Gear mechanism, movement and timepiece.

专利摘要:
According to the invention, the power reserve of a mainspring of a barrel can be improved or the output torque can be increased. A gear mechanism (12) is provided which includes: a plurality of barrels (20) including a barrel in which a mainspring is housed, and which are rotatable about axes O1 and O2 under the action of unwinding of the mainspring , and a ratchet wheel (45) which is rotatable about the axes relative to the barrel during the unwinding of the mainspring; and a finishing gear (15) which is arranged on the front side of the plate (11) and which is driven in rotation under the action of the unwinding of the mainspring. The barrels are arranged away from each other when viewed in a direction perpendicular to the plane of the plate, and in a state of mutual engagement. Each of the plurality of barrels is spaced apart from the finishing gear in the plane of the stage, preventing the barrels and the finishing gear from overlapping.
公开号:CH717086A2
申请号:CH00076/21
申请日:2021-01-28
公开日:2021-07-30
发明作者:Fujieda Hisashi
申请人:Seiko Watch Kk Trading As Seiko Watch Corporation；
IPC主号:

专利说明:

BACKGROUND OF THE INVENTION
1. Field of the invention
The present invention relates to a cog mechanism, a movement and a timepiece.
2. Description of the prior art
[0002] In a movement in a mechanical timepiece, generally, a rotational driving force is transmitted to various types of gear train such as a finishing gear via the rotation of a barrel under the pulse of an energy (output torque) resulting from the unwinding of a mainspring.
[0003] For example, document JP-A-2004-170271 (D1) discloses a movement comprising at least one barrel, a second mobile, a third mobile, a fourth mobile and a center mobile. The second mobile includes a second pinion and a second gear wheel, and the second pinion meshes with the barrel. The third mobile includes a third pinion and a third gear wheel, and the third gear meshes with the second gear wheel. The fourth mobile includes a fourth pinion and a fourth gear wheel, and the fourth gear meshes with the third gear wheel. The center gear includes a center gear wheel and the center gear wheel meshes with the third gear wheel.
[0004] Therefore, in the movement described above, a force of rotation of the barrel can be transmitted to the fourth mobile and the center mobile via the second mobile and the third mobile respectively, the fourth mobile can be rotated one times every 60 seconds and the center rover can be rotated once every 60 minutes. The movement has a structure called the structure of the direct drive of the central second hand in which the fourth mobile is arranged at the center of the movement with the center mobile and a seconds hand is attached to the fourth mobile. The second mobile and the third mobile gear are arranged at positions offset from the center of the movement in a direction taken in the plane of the movement.
[0005] Furthermore, in the movement in the mechanical timepiece in the prior art, in many cases, at least one wheel constituting the cog is arranged in a gear plane overlapping the barrel (that is, that is, overlapping in the direction of the thickness of the movement) in a plan view of the movement. Therefore, it is necessary to take such measures as reducing the outer diameter of a ratchet wheel in order to free the ratchet wheel in the gear plane, or else to reduce the thickness of the barrel itself.
[0006] In particular, when two or more mobiles constituting the gear train, such as the second mobile and the third mobile in the movement described in D1, overlap the barrel in a plane, the thickness of the barrel itself must be reduced.
[0007] However, when the outer diameter of the ratchet wheel is limited, it is difficult to increase a speed reduction ratio or a speed increase ratio for various types of gear train (e.g. , finishing cogs and automatic winding gears) which mesh with the ratchet wheel, resulting in design restrictions such as an increase in the number of mobiles.
When the thickness of the barrel is reduced, the width of the mainspring housed in the barrel is reduced accordingly. Thus, it is necessary to increase the thickness of the mainspring by this same amount, which limits the mainspring which can be used; for example, the number of turns is reduced.
[0009] Consequently, when an output torque of the mainspring is kept constant during the unwinding, the inconvenience is caused by the fact that the power reserve (that is to say the time to return to a natural length of the spring from its armed state, that is to say coiled, following complete unwinding) of the mainspring is reduced. On the contrary, when this duration associated with the power reserve is kept constant, the inconvenience is caused by the fact that the output torque itself becomes smaller.
As described above, when the thickness of the barrel is reduced, the inconvenience is caused by the fact that the duration is reduced or that the output torque itself is reduced.
In order to avoid the planar overlap between at least one wheel constituting the gear train and the barrel, it is conceivable to reduce, for example, the outer diameter of the barrel. However, even in this case, since the outer diameter of the barrel itself is reduced and the mainspring becomes shorter or thinner as a result, the inconvenience is caused by whether the duration is reduced or the output torque itself. same is reduced as in the aforementioned case.
SUMMARY OF THE INVENTION
An object of the present invention is to provide a gear mechanism, a movement and a timepiece which are capable of improving the power reserve provided by the mainspring of a barrel or of increasing the torque. Release.
[0013] (1) A cog mechanism according to the present application includes: a plurality of barrels including a barrel housing a mainspring and which is rotated about an axis during the unwinding of the mainspring, and a ratchet wheel which is rotatable about this axis with respect to the barrel during the unwinding of the mainspring; and a finishing gear which is arranged on the front side of a platen, and which is rotated under the action of the unwinding of the mainspring, the plurality of barrels being arranged at the front of the platen in a state of. mutual gear, and the barrels being separated from each other when viewed in a direction perpendicular to the plane of the plate, and each of the plurality of barrels being away from the finishing gear according to the plane of the plate, so that any superposition in the direction of the thickness is avoided with respect to the finishing gear vis-à-vis the plate.
According to the cog mechanism described in the present patent application, since the plurality of barrels is provided at the front of the plate, the space occupied by a plurality of barrels on the front face of the plate can be increased . Further, all of the barrels among the plurality of barrels are away from the train in a direction of the plane of the stage, preventing the barrels and the train from overlapping in the direction of the thickness of the stage. As a result, the thickness of the barrel can be made as large as possible, for example, to an extent corresponding to a gap between the plate and a gear bridge, and the outer diameters of the barrel and the ratchet wheel can be increased. as much as possible.
From there, it is possible to prevent any restriction of thickness and width of the mainspring in each barrel. For example, when the output torque is kept constant, the life of the mainspring can be improved, and when the power reserve of the mainspring is kept constant, the output torque can be increased. Therefore, the power reserve of the mainspring can be improved or the output torque can be increased, and a gear mechanism exhibiting excellent output torque transmission performance can be implemented.
(2) The gear train includes at least one second mobile which is rotated under the action of the disarming of the mainspring, a third mobile gear which is rotated by that of the second mobile, and a fourth mobile which is rotated via that of the third mobile gear, the fourth mobile being arranged coaxially with a central axis of the plate, away from the plurality of barrels in the plane in the plate, and the second mobile and the third mobile gear being arranged in positions offset with respect to the central axis in a direction extending in the plane of the plate, and away from the plurality of barrels according to a view in this plan.
In this case, since the fourth mobile can be arranged coaxially with the central axis of the plate, for example, by fixing the seconds hand to the fourth mobile, it can be used as a corresponding gear mechanism to what is called a direct drive with three central needles. Even in this case, the second mobile, the third mobile, and the fourth mobile are all distinctively arranged with respect to the plurality of barrels in the direction of the plane, and their overlap in the direction of the thickness of the plate with respect to them. barrels is avoided. Therefore, as described above, it is possible to improve the duration of the mainspring or to increase the output torque, and to efficiently transmit the energy to the second mobile.
[0018] (3) A transmission wheel which meshes with the barrel or the ratchet wheel and the second mobile and which transmits the energy generated by the unwinding of the mainspring to the second mobile can be arranged between any of the plurality of barrels and the second mobile.
In this case, the energy can be transmitted from the barrels to the second mobile via the transmission wheel. This is why it is not necessary to make the barrel or the ratchet wheel of the barrels directly mesh with the second mobile. For example, when the barrel or the ratchet wheel of the barrel and the second mobile are directly in mutual gear engagement via the second pinion, the diameter of the second gear wheel tends to be reduced in order to avoid interference with it. the barrel or the like. However, since the transmission wheel is provided, for example, when the transmission wheel and the second pinion of the second mobile are in mutual gear engagement, the position of the second pinion can be moved away from the barrel. Therefore, it is possible to increase the diameter of the second gear wheel, and it is possible to contribute to an increase in the speed increase ratio of the whole finishing gear.
[0020] In this way, by providing a transmission wheel, the second mobile can be arranged in a position remote from the barrel, and the diameters of the second pinion and of the second gear wheel can be chosen freely with fewer restrictions, thus improving the degree of freedom in the design of the movement. In addition, the speed increase ratio of the finishing gear can be increased.
Since the transmission wheel meshes only with the barrel or the ratchet wheel and the second mobile (for example, the second pinion of the second mobile), the transmission wheel can be a wheel having a single layer structure. Therefore, as long as the transmission wheel pivot does not overlap the barrel in the thickness direction, the transmission wheel is unlikely to affect the thickness of the barrel.
[0022] (4) The third mobile includes a third axis including an upper pivot and a lower pivot, and a third pinion which is formed on the third axis and which meshes with a second gear wheel of the second mobile. The second gear wheel can mesh with the third pinion at a central part in the axial direction of the third axis.
In this case, the energy of the second mobile can be transmitted to the third mobile by meshing with the second gear wheel and the third pinion of the third mobile. At this time, a large load is likely to act on a piece of gear between the second gear wheel and the third pinion. Even in this case, since the second gear wheel meshes with the third pinion at the central part in the axial direction of the third axis, it is easy to evenly distribute the load on the upper pivot and the lower pivot of the third mobile. . Therefore, it is possible to prevent the load from being concentrated on one or the other of the pivots. Thus, for example, it is possible to prevent one or the other of the pivots from wearing out too quickly. Therefore, the durability of all of the third mobile and all of the finishing gear can be improved, and the third mobile can be rotated stably and precisely.
[0024] (5) A center mobile which is arranged coaxially with the central axis of the plate and which includes a central gear wheel meshing with the third pinion is provided. The third mobile includes a third gear wheel which is formed on the third axis and which meshes with a fourth pinion of the fourth mobile. The center gear wheel and the third pinion can mesh in a position closer to the turntable than a meshing position of the second gear that meshes with the third gear, and the third gear and the fourth pinion can mesh in a position farther from the turntable than the second gear wheel.
In this case, by rotating the third mobile gear via the second mobile thanks to the energy coming from the unwinding of the mainspring, the energy supplied to the third mobile can be transmitted to the central mobile by the wheel d central gear, and the fourth mobile by the fourth wheel pinion. As a result, the center mobile and the fourth mobile can be rotated in accordance with the rotation of the third mobile.
In particular, as described above, the second gear wheel meshes with the third pinion of the third mobile at the central portion of the third axis in the axial direction, so that the third mobile rotates stably and precise. Therefore, the center mobile and the fourth mobile which mesh with the third mobile can also rotate with great precision while avoiding, for example, jerks, and it is possible to prevent any deviation of time information or others while ensuring proper movement of the hands.
In addition, the central gear wheel and the third pinion of the third mobile are in gear engagement in a position closer to the plate than that of engagement of the second gear wheel and the third pinion, and the third gear wheel and the fourth pinion of the fourth mobile are in gear engagement in a position farther from the plate than that of the gear of the second gear wheel and the third pinion. That is, the gear position between the center gear wheel and the third gear, the gear position between the second gear wheel and the third gear, and the gear position between the third gear wheel and fourth pinion are arranged in this order from the turntable.
[0028] Consequently, the energy transmitted from the second mobile to the third mobile can be transmitted to the central gear wheel and to the fourth pinion in a balanced manner while being dispersed in the axial direction of the third axis.
[0029] (6) The third mobile and the fourth mobile can be arranged closer to the plate than a virtual surface parallel to the barrel cover in the barrel.
In this case, the third mobile and the fourth mobile, which are located downstream of the energy transmission of the second mobile, are arranged closer to the plate than the virtual surface. In particular, since the fourth mobile, which is arranged coaxially with the central axis of the plate, is arranged closer to the plate, the finishing gear can be arranged in a position close to the plate in the central part of the plate. platinum, and its height can be kept low.
The central part of the plate is an area in which components of a timepiece are likely to be concentrated, and this is more particularly remarkable in the case of a direct drive with a central second hand. However, even in this case, since the height of the cog can be kept lower than the central part of the plate, in addition to facilitating the arrangement of other timepiece components, it is possible to preventing the timepiece from including a protruding central part, for example.
[0032] (7) A space is provided on the opposite side of the plate with respect to the virtual surface in the direction of the thickness of the plate, and an additional functional unit can be arranged in this space.
In this case, the additional functional unit which adds a function to the timepiece is arranged using the secure space by arranging the third mobile and the fourth mobile closer to the plate than the virtual surface. As a result, it is possible to contribute to the versatility of the timepiece.
[0034] In particular, since the additional functional unit is arranged using space efficiently, it is possible to prevent, for example, the central part of the timepiece from being protruding; Thus, it is possible to implement a timepiece having versatility and excellent appearance and aesthetics, and it is possible to prevent the appearance of the timepiece from having too industrial an appearance.
[0035] (8) The additional functional unit is an automatic winding mechanism, including: an oscillating weight which is rotatably mounted about an axis of rotation, and an automatic winding gear which transmits the energy resulting from the rotation oscillating weight to any one of the plurality of barrels, and rotates the barrel in one direction. The oscillating mass is arranged coaxially with the axis of rotation, and includes a bearing comprising an outer ring on which is arranged an oscillating mass pinion which meshes with the automatic winding gear. The outer ring can be arranged away from the barrels in a plane view of the plate, thus avoiding any overlap in the thickness direction with respect to the barrels.
In this case, since the automatic winding mechanism is provided as an additional functional unit, the energy of the oscillating weight can be used to always rotate the barrel in the same direction via the automatic winding gear. As a result, the mainspring can be wound up, and the automatic winding function can be added. In particular, since the automatic winding mechanism is arranged using the space made available, it is possible to prevent the central part of the timepiece from protruding as described above, and it is possible to implement a self-winding timepiece which includes an automatic winding mechanism and which has excellent appearance and aesthetics.
In addition, since the outer ring is arranged using the space made available, it is possible to secure the height of the outer ring. Therefore, the length of the axle of the wheel which meshes with the oscillating weight pinion of the automatic winding gear can be set to a length which allows the pivots to be formed on the axle. As a result, it is possible to pivotally support (rotational guide) the wheel which meshes with the oscillating mass by using the pivots.
When the pivots can not be formed due to the short length of the axis, a pin guide is often used. In the case of a spindle, since there is a limit to the reduction in diameter, the frictional resistance is important and a loss of power is likely to occur. On the other hand, since the pivots can be formed by securing the length of the axle as described above, the diameters of the pivots and a guide part can be reduced, the frictional resistance can be reduced, and the efficiency. transmission can be improved.
In addition, since the outer ring is also away from the barrel in the direction of the plane, their overlap with the barrel in the direction of the thickness of the plate is avoided. As a result, the thickness of the barrel can be increased without being affected by the outer ring, and the outer diameters of the movement wheel and the ratchet wheel can be increased.
[0040] (9) The cog mechanism includes two barrels. The additional functional unit can be arranged on the opposite side of the finishing gear train with respect to a second virtual line connecting the central axis of the plate and an intermediate position which is located on a first virtual line connecting the centers of two barrels in a row. plan view of the plate and located between the centers of the barrels.
[0041] In this case, it is possible to arrange the additional functional unit and the cog in a balanced manner while using the space, and to contribute to a reduction in the total thickness of the timepiece and the like.
[0042] (10) A movement according to the present application includes the cog mechanism described above.
[0043] (11) A timepiece according to the present application includes the movement described above.
[0044] In this case, since a cog mechanism having excellent output torque transmission performance by improving the duration of the mainspring or by increasing the output torque is provided, a movement and a timepiece which have high reliability of operation can be achieved.
Thus, according to the present application, a gear mechanism, a movement and a timepiece which are capable of improving the duration of the mainspring or of increasing the output torque can be obtained.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is an external view showing a timepiece according to one embodiment of the invention. Figure 2 is a plan view of a movement shown in Figure 1. Figure 3 is a sectional view showing a relationship between a first barrel and a second barrel shown in Figure 2. Figure 4 is a side view. section showing a relationship between the second barrel shown in Figure 2 and a finishing gear. Figure 5 is a sectional view of a central portion of a plate shown in Figure 2. Figure 6 is a sectional view showing a relationship between the first barrel shown in Figure 2 and an automatic winding gear. Figure 7 is a perspective view of an oscillating weight shown in Figure 2. Figure 8 is a plan view of a movement showing a variant of a gear mechanism according to the invention. Fig. 9 is a sectional view showing a relationship between the second barrel shown in Fig. 2 and the finishing gear.
DESCRIPTION OF EMBODIMENTS
In what follows, an embodiment of the invention will be described with reference to the drawings. In the present embodiment, as an example of a timepiece, a self-winding mechanical timepiece having a structure of the direct drive of the central second hand will be described as an example in which an hour hand, a hand minutes and a seconds hand are arranged in the center of a movement.
In each drawing of the present embodiment, in order to make the drawing more visible, part of the timepiece components may be omitted, and each timepiece component may be illustrated in a simplified manner.
(Basic configuration of a timepiece)
Generally, reference is made to a "movement" to denote a mechanical member including a driving part of the timepiece. We refer to an "assembly" of the timepiece to denote a state where a dial and hands are attached to the movement and placed in a timepiece case to make it a finished product. Among the two sides of a plate which constitutes a plate for the timepiece on which various components are arranged, one side (that is to say, the side where the dial is arranged) where the crystal closing the case of the timepiece is fitted is called the "rear face" of the movement. Of the two sides of the plate, the other side (ie, the side opposite the dial) where the case back of the timepiece is located is called the “front face” of the movement.
In the present embodiment, a direction going from the dial towards the bottom of the case (that is to say the front face) is designated as going upwards and a direction going towards its opposite side (c ' i.e. the back side) is referred to as going down. Therefore, when one follows the direction of the thickness of the plate, one moves in a direction from top to bottom.
As illustrated in Figure 1, the timepiece assembly 1 according to the present embodiment comprises: a movement 10; a dial 4 including a scale or the like indicating at least information relating to time; and hands including an hour hand 5 indicating the hours, a minute hand 6 indicating the minutes and a seconds hand 7 indicating the seconds in a timepiece case 3 including a back (not shown) and a crystal 2 .
As shown in Figures 2 to 4, the movement 10 includes a gear mechanism 12 arranged at the front of a plate 11.
The gear mechanism 12 mainly comprises a plurality of barrels 20 arranged between the plate 11 and a barrel bridge 13 arranged on the front face of the plate 11 and a finishing gear 15 arranged between the plate 11 and a bridge of gear 14 arranged on the front face of the plate 11. The gear mechanism 12 further includes an escapement 16 which controls the rotation of the finishing gear 15, a regulating member (not shown) which controls a speed of the escapement 16 , a manual winding mechanism 17 and an automatic winding mechanism 18.
A timer and the like described below are arranged on the rear face of the plate 11, and the dial 4 is visible through the glass 2.
(Barrel)
As shown in Figures 2 and 3, two barrels 20 are arranged on the front face of the plate 11. The number of barrels 20 is not limited to two and could be three or more.
Reference is made to one of the two barrels 20 as being a first barrel 21, and to the other as being a second barrel 22. The first barrel 21 and the second barrel 22 are arranged outside an axis central C, which passes through the center of the plate 11 in the direction of the thickness; they extend in the plane of the plate 11, and are adjacent to one another.
The first barrel 21 rotates about a first axis 01 relative to the plate 11 and to the barrel bridge 13. The second barrel 22 rotates about a second axis 02 relative to the plate 11 and to the bridge barrel 13.
In the present embodiment, with regard to each of the axes including the first axis O1, the second axis O2 and the central axis C, a direction secant to an axis is referred to as being a radial direction, and a circumferential direction is referred to as a direction rotating about the axis in a plan view taken from the axial direction.
Subsequently, the first barrel 21 and the second barrel 22 will be described in detail.
(First barrel)
As shown in Figures 2 and 3, the first barrel 21 is formed of a barrel structure 31 which accommodates a mainspring 30, a barrel shaft 35, a ratchet wheel shaft 40 and a ratchet wheel 45, and is arranged coaxially with the first axis O1.
The barrel structure 31 includes a flat-bottomed cylindrical barrel main body 32 and a surmounted cylindrical barrel cover 33 which closes the barrel main body 32 from above, and houses the mainspring 30 inside the barrel. main barrel body 32.
The main barrel body 32 has a bottom wall 32a formed in the form of a disc centered on the first axis 01 and a peripheral wall 32b which extends upwards from an outer peripheral edge of the bottom wall 32a and overcomes the mainspring 30 from the outside in a radial direction.
A first fixing hole 34a which penetrates vertically into the lower wall 32a is formed in a central part of the lower wall 32a. A barrel toothing 32c projecting outwardly in the radial direction is formed around the entire circumference on an outer peripheral surface of the peripheral wall 32b. An outer end of the mainspring 30 is fixed to an inner peripheral surface of the peripheral wall 32b.
The barrel cover 33 closes the barrel main body 32 from above. The outer peripheral edge of the barrel cover 33 is mounted on an upper end of the peripheral wall 32b of the barrel main body 32. Accordingly, the barrel main body 32 and the barrel cover 33 are combined with each other. other to form a single piece. A second fixing hole 34b which vertically penetrates into the barrel cover 33 is formed in a central part of the barrel cover 33.
The barrel shaft 35 has a cylindrical shape and is arranged coaxially with the first axis O1. The barrel shaft 35 is inserted through the first mounting hole 34a and the second mounting hole 34b in the barrel 31.
An intermediate portion 35a of the barrel shaft 35 in an axial direction has an outward bulge in the radial direction and is slightly inserted into the main barrel body 32. Then, an inner end of the mainspring 30 is locked on the intermediate part 35a of the barrel shaft 35.
The barrel shaft 35 is inserted in the first fixing hole 34a and in the second fixing hole 34b and can rotate relative to the barrel structure 31 about the first axis O1. Accordingly, the barrel shaft 35 supports the barrel structure 31 and can rotate relative thereto.
The intermediate part 35a of the barrel shaft 35 is slightly inserted into the barrel main body 32, so that a movement of the upper-lower barrel 31 relative to the barrel shaft 35 is regulated. The upper end of the barrel shaft 35 extends and protrudes upwardly beyond the barrel cover 33.
The ratchet wheel shaft 40 includes an axis 41 extending in the upper-lower direction and a flange 42 formed integrally with the axis 41 and protruding outwardly in the radial direction, and is arranged coaxially with the first axis O1.
The axis 41 is inserted into the barrel shaft 35 from above, and is fixed integrally inside the barrel shaft 35 by, for example, interlocking or screwing. A lower end of the pin 41 projects downwardly beyond the barrel shaft 35. An upper end of the pin 41 and the flange 42 are arranged above the barrel shaft 35. A upper pivot 41a and a lower pivot 41b are formed at an upper end and a lower end of the axle 41, respectively.
In the aforementioned ratchet wheel shaft 40, the lower pivot 41b is kept movable in rotation by a bearing arranged in the plate 11, and the upper pivot 41 a is kept movable in rotation by a bearing disposed in the bridge barrel 13. Consequently, the entire first barrel 21 is rotatably supported between the plate 11 and the barrel bridge 13 about the first axis O1. Examples of bearings include a pierced stone formed by a ruby or the like.
The ratchet wheel 45 is arranged coaxially with the first axis O1 between the barrel cover 33 and the flange 42, and is fixed to the upper end of the barrel shaft 35 in the relaxed state by hunting, for example. A lower surface of the flange 42 and an upper surface of the ratchet wheel 45 are in contact with each other. As a result, the ratchet wheel 45 is fixed in a state where it is sandwiched between the flange 42 and the barrel shaft 35, and is not in contact with the barrel 31. That is, , the ratchet wheel 45 is arranged above the barrel 31 in a state in which a gap is formed between the ratchet wheel 45 and the barrel cover 33. A ratchet tooth 45a is formed on the outer peripheral edge of the barrel. the ratchet wheel 45 over the entire circumference.
The mainspring 30 is housed in the barrel 31 in a state where it is wound in a spiral around the first axis O1. As described above, the outer end of the mainspring 30 is secured to the main barrel body 32, and the inner end of the mainspring 30 is locked to the mainspring 35.
Consequently, the mainspring 30 is wound while being elastically deformed and reduced in diameter by a relative rotation between the ratchet wheel 45 fixed to the barrel shaft 35 and the barrel 31, and an energy (output torque ) is transmitted to the ratchet wheel 45 or the barrel 31 by the elastic restoring force at the time of unwinding, so that the ratchet wheel 45 or the barrel 31 can be rotated around the first axis O1.
(Second barrel)
The second barrel 22 has the same configuration as that of the first barrel 21 described above. Consequently, each component of the second barrel 22 is designated by the same reference number as that of the first barrel 21, and its detailed description will not be repeated in detail.
However, in the first barrel 21, the external diameter of the barrel structure 31 and the external diameter of the ratchet wheel 45 are the same, and the teeth of the barrel 32c and the ratchet teeth 45a overlap in the direction going up and down. On the other hand, in the second barrel 22, the outer diameter of the ratchet wheel 45 is smaller than the outer diameter of the barrel structure 31, and the ratchet toothing 45a is arranged above the barrel cover. 33.
(Relationship between the first barrel and the second barrel)
The first barrel 21 and the second barrel 22 formed as described above are adjacent to each other as described above.
Specifically, the first barrel 21 is located closer to a winding stem 50 than the second barrel 22. Then, the first barrel 21 and the second barrel 22 are arranged adjacent to each other in a state. wherein its barrel teeth 32c are in mutual gear engagement. In addition, an intermediate crown wheel 55 which is driven in rotation following a rotation of the winding rod 50 meshes with the ratchet wheel 45 of the first barrel 21 via the ratchet teeth 45a.
The winding stem 50 is rotatably incorporated in a winding stem guide hole (not shown) formed in the plate 11. A crown 51 shown in Figure 1 is connected to the winding stem 50. In Consequently, it is possible to turn the winding stem 50 by the crown 51.
The position of the winding stem 50 in the axial direction is determined by keyless work (not shown) including a pull tab, a lever, a lever spring, and the like. A winding pinion (not shown), which is rotatably mounted relative to the winding stem 50 and not axially movable, is attached to a shaft guide portion of the winding stem 50. A sliding pinion (also called clutch wheel - not shown), which is not rotatable relative to the winding rod 50, but movable in the axial direction, is fixed to a part of the winding rod 50 located closer to its end ( its tip) than the winding pinion.
For example, when the winding stem 50 is set to a winding wheel position (position "0") closest to the movement 10 in the axial direction, the winding pinion and the sliding pinion can mesh with the one with the other. Therefore, by rotating the winding stem 50 via the crown 51 in this state, it is possible to rotate the winding pinion around a coaxial axis using the winding stem 50 via the sliding pinion.
It is possible to rotate the intermediate crown wheel 55 shown in Figure 2 by rotating the winding pinion. The intermediate crown wheel 55 constitutes the manual winding mechanism 17. In the example illustrated, only the intermediate crown wheel 55 is shown for the sake of simplicity, and the manual winding mechanism 17 includes a plurality of intermediate wheels connecting the chain. intermediate crown wheel 55 to the winding pinion.
In any case, the manual winding mechanism 17 is constituted such that the intermediate crown wheel 55 finally rotates as the rotation of the winding pinion.
When the winding stem 50 is rotated in a state where the winding stem 50 is pulled out one notch from the "0" position above, it is possible to rotate a 100 hour wheel and a center mobile 80 to be described later by the sliding pinion and an adjusting wheel (not shown). Accordingly, corrections such as time adjustment can be made by correcting the time.
Since the intermediate crown wheel 55 meshes with the ratchet wheel 45 of the first barrel 21 as described above, it is possible to rotate the ratchet wheel 45 around the first axis 01 via the manual winding mechanism 17 by turning the winding stem 50 to position “0”. Therefore, it is possible to wind the mainspring 30 by the barrel shaft 35.
At this time, as shown in Figures 2 and 3, since the barrel structure 31 of the first barrel 21 and the barrel structure 31 of the second barrel 22 are in mutual gear engagement, the barrel structure 31 of the first barrel 21 rotates around the first axis O1 with the winding of the mainspring 30, and the barrel structure 31 of the second barrel 22 rotates around the second axis 02 accordingly. Consequently, the mainspring 30 can be wound up by the rotation of the barrel structure 31 relative to the second barrel 22.
As described above, concerning the reassembly of the mainspring 30, the mainspring 30 can be reassembled by rotating the ratchet wheel 45 in the first barrel 21 around the first axis O1. On the other hand, the mainspring 30 can be reassembled by rotating the barrel structure 31 in the second barrel 22.
In addition, concerning the output torque (energy) from the unwinding of the mainspring 30, the output torque of the mainspring 30 can be transmitted to the barrel structure 31 of the second barrel 22 by rotating the barrel structure 31 of the first barrel 21. On the other hand, by turning the ratchet wheel 45 in the second barrel 22, it is possible to transmit the output torque of the mainspring 30 of the second barrel 22 and the output torque transmitted from the first barrel 21 to a transmission wheel 110 which will be described later.
As shown in Figure 2, the ratchet wheel 45 is engaged, in the first barrel 21, with a pawl 56 which prevents any reverse rotation of the ratchet wheel 45 in order to avoid any unwinding of the mainspring 30. As a result, the ratchet wheel 45 can only rotate in one direction, that in which the mainspring 30 is wound up.
(Finishing gear and transmission wheel)
As shown in Figures 2 and 4, the finishing gear 15 arranged between the plate 11 and the gear bridge 14, is rotated by the output torque following the unwinding of the motor springs 30 in the first barrel 21 and the second barrel 22, and its role is to move the hour hand 5, the minute hand 6, and the seconds hand 7.
The cog bridge 14 includes an upper cog bridge 14a arranged in the same height position as the barrel bridge 13, and a lower cog bridge 14b located closer to the plate 11 than the upper cog bridge 14a , and has a stepped shape in which the height is changed in two steps.
The finishing gear 15 mainly includes a second mobile 60, a third mobile 70, and a fourth mobile 90. The first barrel 21 and the second barrel 22 are arranged away from the finishing gear 15 according to a view in plane of the plate 11 so as to avoid overlapping the finishing gear 15 in the up and down direction.
In addition, the gear mechanism 12 according to the present embodiment comprises a timer gear including mainly the center mobile 80, the fourth mobile 90, the hour wheel 100, and a minute mobile (not shown) . The gear mechanism 12 further includes the transmission wheel 110 which is arranged between the ratchet wheel 45 in the second barrel 22 and the second mobile 60, and transmits the output torque following the unwinding of the mainspring 30 to the second mobile 60. .
The transmission wheel 110 is a wheel which constitutes a free wheel or the like, and rotates around a third axis 03. In the transmission wheel 110, an upper pivot 110a is supported in rotation by a bearing such that 'a perforated stone, arranged in the upper gear bridge 14a, and a lower pivot 110b is kept movable in rotation by a bearing such as the perforated stone arranged in an overhanging rim 11a formed integrally in the plate 11.
The transmission wheel 110 includes a transmission gear wheel 111 which meshes with the ratchet wheel 45 of the second barrel 22. Accordingly, the transmission wheel 110 rotates around the third axis 03 with the rotation of the wheel. ratchet 45. The transmission wheel 110 is a single-layer wheel including the transmission gear wheel 111 without pinion.
The overhanging rim 11a extends along the direction of the plane of the plate 11 from an upper end of a portion of the plate 11 which rises along the peripheral wall 32b of the barrel structure 31 of the second barrel 22. Accordingly, the transmission wheel 110 is kept movable in rotation by the overhanging rim 11a in a state where it is raised and is located in the same height position as the ratchet wheel 45 and the cover. cylinder 33.
In the transmission wheel 110 constituted as described above, a transmission toothing 111a meshes with a ratchet toothing 45a in a state where the transmission gear wheel 111 is arranged in the same height position ( located in the same plane) as the ratchet wheel 45 of the barrel structure 31 of the second barrel 22.
In particular, the transmission wheel 110 is arranged such that the axes on which the upper pivot 110a and the lower pivot 110b are formed are away from the second barrel 22 in the direction of the plane of the plate 11 and do not overlap in the upper-lower direction. As described above, the transmission gear wheel 111 is arranged in the same plane as the ratchet wheel 45. Therefore, the transmission wheel 110 is unlikely to affect the thickness of the barrel 31.
In the second mobile 60, an upper pivot 60a is kept movable in rotation by a bearing such as the perforated stone arranged in the upper gear bridge 14a, and a lower pivot 60b is kept movable in rotation by a bearing such as the perforated stone arranged in the plate 11, so that the second mobile 60 can be driven in rotation about a fourth axis 04. The second mobile 60 comprises a second pinion 61 which meshes with the transmission gear wheel 111 and a second gear wheel 62 which meshes with a third pinion 71 of the third mobile 70 to be described later. Consequently, the second mobile 60 rotates around the fourth axis 04 in synchronization with the rotation of the transmission wheel 110.
[0100] The second gear wheel 62 is inserted below the overhanging flange 11a which supports the transmission gear wheel 111. Therefore, the transmission wheel 110 is arranged upward and overhangs the second wheel d. 'gear 62.
[0101] In the third mobile 70, an upper pivot 70a is kept movable in rotation by a bearing such as the perforated stone arranged in the lower gear bridge 14b, and a lower pivot 70b is kept movable in rotation by a bearing such as the perforated stone arranged in the plate 11, so that the third mobile 70 can be rotated about a fifth axis 05. The third mobile 70 includes a third axis 73 on which the upper pivot 70a and the lower pivot 70b are formed , the third gear wheel 71 which is formed on the third axis 73 and meshes with the second gear wheel 62, and a third gear wheel 72 which is formed on the third axis 73 and meshes with a fourth gear 92 of the fourth mobile 90 to be described below. Consequently, the third mobile 70 rotates around the fifth axis 05 in synchronization with the rotation of the second mobile 60.
[0102] In particular, since the third mobile 70 is supported by the lower gear bridge 14b located below the upper gear bridge 14a which supports the second mobile 60 and the like, the third mobile 70 is arranged as being closer to the plate 11 as the second mobile 60 and the like. Specifically, the third mobile 70 is arranged below a virtual surface V (see FIG. 4) (on the side of the plate 11) parallel to the barrel cover 33.
The fourth mobile 90 is arranged coaxially with the central axis C of the plate 11; it is arranged in a cylindrical part 95 held by the plate 11, and can rotate around the central axis C.
[0104] The fourth mobile 90 includes an axis 91, the fourth wheel pinion 92 which meshes with the third gear wheel 72, and a fourth gear wheel 93. The axis 91 is rotatably supported by a bearing arranged in the cylindrical part 95. In the illustrated example, the axis 91 is rotatably supported by two bearings arranged at predefined intervals in the direction from top to bottom. An upper pivot 91a of the axis 91 is kept movable in rotation by a bearing such as a perforated stone, arranged in the lower gear bridge 14b.
[0105] Consequently, the fourth mobile 90 rotates around the central axis C in synchronization with the rotation of the third mobile 70.
A lower end of the axis 91 projects downwards beyond the dial 4 and projects downwards beyond the center mobile 80 and the hour wheel 100. A seconds hand 7 is fixed to the lower end of the axis 91. Consequently, the seconds hand 7 is arranged in a direct drive system according to which the seconds hand 7 is moved directly via the rotation of the fourth mobile 90. L The seconds hand 7 rotates at a rotational speed adjusted by the escapement 16 and the regulator, that is to say, one rotation per minute.
Since the fourth mobile 90 formed in this way is also supported by the lower gear bridge 14b similarly to the third mobile 70, the fourth mobile 90 is arranged closer to the plate 11 than the second mobile 60 and the like. Consequently, the fourth mobile 90 is arranged at the same height as the third mobile 70, and is arranged below the virtual surface V.
[0108] The center mobile 80 constituting the timer is arranged coaxially with the central axis C on the rear face of the plate 11, and rotates around the central axis C. The center mobile 80 includes a main body of tubular center movable 81 which surmounts the cylindrical portion 95, a central gear wheel 82 which is combined with an upper end of the center movable main body 81 and meshes with the third pinion 71 of the third movable 70, and a pinion barrel 81a formed in a part of the center movable main body 81. The part is located between the central gear wheel 82 and the hour wheel 100. As a result, the center movable 80 rotates around the central axis. C in synchronization with the rotation of the third mobile 70.
[0109] Specifically, in the center wheel 80, the center wheel main body 81 is arranged inside an hour wheel main body 101 which will be described later in a state where the barrel 81a overlaps an hour pinion 102 which will be described later. As a result, the center mobile 80 can be positioned in the up and down direction by the hour wheel 100, and can stably rotate around the central axis C while being guided by the hour wheel 100.
[0110] The center movable main body 81 and the center gear wheel 82 are combined in a state in which a predetermined pressure contact force (frictional force) is maintained. Therefore, when a relative rotational force exceeding the pressing contact force (frictional force) acts between the center movable main body 81 and the center gear wheel 82, so that when the time is set, it is possible to slide the center gear wheel 82 relative to the center movable main body 81.
A lower end of the center mobile main body 81 protrudes below the hour wheel 100 and is arranged above the lower end of the axle 91 in the fourth mobile 90. The hand minute hand 6 is attached to the lower end of center mobile main body 81. Therefore, minute hand 6 is attached closer to dial 4 than seconds hand 7 attached to fourth mobile 90. Accordingly , the minute hand 6 can be moved directly via the rotation of the center mobile 80.
[0112] The minute hand 6 rotates at a speed of rotation adjusted by the escapement 16 and the regulator, that is to say, one rotation per hour. Since the center mobile 80 is located below the fourth gear wheel 93, the center mobile 80 is arranged below the virtual surface V.
The hour wheel 100 constituting the timer is arranged coaxially with the central axis C on the rear face of the plate 11, and rotates around the central axis C. The hour wheel 100 includes the main body hour wheel 101 which surmounts center wheel main body 81, and hour pinion 102 which is integrally formed on an upper end of hour wheel main body 101 and meshes with a minute wheel body (no. represented).
[0114] The minute wheel set also meshes with the barrel pinion 81a in the center wheel set 80. Consequently, the hour wheel 100 rotates around the central axis C in synchronization with the rotation of the center wheel unit 80 and the minute mobile.
[0115] The lower end of the hour wheel main body 101 protrudes downward beyond the dial 4 and is arranged above the lower end of the center movable main body 81. The clock hand hour 5 is attached to the lower end of the hour wheel main body 101. Therefore, hour hand 5 is located closer to dial 4 than minute hand 6 attached to center mobile 80. Accordingly , the 5 hour hand can be moved directly via the rotation of the 100 hour wheel.
[0116] The hour hand 5 rotates at a speed of rotation adjusted by the escapement 16 and the regulating member, that is to say, one rotation in 12 hours. The hour wheel 100 is located below the central gear wheel 82, and is therefore arranged below the virtual surface V described above.
In the finishing gear 15 and the timer gear which are formed as described above, the fourth mobile 90, the center mobile 80, and the hour wheel 100 are arranged coaxially with the central axis C, and the second mobile 60, the third mobile 70, and the minute mobile are arranged in positions offset from the central axis C in a plan view of the plate 11. In addition, the third mobile 70, the fourth mobile 90, the center mobile 80, the hour wheel 100, and the minute mobile are arranged below the virtual surface V. Therefore, as shown in FIG. 4, a space S in which the mechanism winding mechanism 18 can be arranged and provided above the virtual surface V.
The automatic winding mechanism 18 will be described below.
(Exhaust and regulator)
As illustrated in Figures 2 and 4, the escapement 16 comprises an intermediate escape gear wheel 120 which rotates about a sixth axis 06 as the rotation of the fourth wheel 90, a mobile d 'escape gear 130 which rotates about a seventh axis 07 as the rotation of the intermediate exhaust gear wheel 120 takes place, and an anchor (not shown) which allows the escape of the gear wheel set. The escapement 130 which rotates smoothly, and controls the finishing gear 15 via a regular oscillation of a balance wheel (not shown).
[0120] In the intermediate exhaust gear mobile 120, an upper pivot 120a is kept movable in rotation by a bearing such as the perforated stone arranged in the lower gear bridge 14b, and a lower pivot 120b is kept movable in rotation by a bearing such as the perforated stone arranged in the plate 11, so that the intermediate escape gear wheel 120 can be driven in rotation about the sixth axis 06. The intermediate escape gear wheel mobile 120 has an intermediate exhaust gear wheel 121 which meshes with the fourth gear wheel 93 and an intermediate escape gear wheel 122. Accordingly, the intermediate exhaust gear wheel 120 rotates around the sixth. axis 06 synchronously with the rotation of the fourth mobile 90.
[0121] In the escape gear mobile 130, an upper pivot 130a is kept movable in rotation by a bearing such as the perforated stone arranged in an exhaust bridge 135, and a lower pivot 130b is kept movable in rotation by a bearing such as the perforated stone arranged in the plate 11, so that the exhaust gear mobile 130 can be driven in rotation about the seventh axis 07. The exhaust gear mobile 130 includes a mobile exhaust gear 131 which meshes with the intermediate exhaust gear wheel 122, and an exhaust gear wheel 132 including a plurality of exhaust teeth. The anchor includes an inlet vane and an outlet vane which can be disengaged from the exhaust teeth.
[0122] The regulator includes the balance which mainly uses a hairspring (not shown) as a source of energy and which rotates in a reciprocating motion (alternating back and forth rotation) at a stable amplitude. (oscillation angle) and according to an output torque of the mainspring 30.
[0123] The escapement 16 and the regulator which are formed as described above can control the rotation of the finishing gear 15 and the timer, and as described above, the seconds hand 7, l The 6 minute hand and 5 hour hand can be moved appropriately to maintain an accurate time display.
(Automatic winding mechanism)
[0124] As illustrated in Figure 2, the automatic winding mechanism 18 functions as an additional functional unit to add an automatic winding function to the timepiece 1, and is provided using the secure space S above. of the virtual surface V shown in Figure 4.
More specifically, the automatic winding mechanism 18 is arranged on the opposite side of the finishing gear 15 with respect to a second virtual line L2 in a plan view of the plate 11. The second virtual line L2 connects an intermediate position P and the central axis C of the plate 11. The intermediate position P is located between the centers of the first barrel 21 and of the second barrel 22.
[0126] The automatic winding mechanism 18 is a mechanism which automatically winds the mainspring 30 in the first barrel 21 by rotating an oscillating weight 150 shown in FIG. 2, which is rotated in response to, for example, a movement of a user's arm.
[0127] As shown in Figures 2 and 4, the automatic winding mechanism 18 includes the oscillating weight 150 which is rotatably mounted about an axis of rotation, and an automatic winding gear 170 which transmits the rotational energy of the oscillating mass 150 towards the ratchet wheel 45 of the first barrel 21 to rotate the ratchet wheel 45 in one direction.
In the present embodiment, a case will be described by way of example according to which the axis of rotation is coaxial with the central axis C of the plate 11. In other words, the oscillating mass 150 rotates around the central axis C. However, the invention is not limited to such a case; for example, the automatic winding mechanism 18 could be used such that the axis of rotation is arranged slightly offset from the central axis C in a plan view of the plate 11, and the axis of rotation and the central axis C are not coaxial.
[0129] Furthermore, in the present embodiment, the following case is described where the energy of the oscillating mass 150 is transmitted to the ratchet wheel 45 of the first barrel 21 in a state where the oscillating mass 150 rotates in the two directions around the central axis C, and the automatic winding gear 170 switches the rotation of the oscillating mass 150 from these two directions to the rotation in one direction only.
However, such a case is not given by way of example and the invention is not limited to this case. For example, the oscillating mass 150 can rotate about the central axis C only in one direction, and the automatic winding gear 170 can transmit energy from the rotation of the oscillating mass 150 to the ratchet wheel 45. As such However, while the rotational energy of the oscillating weight 150 can be transmitted to the ratchet wheel 45 using the automatic winding mechanism 18 and the ratchet wheel 45 can still be rotated in one direction, the configuration of the ratchet wheel 45 can still be rotated in one direction. automatic winding gear 170 can be adjusted appropriately as required.
[0131] As shown in Figures 5 and 6, the oscillating weight 150 and the automatic winding gear 170 are supported using a first automatic winding bridge 180 and a second automatic winding bridge 181 which are arranged below the first. automatic winding bridge 180 and are combined with the first automatic winding bridge 180. Therefore, the automatic winding mechanism 18 is assembled as a functional unit.
[0132] Specifically, the oscillating weight 150 is rotatably mounted around the central axis C while being housed in a housing hollow 182 formed in the first automatic winding bridge 180. A shaft 183 in the upright position is formed of coaxially with the central axis C in the housing hollow 182. The automatic winding gear train 170 is rotatably mounted while being arranged between the first automatic winding bridge 180 and the second automatic winding bridge 181.
[0133] The oscillating weight 150 is arranged above the fourth mobile 90 in a state that it is rotatable in two directions around the central axis C, and it acts as a source of energy to actuate the mechanism of automatic winding 18.
[0134] Specifically, as shown in Figures 5 and 7, the oscillating weight 150 includes a ball bearing (bearing according to the invention) 151 and a weight 160, and rotates clockwise and in its opposite direction around the central axis C according to the movements of the user's arm or others.
[0135] The ball bearing 151 includes an inner ring 152 fixed to the shaft 183 formed in the housing recess 182, an outer ring 153 surmounting the inner ring 152, and a plurality of balls 154 which are rotatably interposed. between the inner ring 152 and the outer ring 153. Accordingly, the outer ring 153 can rotate relative to the inner ring 152 about the central axis C via the balls 154. An oscillating weight pinion 153a which meshing with the automatic winding gear 170 is formed around the entire circumference of an outer peripheral surface of the outer ring 153.
[0136] The weight 160 is configured as a fan in a plan view, and is located outside at the outer ring 153. Therefore, the weight 160 and the outer ring 153 are integrally rotated around. of the central axis C.
[0137] As shown in Figure 2, the outer ring 153 including the oscillating weight pinion 153a formed as described above is also arranged away from the first barrel 21 and the second barrel 22 in a plan view of the plate 11 to avoid any overlap in the direction from top to bottom.
[0138] As shown in Figures 2, 5 and 6, the automatic winding gear 170 includes a first inverting freewheel 190 which rotates following the rotation of the outer ring 153, a second inverting freewheel mobile 200 which is driven in rotation following that of the first inverting freewheel 190, a first inverting wheel 210 which includes a first lower inverting wheel 211 and a first inverting transmission wheel 212 and which rotates about an eighth axis 08, a second inverting wheel 220 which includes a second lower inverting wheel 221 and a second inverting transmission wheel 222 and which rotates about a ninth axis 09, a first reduction wheel 230 which rotates only in one direction following the rotation of the first transmission wheel inverter 212 or the second inverting transmission wheel 222, a second reduction wheel 240 which rotates following the rotation of the first reduction wheel 230, and a third reduction mobile 250 which rotates following the rotation of the second reduction mobile 240 and which transmits the energy of the oscillating mass 150 to the ratchet wheel 45 of the first barrel 21.
In Figures 5 and 6, the first inverting wheel 210 and the second inverting wheel 220 are not shown.
[0140] As shown in Figures 2 and 5, in the first inverting freewheel 190, an upper pivot 190a is kept movable in rotation by a bearing such as the perforated stone arranged in the first automatic winding bridge 180, and a pivot lower 190b is kept movable in rotation by a bearing such as the perforated stone arranged in the second automatic winding bridge 181. The first inverting freewheel 190 includes a first intermediate wheel 191 which meshes with the oscillating weight pinion 153a, and a first Reverse freewheel gear 192. Accordingly, the first reverse wheel 190 rotates in response to the rotation of the oscillating mass 150.
[0141] In the intermediate center mobile 200, an upper pivot 200a is kept movable in rotation by a bearing such as the perforated stone arranged in the first automatic winding bridge 180, and a lower pivot 200b is kept movable in rotation by a bearing such as the perforated stone disposed in the second automatic winding bridge 181. The intermediate center mobile 200 includes an intermediate center wheel 201 which meshes with the first inverting freewheel pinion 192. Consequently, the second freewheel mobile inverter 200 is rotatable in response to the rotation of the first inverter freewheel 190.
[0142] As illustrated in FIG. 2, the first inverter wheel 210 includes an axis which is rotatably mounted around the eighth axis 08, the first lower inverter wheel 211 fixed to the axis, and the first inverter transmission mobile 212 which is combined with the axis and can rotate with respect to this axis.
[0143] The axis is rotatably mounted between the first automatic winding bridge 180 and the second automatic winding bridge 181. The first lower inverter wheel 211 meshes with the center intermediate wheel 201. Consequently, the first lower inverter wheel 211 can be rotated around the eighth axis 08 following that of the second reversing wheel mobile 200.
[0144] A reversing mechanism (not shown) such as a one-way clutch is arranged between the first reversing transmission wheel 212 and the first lower reversing wheel 211 to allow the first lower reversing wheel 211 to rotate with the first transmission wheel. to inverter 212 when the first lower inverter wheel 211 rotates in one direction around the eighth axis 08, and to allow the first inverter transmission wheel 212 to remain at rest when the first lower inverter wheel 211 rotates in the other direction around the eighth axis 08.
[0145] For example, the first reversing transmission wheel 212 rotates in the same direction when the first lower reversing wheel 211 rotates clockwise around the eighth axis 08, but does not move when the first reversing wheel lower 211 rotates counterclockwise.
[0146] The second inverting wheel 220 comprises an axis which is rotatably mounted around the ninth axis 09, the second lower inverting wheel 221 fixed to the axis, and the second inverting transmission wheel 222 which is combined with the axis and can rotate with respect to the axis.
[0147] The axis is rotatably mounted and supported by pivots between the first automatic winding bridge 180 and the second automatic winding bridge 181. The second lower inverting wheel 221 meshes with the first lower inverting wheel 211. Consequently, the second lower inverter wheel 221 rotates around the ninth axis 09 following the rotation of the first lower inverter wheel 211.
[0148] A reversing mechanism (not shown) such as a one-way clutch is provided between the second reversing transmission wheel 222 and the second lower reversing wheel 221 to allow the second lower reversing wheel 221 to rotate synchronously with the second. reverse gear wheel 222 when the second lower reverse wheel 221 rotates in one direction around the ninth axis 09, and to allow the second reverse drive wheel 222 to remain at rest when the second lower reverse wheel 221 rotates in the other direction around the ninth axis O.
[0149] For example, the second reversing transmission wheel 222 rotates in the same direction when the second lower reversing wheel 221 rotates clockwise around the ninth axis 09, but does not move when the second reversing wheel lower 221 rotates counterclockwise.
[0150] As shown in Figures 2 and 6, in the first reduction mobile 230, an upper pivot 230a is kept movable in rotation by a bearing such as the perforated stone held arranged in the first automatic winding bridge 180, and a lower pivot 230b is kept movable in rotation by a bearing such as the perforated stone arranged in the second automatic winding bridge 181. The first reduction mobile 230 includes a first reduction gear element 231 which meshes with the first inverting transmission wheel 212 and the second inverting transmission wheel 222, and a first reduction pinion 232.
[0151] Since the first inverter wheel 210 and the second inverter wheel 220 are formed as described above, for example, when the first lower inverter wheel 211 is driven clockwise around the eighth axis 08 continued upon rotation of the oscillating mass 150, the first inverter transmission wheel 212 is rotated clockwise about the eighth axis 08. Thus, since the second lower inverter wheel 221 is rotated in counterclockwise around the ninth axis 09 following the rotation of the first lower inverter wheel 211, the second inverting transmission wheel 222 remains at rest. Consequently, the first reduction mobile 230 rotates counterclockwise in synchronization with the rotation of the first inverting transmission wheel 212.
On the contrary, when the first lower inverter wheel 211 is rotated counterclockwise around the eighth axis 08 due to the rotation of the oscillating mass 150, the first inverting transmission wheel 212 remains at rest. Thus, since the central lower stage wheel (second inverter wheel 221) rotates clockwise around the ninth axis 09 following the rotation of the first lower inverter wheel 211, the second inverter transmission mobile 222 rotates clockwise around the ninth axis 09. Consequently, the first reduction mobile 230 rotates counterclockwise following the rotation of the second inverting transmission wheel 222.
As described above, the first reduction mobile 230 always rotates in one direction (counterclockwise in the above case) independently of the direction of rotation of the oscillating mass 150.
[0154] In the second reduction mobile 240, an upper pivot 240a is kept movable in rotation by a bearing such as the perforated stone arranged in the first automatic winding bridge 180, and a lower pivot 240b is kept movable in rotation by a bearing such as the perforated stone disposed in the second automatic winding bridge 181. The second reduction mobile 240 includes a second reduction gear element 241 which meshes with the first reduction pinion 232 and a second reduction pinion 242. Consequently, the second reduction mobile 240 rotates synchronously with the rotation of the first reduction mobile 230.
In the third reduction mobile 250, an upper pivot 250a is kept movable in rotation by a bearing such as the perforated stone arranged in the first automatic winding bridge 180, and a lower pivot 250b is kept movable in rotation by the bearing such as the perforated stone disposed in the second automatic winding bridge 181. The third reduction gear 250 includes a third reduction gear element 251 which meshes with the second reduction pinion 242, and a third reduction pinion 252 which meshes with the ratchet wheel 45 of the first barrel 21. Consequently, the third reduction wheel set 250 rotates synchronously with the rotation of the second reduction wheel set 240, and transmits the energy generated by the oscillating mass 150 to the ratchet wheel 45.
[0156] Consequently, it is possible to rotate the ratchet wheel 45 of the first barrel 21 around the first axis 01 to arm, that is to say to wind up the mainspring 30. The direction of rotation of the winding gear automatic 170 is adjusted so that the direction of rotation of the third reduction mobile wheel 250 is the same as the direction of rotation of the intermediate crown wheel 55 of the manual winding mechanism 17.
(Operation of the cog mechanism, movement and timepiece)
In what follows, the operation of the gear mechanism 12, the movement 10 and the timepiece 1 formed as described above will be described. First, movements of the seconds hand 7, minute hand 6, and hour hand 5 will be briefly described.
In this case, the ratchet wheel 45 of the second barrel 22 shown in FIG. 2 is driven in rotation by the output torque under the impulse of the unwinding, that is to say the unwinding of the mainspring 30 in the first barrel 21 and of the mainspring 30 in the second barrel 22. Thus, the transmission wheel 110, the second mobile 60 and the third mobile 70 can be driven sequentially one after the other. Consequently, the fourth mobile 90 and the center mobile 80 can be driven in rotation via that of the third mobile 70 and the hour wheel 100 can be driven in rotation by the minute mobile. As a result, the seconds hand 7, the minute hand 6 and the hour hand 5 can be moved.
In what follows, a brief description will be given of a case where the mainspring 30 is wound up by the manual winding mechanism 17.
[0160] In this case, the winding stem 50 is actuated in rotation when it is in a state in which it is located in the "0" position. In this way, the ratchet wheel 45 of the first barrel 21 can be driven in rotation around the first axis O1 by the intermediate crown wheel 55, and the mainspring 30 can be wound up in the first barrel 21.
The first barrel structure 31 of the first barrel 21 rotates around the first axis O1 following the reassembly of the mainspring 30, so that the barrel structure 31 of the second barrel 22 rotates around the second axis 02. Consequently, the mainspring 30 in the second barrel 22 is wound up by the rotation of the barrel structure 31.
[0162] Next, a brief description will be given of a case where the mainspring 30 is wound up by the automatic winding mechanism 18.
In this case, the oscillating mass 150 rotates suitably in both directions around the central axis C, for example, according to the movements of the user's arm. The oscillating mass 150 rotates, so that the energy can be transmitted to the first lower inverter wheel 211 of the first inverter wheel 210 and the second lower inverter wheel 221 of the second inverter wheel 220 by the first inverter wheel 190 and the second inverting wheel mobile 200. Therefore, the first lower inverting wheel 211 can be rotated about the eighth axis 08, and the second lower inverting wheel 221 can be rotated around the ninth axis 09.
[0164] Accordingly, an inverting transmission wheel of the first inverting transmission wheel 212 and the second inverting transmission wheel 222 rotates in the direction of rotation of the first lower inverting wheel 211 and the second inverting wheel 220, and the other reverse gear wheel can remain at rest.
[0165] Consequently, regardless of the direction of rotation of the oscillating mass 150, the first reduction wheel 230 can always be driven in rotation in one direction. Consequently, the second reduction mobile 240 and the third reduction mobile 250 can be driven in rotation via the first reduction mobile 230, and the ratchet wheel 45 of the first barrel 21 can be driven in rotation about the first axis O1 by the third reduction mobile 250. Consequently, as in the case of the manual winding mechanism 17 described above, the mainspring 30 of the first barrel 21 can be wound up, and the mainspring 30 of the second barrel 22 can be wound up in continued.
[0166] In particular, according to the gear mechanism 12 of the present embodiment, as illustrated in FIG. 2, since the two barrels 20 (first barrel 21 and second barrel 22 forming a plurality of barrels) are arranged on the front face of the plate 11, it is possible to increase the space occupied by the two barrel structures 31 outside this zone on the front face of the plate 11. In addition, the first barrel 21 and the second barrel 22 are at the finishing gear 15 gap in a plan view of the platen 11 so as to avoid an overlap with the finishing gear 15 in the up-down direction. Accordingly, the thickness of the barrel 31 can be made as large as possible, for example, to an extent corresponding to a spacing between the plate 11 and the gear bridge 14, and the outer diameter of the barrel 31 and the ratchet wheel. 45 can be made as large as possible.
[0167] From this it is possible to prevent restrictions, for example, on the thickness and width of the mainsprings 30 in the first barrel 21 and the second barrel 22. For example, when the output torque is kept constant, the power reserve of the mainspring 30 can be improved, and when the power reserve associated with the mainspring 30 is kept constant, the output torque can be increased.
[0168] Therefore, the power reserve associated with the mainspring 30 can be improved or the output torque can be increased, and a gear mechanism 12 having excellent transmission performance in terms of output torque can be implemented. .
[0169] Consequently, the movement 10 and the timepiece 1 which are provided with the gear mechanism 12 can constitute a movement and a timepiece having high operating reliability.
[0170] Regarding the fact that the first barrel 21 and the second barrel 22 are both arranged away from the finishing gear 15 when viewed in a plan view of the plate 11, it is not provided by the invention that the teeth of the barrel 32c in the barrel structure 31 or the ratchet teeth 45a in the ratchet wheel 45 and the teeth of the wheels constituting the finishing gear 15 overlap in the direction of the plane due to of their mutual gear rotation.
For example, the teeth of the second gear wheel 62 of the second mobile 60 and the teeth of the third gear 72 of the third mobile 70 may overlap in a plane by meshing with the teeth of the barrel 32c and the ratchet teeth 45a. However, this is not intentional within the scope of the invention. Even in this case, if any overlap between the teeth of the second gear 62 or the teeth of the third gear 72 in the up-down direction with respect to, for example, the body is prevented main barrel 32, it is possible to increase the thickness of the barrel structure 31 as mentioned above.
[0172] In addition, according to the gear mechanism 12 described in the present embodiment, since the fourth mobile 90, the center mobile 80, and the hour wheel 100 are arranged coaxially with the central axis C of plate 11, this can be used as a cog mechanism 12 corresponding to what is called a direct-drive mechanism with the central second hand (with all three seconds, minutes and hours hands arranged coaxially in the center of the dial) .
[0173] Furthermore, since the energy can be transmitted from the ratchet wheel 45 of the second barrel 22 to the second mobile 60 via the transmission wheel 110, for example, it is not necessary to engage directly the ratchet wheel 45 of the second barrel 22 with the second mobile 60.
[0174] At this time, for example, when the ratchet wheel 45 of the second barrel 22 and the second mobile 60 are directly meshed with the second pinion 61 of the second mobile 60, it is necessary to reduce the diameter of the second gear wheel 62 in order to avoid, for example, interference with the second barrel 22. However, in the present embodiment, since the transmission wheel 110 is provided, the position of the second gear 61 may be moved from the second barrel 22. Therefore, it is possible to increase the diameter of the second gear wheel 62, and it is possible to contribute to an increase in the speed increase ratio of the whole finishing gear. 15.
[0175] In this way, by arranging a transmission wheel 110, the second mobile 60 can be arranged in a position remote from the second barrel 22, and the diameters of the second pinion 61 of the second mobile 60 and of the second gear wheel 62 can be freely selected with few restrictions, thus improving the degree of freedom in the design of the movement. In addition, the gear ratios determining the speed of the finishing gear 15 can be increased.
[0176] As described above, in the transmission wheel 110, the transmission gear wheel 111 is arranged in the same plane as the ratchet wheel 45, and the axis on which the upper pivot 110a and the pivot lower 110b are formed is arranged in a position remote from the second barrel 22. Therefore, the transmission wheel 110 is unlikely to affect the thickness of the second barrel 22.
[0177] Further, as shown in Fig. 4, the transmission wheel 110 is supported by the overhanging flange 11a, such that the transmission wheel 110 is arranged upward and overhangs the second gear wheel 62. Therefore, in combination with using the transmission wheel 110 described above, the outer diameter of the second gear wheel 62 can be freely chosen with few restrictions, and the degree of freedom in terms of gear increase ratio selection can be improved.
[0178] In addition, since it is possible to adjust the length of the axis of the transmission wheel 110 such that a distance between the transmission gear wheel 111 towards the upper pivot 110a and the pivot lower 110b are substantially equal, it is easy to evenly distribute the load to the upper pivot 110a and the lower pivot 110b, and it is possible to prevent the load from being concentrated on either pivot.
[0179] Therefore, since it is possible to prevent one of the pivots from wearing out too quickly and there is no need to increase the diameter of the pivots, durability of the transmission wheel 110 can be improved. improved, and the output torque transmission efficiency can be improved.
[0180] In addition, since the third mobile 70, the fourth mobile 90, the center mobile 80, the hour wheel 100, and the like are arranged closer to the plate 11 than the virtual surface V with respect to the second mobile 60 , in the central part of the stage 11, the finishing gear 15 can be arranged in a position close to the stage 11 while keeping the height of the timer gear low, and the overall height can be kept at a reduced level. Therefore, in addition to facilitating the arrangement of other timepiece components in the central part of the plate 11, it is possible to prevent the timepiece 1 from having a protruding central part, for example.
[0181] In particular, since the third mobile 70 is arranged closer to the plate 11, the second gear wheel 62 can be made to mesh with the third pinion 71 of the third mobile 70 in a position closer to that of the third gear 72 as the center gear 82. Therefore, the second gear 62 can be meshed with the third gear 71 near the center portion in the axial direction. of the third axis 73 of the third mobile 70.
[0182] During normal needle movement, since the output torque of the second mobile 60 is transmitted to the third mobile 70 via the gear between the second gear wheel 62 and the third pinion 71 of the third mobile 70, a large load acts at the gear part between the second gear 62 and the third gear 71. Even so, since the second gear 62 meshes with the third gear 71 near the part central in the axial direction of the third axis 73, it is easy to distribute the load uniformly between the upper pivot 70a and the lower pivot 70b of the third mobile 70. Consequently, it is possible to prevent the load from being concentrated on the 'one or the other of the pivots, and it is possible to prevent one of the pivots from wearing out too quickly. Therefore, the durability of all of the third mobile 70 and all of the finishing gear 15 can be improved, and the third mobile 70 can be rotated stably and precisely.
[0183] Since the third mobile 70 is rotated in a stable and precise manner in this way, the center mobile 80 and the fourth mobile 90 which mesh with the third mobile 70 can also be rotated with great precision while at the same time. avoiding, for example, jerks, and it is possible to prevent deviation of instruction for displaying time information or the like, while allowing proper movement of the hands.
[0184] In addition, the gear position between the central gear wheel 82 and the third pinion 71 of the third mobile 70, the gear position between the second gear wheel 62 and the third pinion 71, and the Gear part between the third gear wheel 72 and the fourth pinion 92 of the fourth mobile 90 are arranged in this order viewed from the platen side 11. Therefore, the energy transmitted from the second mobile 60 to the third mobile 70 can be transmitted. to the central gear wheel 82 and to the fourth wheel pinion 92 in a balanced manner while being dispersed in the axial direction of the third axis 73.
[0185] In addition, by using the space S secured by arranging the third mobile 70, the fourth mobile 90, the center mobile 80, the hour wheel 100 and the like closer to the plate 11 than the virtual surface V, the automatic winding mechanism 18 is arranged so as to provide the timepiece 1 with an additional function. Therefore, it is possible to contribute to the versatility of timepiece 1.
[0186] In particular, since the automatic winding mechanism 18 is arranged by effectively using the space S, it is possible to prevent the central portion of the timepiece 1 from protruding, and it is thus possible to put implementing a timepiece 1 having versatility and excellent aesthetic appearance. Therefore, it is possible to prevent the timepiece 1 from having the appearance of an industrial design.
[0187] Further, while the outer ring 153 is arranged using the space S, the height of the outer ring 153 can be secured as shown in Fig. 5. Therefore, the length of the axis of the first inverting freewheel 190 which meshes with the oscillating weight pinion 153a of the self-winding gear train 170 can be adjusted to a length which forms the upper pivot 190a and the lower pivot 190b. Accordingly, it is possible to keep rotatably movable (by providing rotational guidance) of the first inverting freewheel 190 by using the upper pivot 190a and the lower pivot 190b.
[0188] When the pivots (upper pivot 190a and lower pivot 190b) cannot be produced due to the short length of the axis of the first inverting freewheel 190, a pin guide is often used. In the case of the pin, since there is a limit to the reduction in diameter, the frictional resistance is important and power loss is likely to occur. On the other hand, in the present embodiment, since the upper pivot 190a and the lower pivot 190b can be formed by ensuring the length of the axis of the first inverter wheel 190 as described above, the diameters of the upper pivot 190a, the lower pivot 190b and the like can be reduced, the friction resistance can be reduced, and the transmission efficiency can be improved.
[0189] In addition, as shown in Figure 2, since the outer ring 153 is also away from the first barrel 21 and the second barrel 22 in a plan view, the thickness of the barrel structure 31 can be increased without being affected by the outer ring 153, and the outer diameters of the barrel structure 31 and the ratchet wheel 45 can be increased.
[0190] In addition, since the automatic winding mechanism 18 is arranged on the opposite side of the finishing gear 15 with respect to the second virtual line L2 connecting the intermediate position P located on the first virtual line L1 and the central axis C of plate 11, the automatic winding mechanism 18 can be arranged in a balanced manner with respect to the finishing gear 15 while using the space S, which can contribute, for example, to a reduction in the total thickness of the part d 'watchmaking 1.
[0191] The preferred embodiment of the invention described above was only by way of example, and is not intended to be interpreted in a limiting manner in order to define the scope of the invention. Other embodiments could be embodied in a variety of other forms, and various omissions, substitutions and changes could be made without departing from the spirit of the invention. The embodiment and its variations include, for example, modifications which can be readily devised by those skilled in the art, those which are substantially identical to the features described above, and those which would fall within the scope of equivalents.
For example, in the embodiment described above, the gear mechanism 12 including two barrels 20 (first barrel 21 and second barrel 22) is given by way of example. The number of barrels of the plurality of barrels 20, however, is not limited to two, and three or more barrels could be envisioned.
In the above embodiment, an example is described according to which the barrel structure 31 of the first barrel 21 and the barrel structure 31 of the second barrel 22 are in mutual gear engagement. The invention is not however limited to such a configuration, and, for example, the ratchet wheel 45 of the first barrel 21 and the ratchet wheel 45 of the second barrel 22 could be brought into mutual gear engagement.
[0194] In this case, for example, the intermediate crown wheel 55 and the third reduction wheel 250 can mesh with the barrel structure 31 of the first barrel 21, and the transmission wheel 110 can mesh with the barrel structure 31 of the second barrel 22. In this configuration, the same operation and the same operational benefits can be obtained.
[0195] Furthermore, the first barrel 21 and the second barrel 22 cannot be brought into direct mutual meshing through the barrel structure 31 or the ratchet wheel 45 of the first barrel 21 and of the second barrel 22. For example, the first barrel 21 and the second barrel 22 can mesh indirectly through an intermediate wheel such as a reference. Even in this case, the same operation can be obtained and the same effects can be achieved.
[0196] In the above embodiment, in the first barrel 21 and the second barrel 22, the ratchet wheel shaft 40 is used to secure the ratchet wheel 45 to the barrel structure 31. However, the ratchet wheel shaft 40 is used to secure the ratchet wheel 45 to the barrel structure 31. The invention is not limited to such a case. For example, the ratchet wheel 45 and the barrel structure 31 can be attached to each other by screws, or the ratchet wheel 45 can be placed on the barrel shaft 35 or the barrel structure 31. without fixing.
[0197] In the embodiment described above, the transmission wheel 110 is not essential and could not be provided. In this case, the second pinion 61 of the second mobile 60 can mesh directly with the ratchet wheel 45 of the second barrel 22.
Furthermore, in the above embodiment, the case of the direct drive seconds hand is given only by way of example in which the seconds hand 7 is fixed directly to the fourth mobile 90. However, the invention is not limited to such a case. For example, the seconds hand 7 arranged in a position offset from the central axis C of the plate 11 can be driven by the fourth mobile 90 via another timepiece component. In addition, energy can be transmitted from the fourth mobile 90 to other timepiece components.
In the embodiment described above, the self-winding timepiece 1 is given only by way of example. However, the invention is not limited to such a configuration, and the automatic winding mechanism 18 cannot be provided.
[0200] For example, as shown in FIG. 8, a timepiece 300 can be provided with a cog mechanism 301 which does not include the automatic winding mechanism 18 described above. Notably, in this case, since the space S guaranteed above the virtual surface V can be vacant as shown in figure 9, the space S can be effectively used to provide some additional functional units in place of the mechanism of automatic winding 18. For example, a power reserve mechanism including a power reserve gear can be provided to clearly indicate information (amount of power reserve) relating to a level of winding of the mainspring 30 according to the amount of winding. reassembly carried out.

权利要求:
Claims (11)
[1]
1. Gear mechanism (12), comprising:a plurality of barrels (20) including a barrel (22) in which is housed a mainspring (30) and which is rotated about an axis during the unwinding of the mainspring (30), and a ratchet wheel ( 45) which is rotatable about this axis with respect to the barrel during the unwinding of the mainspring (30); anda finishing gear train (15) which is arranged at the front of a plate (11) and which is driven in rotation under the action of the unwinding of the mainspring (30),the plurality of barrels (20) being arranged at the front of the stage (11) in a state of mutual gear, and the barrels being spaced apart from each other when viewed in a direction perpendicular to the plane of the stage (11), andeach of the plurality of barrels (20) being arranged also away from the finishing gear (15) according to the plane of the plate (11), so that any superposition in the direction of thickness is avoided with respect to the finishing gear (15) vis-à-vis the plate (11).
[2]
2. cog mechanism (12) according to claim 1, whereinthe finishing gear (15) includes at leasta second mobile (60) which is driven in rotation under the action of the unwinding of the mainspring (30),a third mobile gear (70) which is rotated under the action of that of the second mobile (60), anda fourth mobile (90) which is rotated under the action of that of the third mobile gear (70),the fourth mobile (90) being arranged coaxially with a central axis (C) of the plate (11), away from the plurality of barrels (20) in the plane of the plate (11), andthe second mobile (60) and the third mobile (70) gear being arranged in offset positions with respect to the central axis (C) in a direction extending in the plane of the plate (11) , and away from the plurality of barrels (20) also in a view in this plane.
[3]
3. cog mechanism (12) according to claim 2, whereina transmission wheel (110) which meshes with the barrel or the ratchet wheel (45) and the second mobile (60), and which transmits the energy generated by the unwinding of the mainspring (30) to the second mobile, is arranged between any one of the barrels among the plurality of barrels (20) and the second mobile (60).
[4]
4. cog mechanism (12) according to claim 2 or 3, whereinthe third mobile (70) includesa third axis (73) comprising an upper pivot (70a) and a lower pivot (70b), anda third pinion (71) which is formed on the third axis (73) and which meshes with a second gear wheel (62) of the second mobile (60), andthe second gear wheel (62) meshes with the third pinion (71) at a central part in the axial direction of the third axis (73).
[5]
5. A cog mechanism (12) according to claim 4, further comprising:a center mobile (80) which is arranged coaxially with the central axis (C) of the plate (11) and which includes a central gear wheel (82) meshing with the third pinion (71) of the third mobile (70),the third mobile (70) including a third gear wheel (72) which is formed on the third axis (73) and which meshes with a fourth pinion (92) of the fourth mobile (90), andthe central gear wheel (82) and the third gear (71) mesh in a position closer to the turntable relative to the meshing position of the second gear (62) which meshes with the third gear ( 71), and the third gear wheel (72) and the fourth pinion (92) mesh in a position farther from the plate (11) than the second gear wheel (62).
[6]
6. cog mechanism (12) according to one of claims 2 to 5, whereinthe third mobile (70) and the fourth mobile (90) are arranged closer to the plate (11) than a virtual surface parallel to the barrel cover in the barrel.
[7]
7. cog mechanism (12) according to claim 6, whereina space (S) is provided on the opposite side of the plate (11) from the virtual surface in the direction of the thickness of the plate (11), andan additional functional unit is arranged in this space (S).
[8]
8. A cog mechanism (12) according to claim 7, whereinthe additional functional unit is an automatic winding mechanism (18) including:an oscillating mass (150) which is rotatably mounted about an axis of rotation, andan automatic winding gear (170) which transmits the energy resulting from the rotation of the oscillating weight (150) to any one of the plurality of barrels (20), and rotates said plurality of barrels (20) in one sense,the oscillating mass (150) being arranged coaxially with the axis of rotation, and includes a bearing (151) having an outer ring (153) on which is arranged an oscillating mass pinion (153a) which meshes with the gear train. automatic winding (170), andthe outer ring (153) being arranged away from the barrels (20) according to a view in the plane of the plate, thus avoiding any overlap in the thickness direction with respect to the barrels (20).
[9]
9. cog mechanism (12) according to claim 7 or 8, comprising:two barrels (21,22), and in whichthe additional functional unit is arranged on the opposite side of the finishing gear (15) vis-à-vis a second virtual line connecting the central axis (C) of the plate (11) and an intermediate position which is located on a first virtual line connecting the centers of two barrels (21,22) in a plan view of the plate (11) and located between the centers of the barrels (21,22).
[10]
10. Movement comprising:the cog mechanism (12) according to one of claims 1 to 9.
[11]
11. Timepiece comprising:the movement according to claim 10.

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同族专利:

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公开号 | 公开日

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CN113189855A|2021-07-30|

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JP6730538B1|2020-07-29|

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JP2021117196A|2021-08-10|

引用文献:

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公开号 | 申请日 | 公开日 | 申请人 | 专利标题

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法律状态:

优先权:

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申请号 | 申请日 | 专利标题

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JP2020012705A|JP6730538B1|2020-01-29|2020-01-29|Wheel train mechanism, movement and clock|

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