Frequency stabilization mechanism, movement and mechanical timepiece.

专利摘要:
The present invention relates to a frequency stabilization mechanism, such as a tourtillon, which enables size reduction while achieving improvement in gait precision. The frequency stabilization mechanism includes: an outer cage (32) and an inner cage (33) rotatably arranged with respect to each other; a constant force spring (59) provided between the outer cage (32) and the inner cage (33) and configured to apply a driving torque to the inner cage (33) so that the inner cage (33) rotates by relative to the outer cage (32); a stop wheel (69) provided on the outer cage (32); and a stopper (73) configured to perform engagement and release operations on the stopper wheel (69) following the rotation of the inner cage (33), in which the axis of rotation (L1 ) of the outer cage (32) and the axis of rotation (L6) of the inner cage (33) are concurrent. The invention also relates to a movement and a mechanical timepiece comprising such a mechanism.
公开号:CH710863B1
申请号:CH00305/16
申请日:2016-03-09
公开日:2020-09-30
发明作者:Kawauchiya Takuma；Nakajima Masahiro；Niwa Takashi；koda Masayuki
申请人:Seiko Instr Inc；
IPC主号:

专利说明:

BACKGROUND OF THE INVENTION
1. Field of the invention
[0001] This invention relates to a frequency stabilization mechanism, a movement, and a mechanical timepiece.
2. Description of the prior art
As the main mechanisms determining the precision in the operation of a mechanical timepiece, there is a regulator and an escapement. The regulator is composed of a balance and a hairspring. The spring balance is made to oscillate in a fixed cycle by the elastic force of the balance spring. It is desirable that the position of the gravitational center of the spiral balance is located on the axis of a balance shaft. When the axis of the balance shaft and the position of the center of gravity of the balance spring deviate from each other, if the timepiece is in a vertically raised position, then unnecessary torque is generated due to the off-center gravitational center of the spiral balance. As a result, depending on the direction in which the gravitational force is exerted, an error is generated in the walking accuracy. This error is referred to as the vertical tilt difference.
[0003] Further, the hairspring is also formed in a hairspring configuration, so that, due to the characteristics due to this configuration, a difference in vertical inclination is generated depending on the direction in which the gravitational force is. exerted when the timepiece is in the raised position. In this way, the regulator of a mechanical timepiece involves a difference in vertical tilt due to two factors.
As a mechanism for solving this problem of vertical tilt difference, we know the tourbillon mechanism (frequency stabilization mechanism). In the tourbillon mechanism, the regulator and the escapement are arranged in a single cage, which is rotated in fixed cycles. As a result, it is possible to average the error in the walking accuracy generated by the gravitational force, making it possible to suppress the difference in vertical tilt.
[0005] However, in the above tourbillon mechanism, the rotation is carried out around a single axis, so that it is difficult to eliminate the differential error in the running precision (to which we refer hereinafter as being the difference in horizontal inclination between the case where the timepiece is positioned flat in a horizontal plane and the case where it is in a vertically raised position).
[0006] Under these conditions, various techniques have been proposed to simultaneously eliminate the difference in inclination with respect to the vertical and the difference in inclination with respect to the horizontal.
[0007] For example, a technique has been proposed capable of simultaneously eliminating the difference in vertical inclination and the difference in horizontal inclination by the rotation of the regulator and the exhaust via a plurality of rotating cages around different axes of rotation (see, for example, international publication No. 2004/077171 (patent document 1) and European patent No. 1465024 (patent document 2)).
[0008] Ideally, the regulator oscillates at a fixed oscillation frequency. In fact, however, the amplitude of the spring balance varies under the influence of various error factors, resulting in fluctuation of the cycle of oscillation of the balance spring. As a result of this fluctuation in the oscillation cycle, the running precision of the timepiece deteriorates.
[0009] The sprung balance oscillates through the application of a driving torque generated by the elastic force of a barrel spring, so that, as a consequence of the unwinding of the barrel spring, the angle of oscillation of the balance hairspring is reduced, resulting in a fluctuation in the cycle of oscillation of the hairspring. It is difficult to eliminate this fluctuation of the cycle of oscillation of the balance spring even using the aforementioned tourbillon mechanism. Therefore, to improve the running accuracy, it is desirable to supply the regulator with a fixed amount of energy.
As a mechanism for providing a fixed amount of energy to the regulator, constant force mechanisms are known, such as a winding mechanism. And, a technique has been proposed which further improves walking precision by providing this constant force mechanism independent of the tourbillon mechanism (see, for example, US Patent No. 6948845 (Patent Document 3)).
However, in patent document 3, the mechanism as a whole is rather large in size, and when the mechanism is arranged in a timepiece of limited volume, it is rather difficult to effectively arrange the other mechanisms therein. .
SUMMARY OF THE INVENTION
[0012] One aspect of the present application consists in providing a frequency stabilization mechanism, a movement, and a mechanical timepiece which allows a reduction in size while achieving an improvement in terms of running precision.
To achieve the above aspect, there is provided in accordance with the present application a frequency stabilization mechanism comprising: a plurality of cages intertwined and arranged rotatably with respect to each other; a constant force spring provided between a first and a second adjacent one of the plurality of cages, and which is configured to impart torque to the second cage such that the second cage rotates relative to the first cage; a stop wheel provided on the first cage; and a stopper configured to perform the engaging and releasing operations on the stopper wheel following rotation of the second cage, and wherein the axes of rotation of at least two of the plurality of cages are concurrent.
[0014] Thus, by arranging a constant force spring between two adjacent cages, it is possible to impart a driving torque in rotation to a cage in a stable manner without involving an increase in the size of the mechanism as a whole. Further, due to the fact that the construction consists of a plurality of cages, it is possible to eliminate the difference in horizontal tilt. Therefore, it is possible to provide a frequency stabilization mechanism which is both small and improves gait accuracy.
According to the present application, a frequency stabilization mechanism is provided, in which the stop device and an exhaust / regulator mechanism are provided in a first cage.
[0016] Due to this architecture, it is possible to apply a driving torque in rotation in a stable manner to the first cage equipped with the exhaust / regulator mechanism. Therefore, it is possible to stabilize the rotational torque transmitted to the exhaust / regulator mechanism, because it is possible to stabilize the operation of the exhaust / regulator mechanism.
According to the present application, there is provided a frequency stabilization mechanism, in which two cages are provided; the driving force of a gear train is transmitted to an outer cage, and the stop wheel is provided on the outer cage, while the stop device and the exhaust / regulator mechanism are provided in an internal cage.
Due to this architecture, it is possible to apply a rotational drive torque stably to the internal cage equipped with the exhaust / regulator mechanism while achieving a size reduction.
According to the present application, a frequency stabilization mechanism is provided, in which the exhaust / regulator mechanism is equipped with an exhaust mobile configured to rotate on the internal cage when the internal cage is rotated. , and a spiral balance configured to rotate and oscillate on the internal cage when the exhaust mobile is driven in rotation; and the spiral balance is arranged such that the axis of rotation of the spring balance and the axis of rotation of the outer cage are concurrent.
The fact that the axis of rotation of the spring balance and the axis of rotation of the outer cage are therefore arranged to be concurrent means that the center of rotation of the spring balance is located at the center of rotation of the cage external. Due to this architecture, it is possible to prevent unnecessary space formation in the inner cage and the outer cage. Therefore, it is possible to reliably reduce the size of the frequency stabilization mechanism, and realize an improvement in design.
[0021] In addition, since the spiral balance is mounted in the internal cage, it is possible to stabilize the rotational torque transmitted to the spiral balance. As a result, it is possible to suppress the fluctuation of the oscillation angle of the sprung balance.
According to the present application, there is provided a frequency stabilization mechanism, in which the axis of rotation of the internal cage and the axis of rotation of the spring balance are concurrent.
[0023] Because of this architecture, the provision of at least two cages - the outer cage and the internal cage - give the possibility of orienting the sprung balance in all directions. Therefore, it is possible to provide a frequency stabilization mechanism simplified as much as possible in its structure, and the running precision of which is improved while realizing a reduction in size.
According to the present application, a frequency stabilization mechanism is provided, in which the center of gravity of the sprung balance is located on at least one of the two axes of rotation chosen from the axis of rotation of the internal cage and the axis of rotation of the outer cage.
Because of this architecture, it is possible to make it difficult, because of the rotation of each cage, the action of a centrifugal force on the sprung balance. Therefore, it is possible to stabilize the operation of the spiral balance.
According to the present application, a frequency stabilization mechanism is provided, in which the center of gravity of the internal cage is located on the axis of rotation of the internal cage.
[0027] Due to this architecture, it is possible to minimize the rotational torque required to rotate the internal cage. Therefore, it is possible to improve the transmission efficiency, and improve the walking precision.
[0028] According to the present application, a frequency stabilization mechanism is provided, in which the center of gravity of the outer cage is located on the axis of rotation of the outer cage.
[0029] Due to this architecture, it is possible to minimize the rotational torque required to rotate the outer cage. As a result, it is possible to effectively perform the winding of the constant force spring by the outer cage, making it possible to stabilize the degree of winding of the constant force spring. So, it is possible to improve the transmission efficiency, and improve the walking precision.
According to the present application, there is provided a frequency stabilization mechanism, in which the stop device is equipped with an arm pivoting relative to the outer cage, and configured to swing as a result of the rotation of the internal cage, and a pallet arranged on the arm, capable of being engaged and released from the stop wheel; the pivot axis of the arm is defined in a direction crossing the axis of rotation of the stop wheel; such that the vector of a gear engaging force generated when the stop wheel and the pallet are mutually engaged with each other extends along the direction of the pivot axis of the arms.
[0031] In the case where the pivot axis of the arm is therefore defined in a direction crossing the axis of rotation of the stop wheel, it is possible to prevent the generated gear engagement force from affecting the inner cage when the stop wheel and the pallet are engaged with each other. Therefore, it is possible to minimize the rotational torque required to rotate the inner cage.
According to the present application, a frequency stabilization mechanism is provided, in which the stop device is equipped with an arm pivoting relative to the outer cage and configured to tilt following the rotation of the inner cage, and a pallet arranged on the arm and capable of being engaged and disengaged from the stop wheel; the pivot axis of the arm is configured to extend along the axis of rotation of the stop wheel such that the vector of a gear engagement force generated when the stop wheel and the pallet are mutually engaged with each other, pass over the pivot axis of the arm.
[0033] In the case where the pivot axis of the arm is therefore defined to extend along the axis of rotation of the stop wheel, it is possible to prevent the generated gear engagement force. affect the inner cage when the stop wheel and the pallet are engaged with each other. Therefore, it is possible to minimize the rotational torque required to rotate the inner cage.
According to the present application, a frequency stabilization mechanism is provided, in which the arm is provided with a balancer; and the center of gravity of the arm is located in the pivot axis of the arm.
[0035] Due to this architecture, it is possible to prevent the gravitational force of the arm itself from affecting the oscillation movement thereof due to the tilt of the frequency stabilization mechanism. Therefore, it is possible to maintain a fixed force required to ensure the smooth functioning of the swinging movements of the arm, making it possible to further improve the walking accuracy.
According to the present application, a frequency stabilization mechanism is provided, in which a regulating part is provided to regulate the degree of relative rotation of the two cages kinematically connected to each other by the constant force spring .
Thanks to this architecture, it is possible to prevent the constant force spring from being disarmed beyond a predetermined degree. Therefore, it is possible to apply a rotating driving torque to a desired cage stably.
According to the present application, there is provided a frequency stabilization mechanism, in which, among the two cages mutually connected to one another kinematically by the constant force spring, the outer cage is equipped with a wheel constant force spring winding for winding the spring at constant force; the constant force spring winding wheel is provided with a regulating plate; of the two cages mutually connected to each other by the constant force spring, the inner cage is provided with an engaging insert pin which can mesh with the regulating plate by engaging in a oblong hole; and the regulating plate provided with the oblong hole and the engaging insert pin here constitute the regulating part.
Thanks to this architecture, it is possible to reliably prevent the unwinding of the constant force spring using a simple structure. Therefore, it is possible to reliably improve the walking accuracy while realizing a size reduction of the frequency stabilization mechanism.
According to the present application, a frequency stabilization mechanism is provided, in which the respective rotation cycles of the plurality of cages are defined as corresponding to mutually indivisible whole numbers.
Indeed, in the case where the respective rotation cycles of the cages are mutually divisible numbers, there is an increase in the number of times that the relative orientation of the escape / regulator mechanism (sprung balance) arranged in one of the cages is the same as that of the other cages. For example, assuming that the ratio of the rotation cycles of the two cages is set at 1: 1, and that the sprung balance is arranged in one of the cages, the sprung balance resumes the same orientation when the other cage rotates. Therefore, by determining the rotation cycles of the cages to be equal to mutually indivisible numbers, the sprung balance takes longer to resume the same orientation at the same location. Therefore, it is possible to dissipate the influence of the gravitational force, making it possible to reliably eliminate the difference in horizontal tilt, and to dissipate the stresses applied to the rotating shaft, etc.
According to the present application, there is provided a frequency stabilization mechanism comprising: a fixed wheel, supplied separately from the plurality of cages; and a stop wheel drive wheel integrally attached to the stop wheel and in engagement with the fixed wheel, wherein the number of teeth of the fixed wheel and the number of teeth of the wheel drive wheel of stop are defined as corresponding to mutually indivisible numbers.
Thanks to this architecture, in the case where the respective rotation cycles of the cages are set to mutually indivisible numbers, it is possible to reduce, with a simple structure, the number of times the exhaust / regulator mechanism (spiral balance) arranged in one of the cages takes the same relative orientation as the other cages.
According to the present application, a movement is provided equipped with a frequency stabilization mechanism as described above.
Thanks to this architecture, it is possible to provide a movement allowing a reduction in size while improving the precision of walking.
According to the present application, we provide a mechanical timepiece equipped with a movement as described above.
Because of this architecture, it is possible to provide a mechanical timepiece allowing a reduction in size while improving the precision of the rate.
According to the present application, a constant force spring is arranged between two adjacent cages, thanks to which it is possible to apply a driving torque in rotation to a cage in a stable manner without causing an increase in the size of the mechanism in his outfit. Further, by forming the mechanism by a plurality of cages, it is possible to eliminate the difference in horizontal tilt. Therefore, it is possible to provide a small frequency stabilization mechanism while improving the walking precision.
BRIEF DESCRIPTION OF THE DRAWINGS
[0049]<tb> <SEP> Fig. 1 is a front side plan view of a movement of a mechanical timepiece according to a first embodiment of the present invention.<tb> <SEP> Figure 2 is a schematic sectional view of the mechanical timepiece according to the first embodiment of the present invention.<tb> <SEP> Fig. 3 is a perspective view of a vortex with a constant force device according to the first embodiment of the present invention.<tb> <SEP> Fig. 4 is a perspective view of an outer cage according to the first embodiment of the present invention seen from a side.<tb> <SEP> Fig. 5 is a perspective view of the outer cage according to the first embodiment of the present invention seen from the other side.<tb> <SEP> Figure 6 is a view in the direction of arrow A in Figure 4.<tb> <SEP> Figure 7 is a view in the direction of arrow B in Figure 5.<tb> <SEP> Fig. 8 is a perspective view illustrating how a stop wheel drive wheel and a constant force spring winding wheel mesh with a fixed wheel according to the first embodiment of the present invention. .<tb> <SEP> Fig. 9 is a plan view, seen from the rear side of the outer cage according to the first embodiment of the present invention.<tb> <SEP> Fig. 10 is a perspective view illustrating the positional relationship between a stop wheel and a stop device according to the first embodiment of the present invention.<tb> <SEP> Fig. 11 is a perspective view of an inner cage according to the first embodiment of the present invention seen from a side.<tb> <SEP> Fig. 12 is a perspective view of the inner cage according to the first embodiment of the present invention seen from the other side.<tb> <SEP> Figure 13 is a diagram taken in the direction of arrow C in Figure 11.<tb> <SEP> Figure 14 is a diagram taken in the direction of arrow D in Figure 11.<tb> <SEP> Fig. 15 is a diagram illustrating the positional relationship between the constant force spring winding wheel and a phase regulating plate according to the first embodiment of the present invention.<tb> <SEP> Fig. 16 is a perspective view of the inner cage according to the first embodiment of the present invention, part of which has been deleted.<tb> <SEP> Fig. 17 is a diagram illustrating the operation of the outer cage and the inner cage according to the first embodiment of the present invention.<tb> <SEP> Fig. 18 is a diagram illustrating the operation of the outer cage and the inner cage according to the first embodiment of the present invention.<tb> <SEP> Fig. 19 is a diagram illustrating the operation of the outer cage and the inner cage according to the first embodiment of the present invention.<tb> <SEP> Fig. 20 is a diagram illustrating the operation of the outer cage and the inner cage according to the first embodiment of the present invention.<tb> <SEP> Fig. 21 is a diagram illustrating the operation of the outer cage and the inner cage according to the first embodiment of the present invention.<tb> <SEP> Fig. 22 is a diagram illustrating the operation of the outer cage and the inner cage according to the first embodiment of the present invention.<tb> <SEP> Figures 23A and 23B are diagrams illustrating the gear between a stop wheel and a stop anchor, and the behavior of the stop anchor according to the first embodiment of the present invention. invention; Fig. 23A is a diagram illustrating the stop wheel viewed from the axial direction, and Fig. 23B is a diagram illustrating the stop wheel seen from the radial direction.<tb> <SEP> Figures 24A and 24B are diagrams illustrating the gear between the stop wheel and the stop anchor, and the behavior of the stop anchor according to the first embodiment of the present invention; Fig. 24A is a diagram illustrating the stop wheel viewed from the axial direction, and Fig. 24B is a diagram illustrating the stop wheel seen from the radial direction.<tb> <SEP> Fig. 25 is a perspective view of a modified stop anchor according to the first embodiment of the present invention.<tb> <SEP> Fig. 26 is a perspective view of a vortex with a constant force device according to a second embodiment of the present invention seen from a side.<tb> <SEP> Fig. 27 is a perspective view of the vortex with a constant force device according to the second embodiment of the present invention seen from the other side.<tb> <SEP> Fig. 28 is a perspective view of a vortex with a modified constant force device according to the second embodiment of the present invention.<tb> <SEP> Fig. 29 is a side view of a modification of the vortex with a constant force device according to the second second embodiment of the present invention.<tb> <SEP> Fig. 30 is a perspective view of a vortex with a constant force device according to a third embodiment of the present invention seen from a side.<tb> <SEP> Fig. 31 is a perspective view of the vortex with a constant force device according to the third embodiment of the present invention seen from the other side.<tb> <SEP> Fig. 32 is a perspective view illustrating the positional relationship between the stop wheel and the stop device according to the third embodiment of the present invention.<tb> <SEP> Fig. 33 is a perspective view of a modified stop anchor according to the third embodiment of the present invention.<tb> <SEP> Fig. 34 is a perspective view of a vortex with a constant force device according to a fourth embodiment of the present invention seen from a side.<tb> <SEP> Fig. 35 is a perspective view of the vortex with a constant force device according to the fourth embodiment of the present invention seen from the other side.
DESCRIPTION OF EMBODIMENTS
[0050] In the following, embodiments of this invention will be described with reference to the drawings.
(First embodiment)
(Mechanical timepiece)
[0051] First, the first embodiment of this invention will be described with reference to Figures 1 to 24.
Figure 1 is a plan view of the front side of the movement of a mechanical timepiece 1, and Figure 2 is a schematic sectional view of the mechanical timepiece 1.
As shown in Figures 1 and 2, the mechanical timepiece 1 is composed of a movement 10 and a case (not shown) accommodating this movement 10.
[0054] The movement 10 has a plate 11 constituting a support plate. On the rear side of this plate 11, a dial is arranged (not shown). Reference will be made to the gear train mounted on the front side of the movement 10 as being the front gear train, to the gear train mounted on the rear side of the movement 10 as the rear gear train.
The plate 11 has a winding stem guide hole 11a, in which a winding stem 12 is rotatably mounted.
The position in the axial direction of this winding stem 12 is determined by a switching device having an adjusting lever 13, a rocker 14, a rocker spring 15, and an adjusting lever jumper 16. Further , a winding pinion 17 rotatably arranged on the guide shaft of the winding stem 12.
In this architecture, when the winding stem 12 is rotated in a state in which the winding stem 12 is in a first winding stem position (0th step) closest to the inside of the movement 10 the along the axis of rotation, the winding pinion 17 rotates by means of the rotation of a sliding pinion (not shown). And, by the rotation of the winding pinion 17, a crown wheel 20 in engagement therewith is rotated. And, by the rotation of the drive ring 20, a ratchet wheel 21 engaged therewith is rotated. Then, by the rotation of this ratchet wheel 21, a mainspring (not shown) housed in a movement barrel 22 is wound up.
Apart from the aforementioned movement barrel 22, the front gear train of the movement 10 is formed by a central mobile 25 and a third mobile 26, and performs the function of transmitting the driving torque in rotation of the barrel movement 22. Further, on the front side of movement 10 is arranged a tourbillon 30 provided with a constant force device for controlling the rotation of the front gear train.
The central mobile 25 comprises a shaft 25a, a pinion 25b fixed to the shaft 25a, and a toothed wheel 25c. And, the pinion 25b of the central mobile 25 is in mesh with the movement barrel 22. Apart from this aspect, the central mobile 25 is provided with a carriageway 27, a minute hand 29a mounted on the carriageway 27, of a 28 hour wheel, and a 29b hour hand mounted to this 28 hour wheel.
In this architecture, when the central mobile 25 rotates, the roadway 27 engaged slightly by force in the central mobile 25 rotates simultaneously with it, and the minute hand 29a mounted on the roadway 27 indicates the "minute." Further, on the basis of the roadway rotation 27, the hour wheel 28 is rotated by that of a minute wheel (not shown), and the hour hand 29b mounted to the hour wheel 28 indicates the '"hour."
[0061] In addition, the third mobile 26 comprises a shaft 26a, a pinion 26b fixed to this shaft 26a, and a toothed wheel 26c. And, the pinion 26b of the third mobile 26 is engaged with the toothed wheel 25c of the central mobile 25. Further, the vortex with a constant force device 30 is meshed with the toothed wheel portion 26c of the third mobile 26.
(Tourbillon with a constant force device)
FIG. 3 is a perspective view of the vortex with a constant force device 30.
As shown in Figures 2 and 3, the tourbillon with a constant force device 30 is a mechanism controlling the rotation of the aforementioned front gear train. Further, the tourbillon with a constant force device 30 has a mechanism called a tourbillon mechanism configured to reduce the influence of gravitational force depending on the orientation of a sprung balance 101 described below. Further, the tourbillon with a constant force device 30 is equipped with a constant force device 3 for suppressing a fluctuation in the rotational torque transmitted to an escapement mobile 124 described below.
In the following, the vortex with a constant force device 30 will be described in detail.
The tourbillon with constant force device 30 is rotatably supported by a front cage bridge 23 mounted on the front side of the plate 11 and a rear cage bridge 24 mounted on the rear side of the plate 11. The tourbillon with constant force device 30 is equipped with a fixed wheel 31 fixed to the plate 11 on the side of the front cage bridge 23, an outer cage 32 rotatably supported by the front cage bridge 23 and the rear cage bridge 24, and an inner cage 33 rotatably supported with respect to the outer cage 32 within the outer cage 32.
The fixed wheel 31 is configured substantially in the form of a disc, and has toothing 31a at the peripheral edge of its rear side (plate side 11).
(Outer cage)
[0067] Figure 4 is a perspective view of the outer cage 32 from a first side; Figure 5 is a perspective view of the outer cage 32 from the other side; Figure 6 is a diagram taken in the direction of arrow A visible in Figure 4; and Figure 7 is a diagram taken in the direction of arrow B visible in Figure 5.
As shown in Figures 4 to 7, the outer cage 32 has an outer frame 34 constituting the outer frame of the outer cage. The outer frame 34 is provided with a rear disc-shaped pedestal 35 arranged on the rear side, and a rear disc-shaped pedestal 36 arranged on the front side.
In the following description of the outer cage 32, we will simply refer to the radial direction to indicate the radial direction of each base 35, 36, and simply refer to the peripheral direction to indicate the peripheral direction of each base 35, 36.
The rear base 35 is provided with a pivot 35a projecting towards the rear cage bridge 24. This pivot 35a is rotatably supported by a precious stone bearing (not shown) provided in the rear cage bridge 24 .
On the other hand, the front base 36 is located on the front side of the fixed wheel 31 by a recess 23a formed in the front cage bridge 23. And, on the front side of the front base 36, an external pinion cage 37 is provided, and this outer cage pinion 37 engages with toothed wheel 26c of third mobile 26.
A shaft 38 is forced into the front base 36 and the outer cage gear 37. Due to this shaft 38, the front base 36 and the outer cage 37 rotate integrally. Further, at one end of the shaft 38, a pivot 38a is integrally formed by projecting from the outer cage sprocket 37 toward the front cage bridge 23. This pivot 38a is rotatably supported by a spindle bearing. gemstone (not shown) provided in the front cage bridge 23.
The pivot 35a of the rear base 35 and the pivot 38a of the front base 36 are arranged in the same straight line, and this straight line constitutes the axis of rotation L1 of the outer cage 32.
Between the rear base 35 and the front base 36, four longitudinal uprights 39 are formed integrally and so as to be straddling the rear plinth 35 and the front plinth 36. The longitudinal uprights 39 are formed by integrating a pair of curved portions 39a extending radially outwardly while being curved from base portions 35 and 36, a pair of radial extending portions 39 extending radially outwardly from curved portions 39a , and an axial extension part 39c connecting the distal ends of these radial extension parts 39b.
So by constructing the longitudinal uprights 39, it is possible to prevent any interference between the fixed wheel 31 and the outer frame 34 even if the front base 36 protrudes from the front side of the fixed wheel 31.
In addition, the four longitudinal uprights 39 are arranged in pairs to be in axial symmetry with respect to the axis of rotation L1. In other words, the four longitudinal uprights 39 are arranged such that they form two angular sectors K1 of large interval and two angular sectors K2 of small intervals compared to the angular sectors of large interval K1, and that the angular sectors of large interval K1 and the angular sectors of small interval K2 are formed alternately.
A side frame 41 extending in the peripheral direction for connecting the axial extension portions 39c is integrally formed with the longitudinal posts 39, and substantially centrally thereof in the axial direction of the axial portions d. 'extension 39c. From this side frame 41, the part corresponding to the angular sector of large gap K1 is cut, and an internal cage support part 42 is held in position by means of a fixing by a screw 43 to connect the cut parts.
The inner cage support portion 42 serves to rotatably support the inner cage 33, and is formed by incorporating a disc-shaped bearing seat 44, and a branch 46 extending on both sides of the center. in the radial direction of the running surface 44.
In the center in the radial direction of the bearing seat 44, a gemstone bearing 45 is provided to rotatably support the inner cage 33. The central axis L2 of the gemstone bearing 45 is orthogonal to the axis rotation L1 of the outer cage 32, that is to say, extends along the radial direction of the outer cage 32.
The branch 46 is formed by a screw seat 46a resting against the side frame 41 and is substantially in the form of a parallelepiped such that it is elongated in the direction in which extends the side frame 41, and by a raised portion 46b curved and extending from the proximal end (the side end of the bearing seat 44) of the screw seat 46a towards the opposite side of the side frame 41. And, the bearing seat 44 is connected to the distal end of the elevated part 46b. In other words, the running surface 44 is arranged to be away from the side frame 41.
A screw hole (not shown) is formed on the side of the distal end of the screw seat 46a. The screw 43 is inserted into this screw hole, and is further screwed into the side frame 41, by which the inner cage support part 42 is attached and fixed by the screw 43. On the other hand, a fixed driving wheel exhaust 47 is attached and secured to the proximal end side of the screw seat 46a by a screw 48.
The fixed driving exhaust wheel 47 serves to rotate an exhaust mobile 124 described below, and is formed in a substantially ring-shaped configuration. And, the exhaust drive fixed wheel 47 is arranged such that its central axis is coaxial with the central axis L2 of the gemstone bearing 45 provided in the inner cage support portion 42. Further, the fixed wheel exhaust driver 47 has teeth 47a at the peripheral edge of the side of the axis of rotation L1. Further, the exhaust drive fixed wheel 47 is integrally arranged with a pair of mounting tabs 49 at the position corresponding to the screw seat 46a of the inner cage support portion 42. A screw 48 is inserted. in these mounting brackets 49; Further, the screw is threaded into the screw seat 46a, by which the mounting tabs 49 are attached and secured by the screw 48.
The side frame 41 has a ring-shaped bearing support 51 arranged integrally on the side opposite to the inner cage support portion 42 (fixed exhaust drive wheel 47) with the axis of rotation L1 interposed between them. This bearing support 51 is provided with a ball bearing 52.
[0084] The ball bearing 52 is arranged such that its central axis L3 is coaxial with the central axis L2 of the precious stone bearing 45 provided in the internal cage support portion 42. A turntable 53 is supported by rotatably by the ball bearing 52. The turntable 53 is formed by integrating a substantially disc-shaped main body 53a, and a support shaft 53b protruding from the radial center of the platter main body 53a. This support shaft 53b is rotatably supported by the ball bearing 52.
A constant force spring winding wheel 54 is fixed to the main plate body 53a of the turntable 53, and the constant force spring winding wheel 54 and the turntable 53 rotate integrally. A toothing 54a is formed on the outer peripheral part of the constant force spring winding wheel 54. The teeth 54a mesh with the teeth 31a of the fixed wheel 31 (see FIG. 3).
At the center in the radial direction of the constant force spring winding wheel 54, there is provided a gemstone bearing 55 for rotatably supporting the inner cage 33. Further, an insertion pin 56 projecting in the direction of the rotation axis L1 is mounted to the constant force spring winding wheel 54 at a position offset from that of the gemstone bearing 55 outwardly in the radial direction. This insertion pin 56 cooperates with a phase regulating plate 153 described below to adjust the rotational phase of the inner cage 33 and the constant force spring winding wheel 54.
[0087] In addition, the constant force spring winding wheel 54 is equipped with a piton holder 57 on the side opposite the insertion pin 56 with the precious stone bearing 55 interposed between them. A piton 58 is attached to this piton holder 57 via a fixing screw 57a (see FIG. 9). The outer end portion of the constant force spring 59 is attached to the eyebolt 58 (see Figure 9).
The constant force spring 59 is used to apply a driving torque in rotation to the inner cage 33 relative to the outer cage 32, and is configured in the form of a spiral. The inner end portion of the constant force spring 59 is attached to the inner cage 33 via a ferrule 152.
A stop wheel bearing 61 is attached and fixed by a screw 62 to the side frame 41 in a position corresponding to one of the two angular sectors of small interval K2.
The stop wheel bearing 61 is formed by incorporating a disc-shaped rolling seat 63, and a pair of branches 64 extending on both sides in the same direction as the side frame 41, in the direction radial of the bearing seat 63. A gemstone bearing 65 is provided centrally in the radial direction of the bearing seat 63.
On the other hand, each branch 64 is formed by integrating a branch main body 64a extending from the bearing seat 63, and a screw seat 64b extending from the distal end of the branch main body 64a. The screw seat 64b is formed such that the direction normal to the plane in which it extends is orthogonal to that of the branch part main body 64a. And, the screw seat 64b is attached and fixed to the side frame 41 by the screw 62 in a state in which it contacts the rear end of the side frame 41. In this attached / fixed state, the bearing seat 63 and the branches 64 face each other at a predetermined distance from the side frame 41.
A substantially disc-shaped raceway 66 is formed to be integrated with the side frame 41 in the opposite position of the stop wheel bearing 61 from the raceway 63. A gemstone bearing 67 is provided for in this bearing seat 66.
And, between the side frame 41 and the stop wheel bearing 61, a stop wheel drive wheel 68 and a stop wheel 69 are arranged, and the stop wheel drive wheel 68 and the stop wheel 69 are rotatably supported by the two gemstone bearings 65 and 67. In this way, the axis of rotation L4 of the stop wheel drive wheel 68 and the stop wheel 69 is orthogonal to the axis of rotation of the constant force spring winding wheel 54 (the central axis L3 of the ball bearing 52), that is, it extends along the direction radial of the outer cage 32.
The stop wheel drive wheel 68 and the stop wheel 69 are arranged to be superimposed on each other with a small distance between them, and a shaft 71 is driven into its respective centers in the radial direction. Due to this shaft 71, the stop wheel drive wheel 68 and the stop wheel 69 are integrated with each other. Further, pivots 71a are provided at both ends of shaft 71, and these pivots 71a are rotatably supported by gemstone bearings 65 and 67, respectively. Accordingly, it is possible for the stop wheel drive wheel 68 and the stop wheel 69 to rotate integrally with each other with respect to the side frame 41.
A toothing 68a is formed on the outer peripheral part of the driving wheel of the stop wheel 68. The toothing 68a engages with the teeth 31a of the fixed wheel 31.
[0096] Here, the diameter of the pitch circle of the stop wheel drive wheel 68 is determined to be equal to the diameter of the pitch circle of the constant force spring winding wheel 54. Further, the number of teeth of toothing 68a of the stop wheel drive wheel 68 is set to be the same as the number of teeth of toothing 54a of the constant force spring winding wheel 54.
FIG. 8 is a perspective view illustrating how the stop wheel drive wheel 68 and the constant force spring winding wheel 54 are held in engagement with the fixed wheel 31.
As shown in the drawing, the stop wheel drive wheel 68 and the constant force spring winding wheel 54 are held in engagement with the fixed wheel 31 in a state where their respective axes of rotation ( L4 and L3) are orthogonal to each other. Further, the stop wheel drive wheel 68 and the constant force spring winding wheel 54 are mounted to the outer frame 34, so that when the outer frame 34 rotates about the axis of rotation L1, they rotate simultaneously at the same rotational speed. That is, the number of teeth of the stop wheel drive wheel 68 and the number of teeth of the constant force spring winding wheel 54 are set to be equal.
The number of teeth of the fixed wheel 31, the number of teeth of the stop wheel drive wheel 68, and the number of teeth of the constant force spring winding wheel 54, are fixed at numbers that are mutually divisible. More specifically, in the present embodiment, the number of teeth of the stop wheel drive wheel 68 and the number of teeth of the constant force spring winding wheel 54 are fixed at 40, and the number of teeth of the fixed wheel 31 is set at 80. However, it is desirable that the number of teeth of the fixed wheel 31, the number of teeth of the stop wheel drive wheel 68, and the number of teeth of the stop wheel of constant force spring winding 54 are defined as being equal to mutually indivisible numbers. This will be discussed in detail below.
As shown in Figure 8, the stop wheel 69 is a member formed, for example, of a material having a crystalline orientation such as a metallic material or a silicon single crystal, and is formed by electroforming, or a technique based on an optical method such as photolithography, for example, the LIGA (Lithographie Galvanoformung Abformung), DRIE (Deep Reactive Ion Etching), MIM (Metal Injection Molding) process, etc.
[0101] On the outer peripheral part of the stop wheel 69, a plurality of hooking parts 72 are formed to project radially outwards. The hooking parts 72 are arranged at equal peripheral intervals.
In this architecture, a stop device 73 is engaged with and released from the stop wheel 69.
[0103] Figure 9 is a plan view of the outer cage 32 from the rear side, and Figure 10 is a perspective view illustrating the positional rotation between the stop wheel 69 and the stop device 73.
[0104] As illustrated in Figures 9 and 10, the stopper 73 has a stopper anchor 74 configured substantially L-shaped in a plan view from the rear side. More specifically, the stop anchor 74 is formed by integrating a stop anchor body 75 arranged on the side of the stop wheel drive wheel 68, a fork 76 arranged on the side of the stop wheel. the constant force spring winding wheel 54, and a link portion 77 connecting the stop anchor body 75 and the fork portion 76.
[0105] Stopper anchor body 75 extends along side frame 41 to which stopper wheel drive wheel 68 is mounted, and has a substantially T-shaped configuration in plan view from the top. inner side in the radial direction of the outer cage 32. More specifically, the stop anchor body 75 is provided with an arm 75a extending in the same direction as the side frame 41 from the vicinity of the end. distal portion of the leg portion 64 of the stop wheel bearing 61 adjacent to the gemstone bearing 65, and a pawl support body 75b extending from the distal end of the arm 75a along the radial direction of the stop wheel drive wheel 68 (stop wheel 69).
[0106] The length of the pawl support body 75b is defined to be approximately the same as the outer diameter of the stop wheel drive wheel 68. At both longitudinal ends of the pawl support body 75b are protrusions 75c. integral with the pawl support 75b and projecting towards the stop wheel 69. Pallets 78a and 78b are mounted respectively to these projections 75c. The vanes 78a and 78b protrude from the protrusions 75c in the longitudinal direction of the pawl support body 75b, and their distal end portion can be contacted with the hook portion 72 of the stop wheel 69. In this way Accordingly, the stopper 73 is engaged with and released from the stopper wheel 69. The operation of engaging with and disengaging the stopper wheel 69 from the stopper 73 will be described in detail below. .
[0107] Fork 76 extends along side frame 41 to which constant force spring winding wheel 54 is mounted. The fork 76 is formed by a forked fork main body 76a arranged in a position corresponding to the center in the radial direction of the constant force spring winding wheel 54, and an arm 76b straddling the proximal end of the body. main fork 76a and linkage portion 77. Main fork body 76a is engaged with a triangular cam 151 (see Fig. 10) provided on inner cage 33.
[0108] A through hole 76c is formed at the proximal end of the arm 76b, and a stop anchor shaft 79 is driven into this through hole 76c. Pivots 79a are integrally formed with the stop anchor shaft 79, at both ends thereof.
[0109] As illustrated in detail in Figures 4 and 5, at the position corresponding to the stop anchor shaft 79 of the side frame 41, there is provided a bearing 80 rotatably supporting the anchor shaft. stop 79.
[0110] The bearing 80 is equipped with a base 81 integral with the side frame 41 and extending in a direction orthogonal to that of the side frame 41, and a support portion 83 attached and fixed to this base 81 by a screw 82.
[0111] At the level of the part of the base 81 crossing the side frame 41, a precious stone bearing 84 is provided. The pivot 79a formed integrally at one end of the stop anchor shaft 79 is rotatably supported by this gemstone bearing 84. Further, at both longitudinal ends of the pedestal 81, threaded bores 85 are provided allowing screwing in screws 82 to attach and secure the support portion 83.
[0112] The support portion 83 is configured in a shape, the cross section of which has substantially the shape of a hat. In other words, the support part 83 is provided with a support part main body 83a configured in a shape whose cross section has substantially a U-shape, allowing the reception of the stop anchor shaft 79, and a pair of flanges 83b integrally formed at the distal end of the supporting part main body 83a. And, the flanges 83b are arranged to lean against the base part 81.
[0113] The flanges 83b have insertion holes (not shown) allowing the insertion of the screws 82, and the screws 82 are inserted into these insertion holes; furthermore, the screws 82 are screwed into the threaded bores 85 of the pedestal 81, through which the support portion 83 is attached and fixed to the pedestal 81.
[0114] In the bottom wall portion 83c of the support portion main body 83a, a gemstone bearing 86 is provided to be coaxial with the gemstone bearing 84 of the pedestal 81. Rotally supported by this stone bearing valuable 86, the pivot 79a is integrally formed at the other end of the stop anchor shaft 79.
[0115] In this way, the stop anchor shaft 79 is arranged so that this axis L5 is parallel to the axis of rotation of the constant force spring winding wheel 54 (the axis center L3 of the ball bearing L3), and orthogonal to the axis of rotation L4 of the stop wheel drive wheel 68 and the stop wheel 69.
[0116] And, the stop anchor 74 in which the stop anchor shaft 79 is driven swings around the axis L5 of the stop anchor shaft 79. By the movement of balance of the stop anchor 74, the pallet 78a arranged at the rear of the stop anchor body 75 approaches towards the stop wheel 69, while the pallet 78b arranged at the front is spaced apart by the stop wheel 69; and, conversely, when the vane 78b arranged at the front approaches the stop wheel 69, then the vane 78a arranged at the rear moves away from the stop wheel 69.
[0117] Consequently, the pallet 78a arranged at the rear of the stop anchor body 75 and the pallet 78b arranged on its front side are successively engaged with the stop wheel 69. This oscillating movement of the anchor stop 74 is based on the rotational movement of the triangular cam 151 engaged with the fork portion 76 of the stop anchor 74. The triangular cam 151 is provided on the inner cage 33.
In this architecture, the center of gravity of the outer cage 32 is located on the axis of rotation L1 of the outer cage 32.
(Internal cage)
[0119] Figure 11 is a perspective view of the inner cage 33 from a first side, Figure 12 is a perspective view of the inner cage 33 from the other side, Figure 13 is a diagram taken in the direction arrow C visible in Figure 11, and Figure 14 is a diagram taken in the direction of arrow D visible in Figure 11.
[0120] As illustrated in Figures 11 to 14, the internal cage 33 has an internal frame 90 constituting the internal frame of the internal cage 33. The internal frame 90 has a support plate 91.
[0121] The support plate 91 is formed to be elongated in the direction of the central axis L2 (see Fig. 5) of the gemstone bearing 45 provided in the inner cage support portion 42 of the outer cage 32. Substantially at the center in the longitudinal direction of the support plate 91, there is an anti-vibration bearing 93. Further, block pillars 94 and 95 are respectively attached and fixed to both longitudinal ends of the support plate 91 by screws 96. The block pillars 94 and 95 are configured to take a substantially U-shaped sectional shape, and are arranged with their respective openings directed towards the longitudinal center of the support plate 91.
[0122] Among the two pillar-blocks 94 and 95, the first pillar-block 94 has a lower part 94a at the central part of which is a pivot 97. The pivot 97 projects outwardly in the longitudinal direction of the support plate 91. The pivot 97 is rotatably supported by the gemstone bearing 45 provided at the inner cage support portion 42 of the outer cage 32.
On the other hand, among the two pillar-blocks 94 and 95, the second block 95 has a lower part 95a at the central part of which is a pivot shaft 98. The pivot shaft 98 protrudes towards outside in the longitudinal direction. Further, a pivot 98a protrudes from the distal end of the pivot shaft 98. This pivot 98a is rotatably supported by the gemstone bearing 55 provided in the constant force spring winding wheel 54.
[0124] In this way, the internal cage 33 is supported by the pivots 97 and 98a relative to the external cage 32 to be rotatable about the central axis L2 of the precious stone bearing 45 provided at the level of the support part. of internal cage 42 and around the central axis L3 of the ball bearing 52 provided at the level of the external cage 32. In other words, the axis of rotation L6 of the internal cage 33 is orthogonal to the axis of rotation L1 of the outer cage 32.
[0125] In addition, are forcibly engaged in the pivot shaft 98 a triangular cam 151, a ferrule 152, and a phase regulating plate 153 in this order from the lower part 95a of the second pillar-block 95. In in other words, the triangular cam 151, the ferrule 152, and the phase regulating plate 153 rotate integrally with the internal cage 33.
[0126] The triangular cam 151 is arranged such that it encourages the stop anchor 74 to make a reciprocating and pendulum movement three times per rotation. The inner end portion of the constant force spring 59 is connected to the ferrule 152. In other words, the inner cage 33 is rotatably supported with respect to the outer cage 32, and is kinematically to the outer cage 32 by the. constant force spring 59.
[0127] Fig. 15 is an explanatory view illustrating the positional relationship between the constant force spring winding wheel 54 and the phase regulating plate 153 in the state where the inner cage 33 is mounted to the outer cage 32 .
[0128] As illustrated in Figures 12 and 15, the phase regulating plate 153 is in the form of a disc, and its outer diameter is defined to be slightly larger than the outer diameter of the constant force spring 59. in its disarmed state. In the state where the inner cage 33 is mounted to the outer cage 32, the phase regulating plate 153 is opposed to the constant force spring winding wheel 54 in the direction of the axis of rotation L6 of the internal cage 33.
[0129] In the position corresponding to the insertion pin 56 provided on the constant force spring winding wheel 54 of the outer cage 32, the phase regulating plate 153 has an oblong hole 154 allowing the insertion of this insertion pin 56. The elongated hole 154 is formed to extend in a curved fashion along the peripheral direction. Further, the oblong hole 154 is formed such that, in the state that the insertion pin 56 is inserted into this oblong hole 154, the rotational angle of the phase regulating plate 153 relative to the constant force spring winding wheel 54 does not deviate more than 60 degrees.
[0130] Referring to Figures 11 to 14, at the end of the opposite side of the support plate 91 of the two pillars-blocks 94 and 95, is arranged a bridge plate 155 so that it is astride the two block pillars 94 and 95. The bridge plate 155 has a substantially ring-shaped running surface 157 arranged coaxially with the anti-vibration bearing 93 provided on the support plate 91. An anti-vibration bearing 158 is provided on this running surface 157.
[0131] Arms 159 are formed integrally with the rolling seat 157, they extend respectively in the direction of the two block pillars 94 and 95 from the lateral surface of the rolling seat 157. At the distal ends of the arms 159 are formed supports 161 integral with the arms 159. These supports 161 are formed in a substantially rectangular configuration to be in accordance with the configuration of the side surfaces of the two pillars 94 and 95. These supports 161 are attached and fixed respectively to the two block pillars 94 and 95 by screws 156. In this way, the support plate 91, the block pillars 94 and 95, and the bridge plate 155 are integrated to form an internal frame 90.
[0132] Here, the size of the internal frame 90, and the size of the internal diameter of the fixed exhaust driving wheel 47 provided on the external cage 32 are fixed at sizes allowing the insertion of the internal frame 90 in the fixed wheel. exhaust drive 47 in the state where the inner cage 33 is mounted to the outer cage 32. In other words, in the state where the inner cage 33 is mounted to the outer cage 32, part of the inner frame 90 from the side of the first pillar-block 94 is inserted into the fixed exhaust drive wheel 47.
[0133] In the internal frame 90, constructed as described above, a sprung balance 101 is rotatably supported by the anti-vibration bearing 93 of the support plate 91 and the anti-vibration bearing 158 of the bridge plate 155 .
(Spiral balance)
[0134] The spring balance 101 is equipped with a balance shaft 103 rotatably supported by the anti-vibration bearings 93 and 158, a balance wheel 104 mounted on the balance shaft 103, and a balance spring 105, and performs a rotational oscillation movement at an oscillation cycle fixed by the energy transmitted by the hairspring 105.
[0135] The balance shaft 103 is a shaft whose diameter is staggered and gradually decreases in steps in the axial direction from substantially the center and when moving towards its axial ends. At both ends of the balance shaft 103, pivots are formed (not shown) projecting axially outward. The pivots are rotatably supported by the anti-vibration bearings 93 and 158, respectively.
[0136] Here, the anti-vibration bearings 93 and 158 are provided substantially centrally in the longitudinal direction of the support plate 91 and that of the bridge plate 155. In other words, the anti-vibration bearings 93 and 158 are arranged so that their respective axes are located on the axis of rotation L1 of the outer cage 32, and that they cross the axis of rotation L1. In other words, the spiral balance 101 is arranged such that its axis of rotation L7 crosses the axis of rotation L1 of the outer cage 32. In addition, the center of gravity of the spring balance 101 is located on the axis of rotation L1. of the outer cage 32, and on the axis of rotation L6 of the inner cage 33.
The axis of rotation L7 rotates with the internal cage 33, so that the fact that the axis of rotation L7 and the axis of rotation L1 are concurrent naturally implies that the axis of rotation L7 and the axis of rotation L1 are not confused.
[0138] The axis of rotation L7 of the spring balance 101 is orthogonal to the axis of rotation L6 of the inner cage 33. In addition, substantially at the center in the axial direction of the balance shaft 103 where the diameter of l The shaft is maximum, a shoulder 103a is formed integrally with the balance shaft 103, and the balance wheel 104 is inserted into and fixed to the balance shaft 103 to be positioned by the shoulder 103a.
[0139] In addition, the balance shaft 103 is provided with a double roller 106 (see FIG. 13) on the opposite side of the balance wheel 104 from the shoulder 103a. The double roller 106 is provided with an inserted cylinder 106a threaded and fixed to the balance shaft 103, and an annular flange 106b integrally formed with the shoulder part 103a on the side of the cylinder part 106a. An impulse pin 107 (see figure 16) is provided on the flange 106b to protrude from the side of the support plate 91. The impulse pin 107 is used to swing an anchor 125 of an escape mechanism. regulator 120 described below.
[0140] The hairspring 105 is, for example, a flat hairspring wound in a hairspring in a single plane, and its internal end part is fixed, by a ferrule 111, to the portion of the balance shaft 103 on the plate. of bridge 155 on the side of the balance wheel 104.
[0141] On the other hand, a peg 109 is mounted to the outer end portion of the hairspring 105. The peg 109 is fixed to a tenon support 110 provided on a bridge plate 155. In addition, the hairspring 105 serves to accumulate energy transmitted to dual roller 106 from the exhaust / regulator mechanism 120 described below, and to transmit this energy to the balance shaft 103 and the balance wheel 104.
(Exhaust mechanism / regulator)
[0142] Figure 16 is a perspective view of the internal cage 33, part of which has been deleted.
[0143] As illustrated in Figures 11 to 13 and in Figure 16, the exhaust / regulator mechanism 120 is mounted to the support plate 91.
[0144] The exhaust / regulator mechanism 120 is equipped with an exhaust mechanism carrier 121 mounted to the support plate 91, an exhaust mobile 124 rotatably supported by the exhaust mechanism carrier 121 and the support plate 91, and an anchor 125.
[0145] The escape mechanism carrier 121 is arranged on the second pillar-block 95 on the side of the balance shaft 103, and has a base 121a configured substantially in the form of a C along the balance shaft 103. .
[0146] On the two lateral sides of the support plate 91, the base 121a has integrated screw seats 121b. Screws 122 are inserted in these screw seats 121b respectively. The screws 122 are screwed into the threaded holes 123 provided in the support plate 91, whereby the base 121a is attached and fixed to the support plate 91.
In the vicinity of the screw seats 121b of the base 121a, there are respectively, coming from material with the screw seats 121b, raised parts 121c, and, in addition, a carrier plate 121d integrated with the raised parts 121c.
[0148] The carrier plate 121d extends from each raised portion 121c on the side of the first pillar-block 94 bypassing the balance shaft 103. Thus, when the exhaust mechanism carrier 121 is viewed from the axial direction of balance shaft 103, an opening 121e is formed in this escape mechanism carrier 121 allowing insertion of the balance shaft 103 and the double roller 106. Further, the carrier plate 121d is integrally formed with the elevated parts 121c, so that it faces the support plate 91 at a predetermined interval.
[0149] The carrier plate 121d, formed as described above, is provided with a first gemstone bearing (not shown) to rotatably support the exhaust mobile 124, and a second gemstone bearing 125a to support rotary anchor 125.
[0150] At the position of the support plate 91 corresponding to the first precious stone bearing, a shaft support 127 is provided. The shaft support 127 serves to support the shaft body 131 of the exhaust mobile 124, and has a substantially annular flange 127a attached to the support plate 91. The flange 127a is arranged so that its central opening is located coaxial with the first precious stone bearing of the carrier plate 121d.
[0151] On the flange 127a, a wall 127b is formed integrally with the flange 127a and protruding from the side opposite to the bridge plate 155. This wall 127b extends from the support plate 91 to the outer side in the radial direction of the fixed exhaust drive wheel 47 provided on the outer cage 32. Further, the wall 127b is configured to take a substantially C-shaped sectional shape, so that the fixed exhaust drive wheel 47 can be opened. Further, on the inner peripheral surface side, at the distal end of wall 127b, a substantially disc-shaped bearing seat 127c is integrally formed with wall 127b such that it is orthogonal to wall 127b. . The bearing seat 127c is provided with a gemstone bearing 128. This gemstone bearing 128 is arranged coaxially with the first gemstone bearing of the escape mechanism carrier 121.
[0152] In this construction, the escape mobile 124 is rotatably supported by the first gemstone bearing of the escape mechanism carrier 121 and the gemstone bearing 128 of the rod support portion 127.
[0153] The exhaust mobile 124 is equipped with the shaft body 131, and an exhaust toothed wheel 132 inserted on the shaft body 131 and fixed thereon. The major part of the shaft body 131 is accommodated in the shaft holder 127. In addition, the end portion of the shaft body 131 on the side of the exhaust mechanism carrier 121 protrudes to reach, via the flange 127a of the shaft support 127, the bearing plate 121d of the exhaust mechanism carrier 121. Further, at both axial ends of the shaft body 131, pivots 131a are respectively formed integrally with the body d. The shaft 131. These pivots 131a are rotatably supported by the first gemstone bearing of the escape mechanism carrier 121st by the gemstone bearing 128 of the shaft carrier 128.
[0154] At the level of the part of the shaft body 131 housed in the shaft support 127, an exhaust pinion 131b is formed integrally with the shaft body 131.
[0155] Here, in the state in which the inner cage 33 is mounted to the outer cage 32, the first pillar-block 94 on the side of the inner frame 90 is inserted into the fixed exhaust drive wheel 47. Further, the wall 127b of the shaft support 127 extends from the support plate 91 to the outer side in the radial direction of the fixed exhaust drive wheel 47 provided on the outer cage 32. Thus, the exhaust pinion 131b is meshing with teeth 47a of the fixed exhaust drive wheel 47.
[0156] The escape gear 132 is a member formed, for example, from a metallic material or from a material with a crystalline orientation such as monocrystalline silicon; and it is formed by electroforming or a technique based on an optical method such as photolithography including the LIGA (Lithographie Galvanoformung Abformung), DRIE (Deep Reactive Ion Etching), and MIM (Metal Injection Molding) processes.
[0157] The escape toothed wheel 132 has a substantially annular hub 133 to be forcibly engaged in the shaft body 131. The shaft body 131 is driven into a through hole 133a formed in this hub 133. In addition, Between the backing plate 91 and the backing plate 121d of the escape mechanism carrier 121, there is the escape gear portion 132.
[0158] On the outer side of the hub 133 in the radial direction, a rim 134 configured in the shape of a ring is provided to surround this hub 133. The rim 134 and the hub 133 are connected by a plurality of (four in this embodiment) spokes 135. The spokes 135 extend along the radial direction, and are arranged at equal peripheral intervals.
[0159] Further, at the outer peripheral edge of the rim 134, a plurality of (twenty in this embodiment) teeth 136 are formed in a special hook-shaped configuration to project radially outward. Paddles 140a and 140b of the anchor 125 are engaged and disengaged with and from the distal ends of these teeth 136.
[0160] On the other hand, the support plate 91 is provided with a precious stone bearing 129 at the position corresponding to the second precious stone bearing 125a of the escape mechanism carrier 121. This precious stone bearing 129 is arranged with coaxial with the second precious stone bearing 125a. In addition, the anchor 125 is rotatably supported by the second gemstone bearing 125a of the escape mechanism carrier 121 and the gemstone bearing 129 of the support plate 91.
[0161] The anchor 125 is used to encourage the exhaust mobile 124 to escape and to encourage it to turn regularly, and is equipped with an anchor bearing 137, a fork body 138 inserted into and fixed within reach of anchor 137, and a pallet rod 139 integral with the fork body 138.
[0162] The anchor bearing 137 is a shaft body, and is rotatably supported by the second gemstone bearing 125a of the escape mechanism carrier 121 and by the gemstone bearing 129 of the support plate. 91.
[0163] The fork body 138 and the pallet rod 139 are formed into a three fork configuration by, for example, electroforming. As the electroforming metal for forming the fork body 138 and the pallet shank 139, it is possible to use, for example, high hardness chromium, nickel, iron, or an alloy containing them.
[0164] Two beams 138a and 138b are connected to the fork body 138. The fork body 138 has, at a connecting portion 138c of the two beams 138a and 138b, an insertion hole 138b allowing the insertion of the anchor span 137. Additionally, the two beams 138a and 138b extend in opposite directions from the connecting portion 138c. Among the two beams 138a and 138b, a beam 138b extends in the direction of the double roller 106 provided on the anchor rod 103.
[0165] Alongside the distal end of the two beams 138a and 138b, slots 138e and 138f are formed respectively to be open towards the side of the exhaust mobile 124. The pallets 140a and 140b are respectively linked and fixed to the slots 138e and 138f by gluing or the like.
[0166] The vanes 140a and 140b are substantially rectangular ruby prisms, and project from the distal ends of the beams 138a and 138b towards the teeth 136 of the escape gear 132.
[0167] At the distal end of a beam 138b are provided entry horns 141 and a protective pin 142 is arranged between the entry horns 141. In addition, on the inner side of the entrance horns 141 , is formed a pallet carrier 143 in and from which the impulse pin 107 of the balance spring 101 is respectively engaged and disengaged.
[0168] On the other hand, the pallet rod 139 is formed to protrude from the connecting part 138c of the fork body 138 in the direction of the opposite side with respect to the exhaust mobile 124.
[0169] The support plate 91 has, on two lateral sides of the pallet rod 139 and at the positions corresponding to the distal end of the pallet rod 139, stop pins 144a and 144b configured such that they are s 'erect vertically above the support plate 91. Via these stop pins 144a and 144b, the rotational range of the pallet fork body 138 and the pallet rod 139 is regulated.
In this architecture, the center of gravity of the internal cage 33 is located on the axis of rotation L6 of the internal cage 33.
(Operation of the tourbillon with constant force device)
In what follows, the operation of the tourbillon with a constant force device 30 is described.
[0172] First of all, with reference to FIGS. 11, 12 and 16, the operation of the balance with hairspring 101 mounted in the internal cage 33 and of the escape mechanism 120 will be described.
[0173] The sprung balance 101 receives the torque from the escape wheel assembly 124 via the impulse pin 107, and oscillates freely due to this torque and the elastic spring force of the hairspring 105. Due to the oscillation Free from the spiral balance 101, the pallet carrier 143 which can be engaged in and disengaged from the impulse pin 107 swings right and left around the anchor seat 137 with the fork body 138.
[0174] As a result of the swing of the fork body at 138, the two vanes 140a and 140b are brought into contact alternately with the teeth 136 of the escape toothed wheel 132. Consequently, the exhaust mobile 124 s constantly escapes in a fixed cycle.
[0175] Here, the anchor 125 is equipped with the pallet rod 139 formed integrally with the fork body 138, and this pallet rod 139 is confined in a rotational range by the stop pins 144a and 144b. Therefore, it is possible to prevent the anchor 125 from swaying beyond a predetermined range after being subjected to an external shock or the like.
[0176] Next, with reference to Figures 1, 10 and 17 to 24, the operation of the outer cage 32 and the inner cage 33 will be described.
[0177] Figures 17 to 22 are diagrams illustrating the operation of the outer cage 32 and the inner cage 33; they illustrate the state of the outer cage 32 and of the inner cage 33 at each moment of the cycle. Figures 23A, 23B, 24A and 24B illustrate the gearing engagement state of the stop wheel 69 and the stop anchor 74, and the behavior of the stop anchor 74; Figures 23A and 24A illustrate the stop wheel 69 viewed from the axial direction, and Figures 23B and 24B illustrate the stop wheel 69 seen from the radial direction.
[0178] As shown in Figures 1 and 17, in the outer cage 32, the outer cage pinion 37 is engaged with the toothed wheel 26c of the third mobile 26, so that the rotational force of the movement barrel 22 is transmitted to the outer cage 32 via the front gear train. In addition, the outer frame 34 tries to rotate around the axis of rotation L1 (see arrow Y1 in Figure 17).
[0179] Then, the driving wheel of the stop wheel 68 provided on the outer frame 34 and in engagement with the teeth 31a of the fixed wheel 31 tries to rotate (see arrow Y2 in FIG. 17), and the wheel constant force spring surround 54 attempts to rotate (see arrow Y3 in Figure 17). The outer frame 34 is configured to rotate every two minutes (120 seconds).
[0180] At this time, when one of the two pallets 78a and 78b of the stop anchor 74 is in contact with (engaged with) the hooking part 72 of the stop wheel 69 rotating integrally with the stop wheel drive wheel 68, the stop wheel drive wheel 68 and the stop wheel 69 stop. Therefore, the outer frame 34 and the constant force spring winding wheel 54 stop.
[0181] Here, as shown in FIG. 10, the hooking part 72 of the stop wheel 69 and the two paddles 78a and 78b of the stop anchor 74 are formed so that the vector F1 of the load (gear engagement force) applied when the vanes 78a and 78b are in contact with the hooking portion 72 is parallel to the axis L5 of the stop anchor shaft 79. Therefore, it It is possible to prevent the torque around the stop anchor shaft 79 from being allowed to act on the stop anchor 74 due to the gear engaging force of the hook portion 72 of the stop wheel 69 and the paddles 78a and 78b of the stop anchor 74.
[0182] On the other hand, as shown in Figure 17, the inner cage 33 is rotatably supported relative to the outer cage 32, and is kinematically connected to the outer cage 32 via the constant force spring 59. Therefore, to Upon receiving the biasing force of the constant force spring 59, the inner frame 90 rotates about the axis of rotation L6 relative to the outer frame 34 (see arrow Y4 in Fig. 17). At this moment, the shaft body 131 of the exhaust mobile 124, in engagement with the fixed driving exhaust wheel 47 of the outer cage 32, is driven in rotation.
[0183] Here, the escapement mobile 124 constitutes the escape mechanism 120, and it is encouraged to escape constantly in a fixed cycle by the anchor 125 and the sprung balance 101. In other words, to Because of the escapement of the exhaust mobile 124 in a fixed cycle, the internal cage 33 rotatably supporting the exhaust mobile 124 repeats the phases of rotation and stop at fixed cycles.
[0184] More specifically, the exhaust mobile 124 rotates at a fixed speed so that the internal frame 90 can make one rotation per minute. In other words, the internal frame 90 rotates once every sixty seconds.
[0185] Thus, examples of the construction indicating a "second" include one in which what corresponds to a seconds hand is arranged on the rear side of the outer peripheral surface of the fixed escape drive wheel 47 and in which a disc with an engraved scale is arranged in the position corresponding to the seconds hand of the internal frame 90. In this architecture, the seconds hand remains at rest, while the scale turns as soon as the internal frame 90 turns, so that it is possible to display a „second“.
[0186] The internal frame 90 makes one rotation per minute, while the central mobile 25 makes one rotation per hour.
[0187] Here, by the rotation of the internal frame 90, the triangular cam 151 integrated into the internal frame 90 is also driven in rotation. By means of the rotation of the triangular cam 151, the stop anchor 74 of the outer cage 32 engaged with this triangular cam 151 swings around the stop anchor shaft 79.
[0188] The triangular cam 151 is configured in a shape intended to cause to make three back and forth movements of the stop anchor 74 per minute in a pendulum movement for one complete revolution, so that the stop anchor 74 makes three reciprocating movements of the balance per minute. As a result, the hooking portion 72 of the stop wheel 69 and the paddles 78a and 78b are engaged and disengaged from each other repeatedly.
[0189] More specifically, assuming, for example, that among the two pallets 78a and 78b of the stop anchor 74, the front surface pallet 78b is engaged with the hooking part 72 of the stop wheel 69. When, in this state, the stop anchor 74 begins to swing as a result of the rotation of the internal frame 90 (triangular cam 151) as shown in Figures 23A and 23B, the front pallet 78b moves to be released from it. the rotational path of the hooking part 72. On the other hand (see arrow Y5 in figure 23B), the rear pallet 78a moves in the direction of the rotational path of the hooking part 72 (see arrow Y6 in Figure 23B).
[0190] Here, as illustrated in detail in FIG. 23B, at the moment when the front pallet 78b is released from the hooking part 72 of the stop wheel 69, the rear pallet 78a is located on the rotational path of the hooking portion 72. Thus, when the front pallet 78b is released from the hooking portion 72 of the stop wheel 69, the stop wheel 69 rotates until the rear surface pallet 78a and the hooking portion 72 are engaged with each other next time. More specifically, the number of hooking parts 72 formed on the stopper wheel 69 is three, and the catching parts 72 are arranged at equal intervals, so that the stopper wheel 69 turns 60 degrees. .
When the stop wheel 69 rotates, the outer frame 34 rotates around the axis of rotation L1; furthermore, the constant force spring winding wheel 54 rotates. Here, the diameter of the pitch circle of the stop wheel drive wheel 68 is determined to be the same as the diameter of the pitch circle of the constant force spring winding wheel 54. Further, the number of teeth of the toothing 68a of the stop wheel drive wheel 68 is set to the same number of teeth of the toothing 54a of the constant force spring winding wheel 54. Therefore, when the stop wheel 69 rotates by 60 degrees, the constant force spring winding wheel 54 also rotates 60 degrees.
[0192] The constant force spring winding wheel 54 is provided with the eyebolt support 57 (eyelet 58), so that when the constant force spring charging wheel 54 rotates, the eyebolt 58 moves by. solidarity with him. By the movement of the pin 58, the constant force spring 59 is raised by 60 degrees. In addition, since the stop wheel 69 stops again after the constant force spring 59, the outer frame 34 also stops. On the other hand, the internal frame 90 rotates relative to the external frame 34 as soon as it undergoes the biasing force of the constant force spring 59 which is wound up. By repeating this, the internal cage 33 and the exhaust mobile 124 continue to rotate at a fixed speed.
[0193] More specifically, changes related to the passage of time in the vortex with the constant force device 30 will be described with reference to FIGS. 17 to 22.
[0194] First, when 20 seconds have elapsed from the state of Fig. 17, the constant force vortex 30 reaches the state like that shown in Fig. 18. When 20 more seconds have passed (ie that is, when 40 seconds have elapsed from the state of Fig. 17), the constant force vortex 30 reaches the state shown in Fig. 19.
[0195] When a further 20 seconds have elapsed (i.e., when 60 seconds have elapsed from the state shown in Fig. 17), the constant force vortex 30 reaches the state shown. in Figure 20.
[0196] When another 20 more seconds have elapsed (i.e., when 80 seconds have elapsed from the state of Fig. 17), the constant force vortex 30 reaches the state. shown in Fig. 21. When another 20 more seconds have elapsed (i.e., when 100 seconds have elapsed from the state of Fig. 17), the constant force vortex 30 reaches the state shown in Fig. 22. And when 120 seconds have elapsed, the outer frame 34 rotates fully back to the state of Fig. 17 again.
[0197] Here, the constant force spring winding wheel 54 provided on the outer cage 32 and the phase regulating plate 153 provided on the inner cage 33 are arranged to be opposed to each other. Further, the insert pin 56 protruding from the constant force spring loading wheel 54 and the slot 154 of the phase regulating plate 153 are engaged with each other. Further, due to this architecture, the rotational angle of the phase regulating plate 153 relative to the constant force winding wheel 54 is not shifted by 60 degrees or more. Therefore, it is possible to prevent the constant force spring 59 from being disarmed beyond a predetermined degree.
[0198] In this way, in the first embodiment described above, the tourbillon with constant force device 30 is formed by the outer cage 32, and the inner cage 33 intended to be rotatable relative to the outer cage 32 Further, the axis of rotation L1 of the outer cage 32 and the axis of rotation L6 of the inner cage 33 are orthogonal to each other. Therefore, the spiral balance 101 provided in the internal cage 33 can be oriented in all directions, making it possible to simultaneously suppress the difference in vertical inclination and the difference in horizontal inclination.
[0199] Furthermore, between the outer cage 32 and the inner cage 33, the constant force spring 59 is arranged such that it connects the outer cage 32 and the inner cage 33. In addition, the engagement operations and release of the stop wheel 69 provided on the outer cage 32 relative to the stop device 73 (stop anchor 74) are carried out repeatedly following receipt of the rotational movement of the inner cage 33. Therefore, it is possible to impart a rotational driving torque to the inner cage 33 in a stable manner without requiring an increase in size of the vortex with constant force device 30.
[0200] In addition, thanks to the fact that the constant force spring 59 arranged between the outer cage 32 and the inner cage 33, and connecting the outer cage 32 and the inner cage 33, it is possible to impart a driving torque rotating to the inner cage 33 in a stable manner. The spring balance 101 undergoes free oscillation by means of the transmission of the rotational torque from the internal cage 33 to the exhaust mobile 124, so that, when a torque is imparted to the internal cage 33 in a stable manner , it is possible to stabilize the angle of oscillation of the spiral balance. Therefore, it is possible to reliably improve the running accuracy of the mechanical timepiece 1.
[0201] The spring balance 101 provided in the inner cage 33 is arranged so that its axis of rotation L7 crosses the axis of rotation L1 of the outer cage 32. Therefore, it is possible to prevent the generation of a space unnecessary between the outer cage 32 and the inner cage 33. Therefore, it is possible to reliably achieve a reduction in size of the tourbillon with constant force device 30, and to realize an improvement in design.
Furthermore, the center of gravity of the spiral balance 101 is located on the axis of rotation L1 of the outer cage 32 and on the axis of rotation L6 of the inner cage 33. Therefore, it is possible to make it difficult any action of the centrifugal force on the spring balance 101 due to the rotation of the cages 32 and 33. Consequently, it is possible to stabilize the operation of the spring balance 101.
[0203] In addition, the center of gravity of the inner cage 33 is located on the axis of rotation L6 of the inner cage 33. Therefore, it is possible to minimize the rotational torque required to rotate the inner cage 33. By Consequently, it is possible to improve the efficiency of the tourbillon with a constant force device 30, and to improve the precision of the rate.
[0204] The center of gravity of the outer cage 32 is located on the axis of rotation L1 of the outer cage 32. Therefore, it is possible to minimize the rotational torque required to rotate the outer cage 32. Accordingly, the The winding of the constant force spring 59 by the outer cage 32 can be effected efficiently, making it possible to stabilize the amount of winding of the constant force spring 59. Thus, it is possible to improve the efficiency of the tourbillon with constant force device 30, making it possible to improve walking precision.
[0205] Furthermore, the axis L5 of the stop anchor shaft 79 for oscillating support the stop anchor 74 is orthogonal to the axis of rotation L4 of the stop wheel 69. In addition, the two paddles 78a and 78b of the hooking part 72 of the stop wheel 69 and the stop anchor 74 are formed such that the vector F1 of the load ( gear) applied in the state in which the vanes 78a and 78b are in contact with the hooking part 72 is parallel to the axis L5 of the stop anchor shaft 79.
[0206] Thus, it is possible to prevent the rotational drive torque acting on the stop anchor shaft 79 from acting on the stop anchor 74 due to the engagement force. gear of the hooking part 72 of the stop wheel 69 and of the vanes 78a and 78b of the stop anchor 74. As a result, no excessive rotational driving torque acts on the inner cage 33 via triangular cam 151. Therefore, it is possible to minimize the rotational torque required to rotate the inner cage 33.
[0207] In addition, the constant force spring winding wheel 54 provided on the outer cage 32 and the phase regulating plate 153 provided on the inner cage 33 are arranged to be opposed to each other. Further, the insert pin 56 projecting from the constant force spring charging wheel 54 and the slot 154 of the phase regulating plate 153 are engaged with each other. In addition, due to this architecture, the rotational angular offset of the phase regulating plate 153 relative to the constant force spring winding wheel 54 does not exceed 60 degrees. Therefore, it is possible to prevent the constant force spring 59 from disarming beyond a predetermined degree. Therefore, it is possible to impart a rotational driving torque to the inner cage 33 stably.
(Modification of the first embodiment)
In the first embodiment described above, the axis of rotation L1 of the outer cage 32 and the axis of rotation L6 of the inner cage 33 are orthogonal to each other. This, however, should not be construed in a limiting manner as the only possible configuration; any other construction in which the axis of rotation L1 of the outer cage 32 and the axis of rotation L6 of the inner cage 33 are concurrent will also work.
[0209] Furthermore, in the first embodiment described above, the outer frame 34 rotates in 120 seconds. This, however, should not be understood in a limiting manner as being the only possible configuration.
[0210] For example, it is possible to induce the outer frame 34 to make a full revolution in 60 seconds by changing the configuration of the triangular cam 151 or by separately providing an amplifier or the like. In the event that the outer frame 34 is prompted to rotate in 60 seconds, it is also possible to indicate the “second” by means of the seconds hand provided on the outer frame 34 and a dial (not shown ).
[0211] Furthermore, in the first embodiment described above, the outer frame 34 is provided with an outer pinion of the cage 37, and this outer pinion of the cage 37 is engaged with the toothed wheel 26c of the third mobile 26. In addition, the driving torque in rotation of the movement barrel 22 is transmitted to the outer cage 32 via the front gear train. This, however, should not be construed in a limiting manner as constituting the only possible arrangement; any other configuration in which the outer frame 34 remains in engagement with one of the toothed wheels constituting the front gear train will also work. For example, it is also possible to form a toothing on the side frame 41 of the outer frame 34, bringing the teeth of this toothing into engagement with a toothed wheel of the front gear train.
[0212] Further, in the first embodiment described above, the fixed wheel 31 is configured substantially in the form of a disc, and the teeth 31a are formed at the peripheral edge of the rear side (on the side of the plate 11 ). In addition, the constant force spring winding wheel 54 and the stop wheel drive wheel 68 are engaged with these teeth 31a. This, however, should not be construed in a limiting manner as being the only possible configuration; each of the elements selected from the fixed wheel 31, the constant force spring winding wheel 54, and the stop wheel drive wheel 68 could also be configured to form a bevel-type gear, i.e. say with referral. In this architecture, it is possible to increase the gear engagement area between the toothed wheels, so that it is possible to improve the efficiency of the transmission.
[0213] Furthermore, in the first embodiment described above, the sprung balance 101 is arranged such that its axis of rotation L7 crosses the axis of rotation L1 of the outer cage 32. This, however, does not should not be construed in a limiting manner as being the only possible configuration; the axes of rotation L1 and L7 may not intersect completely, and a greater or lesser deviation is allowed. In other words, it is only necessary that the spring balance 101 is arranged such that the axis of rotation L7 of the spring balance 101 is located in the vicinity of the axis of rotation L1 of the outer cage 32. This is due to the fact that an error is actually generated during production and a certain clearance is generated in the assembly part of each component. Even in this case, the spring balance 101 is arranged substantially in the center of the inner cage 33, so that it is possible to prevent the generation of unnecessary space between the outer cage 32 and the inner cage 33.
[0214] In addition, in the first embodiment described above, the center of gravity of the sprung balance 101 is located in the axis of rotation L1 of the outer cage 32 and in the axis of rotation L6 of the cage. internal 33. This, however, should not be construed in a limiting manner as being the only possible configuration; any other construction in which the center of gravity of the spiral balance 101 is located on at least one of the axis of rotation L1 of the outer cage 32 and the axis of rotation L6 of the inner cage 33 will also work. Even in the case where the center of gravity of the spiral balance 101 is located on one of the axes among the axis of rotation L1 of the outer cage 32 and the axis of rotation L6 of the inner cage 33, it is possible to 'prevent the centrifugal force of the cage rotating around the axis of rotation on which the center of gravity is located from acting on the balance spring 101. Therefore, it is possible to stabilize the operation of the balance spring 101.
[0215] Further, in the first embodiment described above, the number of teeth of the fixed wheel 31, the number of teeth of the stop wheel drive wheel 68, and the number of teeth of the wheel of constant force spring windings 54 are set at numbers which are mutually divisible. Note, however, that it is desirable that the number of teeth of the fixed wheel 31, the number of teeth of the stop wheel drive wheel 68, and the number of teeth of the force spring winding wheel constant 54 are set to mutually indivisible numbers. Due to this configuration, the balance spring 101 will take longer to resume the same orientation in the same position. Therefore, it is possible to disperse the influence of the gravitational force, making it possible to more reliably eliminate the difference in horizontal tilt, and to disperse the exercise of the stresses applied to the balance shaft 103.
[0216] That is to say, for example, in the case where, as in the first embodiment described above, the number of teeth of the fixed wheel 31, the number of teeth of the driving wheel of stop wheel 68, and the number of teeth of the constant force spring winding wheel 54 are fixed to mutually divisible numbers, the rotation cycles of cages 32 and 33 are also mutually divisible. In this case, as described in relation to the change related to the passage of time in the tourbillon with constant force device 30 with reference to Figures 17 to 22, the balance spring 101 resumes the same orientation every 120 seconds (each time the frame 34 rotates). Thus, the balance spring 101 becomes subject to the influence of gravitational force.
[0217] However, when the number of teeth of the fixed wheel 31, the number of teeth of the stop wheel drive wheel 68, and the number of teeth of the constant force spring winding wheel 54 are fixed. on mutually indivisible numbers (when the rotational cycles of cages 32 and 33 are set to mutually indivisible numbers), it takes the spring balance 101 longer to resume the same orientation in the same position. Therefore, it is possible to disperse the influence of the gravitational force, making it possible to more reliably eliminate the difference in horizontal tilt, and to disperse the exercise of the stresses applied to the balance shaft 103.
[0218] Further, in the first embodiment described above, the stopper anchor 74 of the stopper 73 is formed by integrating the stopper anchor body 75, the fork 76, and the link portion 77, and the fork 76 is formed by the fork main body 76a, and the arm 76b straddling the proximal end of the fork main body 76a and the link portion 77. Further, the body The main fork 76a is engaged with the triangular cam 151 provided on the cage 33. However, the configuration of the stopper anchor 74 is not restricted to this, and the following architecture is therefore acceptable.
[0219] FIG. 25 is a perspective view of a modification of the stop anchor 74 according to the first embodiment. Components which are the same as those of the first embodiment are indicated by the same reference numerals, and its description will be omitted (This also applies to the following embodiments and modifications thereof).
[0220] As shown in this drawing, the main fork body 76a of the stop anchor 74 has, at its distal ends, integrated balancers 76d. Balancers 76d are weights formed of the same material as the stop anchor 74. Balancers 76d are angled and extend symmetrically on the reverse side of each other toward their distal ends. In addition, balancers 76d have a tapered shape towards their distal ends.
[0221] Thanks to the balancers 76d, the center of gravity of the stop anchor 74 as a whole is located on the axis L5 of the stop anchor shaft 79. Therefore, it is possible to prevent the gravitational force of the stop anchor 74 to affect the force required for the swing of the stop anchor 74 due to the vertically raised position and the position without horizontal tilt of the mechanical timepiece 1 Therefore, by modifying the stop anchor 74 of the first embodiment described above, it is possible to prevent changing the necessary pulse force required by the inner cage 33 (triangular cam 151). to swing the stop anchor 74.
[0222] Here, the rotational torque of the internal cage 33 is transmitted to the escapement mobile 124, and the sprung balance 101 undergoes free oscillation, so that the angle of oscillation of the sprung balance is not changed if the rotational torque of the internal cage 33 is not changed. Therefore, due to the balancers 76d, the force required for the rocking movement of the stop anchor 74 of the inner cage 33 is prevented from being changed, whereby it is possible to reliably improve the accuracy of the rate of the mechanical timepiece 1.
[0223] In the above-described modification of the first embodiment, the balancers 76d are integrally formed with the fork main body 76a of the stop anchor 74. This, however, should not be construed in a limiting manner. as to the only possible construction; the balancers 76d can in fact be formed separately from the main fork body 76a, and can then be mounted to the main fork body 76a. In this case, the balancers 76d can be driven into the fork main body 76a; or, for example, screws or the like can be formed on the fork main body 76a and the rockers 76d, and the rockers 76d can be removably mounted on the fork main body 76a. By removably arranging the balancers 76d on the fork main body 76a, it is possible to easily adjust the gravitational position of the stopper anchor 74 by the balancers 76d.
(Second embodiment)
(Tourbillon with constant force device)
[0224] In the following, the second embodiment of this invention will be described with reference to Figures 26 and 27.
[0225] Fig. 26 is a perspective view of a vortex with a constant force device 230 according to the second embodiment from one side, and Fig. 27 is a perspective view of the vortex with a constant force device 230. according to the second embodiment from the other side.
[0226] This second embodiment is identical to the first embodiment described above in that the tourbillon with a constant force device 230 is inserted into the mechanical timepiece 1, and is a mechanism for controlling of the rotation of the front gear train (this also applies to the following embodiments).
[0227] The tourbillon with constant force device 230 according to the second embodiment is equipped with an outer cage 232, and an inner cage 233 provided in the outer cage 232 and having an axis of rotation L26 extending in a direction orthogonal to the axis of rotation L21 of the outer cage 232. In addition, the inner cage 233 is provided with the spring balance 101 and the escapement mechanism 120.
[0228] Here, in the internal cage 233 of the second embodiment, the axis of rotation L26 of the internal cage 233 and the axis of rotation L7 of the spring balance 101 are defined as being the same. With respect to this aspect, this embodiment is considerably different from the first embodiment described above.
[0229] Furthermore, an outer frame 234 of the outer cage 232 is formed to be elongated in the direction orthogonal to the front rear direction of the plate 11 (see Figures 1 and 2), and the axis of rotation L21 of the outer cage 232 is also configured to extend in a direction orthogonal to the front rear direction of the plate 11. The outer cage sprocket 37 is arranged at an end portion in the longitudinal direction of the outer frame 234 , and is engaged with a toothed wheel of the front gear train.
[0230] In addition, on the side of the plate 11 is a fixed wheel 231 on the side opposite to that where the outer cage pinion 37 of the outer cage 232 is located. On the other hand, the outer frame 234 is provided. of a freewheel 205 in mesh with the teeth 231a of the fixed wheel 231, and of a constant force spring winding wheel 254 in engagement with the freewheel 205.
[0231] Here, the axis of rotation of the teeth 231a of the fixed wheel 231 and the axis of rotation of the free wheel 205 are orthogonal to each other. Thus, the fixed wheel 231 and the free wheel 205 can be formed in a bevel gear configuration, i.e. with a return. In this case, it is necessary to provide that the freewheel 205 is provided with an external toothed wheel configured to rotate integrally with it and in engagement with the constant force spring winding wheel 254.
[0232] In this configuration, when the outer frame 234 rotates, the freewheel 205 engaged with the fixed wheel 231 tries to rotate while making a revolution around the fixed wheel 231. In addition, the driving torque rotation of the freewheel 205 is transmitted to the constant force spring winding wheel 254.
[0233] Further, the outer cage 232 provided with a turntable 255 attached to the constant force spring winding wheel 254 and configured to rotate integrally with the constant force spring winding wheel 254. This turntable 255 is provided with the stop wheel 69. On the other hand, the internal cage 233 has vanes (not shown) which can be engaged with and disengaged from the hooking part 72 of the stop wheel. 69. In addition, between the outer cage 232 and the inner cage 233 is disposed a constant force spring (not shown) which kinematically connects the outer cage 232 and the inner cage 233. In addition, the inner cage 233 is actuated in rotation. by the elastic force of this constant force spring.
[0234] In this construction, when the inner cage 233 is rotated by a predetermined angle (more specifically, six degrees in this second embodiment), the engagement between the stop wheel 69 and the paddles is released. , and the outer cage 232 is rotated by a predetermined angle (more specifically, six degrees in this second embodiment). As a result, the constant force spring is wound up. By repeating this, the inner cage 233 and the escape mechanism 120 continue to actuate the movement at a fixed speed.
[0235] Therefore, in the second embodiment described above, even if the axis of rotation L26 of the internal cage 233 and the axis of rotation L7 of the spring balance 101 are configured to be the same, it is possible to 'obtain the same effect as that of the first embodiment described above.
(Modification of the second embodiment)
[0236] In the second embodiment described above, the axis of rotation L21 of the outer cage 232 and the axis of rotation L26 of the inner cage 233 are orthogonal to one another. This, however, should not be construed in a limiting manner as constituting the only possible configuration; any other construction will be suitable as long as the axis of rotation L21 of the outer cage 232 and the axis of rotation L26 of the inner cage 233 are concurrent.
[0237] Furthermore, in the second embodiment described above, the axis of rotation L26 of the internal cage 233 and the axis of rotation L7 of the sprung balance 101 are configured to coincide. This, however, should not be construed in a limiting manner either; any other configuration will be suitable as long as the axis of rotation L26 of the internal cage 233 and the axis of rotation L7 of the spring balance 101 are parallel to each other.
[0238] In addition, the axis of rotation L7 of the spring balance 101 can be arranged as being oblique with respect to the axis of rotation L26 of the internal cage 233. This will be described in detail with reference to FIGS. 28 and 29.
[0239] Fig. 28 is a perspective view of a modification of the vortex with a constant force device 230 according to the second embodiment, and Fig. 29 is a side view of the vortex modification with a constant force device 230 according to the second embodiment.
[0240] As shown in Figures 28 and 29, the inner cage 233 has a rotating body 261 rotatably supporting the inner cage 233 relative to the outer cage 232.
[0241] The rotating body 261 has a base 261a substantially in the form of a disc. One end of a balance shaft 203 is rotatably supported in the center in the radial direction of this base 261a. Furthermore, the base 261a comprises, on a surface 261c on the side opposite to that where the balance shaft 203 is supported and in a position which deviates from the axis of the balance shaft 203 (axis of rotation L7 balance spring 101), a projecting pivot 261b. The pivot 261b extends obliquely with respect to the axis of the balance shaft 203. The pivot 261b thus configured is rotatably supported by a precious stone bearing 235a provided on a running surface 235 of the cage. external 232.
[0242] In other words, the axis of the pivot 261b constitutes the axis of rotation L26 of the internal cage 233, and the axis of rotation L7 of the spiral balance 101 is inclined relative to this axis of rotation L26. The base 261a is also arranged so that its front direction is inclined with respect to the axis of rotation L26.
[0243] On the other hand, an intermediate rotary body 262 is provided on the side opposite the rotary body 261 of the internal cage 233. This intermediate rotary body 262 is arranged between the external cage 232 and the internal cage 233. In addition, the Intermediate rotary body 262 is rotatably supported relative to outer cage 232. Further, the side of inner cage 233 opposite to rotary body 261 is rotatably supported by intermediate rotary body 262.
[0244] More specifically, the intermediate rotating body 262 includes a base portion 262a extending parallel to the base 261a of the rotating body 261. The stop wheel 69, etc. are arranged on this base part 262a. Further, substantially in the center in the frontal direction of the base portion 262a is a gemstone bearing (not shown), and a lower pivot 261d of the inner cage 233 is rotatably supported by this gemstone bearing. . This lower pivot 261d is arranged coaxially with the balance shaft 203.
[0245] Further, the base portion 262a has a shaft 262b protruding from a surface 262c on the side opposite to where a balance shaft 293 is supported, and in a position offset from the axis of rotation. L7 of the balance spring 101. The shaft 262b extends obliquely relative to the axis of the balance shaft 203. The shaft 262b thus constructed is rotatably supported by a ball bearing (not shown) arranged on a rolling surface 236 of the outer cage 232.
[0246] In other words, the axis of the shaft 262b constitutes the axis of rotation L26 of the internal cage 233, and the axis of rotation L7 of the spiral balance 101 is inclined relative to this axis of rotation. L26. The base part 262a is also arranged so that its front direction is inclined with respect to the axis of rotation L26.
[0247] Here, when, as in the second embodiment described above, a formation of two cages is carried out (the outer cage 232 and the inner cage 233), and the axis of rotation L26 of the inner cage 233 and the axis of rotation L7 of the spiral balance 101 are configured to coincide, the orientation in which the spiral balance 101 is directed is restricted.
[0248] Thus, as in the modification of the second embodiment described above, the axis of rotation L7 of the sprung balance 101 is inclined relative to the axis of rotation L2 of the internal cage 233, whereby it is possible to widen the orientation in which the sprung balance 101 is directed. This makes it possible to simultaneously suppress the difference in vertical inclination and the difference in horizontal inclination.
[0249] It is desirable that the angle of inclination θ of the axis of rotation L7 of the spring balance 101 relative to the axis of rotation L26 of the internal cage 233 is 45 degrees. By setting the tilt angle θ to 45 degrees, it is possible to suppress the vertical tilt difference and the horizontal tilt difference more effectively. The reason for this is as follows.
[0250] Even in the case where the angle of inclination θ is fixed at 45 degrees, there is a limitation to the orientation of the balance spring 101 in the internal cage 233. However, when the total range of orientation of the Spiral balance 101 in the case of vertical recovery, and the total range of orientation of the spiral balance 101 in the case of horizontal flat positioning are taken into account, the spiral balance 101 must be oriented in all directions. In other words, a direction of the sprung balance 101 and the frequency of orientation in that direction in the case of vertical inclination are the same as in the case of completely horizontal positioning. Therefore, it is possible to eliminate the error of walking accuracy generated between a fully horizontal position at and a vertically raised position.
[0251] On the other hand, in the case where the angle of inclination θ is less than 45 degrees, even when the total range of orientation of the sprung balance 101 in the case of a vertical bearing, and the total range d The orientation of the spiral balance 101 in the case of a horizontal flat positioning are taken into consideration, there is a direction in which the spiral balance 101 is not oriented. That is to say, when the total range of orientation of the balance spring 101 in the case of a vertical lift, and the total range of orientation of the balance spring 101 in the case of a horizontal position lying flat are different from each other. Therefore, it is impossible to eliminate the error of walking accuracy generated between the horizontal flat position and the vertically raised position. Therefore, it is desirable that the tilt angle θ be equal to 45 degrees.
(Third embodiment)
(Tourbillon with a constant force device)
[0252] In the following, the third embodiment according to this invention will be described with reference to Figures 30 to 32.
[0253] Fig. 30 is a perspective view of a vortex with a constant force device 330 according to the third embodiment from one side, Fig. 31 is a perspective view of the vortex with a constant force device 330 according to the third embodiment from the other side, and Fig. 32 is a perspective view illustrating the positional relationship between a stop wheel 369 and a stop device 373 according to the third embodiment.
[0254] As illustrated in Figures 30 to 32, the difference between the first embodiment described above and the third embodiment is as follows: in the first embodiment described above, the axis of rotation L4 of the stop wheel 69 and the pivot axis of the stop anchor 74 (the L5 axis of the stop anchor shaft 79) are orthogonal to each other, while that in the third embodiment, the axis of rotation L4 and the pivot axis (the axis L5 of a stop anchor shaft 379) are parallel to each other.
[0255] More specifically, a stop wheel 369 is arranged on the inner side of the bearing bracket 51 in the radial direction of an outer frame 334. Additionally, the stop wheel 369 is arranged so that its axis of rotation coincides with the axis of the bearing support 51 (ball bearing 52).
[0256] Further, a stop anchor 374 of a stopper 373 is formed separately by the following elements: a stop anchor body 375 which can be engaged with and disengaged from the stop wheel 369, and a fork 376 to be engaged with a triangular cam (not shown in relation to this third embodiment) provided in the internal cage 33.
[0257] The stop anchor body 375 and the fork 376 are arranged to be opposed to each other in the radial direction of the outer cage 332, and their respective proximal end sides are driven into it. anchor shaft 379 and supported by the latter. Additionally, between the stop anchor body 375 and the fork 376, the stop wheel 369, the constant force spring winding wheel 54, the phase regulating plate 153, the constant force spring 59, and the triangular cam 151 are arranged in this order from the stop anchor body 375.
[0258] On the other hand, the stop anchor shaft 379 is rotatably supported by the bearing 80 of the outer frame 334, and its axis L5 is parallel to the axis of rotation of the winding wheel. constant force spring 54 (the axis of rotation L4 of the stop wheel 369).
[0259] The stop anchor body 375 is configured substantially in a C-shape viewed from the direction of the axis of rotation L4 of the stop wheel 369. More specifically, the stop anchor body 375 s extends in the front rear direction of the plate 11 (see Figures 1 and 2) from the stop anchor shaft 379 along the peripheral direction of the stop wheel 369; overall, it spans approximately half a circle. At both distal ends of the stop anchor body 375, vanes 378a and 378b are integrally formed with the remainder of the anchor body 375; these pallets can be engaged with and respectively disengaged from the hooking part 72 of the stop wheel 369.
[0260] In this construction, when the triangular cam 151 rotates with the rotation of the internal cage 33, the fork 376 of the stop anchor 374 engaged with the triangular cam 151 follows a pendulum movement around the shaft of stop anchor 379. Further, stop anchor body 375 also swings around stop anchor shaft 379. Additionally, paddles 378a and 378b of anchor body stopper 375 are engaged with and respectively disengaged with and from the hooking part 372 of the stopper wheel 369 repeatedly.
[0261] Here, the hooking portion 372 of the stop wheel 369 and the two paddles 378a and 378b of the stop anchor 374 are arranged such that the vector F31 of the load (gripping force d gear) applied in the state in which the vane parts 378a and 378b are in contact with the hooking part 372 which passes on the axis L5 of the stop anchor shaft 379.
[0262] Thus, according to the third embodiment described above, in the case where the axis of rotation L4 of the stop wheel 369 and the pivot axis of the stop anchor 374 (the axis L5 of the stop anchor shaft 379) are parallel to each other, it is possible to prevent the rotational drive torque exerted around the stop anchor shaft 379 to be allowed to act on the stopper anchor 374 due to the engagement force between the hooking portion 372 of the stopper wheel 369 and the paddles 378a and 378b of the anchor stop 374.
[0263] Accordingly, no excessive rotational drive torque is applied to the inner cage 33 via the triangular cam 151. Thus, it is possible to minimize the torque required to rotate the inner cage 33.
[0264] In addition, it is possible to coaxially arrange and integrate the stop wheel 369 and the constant force spring winding wheel 54, so that there is no need to provide the stop wheel drive wheel 68 of the first embodiment described above. Therefore, in comparison with the first embodiment described above, it is possible to reduce the number of components of the vortex with constant force device 330.
[0265] Further, the stopper 373 (stopper anchor 374) can also be reduced in size, and there is no need to form the stopper 374 in an L-shaped configuration, so that it is possible to improve the rigidity of the stop anchor 374.
(Modification of the third embodiment)
[0266] In the third embodiment described above, the stop wheel 369 is arranged on the inner side of the bearing support 51 in the radial direction of the outer frame 334, and its axis of rotation coincides with that of the bearing support 51 (ball bearing 52). This, however, should not be construed in a limiting manner in terms of possible configuration; any other construction remains adequate as long as the axis of rotation L4 of the stop wheel 369 and the pivot axis of the stop anchor 374 (the axis L5 of the anchor rod d 'stop 379) are substantially parallel to each other.
[0267] In the third embodiment described above, in the stopper anchor 374 of the stopper 373, the stopper anchor body 375 and the fork 376 are made as separate components. In addition, the stop anchor body 375 and the fork 376 are arranged to be opposed to each other in the radial direction of the outer cage 332, and their respective proximal ends are force-fitted into and supported. then by the stop anchor shaft 379. However, the construction possibilities for the stop anchor 374 are not restricted to this, and the following construction is also acceptable.
[0268] Figure 33 is a perspective view of a modification of the stop anchor 374 according to a third embodiment.
[0269] As shown in the drawing, a balancer 380 is formed integrally on the fork 376 of the stop anchor 374, on the opposite side with respect to the stop anchor shaft 379. The balancer 380 is a weight formed of the same material as the fork 376, and extends in a direction orthogonal to the arm 376b of the fork 376 and the axis L5 of the stop anchor shaft 379. The balancer 380 comprises two main bodies of weights 380a arranged respectively on each side of the stop anchor shaft 379. Each of these main bodies of weight 380a is formed as a 1/4 of a circle seen from the direction of the axis L5 of the shaft stop anchor 379.
[0270] By providing the balancer 380, the center of gravity of the stop anchor 374 as a whole is located on the axis L5 of the stop anchor shaft 379. Therefore, it is possible to 'prevent the gravitational force of the stop anchor 374 from affecting the force required for the swing of the stop anchor 74 due to vertical rise and horizontal flat positioning of the workpiece. mechanical timepiece 1. Therefore, according to this modification of the stop anchor 374 of the third embodiment described above, it is possible to prevent the force required by the inner cage 33 (triangular cam 151) to swing the stop anchor 374 be modified. Therefore, it is possible to reliably improve the running accuracy of the mechanical timepiece 1.
[0271] In the modification of the third embodiment described above, the balancer 380 is integrally formed on the fork 376 of the stop anchor 374. This, however, should not be construed in a limiting manner. possible configurations; the balance 380 could also be formed independently of the fork 376, and mounted to the fork 376.
[0272] In this case, the balancer 380 can be force-fitted into the fork 376; or, for example, it is also possible to form a screw or the like on the fork 376 and the balancer 380, by arranging the balancer 380 removably with respect to the fork 376. By arranging the balancer 380 removably on the fork. the fork 376, it is possible to easily adjust the position of the center of gravity of the stop anchor 374 by the balancer 380.
[0273] Further, instead of being formed on the fork 376, the balancer 380 can be formed on the stop anchor body 375 of the stop anchor 374. In other words, any construction may be suitable as long as the center of gravity of the stop anchor 374 as a whole is located on the axis L5 of the stop anchor shaft 79 by the balance 380.
(Fourth embodiment)
(Tourbillon with a constant force device)
[0274] In the following, the fourth embodiment of this invention will be described with reference to Figures 34 and 35.
[0275] Fig. 34 is a perspective view of a vortex with a constant force device 430 according to the fourth embodiment from one side, and Fig. 35 is a perspective view of the vortex with a constant force device 430 according to the fourth embodiment from the other side. In the fourth embodiment, components which are the same as those of the second embodiment described above are indicated by the same reference numerals, and its description will be omitted.
[0276] As shown in Figures 34 and 35, in the tourbillon with constant force device 430 according to the fourth embodiment, a third cage 404 is further added to the tourbillon with constant force device 230 according to the second embodiment. described above.
[0277] More specifically, the third cage 404 has a third frame 406 formed to surround the outer cage 232 from the outside. The basic construction of the third frame 406 is the same as that of the outer cage 32 of the first embodiment described above.
[0278] In other words, the third frame 406 is mainly composed of a rear base 35, a front base 36, a longitudinal frame 39 provided to be straddling the rear base 35 and the front base 36, and a side frame 41. The rear base 35 is provided with a pivot 35a. On the other hand, the front pedestal 36 is provided with a third cage gear 437, and a pivot 437a projecting from the third cage gear 437.
[0279] In addition, the pivot 35a of the rear pedestal 35 is rotatably supported by the rear side cage bridge 24, and the pivot 437a of the third cage sprocket 437 is rotatably supported by the front side cage bridge 23 Further, the front gear train is meshed with the third cage gear 437, and the rotational driving torque of the front gear train is transmitted to the third cage 404 by the third cage gear 437.
[0280] The fixed wheel 35 is located on the front side of the third cage 404. Furthermore, the side frame 41 of the third frame 406 is provided with two outer cage bearings 442a and 442b arranged one opposite the other. , with the axis of rotation L8 of the third cage 404 in the center. The outer cage bearings 442a and 442b serve to rotatably support the outer cage 232, and are respectively equipped with gemstone bearings (not shown).
[0281] Among the two outer cage bearings 442a and 442b, a first outer cage bearing 442b (the one on the right hand needle side in FIG. 35) is provided, on the inner surface side, with a fixed wheel outer cage drive 431. The fixed outer cage drive wheel 431 corresponds to the fixed wheel 231 of the second embodiment described above, and is arranged coaxially with the gemstone bearing (not shown) of the cage bearing. 442b so as not to engage with the fixed wheel 31. Further, centrally in the radial direction of the fixed outer cage drive wheel 431, an opening (not shown) is made to allow the insertion of a pivot (not shown) disposed at one end in the longitudinal direction of the outer cage 232. Accordingly, a longitudinal end of the outer cage 232 is rotatably supported by a first outer cage bearing 442b.
[0282] At the other longitudinal end of the outer cage 232 (the right end in FIG. 34) is disposed an outer cage drive wheel 405. This outer cage drive wheel 405 is integrated into the outer frame 234. Further, at the center in the radial direction of the outer cage drive wheel 405, a pivot (not shown) protrudes. This pivot is rotatably supported by the other outer cage bearing 442a. In this way, in the third cage 404, the outer cage 232 is arranged such that its axis of rotation L21 is orthogonal to the axis of rotation L8 of the third cage 404. Further, the outer cage drive wheel 405 is engaged with the fixed wheel 31.
[0283] According to this architecture, when the internal cage 233 is rotated by a predetermined angle, and the engagement between the stop wheel 69 provided on the outer cage 232 and the pallet provided on the inner cage 233 is released, the third cage 404 rotates through a predetermined angle. As the third cage 404 rotates, the outer cage 232 rotates about the axis of rotation L8 of the third cage 404. At this time, the outer cage drive wheel 405 of the outer cage 232 is engaged with the wheel. fixed 31, so that the outer cage 232 rotates around the axis of rotation L21 of the outer cage 232 while rotating about the axis of rotation L8 of the third cage 404.
[0284] Then, the freewheel 205 engaged with the fixed outer cage drive wheel 431 provided on the third cage 404 rotates while making a revolution around the fixed outer cage drive wheel 431. In addition, the wheel of constant force spring winding 254 engaged with freewheel 205 rotates to wind a constant force spring (not shown). By repeating this, the inner cage 233 and the escape mechanism 120 continue to actuate the movement at a fixed speed.
[0285] Here, when, as in the second embodiment described above, the axis of rotation L26 of the internal cage 233 and the axis of rotation L7 of the balance spring 101 are configured to be merged while forming a system with two cages (the outer cage 232 and the inner cage 233), there is a limitation to the direction in which the balance spring 101 is oriented.
[0286] However, in this fourth embodiment, the third cage 404 is also provided in addition to the two cages 232 and 233 of the second embodiment described above, and the axis of rotation L8 of the third cage 404 and the axis of rotation L21 of the outer cage 232 are orthogonal to each other, whereby it is possible to orient the spiral balance 101 in all directions.
[0287] Further, in the second embodiment described above, in order to bring the cage outer gear 37 and a toothed wheel of the front gear train into engagement with each other, it is necessary to 'arrange the toothed wheel orthogonally to the other toothed wheels of the front gear train; furthermore, to rotatably support the outer cage 232, it is necessary to perform machining on the platen 11, etc. However, due to the configuration of the fourth embodiment, it is possible to put a toothed wheel of the front gear train in mesh with the third cage gear 437, with all the toothed wheels of the front gear train oriented in. ordinary management. Further, the third cage 404 can be rotatably supported by the front cage bridge 23 and the rear cage bridge 24 (see Figure 2).
The present invention is not limited to the embodiments described above but allows various modifications of the above embodiments without departing from the scope of the spirit of the invention.
[0289] For example, the constructions of the first to fourth embodiments described above (including modifications of the embodiments) can be arbitrarily combined with each other.
[0290] In addition, in the first to third embodiments described above, the tourbillon with constant force device 30, 230, 330 is composed of two cages (the outer cage 32, 232, 332 and the inner cage 33 , 233), and, in the fourth embodiment described above, the tourbillon with constant force device 430 is composed of three cages (the outer cage 232, the inner cage 233, and the third cage 404).
[0291] This, however, should not be construed in a limiting manner in terms of possible configuration; the vortex with constant force device can consist of four or more cages. Also in this case, any other configuration would be acceptable as long as the constant force spring 59 is disposed between at least two adjacent cages, and the axes of rotation of at least two cages are concurrent.
[0292] In addition, in the case where the tourbillon with constant force device is formed by four or more cages, it is desirable to dispose the constant force spring 59 between the two adjacent cages closest to the balance spring 101. Thanks to this with such an arrangement, it is possible to impart a driving torque in a stable manner to the cage in which the sprung balance 101 is arranged. Consequently, it is possible to suppress any fluctuation in the oscillation angle of the balance spring 101.

权利要求:
Claims (17)
[1]
1. Frequency stabilization mechanism comprising:a plurality of intertwined and rotatably arranged cages with respect to each other;a constant force spring (59) disposed between a first and a second adjacent one of the plurality of cages, and which is configured to impart torque to the second cage such that the second cage rotates relative to the first cagea stop wheel (69) provided on one of said cages; anda stop device (73) configured to perform engagement and release operations on the stop wheel (69) following the rotation of the other cage,wherein the rotational axes of at least two of the plurality of cages are concurrent.
[2]
2. A frequency stabilization mechanism according to claim 1, wherein the stop device (73) and an exhaust / regulator mechanism (120) are disposed in the first cage.
[3]
3. A frequency stabilization mechanism according to claim 2, wherein two cages forming said plurality of cages are provided;the driving force of a gear train is transmitted to a said outer cage, and the stop wheel (69) is provided on the outer cage (32); whilethe stop device (73) and the exhaust / regulator mechanism (120) are provided in a said internal cage (33).
[4]
A frequency stabilization mechanism according to claim 3, wherein the exhaust / regulator mechanism (120) is equipped with:an exhaust mobile (124) configured to rotate on the internal cage (33) with the rotation of the internal cage (33), anda spiral balance (101) configured to rotate and oscillate on the internal cage (33) following the rotation of the exhaust mobile (124); andthe spring balance (101) is arranged so that the axis of rotation of the spring balance (101) and the axis of rotation of the outer cage (32) are concurrent.
[5]
5. Frequency stabilization mechanism according to claim 4, wherein the axis of rotation of the inner cage (33) and the axis of rotation of the spring balance (101) are concurrent.
[6]
6. Frequency stabilization mechanism according to claim 4 or 5, wherein the center of gravity of the sprung balance (101) is located on at least one of the axes of rotation among the axis of rotation of the inner cage (33) and the axis of rotation of the outer cage (32).
[7]
7. Frequency stabilization mechanism according to one of claims 3 to 6, wherein the center of gravity of the internal cage (33) is located on the axis of rotation of the internal cage (33).
[8]
8. Frequency stabilization mechanism according to one of claims 3 to 7, wherein the center of gravity of the outer cage (32) is located on the axis of rotation of the outer cage (32).
[9]
9. Frequency stabilization mechanism according to one of claims 3 to 8, wherein the stop device (73) is equipped with:a pivoting arm arranged on the outer cage (32) and configured to tilt following the rotation of the inner cage (33), anda pallet disposed on the arm and capable of being engaged with and disengaged from the stop wheel (69);the pivot axis of the arm is set in a direction crossing the axis of rotation of the stop wheel (69); andthe adjustment is made so that the vector of a gear engaging force generated when the stop wheel (69) and the vane are engaged with each other extends along the direction the pivot axis of the arm.
[10]
10. Frequency stabilization mechanism according to one of claims 3 to 8, wherein the stop device (73) is equipped with:a pivoting arm arranged on the outer cage (32) and configured to tilt following the rotation of the inner cage (33), anda pallet provided on the arm and capable of being engaged with and disengaged from the stop wheel (69);the pivot axis of the arm is fixed so as to extend along the axis of rotation of the stop wheel (69); andthe adjustment is made so that the vector of a gear engaging force generated when the stop wheel (69) and the pallet part are engaged with each other crosses the pivot axis of the arm.
[11]
11. A frequency stabilization mechanism according to claim 9 or 10, wherein the arm is equipped with a balancer; andthe center of gravity of the arm is located on the pivot axis of the arm.
[12]
12. Frequency stabilization mechanism according to one of claims 1 to 11, wherein there is a regulating part regulating the degree of relative rotation of two cages connected to each other by the constant force spring (59 ).
[13]
13. Frequency stabilization mechanism according to claim 12, wherein, among the two cages kinematically connected by the constant force spring (59), the outer cage (32) is provided with a spring force winding wheel. constant (54) to charge the constant force spring (59);the constant force spring winding wheel (54) is provided with a regulating plate (153);of the two cages connected to each other by the constant force spring (59), the inner cage (33) is provided with an insertion pin (56) which can be engaged in an oblong hole (154 ) the regulating plate (153); andthe regulating plate (153) provided with the oblong hole (154) and the insert pin (56) constitute said regulating part.
[14]
14. Frequency stabilization mechanism according to one of claims 1 to 13, wherein the respective rotation cycles of the plurality of cages are set to mutually indivisible whole numbers.
[15]
15. A frequency stabilization mechanism according to claim 14, comprising:a fixed wheel (31) provided separately from the plurality of cages; anda stop wheel drive wheel (68) fixedly attached to the stop wheel (69) and meshed with the fixed wheel (31),wherein the number of teeth of the fixed wheel and the number of teeth of the stop wheel drive wheel (68) are set to mutually indivisible integers.
[16]
16. Movement (10) equipped with a frequency stabilization mechanism according to one of claims 1 to 15.
[17]
17. Mechanical timepiece (1) equipped with a movement (10) according to claim 16.

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同族专利:

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公开号 | 公开日

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US20160266547A1|2016-09-15|

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CN105954996B|2019-08-06|

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CH710863A2|2016-09-15|

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US9568887B2|2017-02-14|

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CN105954996A|2016-09-21|

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