Constant force device, movement and mechanical watch.

专利摘要:
A constant force device includes an output unit (34) that produces an output torque, a constant force spring with a first end attached to an input unit (33), and a second end attached to the input unit (34). output unit (34) which provides a torque to the output unit (34), said input unit (33) periodically restoring a pre-tension in the constant force spring by rotating about an input axis a wheel and lock gear assembly (70) which is rotatably supported about a stopping wheel axle in the input unit (33) and which can circulate about the axis an abutment which is attached to the output unit (34) and which engages with the wheel and lock gear assembly (70) in response to rotation of the wheel assembly and pinion (70) which rotates about the stop wheel axle. In one of its configurations, the device functions as a whirlpool. The invention also relates to a watch movement comprising such a device and a mechanical watch comprising such a movement.
公开号:CH708526B1
申请号:CH01338/14
申请日:2014-09-04
公开日:2018-09-14
发明作者:Kawauchiya Takuma；Niwa Takashi；Nakajima Masahiro；koda Masayuki
申请人:Seiko Instr Inc；
IPC主号:

专利说明:

Description
Background of the Invention 1. Field of the Invention [0001] The present invention relates to a constant force device, a movement and a mechanical watch. 2. Description of Related Art [0002] In a mechanical watch, if the rotational torque transmitted to the wheel and exhaust pinion assembly of an exhaust from a barrel drum varies in response to the course of the Main spring of the barrel drum, the oscillation angle formed by the balance wheel with spring balance changes and the cadence of the watch changes. Therefore, to suppress the variation of the rotational torque transmitted to the wheel and exhaust pinion assembly, a constant force device is proposed in which a constant force spring (pre-tension spiral spring) is disposed between the drum. barrel and exhaust.
For example, as a constant force device, there are known devices which comprise a wheel and stop gear assembly provided with a stop pinion (stop wheel gear), a wheel and pinion gear assembly. exhaust with an exhaust pinion (exhaust wheel shaft), a tension ring mounted on a tension ring pinion, a constant force spring provided between the tension ring and the wheel and pinion gear assembly exhaust and a cam mounted on the exhaust pinion. The constant force spring applies a rotational force to the wheel and exhaust pinion assembly so that the wheel and pinion exhaust assembly rotates relative to the tension ring (see, for example, Japanese Patent No. 4,105,941 [Patent Reference 1]).
According to this configuration, when the rotation of the wheel and exhaust pinion assembly is stopped or restarted by a pallet of a first anchoring device, the rotation of the wheel and pinion stop assembly is stopped. or restarted by a pallet of a second anchoring device. The second anchor is caused to perform an oscillation motion by a fork-shaped portion that engages the cam. Then, if the rotation of the wheel and pinion gear assembly is restarted, the tension ring rotates. In this way, the constant force spring is wound in a regular manner. Therefore, it is possible to suppress the variation of the rotational torque transmitted to the wheel and exhaust pinion assembly.
Incidentally, in the related art described above, the rotation of the wheel and stop gear assembly is stopped or restarted by causing the second anchor device to perform an oscillation movement using cam and fork-shaped portion. There is therefore a problem of increasing energy loss for stopping or restarting the rotation of the wheel and pinion assembly. SUMMARY OF THE INVENTION [0006] The present application consists in providing a constant force device, a movement and a mechanical watch which can reduce a loss of energy to control the rotation of a wheel and pinion gear assembly.
It is proposed a constant force device for adjusting the output torque according to the present application. The constant force device comprises an output unit which produces the output torque by rotating about an output axis, a constant force spring which applies a rotational force to the output unit, an input unit which periodically restores a pre-tension in the constant force spring by rotating about an input axis, a wheel and pinion gear assembly which is rotatably supported (revolution about its axis) about a wheel axle stop in the input unit, and which can circulate (rotation around it) around the input axis, and a stop attached to the output unit that starts engaged with the wheel and idle gear assembly in response to rotation of the wheel and idle gear assembly that circulates around the stopping wheel axle body.
In this way, it is possible to stop or restart the rotation of the wheel assembly and pinion stop and adjust a degree of progression of its rotation by rotating the stop around the axis of exit. Therefore, a movement of the uncoupled abutment of the wheel and idler assembly functions as the rotational movement similar to the wheel and idle gear assembly, thereby reducing the energy loss. In other words, since the transmission path between the wheel and sprocket assembly and the output unit is simplified, it is possible to decrease the loss experienced by the output unit from the set. wheel and pinion. It is therefore possible to more stably guarantee the output torque of the output unit.
In the constant force device according to one embodiment of the present invention, the input axis and the output axis are arranged coaxially with respect to each other.
According to this configuration, since a transmission distance is effectively shortened between the wheel and pinion gear assembly and the output unit, it is possible to further remove the loss.
The constant force device according to one embodiment of the present invention further comprises a wheel and fixed gear assembly which is disposed coaxially with the input shaft and which can not rotate with the input unit and the output unit, in other words a fixed wheel and pinion assembly which is arranged to be separated from the rotational movement of the input unit and the output unit by itself. The wheel and pinion assembly has an axis which serves as the axial center, and which is configured to circulate about the input axis being arranged to engage the wheel and pinion assembly. fixed.
According to this configuration, the wheel and pinion gear assembly can achieve a planetary movement for revolution and rotation, while meshing with the wheel and fixed gear assembly. Therefore, the wheel and pinion assembly can execute the revolution and rotation by circulating around the input axis of the input unit to which the wheel and pinion assembly is attached. way to turn. It follows that it becomes possible to adjust the degree of progression of the rotation of the wheel and pinion assembly using a simple structure. Therefore, it is possible to effectively use the space around the input unit and the wheel and pinion assembly. Then, in conjunction with an effective spatial arrangement for the abutment described above, the constant force device can be effectively installed.
In the constant force device according to an embodiment of the present invention, the wheel and pinion assembly has a toothed surface essentially having the shape of an arc in which the input shaft serves as a center. .
As described above, the wheel and pinion gear assembly has the arcuate toothed surface in order to obtain a friction angle, that is to say the toothed surface having essentially the shape of an arc, in which the input axis serves as a center. Therefore, the tooth surface of the teeth of the wheel and pinion gear assembly is formed in accordance with a locus of movement of the abutment. Therefore, when the wheel and pinion assembly and the stop are engaged with each other, a loss due to friction caused by sliding between these two elements is suppressed and it is possible to prevent the stop to receive an unnecessary load. Therefore, it is possible to suppress the loss of the output unit from the wheel and pinion gear assembly, allowing stable output.
In the constant force device according to an embodiment of the present invention the output unit supports a rocker arm with pivot spring so as to be pivotable.
According to this configuration, it is possible to rotate the balance with spring balance at the same time as the output unit. It is therefore possible to reduce the influence of the gravity which is caused by the orientation of the balance relative to the balance spring. That is, this configuration can function as a vortex mechanism that can suppress a change in pendulum swing cycles with pendulum spring that is caused by the direction of the force of gravity.
In the constant force device according to one embodiment of the present invention, the output unit is selected from a wheel and exhaust pinion assembly and a wheel and pinion assembly.
According to this configuration, it is possible to save the placement space of the device with constant force. A component forming part of the constant force device may be shared with a component forming part of the escapement or wheel train. Therefore, it is possible to reduce the number of components in the constant force device.
The constant force device according to one embodiment of the present invention further comprises a phase shift control mechanism which regulates the rotational movement of the output unit relative to the input unit. The phase shift control mechanism regulates at least the rotational movement in a direction in which the input unit is late with respect to the output unit.
According to this configuration, it is possible to prevent the input unit from being late compared to the output unit. Therefore, for example, when a second hand or the like is placed in the input unit, it is possible to prevent a strongly offset display of the second hand.
In addition, it is possible to adjust the maximum separation distance between the wheel assembly and stop pinion and the stop. Therefore, for example, including when a sudden input torque is applied to the input unit and the wheel and pinion gear assembly suddenly collides with the stopper, it is possible to reduce the collision force. Therefore, it is possible to prevent damage to the stopper or wheel and pinion assembly.
In the constant force device according to one embodiment of the present invention, the phase shift control mechanism regulates the rotational movement in a direction in which the input unit is in advance of the unit of rotation. exit.
According to this configuration, when the output unit rotates in the opposite direction due to an impact due to a fall or the like, it is possible to prevent the wheel and pinion stop assembly and the stop be damaged due to collision of the stop with the wheel and pinion assembly.
In the constant force device according to one embodiment of the present invention, the phase shift control mechanism has a protrusion which is formed on one of the output and input units, and a hole which is formed in the other unit among the output unit and the input unit, and which can engage with the protrusion.
According to this configuration, it is possible to allow the phase shift control mechanism to have a simple structure.
A movement according to the present application comprises the constant-force device and a rocker with spring balance which is set in motion by an output torque provided by the constant-force device.
According to this configuration, it is possible to provide the movement which can reduce the energy loss to limit the rotation of the wheel and pinion assembly.
A mechanical watch according to the present invention comprises the movement.
According to this configuration, it is possible to provide the mechanical watch which can reduce the energy loss to limit the rotation of the wheel assembly and pinion stop.
According to the present application, it is possible to stop or restart the rotation of the wheel assembly and pinion stop and adjust the degree of progression of its rotation by rotating the stop around the axis Release. As a result, the movement of the disengaged stop of the wheel and pinion gear assembly is similar to the movement of the wheel and pinion gear assembly, thereby reducing the energy loss. In other words, since the transmission path between the wheel and sprocket assembly and the output unit is simplified, it is possible to decrease the loss experienced by the output unit from the set. wheel and pinion. It is therefore possible to guarantee a more stable output unit output torque.
Brief description of the drawings [0031]
Fig. 1 is a plan view of a front side of a movement of a mechanical watch according to a first embodiment of the present invention.
Fig. 2 is a perspective view of a vortex with a constant force device according to the first embodiment of the present invention.
Fig. 3 is a cross-sectional view taken along the axis A-A of FIG. 2.
Fig. 4 is a perspective view when an outer carriage according to the first embodiment of the present invention is seen from a fixed wheel bridge side.
Fig. 5 is a perspective view when the outer carriage according to the first embodiment of the present invention is seen from a carriage bridge side.
Fig. 6 is a plan view of a stopping wheel according to the first embodiment of the present invention.
Fig. 7 is a perspective view when an inner carriage according to the first embodiment of the present invention is seen from a fixed wheel bridge side.
Fig. 8 is a perspective view when the inner carriage according to the first embodiment of the present invention is seen from a carriage bridge side.
Fig. 9 is a perspective view of a bearing unit of an exhaust mechanism according to the first embodiment of the present invention.
Fig. 10 is a plan view of the exhaust mechanism according to the first embodiment of the present invention.
Fig. 11 is a view illustrating an operation of a wheel and idler assembly, an abutment 96, and a wheel and idler assembly according to the first embodiment of the present invention, FIGS. 11 a to 11 d illustrating a gradual change.
Fig. 12 is a perspective view when a main portion according to a first modification example of the first embodiment of the present invention is viewed from a fixed wheel bridge side.
Fig. 13 is a perspective view of a stopper according to the first modification example of the first embodiment of the present invention.
Fig. 14 is a perspective view when a main portion according to a second modification example of the first embodiment of the present invention is viewed from a fixed wheel bridge side.
Fig. 15 is a perspective view of an eccentric pin according to the second modification example of the first embodiment of the present invention.
Fig. 16 is a plan view of a phase shift control mechanism according to the second modification example of the first embodiment of the present invention.
Fig. 17 is a partially enlarged plan view illustrating a coupling state between a stop wheel and a stop according to a third exemplary modification of the first embodiment of the present invention.
Fig. 18 is a plan view illustrating a coupling state between a stop wheel and a pawl of an abutment according to a fourth modification example of the first embodiment of the present invention.
Fig. 19 is a plan view of a stopping wheel according to a fifth exemplary modification of the first embodiment of the present invention.
Fig. 20 is a plan view of a constant force device according to a second embodiment of the present invention.
Fig. 21 is a cross-sectional view taken along the axis B-B of FIG. 20.
Fig. 22 is a cross-sectional view of a constant force device according to an exemplary modification of the second embodiment of the present invention.
Detailed Description of the Preferred Embodiments [0032] (First Embodiment) [Mechanical Watch] In the following, a first embodiment of the present invention will be described with reference to FIGS. 1 to 11. [0035] FIG. 1 is a plan view of a front side of a movement of a mechanical watch 1.
As shown in the figure, the mechanical watch 1 is configured to have a movement 10 and a housing (not shown) which accommodates the movement 10.
The movement 10 has a main plate 11 forming a frame. A dial (not shown) is placed at the rear of the main plate 11. A set of wheels integrated at the front of the movement 10 is called the front wheelset and a set of wheels integrated at the rear of the movement 10 is called rear wheel train.
A winding stem guide hole 11a is formed in the main plate 11 and a winding stem 12 is integrated so as to rotate. The winding stem 12 has a position axially determined by a switching device provided with an adjusting lever 13, a player 14, a sliding spring 15 and a setting lever jumper 16. , a winding pinion 17 is provided so as to be able to rotate on a guide axis of the winding stem 12.
In such a configuration, if the winding stem 12 is turned while it is in a first winding stem position (zero step), which is closest to the inside of the movement 10 in the direction of its axis, the winding pinion 17 rotates via the rotation of a clutch wheel (not shown). Then, if the winding pinion 17 rotates, a meeting wheel 20 meshing with it rotates. Then, if the encounter wheel 20 turns, a ratchet 21 meshing with it turns. In addition, if the ratchet 21 rotates, a main spring (not shown) housed in a barrel wheel 22 is wound.
The front wheelset of the movement 10 is configured to comprise not only the barrel wheel 22, but also a wheel and central gear assembly 25, a third wheel and pinion assembly 26, a second wheel and pinion assembly 27 and a fifth assembly wheel and pinion 28, and performs the function of transmitting the rotational force of the barrel wheel 22. In addition, a vortex with constant force device 30 which limits the rotation of the front wheel set is placed at the before movement 10.
The wheel assembly and central pinion 25 meshes with the barrel wheel 22. The third wheel and pinion assembly 26 meshes with the wheel assembly and central pinion 25. The second wheel and pinion assembly 27 s' meshes with the third wheel and pinion assembly 26. The fifth wheel and pinion assembly 28 meshes with the second wheel and pinion assembly 27. Then, the constant force vortex 30 meshes with the fifth wheel and pinion assembly 28 [0042] (Tourbillon with constant force device) FIG. 2 is a perspective view of the vortex with constant force device 30, FIG. 3 being a cross-sectional view thereof taken along the axis A-A of FIG. 2.
As shown in FIGS. 2 and 3, the vortex with constant force device 30 is a mechanism for limiting the rotation of the front wheel set described above. In addition, the vortex with constant force device 30 has what is called a vortex mechanism which reduces the influence of gravity which is caused by an orientation of a pendulum with pendulum spring 101 (which will be described later). ) and eliminates a disordered operation of the balance with pendulum spring 101. In addition, the vortex with constant-force device 30 comprises a constant-force device 3 which suppresses the variations of the rotational torque transmitted to a wheel and exhaust pinion assembly. 111 (which will be described later).
Hereinafter, the vortex with constant force device 30 will be described in detail.
The vortex with constant force device 30 comprises a wheel and fixed gear assembly 31 which is fixed to the main plate 11 in a fixed wheel bridge 29 attached to the front of the main plate 11, an outer carriage (unit 33) which is attached to the rear of the main plate 11 and which is rotatably supported between the fixed wheel bridge 29 (see Fig. 3) and a trolley bridge 32 placed opposite fixed wheel bridge 29, and an inner carriage (output unit) 34 which is supported inside the outer carriage 33 so as to be rotatable relative to the outer carriage 33.
The wheel and fixed gear assembly 31 has a wheel main body 31a having substantially the shape of a disk. A hole stone 31b which supports the outer carriage 33 in a rotatable manner is placed in the substantial center of the wheel main body 31a in a radial direction. In addition, screw insertion holes 31c which attach and fix the fixed wheel and pinion assembly 31 to the fixed wheel bridge 29 are provided at the periphery of the hole stone 31b of the wheel main body 31a. Screws (not shown) are inserted into the screw insertion holes 31c. In addition, a toothed portion 31d is formed on an outer peripheral portion of the wheel main body 31a.
[Outer carriage] [0049] FIG. 4 is a perspective view of the outer carriage 33 seen from the fixed wheel bridge side 29, FIG. 5 being a perspective view of the outer carriage 33 seen from the carriage bridge side 32.
As shown in Figs. 2 to 5, the outer carriage 33 has a first substantially disk-shaped outer carriage bearing 35 disposed on the fixed wheel bridge side 29 and a second substantially disk-shaped outer carriage bearing 36 disposed on the carriage bridge side 32. The first outer carriage bearing 35 and the second outer carriage bearing 36 are arranged coaxially with the wheel and fixed gear assembly 31.
In addition, a hole stone 35a is disposed coaxially with the hole stone 31b of the fixed wheel and pinion assembly 31 in the first outer carriage bearing 35. The hole stone 35a is used to support a carriage interior 34 so that it can rotate. In addition, a first outer rotating body 37 is provided on the fixed wheel bridge surface 29 of the first outer carriage bearing 35.
In order to correspond to the shape of the first outer carriage bearing 35, the first outer rotary body 37 is configured to have a base 37a having substantially the shape of a disk. In addition, the first outer rotary body 37 has a pin 37b which protrudes towards the fixed wheel bridge side 29 from a substantial center of the base 37a in the radial direction. The base 37a is attached and fixed to the first outer carriage bearing 35 via the screws 38. In addition, the post 37b is inserted into the hole stone 31b of the wheel and fixed gear assembly 31. In this way, the first outer rotary body 37 is rotatably supported via the wheel and fixed gear assembly 31.
In contrast, a hole stone 36a is disposed coaxially with the hole stone 35a of the first outer carriage bearing 35, in the second outer carriage bearing 36. The hole stone 36a is also used to support the inner carriage. 34 in such a way that it can rotate in cooperation with the hole stone 35a of the first outer carriage bearing 35. In addition, a second outer rotary body 39 is provided on the carriage deck side surface 32 of the second carriage bearing. outside 36.
In order to correspond to the shape of the second outer carriage bearing 36, the second outer rotary body 39 is configured to integrally mold a base 39a having substantially the shape of a disk and a pin 39b which protrudes to the side trolley bridge 32 from a substantial center of the base 39a in the radial direction. Post 39b is rotatably supported via a hole 32a of the carriage bridge 32. In addition, the base 39a is attached and secured to the second outer carriage bearing 36 via a screw 40.
In addition, an outer ring-shaped gear 41 is placed on a radially outer side further away from the first outer carriage bearing 35. The outer gear 41 meshes with the fifth wheel and pinion assembly 28. .
In addition, the outer gear 41 and the first outer carriage bearing 35 are connected to each other by three first arms 42. The first three arms 42 extend in the radial direction and are placed at equal intervals in the circumferential direction.
In contrast, three radially outwardly extending second arms 43 are integrally molded into the outer peripheral portion of the second outer carriage bearing 36. These second arms 43 are placed at equal intervals in the circumferential direction so to correspond to the first arms 42 on the side of the first outer carriage bearing 35.
[0058] Disc-shaped shaft washers 44 and 45 are respectively integrally molded in a connecting portion between the first arm 42 and the external gear 41 and a distal end of the second arm 43. Then, shafts 46 are axially extending respectively between the shaft washers 44 and 45. Both ends of the shafts 46 are attached and secured to the shaft washers 44 and 45 by threaded screws 47 from the top of the washers. 44 and 45.
In addition, a support bridge 48 having the shape of a ring so as to surround the periphery of the first outer carriage bearing 35 is placed between the first outer carriage bearing 35 and the outer gear 41. The diameter The inside of the support bridge 48 is set to be essentially the same as the outside diameter of the toothed portion 31 d of the wheel and fixed gear assembly 31.
In addition, the support bridge 48 is integrally molded so as to be connected to the first arm 42. A stop wheel bearing unit 50 and a wheel and stop gear assembly 70 supported by the control unit. stopping wheel bearing 50 so as to be rotatable are placed in the support bridge 48.
Here, the stop wheel bearing unit 50 and the wheel and stop gear assembly 70 form the constant-force device 3. The constant-force device 3 has a constant-force spring 68 (which will be described later) and a stop 96 in addition to the stop wheel bearing unit 50 and the wheel and pinion gear assembly 70.
The stop wheel bearing unit 50 is configured to have a ring-shaped axis insertion portion 51 integrally molded onto the support bridge 48, a first wheel bearing of stop 52 mounted on the fixed wheel bridge side 29 of the support bridge 48 and a second stop wheel bearing 53 mounted on the carriage bridge side 32 of the support bridge 48.
The first stop wheel bearing 52 has a wall 54 extending towards the fixed wheel bridge side 29 from a position corresponding to the axis insertion portion 51 of the support bridge 48. The wall 54 is formed in a substantially C-shaped sectional sectional configuration so as to open radially on the inner side. A substantially disc-shaped bearing washer 55 is integrally molded on an inner peripheral surface of the distal end of the wall 54 so as to be perpendicular to the wall 54. Next, a hole 55a is formed, in the direction of the thickness, in the substantial center of the bearing washer 55 in the radial direction. A hole stone 56 which supports the wheel and pinion assembly 70 so that it can rotate is placed in the hole 55a.
In addition, a pair of posts 57 extending from both sides to the wall 54 are integrally molded on the proximal end side of the wall 54. Disc-shaped screw washers 57a are respectively integrally molded in the distal end of the pair of posts 57. The screw washer 57a is attached and fixed to the support bridge 48 by a screw 58.
In contrast, the second stop wheel bearing 53 has a substantially disc-shaped bearing washer 61 positioned in a position corresponding to the axis insertion portion 51 formed in the support bridge 48. Next a hole 61a is formed in the direction of the thickness in the substantial center of the bearing washer 61 in the radial direction. A hole stone 62 which supports the wheel and pinion assembly 70 so that it can rotate is placed in the hole 61a.
A pair of posts 63 are integrally molded on both sides in the outer peripheral portion of the bearing washer 61 above the hole stone 62. Disc-shaped screw washers 63a are respectively integrally molded in the distal end of the pair of posts 63. The screw washers 63a are attached and fixed to the support bridge 48 by screws 64.
Ascending portions 63b are respectively formed in the distal end portion of the screw washer 63a and in the post 63. A gap S1 is formed between the bearing washer 61, the post 63 and the support bridge 48. A stop wheel 72 of the wheel and pinion gear assembly 70 is located in the gap S1.
In addition to the stop wheel 72, the wheel and stop gear assembly 70 has a stop wheel axis 71 inserted into the insertion portion of the shaft 51 formed in the support bridge 48. Studs 71a and 71b are respectively and integrally molded at both ends of the axis of the stop wheel 71. The pin 71a of the fixed wheel bridge side 29 is rotatably supported via the hole stone 56 of the first On the other hand, the pin 71b of the carriage bridge side 32 is rotatably supported via the hole stone 62 of the second lock wheel bearing 53.
In addition, a stop gear 71c is integrally molded on the stop wheel axis 71, from the substantial center in the axial direction through the front of the pin 71a of the fixed wheel bridge side 29. Here, the inside diameter of the support bridge 48 in which the stop wheel bearing unit 50 is located is chosen to be essentially the same as the outside diameter of the toothed portion 31 d of the wheel and pinion assembly. As a result, the lock gear 71c is adapted to mesh with the toothed portion 31d. On the other hand, the stopwheel 72 is externally attached and fixed in the vicinity of a base portion of the post 71b of the carriage bridge side 32 in the stop wheel axle body 71. stop 71 and stop wheel 72 are integrated with each other so as not to be rotatable relative to each other.
[0070] FIG. 6 shows a plan view of the stop wheel 72.
As illustrated by the figure, for example, the stop wheel 72 is made of a material having a crystal orientation similar to a metal material and a single crystal silicon, and is formed by a process called lithography galvanoformung abformung ( LIGA) in which an optical process such as electroforming and photolithography technology is integrated, a deep reactive ion etching (DRIE) or a metal injection molding (MIM).
The stop wheel 72 is formed by integrally molding a central portion 73 placed and fixed externally on the stop wheel axis 71, a flange 74 disposed on the outer side in the radial direction of the central portion 73. and having the shape of a ring so as to surround the periphery of the central portion 73, and a radius 75 connecting the central portion 73 and the flange 74.
Multiple hooks 76 (five in this embodiment) are formed to protrude radially outwardly into the outer peripheral portion of the flange 74. More specifically, the hooks 76 are formed into a substantially triangular shape such as the shows the plan view in the axial direction, essentially triangular openings 76a being formed in a most central portion thereof. In addition, the hooks 76 are formed so that a vertex P1 thereof is oriented in the direction of rotation (clockwise in Fig. 6) Y1 of the wheel. 72. The side side 76b of the front side in the direction of rotation Y1 is configured to be shorter than the side side 76c of the rear side in the direction of rotation Y1. In other words, while the lateral side 76b of the front side is formed to be connected to the spoke 75, the side side 76c of the back side is formed to be connected to the flange 74. The details of a rotation operation of the Stopwheel 72 will be described later.
Here, the radius 75 and the lateral side 76b of the front side have the shape of an arc. The center of this arc is located coaxially with the axis C1 of the wheel assembly and fixed gear 31, that is to say the axis of rotation of the outer carriage 33.
According to this configuration, the stop 96 (which will be described later) placed in the inner carriage 34 is engaged with the lateral side 76b of the front side of the hook 76 or disengaged therefrom.
In addition, as shown in FIGS. 4 and 5, in the support bridge 48, a ring-shaped bearing unit insertion portion 65 is integrally molded on one side which is diametrically opposed to the axis insertion portion 51 in the first outer carriage bearing 35. A bearing 133 of an exhaust mechanism bearing unit 130 (to be described later) is inserted into the bearing unit insertion portion 65. In addition, one first three arms 42 protrude from the outer peripheral portion of the bearing unit insertion portion 65.
In addition, a bolt carrier 66 is integrally molded in a position adjacent to the bearing unit insertion portion 65 in the support bridge 48. A bolt 67 is mounted in the bolt carrier 66. outer end portion of the constant force spring 68 is attached to the peak 67.
The constant force spring 68 serves to apply a rotational force to the inner carriage 34 relative to the outer carriage 33 and is formed in a spiral shape. An inner end portion of the constant force spring 68 is attached to the inner carriage 34 via a ferrule 69.
[Interior] Cart [0080] FIG. 7 is a perspective view of the inner carriage 34 as seen from the fixed wheel bridge side 29, FIG. 8 being a perspective view of the inner carriage 34 as seen from the carriage bridge side 32.
As shown in FIGS. 2, 3, 7 and 8, the inner carriage 34 has a first substantially disk-shaped inner trolley bearing 81 disposed on the fixed wheel bridge side 29 and a second substantially disk-shaped inner trolley bearing 82 disposed on the bridge side. The first inner carriage bearing 81 and the second inner carriage bearing 82 are arranged coaxially with the first outer carriage bearing 35 and the second outer carriage bearing 36 of the outer carriage 33.
In addition, a first inner rotational body 83 is provided on the surface of the first inner carriage bearing 81 on the first outer carriage bearing side 35. In order to correspond to the shape of the first inner carriage bearing 81, the first body inner rotator 83 is formed by integrally molding a base 83a which is substantially disk-shaped, an axle 83b protruding toward the first outer carriage bearing side 35 from the substantial center of the base 83a in the radial direction, and a pin 83c protruding from the distal end of the axis 83b.
Then, the base 83a is attached and fixed to the first inner carriage bearing 81 via the screws 84. In addition, the post 83c is inserted into the hole stone 35a of the first outer carriage bearing 35. In this way, the inner carriage 34 is rotatably supported relative to the outer carriage 33.
In addition, the constant force spring 68 and the ferrule 69 are fixed to the axis 83b. In this manner, a biasing force of the constant-force spring 68 is applied to the inner carriage 34 relative to the outer carriage 33. That is, a rotational force is applied to the inner carriage 34 relative to the carriage external 33 by the spring with constant force 68.
In contrast, a second inner rotatable body 85 is provided on the surface of the second inner carriage bearing 82 on the second outer carriage bearing side 36. In order to correspond to the shape of the second inner carriage bearing 82, the second body Inner rotary gear 85 is formed by integrally molding a base 85a having substantially the shape of a disc and a pin 85b which protrudes towards the second outer carriage bearing side 36 from the substantial center of the base 85a in the radial direction. The post 85b is rotatably supported via the hole stone 36a of the second outer carriage bearing 36. In addition, the base 85a is attached and secured to the inner carriage second bearing 82 via the screws 86.
In addition, anti-shock bearings 87a and 87b are respectively placed in the first inner carriage bearing 81 and the second inner carriage bearing 82. The anti-shock bearings 87a and 87b are arranged coaxially with respect to the hole-shaped stone 35a. first outer carriage bearing 35 and 36a hole stone of the second outer carriage bearing 36. The. Anti-shock bearings 87a and 87b serve to support the rocker with spring balance 101 (which will be described later) so that it can rotate.
Three first radially outwardly extending arms 88 are integrally molded into the outer peripheral portion of the first inner carriage bearing 81. In addition, three radially outwardly extending second arms 89 are integrally molded into the outer peripheral portion of the second inner carriage bearing 82. The first arms 88 and second arms 89 are respectively placed at equal intervals in the circumferential direction; in addition, they are arranged so as to face each other in the axial direction. In addition, the respective first arms 88 are arranged to be located between the first three arms 42 which are respectively formed in the outer carriage 33. In addition, the respective second arms 89 are arranged to be located between the three second arms 43 which are respectively formed in the outer carriage 33.
In addition, substantially disk-shaped shaft washers 91 and 92 are respectively integrally molded into the distal end of the respective arms 88 and 89. Then axially extending shafts 93 are respectively placed between the shaft washers 91 and 92. Both ends of the shaft 93 are attached and secured to the shaft washers 91 and 92 by screws 94 threaded from the top of the shaft washers 91 and 92.
In addition, a support bridge 95 in the shape of a ring so as to surround the periphery of the first inner carriage bearing 81 is placed outside the first inner carriage bearing 81 in the radial direction. The inside diameter of the support bridge 95 is set to be substantially the same as the outside diameter of the toothed portion 31 d of the wheel and fixed gear assembly 31. In addition, the support bridge 95 is integrally molded so as to be connected to the first arm 88.
The stop 96 is disposed in the support bridge 95. The stop 96 is engaged with the hook 76 of the wheel assembly and stop pinion 70 or disengaged therefrom in response to the rotational movement of the wheel and pinion assembly 70 disposed in the inner carriage 34 or in the outer carriage 33 (details will be described later).
The stop 96 is configured to have a pawl 98 coming into contact with the hook 76 of the wheel assembly and stop pinion 70 and a support portion 99 supporting the pawl 98. The support portion 99 presents a substantially Z-shaped cross-sectional shape, a slot 99a being formed on the fixed wheel bridge side 29 so that the wheel and lock pinion assembly side 70 is open. The pawl 98 is housed and fixed in the slot 99a. In addition, a side opposite the side of the support portion 99 to which the pawl 98 is attached is attached and fixed to the support bridge 95 via a screw 97.
In addition, the exhaust mechanism bearing unit 130 is disposed in the support bridge 95. The exhaust mechanism bearing unit 130 supports an exhaust 102 (which will be described later).
FIG. 9 is a perspective view of the exhaust mechanism bearing unit 130.
As shown in FIGS. 7-9, the exhaust mechanism bearing unit 130 is configured to be provided with an integrally molded shaft insertion portion 131 on the support bridge 95, a substantially shaped bearing washer 132 disc, a bearing 133 which is attached to the fixed wheel bridge side 29 of the support bridge 95, an exhaust mechanism support 134 which is attached to the carriage bridge side 32 of the support bridge 95.
The axis insertion portion 131 is placed on the opposite side diametrically to the insertion portion of the axis body 51 of the outer carriage 33 above the first inner rotatable body 83. In addition, the washer of Bearing 132 is disposed in a position which is adjacent to the insertion portion of the axis body 131 and wherein the support bridge 95 and the first arm 88 are connected to each other. A hole 132a, in the direction of the thickness, is formed in the substantial center of the bearing washer 132 in the radial direction, and a hole stone 132b is disposed in the hole 132a.
In addition, the bearing 133 has a wall 135 extending towards the fixed wheel bridge side 29 from a position corresponding to the insertion portion of the axis body 131 of the support bridge 95. The wall 135 is inserted in the bearing unit insertion portion 65 formed in the outer carriage 33 and is formed to extend to the wheel and fixed gear assembly 31. In addition, the wall 135 is formed in a manner that sectional configuration substantially C-shaped so that its radially inner side is open. A substantially disc-shaped bearing washer 136 is integrally molded on the inner peripheral surface side of the distal end of the wall 135 so as to be perpendicular to the wall 135. Next, a hole 136a, in the thickness direction , is formed in the substantial center of the bearing washer 136 in the radial direction, and a hole stone 137 is disposed in the hole 136a.
In addition, a pair of posts 138 extending from both sides to the wall 135 are integrally molded on the proximal end side of the wall 135. Disc-shaped screw washers 138a are integrally molded respectively. in the distal end of the pair of uprights 138. The screw washers 138a are attached and fixed to the support bridge 95 by screws 139.
In contrast, the exhaust mechanism support 134 has two substantially disc-shaped bearing washers 141 and 142 located in a position corresponding to the axle insertion portion 131 and the bearing washer 132 formed. in the support bridge 95. Holes 141a and 142a are formed, in the direction of the thickness, in the substantial center of the bearing washers 141 and 142 in the radial direction. Hole stones 143 and 144 are respectively provided in the holes 141a and 142a.
In addition, the exhaust mechanism support 134 has an upright 145 connecting the respective bearing washers 141 and 142. The upright 145 is formed in a substantially arcuate configuration in a plan view in the axial direction so as to corresponding to the shape of the support bridge 95. Disc-shaped screw washers 145a are respectively and integrally molded in both ends of the upright 145. The specification washers 145a are attached to the support bridge 95 by spacers 146. Next , the washers 145a are attached and fixed to the support bridge 95 by screws 147.
Here, the exhaust mechanism support 134 is fixed to the support bridge 95 via the spacers 146. Therefore, a gap S2 is formed between the support bridge 95 and the exhaust mechanism support 134. exhaust mechanism 102 is provided in the gap S2. In addition, the rocker with spring balance 101 is provided between the anti-shock bearings 87a and 87b of the inner carriage 34 configured as described above.
[Pendulum with balance spring] [0102] As shown in FIGS. 3 and 8, the rocker arm 101 comprises a rocker shaft 103 which is rotatably supported via the shock bearing 87a of the first inner carriage bearing 81 and the shock bearing 87b of the second inner carriage bearing 82, a balance wheel 104 which is fixed to the balance shaft 103 and a balance spring 105. The energy transmitted by the balance spring 105 rotates the balance with spring balance 101 forwards and backwards according to constant oscillation cycles.
The axis of pendulum 103 is an axis which is formed so that its diameter is gradually reduced in steps from its center to its two ends. Tenons 103a and 103b are respectively formed to protrude axially outwardly in both ends of the balance shaft 103. The respective pins 103a and 103b are rotatably supported via the respective anti-shock bearings 87a and 87b. . In addition, the rocker wheel 104 is externally attached and attached to a large diameter portion 103c in which an axial diameter in the axial substantial center is greatest. The rocker wheel 104 and the balance shaft 103 are integrated with each other so as not to be rotatable relative to each other. An outer flange 103c1 is formed on the first inner carriage bearing side 81 of the rocker wheel 104 in the large diameter portion 103c. The outer flange 103c1 determines an axial position of the rocker wheel 104.
In addition, a double cylindrical roller 106 is externally attached and fixed to a side opposite to the rocker wheel 104 of the outer flange 103c1. An annular rim portion 106a protruding radially outwardly is integrally molded into a lateral end of the large diameter portion 103c of the double roller 106. An ellipse 107 (see Fig. 3) is located in the rim portion 106a. The ellipse 107 is used to cause the oscillation of an anchor (which will be described later) 112 of the escape mechanism 102.
The balance spring 105 is, for example, a flat balance spring wound spirally in the same plane. An inner end portion thereof is attached to the second inner carriage bearing side 82 instead of the large diameter portion 103c of the balance shaft 103 via a ferrule 108. In contrast, a piton 109 is mounted on an outer end portion of the pendulum spring 105. The stud 109 is fixed to a bolt carrier 110 provided in the second carriage bearing 82. Next, the balance spring 105 has a function of storing the energy. transmitted by the escape mechanism 102 to the double roller 106 and transmission of energy to the balance shaft 103 and the rocker wheel 104.
[0106] (Escapement mechanism) [0107] FIG. 10 is a plan view of the exhaust mechanism 102.
As shown in FIGS. 3 and 10, the escapement mechanism 102 includes the wheel and exhaust pinion assembly 111 and the anchor 112 which causes the escapement of the wheel and exhaust pinion assembly 111 to rotate. regularly.
The wheel and exhaust pinion assembly 111 comprises an axis 113 and an escape wheel 114 which is mounted externally and fixed to the axis 113.
A first pin 113a and a second pin 113b whose diameters are respectively reduced in steps are integrally molded at both ends of axis 113. The axis 113 is inserted into the axis insertion portion 131 of the bridge. support 95 and the first post 113a is supported by the hole stone 143 of the exhaust mechanism support 134 so as to be rotatable. In contrast, the second pin 113b is supported by the hole stone 137 of the bearing 133 so as to be rotatable.
In addition, an escape pinion 115 is integrally molded on the bearing washer side 136 of the bearing 133 in the axis 113. Here, the inside diameter of the support bridge 95 in which the bearing unit of the bearing mechanism Exhaust 130 is placed is set to be substantially the same as the outer diameter of the toothed portion 31 d of the wheel and fixed gear assembly 31. Therefore, the escape pinion 115 is adapted to mesh with the portion toothed 31 d.
As illustrated in detail in FIG. 10, the escape wheel 114 is made of a material having a crystal orientation such as a metallic material and a single crystal silicon, and is formed by a process called lithography galvanoformung abformung (LIGA) in which an optical process such as electroforming and a photolithography technology is integrated, a deep reactive ion etching (DRIE) or a metal injection molding (MIM).
The escape wheel 114 has a substantially ring-shaped central portion 116 which is mounted to fit tightly on the shaft 113. The shaft 113 is mounted tightly fitting in a hole 116a formed in the central portion. 116. Then, the central portion 116 is placed in the gap S2 between the support bridge 95 and the exhaust mechanism support 134.
A flange 117 which has the shape of a ring so as to surround the central portion 116 is placed outside the central portion 116 in the radial direction. The rim 117 and the central portion 116 are connected together by a plurality of spokes 118 (four in this embodiment). The spokes 118 extend radially and are spaced at equal intervals in the circumferential direction.
In addition, a plurality of teeth 119 (20 in this embodiment) which have a special hook shape are formed to protrude radially outwardly on the outer peripheral edge of the rim 117. Pallets 125a and 125b of the anchor 112 (which will be described later) are engaged with the distal end of the teeth 119 or disengaged therefrom.
As shown in FIGS. 8 to 10, the anchor 112 includes an anchor shaft 121, an anchor body 122 and a rod 126 which are externally attached and attached to the anchor shaft 121.
The anchor axis 121 is an axle which is rotatably supported via the hole-shaped stone 132b provided in the support bridge 95 and via a hole-shaped stone 144 provided in the support mechanism. exhaust 134.
For example, the anchor body 122 is formed so that two pallet jibs 123a and 123b formed by electroforming are connected to each other. A hole 122a that can be inserted into the anchor axis 121 is formed in a connecting portion 123c between the two pallet jibs 123a and 123b. The two pallet jibs 123a and 123b are in an extended state from the connecting portion 123c to respectively opposite sides.
For example, as an electroforming metal for the formation of the anchor body 122, it is possible to use extremely rigid chromium, nickel and iron, as well as an alloy containing these materials.
Slots 124a and 124b are respectively formed at the distal end of the two pallet jibs 123a and 123b so that the assembly wheel and exhaust pinion 111 is open. Pallets 125a and 125b are respectively bonded and fixed to slots 124a and 124b by means of an adhesive. Pallet 125 consists of a substantially square columnar ruby and protrudes from the distal end of the respective pallet jibs 123a and 123b to toothed portion 119 of escapement wheel 114.
In contrast, the rod 126 is also formed by electroforming, for example. An insertion hole 126a into which the anchor axis 121 can be inserted is formed in its proximal end. Then, the rod 126 is inserted and fixed in the anchor axis 121 from the escape mechanism support side 134 of the anchor body 122. The rod 126 is formed to extend from the axle anchor 121 to the pendulum axis side 103.
A pair of horns 127 and a stinger 128 disposed between the pair of horns 127 are disposed in the distal end of the rod 126. Next, a pallet receptacle 129 with which the ellipse 107 of the balance with spring balance 101 is engaged or from which it is disengaged is formed inside the horns 127.
[0123] (Operation of the vortex with a constant force device) [0124] In what follows, operation of the vortex with constant force device 30 will be described.
[0125] Firstly, if one refers to FIGS. 8 to 10, an operation of the rocker with spring balance 101 and the escape mechanism 102 which are mounted on the inner carriage 34 will be described. The balance with spring balance 101 receives a rotational force of the wheel and exhaust pinion assembly 111 via the ellipse 107 and performs a free oscillation due to the rotational force and the tension of the balance spring 105. If the pendulum beam 101 performs a free oscillation, the wand 126 forming the pallet receptacle 129 which can be engaged with or disengaged from the ellipse 107 oscillates from one side to the other about the axis anchor 121.
Then, the anchor body 122 fixed to the anchor axis 121 also oscillates integrally with the rod 126. If the anchor body 122 oscillates, the two pallets 125a and 125b come into contact, alternately and repetitively, with the toothed portion 119 of the escape wheel 114. In this way, the wheel and exhaust pinion assembly 111 always rotates at a constant speed.
[0127] Thereafter, if one refers to FIG. 11, an operation of the outer carriage 33 and the inner carriage 34 will be described.
[0128] Figs. 11a to 11d are views showing an operation of the wheel and lock gear assembly 70 provided in the outer carriage 33 as well as operation of the abutment 96 and the wheel and idler assembly 111 which are provided in the inner carriage 34.
First, a rotational force received by the outer carriage 33, and an operation of the wheel and pinion assembly 70 which receives the rotational force, will be described.
In the outer carriage 33, since the external gear 41 is meshing with the fifth wheel and pinion assembly 28, the rotational force of the barrel wheel 22 is transmitted to the outer carriage 33 via the wheel set. before. In addition, in the wheel and pinion gear assembly 70, the stop pinion 71c meshes with the toothed portion 31d of the wheel and pinion gear assembly 31. Therefore, since the outer carriage 33 rotates, the wheel and stop gear assembly 70 rotates about the axial center of the stop gear 71c (clockwise in Fig. 11a, see arrow Y2) and circulates around the assembly wheel and fixed gear 31 (counterclockwise in Fig. 11a, see arrow Y3).
In the following, a rotational force received by the inner carriage 34, and an operation of the assembly wheel and exhaust pinion 111 which receives the rotational force, will be described.
The inner carriage 34 is rotatably supported relative to the outer carriage 33 and is connected to the outer carriage 33 by the constant-force spring 68. As a result, the inner carriage 34 rotates relative to the outer carriage 33 by receiving a biasing force of the constant force spring 68. In addition, in the wheel and exhaust pinion assembly 111, the escape gear 115 is in gear with the toothed portion 31d of the wheel and pinion gear assembly 31 Therefore, since the inner carriage 34 rotates, the wheel and exhaust pinion assembly 111 rotates about the axial center of the wheel and exhaust pinion assembly 111 (clockwise on Fig. 11a, see arrow Y4) and circulates around the wheel and fixed gear assembly 31 (counterclockwise in Fig. 11a, see arrow Y5).
Here, the wheel and exhaust pinion assembly 111 configures the escapement mechanism 102 and is adapted to rotate continuously at a constant speed via the anchor 112 or the pendulum with spring balance 101. that is, since the wheel and exhaust pinion assembly 111 rotates at a constant speed, the inner carriage 34, which supports the wheel and exhaust pinion assembly 111 so that it can turn, rotate at a constant speed. More specifically, the wheel and exhaust pinion assembly 111 rotates at a constant speed such that the inner carriage 34 performs one revolution per minute. In other words, the inner carriage 34 rotates six degrees per second. Since the inner carriage 34 performs one revolution per minute, the wheel and central gear assembly 25 performs one revolution per hour.
Here, the hook 76 of the wheel and stop gear assembly 70 is engaged with the pawl 98 of the abutment 96 and is decoupled from it repeatedly.
As shown in FIG. 11a, in an initial state where the hook 76 of the wheel and pinion gear assembly 70 is engaged with the pawl 98 of the abutment 96 (hereinafter, this initial state is designated as the Os point), a portion of the hook 76 which corresponds to a range of six degrees around the axis of rotation of the outer carriage 33 and the inner carriage 34 is engaged with the pawl 98. More specifically, in a state where the distal end of the pawl 98 is in contact with a lateral side 76b (see Fig. 6) of the hook 76, the hook 76 and the pawl 98 are engaged with each other.
The range of six degrees represents an extent of an angle in which the inner carriage 34 rotates in one second.
At this point Os, the rotation of the wheel assembly and stop gear 70 is regulated by the stop 96. Therefore, the outer carriage 33 is in a stopped state. Then, the biasing force of the constant force spring 68 only rotates the inner carriage 34. Since the inner carriage 34 rotates, the wheel and exhaust pinion assembly 111 rotates continuously.
Then, as shown in FIG. 11b, if 0.5 seconds elapses from the point Os, the inner carriage 34 rotates three times. Then, the stopper 96 attached to the inner carriage 34 also moves integrally with the inner carriage 34 (clockwise in Fig. 11b, see arrow Y6). Consequently, the pawl 98 of the abutment 96 slides on the lateral side 76b of the front side of the hook 76 in a direction allowing it to be disengaged. Then, a portion of the hook 76 which corresponds to an extent of three degrees about the axis of rotation of the outer carriage 33 and the inner carriage 34 is in a state in engagement with the pawl 98.
Then, as shown in FIG. 11c, if it is the moment immediately before a second elapses from the point Os, that is to say if about 0.99 seconds elapses, the pawl 98 slides more on the lateral side 76b of the front side of the hook 76, in which state the hook 76 and the pawl 98 are engaged with each other becoming a state immediately before the hook 76 and the pawl 98 uncouple from each other . Then, at the next moment, that is to say if a second elapses, the hook 76 and the pawl 98 are in a state of disengagement with respect to each other.
[0140] Then, as shown in FIG. 11 d, the outer carriage 33 rotates. In response to this rotation, the wheel and pinion assembly 70 rotates about the axial center of the pinion 71c and circulates around the wheel and pinion gear assembly 31. In other words, the wheel assembly and stop gear 70 rotates while moving toward the stop 96. Then, the wheel and stop gear assembly 70 is again stopped so that the hook 76 (76A) engages the ratchet 98 at the point Bone is engaged with the ratchet 98 of the next hook 76 (76B).
An angle according to which the outer carriage 33 rotates until the wheel and pinion 70 assembly rotates while the hook 76 and the ratchet 98 disengage from each other and the assembly wheel and stop gear 70 is stopped represents six degrees.
Here, since the outer carriage 33 rotates, the pin 67 attached to the outer carriage 33 also moves integrally with the outer carriage 33 (clockwise in Fig. 11d, see arrow). Y7). Since the bolt 67 is moved, the constant force spring 68 is wound. Specifically, the constant force spring 68 is wound until the outer carriage 33 rotates six degrees.
Then, in a state where the constant force spring 68 is wound, the outer carriage 33 (wheel assembly and stop pinion 70) is stopped and the prestressing force of the constant force spring 68 rotates the inner carriage. 34. Since this operation is repeated, the inner carriage 34 and the wheel and exhaust pinion assembly 111 continue to rotate at a constant speed.
As described above, in the first embodiment, the outer carriage 33 and the inner carriage 34 are rotatably supported relative to the wheel and fixed gear assembly 31 and can be rotated one by one. relationship to the other; the wheel and stop gear assembly 70 being disposed in the outer carriage 33. On the other hand, the stop 96 which stops and starts the rotation of the wheel and stop gear 70 is arranged in the inner carriage 34. Next in response to the rotation of the outer carriage 33, the wheel and lock gear assembly 70 is configured to rotate about the axial center of the stop pinion 71c and to circulate around the wheel and pinion gear assembly 31. In FIG. however, the stop 96 is configured to be moved integrally with the inner carriage 34. That is, the wheel and pinion assembly 70 is configured to execute planetary movement (revolution during rotation) around the wheel and fixed gear assembly 31.
Therefore, according to the first embodiment described above, it is possible to stop or restart the rotation of the wheel assembly and stop pinion 70 while rotating the stopper 96 integrally with the inner carriage. 34 and, further, while circulating the entire wheel and lock gear 70 integrally with the outer carriage 33. Therefore, it is not necessary to use an oscillating member as in the related art to limit the rotation of the assembly wheel and pinion 70. To this extent, it is possible to reduce a loss of energy. In other words, since the wheel and lock gear assembly 70 and the inner carriage 34 are in close contact with each other, it is possible to reduce the loss to the inner carriage 34 from the wheel and pinion assembly 70. In addition, the movement of the stop 96 is a rotational movement similar to that of the wheel and pinion assembly 70. Therefore, it is possible to reduce the loss. of energy and it is possible to simplify the transmission path between the wheel assembly and pinion 70 and the inner carriage 34. Therefore, it is possible to ensure a more stable rotation torque of the inner carriage. In this way, the rate of the balance with spring balance can be stabilized, which guarantees greater accuracy.
In addition, the vortex with constant force device 30 is configured so that, to cause rotation and revolution of the wheel and pinion 70 assembly around the wheel and pinion gear assembly 31 , the stop gear 71c is disposed in the wheel and stop gear assembly 70 and the stop gear 71c is brought into engagement with the toothed portion 31d of the wheel and fixed gear assembly 31. Consequently, it is possible to cause the wheel and lock gear 70 and the stopper 96 to engage with each other or to disengage from one another using a simple structure. Therefore, it is possible to reduce the weight, the size and the cost of the vortex with constant force device 30. In addition, it becomes possible to adjust the degree of progression of the rotation of the wheel and pinion assembly. stop 70 using a simple structure. Therefore, it is possible to effectively utilize the space around the outer carriage 33 and the wheel and pinion assembly 70. Then, the vortex with constant force device 30 can be effectively installed.
In addition, the lateral side 76b of the front side of the hook 76 of the stop wheel 72 is formed in an arcuate configuration, the center of the arc being defined so as to be coaxial with the center of rotation of the carriage 33. That is to say that the shape of the lateral side 76b of the front side is the same as a locus of movement of the pawl 98 of the stop 96 which slides on the lateral side 76b. Therefore, when the pawl 98 slides on the lateral side 76b, a loss due to friction is suppressed and an unnecessary load is not applied to the stopper 96.
[0148] That is, for example, if the hook 76 projects further forward in a direction of rotation Y1 (see Fig. 6) of the outer carriage 33 than that of the first embodiment described herein. above, when the pawl 98 slides in the direction allowing its disengagement, a force which pushes the stop wheel 72 in a direction of movement backwards is necessary.
Therefore, the lateral side 76b of the front side of the hook 76 has the shape of an arc and the center of the arc is defined so as to be coaxial with the center of rotation of the outer carriage 33. In this way the unnecessary load is not applied to the stopwheel 72. Therefore, it is possible to improve the operating efficiency of the vortex with constant force device 30.
The surface that comes into contact with the lateral side 76b of the hook 76 in the pawl 98 may have the shape of an arc, similar to the lateral side 76b. According to this configuration, the hook 76 and the pawl 98 come into surface contact with each other. In this way, it is possible to prevent a high pressure from being applied locally to the hook 76 and the pawl 98. Therefore, it is possible to extend the durability of the stopping wheel 72 or pawl 98.
In addition, according to the first embodiment described above, the rocker with spring balance 101 is disposed in the inner carriage 34. Therefore, the rocker with spring balance 101 can rotate with the inner carriage 34. Therefore it is possible, for example, to reduce the influence of gravity that can be caused by a user who changes the orientation of the mechanical watch 1, that is to say the influence of the gravity that is This is because it is possible to eliminate the variations of the oscillation cycles of the rocker arm 101 which can be caused by a direction of gravity.
In addition, the pin 37b of the first outer rotary body 37 and the pin 39b of the second outer rotary body 39 which support the outer carriage 33 so that it can rotate, and the pin 83c of the first inner rotary body 83 and the tenon 85b of the second inner rotatable body 85 which support the inner carriage 34 so that it can rotate are all arranged coaxially. Therefore, the transmission distance is effectively shortened between the wheel and idler gear 70 and the inner carriage 34. Therefore, it is possible to further reduce the energy loss.
Incidentally, according to the constant-force device of the related art, if a phase shift between the wheel and exhaust pinion assembly and the tension ring (corresponding to the phase difference between the outer carriage 33 and the inner carriage 34 in the present embodiment) is increased, even if the barrel wheel is rolled up again, the wheel and idler assembly and the pallet of the second anchor device are ultimately engaged with each other. the other before the pre-tension spring (corresponding to the constant force spring in the present embodiment) disposed between the wheel and exhaust pinion assembly and the tension ring has the predetermined winding amount ( amount of initial winding). Therefore, according to the constant force device of the related art, if the phase shift between the wheel and exhaust pinion assembly and the tension ring is increased, it is difficult to wind the pre-tension spring of in order to obtain the predetermined winding quantity. Therefore, the constant-force device of the related art requires an essential configuration of a phase shift control mechanism to prevent the phase shift from being increased beyond a predetermined level between the wheel and pinion assembly. exhaust and the tension ring.
However, according to the first embodiment, the stop 96 is fixed to the inner carriage 34 and the stop 96 is moved to rotate about the axis of rotation of the inner carriage 34. Therefore, including when the phase shift is increased between the outer carriage 33 and the inner carriage 34, it is not possible for the stop wheel 72 and the stopper 96 to engage with each other until the force spring constant 68 has the predetermined winding amount. Therefore, in a case where the phase shift control mechanism 160 is not provided, it is possible to maintain the winding amount of the constant force spring 68 so that it is always constant. [0155] (First modification example of the first embodiment) [0156] In the following, with reference to FIGS. 12 and 13, a first modification example of the first embodiment will be described.
[0157] FIG. 12 is a perspective view of a portion of the inner carriage 34 and the wheel and pinion assembly 70 disposed in the outer carriage 33 according to the first modification example of the first embodiment, seen from the bridge side of fixed wheel 29, FIG. 13 being a perspective view of a stop 196 according to the first modification example of the first embodiment. The same reference numbers are assigned to elements that are the same as those of the first embodiment described above; their description will therefore be omitted (in the following description, this will also be applied to each modification example of the first embodiment, to the second embodiment, and to an example of modification of a second embodiment).
As shown in FIGS. 12 and 13, a difference between the first embodiment and the first modification example of the first embodiment is that the shape of the stop 96 of the first embodiment is different from the shape of the stop 196 of the first example. modifying the first embodiment.
More specifically, the stop 196 is configured to have the pawl 98 which comes into contact with the hook 76 of the wheel assembly and stop pinion 70 and a support portion 150 which supports the ratchet 98. Support portion 150 is configured to have a substantially rectangular ratchet carrier 151 that supports ratchet 98 and a ring-shaped fixed portion 152 that is integrally molded on one side of ratchet carrier 151.
A housing recess 151a of the pawl is formed in the pawl support 151 so that it is open on the wheel assembly side and stop pinion 70, the pawl 98 being housed in the ratchet support 151 .
Then, in the stop 196, the fixing portion 152 is interposed and fixed between the first inner carriage bearing 81 and the first inner rotary body 83. More specifically, in the stop 196, the fixing portion 152 is placed between the first inner carriage bearing 81 and the first inner rotary body 83. Next, the first inner rotary body 83 is attached and secured to the first inner carriage bearing 81 via a screw 84.
Here, an outer diameter E1 of the attachment portion 152 is chosen to be substantially the same as the outer diameter of the first inner carriage bearing 81. In addition, an inner diameter E2 of the attachment portion 152 is chosen so that its inner peripheral edge is located more radially outside than a position of placement of the screw 84. In this way, the fixing portion 152 and the screw 84 do not interfere with the with each other.
In addition, a slot 152a is formed in the attachment portion 152, thereby completing a spring function.
In addition, a stepped portion 83d which receives the fixing portion 152 is formed in a position corresponding to the attachment portion 152, in the base 83a of the first inner rotational body 83. A depth of the stage difference in stepped portion 83d is determined to be slightly higher than a depth of attachment portion 152.
On the basis of this configuration, in a state where the first inner rotational body 83 is attached and secured to the first inner carriage bearing 81 by the screw 84, the attachment portion 152 is housed within the portion stepped 83d of the first inner rotational body 83 in a state where the attachment portion 152 is resiliently deformed so as to expand slightly. Then, the attachment portion 152 is held by a friction force, which is generated by a spring force, between the securing portion 152, on the one hand, and the inner trolley first bearing 81 and the first inner rotating body. 83, on the other hand. In this state, the attachment portion 152 is adapted to be rotatable by receiving a predetermined load. Therefore, a position of the ratchet support 151 in the circumferential direction is meticulously adjusted, the ratchet support 151 being aligned with a predetermined position. In this way, the ratchet support 151 can be held in this position.
According to this configuration, the effect which is the same as in the first embodiment described above can be obtained. In addition to this, without changing a radial position in which the stop wheel 72 of the wheel and pinion assembly 70 and the pawl 98 of the stop 196 are engaged with each other, it is possible to adjusting a relative position (phase) between the outer carriage 33 and the inner carriage 34 at the moment when the stop wheel 72 and the pawl 98 of the stop 196 are disengaged from each other.
[0167] (Second example of modification of the first embodiment) [0168] In what follows, with reference to FIGS. 14 to 16, a second example of modification of the first embodiment will be described.
[0169] FIG. 14 is a perspective view of a portion of the outer carriage 33 and a portion of the inner carriage 34 according to the second modification example of the first embodiment, seen from the fixed wheel bridge side 29.
As shown in the figure, a difference between the first embodiment and the second modification example of the first embodiment is that only the second modification example is provided with the phase shift control mechanism 160 which limits the phase shift between the outer carriage 33 and the inner carriage 34 so that it falls within a predetermined angle range.
The phase shift control mechanism 160 comprises a control ring 161 integrally molded on the support bridge 48 of the outer carriage 33, and an eccentric pin 162 provided on the support bridge 95 of the inner carriage 34 and inserted into the ring. regulation 161.
The control ring 161 is placed between the bearing unit insertion portion 65 on the support bridge 48 and the axis insertion portion 51. On the other hand, a pin-shaped fixing portion The eccentric pin 162 is integrally formed in a position corresponding to the control ring 161 in the radial direction on the support bridge 95 of the inner carriage 34. The eccentric pin 162 is fixed to the pin fixing portion 163 so as to protrude to the regulation ring 161.
[0173] FIG. 15 is a perspective view of the eccentric pin 162, FIG. 16 being a plan view of the phase shift control mechanism 160.
[0174] As shown in FIG. 15, the eccentric pin 162 is configured to have a pin main body 162a and a securing pin 162b integrally molded into the proximal end of the pin main body 162a. Then, the securing pin 162b is snugly mounted on the pin fixing portion 163 of the inner carriage 34, thereby securing the eccentric pin 162 to the inner carriage 34. The closely fitting arrangement described herein is what the it is called a tight fitting fitting. The eccentric pin 162 is snug-fitting to such an extent that the eccentric pin 162 is rotatable about the axial center of the securing pin 162b.
Here, the axial center C2 of the main pin body 162a and the axial center C3 of the securing pin 162b are offset relative to each other by a distance Ad. In addition, a recess 164 is formed in the distal end of the pin main body 162a in the radial direction. For example, the eccentric pin 162 can be rotated using a flat screwdriver.
[0176] On the other hand, as shown in FIG. 16, a peripheral inner surface of the regulating ring 161 has a shape in which both sides in the circumferential direction are subjected to bidirectional machining. A width W1 of the bidirectional machining is set so that an angle of rotation of the inner carriage 34 relative to the outer carriage 33 falls within a predetermined angle range when the inner carriage 34 rotates relative to the outer carriage 33 and that the eccentric pin 162 contacts the inner peripheral surface of the regulating ring 161.
For example, it is preferable that this predetermined angle be about six degrees. The six degrees represent an angle (one second) during which the stop wheel 72 of the wheel and pinion gear assembly 70 and the pawl 98 of the stopper 96 are disengaged from each other. The predetermined angle is sufficiently respected if the angle of rotation of the inner carriage 34 relative to the outer carriage 33 is six degrees. In addition, the reason why the predetermined angle is set to be about six degrees lies in the fact that in practice, a manufacturing defect occurs at each component. This is why the angle is obtained by adding a spacing that absorbs this manufacturing defect.
Herein, it is possible to adjust a circumferential phase shift amount between the axial center C2 of the pin main body 162a and the axial center C3 of the securing pin 162b by rotating the eccentric pin 162. Therefore, y including if the manufacturing defect occurs at the control ring 161, by rotating the eccentric pin 162, it is possible to adjust a regulation position for the rotation of the inner carriage 34 relative to the outer carriage 33, c that is, it is possible to very precisely adjust a position which can regulate the rotation of the inner carriage 34.
In addition, including when the position of the stop 96 is adjusted to adjust the position of the inner carriage 34 relative to the outer carriage 33, it is possible to adjust the position of the eccentric pin 162 so as to that the rotation of the inner carriage 34 can be regulated in the corresponding position.
Therefore, according to the second modification example of the first embodiment described above, the effect which is the same as in the first embodiment described above can be obtained. In addition to this, for example, including when the mechanical watch 1 falls and receives an impact on the outside, it is possible to prevent the pawl 98 of the stop 96 from being damaged by a collision with the lateral side 76c of the stop wheel 72 due to the reverse rotation of the inner carriage 34, or to prevent the vertex P1 of the hook 76 of the stop wheel 72 from being damaged by a collision with the stopper 96. In addition, when the The wheel set is stopped to set the hands like a minute hand or an hour hand (both not shown), it is possible to prevent the inner carriage 34 from advancing unnecessarily. Therefore, it is possible to reliably stabilize the operation of the vortex with constant force device 30.
In addition, it is possible to prevent a delay in the phase of the outer carriage 33 relative to the inner carriage 34. Therefore, for example, including when a second hand is placed in the outer carriage 33, it is possible to prevent a strongly offset display of the second hand.
To be more specific, if the main spring (not shown), housed in the barrel wheel 22 is expanded, the rotational force transmitted to the outer carriage 33 is insufficient. Therefore, the force of the constant-force spring 68 (force in a direction where the constant-force spring 68 is released) outweighs the rotational force, resulting in a large phase shift of the outer carriage 33 relative to the inner carriage. 34. That is, the phase of the outer carriage 33 with respect to the inner carriage 34 is considerably delayed (hereinafter, the phase delay is simply referred to as the phase delay). However, it is possible to regulate the phase retardation of the outer carriage 33 relative to the inner carriage 34 so that it is equal to six degrees, for example by placing the regulation mechanism of the phase shift 160. It is possible to remove the display gap from the second hand hour so that it is equal to one second.
In addition, when the main spring of the barrel wheel 22 is rewound from the expanded state of the main spring of the barrel wheel 22, the rotational force is rapidly applied to the outer carriage 33, resulting in the vigorous rotation of the outer carriage 33. Then, the stop wheel 72 collides with the stop 96.
At this time, if the phase retardation of the outer carriage 33 relative to the inner carriage 34 is considerable, the impact applied to the stop 96 and the stop wheel 72 increases to this extent. However, it is possible to reduce the phase lag of the outer carriage 33 relative to the inner carriage 34 by placing the phase shift control mechanism 160. Therefore, it is possible to prevent the stop 96 or the stop wheel 72. to be damaged by the impact.
As described above, two surfaces subjected to bidirectional machining on the control ring 161 of the phase shift control mechanism 160 are configured to have largely different roles depending on a direction of movement of the eccentric pin. 162.
[0186] That is, in the two surfaces subjected to bidirectional machining on the regulating ring 161, a surface (see portion X in Fig. 16) which regulates a rotational movement in one direction where the phase of the outer carriage 33 is delayed relative to the inner carriage 34 (rotational movement in a direction where the constant force spring 68 in the outer carriage 33 is unwound) plays a role of removing the display gap from time. In addition, the surface serves to prevent the stop 96 or the stop wheel 72 from being damaged by the impact when the barrel wheel 22 is wound.
On the other hand, in the two surfaces subjected to bidirectional machining at the regulation ring 161, a surface (see portion Y in Fig. 16) which regulates an eventual rotation in a direction where the phase of the carriage external 33 is in advance with respect to the inner carriage 34 (rotational movement in a direction in which the spring constant force 68 in the outer carriage 33 is wound) has the function of preventing the wheel and pinion assembly 72 and the abutment 96 to be damaged as the abutment 96 collides with the wheel and lock gear assembly 72 when a fall impact causes rotation in reverse of the inner carriage 34.
In the second modification example of the first embodiment described above, a case has been described in which the regulation ring 161 is placed between the bearing unit insertion portion 65 on the bridge of the invention. support 48 and the axis insertion portion 51. However, without this being exhaustive, the position of the regulation ring 161 can be determined so as to be any desired position on the support bridge 48. The position of the eccentric pin 162 can also be determined arbitrarily according to the position of the regulating ring 161.
In addition, the eccentric pin 162 can be placed in the outer carriage bearings 35 and 36 of the outer carriage 33 and in the outer rotary bodies 37 and 39, an elliptical hole (ellipse) in which the eccentric pin 162 can be inserted in the inner carriage bearings 81 and 82 and the inner rotating bodies 83 and 85 of the inner carriage 34. In this way, the hole can be allowed to function as the regulating ring 161. In addition, the pin The eccentric 162 may be placed in the inner carriage bearings 81 and 82 and in the inner rotatable bodies 83 and 85, an elliptical hole in which the eccentric pin 162 may be inserted which can be formed in the outer carriage bearings 35 and 36 and in the outer rotating bodies 37 and 39.
In addition, in the second modification example of the first embodiment described above, a case has been described in which the phase shift control mechanism 160 is configured to comprise the control ring 161 and the eccentric pin 162 inserted into the regulation ring 161. However, without being exhaustive, a configuration can be adopted, which can regulate the phase difference between the outer carriage 33 and the inner carriage 34. For example, pins which are different from the eccentric pin 162 can be respectively placed in positions corresponding to the two surfaces of the control ring 161 which are subjected to bidirectional machining. In this way, a configuration can be adopted in which these pins regulate the movement of the eccentric pin 162.
In addition, in the second modification example of the first embodiment described above, a case has been described in which the regulation ring 161 can regulate the phase shift of the outer carriage 33 relative to the inner carriage 34, by example, so that it is equal to six degrees. However, without being exhaustive, depending on the role of the regulation ring 161, a shape of the regulating ring 161 can be arbitrarily modified.
That is, for example, that when the regulation ring 161 precisely regulates only the movement in the sense that the phase of the outer carriage 33 is delayed with respect to the inner carriage 34, in both surfaces of the regulating ring 161 which are subjected to bidirectional machining, only the position of the surface (see portion A in Fig. 16) which regulates the rotational movement in the sense that the phase is delayed can be formed with precision.
On the other hand, when the regulation ring 161 precisely regulates only the rotational movement in the sense that the phase of the outer carriage 33 is in advance with respect to the inner carriage 34, in the two surfaces of the regulation ring 161. which are subjected to bidirectional machining, only the position of the surface (see portion B in Fig. 16) which regulates the rotational movement in the direction that the phase is in advance can be precisely formed. [0194] (Third modification example of the first embodiment) [0195] In the following, with reference to FIG. 17, a third exemplary modification of the first embodiment will be described.
[0196] FIG. 17 is a partially enlarged plan view illustrating a coupling state between a stop wheel 372 (wheel and stop gear assembly 370) and the stop 96 according to the third modification example of the first embodiment.
As shown in the figure, a difference between the first embodiment and the third modification example of the first embodiment lies in the fact that the engagement state is different between a hook 376 of the stop wheel. 372 and the pawl 98 of the abutment 96.
More specifically, in the first embodiment, the hook 76 and the pawl 98 are engaged with respect to each other, in a state where the distal end of the pawl 98 is in contact with the lateral side 76b (see Fig. 6) of the hook 76. On the other hand, in the third modification example of the first embodiment, the hook 376 and the pawl 98 are engaged with each other in relation to each other. a state where the vertex P1 of the hook 376 is in contact with the lateral side 98a of the pawl 98.
[0199] Compared to the hook 76 of the first embodiment, the hook 376 is formed so that the vertex P1 is more gradually tilted forward so that the vertex P1 comes into contact with the ratchet 98 earlier than a lateral side 376b.
[0200] Here, the ratchet 98 is generally made of a ruby. Therefore, when compared to a case in which the distal end of the pawl 98 is brought into contact with the lateral side 76b (see Fig. 6) of the hook 76 as previously described in the first embodiment, the wheel stop 372 is less likely to be damaged, adopting a configuration in which the apex P1 of the hook 376 is brought into contact with the lateral side 98a of the pawl 98 as described in the third modification example of the first embodiment.
More specifically, for example, the Vickers hardness (HV) of the ruby forming the pawl 98 is about 2,000. In contrast, the stop wheel 372 is generally formed of a metallic material such as nickel. The Vickers hardness of a metal such as nickel is about 500 to 700. Here, since a component is vulnerable to the impact of a harder material, when compared to a case where a portion of Since the sharp, distal end of the ruby collides with the component, it is unlikely that damage will occur in a case where a sharp distal end portion formed of nickel collides with the component. Therefore, the stop wheel 372 is less likely to be damaged. Therefore, it is possible to extend the durability of the stop wheel 372.
In the third modification example described above, a case has been described in which the vertex P1 of the hook 376 is brought into contact with the lateral side 98a of the pawl 98 by changing the shape of the hook 376. However, without that this is exhaustive, a configuration can be adopted in which the vertex P1 of the hook 376 is brought into contact with the lateral side 98a of the pawl 98 by changing a fastening angle of the pawl 98. However, when this configuration is adopted, if a projected angle of the pawl 98 is strongly modified, a direction of the force (vector) does not pass through the center of rotation of the stop wheel 372. In this case, it is possible that the performance of the constant force are poor. Therefore, it is necessary to focus on the design.
[0203] (Fourth example of modification of the first embodiment) [0204] In the following, with reference to FIG. 18, a fourth modification example of the first embodiment will be described.
[0205] FIG. 18 is a plan view illustrating a state of engagement between a stop wheel 472 (wheel and pinion gear assembly 470) and a pawl 498 of a stopper 496 according to a fourth modification example of the first embodiment.
As shown in the figure, a difference between the third modification example of the first embodiment and the fourth modification example of the first embodiment is that a shape of the pawl 498 is different.
More specifically, a lateral side 498a on the outer peripheral side of the pawl 498 has the shape of an arc. The center of the arc is located coaxially with an axial center C1 of the wheel assembly and fixed gear 31, that is to say the center of rotation of the outer carriage 33 and the center of rotation of the inner carriage 34. therefore, the force vector which is applied to the stop 496 by the stop wheel 472 always passes through the center of rotation of the outer carriage 33 and the center of rotation of the inner carriage 34. Therefore, it is possible to minimize the the influence that a load applied when the wheel and pinion gear 470 and the stopper 496 are engaged with each other is applied to the outer carriage 33 or the inner carriage 34.
[0208] To be more specific about this influence, when the vector of the force applied to the stop 496 by the wheel and pinion 470 does not pass through the center of rotation, the outer carriage 33 applies a torque to inner carriage 34 so that it rotates forwards or backwards. Consequently, the torque of the inner carriage 34 is obtained by adding or subtracting the torque transmitted by the outer carriage 33 to the torque generated by the constant-force spring 68. The torque of the outer carriage 33 varies proportionally with the torque of the wheel. 22. It follows that the torque of the inner carriage 34 is no longer constant.
[0209] Incidentally, in the fourth modification example described above, when the inner carriage 34 rotates in practice and is moved in a direction where the pawl 498 is disengaged from the hook 476 of the stop wheel 472 (in the clockwise in Fig. 18), a friction force acts between the hook 476 and the pawl 498. This friction force causes the vector of the force applied to the stop 496 to be displaced by the wheel. stopping 472 with respect to the axial center C1. Therefore, it is desirable to determine the shape of the hook 476 (76 or 376) as follows. [0210] (Fifth example of modification of the first embodiment) [0211] FIG. 19 is a plan view of a stopping wheel 572 according to a fifth exemplary modification of the first embodiment and corresponds to FIG. 6 of the first embodiment described above.
As shown in the figure, a lateral side 576b of the hook 576 of the stop wheel 572 is formed such that a combined force vector B3, including a vector B1 in a normal direction of a portion. with which the pawl 98 is in contact and a vector B2 of the friction force applied to the pawl 98, passes through the axial center C1 (center of rotation of the outer carriage 33 and the inner carriage 34) of the wheel and fixed gear assembly 31.
According to this configuration, it is possible to more reliably minimize the influence that a load applied when the stop wheel 572 and the pawl 98 are engaged with each other is applied to the outer carriage. 33 or the inner carriage 34.
[0214] (Second embodiment) [0215] In the following, with reference to FIGS. 20 and 21, a second embodiment will be described.
[0216] FIG. 20 is a plan view of a constant force device 230 according to the second embodiment and illustrates a second wheel and pinion assembly 227. FIG. 21 is a cross-sectional view taken along the axis B-B of FIG. 20.
[0217] As shown in FIGS. 20 and 21, a difference between the first embodiment and the second embodiment is that while the vortex with constant force device 30 according to the first embodiment has what is known as a vortex function. , the constant force device 230 according to the second embodiment does not have the vortex function. In addition, in the constant force device 230, the second wheel and pinion assembly 227 also functions as a partial configuration (output unit). The second embodiment does not have the fifth wheel and pinion assembly 28, unlike the first embodiment.
More specifically, the constant-force device 230 comprises the wheel and fixed gear assembly 31 which is fixed to the main plate 11 (not shown in Figures 20 and 21), an axle 231 which is supported, so as to be rotatable, via the hole stone 31b of the wheel and fixed gear assembly 31 and a hole stone placed in a train wheel bridge (not shown), a carriage 232 and a second wheel and pinion assembly 227 which are attached to the shaft 231, the wheel and pinion assembly 70 which is attached to the carriage 232 and the exhaust mechanism 102 which meshes with the second wheel and pinion assembly 227.
[0219] As shown in FIG. 21 axis 231 is configured so that a portion thereof on the wheel and pinion fixed wheel side 31 and slightly separated from the substantial center in the axial direction serve as large diameter portion 231a whose axis diameter is the biggest. Then, the axis 231 is formed so that the diameter is progressively reduced in pitch as it goes from the large-diameter portion 231a to both ends in the axial direction.
More specifically, in the axis 231, a first portion of axis 231b whose diameter is smaller than the large-diameter portion 231a is integrally molded on the axle side of the wheel train (upper side on the Fig. 21) of the large diameter portion 231a. In addition, a second axis portion 231c whose diameter is further reduced than the first axis portion 231b is integrally molded at the distal end of the first axis portion 231b. Then, lugs 231d and 23l are respectively formed to protrude axially outwardly into the distal end of the second axle portion 231c and the wheel and fixed gear assembly side 31 of the large diameter portion 231a.
In the axis 231 configured as described above, a stud 231 d is inserted in the hole stone 31b of the wheel and fixed gear assembly 31, the other stud 231e being inserted into the hole stone of the train wheel bridge (not shown). In this way, the axis 231 is rotatably supported.
In addition, the carriage 232 is externally attached and fixed to the first axis portion 231b of the axis 231, the second wheel and pinion assembly 227 being rotatably supported via the second portion of 231c axis of the axis 231. That is, while the carriage 232 rotates integrally with the axis 231, the second wheel and pinion assembly 227 is rotatably supported relative to the carriage 232 .
The carriage 232 has a substantially annular central portion 233 which is mounted to fit tightly or inserted on the axis 231. The shaft 231 is mounted tight fitting or inserted into a hole 233a formed in the central portion 233. When the shaft 231 is inserted into the hole 233a, the carriage 232 is bonded and fixed to the axis 231 by means of an adhesive.
In addition, an outer gear 234 in the shape of a ring so as to surround the central portion 233 is placed outside the central portion 233 in the radial direction. The external gear 234 meshes with the third wheel and pinion assembly (not shown).
In addition, the central portion 233 and the external gear 234 are connected to one another by three spokes 235. The three spokes 235 extend in the radial direction and are placed at equal intervals in the circumferential direction.
In addition, in the external gear 234, a stop wheel bearing unit 250 which supports the wheel and lock gear 70 so that it can rotate is placed between two spokes 235. among the three rays 235.
The stop wheel bearing unit 250 is configured to have an axis insertion hole 251 integrally formed in the external gear 234, the first stop wheel bearing 52 which is mounted on the main deck side 11 (inner side in Fig. 21) of the outer gear 234, and the second stop wheel bearing 53 which is mounted on the gear wheel bridge side (upper side in Fig. 21) external gear 234.
The pin insertion hole 251 is formed so that the stop wheel pin 71 configuring the wheel and pinion gear assembly 70 can be inserted into the insertion hole of axis 251.
The configuration of the first stop wheel bearing 52, the second stop wheel bearing 53 and the wheel and stop gear assembly 70 is the same as that of the first embodiment described above. . As a result, the same reference numbers will be assigned to them and their description will be omitted. That is, the configuration in which, in the hook 76 of the wheel and pinion gear assembly 70, the side side 76b of the front side is arc-shaped and the center of the arc is set to be coaxial with the axis body 231 is also the same as that of the first embodiment described above. In addition, the configuration in which the pinion 71c configuring the wheel and pinion gear assembly 70 meshes with the toothed portion 31 d of the wheel and pinion gear assembly 31 is also the same as that of the first embodiment described above.
In addition, on an inner peripheral side of the outer gear 234, a stud carrier 266 is integrally formed on one side which is substantially opposed to a portion provided with the stop wheel bearing unit 250. on the axis 231. The stud 67 is mounted tight fitting in the stud holder 266. An outer end of the constant force spring 68 is fixed to the stud 67. On the other hand, an inner end portion of the constant force spring 68 is attached to the second wheel and pinion assembly 227 via the ferrule 69.
[0231] A cylindrical bearing housing 236 protruding toward the carriage side 232 is integrally molded in the substantially radial center of the second wheel and pinion assembly 227. The ferrule 69 is externally attached and secured to the bearing housing 236.
In addition, a cylindrical bearing 237 is mounted with a tight fit in the bearing housing 236. The second wheel and pinion assembly 227 is rotatably supported via the second axle portion 231c of the axle. 231 via the bearing 237. The bearing 237a, for example, is formed of a ruby.
In addition, a C-shaped retaining ring 238 is attached to the distal end side (the side of the other post 213e) of the second axis portion 231c. The axial movement of the second wheel and pinion assembly 227 is regulated by the C-shaped retaining ring 238 and a stepped portion 239 formed between the second axis portion 231c and the first axis portion 231b.
In addition, the stop 96 which is engaged with the hook 76 of the wheel assembly and stop pinion 70 and disengaged therefrom is placed in the second wheel and pinion assembly 227. The configuration of the stop 96 is also the same as that of the first embodiment described above. As a result, the same reference numbers will be assigned to them and their description will be omitted.
[0235] An exhaust pinion 241 of a wheel and exhaust pinion assembly 240 meshes with the second wheel and pinion assembly 227 configured as described above. The wheel and exhaust pinion assembly 240 comprises an axis 242 and an escape wheel 114 which is mounted externally and fixed to the axis 242.
A first stud 242a and a second stud 242b whose diameters are respectively reduced in steps are integrally molded at both ends of the axis 242. The first stud 242a is supported by the wheel axle bridge (not shown) of way to turn. In contrast, the second pin 242b is supported by the main plate 11 so as to rotate. In addition, the exhaust pinion 241 is integrally molded on the portion of the axis 242 located between its substantial center in the axial direction to the first pin 242a.
The wheel and exhaust pinion assembly 240 configured as described above configures the exhaust mechanism. The escape mechanism of the second embodiment also has a basic configuration that is the same as that of the escape mechanism 102 of the first embodiment described above. Therefore, his description will be omitted. In addition, like the first embodiment, the second embodiment is also equipped with the balance with spring balance. However, the balance with pendulum spring is also configured as described in the first embodiment. Therefore, in the second embodiment, the illustration and description of the balance with pendulum spring will be omitted.
[0238] (Operation of the constant-force device) [0239] In the following, the operation of a constant-force device 230 will be described.
[0240] First, a rotational force received by the carriage 232, and the operation of the wheel and lock gear assembly 70 which receives the rotational force, will be described.
Since the external gear 234 meshes with the third wheel and pinion assembly (not shown), the rotational force of the barrel wheel (not shown) is transmitted to the carriage 232 via the front wheelset. . Furthermore, in the wheel and stop gear 70 assembly, the stop gear 71c meshes with the toothed portion 31d of the wheel and fixed gear 31 assembly. Therefore, if the carriage 232 turns, the wheel and pinion assembly 70 rotates about the axial center of the pinion gear 71c and circulates around the wheel and fixed gear assembly 31.
In contrast, the second wheel and pinion assembly 227 is rotatably supported relative to the carriage 232, and is connected to the carriage 232 via the constant force spring 68. Therefore, the second wheel and pinion assembly 227 rotates relative to the carriage 232 by receiving a prestressing force of the constant force spring 68.
In addition, the exhaust pinion 241 of the wheel assembly and exhaust pinion 240 meshes with the second wheel and pinion assembly 227. The second wheel and pinion assembly 227 always rotates at a constant speed. Therefore, the second wheel and pinion assembly 227 is controlled to rotate once per minute.
Here, the hook 76 of the wheel and lock gear assembly 70 and the pawl 98 of the abutment 96 are engaged with each other and disengaged from one another repeatedly. When the hook 76 of the wheel and lock gear assembly 70 and the pawl 98 of the abutment 96 are engaged with each other and the rotation of the wheel and idler gear assembly 70 is stopped. , the rotation of the carriage 232 is also stopped. On the other hand, the second wheel and pinion assembly 227 rotates continuously thanks to the prestressing force of the constant-force spring 68.
Then, if the stop 96 is displaced in response to the rotation of the second wheel and pinion assembly 227 and the pawl 98 of the stop 96 and the hook 76 of the wheel and pinion 70 are disengaged. one of the other, the carriage 232 rotates. At this time, the wheel and stop gear assembly 70 rotates about the axial center of the stop gear 71c and circulates around the wheel and fixed gear assembly 31. In other words, the assembly wheel and stop gear 70 rotates while moving toward the stop 96. Then, the hook 76 of the wheel and stop gear assembly 70 and the pawl 98 of the stop 96 are engaged with each other. other and rotation of the wheel and pinion gear assembly 70 is stopped.
As in the first embodiment described above, the maximum amount of meshing between the hook 76 of the wheel and lock gear assembly 70 and the pawl 98 of the abutment 96 represents a quantity in a range. corresponding to the range of six degrees of rotation about the axis body 231, in the hook 76. In addition, the angle at which the carriage 232 rotates until the hook 76 and the catch 98 are disengaged. from each other, that the wheel and stop gear assembly 70 rotates and that the wheel and stop gear assembly 70 is stopped again represents six degrees, as in the first embodiment described above. .
Here, since the carriage 232 rotates, the pin 67 attached to the carriage 232 is also moved integrally with the carriage 232. Since the pin 67 is moved, the constant force spring 68 is wound. Specifically, the constant force spring 68 is wound until the carriage 232 rotates six times.
Then, in a state where the constant force spring 68 is wound, the carriage 232 (wheel assembly and stop pinion 70) is stopped and the prestressing force of the constant force spring 68 causes the rotation of the second set 227. Since this operation is repeated, the second wheel and pinion assembly 227 rotates continuously at a constant speed.
Therefore, according to the second embodiment described above, it is possible to stop or restart the rotation of the wheel assembly and stop gear 70 by rotating the stop 96 integrally with the second set wheel and pinion 227 and, moreover, by circulating the wheel and lock gear assembly 70 integrally with the carriage 232. Therefore, it is not necessary to use an oscillating element as in the related art for regulating the rotation of the wheel and pinion assembly 70. In this respect, it is possible to reduce the energy loss. In other words, since the wheel and pinion 70 assembly and the second wheel and pinion assembly 227 are in close contact with each other, it is possible to reduce the loss obtained by the second wheel and pinion assembly 227 from wheel and pinion assembly 70.
In addition, in order to cause rotation and revolution of the wheel and stop gear assembly 70 around the wheel and fixed gear assembly 31, a configuration is adopted in which the stop gear 71c is disposed in the wheel assembly and stop gear 70 and the stop gear 71c is meshing with the toothed portion 31d of the wheel and fixed gear assembly 31. Therefore, it is possible to ensure that the wheel and pinion assembly 70 and stop 96 are engaged with each other or disengaged from each other using a simple structure. Therefore, it is possible to reduce the weight, size and cost of the constant force device 230.
In addition, the second wheel and pinion assembly 227 also serves as a partial configuration of the constant-force device 230. Therefore, it is possible to save the placement space of the constant-force device 230 and it is possible to reduce the number of components in the constant force device 230.
[0252] (Example of modification of the second embodiment) [0253] In the following, with reference to FIG. 22, an exemplary modification of the second embodiment will be described.
FIG. 22 is a cross-sectional view of a constant force device 330 according to an exemplary modification of the second embodiment.
As shown in the figure, a difference between the constant-force device 230 of the second embodiment and the constant-force device 330 according to the modification example of the second embodiment is that the shape of the wheel and fixed gear assembly 31 of the second embodiment is different from the shape of a wheel and fixed gear assembly 331 according to the modification example of the second embodiment.
More specifically, the wheel and fixed gear assembly 331 according to the modification example of the second embodiment has the shape of a ring and a toothed portion 331 d is formed in an inner peripheral edge of the latter. this. Then, the diameter of a pitch circle of the toothed portion 331d of the wheel and fixed gear assembly 331 is set to have a dimension that allows the toothed portion 331d to mesh with the stop pinion 71c of the toothed portion 331d. stop wheel axis 71.
In addition, the wheel and lock gear assembly 70 is not provided with the first stop wheel bearing 52. The respective lugs 71a and 71b of the stop wheel axle body 71 are supported. , so as to be rotatable via the hole stone 62 of the second stop wheel bearing 53 and via a hole stone 362 disposed in the carriage 232.
According to this configuration, the wheel and fixed gear assembly 331 is not placed in the main plate 11 contrary to the second embodiment described above, and is arranged between the second stop wheel bearing 53 and the cart 232.
Therefore, according to the modification example of the second embodiment described above, it is not necessary to guarantee a space for the placement of the wheel and fixed gear 331 between the carriage 232 and the 11. Therefore, to this extent, it is possible to reduce the thickness of the constant-force device 330.
In the embodiments described above, a case has been described in which the lateral side 76b of the front side of the hook 76 of the wheel and pinion gear assembly 70 has the shape of an arc, the center of the arc is set to be coaxial with the center of rotation of the outer carriage 33 in the first embodiment, and the center of the arc is set to

权利要求:
Claims (11)
[1]
be coaxial with the axis body 231 in the second embodiment. However, without being exhaustive, the lateral side 76b can have any shape that allows the hook 76 to be engaged with or disengaged from the pawl 98 of the abutment 96. In addition, in the first embodiment described above, a case has been described in which the inner end portion of the constant-force spring 68 is fixed to the axis 83b of the inner carriage 34 via the ferrule 69. In addition, in the second embodiment described above, a case has been described wherein the inner end portion of the constant force spring 68 is attached and secured to the bearing housing 236 of the second wheel and pinion assembly. 227 via the ferrule 69. However, without being exhaustive, a configuration can be adopted in which the ferrules 69 are respectively mounted slightly fitting on the axis 83b of the inner carriage 34 and on the bearing housing 236 of the second set According to this configuration, it is possible to adjust a predetermined winding quantity (initial winding quantity) of the constant-force spring 68 by rotating the ferrule 69 about the axial center relative to the axis 83b of the inner carriage 34 and the bearing housing 236 of the second wheel and pinion assembly 227. In this way, it is possible to adjust the spring output torque. As a result, it is possible to adjust an oscillation angle of the balance with pendulum spring (for example, the rocker with spring balance 101 of FIGS. 2 and 3). In addition, in the first embodiment described above, a case has been described in which the outer end portion of the constant force spring 68 is fixed to the outer carriage 33 and the inner end portion of the constant force spring 68 is attached to the inner carriage 34. In addition, in the second embodiment described above, a case has been described in which the outer end portion of the constant force spring 68 is attached to the external gear 234 and the inner end portion of the constant force spring 68 is attached to the second wheel and pinion assembly 227. However, without being exhaustive, the inner end portions of the constant force spring 68 may be respectively fixed. to the outer carriage 33 and to the outer gear 234, and the outer end portions of the constant force spring 68 can be respectively fixed to the inner trolley 34 and the second wheel and pinion assembly 227. [0264] Here, in the constant-force spring 68, when compared to the outer end portion, the inner end portion is less likely to be subjected to the influence of a step movement (in the first embodiment and the second embodiment described above, a movement in which the outer carriage 33 and the second wheel and pinion assembly 227 rotate by one step; six degrees) on the input side (the outer carriage 33 and the second wheel and pinion assembly 227). Therefore, in the configuration described above, it is possible to cause the constant-force spring 68 to operate stably. In addition, in the second embodiment described above, a case has been described in which the second wheel and pinion assembly 227 also serves as a partial configuration of the constant-force device 230. However, without this being exhaustive. , any one of the escape wheel 114, the second wheel and pinion assembly 227, the third wheel and pinion assembly 26 and the wheel and pinion gear unit 25 may be configured according to the partial configuration (output unit ) of the constant-force device 230. [0266] In addition, in the modification example of the second embodiment described above, a case has been described which uses the wheel and fixed gear assembly 331 having the form of a ring. However, without being exhaustive, the first embodiment and the respective modification examples of the first embodiment described above can also use the wheel and fixed gear 331 which has the shape of a ring. In this way, it is possible to reduce the thickness of the vortex with constant force device 30. Claims
A constant force device for adjusting an output torque, comprising: an output unit (34) which produces the output torque by rotating about an output axis; a constant force spring (68) with a first end attached to an input unit (33) and a second end attached to the output unit (34) and which provides torque to the output unit (34) ; said input unit (33) periodically restoring a pre-tension in the constant force spring (68) by rotating about an input axis; a wheel and lock gear assembly (70; 370; 470) which is rotatably configured about a stop wheel axle (71) in the input unit (33), and which can circulate around the entrance axis; and a stop (96; 196; 496) which is attached to the output unit (34) and which engages with the wheel and lock gear assembly (70; 370; 470) in response to the rotation the wheel and lock gear assembly (70; 370; 470) which rotates about the stop wheel axle (71).
[2]
The constant force device of claim 1, wherein the input axis and the output axis are coaxially disposed relative to each other.
[3]
The constant force device of claim 1 or 2, further comprising: a fixed wheel and pinion assembly (31; 331) which is positioned coaxially with the input axis and which can not rotate with the drive unit (33) and the output unit (34), wherein the wheel and lock gear assembly (70; 370; 470) comprises a stop wheel axle body (71) in which stop wheel axle serves as an axial center, and wherein the stop wheel axle (71) is configured to be able to circulate around the input axis being positioned to engage with the wheel and fixed gear assembly (31; 331).
[4]
4. Constant force device according to one of claims 1 to 3, wherein the stop wheel (72; 372; 472), which comprises the wheel and sprocket of a stop (70; 370; 470) , has a toothed surface having substantially the shape of an arc in which the input axis serves as a center.
[5]
5. Constant force device according to one of claims 1 to 4, wherein the output unit (34) supports a rocker arm with spring balance (101) so as to be rotatable.
[6]
6. Constant force device according to one of claims 1 to 4, wherein the output unit (34) is selected from a wheel and exhaust pinion assembly (111; 240), and a wheel and pinion assembly ( 25; 26; 27; 227).
[7]
The constant force device according to one of claims 1 to 6, further comprising: a phase shift control mechanism (160) which regulates a rotational movement of the output unit (34) relative to the unit input (33), wherein the phase shift control mechanism (160) regulates the rotational movement in a direction in which the input unit (33) is lagging with respect to the output unit (34). ).
[8]
The constant force device according to one of claims 1 to 6, further comprising: a phase shift control mechanism (160) which regulates a rotational movement of the output unit (34) relative to the unit input (33), wherein the phase shift control mechanism (160) regulates the rotational movement in a direction in which the input unit (33) is in advance with respect to the output unit (34). ).
[9]
The constant force device of claim 7 or 8, wherein the phase shift control mechanism (160) comprises: a protrusion which is formed in one of the output and input units (33; 34); and a hole which is formed in the other unit among the output unit (34) and input unit (33), and which is engageable with the protrusion.
[10]
A movement comprising: a constant force device (3) according to claim 1; and a pendulum beam (101) which is actuated by an output torque provided by the constant force device.
[11]
Mechanical watch comprising: a movement according to claim 10.

类似技术:

---

公开号 | 公开日 | 专利标题

---

CH708526B1|2018-09-14|Constant force device, movement and mechanical watch.

---

EP1046965B1|2004-08-18|Self-winding watch

---

CH708525B1|2018-12-14|Mechanism for stabilizing the operation of the sprung balance, watch movement and mechanical watch.

---

EP2583143B1|2015-03-25|Mechanism for advancing a tourbillon cage or a karrusel cage by periodic jumps

---

EP2166419A1|2010-03-24|Clock timepiece movement comprising a constant-force device

---

EP1772783A1|2007-04-11|Watch movement with constant-force device

---

EP2583142B1|2015-01-07|Mechanism for advancing a karrusel cage by periodic jumps

---

CH708390B1|2020-04-30|Escapement comprising an anchor, timepiece movement and timepiece comprising such an escapement.

---

CH709329A2|2015-09-15|Exhaust, room and clockwork timepiece.

---

EP2690507A1|2014-01-29|Holorological hairspring

---

CH709328B1|2020-03-31|Escapement, timepiece movement and timepiece.

---

CH708937B1|2020-03-31|Oscillating element for watch movement.

---

CH701075B1|2010-11-30|Cannon-pinion wheel and arbor assembly for clock movement, has wheel whose hub is connected to felloe to form rigid, monolithic and effectively non-deformable assembly, and pad with surface provided in contact with periphery of arbor

---

CH705938B1|2016-04-29|Planetary gear timepiece.

---

EP3306415B1|2020-05-20|Mechanical clock movement with power-reserve detection

---

EP1272906A1|2003-01-08|Escapement device for timepiece component

---

CH710863A2|2016-09-15|frequency stabilization mechanism, movement and mechanical timepiece.

---

CH710108B1|2020-03-31|Constant force mechanism, movement and timepiece.

---

CH712077A2|2017-07-31|Tourbillon, movement and timepiece.

---

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

---

EP1791041A1|2007-05-30|Timepiece movement

---

CH706543B1|2017-12-29|Clock exhaust mechanism comprising means for decoupling between the pinion and the escape wheel.

---

CH717089A2|2021-07-30|Exhaust and regulator assembly, timepiece movement and timepiece.

---

EP3783444A1|2021-02-24|Timepiece mechanism comprising a locking device

---

CH703331B1|2014-12-31|feed mechanism by periodically skipping a tourbillon cage or carousel cage.

同族专利:

---

公开号 | 公开日

---

JP2015072254A|2015-04-16|

---

US20150063084A1|2015-03-05|

---

US9052693B2|2015-06-09|

---

CH708526A2|2015-03-13|

---

JP6355102B2|2018-07-11|

---

CN104423242A|2015-03-18|

---

CN104423242B|2018-05-04|

引用文献:

---

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

---

---

DE50115494D1|2001-12-15|2010-07-08|Richemont Int Sa|Constant-force device|

---

EP1445669A1|2003-02-10|2004-08-11|Richemont International S.A.|Constant force escapement mechanism for a timepiece with indirect seconds|

---

DE602005021883D1|2005-10-10|2010-07-29|Montres Breguet Sa|Movement with constant force device|

---

DE102005058321B4|2005-12-07|2007-09-06|Lange Uhren Gmbh|Clock|

---

DE102007042797B4|2007-09-07|2010-04-08|Lange Uhren Gmbh|Clock|

---

EP2166419B1|2008-09-18|2013-06-26|Agenhor SA|Clockwork comprising a constant-force device|

---

CN201698159U|2010-06-07|2011-01-05|天津海鸥表业集团有限公司|Constant-force device of watch|

---

EP2397920A1|2010-06-17|2011-12-21|Blancpain S.A.|Mechanism for a jumping tourbillon or karussel cage|

---

EP2506092B1|2011-03-31|2020-01-08|Cartier International AG|Escapement mechanism, in particular for a clock movement|US9568887B2|2015-03-09|2017-02-14|Seiko Instruments Inc.|Operation stabilizing mechanism, movement, and mechanical timepiece|

---

CH711931A2|2015-12-18|2017-06-30|Montres Breguet Sa|Mechanism for adjusting the torque ratio between clockwork mobiles.|

---

JP6630168B2|2016-01-27|2020-01-15|セイコーインスツル株式会社|Escapement devices, constant force devices, movements and mechanical watches|

---

JP6566432B1|2018-06-07|2019-08-28|セイコーインスツル株式会社|Constant torque mechanism, watch movement and watch|

---

CN111062161B|2019-12-11|2021-09-24|浙江大学|Large-tension high-stability light and small constant force device|

法律状态:

优先权:

---

申请号 | 申请日 | 专利标题

---

JP2013183351|2013-09-04|

---

JP2014136182A|JP6355102B2|2013-09-04|2014-07-01|Constant force devices, movements and mechanical watches|

---