate, 33: second bearing (minute hand wheel bearing) 34: train wheel bearing, 35: sun wheel holder, 36: hand seat (hour hand seat), 37: hand seat (24 o'clock hand seat), 39: winding true , 40 ... wheel train mechanism, 41 ... fourth wheel (second hand car), 42 ... second wheel (minute hand car), 43 ... day rear wheel, 44 ... 24 o'clock middle car, 45 ... 24 hour hour wheel, 50, 50A ... date feeding mechanism (calendar feeding mechanism), 51 ... correction car, 52 ... second day turning middle car, 60 ... time difference correction mechanism, 62 ... spelling car, 63 ... first correction middle car, 64 ... second correction Intermediate car, 70: In-cylinder wheel (hour hand wheel), 71: Cylindrical gear, 72: At jumper, 73: At jumper jumper, 74: Tube Body, 80: date feeding part, 81: date turning gear (calendar turning gear), 82, 82 A: date feeding claw (calendar feeding claw), 83: date feeding cam (calender feeding cam), 84: date feeding lever (calender Feed levers, 85, supporting portions, 86, axles, 87, sun jumpers, 251, teeth, 261, teeth, 321, central pipes (second guiding portions), 321A, 321B, 331A, 331B, guiding portions, 322, ... Pin, 331: Secondary axle (first guide), 341: Hole stone, 351: Opening, 352: Tubular part (third guide), 411: Axle (second hand shaft), 411A: Projection, 412 ... 4th gear, 413 ... 4th kana, 421 ... axle (minute hand shaft), 422 ... 2nd gear, 423 ... second kana, 451 ... axle (24h hand shaft), 451A ... 1st cylindrical portion, 451B ... Second cylindrical portion, 452 24 o'clock cylindrical gear 711: tooth: 712: fitting portion: 721, 722: hour jumper body, 721A, 722A: hour jumper body main portion, 721B, 722B: jump control portion, 721C, 722C: jump control claw portion, 723: Fixing pin, 731: Tooth, 741: Axle (part of hour hand shaft), 742: Cylindrical body gear, 811: Opening, 821, 823, 824: Claw, 822: Engagement hole, 831: Protrusion , 832 ... arc part, 833 ... radius part, 841 ... tip part, 842 ... projection part, 843 ... projection part, O1 ... axis line.

Claims (7)

With an hour wheel,
The day behind the car,
Maki and
And a time difference correction wheel train that rotates in conjunction with the winding stem,
The hour wheel is
A cylindrical gear that rotates in conjunction with the sun wheel of the day;
A jumper formed of a plurality of jumper bodies stacked in the axial direction of the cylindrical gear;
Jumper kana when engaged with the plurality of jumper bodies;
An hour hand is attached, and it comprises: a cylinder car body which rotates in conjunction with the cylinder gear via the hour jumper and the time jumper kana, and which rotates in conjunction with the time difference correction wheel train. Watch movement. In the watch movement according to claim 1,
When viewed from the axial direction, the plurality of jumper bodies have the same shape and size as each other, and the thickness dimensions along the axial direction are the same. In the watch movement according to claim 1,
The timepiece movement characterized in that at least one of a shape, a size, and a thickness dimension along the axial direction of the plurality of jumper bodies when viewed from the axial direction are different from each other. The watch movement according to any one of claims 1 to 3.
The plurality of jumper bodies are fixed to the cylindrical gear and rotate integrally with the cylindrical gear,
The watch jumper is fixed to the tubular body and rotates integrally with the tubular body. In the watch movement according to claim 4,
The cylindrical gear is
At the time of the above, it has an annular shape surrounding the outer periphery of the jumper kana
It has an arc part which protrudes from the inner peripheral edge in the axial direction and has an arc shape seen from the axial direction,
The plurality of jumpers are respectively
A jumper body body portion when guided by the arc portion;
A movement for watch, comprising: a jump control portion having a jump control claw portion extended from the jumper body main portion and engaged with the jumper jumper. The watch movement according to any one of claims 1 to 5.
A watch movement characterized by comprising a 24-hour hand wheel attached with a 24-hour hand and rotating in conjunction with the cylindrical gear. A watch movement according to any one of the preceding claims.
A timepiece comprising: the hour hand.

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