Constant torque mechanism, timepiece movement, and timepiece.

专利摘要:
The invention relates to a constant torque mechanism (30) comprising a support rotating around a first axis (O1) using energy supplied by an energy source; a planetary gear wheel (45) rotatably mounted on the support and performing a complete revolution around the first axis (O1) while turning around a second axis (O2); a constant force spring (100) supplied with energy by the rotation of the support; a constant force wheel (60) rotating with the energy of the constant force spring (100) and transmitting the energy of the constant force spring (100) to an exhaust; a synchronous rotary part rotating in a first direction of rotation about the first axis (O1) in synchronization with the rotation of the constant force wheel (60); and an engagement claw (86) rotating in the first direction of rotation in accordance with the rotation of the synchronous rotating part, which can engage and disengage from the planetary gear wheel (45). The engagement claw (86) engages the planetary gear wheel (45) to restrict rotation of the planetary gear wheel (45), and is then moved relative to the synchronous rotating portion to ability to remove from planetary gear wheel (45). The invention also relates to a timepiece movement comprising such a mechanism and a timepiece comprising such a movement.
公开号:CH715052A2
申请号:CH00777/19
申请日:2019-06-07
公开日:2019-12-13
发明作者:Mori Yuichi；Fujieda Hisashi
申请人:Seiko Instr Inc；
IPC主号:

专利说明:

Description
BACKGROUND OF THE INVENTION
1. Field of the invention The present invention relates to a constant torque mechanism, a timepiece movement, and a timepiece.
2. Description of the Prior Art [0002] Generally, in a mechanical timepiece, when a torque (energy) transmitted from a movement barrel to an escapement varies according to the degree of winding of the mainspring, the angle The balance of oscillation of the balance spring changes according to the fluctuation of the torque, causing a change in the running of a timepiece, that is to say a delay or a certain advance of the timepiece. Consequently, constant torque mechanisms are known for energy transmission channels from the movement barrel to the exhaust in order to suppress any fluctuation in the torque transmitted to the exhaust.
Different types of constant torque mechanism of this type are proposed and, for example, in the case where we focus on periodic control, we can mainly classify them into three systems consisting of: cam systems, systems using gear trains, and planetary wheel systems.
The constant torque mechanism based on a cam system comprises, for example, a follower or a fork engaging with a cam connected to a gear train on the side of the exhaust and oscillating according to the rotation of the cam, and periodically engaging and disengaging from an engagement and disengagement claw provided on the follower or the fork and which cooperates with an escape wheel kinematically connected to a cog arranged on the side of the energy source for control an engagement and disengagement cycle. Therefore, it is possible to wind a constant torque spring between the cog located on the side of the power source and the cog located on the side of the exhaust.
In the constant torque mechanism based on a gear train system, the cog located on the side of the power source and the cog located on the exhaust side are connected together by a differential mechanism, and the engagement and disengagement claw engaging with a stop wheel and then disengaging itself therefrom, penetrates inside the disc corresponding to the envelope of the stop wheel, and leaves the latter, so that it is possible to periodically check a phase difference.
For example, as described in the Swiss patent application CH A 296,060 (patent document 1) and the Swiss patent application CH A 707,938 (patent document 2), the constant torque mechanism using a planetary wheel includes a planetary mechanism using the stop wheel as a planetary wheel, and it is possible to periodically check the phase difference between the cog located on the side of the power source, and the cog located on the exhaust side by the planetary mechanism. The planetary wheel performs a complete revolution around a solar wheel while turning on itself to follow the engagement and release claw provided in the solar wheel kinematically connected to the cog located on the side of the exhaust in order to put periodically engaged with the engagement and release claw, then to release it.
Meanwhile, in the constant torque mechanism based on a planetary wheel system, in a state where the tip of a tooth of the planetary wheel and the engagement and release claw are in mutual contact, the direction of the force applied between the planetary wheel and the engagement and release claw is located along a normal direction of the contact portion between the planetary wheel and the engagement and release claw. Therefore, immediately before the planetary wheel and the engagement and disengagement claw are released from each other, in a state where the tooth tip of the planetary wheel and a corner of the engagement claw and release are in mutual contact, the direction of the force applied between the planetary wheel and the engagement and release shoe approaches the direction of rotation of the engagement and release shoe. Consequently, a torque transmitted from the solar wheel fitted with the engagement and release claw to the exhaust increases and the oscillation angle of the balance spring changes.
SUMMARY OF THE INVENTION According to one aspect of the present invention, the patent application aims to provide a constant torque mechanism, a timepiece movement and a timepiece in which any fluctuation in torque transmitted to an exhaust is removed.
The constant torque mechanism according to this aspect of this patent application comprises a support rotating around a first axis using energy supplied by an energy source; a planetary gear wheel being rotatably mounted on the support and making a complete revolution around the first axis while rotating around a second axis; a constant force spring being supplied with energy by the rotation of the support; a constant force wheel rotating thanks to the energy of the constant force spring and transmitting the energy of the constant force spring to an exhaust; a synchronous rotary part rotating in a first direction of rotation around the first axis in
CH 715 052 A2 synchronization with the rotation of the wheel at constant force; and an engagement claw rotating in the first direction of rotation in accordance with the rotation of the synchronous rotating portion, capable of engaging and releasing from the planetary gear wheel, engaging the wheel planetary gear when in a rotation casing of the planetary gear wheel to restrict rotation of the planetary gear wheel, and then being moved relative to the synchronous rotating portion so that it can be removed outside the rotation envelope.
According to this configuration, the engagement claw is moved relative to the synchronous rotary part so as to withdraw outside the rotation envelope of the planetary gear wheel, so that it is possible reduce the torque transmitted, in the first direction of rotation, from the planetary gear wheel to the synchronous rotating part via the engagement claw immediately before the clearance between the planetary gear wheel and the engagement claw. Therefore, it is possible to suppress any fluctuation in the torque transmitted from the synchronous rotating part to the exhaust via the constant force wheel. Therefore, it is possible to suppress the fluctuation of the torque transmitted to the exhaust.
In the constant torque mechanism according to the invention, it is desirable that the engagement claw is moved in a direction extending along the first direction of rotation relative to the synchronous rotary part to withdraw from the 'rotation envelope.
According to this configuration, when the direction of the force applied between the planetary gear wheel and the engagement claw immediately before the disengagement of the planetary gear wheel relative to the engagement claw approaches the first direction of rotation, the engagement claw is compressed by the planetary gear wheel and the engagement claw can be moved relative to the synchronous rotating part. Thus, the torque in the first direction of rotation transmitted from the planetary gear wheel to the synchronous rotating part via the engagement claw is reduced by the displacement of the engagement claw. Therefore, it is possible to suppress the fluctuation of the torque transmitted from the synchronous rotating part to the exhaust via the constant force wheel.
In the constant torque mechanism according to the invention, it is desirable that the constant torque mechanism further comprises a spring directly or indirectly compressing the engagement claw towards the inside of the rotation casing.
According to this configuration, it is possible to eliminate the fact that one can remain in a state in which the engagement claw is in a retracted position where it no longer encroaches on the rotation casing of the wheel. planetary gear. Thus, it is possible to functionally stabilize the engagement and disengaging operation of the engagement claw with respect to the planetary gear wheel.
In the constant torque mechanism according to the invention, it is desirable that the constant torque mechanism further comprises a lever body which rotatably carries the engagement claw relative to the synchronous rotary part, and being arranged dissociated from the spring.
According to this configuration, it is possible to stably support the engagement claw compared to the case where the engagement claw is supported by the part formed by the spring itself. Consequently, it is possible to stabilize the movement of the engagement claw with respect to the synchronous rotary part and functionally stabilize the engagement and disengagement operation of the engagement claw with respect to the gear wheel. planetary.
In the constant torque mechanism according to the invention, it is desirable that the engagement claw is supported by the spring.
According to this configuration, it is possible to reduce the number of components compared to the case of a configuration in which the engagement claw is not supported directly by the spring.
In the constant torque mechanism according to the invention, it is desirable that the synchronous rotary part comprises a first limiting part restricting the movement of the engagement claw, when it is engaged with the gear wheel planetary, in a direction along a second direction of rotation about the first axis relative to the synchronous rotating part.
According to this configuration, when the engagement claw rotates in the first direction of rotation with the synchronous rotating part, the engagement claw moves in the direction corresponding to the second direction of rotation opposite to the first direction of rotation with respect to the synchronous rotating part, so that it is possible to prevent the fact that the engagement claw can no longer be released from the planetary gear wheel. Therefore, it is possible to functionally stabilize the engagement and disengaging operation of the engagement claw with respect to the planetary gear wheel.
In the constant torque mechanism according to the invention, it is desirable that the synchronous rotary part comprises a second limiting part restricting the movement of the engagement claw in a retracted position outside the rotation envelope according to a direction corresponding to the first direction of rotation relative to the synchronous rotating part.
According to this configuration, when the engagement claw is withdrawn outside the rotation casing of the planetary gear wheel, the engagement claw moves in the direction corresponding to the first direction of rotation by
CH 715 052 A2 relative to the synchronous rotating part, but in such a way that it is possible to prevent the fact that the engagement claw can no longer penetrate again within the rotation casing of the wheel planetary gear and end up in the engagement position. Therefore, it is possible to functionally stabilize the engagement and disengaging operation of the engagement claw with respect to the planetary gear wheel.
In the constant torque mechanism according to the invention, it is desirable that the engagement claw is arranged so as to be able to oscillate around the first axis relative to the synchronous rotating part.
According to this configuration, a shaft extending along the first axis and supporting the synchronous rotary part can be used as a shaft which movably supports an element to which the engagement claw is attached relative to the synchronous rotary part . On the other hand, in a case where the engagement claw is arranged so as to be able to oscillate around an axis different from the first axis relative to the synchronous rotary part, it is necessary to supply the shaft disposed on the axis different from the first axis in the synchronous rotary part since the shaft movably supporting the element to which the engagement claw is fixed relative to the synchronous rotary part. Consequently, it is possible to reduce the number of components compared to the case where the engagement claw is arranged so as to be able to oscillate about an axis different from the first axis relative to the synchronous rotating part.
In the constant torque mechanism according to the invention, it is desirable that the engagement claw is arranged so as to be able to oscillate around a third axis different from the first axis and the second axis relative to the rotary part synchronous.
According to this configuration, since a rotary shaft for the engagement claw is disposed on a third axis different from the first axis, it is possible to improve the degree of freedom in the design of the constant torque mechanism. A timepiece movement according to this patent application includes the constant torque mechanism described above.
A timepiece according to the present patent application comprises the timepiece movement described above.
In such a configuration, since a constant torque mechanism is provided in which a fluctuation in the torque transmitted to the exhaust is eliminated, it is possible to provide a movement of a timepiece and a timepiece with high precision.
According to one aspect of this patent application, it is possible to provide a constant torque mechanism, in which any fluctuation in the torque transmitted to the exhaust is eliminated, as well as such a movement of a timepiece, and such a timepiece.
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is an external view of a timepiece according to a first embodiment.
Fig. 2 is a functional diagram of a movement according to the first embodiment.
Fig. 3 is a perspective view of part of the movement according to the first embodiment taken from above.
Fig. 4 is a sectional view illustrating part of the movement according to the first embodiment.
Fig. 5 is a plan view of part of the movement of the first embodiment taken from above.
Fig. 6 is a plan view of an engagement and disengagement lever unit according to the first embodiment taken from above.
Fig. 7 is a sectional view illustrating the engagement and disengagement lever unit of the first embodiment.
Fig. 8 is a perspective view of a planetary wheel and the engagement and disengagement lever unit of the first embodiment taken from above.
Fig. 9 is a perspective view of the planetary wheel and the engagement and disengagement lever unit of the first embodiment taken from below.
Fig. 10 is a plan view of part of a constant torque mechanism of the first embodiment seen from above.
Fig. 11 is an explanatory view of the operation of the constant torque mechanism of the first embodiment.
CH 715 052 A2
Fig. 12 is an explanatory view of an operation of the constant torque mechanism according to the first embodiment.
Fig. 13 is an explanatory view of the operation of the constant torque mechanism according to the first embodiment.
Fig. 14 is an explanatory view of the operation of the constant torque mechanism according to the first embodiment.
Fig. 15 is a plan view of a planetary wheel and an engagement and disengagement lever unit according to a second embodiment, according to a view taken from above.
Fig. 16 is an explanatory view of the operation of a constant torque mechanism according to the second embodiment.
Fig. 17 is a plan view of a planetary wheel and an engagement and disengagement lever unit according to a third embodiment according to a view taken from above.
Fig. 18 is an explanatory view of the operation of a constant torque mechanism according to the third embodiment.
Fig. 19 is a plan view of a planetary wheel and an engagement and disengagement lever unit according to a fourth embodiment as seen from above.
Fig. 20 is an explanatory view of an operation of a constant torque mechanism according to the fourth embodiment.
DESCRIPTION OF THE EMBODIMENTS Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, the same reference numbers are given to the configurations having the same or similar functions. In the embodiment which follows, a mechanical timepiece will be described as an example for a timepiece.
[First embodiment] [Basic configuration of the timepiece) Generally, reference is made to the mechanical body comprising a drive part for the timepiece as being a “ movement". We are referring to a state in which a dial and hands are attached to the movement, placed in a timepiece box, and assembled to form a finished product as constituting an "assembly" of the timepiece.
Among the two faces of a plate constituting a base plate of the timepiece, reference is made to the side provided with the glass closing the case of the timepiece (that is to say, the dial side) as the “back side” of the movement. Furthermore, among the two faces of the plate, reference is made to the side having the bottom of the case of the timepiece (that is to say, the side opposite to the dial) as being the "front face" of the movement.
In addition, according to the embodiment described, a description is given in which the direction going from the dial towards the bottom of the case is defined as being the direction "upwards" and the direction opposite to it is defined as being the "down" direction. Further, the direction going clockwise seen from above is defined as clockwise and the direction going counterclockwise seen from above is defined as being counterclockwise taking each axis of rotation as the center.
[0038] FIG. 1 is an external view of the timepiece according to the first embodiment.
As illustrated in FIG. 1, a set of a timepiece 1 according to this embodiment comprises a movement 10 (the movement of the timepiece), a dial 3 having indicators indicating information linked at least to the current time, and hands 4 including an hour hand 5, a minute hand 6, and a second hand 7 in the case of the timepiece consisting of a case back (not shown) and a crystal 2.
[0040] FIG. 2 is a block diagram of the movement according to the first embodiment.
As illustrated in FIG. 2, the movement 10 comprises a movement barrel 11 which constitutes a source of energy, a cog located on the side of the energy source 12 connected to the movement barrel 11, an escapement 14 whose speed is controlled by a speed regulator speed 13, a cog located on the side of the exhaust 15 connected to the exhaust 14, and a constant torque mechanism 30 disposed between the cog located on the side of the power source 12 and the cog located on the side of the exhaust 15.
CH 715 052 A2 In addition, the constant torque mechanism 30 generally constitutes part of a front wheel train including a second mobile, a third mobile, a fourth mobile, and the like. The cog located on the side of the energy source 12 according to the embodiment described is a cog positioned on the side of the barrel of the movement 11, which is the energy source of the constant torque mechanism 30, seen from the torque mechanism constant 30. Similarly, the cog located on the side of the escapement 15 according to the embodiment described is a cog positioned on the side of the escapement 14 relative to the constant torque mechanism 30, seen from the constant torque mechanism 30.
A mainspring 16 is housed in the barrel of the movement 11. The mainspring 16 is wound up by the action of the rotation of a winding stem (not shown) connected to a crown 17 illustrated in FIG. 1. The barrel of the movement 11 rotates with an energy (torque) which is a function of the unwinding of the mainspring 16, and the energy is transmitted to the constant torque mechanism 30 via the train situated on the side of the energy source 12. In addition, in this embodiment, the case where energy is transmitted from the movement barrel 11 to the constant torque mechanism 30 via the gear train located on the side of the energy source 12 is described by way of example, but the present invention is not limited to such a case. For example, the energy of the movement barrel 11 can be directly transmitted to the constant torque mechanism 30 without the cog located on the side of the energy source 12.
For example, the cog located on the side of the energy source 12 comprises a first transmission wheel 18. The first transmission wheel 18 is, for example, the third mobile. The first transmission wheel 18 is supported essentially between a plate 23 (see fig. 4) and a gear train (not shown). The first transmission wheel 18 rotates on the basis of the rotation of the movement barrel 11. In addition, when the first transmission wheel 18 rotates, a pinion (not shown) rotates on the basis of this rotation. The minute hand 6 illustrated in fig. 1 is attached to the pinion and the minute hand 6 displays the current minutes via the rotation of the pinion. The minute hand 6 rotates at a speed controlled by the escapement 14 and the speed regulator 13, that is to say by carrying out one complete revolution in one hour.
In addition, when the first transmission wheel 18 rotates, a minute wheel (not shown) rotates on the basis of this rotation and an hour wheel (not shown) rotates on the basis of the rotation of the wheel of minutes. The hour hand 5 illustrated in fig. 1 is attached to the hour wheel and the hour hand 5 indicates the current time via the rotation of the hour wheel. The hour hand 5 rotates at a speed controlled by the exhaust 14 and the cruise control 13, and performs, for example, a revolution in 12 hours.
The cog located on the side of the exhaust 15 mainly comprises a second transmission wheel 19. The second transmission wheel 19 is, for example, the fourth mobile. The second transmission wheel 19 is essentially supported between the plate 23 and the gear train, and rotates on the basis of the rotation of a lower level constant force wheel 60 of the constant torque mechanism 30, which will be described later. . In the case where the second transmission wheel 19 is the fourth mobile, the second hand 7 illustrated in FIG. 1 is fixed to the second transmission wheel 19 and the second hand 7 indicates the current seconds on the basis of the rotation of the second transmission wheel 19. The second hand 7 rotates at a rotation speed controlled by l exhaust 14 and cruise control 13 to effect, for example, a complete revolution in one minute.
The exhaust 14 mainly includes an exhaust mobile and an anchor (neither of which is shown).
The exhaust mobile is essentially supported between the plate 23 and the gear train, and, for example, meshes with the second transmission wheel 19. Consequently, the energy transmitted from a constant force spring 100 described later in the constant torque mechanism 30 is transmitted to the exhaust mobile via the gear train located on the side of the exhaust 15. Consequently, the exhaust mobile rotates with the energy of the constant force spring 100.
The anchor is pivotally mounted (that is to say so as to be able to oscillate) between the plate 23 and an anchor bridge (not shown), and has a pair of claws made in the form of stones ( not shown). The pair of claws in the form of stones is alternately engaged with an exhaust gear, and released from the latter by the speed regulator 13 in the exhaust mobile according to a predetermined cycle. Consequently, the exhaust mobile is capable of operating according to a predetermined cycle.
The speed regulator 13 mainly comprises a balance spring (not shown).
The balance spring comprises a balance shaft, a balance wheel, and a balance spring, and is essentially supported between the plate 23 and a balance bridge (not shown). The balance spring rotates reciprocally (forward and reverse rotation) at a constant angle of rotation with the balance spring as a source of energy.
(Configuration of the constant torque mechanism) [0053] The constant torque mechanism 30 is a mechanism for suppressing any fluctuation in energy (fluctuation in torque) transmitted to the exhaust 14.
FIG. 3 is a perspective view of part of the movement of the first embodiment, seen from above.
CH 715 052 A2 As illustrated in fig. 3, the constant torque mechanism 30 comprises a fixed wheel 31 having a first axis of rotation O1 extending vertically as a central axis, a constant level upper force wheel 40 rotating around the first axis of rotation O1, the lower level constant force wheel 60 (constant force wheel) arranged coaxially with the higher level constant force wheel 40 and capable of rotating relative to the higher level constant force wheel 40 around the first axis of rotation O1 , an engagement and disengagement lever unit 80 cooperating with the upper level constant force wheel 40 and the lower level constant force wheel 60, the constant force spring 100 transmitting accumulated energy to the constant force wheel upper level 40 and the constant force wheel lower level 60, and a torque adjustment mechanism 110 for adjusting the torque of the constant force spring 1 00. The first axis of rotation O1 is arranged in an offset position in the plane of the plate 23 (see fig. 4) relative to the axes of rotation of the first transmission wheel 18 and the second transmission wheel 19 (see fig. 2) which are described above.
FIG. 4 is a sectional view illustrating part of the movement of the first embodiment.
As illustrated in FIG. 4, the fixed wheel 31 is disposed between the plate 23 and a constant force unit bridge 24. The constant force unit bridge 24 is disposed above the plate 23. The fixed wheel 31 includes a tubular body 32 arranged coaxially with the first axis of rotation O1 and a main wheel body 33 formed integrally with the tubular body 32.
The tubular body 32 is fixed to a lower surface of the constant force unit bridge 24 by a fixed wheel pin 34 projecting downwards from the constant force unit bridge 24. A central hole 35 and a window 36 are formed in the tubular body 32. The central hole 35 extends vertically with a constant internal diameter with the first axis of rotation O1 for the center, and vertically penetrates the tubular body 32. The window 36 is adjacent to the central hole 35 along the direction of alignment between the first axis of rotation O1 and the axis of rotation of the first transmission wheel 18 when the latter are seen from a vertical direction (see FIG. 3). The window 36 penetrates the tubular body 32 in the vertical direction and extends the central hole 35 continuously. Therefore, a vertically penetrating hole inside the fixed wheel 31 is an oblong hole when viewed in the vertical direction.
The main wheel body 33 is formed coaxially with the first axis of rotation O1 and projects from a lower end of the tubular body 32 outward in a radial direction. Fixed teeth 33a are formed over the entire periphery of an external peripheral surface of the main wheel body 33. In other words, the fixed wheel 31 is a toothed wheel whose teeth are formed towards the outside.
The upper level constant force wheel 40 is pivotally mounted between the plate 23 and the constant force unit bridge 24. The upper level constant force wheel 40 comprises a rotation shaft 41 rotating around the first axis O1, a planetary wheel 43 pivoting around the first axis of rotation O1, and a support 47 essentially supporting the planetary wheel 43.
The rotation shaft 41 extends along the first axis of rotation O1. The rotation shaft 41 is essentially supported by the plate 23 and the constant force unit bridge 24 via hole stones 25A and 25B. Hole stones 25A and 25B are formed, for example, into an artificial stone such as ruby. In addition, the 25A and 25B hole stones are not limited to the case of being formed from an artificial stone, but can for example be formed from other fragile materials or from metallic materials such as iron-based alloys. A constant force upper pinion 41 a is formed in an upper part of the rotation shaft 41. The constant force upper pinion 41 meshes with the first transmission wheel 18. Consequently, the energy is transmitted from the barrel movement 11 via the gear train located on the side of the energy source 12 (see the two in fig. 2) towards the rotation shaft 41. The energy of the torque Tb is transmitted from the movement barrel 11 to the rotation shaft 41. Hereinafter, reference is made to the torque Tb as the rotation torque Tb of the movement barrel 11. The rotation shaft 41 rotates clockwise under the impulse of the energy transmitted from the barrel of the movement 11.
Here, a recess 27, which is hollowed out from the axis of rotation of the first transmission wheel 18 in the direction of the first axis of rotation O1, is formed in at least elements chosen from the unit bridge to constant force 24 and the tubular body 32. In the embodiment described, the recess 27 is formed so as to extend both on the bridge of constant force unit 24 and on the tubular body 32. The recess 27 is open in the direction of the axis of rotation of the first transmission wheel 18. A part of the constant-force upper pinion 41 a is disposed inside the recess 27. Consequently, when the movement 10 is assembled, even in a state where the constant force unit bridge 24 and the rotation shaft 41 are arranged in predetermined positions, the first transmission wheel 18 can be kinematically connected to the upper bearing pinion at co force nstante 41 a by being inserted into the recess 27 by sliding.
The support 47 is fixedly mounted on the rotation shaft 41, and carried by the latter. The rotating torque Tb in a clockwise direction is transmitted from the rotation shaft 41 to the support 47. Consequently, the support 47 rotates, thanks to the energy supplied by the barrel of the movement 11, with l 'rotation shaft 41 clockwise around the first axis of rotation O1. The support 47 comprises a lower plate set with stones 48 integrally connected to the rotation shaft 41, and an upper plate set with stones 54 disposed above the lower plate set with stones 48, and fixed to the lower plate set with stones 48.
CH 715 052 A2 The lower plate set with stones 48 is arranged below the fixed wheel 31. The lower plate set with stones 48 comprises a planetary wheel support part 49, supporting the planetary wheel 43, a part spring support 50, supporting the constant force spring 100, and a connecting part 51 connecting the support part of the planetary wheel 49 to the spring support part 50.
[0065] FIG. 5 is a plan view of part of the movement of the first embodiment, seen from above.
As illustrated in FIGS. 3 and 5, the support portion of the planetary wheel 49 extends in a circular arc shape along a circumferential direction around the first axis of rotation O1 when viewed in a vertical direction. The support part of the planetary wheel 49 is formed so that an intermediate part as seen from the vertical direction is lowered by one stage below the two ends.
As illustrated in FIG. 4, the spring support part 50 is arranged on the side opposite to the support part of the planetary wheel 49, the first axis of rotation O1 being interposed between them. A pin insertion hole 50a, through which a constant force spring pin 103 described below is inserted, is formed in the spring support portion 50. The connecting portion 51 has a central hole through which the rotation shaft 41 is inserted. The connecting part 51 is fixed to the rotation shaft 41 at a lower part than that of the upper bearing pinion at constant force 41a. Consequently, the lower plate set with stones 48 rotates integrally with the rotation shaft 41. A support window 52 is formed in the lower plate set with stones 48. The support window 52 is formed on the side of the first axis. of rotation O1 relative to the support part of the planetary wheel 49. The support window 52 penetrates vertically into the lower plate set with stones 48. The support window 52 prevents any contact with the lower plate set with stones 48 and a stone forming an engagement claw 86 (engagement claw) described below.
As illustrated in FIG. 3, the upper plate set with stones 54 is arranged above the support part of the planetary wheel 49 of the lower plate set with stones 48, and above the main wheel body 33 of the fixed wheel 31. upper plate set with stones 54 extends in a circular arc shape along a circumferential direction around the first axis of rotation O1, when the latter is seen from a vertical direction. The upper plate set with stones 54 is stacked on the support part of the planetary wheel 49 of the lower plate set with stones 48, but spaced from the latter by a plurality of flanges 55. The two ends of the upper plate set with stones 54 are fixed to the two ends of the support part of the planetary wheel 49 by a plurality of bolts 56 inserted through the plurality of flanges 55.
As illustrated in FIG. 4, the planetary wheel 43 is rotatably mounted on the support 47. Specifically, the planetary wheel 43 is pivotally mounted between the support portion of the planetary wheel 49 of the lower plate set with stones 48 and the upper plate set with stones 54, by being supported via hole stones 59A and 59B, and can rotate around a second axis of rotation O2. The second axis of rotation O2 is arranged in a position offset in the plane of the plate 23 relative to the first axis of rotation O1 and in a fixed position relative to the support 47. The planetary wheel 43 is arranged vertically between the intermediate part of the support part of the planetary wheel 49 of the lower plate set with stones 48 and the intermediate part of the upper plate set with stones 54 (see fig. 3). The planetary wheel 43 includes a planetary gear 44 and a planetary gear wheel 45.
The planetary gear 44 meshes with the fixed toothing 33a of the fixed wheel 31. Since the fixed wheel 31 is a toothed wheel on its outer periphery, the planetary wheel 43 performs a revolution clockwise around of the first axis of rotation O1 while turning around the second axis of rotation O2 in a clockwise direction, following the rotation of the support 47 in a clockwise direction, meshing between the planetary pinion 44 and the fixed wheel 31.
The planetary gear wheel 45 is formed below the planetary pinion 44 and can rotate (both in rotation on itself and to make a revolution about another axis) without being in contact with the fixed wheel 31. The planetary gear wheel 45 has a plurality of stop teeth 45a which can be engaged with an engagement surface 86a (see fig. 8) of the stone forming the engagement claw 86 described further, and freed from it. The number of stop teeth 45a is equal to 8. However, the present invention is not limited to such a case, and the number of teeth can be changed as required.
As illustrated in FIG. 5, the stop teeth 45a are inclined clockwise around the second axis of rotation O2 and arranged around the second axis of rotation O2 when viewed in the vertical direction. The tip of the stop tooth 45a is an active surface in the process of engagement and disengagement with respect to the engagement surface 86a of the stone constituting the engagement claw 86. The tip of the tooth stop 45a has a surface shape projecting in a curved manner when viewed in the vertical direction. In what follows, the rotation envelope Μ of the planetary gear wheel 45 will be referred to as the rotation envelope Μ, that is to say the circle drawn by the tooth tip of the tooth. stop 45a following the rotation of the planetary wheel 43.
As illustrated in FIG. 4, the lower level constant force wheel 60 is rotatably supported by the rotation shaft 41 of the upper level constant force wheel 40 between the plate 23 and the constant force unit bridge 24. The wheel constant force of lower level 60 is disposed between the support 47 and the plate 23 below the support 47 of the constant force wheel of upper level 40. The constant force wheel of lower level 60
CH 715 052 A2 comprises a lower level tube 61, fitted on the outside of the rotation shaft 41, and a lower level constant force gear wheel 62 integrally connected to the lower level tube 61. In addition, the lower level constant force wheel 60 rotates clockwise around the first axis of rotation O1 under the action of the energy transmitted by the constant force spring 100.
The rotation shaft 41 is inserted into the lower level tube 61 from above and protrudes below the lower level tube 61. Hole stones in the form of a ring 69A and 69B are driven out. inside the upper and lower ends of the lower level tube 61. The rotation shaft 41 is inserted between the stones with hole 69A and 69B, inside these.
The lower level constant force gear wheel 62 is integrally connected to the lower end of the lower level tube 61. Lower level teeth 62a with which the second transmission wheel 19 meshes are formed over the entire outer periphery of the lower level constant force gear wheel 62. Consequently, the lower level constant force wheel 60 can transmit energy from the constant force spring 100 to the second transmission wheel 19 connected to the exhaust 14, that is to say, the gear train located on the side of the exhaust 15.
In addition, in the context of this embodiment, a case is described where the energy of the constant force spring 100 is transmitted to the exhaust 14 via the gear train on the exhaust side 15 by way of example. , but the present invention is not limited to such a case. For example, the energy of the constant force spring 100 can be directly transmitted to the exhaust 14 without the cog located on the side of the exhaust 15.
The engagement and disengagement lever unit 80 comprises the stone forming an engagement claw 86 alternately engaging with the stop tooth 45a of the planetary gear wheel 45, then releasing from that -this, and rotatably supports the stone forming the engagement claw 86 around the first axis of rotation O1. The engagement and release lever unit 80 includes a lever plug 81 and a lever spring 94 arranged fixedly in rotation relative to the lower level tube 61, and an engagement and release lever 84 arranged so as to be free to rotate relative to the lower level tube 61.
The lever plug 81 has a cylindrical shape coaxial with the first axis of rotation O1. The lever plug 81 is fitted to the outside of the upper end of the lower level tube 61 of the lower level constant force wheel 60, and is integrally connected to the lower level tube 61. Therefore, the plug lever 81 rotates clockwise around the first axis of rotation O1 in synchronization with the rotation of the constant force wheel of lower level 60. A collar 82 projecting outward in the radial direction is formed at an upper end of the lever plug 81.
FIG. 6 is a plan view of the engagement and disengagement lever unit of the first embodiment, seen from above. Fig. 7 is a sectional view illustrating the engagement and disengagement lever unit of the first embodiment.
As shown in Figs. 6 and 7, the engagement and release lever 84 is arranged so as to be rotatable about the first axis of rotation O1 relative to the lever plug 81 and the lever spring 94. The engagement and release lever 84 comprises a main lever body 85 (the lever body), the stone forming an engagement claw 86 and a lever pin 87 supported by the main lever body 85.
The main lever body 85 is arranged below the planetary gear wheel 45 of the planetary wheel 43 (see fig. 4). The main lever body 85 is rotatably supported by a vertical intermediate part of the lever plug 81. The main lever body 85 cannot move upward relative to the lower level tube 61 thanks to the collar 82 of the lever plug 81. The main lever body 85 comprises a first lever part 90, a second lever part 91, and a third lever part 92 extending radially outward from the lever plug 81. first lever part 90, the second lever part 91, and the third lever part 92 are arranged so as to be spaced apart from one another in a circumferential direction around the first axis of rotation O1. In the example illustrated, vertically oriented through holes are formed at the ends of the base of the first lever part 90, of the second lever part 91, and of the third lever part 92, however, the shapes for the first lever part 90, the second lever part 91, and the third lever part 92 are not limited to such a case, but can be freely changed. In addition, the shape of the main lever body 85 is not limited to the shape described above, but can be freely changed. For example, the main lever body may not include a third lever part 92.
A stone holding part 90a for holding the stone forming the engagement claw 86 is formed at one end of the first lever part 90. The stone holding part 90a penetrates vertically into the first part lever 90. A pin holding part 91 a for holding the lever pin 87 is formed at one end of the second lever part 91. The pin holding part 91a penetrates vertically into the second lever part 91.
FIG. 8 is a perspective view of the planetary wheel and of the engagement and disengagement lever unit according to the first embodiment, seen from above, while FIG. 9 is a perspective view of the planetary wheel and the engagement and disengagement lever unit of the first embodiment, seen from below.
CH 715 052 A2 As shown in figs. 8 and 9, the stone forming the engagement claw 86 is fixed to the stone retaining part 90a of the first lever part 90, and is rotatably mounted on the main lever body 85 relative to the lever plug 81 and to the lever spring 94. Consequently, the stone forming the engagement claw 86 is arranged so as to be able to oscillate around the first axis of rotation O1. The stone forming the engagement claw 86 is formed, for example, from an artificial stone such as a ruby. However, the stone forming the engagement claw 86 is not limited to the case where it consists of an artificial stone similar to the hole stone described above, but can for example be formed from other fragile materials or materials. metallic such as iron-based alloys. In addition, the stone forming the engagement claw 86 may not be formed separately from the main lever body 85, but could be formed in one piece, that is to say in one piece, with the main lever body 85. The stone forming the engagement claw 86 is held in a state where it projects towards the planetary gear wheel 45 (forward) from the stone holding portion 90a. The stone forming the engagement claw 86 is disposed inside the support window 52 of the support 47 of the upper level constant force wheel 40 (see FIG. 4).
FIG. 10 is a plan view of part of a constant torque mechanism according to the first embodiment, seen from above.
As shown in FIGS. 8 and 10, among the protrusions of the stone forming the engagement claw 86, the lateral surface oriented on the side opposite the first axis of rotation O1 constitutes the engagement surface 86a with which the tip of the stop tooth 45a of the planetary gear wheel 45 is engaged and from which it is alternately released. In the example illustrated, substantially all of the engagement surface 86a is a flat surface, the two ends of which are chamfered in R when the latter is viewed in the vertical direction. In other words, the edges of the engagement surface 86a on both sides in the circumferential direction around the first axis of rotation O1 project in a curved shape when they are seen in the vertical direction. Hereinafter, the edge of the engagement surface 86a will be qualified in the anticlockwise direction around the first axis of rotation O1 with the first edge 86a1. The stone forming the engagement claw 86 engages the planetary gear wheel 45 inside the rotation casing M of the planetary gear wheel 45 to limit the rotation of the planetary wheel 43. more, the stone forming the engagement claw 86 is moved clockwise around the first axis of rotation O1 relative to the planetary wheel 43 and retracts outside the rotation envelope M of the planetary gear wheel 45 to disengage from the stop tooth 45a and release the engagement with the planetary gear wheel 45.
As illustrated in FIG. 7, the lever pin 87 comprises a shaft 87a constituting the body of this part, which takes the form of a column extending vertically, and which is inserted through the pin holding part 91a of the main lever body 85, and a head 87b having a larger diameter located at a lower end of the shaft 87a. The shaft 87a projects both upwards and downwards from the second lever part 91 '. The head 87b is arranged so as to be spaced from the lower surface of the second lever part 91.
As shown in FIGS. 7 and 9, the lever spring 94 is disposed below the main lever body 85 and is fixedly supported by the lower end of the lever plug 81. Consequently, the lever spring 94 rotates in the direction of the needles of a watch around the first axis of rotation O1, in synchronization with the rotation of the lower level constant force wheel 60. The lever spring 94 comprises a base 95 (synchronous rotary part) fixed to the lever cap 81, and a main spring body 97 (elastic part) extending from the base 95.
As illustrated in FIG. 9, the base 95 is configured in annular form so as to surround the first axis of rotation O1. The base 95 is fitted to the outside of the lower end of the lever plug 81, and is integrally connected to the lever plug 81. The base 95 can come to bear on the main lever body 85 of the engagement lever and clearance 84 from below, and restrict the downward movement of the main lever body 85 relative to the lever plug 81. An arm 96 is formed in the base 95.
As illustrated in FIG. 6, the arm 96 extends along an extension direction of the second lever portion 91 of the engagement and release lever 84 when we see the latter in the vertical direction. One end of the arm 96 abuts against the shaft 87a of the lever pin 87 between one end of the second lever part 91 and the head 87b of the lever pin 87 counterclockwise around of the first axis of rotation O1 (see also fig. 9). Consequently, the arm 96 limits the rotation of the engagement and disengagement lever 84 relative to the base 95 in an anti-clockwise direction around the first axis of rotation O1. In other words, the arm 96 limits the movement of the stone forming the engagement claw 86 in engagement with the planetary gear wheel 45 (see the two in FIG. 8) in an anti-clockwise direction around of the first axis of rotation O1 with respect to the base 95. The lever spring 94 compresses the engagement and disengagement lever 84 in a clockwise direction around the first axis of rotation O1 to rotate.
The main spring body 97 is a thin leaf spring. The main spring body 97 extends from the end of the arm 96 counterclockwise around the first axis of rotation O1. The main spring body 97 rotates around the base 95 outward in the radial direction and bears against the shaft 87a of the lever pin 87 by moving clockwise around the first axis of rotation O1 between the end of the second lever part 91 and the head 87b of the lever pin 87 (see also fig. 9). Consequently, the main spring body 97 allows the movement of the engagement and disengagement lever 84 relative to the base 95
CH 715 052 A2 clockwise around the first axis of rotation O1 while compressing the engagement and release lever 84 relative to the base 95 counterclockwise around the first axis of rotation O1. Consequently, the stone forming the engagement claw 86 included in the engagement and release lever 84 is in a state where it has play with respect to the base 95 in a clockwise direction around the first axis of rotation O1.
As illustrated in FIG. 10, the constant force spring 100 is a thin leaf spring made of a metal such as iron or nickel, or an alloy, and has a spiral shape. Specifically, the constant force spring 100 is configured as a spiral corresponding to the Archimedean spiral in a polar coordinate system, taking the first axis of rotation O1 as the origin. Consequently, the constant force spring 100 is wound with a plurality of turns so that each winding is adjacent to each other at substantially equal intervals in the radial direction, when the spring is seen according to the vertical direction.
As illustrated in FIG. 4, the constant force spring 100 is located below the engagement and disengagement lever unit 80, and is disposed between the engagement and disengagement lever unit 80 and the gear wheel. constant lower level force 62. In the constant force spring 100, an external end 101, which constitutes a first peripheral end, is connected to the lower plate set with stones 48 of the support 47 of the upper level constant force wheel 40 via the constant force spring pin 103, and an internal end 102, which constitutes the other peripheral end, is connected to the lower level constant force wheel 60 via a fixing ring 104 and the torque adjustment mechanism 110. Consequently, the constant force spring 100 can transmit accumulated energy to each of the upper level constant force wheel 40 and lower level constant force wheel. ur 60. The constant force spring pin 103 is held in the spring support portion 50 in a state where it projects below the pin insertion hole 50a formed in the spring support portion 50 of the upper level constant force wheel 40. The external end 101 of the constant force spring 100 is fixed to a projecting part of the constant force spring pin 103.
The fixing ring 104 is fixed to the internal end 102 of the constant force spring 100. The fixing ring 104 is configured in annular form and coaxial with the first axis of rotation O1. The fixing ring 104 is integrally connected to a constant force spring cap 111 of the torque adjustment mechanism 110, which will be described later.
The constant force spring 100 is wound in a predetermined amount of windings in a clockwise direction towards the outer end 101 with the inner end 102 as the unwinding position. The constant force spring 100 is elastically deformed to reduce its diameter when it is reassembled, and a prestress is then applied. Consequently, a torque energy Te is generated in the constant force spring 100 and energy is accumulated there. The energy accumulated in the constant force spring 100 is transmitted to the upper level constant force wheel 40 and to the lower level constant force wheel 60 in accordance with the elastic restoring force due to the elastic deformation of the force spring constant 100. Consequently, the upper level constant force wheel 40 and the lower level constant force wheel 60 can rotate around the first axis of rotation O1 in opposite directions relative to each other under the impulse of the energy transmitted by the constant force spring 100. Specifically, the lower level constant force wheel 60 can rotate clockwise and the higher level constant force wheel 40 can rotate clockwise counterclockwise. Hereinafter, reference is made to the torque Te to designate the torque Te of the constant force spring 100. In addition, in a case where the mainspring 16 of the movement barrel 11 is wound with a predetermined quantity of windings, the rotation torque Te is a smaller torque than the rotation torque Tb of the rotation shaft 41.
The torque adjustment mechanism 110 applies a preload to the constant force spring 100 to adjust the rotational torque Te of the constant force spring 100. The torque adjustment mechanism 110 comprises the spring cap of constant force 111 supported by the lower level tube 61 of the lower level constant force wheel 60, a first torque adjustment wheel 112 integrally connected to the constant force spring cap 111, a second torque adjustment wheel 113 connected integrally with the lower level tube 61, and a torque adjustment jumper 114 which engages with the first torque adjustment wheel 112 and the second torque adjustment wheel 113.
The constant force spring plug 111 is arranged in a cylindrical shape coaxial with the first axis of rotation O1. The constant force spring plug 111 is fitted to the outside of the lower level tube 61 between the constant force lower level gear wheel 62 and the engagement and release lever unit 80. The plug constant force spring 111 is arranged movable in rotation relative to the lower level tube 61 around the first axis of rotation O1. The fixing ring 104 is adjusted on the outside of an intermediate part, in the vertical direction, of the constant force spring plug 111, and the constant force spring plug 111 and the fixing ring 104 are integrally connected to each other.
The first torque adjustment wheel 112 is integrally connected to a lower end of the constant force spring plug 111. First torque adjustment teeth 112a are formed over the entire outer peripheral surface of the first wheel d torque adjustment 112. A torque adjustment wheel (not shown) meshes with the first torque adjustment teeth 112a.
CH 715 052 A2 The second torque adjustment wheel 113 is disposed between the lower level constant force gear wheel 62, the constant force spring cap 111, and the first torque adjustment wheel 112. The second torque adjustment wheel 113 is integrally connected to the lower level tube 61. The second torque adjustment wheel 113 is formed with a smaller diameter than that of the first torque adjustment wheel 112. Second torque adjustment teeth 113a are formed over an entire outer peripheral surface of the second torque adjustment wheel 113. The torque adjustment jumper 114 engages reversibly and intermittently with the second teeth d torque adjustment 113a.
The torque adjustment jumper 114 is supported by the first torque adjustment wheel 112, and can make a revolution around the first axis of rotation O1 at the periphery of the second torque adjustment wheel 113. The torque adjustment jumper 114 may limit the rotation of the first torque adjustment wheel 112 clockwise relative to the second torque adjustment wheel 113. In addition, the adjustment jumper of torque 114 can allow the rotation of the first torque adjustment wheel 112 anticlockwise with respect to the second torque adjustment wheel 113.
Consequently, when the constant force spring cap 111 and the first torque adjustment wheel 112 receive energy from the constant force spring 100 in the clockwise direction, the energy is transmitted to the second torque adjustment wheel 113 via the torque adjustment jumper 114. Next, the torque adjustment jumper 114 limits the rotation of the first torque adjustment wheel 112 in the clockwise direction d a watch with respect to the second torque adjustment wheel 113, and the first torque adjustment wheel 112 and the second torque adjustment wheel 113 rotate together clockwise. Consequently, the lower level constant force wheel 60 also rotates clockwise with the second torque adjustment wheel 113.
In addition, when the preload is applied to the constant force spring 100, the torque adjustment wheel (not shown) meshes with the first torque adjustment wheel 112, and the torque adjustment wheel is rotated to rotate the first torque adjustment wheel 112 counterclockwise. Then, the torque adjustment jumper 114 allows the first torque adjustment wheel 112 to rotate anticlockwise with respect to the second torque adjustment wheel 113, so that the constant force spring plug 111 and the fixing ring 104 are rotated anti-clockwise without rotating the constant level lower force wheel 60. Consequently, the internal end 102 of the constant force spring 100 can be rotated counterclockwise. As a result, the constant force spring 100 can be rewound and the preload of the constant force spring 100 increased accordingly, so that the torque Te can be adjusted so as to increase.
[0104] (Operation of the constant torque mechanism) In the following, an operation of the constant torque mechanism 30 having the configuration described above will be described.
In addition, in an initial state, the mainspring 16 of the barrel of the movement 11 is wound up by being wound on itself with a predetermined quantity of windings, and the energy of the torque Tb is transmitted from the barrel movement 11 to the support 47 of the upper level constant force wheel 40 via the gear train located on the side of the energy source 12. In addition, the constant force spring 100 is wound up with a predetermined quantity of windings, and the energy of the torque Te less than the torque Tb is transmitted from the constant force spring 100 to the support 47 of the upper level constant force wheel 40 and the lower level constant force wheel 60.
According to the constant torque mechanism 30 of the embodiment described, since the constant force spring 100 is supplied, the energy accumulated in the constant force spring 100 is transmitted to the lower level constant force wheel 60, and the lower level constant force wheel 60 can be rotated clockwise around the first axis of rotation O1. In detail, the energy of the constant force spring 100 is transmitted to the torque adjustment mechanism 110 via the fixing ring 104. The energy transmitted to the torque adjustment mechanism 110 is transmitted to the constant force wheel of lower level 60. Consequently, the energy is transmitted from the constant force spring 100 to the constant force wheel of lower level 60 so as to rotate clockwise around the first axis of rotation O1 to using the torque Te. Furthermore, the energy of the constant force spring 100 can be transmitted from the lower level constant force wheel 60 to the second transmission wheel 19, and the second transmission wheel 19 can be rotated in accordance with that of the constant force wheel of lower level 60. In other words, the energy of the constant force spring 100 can be transmitted to the gear train on the side of the exhaust 15 via the constant force wheel of lower level 60, and operate the exhaust 14.
In addition, since the energy of the constant force spring 100 can also be transmitted to the constant force wheel of the upper level 40, the constant force wheel of the upper level 40 is rotated counter-clockwise. of a watch around the first axis of rotation O1 by the torque Torque.
CH 715 052 A2 [0109] However, the torque Tb is transmitted from the gear train located on the side of the energy source 12 to the constant-force wheel of higher level 40 to rotate it clockwise. a watch around the first axis of rotation O1. Since the torque Tb is greater than the torque Te, the upper level constant force wheel 40 is prevented from turning counterclockwise around the first axis of rotation O1.
In addition, an energy (torque Tb - torque Te) corresponding to a difference between the torque Tb transmitted from the gear train located on the side of the energy source 12 and the torque Te transmitted from the constant force spring 100 acts on the higher level constant force wheel 40. On the other hand, the stone forming the engagement claw 86 of the engagement and release lever unit 80 engages with the planetary gear wheel 45 in the rotation casing Μ of the planetary gear wheel 45 of the upper level constant force wheel 40, so that the rotation on itself and the revolution of the wheel planetary 43 are limited. Therefore, the upper level constant force wheel 40 and the lower level constant force wheel 60 can be engaged, and the higher level constant force wheel 40 can be prevented from turning clockwise. around the first axis of rotation O1.
As described above, at a stage where the planetary gear wheel 45 and the stone forming the engagement claw 86 are brought into mutual engagement, the upper level constant force wheel 40 is prevented from rotating around of the first axis of rotation O1. In addition, since the energy corresponding to the difference described above acts on the upper level constant force wheel 40, a tip of the stop tooth 45a of the planetary gear wheel 45 engages with the engagement surface 86a of the stone forming the engagement claw 86 to end up in a highly compressed state.
[0112] FIGS. 11 to 14 are explanatory views of the operation of the constant torque mechanism according to the first embodiment, and plan views of the fixed wheel, the planetary wheel, and the engagement and disengagement lever unit when these elements are seen from above. In addition, in Figs. 11 to 14, the fixed wheel, the planetary wheel, and the engagement and disengagement lever unit are illustrated in a simplified manner.
When the lower level constant force wheel 60 rotates using the energy of the constant force spring 100, the lever plug 81 and the lever spring 94 of the engagement lever unit and 80 release rotate accordingly clockwise around the first axis of rotation O1. When the lever spring 94 rotates, the engagement and release lever 84 of the engagement and release lever unit 80 is compressed by the arm 96 of the lever spring 94, and rotates clockwise. 'a watch around the first axis of rotation O1. When the engagement and release lever 84 rotates clockwise, the stone forming the engagement claw 86 disposed on the engagement and release lever 84 moves in the clockwise direction. a watch around the first axis of rotation O1, in a state where it still has play to move clockwise around the first axis of rotation O1. Therefore, the engagement and disengagement lever unit 80 can be gradually released from the planetary gear wheel 45, so that the stone forming the engagement claw 86 retracts out of the envelope. rotation Μ of the planetary gear wheel 45. Consequently, as illustrated in FIGS. 11 to 13, the tip of the stop tooth 45a moves in the anticlockwise direction around the first axis of rotation O1 relative to the engagement surface 86a, while sliding on the surface of engagement 86a in accordance with the movement of release of the stone forming the engagement claw 86.
Here, the force F applied between the stop tooth 45a and the stone forming the engagement claw 86 is a force resulting from a compression force with which the stop tooth 45a comes to bear on the surface. 86a, and a frictional force generated by a sliding movement of the stop tooth 45a on the engagement surface 86a. The compressive force is a force acting parallel to a normal direction at the contact part between the stop tooth 45a and the engagement surface 86a; the frictional force is a force acting parallel to a tangential direction at the level of the contact part between the stop tooth 45a and the engagement surface 86a. The tip of the stop tooth 45a and the first edge 86a1 of the engagement surface 86a have a surface shape which projects in a curved shape when viewed from the vertical direction, so that when the tip of the stop tooth 45a comes into contact with the first edge 86a1 of the engagement surface 86a, the force F approaches clockwise around the first axis of rotation O1 (see fig. 13). Consequently, the engagement and disengagement lever 84 including the stone forming the engagement claw 86 rotates clockwise around the first axis of rotation O1 relative to the base 95 against the pushing force. of the main spring body 97 of the lever spring 94. As illustrated in FIG. 14, when the tip of the stop tooth 45a exceeds the first edge 86a1 of the engagement surface 86a, the engagement between the stop tooth 45a and the stone forming an engagement claw 86 is released. Consequently, the engagement between the upper level constant force wheel 40 and the lower level constant force wheel 60 via the stone forming the engagement claw 86 and the planetary wheel 43 is released.
Consequently, the upper level constant force wheel 40 rotates clockwise around the first axis of rotation O1 with the energy (torque Tb - torque Te), c ' ie the difference between the torque Tb transmitted from the gear train located on the side of the power source 12 and the torque Te transmitted from the constant force spring 100.
CH 715 052 A2 The upper level constant force wheel 40 rotates clockwise around the first axis of rotation O1, so that the constant force spring 100 can be reassembled via the pin of constant force spring 103 fixed to the support 47, and energy can be stored in the constant force spring 100. In other words, it is possible to compensate for a loss of energy lost during the transmission of energy to the lower level constant force wheel 60 using the energy transmitted from the movement barrel 11 used as an energy source. Consequently, the energy of the constant force spring 100 can be constantly maintained and the exhaust 14 can be operated with constant torque.
In addition, even in a case where the power supply with respect to the constant force spring 100 is carried out, the lower level constant force wheel 60 rotates with the energy of the constant force spring 100, and l the energy of the constant force spring 100 is transmitted to the gear train located on the side of the exhaust 15.
In addition, when the power supply with respect to the constant force spring 100 is carried out, the planetary wheel 43 makes a revolution clockwise around the first axis of rotation O1 while turning on itself clockwise around the second axis of rotation O2 in accordance with the rotation of the upper level constant force wheel 40 around the first axis of rotation O1 to follow the stone forming the engagement claw 86. The planetary wheel 43 rotates a total corresponding to one tooth of the stop tooth 45a to catch up with the stone forming the engagement claw 86, and the tip of the stop tooth 45a again engages with the engagement surface 86a of the stone forming the engagement claw 86.
Consequently, since the upper level constant force wheel 40 and the lower level constant force wheel 60 engage again, any rotation of the higher level constant force wheel 40 is prevented, and the power supply to the constant force spring 100 is complete.
The engagement and disengagement between the planetary gear wheel 45 and the stone forming the engagement claw 86 can be carried out intermittently by repeating the operation described above. In other words, the engagement and disengagement between the planetary gear wheel 45 and the stone forming the engagement claw 86 are effected intermittently, and the higher level constant force wheel 40 can be rotated intermittently by relative to the lower level constant force wheel 60 based on the rotation of the lower level constant force wheel 60. Therefore, the power supply to the constant force spring 100 can be effected intermittently.
As described above, the constant torque mechanism 30 of the embodiment comprises the base 95 of the lever spring 94 rotating clockwise around the first axis of rotation O1 in synchronization with the rotation of the lower level constant force wheel 60, and the stone forming the engagement claw 86 turning clockwise around the first axis of rotation O1 in accordance with the rotation of the base 95, capable of engage with and disengage from the planetary gear wheel 45, engaging with the planetary gear wheel 45 in the rotation casing M of the planetary gear wheel 45 to restrict rotation of the planetary gear wheel 45, and then being moved relative to the base 95 so as to be able to retract outside the rotation envelope M of the planetary gear wheel 45. In such a configuration, the stone forming the engagement claw 86 is moved relative to the base 95 and is withdrawn outside the rotation envelope M of the planetary gear wheel 45, so that immediately before the clearance between the wheel d planetary gear 45 and the stone forming the engagement claw 86, it is possible to reduce the torque clockwise around the first axis of rotation O1 which is transmitted from the planetary gear wheel 45 to the base 95 via the stone forming the engagement claw 86. Consequently, it is possible to suppress the fluctuation of the torque transmitted from the base 95 to the exhaust 14 via the lower level constant force wheel 60. Consequently, it is possible to suppress the fluctuation of the torque transmitted to the exhaust 14.
More particularly, in the embodiment described, the tip of the stop tooth 45a of the planetary gear wheel 45 and the first edge 86a1 of the engagement surface 86a of the stone forming the claw engagement 86 have a surface shape projecting in a curved manner when viewed from the vertical direction. Therefore, it is possible to reduce the pressure at the contact surface between the planetary gear wheel 45 and the stone forming the engagement claw 86, and to prevent strong abrasion from occurring between the planetary gear wheel 45 and the stone forming an engagement claw 86 compared to the case where the tip of the stop tooth of the planetary gear wheel and the first edge of the engagement surface of the stone forming a engagement claw does not have a curved projecting surface shape. In addition, in this case, the sliding distance between a tooth tip of the stop tooth 45a of the planetary gear wheel 45 and the first edge 86a1 of the engagement surface 86a of the stone forming a claw d engagement 86 is increased compared to the case where the tooth tip of the planetary gear wheel stop tooth and the first edge of the stone engagement surface forming an engagement claw have no shape surface projecting in a curved manner. Consequently, the period during which the direction of the force F applied between the planetary gear wheel 45 and the stone forming an engagement claw 86 approaches clockwise around the first axis of rotation O1 is increased. Here, within the framework of the embodiment described above, immediately before the clearance between the planetary gear wheel 45 and the stone forming an engagement claw 86, the stone forming the engagement claw 86 is retracted apart. of the rotation envelope M of the planetary gear wheel 45, and the torque in the direction of
CH 715 052 A2 clockwise around the first axis of rotation O1, which is transmitted from the planetary gear wheel 45 to the base 95, can be reduced. Therefore, it is possible to improve the durability of the constant torque mechanism 30 and to suppress the fluctuation of the torque.
In addition, since the abrasion between the planetary gear wheel 45 and the stone forming the engagement claw 86 is eliminated, there is room to increase the force applied at the contact part between the planetary gear wheel 45 and the stone forming the engagement claw 86. Consequently, the distance between the contact part between the planetary gear wheel 45 and the stone forming the engagement claw 86, and the first axis O1 can be reduced, and the constant torque mechanism 30 can be reduced in size.
In addition, the stone forming the engagement claw 86 moves clockwise around the first axis of rotation O1 relative to the base 95, and is withdrawn outside the envelope of rotation M. In this configuration, immediately before the clearance between the planetary gear wheel 45 and the stone forming the engagement claw 86, when the direction of the force F applied between the planetary gear wheel 45 and the stone forming the engagement claw 86 approaches clockwise around the first axis of rotation O1, the stone forming the engagement claw 86 is compressed by the planetary gear wheel 45 and the stone forming the claw d engagement 86 can be moved relative to base 95. Therefore, the torque clockwise around the first axis of rotation O1, which is transmitted from the planetary gear wheel 45 to base 95 via the stone forming an engagement claw 86, is reduced thanks to the displacement of the stone forming the engagement claw 86. Consequently, the fluctuation of the torque transmitted from the base 95 to the exhaust 14 via the constant force wheel level 60 can be deleted.
In addition, the constant torque mechanism 30 further comprises the main spring body 97 indirectly inciting the stone forming an engagement claw 86 to move towards the inside of the rotation envelope M via the main body lever 85. In such a configuration, it is possible to prevent the stone forming an engagement claw 86 from remaining in a state where it is in a retracted position outside the rotation casing M of the wheel d planetary gear 45. Therefore, the operation of engaging and disengaging the stone forming the engagement claw 86 from the planetary gear wheel 45 can be stabilized.
In addition, the constant torque mechanism 30 also comprises the main lever body 85 on which is mounted the stone forming the engagement claw 86 movable in rotation relative to the base 95 of the lever spring 94, and which is supplied separately from the main spring body 97. According to this configuration, it is possible to stably support the stone forming the engagement claw 86 compared to the case where the stone forming the engagement claw 86 is supported by the part elastic formed by the spring. Consequently, it is possible to stabilize the movement of the stone forming the engagement claw 86 relative to the base 95, and to stabilize the operation of engaging and disengaging the stone forming the engagement claw 86 by relative to the planetary gear wheel 45.
In addition, the base 95 of the lever spring 94 includes the arm 96 restricting the movement of the stone forming the engagement claw 86 in engagement with the planetary gear wheel 45 in the counterclockwise direction. shows around the first axis of rotation O1 relative to the base 95. According to this configuration, when the stone forming the engagement claw 86 rotates clockwise around the first axis of rotation O1 with the base 95 , the stone forming the engagement claw 86 can move anti-clockwise around the first axis of rotation O1 relative to the base 95, but in such a way that it is possible to prevent that the stone forming the engagement claw 86 can never be released from the planetary gear wheel 45. Consequently, it is possible to stabilize the engagement and disengagement operation of the stone forming the engagement claw ement 86 relative to the planetary gear wheel 45.
In addition, the stone forming the engagement claw 86 is arranged so as to be able to oscillate around the first axis of rotation O1 relative to the base 95 of the lever spring 94. In this configuration, the lever plug 81 extending along the first axis of rotation O1 and supporting the base 95 can be used as a shaft which movably supports the main lever body 85 to which the stone forming the engagement claw 86 is fixed relative to the base 95 lever spring 94. On the other hand, in a case where the stone forming an engagement claw is arranged so as to be able to oscillate about an axis different from the first axis of rotation O1, it is necessary to supply separately an element constituting the shaft (for example, in the form of a rotary lever shaft 389 as according to the fourth embodiment illustrated in FIG. 19) disposed on an axis different from the first axis of rotation O1 as shaft supports swingably the element to which the stone forming the engaging claw is attached. Consequently, it is possible to reduce the number of components compared to the case where the stone forming the engagement claw 86 is arranged so as to be able to oscillate about an axis different from the first axis of rotation O1.
In what follows, the assembly of the constant torque mechanism 30 will be briefly described. When the constant torque mechanism 30 is assembled, first of all, the lower level constant force wheel 60 is assembled to the plate. 23 with the torque adjustment mechanism 110, the constant force spring 100, and the engagement and disengagement lever unit 80. Next, the upper level constant force wheel 40 is assembled to the lower force tube constant 61 of the lower level constant force wheel 60. Next, the fixed wheel 31, assembled to the constant force unit bridge 24, is assembled to the higher level constant force wheel 40. In this case, while the rotation shaft 41 is inserted into the central hole 35 of the fixed wheel 31, the main wheel body 33 of the fixed wheel 31 is
CH 715 052 A2 connected to the planetary gear wheel 45 of the planetary wheel 43 while avoiding the upper plate set with stones 54 of the support 47. Consequently, it is necessary to insert the rotation shaft 41 into the hole central 35 of the fixed wheel 31 in a state where the fixed wheel 31 is inclined relative to the first axis of rotation O1. According to the embodiment described, the window 36 continuously extends the central hole 35 of the fixed wheel 31 through which the rotation shaft 41 is inserted, and the central hole 35 is formed as an oblong hole when the latter is seen from the vertical direction. Consequently, the rotation shaft 41 can be inserted into the central hole 35 of the fixed wheel 31 in a state where the fixed wheel 31 is inclined relative to the first axis of rotation O1. Therefore, it is possible to provide a constant torque mechanism 30 whose assembly convenience is improved.
In the timepiece 1 and the movement 10 of this embodiment, the fluctuation of the torque transmitted to the exhaust 14 is eliminated and a constant torque mechanism 30 of greater durability is provided, so that it is possible to provide a movement 10 and a timepiece 1 of high precision and excellent durability.
[Second embodiment] [0132] In the following, a second embodiment will be described with reference to FIGS. 15 and 16. The second embodiment differs from the first embodiment in that an engagement and release lever 84 is no longer pushed. The configurations of the elements other than those described below are the same as those of the first embodiment.
[0133] (Configuration of the engagement and disengagement lever unit) [0134] Fig. 15 is a plan view of a planetary wheel and an engagement and disengagement lever unit of the second embodiment seen from above. In addition, in fig. 15, the planetary wheel, and the engagement and disengagement lever unit are illustrated in a simplified manner (which also applies to each following drawing).
As illustrated in FIG. 15, the engagement and disengagement lever unit 180 comprises a degree adjustment lever 194 (synchronous rotary part) in place of the lever spring 94 according to the first embodiment.
The degree adjustment lever 194 is disposed below a main lever body 85 and is integrally connected to a lower end of a lever cap 81. Consequently, the degree adjustment lever 194 rotates clockwise around a first axis of rotation O1 in synchronization with the rotation of a lower level constant force wheel 60. A two-legged fork 195 is formed at one end of the degree adjustment lever 194. A lever pin 87 is disposed inside the fork 195. The interior of the fork 195 is formed so as to be wider than the lever pin 87 in the circumferential direction around the first axis of rotation O1. Consequently, the fork 195 allows the engagement and disengagement lever 84 comprising the lever pin 87 to rotate by a predetermined angle range relative to the degree adjustment lever 194.
The fork 195 rotates clockwise around the first axis of rotation O1 so as to be in contact with the lever pin 87 anti-clockwise around the first axis of rotation O1. Consequently, the degree adjustment lever 194 bears against the engagement and disengagement lever 84 so as to rotate it clockwise around the first axis of rotation O1. In addition, the fork 195 restricts the rotation of the engagement and disengagement lever 84 relative to the degree adjustment lever 194 counterclockwise around the first axis of rotation O1. In other words, the fork 195 restricts the movement of the stone forming the engagement claw 86 in engagement with the planetary gear wheel 45 anti-clockwise around the first axis of rotation O1 relative to the lever of degree adjustment 194. As described above, the stone forming the engagement claw 86 included in the engagement and release lever 84 is in a state where it still has play to move in the direction of clockwise around the first axis of rotation O1 relative to the degree adjustment lever 194.
In addition, the fork 195 restricts the rotation of the engagement and disengagement lever 84 relative to the degree adjustment lever 194 in the clockwise direction around the first axis of rotation O1. In other words, the fork 195 restricts the movement of the stone forming the engagement claw 86 when the latter tends to withdraw out of the rotation casing Μ of the planetary gear wheel 45 in the direction of the needles. a watch around the first axis of rotation O1 relative to the degree adjustment lever 194.
[0139] (Operation of the engagement and release lever unit) [0140] The operation of the engagement and release lever unit 180 having the configuration described above is described here.
Similarly to the first embodiment, when the planetary gear wheel 45 and the stone forming the engagement claw 86 engage with each other, a tip of a tooth stop 45a of the planetary gear wheel 45 engages with an engagement surface 86a of the stone forming the engagement claw 86 to end up in a state of strong mutual compression.
When the lower level constant force wheel 60 rotates under the impulse of the energy of the constant force spring 100, the lever plug 81 and the degree adjustment lever 194 of the lever unit engagement and release 180 rotate clockwise around the first axis of rotation
CH 715 052 A2
O1. When the degree adjustment lever 194 rotates, the stone forming the engagement claw 86 included in the engagement and release lever 84 moves clockwise around the first axis of rotation O1 in a state where it still has play to move clockwise around the first axis of rotation O1. Consequently, the engagement and disengagement lever unit 180 can be gradually released from the planetary gear wheel 45, so that the engagement claw stone 86 is withdrawn outside the envelope. rotation Μ of the planetary gear wheel 45. The tip of the stop tooth 45a moves anticlockwise with respect to the engagement surface 86a while sliding on the engagement surface 86a.
[0143] FIG. 16 is an explanatory view of the operation of a constant torque mechanism according to the second embodiment and a plan view of the planetary wheel and the engagement and disengagement lever unit, seen from above.
When the tip of the stop tooth 45a comes into contact with the first edge 86a1 of the engagement surface 86a, a force F applied between the stop tooth 45a and the stone forming the engagement claw 86 approximates clockwise around the first axis of rotation O1. Consequently, the engagement and disengagement lever 84 moves clockwise around the first axis of rotation O1 with respect to the degree adjustment lever 194 in a clearance directed in the clockwise direction. a watch around the first axis of rotation O1. As illustrated in fig. 16, when the tip of the stop tooth 45a exceeds the first edge 86a1 of the engagement surface 86a, the engagement between the stop tooth 45a and the stone forming the engagement claw 86 is released.
As described above, the constant torque mechanism 130 of the presently described embodiment comprises the degree adjustment lever 194 rotating clockwise around the first axis of rotation O1 in synchronization with the rotation of the lower level constant force wheel 60 in place of the lever spring 94 of the first embodiment. In addition, the stone forming the engagement claw 86 rotates clockwise around the first axis of rotation O1 in accordance with the rotation of the degree adjustment lever 194; it is capable of engaging with and of being released from the planetary gear wheel 45, engages with the planetary gear wheel 45 inside the rotation casing Μ of the planetary gear wheel 45 to restrict the rotation of the planetary gear wheel 45, and is then moved relative to the degree adjustment lever 194 to be able to withdraw outside the rotation casing Μ of the planetary gear wheel 45. Therefore , similarly to the first embodiment, the fluctuation in the torque transmitted from the degree adjustment lever 194 to the exhaust 14 via the constant-level wheel of lower level 60 can be eliminated. Consequently, any fluctuation in the torque transmitted to the exhaust 14 can be eliminated.
In addition, the degree adjustment lever 194 includes the fork 195 restricting the movement of the stone forming the engagement claw 86 in engagement with the planetary gear wheel 45 in the counterclockwise direction around the first axis of rotation O1 with respect to the degree adjustment lever 194. In this configuration, when the stone forming the engagement claw 86 rotates clockwise around the first axis of rotation O1 with the degree adjustment lever 194, the stone forming the engagement claw 86 can move anti-clockwise around the first axis of rotation O1 relative to the degree adjustment lever 194, but in such a way that it is possible to prevent the stone forming the engagement claw 86 from ever being able to be released from the planetary gear wheel 45. Consequently, it is possible to stabilize the operation t of engagement and disengagement of the stone forming the engagement claw 86 relative to the planetary gear wheel 45.
In addition, the degree adjustment lever 194 includes the fork 195 restricting the movement of the stone forming the engagement claw 86 when it withdraws outside the rotation envelope Μ of the gear wheel planetary 45 in a clockwise direction around the first axis of rotation O1 relative to the degree adjustment lever 194. In this configuration, when the stone forming the engagement claw 86 is withdrawn outside the envelope of rotation Μ of the planetary gear wheel 45, the stone forming the engagement claw 86 can move clockwise around the first axis of rotation O1 relative to the degree adjustment lever 194, but in such a way that the stone forming the engagement claw 86 can again penetrate inside the rotation envelope étaire of the planetary gear wheel 45 and end up in the engagement position. Consequently, it is possible to stabilize the engagement and disengagement operation of the stone forming an engagement claw 86 relative to the planetary gear wheel 45.
In the following, a third embodiment will be described with reference to FIGS. 17 and 18. In the first embodiment, the stone forming the engagement claw 86 is indirectly induced to move by the main spring body 97 of the lever spring 94 via the main lever body 85. The third mode of embodiment differs from the first embodiment in that the stone forming the engagement claw 86 is directly actuated by a spring 294. The configuration elements other than those described below are the same as those of the first embodiment. [0150] (Configuration of the engagement and disengagement lever unit) [0151] FIG. 17 is a plan view of a planetary wheel and an engagement and disengagement lever unit according to the third embodiment, viewed from above.
CH 715 052 A2 [0152] As illustrated in lafig. 17, the engagement and disengagement lever unit 280 comprises a base 284 (synchronous rotating part) and the spring 294 in place of the engagement and disengagement lever 84 and the lever spring 94 of the first embodiment .
The base 284 is configured in annular form to surround the first axis of rotation O1. The base 284 is fitted on the outside of a lever plug 81 and is integrally connected to the lever plug 81. Consequently, the base 284 rotates clockwise around the first axis of rotation O1 in synchronization with the rotation of the lower level constant force wheel 60. An edge 284a of the base 284 facing one side of the stone forming the engagement claw 86 extends along the circumferential direction around the first axis O1 when viewed from the vertical direction. The base 284 includes a projecting portion 284b projecting from the edge 284a outward in the radial direction. The projecting portion 284b is adjacent to the edge 284a clockwise around the first axis of rotation O1. The engagement and disengagement lever unit 280 does not include the lever plug 81, and the base 284 can be directly connected to the lower level tube 61 of the lower level constant force wheel 60.
The spring 294 is a thin leaf spring. The spring 294 extends from one end of the base 284 towards the stone forming an engagement claw 86 anticlockwise around the first axis of rotation O1. The spring 294 rotates around the base 284 outward in the radial direction and extends around the base 284 substantially around a position facing the edge 284a of the base 284 from the outside in the radial direction. The stone forming the engagement claw 86 is attached to one end 294a of the spring 294. Consequently, the spring 294 supports the stone forming the engagement claw 86 movably relative to the base 284. The stone forming the claw engagement 86 projects from the end 294a of the spring 294 to the planetary gear wheel 45 (upward). The end 294a of the spring 294 bears against the edge 284a of the base 284. Consequently, the end 294a of the spring 294 is in sliding contact with the edge 284a of the base 284, and can thus move in the direction circumferential around the first axis of rotation O1.
The end 294a of the spring 294 is arranged with a space with respect to the projecting portion 284b of the base 284 in the anticlockwise direction around the first axis of rotation O1. In addition, part of the spring 294 at the base of the end 294a bears against the protruding portion 284b of the base 284 in a clockwise direction around the first axis of rotation O1. Consequently, the end 294a of the spring 294 can rotate within a predetermined angle range relative to the base 284.
The base 284 rotates clockwise around the first axis of rotation O1, so that the spring 294 is compressed by the projecting portion 284b of the base 284 and rotates clockwise d 'a watch around the first axis of rotation O1. In addition, the movement of the end 294a of the spring 294 anticlockwise around the first axis of rotation O1 relative to the base 284 is limited. In other words, the projecting portion 284b of the base 284 restricts the movement of the stone forming the engagement claw 86 in engagement with the planetary gear wheel 45 in the anticlockwise direction around the first axis of rotation. O1 with respect to base 284.
In addition, the spring 294 allows the movement of the stone forming the engagement claw 86 relative to the base 284 in a clockwise direction around the first axis of rotation O1 while acting on the stone forming the engagement claw 86 by inciting it to move in the anticlockwise direction around the first axis of rotation O1 relative to the base 284. In other words, the stone forming the claw d engagement 86 fixed to the end 294a of the spring 294 is in a state where it has play to move clockwise around the first axis of rotation O1 relative to the base 284. The rotation of the spring 294 clockwise around the first axis of rotation O1 relative to the base 284 is limited by the projecting portion 284b. In other words, the projecting portion 284b of the base 284 restricts the movement of the stone forming the engagement claw 86 in the direction of withdrawal outside the rotation envelope Μ of the planetary gear wheel 45 in the direction of clockwise around the first axis of rotation O1 with respect to the base 284.
[Operation of the engagement and release lever unit) [0159] In the following, an operation of the engagement and release lever unit 280 will be described having the configuration described above. .
Similar to the first embodiment, when the planetary gear wheel 45 and the stone forming the engagement claw 86 are brought into mutual engagement, a tip of a stop tooth 45a of the wheel d the planetary gear 45 engages an engagement surface 86a of the stone forming the engagement claw 86 to end up in a state of strong mutual compression.
When the lower level constant force wheel 60 rotates under the impulse of the energy of the constant force spring 100, the lever plug 81 and the base 284 rotate accordingly in a clockwise direction. around the first axis of rotation O1. When the base 284 rotates, the stone forming the engagement claw 86, supported by the spring 294, moves clockwise around the first axis of rotation O1 in a state where it still has play for move clockwise around the first axis of rotation O1. Therefore, the engagement and release lever unit 280 can be gradually released from the
CH 715 052 A2 planetary gear wheel 45, so that the stone forming the engagement claw 86 can be withdrawn outside the rotation casing Μ of the planetary gear wheel 45. The tip of the tooth stop 45a moves counterclockwise relative to the engagement surface 86a while sliding on the engagement surface 86a.
[0162] FIG. 18 is an explanatory view of the operation of a constant torque mechanism according to the third embodiment and consists of a plan view of a planetary wheel and of an engagement and disengagement lever unit, seen from above .
When the tip of the stop tooth 45a comes into contact with the first edge 86a1 of the engagement surface 86a, a force F applied between the stop tooth 45a and the stone forming an engagement claw 86 approximates clockwise around the first axis of rotation O1. Consequently, the stone forming the engagement claw 86 moves clockwise around the first axis of rotation O1 with respect to the base 284 in a play directed clockwise around. of the first axis of rotation O1. As illustrated in fig. 18, when the tip of the stop tooth 45a exceeds the first edge 86a1 of the engagement surface 86a, the engagement between the stop tooth 45a and the stone forming an engagement claw 86 is released.
As described above, the constant torque mechanism 230 of the embodiment comprises the base 284 of the engagement and release lever unit 280 rotating clockwise around the first axis O1 rotation in synchronization with the rotation of the wheel at constant force of lower level 60 in place of the base 95 of the lever spring 94 according to the first embodiment. In addition, the stone forming the engagement claw 86 rotates clockwise around the first axis of rotation O1 in accordance with the rotation of the base 284; it is capable of engaging with and freeing itself from the planetary gear wheel 45, and is engaged with the planetary gear wheel 45 inside the rotation casing Μ of the gear wheel planetary 45 in order to restrict the rotation of the planetary gear wheel 45, and it is then moved relative to the base 284 so that it can be withdrawn outside the rotation envelope Μ of the planetary gear wheel 45 Consequently, similar to the first embodiment, the fluctuation in the torque transmitted from the base 284 to the exhaust 14 via the constant level lower level wheel 60 can be suppressed. Thus, any fluctuation in the torque transmitted to the exhaust 14 can be eliminated.
In addition, the constant torque mechanism 30 further comprises the spring 294 acting directly on the stone forming the engagement claw 86 to encourage it to move towards the inside of the rotation envelope Μ of the planetary gear wheel 45. According to this configuration, it is possible to prevent the stone forming the engagement claw 86 from being kept in a state where it is removed outside the rotation casing Μ of the planetary gear 45. Therefore, the operation of engaging and disengaging the stone forming the engagement claw 86 from the planetary gear wheel 45 can be stabilized.
In addition, the stone forming the engagement claw 86 is supported by the spring 294. According to this configuration, it is possible to reduce the number of components compared to a configuration in which the stone forming the engagement claw 86 is not supported by the spring.
In addition, the base 284 of the engagement and disengagement lever unit 280 comprises the projecting portion 284b limiting the movement of the stone forming the engagement claw 86 in engagement with the planetary gear wheel 45 anti-clockwise around the first axis of rotation O1 with respect to the base 284. According to this configuration, when the stone forming the engagement claw 86 rotates clockwise around the first axis of rotation O1 with the base 284, the stone forming the engagement claw 86 can move anticlockwise around the first axis of rotation O1 relative to the base 284, but in such a way that it is possible to prevent the stone forming the engagement claw 86 from ever being able to be released from the planetary gear wheel 45. Consequently, it is possible to stabilize the engagement operation and d clearance of the stone forming an engagement claw 86 relative to the planetary gear wheel 45.
In addition, the base 284 of the engagement and release lever unit 280 includes the projecting portion 284b limiting the movement of the stone forming the engagement claw 86 when it is withdrawn outside the rotation envelope Μ of the planetary gear wheel 45 clockwise around the first axis of rotation O1 relative to the base 284. According to this configuration, when the stone forming the engagement claw 86 is retracts outside the rotation envelope Μ of the planetary gear wheel 45, the stone forming the engagement claw 86 can move clockwise around the first axis of rotation O1 relative to the base 284, but so that the stone forming the engagement claw 86 can again penetrate inside the rotation envelope Μ of the planetary gear wheel 45 and end up in the engagement position. Consequently, it is possible to stabilize the engagement and disengagement operation of the stone forming an engagement claw 86 relative to the planetary gear wheel 45.
Fourth embodiment [0170] In the following, a fourth embodiment will be described with reference to FIGS. 19 and 20. The fourth embodiment differs from the first embodiment in that the stone forming the engagement claw 86 is arranged
CH 715 052 A2 so that it can oscillate around a third axis of rotation 03 different from the first axis of rotation O1. The configurations other elements than those described below are the same as those of the first embodiment.
[0171] (Configuration of the engagement and disengagement lever unit) [0172] Fig. 19 is a plan view of a planetary wheel and an engagement and disengagement lever unit of the fourth embodiment, viewed from above.
As illustrated in FIG. 19, the engagement and disengagement lever unit 380 a stone forming an engagement claw 86 supports so that it can oscillate around the third axis of rotation 03. The third axis of rotation 03 is located in an offset position in the plane of the plate 23 (see fig. 4) relative to the first axis of rotation O1 and the second axis of rotation 02. The engagement and disengagement lever unit 380 is fixedly supported by an upper end of a lower level tube 61 of a lower level constant force wheel 60. The engagement and disengagement lever unit 380 comprises an engagement and disengagement lever 384 and a spring lever 394 in place of the engagement and disengagement lever 84 and the lever spring 94 of the first embodiment.
The lever spring 394 is fixedly supported by a lever plug 81. The lever spring 394 comprises a base 395 (synchronous rotating part) fixed to the lever plug 81 and a main spring body 397 extending from base 395.
The base 395 is configured in annular form surmounting the first axis of rotation O1. The base 395 is fitted to the outside of the lever plug 81 and is integrally connected to the lever plug 81. Consequently, the base 395 rotates clockwise around the first axis of rotation O1 in synchronization with the rotation of the wheel at constant force of lower level 60. The base 395 is provided with a protruding lever pin 398 (first limitation part). The lever pin 398 is arranged between the stone forming an engagement claw 86 and the first axis of rotation O1 when viewed from the vertical direction. The lever pin 398 has a cylindrical shape and projects upward from the base 395. In addition, the engagement and release lever unit 380 may not include the lever plug 81 and the base 395 may be directly connected to the lower level tube 61 of the lower level constant force wheel 60.
The main spring body 397 is a thin leaf spring. The main spring body 397 extends from one end of the base 395 toward the stone forming the engagement claw 86 counterclockwise. The main spring body 397 rotates around the base 395 outward in the radial direction and extends to a position facing the stone forming the engagement claw 86 counterclockwise around of the first axis of rotation O1 when viewed from the vertical direction.
The engagement and disengagement lever 384 is rotatably mounted around the third axis of rotation 03 relative to the base 395 of the lever spring 394. The third axis of rotation 03 is disposed in a fixed position relative to the base 395 of the lever spring 394. Consequently, the engagement and disengagement lever 384 is arranged so as to be able to carry out a movement of revolution around the first axis of rotation O1. In the example illustrated, the third axis of rotation 03 is arranged outside the lever plug 81 in the radial direction relative to the lever pin 398. The engagement and disengagement lever 384 comprises a main body of lever 385 and the stone forming the engagement claw 86 supported by the main lever body 385.
The main lever body 385 is disposed below the planetary gear wheel 45 of the planetary wheel 43, and above the base 395 of the lever spring 394. The main lever body 385 is supported rotatably relative to the base 395 by a lever rotation shaft 389 extending along the third axis of rotation 03. The stone forming the engagement claw 86 is fixed to the main lever body 385. Consequently, the stone forming the engagement claw 86 is arranged so as to be able to oscillate around the third axis of rotation 03. The stone forming the engagement claw 86 projects from the main lever body 385 towards the planetary gear wheel 45 (to the top). The stone forming the engagement claw 86 is arranged outside the lever plug 81 in the radial direction from the third axis of rotation 03.
The main lever body 385 bears against the lever pin 398 clockwise around the third axis of rotation 03. Consequently, the movement of the main lever body 385 in the opposite direction clockwise around the third axis of rotation 03 is restricted by the lever pin 398. That is to say, the lever spring 394 including the lever pin 398 restricts the movement of the stone forming a claw engagement 86 engaged with the planetary gear wheel 45 counterclockwise around the third axis of rotation 03 relative to the base 395.
The main lever body 385 bears against one end of the main spring body 397 of the lever spring 394 coming from an anti-clockwise direction around the third axis of rotation 03. Consequently, the movement of the main lever body 385 is allowed clockwise around the third axis of rotation 03 relative to the base 395 while being pushed by the main spring body 397 counterclockwise a watch around the third axis of rotation 03 relative to the base 395 of the lever spring 394. Consequently, the stone forming the engagement claw 86 fixed to the main lever body 385 is located
CH 715 052 A2 in a state where it has a clearance to move clockwise around the third axis of rotation 03 relative to the base 395.
Here, the third axis of rotation 03 is disposed between the stone forming the engagement claw 86 and the first axis of rotation O1 in the radial direction of the lever plug 81. Consequently, the lever pin 398 of the spring lever 394 restricts the movement of the stone forming the engagement claw 86 in engagement with the planetary gear wheel 45 in the anti-clockwise direction around the first axis of rotation O1 relative to the base 395. In addition, the stone forming the engagement claw 86 is in a state where it has clearance to move clockwise around the first axis of rotation O1 relative to the wheel at constant force of lower level 60. The direction along the clockwise direction around the first axis of rotation O1 is a direction parallel to the clockwise direction around the first axis of rotation O1 or slightly inclined by clockwise around the first axis of rotation O1. The same is applied to a direction along counterclockwise around the first axis of rotation O1.
[0182] (Operation of the engagement and release lever unit) [0183] In the following, the operation of the engagement and release lever unit 380 having the configuration described above will be described. .
Similarly to the first embodiment, at the moment when the planetary gear wheel 45 and the stone forming the engagement claw 86 come into engagement with each other, the tip of a tooth d The stop 45a of the planetary gear wheel 45 engages with an engagement surface 86a of the stone forming the engagement claw 86 to be in a state of strong mutual compression.
When the lower level constant force wheel 60 rotates under the impulse of the energy of the constant force spring 100, the base 395 of the lever spring 394 rotates accordingly clockwise around of the first axis of rotation O1. When the base 395 rotates, the engagement and disengagement lever 384 performs a movement of revolution clockwise around the first axis of rotation O1. Then, the stone forming the engagement claw 86 included in the engagement and release lever 384 moves clockwise around the first axis of rotation O1, in a state where it has play for move clockwise around the first axis of rotation O1. Consequently, the engagement and disengagement lever unit 380 can be gradually released from the planetary gear wheel 45, so that the stone forming the engagement claw 86 is withdrawn outside the casing. rotation M of the planetary gear wheel 45. The tip of the stop tooth 45a moves anticlockwise with respect to the engagement surface 86a while sliding on the engagement surface 86a.
[0186] FIG. 20 is an explanatory view of the operation of a constant torque mechanism of the fourth embodiment and is a plan view of the planetary wheel and the engagement and disengagement lever unit, viewed from above.
When the tip of the stop tooth 45a comes into contact with the first edge 86a1 of the engagement surface 86a, a force F applied between the stop tooth 45a and the stone forming the engagement claw 86 approximates clockwise around the first axis of rotation O1. Consequently, the stone forming the engagement claw 86 moves clockwise around the first axis of rotation O1 relative to the base 395 of the lever spring 394 according to a play in the clockwise direction d 'a watch around the first axis of rotation O1. As illustrated in fig. 20, when the tip of the stop tooth 45a exceeds the first edge 86a1 of the engagement surface 86a, the engagement between the stop tooth 45a and the stone forming the engagement claw 86 is released.
As described above, the constant torque mechanism 330 of the embodiment described comprises the base 395 of the lever spring 394 rotating clockwise around the first axis of rotation O1 in synchronization with the rotation of the lower level constant force wheel 60 in place of the base 95 of the lever spring 94 of the first embodiment. In addition, the stone forming the engagement claw 86 rotates clockwise around the first axis of rotation O1 in accordance with the rotation of the base 395, is capable of engaging the wheel. planetary gear 45 and to release it, comes into engagement with the planetary gear wheel 45 inside the rotation envelope M of the planetary gear wheel 45 to limit the rotation of the gear wheel planetary 45, and is then moved relative to the base 395 in order to be able to withdraw outside the rotation envelope M of the planetary gear wheel 45. Consequently, in a similar manner to the first embodiment, the fluctuation of the torque transmitted from the base 395 to the exhaust 14 via the lower level constant force wheel 60 can be eliminated. Consequently, any fluctuation in the torque transmitted to the exhaust 14 can be eliminated.
In addition, the constant torque mechanism 30 further comprises the main spring body 397 acting indirectly on the stone forming the engagement claw 86 to encourage it to move towards the inside of the rotation envelope. M via the main lever body 385. According to this configuration, it is possible to prevent the stone forming the engagement claw 86 from being maintained in a state where it is withdrawn outside the rotation envelope M of the wheel planetary gear 45. Therefore, the engagement and disengagement operation of the stone forming the engagement claw 86 relative to the planetary gear wheel 45 can be stabilized.
CH 715 052 A2 [0190] In addition, the base 395 of the lever spring 394 includes the lever pin 398 restricting the movement of the stone forming the engagement claw 86 in engagement with the planetary gear wheel 45 in the direction counterclockwise around the first axis of rotation O1 with respect to the base 395. According to this configuration, when the stone forming the engagement claw 86 rotates clockwise around the first axis of rotation O1 with the base 395, the stone forming the engagement claw 86 can move in a direction anti-clockwise around the first axis of rotation O1 relative to the base 395, but in such a way so that it is possible to prevent the stone forming the engagement claw 86 from ever being able to be released from the planetary gear wheel 45. Consequently, it is possible to stabilize the engagement operation and for clearing the stone forming the engagement claw 86 relative to the planetary gear wheel 45.
In addition, the stone forming the engagement claw 86 is arranged so as to be able to oscillate around the third axis of rotation 03, which is different from the first axis of rotation O1 and from the second axis of rotation O2, with respect to the base 395 of the lever spring 394. According to this configuration, since a rotation shaft of the stone forming the engagement claw 86 is disposed on the third rotation axis 03 different from the first rotation axis O1, it is possible to improve the degree of freedom in the design of the constant torque mechanism 30. In addition, the direction in which the stone forming the engagement claw 86 moves when it is released from the planetary gear wheel 45 can be tilted relative to the clockwise direction around the first axis of rotation O1. Consequently, immediately before the clearance between the planetary gear wheel 45 and the stone forming the engagement claw 86, the force F applied between the planetary gear wheel 45 and the stone forming the engagement claw 86 may locate along the direction of movement of the stone forming the engagement claw 86. Therefore, it is possible to allow the stone forming the engagement claw 86 to retract as reliably as possible outside of the rotation envelope M of the planetary gear wheel 45, and of stabilizing the engagement and disengagement operation of the stone forming an engagement claw 86 relative to the planetary gear wheel 45.
The present invention is not limited to the embodiments described above with reference to the drawings, and various examples of variants are conceivable without departing from the scope of its technical teaching.
For example, in the embodiments described above, the fixed wheel 31 is an external toothed wheel, but the invention is not limited to this, and the fixed wheel can also consist of an internal toothed wheel .
Furthermore, in the embodiments described above, the upper level constant force wheel 40 and the lower level constant force wheel 60 are arranged coaxially, but the invention is not limited to such a configuration. The wheel connected to the higher level constant force wheel or the lower level constant force wheel could be interposed between the higher level constant force wheel and the constant force spring, or between a lower level constant force wheel and the spring at constant force.
In addition, in the embodiment described above, the tip of the stop tooth 45a of the planetary gear wheel 45 and the first edge 86a1 of the engagement surface 86a of the stone forming the engagement claw 86 are configured in the form of a surface projecting in a curved manner, but the invention is not limited to such a configuration. The tip of the planetary gear wheel stop tooth and the edge of the engagement surface of the stone forming the engagement claw may not be formed in this curved surface shape. However, in terms of reducing the contact surface pressure between the planetary gear wheel and the engagement claw stone to suppress abrasion between the planetary gear wheel and the engagement claw stone , it is preferable that at least one of the points among the tip of the stop tooth of the planetary gear wheel and the edge of the engagement surface of the stone forming the engagement claw has such a shape. surface projecting in a curved manner.
In addition, in the embodiments described above, the torque adjustment mechanism 110 is provided in the constant torque mechanism, but the torque adjustment mechanism 110 may not be arranged there. In this case, in a state where a predetermined preload is applied to the constant force spring 100, the internal end 102 of the constant force spring 100 can be fixed to the lower level tube 61.
Moreover, without departing from the spirit of the present invention, it is possible to replace configuration elements of the embodiments described above with well-known configuration elements as required, and moreover each embodiments described above can be combined as appropriate.

权利要求:
Claims (11)
[1]
claims
1. Constant torque mechanism (30) comprising:
a support (47) rotating around a first axis (O1) using energy supplied by an energy source;
a planetary gear wheel (45) rotatably mounted on the support (47) and carrying out a complete revolution around the first axis (O1) while turning around a second axis (O2);
a constant force spring (100) being supplied with energy by the rotation of the support (47);
a constant force wheel (60) rotating with the energy of the constant force spring (100) and transmitting the energy of the constant force spring (100) to an exhaust;
CH 715 052 A2 a synchronous rotary part rotating in a first direction of rotation around the first axis (O1) in synchronization with the rotation of the constant force wheel (60); and an engagement claw (86) rotating in the first direction of rotation in accordance with the rotation of the synchronous rotating part, capable of engaging with the planetary gear wheel (45) and being released therefrom, coming engaged with the planetary gear wheel (45) when in the rotation casing (M) of the planetary gear wheel (45) to restrict rotation of the planetary gear wheel (45 ), and then being moved relative to the synchronous rotating part in order to be able to withdraw outside the rotation envelope (M).
[2]
2. Constant torque mechanism (30) according to claim 1, wherein the engagement claw (86) is moved in a direction corresponding to the first direction of rotation relative to the synchronous rotary part to withdraw outside the rotation envelope (M).
[3]
3. Constant torque mechanism (30) according to claim 1 or 2, further comprising: a spring directly or indirectly compressing the engagement claw (86) towards the inside of the rotation casing (M).
[4]
The constant torque mechanism (30) of claim 3, further comprising: a lever body (85) rotatably carrying the engagement claw (86) relative to the synchronous rotating portion, and which is arranged to dissociated from the spring.
[5]
5. Constant torque mechanism (30) according to claim 3, wherein the engagement claw (86) is supported by the spring.
[6]
6. Constant torque mechanism (30) according to one of claims 1 to 5, in which the synchronous rotary part comprises a first limiting part limiting the movement of the engagement claw (86), when it is engaged with the planetary gear wheel (45), in a direction extending along a second direction of rotation around the first axis (O1) relative to the synchronous rotating part.
[7]
7. constant torque mechanism (30) according to one of claims 1 to 6, wherein the synchronous rotary part comprises a second limiting part limiting the movement of the engagement claw (86), when the latter is withdrawn outside the rotation envelope (M), in a direction extending along the first direction of rotation relative to the synchronous rotary part.
[8]
8. Constant torque mechanism (30) according to one of claims 1 to 7, in which the engagement claw (86) is arranged so as to be able to oscillate around the first axis (O1) relative to the synchronous rotating part. .
[9]
9. Constant torque mechanism (30) according to one of claims 1 to 7, in which the engagement claw (86) is arranged in an oscillating fashion around a third axis (03) different from the first axis (O1). and the second axis (O2) with respect to the synchronous rotating part.
[10]
10. Movement (10) of a timepiece (1) comprising the constant torque mechanism (30) according to one of claims 1 to 9.
[11]
11. Timepiece (1) comprising the movement (10) of timepiece (1) according to claim 10.
CH 715 052 A2

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EP2957964B1|2017-02-01|Tilting coupling device for timepiece

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CH715052A2|2019-12-13|Constant torque mechanism, timepiece movement, and timepiece.

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WO2013104941A1|2013-07-18|Timepiece with automatic winding

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CH713702A2|2018-10-15|Torque compensation mechanism, constant force mechanism, timepiece movement and timepiece.

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EP2096504B1|2011-11-16|Mechanism for displaying dead seconds

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EP2990880B1|2016-12-21|Clockwork

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CH714862A2|2019-09-30|Return spring, gear train mechanism, timepiece movement, and mechanical timepiece.

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CH713705A2|2018-10-15|Mechanism with constant force, movement of timepiece and timepiece.

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EP3707563A1|2020-09-16|Driving member of a timepiece

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CH716864A2|2021-05-31|Tourbillon for watch movement.

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CH714615A2|2019-07-31|Mechanism for transmitting an arming force, movement and mechanical timepiece.

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CH713658B1|2019-09-30|Watch movement comprising two regulating members.

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CH717288A2|2021-10-15|Stop pawl for clockwork movement.

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CH705304B1|2016-02-29|drive mechanism.

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WO2019102374A1|2019-05-31|Holder for a wheel carrying a display disc

同族专利:

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公开号 | 公开日

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JP2019211404A|2019-12-12|

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JP6566432B1|2019-08-28|

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CN110579953A|2019-12-17|

引用文献:

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JP6057659B2|2012-10-18|2017-01-11|セイコーインスツル株式会社|Constant torque mechanism for watch, movement and mechanical watch equipped with the mechanism|

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JP6040063B2|2013-03-12|2016-12-07|セイコーインスツル株式会社|Torque adjustment device, movement and mechanical watch|

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JP6091297B2|2013-04-04|2017-03-08|セイコーインスツル株式会社|Escapement, movement, and watch|

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JP6143185B2|2013-09-04|2017-06-07|セイコーインスツル株式会社|Operation stabilization mechanism, movement and mechanical watch|

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JP6355102B2|2013-09-04|2018-07-11|セイコーインスツル株式会社|Constant force devices, movements and mechanical watches|

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EP2916177B1|2014-03-05|2018-11-07|Nivarox-FAR S.A.|Hairspring intended for being clamped by a spring washer|

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EP2945026B1|2014-05-14|2018-01-03|ETA SA Manufacture Horlogère Suisse|Quick correction mechanism of a timepiece|

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JP6388333B2|2014-09-08|2018-09-12|セイコーインスツル株式会社|Constant force mechanism, movement and watch|

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JP6968814B2|2015-12-21|2021-11-17|デトラ ソシエテ アノニム|Clock escape device and how such device works|

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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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JP2018109795A|JP6566432B1|2018-06-07|2018-06-07|Constant torque mechanism, watch movement and watch|

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