JP6847757B2 - Movement and watches - Google Patents

Description

The present invention relates to movements and watches.

As a movement of a mechanical timepiece, a configuration having a plurality of speed governors is known. For example, Patent Document 1 below discloses a configuration in which each carriage of two tourbillons equipped with a speed governor is operated alternately during the daytime and at nighttime.

Japanese Patent No. 4846781

However, in the configuration of Patent Document 1 described above, since the time is displayed based on the rotation of the second wheel that meshes with the barrel wheel, it is necessary to always maintain the rotation speed of the barrel wheel constant regardless of the operating carriage. It was. That is, in the configuration of Patent Document 1, the energy consumption of the barrel wheel does not change even if the carriage to be operated is switched. Therefore, there is still room for improvement in terms of saving energy in the barrel car (Zenmai) and increasing the operating time (duration of the Zenmai) of the clock.

The present invention has been made in consideration of such circumstances, and an object of the present invention is to provide a movement and a timepiece capable of saving energy.

In order to solve the above problems, the movement according to one aspect of the present invention includes a first balance wheel and a second balance wheel that reciprocate, a first state in which the power of an incense box wheel can be transmitted to the first balance sheet, and the incense box. A power transmission mechanism for switching the second state in which the power of the vehicle can be transmitted to the second balance wheel and rotating the incense box wheel at different rotation speeds in the first state and the second state, and a pointer are attached. It includes a pointer wheel in which power is transmitted from the incense box wheel via the power transmission mechanism.

According to this aspect, since the first balance and the second balance are connected to the barrel wheel via the power transmission mechanism, for example, by adjusting the gear ratio of the power transmission mechanism, the first state and the second state The barrel wheel can be rotated at different rotation speeds. As a result, it is possible to save energy in the barrel car (Zenmai) and increase the operating time (duration of the Zenmai) of the clock.
Moreover, in this embodiment, since power is transmitted from the barrel wheel to the pointer wheel via the power transmission mechanism, the first balance and the first balance are different from the configuration in which the pointer wheel is connected between the barrel wheel and the power transmission mechanism. 2 The swing angle, frequency, torque, etc. of the balance can be changed as appropriate. Then, by making the swing angles of the first balance and the second balance different, the rotation speed of the barrel wheel can be switched according to the swing angle of the balance when the operating balance is switched. Therefore, when the watch is not worn or when it is relatively difficult to input disturbance even when the watch is worn, by operating a balance wheel with a small swing angle, energy saving in the barrel wheel can be achieved and the operating time of the watch can be reduced. Can be increased.
On the other hand, for example, in a state in which a watch is worn or in a situation where disturbance is relatively easy to be input (during sports), the influence on the disturbance can be suppressed by operating a balance with a large swing angle or the like. As a result, the timing accuracy can be improved.

In the above aspect, the first balance wheel has a higher frequency than the second balance wheel, and the power transmission mechanism rotates the barrel wheel according to the frequencies of the first balance wheel and the second balance wheel. At the same time, the power output from the barrel wheel may be changed to rotate the pointer wheel at a constant rotation speed.
According to this aspect, the power transmission mechanism shifts the power of the barrel wheel according to the first state and the second state, so that the same pointer wheel can rotate at a constant rotation speed regardless of the first state and the second state. Can be rotated with.
Moreover, in this embodiment, by making the frequencies of the first and second balances different, the influence on the disturbance can be surely suppressed when the balance with a high frequency is operated, and the timekeeping accuracy is improved. be able to.
On the other hand, when the balance with a low frequency is operated, it is possible to further improve the energy saving in the barrel wheel.

In the above aspect, the torques of the first balance and the second balance may be different from each other.
According to this aspect, by making the torques of the first balance and the second balance different, it is possible to surely suppress the influence on the disturbance when operating the balance with high torque, and it is possible to improve the timekeeping accuracy. it can.
On the other hand, when a balance with a small torque is operated, it is possible to further improve energy saving in the barrel wheel (Zenmai).

In the above aspect, the power transmission mechanism includes a transmission mechanism connected to the first balance wheel and the second balance sheet, and the transmission mechanism is arranged coaxially with the first solar wheel and the first solar wheel. It has three gears, a second sun wheel, a carrier that supports the first sun wheel and a planetary wheel that meshes with the second sun wheel so as to rotate and revolve, and among the three gears. The first gear transmits power to the first balance in the first state, the second gear transmits power to the second balance in the second state, and the third gear transmits power from the incense box wheel. May be done.
According to this aspect, by adopting a planetary mechanism as the first transmission mechanism, it is possible to easily switch between the first state and the second state. That is, in the first state, by regulating the rotation of the second gear, the power transmitted to the third gear is transmitted to the first gear via the planetary wheel and then transmitted to the pointer wheel. On the other hand, in the second state, by regulating the rotation of the first gear, the power transmitted to the third gear is transmitted to the second gear via the planetary wheel and then transmitted to the pointer wheel.

In the above aspect, the planetary vehicle may rotate the first gear and the second gear at different rotational speeds according to the frequencies of the first balance and the second balance.
According to this aspect, the rotation speeds of the first gear and the second gear can be made different by adjusting the number of teeth of the planetary wheel. As a result, the difference in frequency between the first balance and the second balance can be canceled by the first transmission mechanism. Therefore, the pointer wheel can be operated at a constant rotation speed regardless of the first state and the second state.

In the above aspect, the power transmission mechanism regulates the reciprocating rotation of the second balance in the first state, and regulates the reciprocating rotation of the first balance in the second state. You may be prepared.
According to this aspect, by restricting the reciprocating rotation of the balance with hairspring that does not contribute to hand movement in the first state and the second state, the whiskers of the balance with hair movement that do not contribute to hand movement can be held in a stretched and deformed state (natural length). Can be suppressed). Therefore, after switching between the first state and the second state, the balance with hairspring can be quickly returned to normal operation.

The watch according to one aspect of the present invention may include the movement of the above aspect.
According to this aspect, it is possible to provide a high quality and highly reliable timepiece.

According to the present invention, energy saving can be achieved.

It is an external view of the timepiece which concerns on 1st Embodiment. It is a top view which looked at the main part of the movement which concerns on 1st Embodiment from the back side. It is a system diagram of the movement which concerns on 1st Embodiment. It is a perspective view of the main part of the movement which concerns on 1st Embodiment. It is an exploded perspective view of the 1st differential mechanism. It is sectional drawing of the 1st differential mechanism. It is an exploded perspective view of the 2nd differential mechanism. It is sectional drawing of the 2nd differential mechanism. It is a top view corresponding to FIG. 2 in a low vibration mode. It is a system diagram of the movement which concerns on the modification of 1st Embodiment. It is a system diagram of the movement which concerns on the modification of 1st Embodiment. It is sectional drawing of the 1st differential mechanism in the movement which concerns on 2nd Embodiment. It is sectional drawing corresponding to FIG. 12 for demonstrating a high vibration mode. It is sectional drawing of the 2nd differential mechanism which concerns on other structure of embodiment.

Hereinafter, embodiments according to the present invention will be described with reference to the drawings.
(First Embodiment)
[clock]
FIG. 1 is an external view of the clock 1. In each of the drawings shown below, in order to make the drawings easier to see, some of the timepiece parts may be omitted, and each timepiece part may be simplified and shown.
As shown in FIG. 1, the watch 1 of the present embodiment is configured by incorporating a movement 2, a dial 3, various pointers 4 to 6, and the like in the watch case 7.

The watch case 7 includes a case main body 11, a case lid (not shown), and a cover glass 12. A crown 15 is provided at the 3 o'clock position (on the right side in FIG. 1) on the side surface of the case body 11. The crown 15 is for operating the movement 2 from the outside of the case body 11. The crown 15 is fixed to the winding stem 19 inserted in the case body 11.

[Movement]
The movement 2 is configured by rotatably supporting a plurality of gears or the like on a main plate 21 constituting the substrate of the movement 2. The above-mentioned winding stem 19 is incorporated in the main plate 21. Volume 19 is used to correct the date and time. The winding stem 19 is rotatable around its axis and movable in the axial direction. In the following description, the cover glass 12 side (dial 3 side) of the watch case 7 is referred to as the "back side" of the movement 2 with respect to the main plate 21, and the case lid side (opposite to the dial 3 side) is referred to. It is referred to as the "front side" of the movement 2. Further, each of the gears described below is provided with the front and back surfaces of the movement 2 as the axial direction.

FIG. 2 is a plan view of the main part of the movement 2 as viewed from the back side. FIG. 3 is a system diagram of the movement 2. The numbers in parentheses in FIG. 3 indicate the ratio of the operating speed in the low vibration mode when the operating speed in the high vibration mode described later is 1.
As shown in FIGS. 2 and 3, the main plate 21 (see FIG. 1) of the movement 2 includes a barrel wheel 24, a second wheel 25, a switching mechanism (power transmission mechanism) 26, and a first speed governor 27. A second speed governor escapement 28, a regulation mechanism (power transmission mechanism) 29, a display wheel train 30, and the like are mounted.

The barrel wheel 24 has a royal fern (not shown) that serves as a power source for the clock 1 inside. The royal fern is wound up, for example, by rotating the winding stem 19. The barrel wheel 24 rotates due to the rotational force (restoring force) when the royal fern is rewound.
The second kana 25a of the second wheel 25 meshes with the barrel wheel 24. The second gear 25b of the second wheel 25 is connected to the switching mechanism 26.

<Switching mechanism>
FIG. 4 is a perspective view of a main part of the movement 2.
As shown in FIG. 4, the switching mechanism 26 includes a first differential mechanism (transmission mechanism) 42, a second differential mechanism 43, a first fourth wheel 44, a second fourth wheel 45, and the like.
The first differential mechanism 42 transmits the power transmitted from the barrel wheel 24 via the second wheel 25 to either the first fourth wheel 44 or the second fourth wheel 45.

FIG. 5 is an exploded perspective view of the first differential mechanism 42. FIG. 6 is a cross-sectional view of the first differential mechanism 42.
As shown in FIGS. 5 and 6, the first differential mechanism 42 includes a first table solar wheel (first solar wheel, third gear) 51, a first carrier (first gear) 52, a first planetary wheel 53, and It has a first back solar wheel (second solar wheel, second gear) 54. Of the first differential mechanism 42, the first front solar wheel 51, the first carrier 52, and the first back solar wheel 54 are arranged coaxially with each other with the front and back directions as axial directions, and can rotate relative to each other. It is configured.

First, the first carrier 52 has a first carrier true 52a and a carrier main body portion 52b fixed to the first carrier true 52a.
The first carrier true 52a penetrates the first front solar wheel 51 and the first back solar wheel 54 in the front and back directions, respectively.

The carrier main body 52b is arranged between the first front solar wheel 51 and the first back solar wheel 54 in the front and back directions. The carrier main body portion 52b has a hub portion 61 fixed to the first carrier true 52a, a rim portion 62 surrounding the hub portion 61, and a spoke portion 63 connecting the hub portion 61 and the rim portion 62. ing.
A first carrier gear 52c is formed on the outer peripheral surface of the rim portion 62.

The first table solar wheel 51 is configured by disposing the first table sun kana 51b and the first table sun gear 51c at both ends in the front and back directions of the first table sun true 51a.
Table 1 Sun true 51a is formed in a tubular shape. The front end portion of the first carrier true 52a described above is inserted into the sun true 51a in Table 1 via a bearing 64. As a result, the table 1 solar wheel 51 is configured to be rotatable with respect to the first carrier 52.
Table 1 Sun Kana 51b is located at the front end of Table 1 Sun True 51a. Table 1 The sun kana 51b meshes with the second gear 25b of the second wheel 25.

The first back solar wheel 54 is configured by disposing the first back sun kana 54b and the first back sun gear 54c at both ends of the first back sun true 54a in the front and back directions.
The first back sun true 54a is formed in a tubular shape. The back end portion of the first carrier true 52a described above is inserted into the first back sun true 54a via a bearing 65. As a result, the first back solar wheel 54 is configured to be rotatable with respect to the first carrier 52.

The first planetary vehicle 53 is rotatably supported by one spoke portion 63a of the spoke portions 63 of the first carrier 52 (carrier main body portion 52b) described above. The first planetary vehicle 53 is configured by disposing the first planetary kana 53b and the first planetary gear 53c at both ends of the first planetary true 53a in the front-back direction.
The first planet Shin 53a penetrates one spoke portion 63a in the front-back direction. The first planetary true 53a is rotatably supported by one spoke portion 63a via a bearing 66.

The first planet kana 53b is arranged at the front end portion (the portion located on the front side with respect to the carrier main body portion 52b) of the first planet true 53a. The first planet Kana 53b meshes with the above-mentioned Table 1 solar gear 51c.
The first planetary gear 53c is arranged at the back end portion (the portion located on the back side with respect to the carrier main body portion 52b) of the first planet true 53a. The first planetary gear 53c is meshed with the above-mentioned first back sun kana 54b. Therefore, the first planetary vehicle 53 of the present embodiment revolves around the first sun wheels 51a and 54a with the rotation of the first carrier 52, and with respect to the first carrier 52 with the rotation of the solar vehicles 51 and 54. Rotate.

Here, in the present embodiment, the number of teeth of the first differential mechanism 42 is set as shown in Table 1 below.

In this case, as shown in Table 2 below, when the first carrier 52 is fixed, the gear ratio (acceleration ratio) of the first back solar vehicle 54 with respect to the first front solar vehicle 51 is "3". .. On the other hand, when the first back solar vehicle 54 is fixed, the gear ratio (acceleration ratio) of the first carrier 52 with respect to the first front solar vehicle 51 is "1.5". That is, the gear ratio of the first back solar vehicle 54 with respect to the first front solar vehicle 51 when the first carrier 52 is fixed is the first carrier with respect to the first front solar vehicle 51 when the first back solar vehicle 54 is fixed. It is twice the gear ratio of 52.

As shown in FIG. 4, the first fourth kana 44a of the first fourth wheel 44 meshes with the first carrier gear 52c described above. The first fourth gear 44b of the first fourth wheel 44 is connected to the first speed governor 27.
The second fourth kana 45a of the second fourth wheel 45 meshes with the first back sun gear 54c described above. The second fourth gear 45b of the second fourth wheel 45 is connected to the second speed governor 28. In the present embodiment, the number of teeth of the fourth wheels 44 and 45 of each of the fourth wheels 44a and 45a and the number of teeth of the fourth gears 44b and 45b are the same.

As shown in FIGS. 2 and 4, the first governor escapement 27 has a first escape wheel 71, a first pallet fork 72, and a first balance with hairspring 73.
The first escape wheel 71 has a first escape gear 71a and a first escape wheel 71b. The first escape kana 71a meshes with the first fourth gear 44b of the first fourth wheel 44 described above. That is, the first escape wheel 71 rotates with the rotation of the first fourth wheel 44.

The first ankle 72 is configured to be reciprocally rotatable with the front and back surfaces as axial directions. The first pallet fork 72 includes a pair of claw stones 74a and 74b. The claw stones 74a and 74b alternately engage with the first escape gear 71a of the first escape wheel 71 as the first pallet fork 72 reciprocates. The rotation of the first escape wheel 71 is temporarily stopped when one of the pair of claw stones 74a and 74b is engaged with the first escape wheel 71a. Further, the first escape wheel 71 rotates when the pair of claw stones 74a and 74b are separated from the first escape gear 71a. By continuously repeating these operations, the first escape wheel 71 rotates intermittently. Then, the above-mentioned switching mechanism 26 operates intermittently due to the intermittent rotational movement of the first escape wheel 71.

The first balance sheet 73 controls the speed of the first escape wheel 71 (the first escape wheel 71 escapes at a constant speed). The first balance with hairspring 73 mainly has a first balance with hairspring 81, a first balance with hairspring 82, and a first balance spring 83.
The first balance spring 81 rotates forward and reverse at a constant frequency with the front and back directions as axial directions by the power transmitted from the first hairspring 83. The first balance with hairspring 81 repeats engagement and disengagement with the ankle haco (not shown) of the first ankle 72 in synchronization with the reciprocating rotation of the first balance with hairspring 73. As a result, the first pallet fork 72 reciprocates, so that the claw stones 74a and 74b repeatedly engage with and disengage from the first escape wheel 71.

The first balance sheet 82 is fixed to the first balance sheet 81 by press fitting or the like.
The first hairspring 83 is a spiral balance spring when viewed from the front and back directions. The inner end of the first hairspring 83 is connected to the first balance spring 81, and the outer end is connected to the hairspring (not shown).

The second governor escapement 28 has a second escape wheel 85, a second pallet fork 86, and a second balance with hairspring 87. Since the second speed governor 28 has the same configuration as the first speed governor 27, the description thereof will be omitted as appropriate.
The second escape wheel 85 has a second escape gear 85a and a second escape wheel 85b. The second stubborn 85a meshes with the fourth gear 45b of the second fourth wheel 45 described above. That is, the second escape wheel 85 rotates with the rotation of the second fourth wheel 45. The number of teeth of the second escape wheel 85b is set to be twice that of the number of teeth of the first escape wheel 71b of the first escape wheel 71.

The second pallet fork 86 includes a pair of claw stones 91a and 91b. The claw stones 91a and 91b rotate intermittently by alternately engaging with the second escape gear 85a of the second escape wheel 85 as the second pallet fork 86 reciprocates. Then, the above-mentioned switching mechanism 26 operates intermittently due to the intermittent rotational movement of the second escape wheel 71.

The second balance with hairspring 87 controls the speed of the second escape wheel 85 (the second escape wheel 85 escapes at a constant speed). The second balance with hairspring 87 mainly has a second balance with hairspring 92, a second balance with hairspring 93, and a second balance spring 94.

Here, the frequencies of the first balance sheet 73 and the second balance sheet 87 are different from each other. In the present embodiment, the frequency of the first balance sheet 73 is set to 4 Hz (8 vibrations per second). The frequency of the second balance sheet 87 is set to 1/2 times the frequency of the first balance sheet 73 (2 Hz (4 vibrations per second)). The frequency F of the balance with hairspring 73 and 87 is expressed by the following equation (1). In equation (1), I represents the "moment of inertia" of the balance spring and K represents the "spring constant" of the balance spring.

As can be seen from the equation (1), the frequency F of the balance springs 73 and 87 changes according to the moment of inertia I of the balance springs 73 and 87 and the spring constant K of the balance spring 83 and 94. Specifically, the smaller the moment of inertia I, the higher the frequency F, and the larger the spring constant K, the higher the frequency F. In the present embodiment, the moment of inertia I of the first balance sheet 73 (outer diameter of the first balance wheel 82) is made smaller than the moment of inertia I of the second balance sheet 87 (outer diameter of the second balance wheel 93). The frequencies F of the balances 73 and 87 are different. The moment of inertia I may be adjusted by changing the materials of the balance wheels 82 and 93. Further, the frequency F of the balance springs 73 and 87 may be different by making the spring constants K of the hairsprings 83 and 94 different. Further, the frequencies F of the balance plates 73 and 87 can be changed as appropriate if they are different from each other.

FIG. 7 is an exploded perspective view of the second differential mechanism 43. FIG. 8 is a cross-sectional view of the second differential mechanism 43.
As shown in FIGS. 7 and 8, the second differential mechanism 43 transmits the power of the first differential mechanism 42 to the display train wheel 30. Specifically, the second differential mechanism 43 has a second front solar vehicle 101, a second carrier 102, a second planetary vehicle 103, and a second back solar vehicle 104. Of the second differential mechanism 43, the second front solar wheel 101, the second carrier 102, and the second back solar wheel 104 are arranged coaxially with each other with the front and back directions as axial directions, and can rotate relative to each other. It is configured. In the following description, the description of the same configuration as that of the first differential mechanism 42 will be omitted as appropriate.

First, the second carrier 102 has a second carrier true 102a and a carrier main body 102b fixed to the second carrier true 102a.
The second carrier true 102a penetrates the second front solar wheel 101 and the second back solar wheel 104 in the front and back directions, respectively.

The carrier main body 102b is arranged between the second front solar wheel 101 and the second back solar wheel 104. The carrier main body 102b has a hub 110 fixed to the second carrier true 102a, a rim 111 surrounding the hub 110, and spokes 112 connecting the hub 110 and the rim 111. ing.
A second carrier gear 102c is formed on the outer peripheral surface of the rim portion 111. The second carrier gear 102c meshes with the first carrier gear 52c of the first carrier 52 described above.

The second table solar wheel 101 is configured by disposing the second table sun kana 101b and the second table sun gear 101c at both ends in the front and back directions of the second table sun true 101a.
Table 2 Sun true 101a is formed in a tubular shape. The front end portion of the second carrier true 102a described above is inserted into the sun true 101a in Table 2 via a bearing 115.

The second back solar wheel 104 is configured by disposing a second back sun kana 104b and a second back sun gear 104c at both ends of the second back sun true 104a in the front and back directions.
The second back sun true 104a is formed in a tubular shape. The back end of the second carrier true 102a described above is inserted into the second back sun true 104a via a bearing 116.
The second back sun gear 104c meshes with the first back sun gear 54c described above.

The second planetary vehicle 103 is rotatably supported by one spoke portion 112a of the spoke portions 112 of the second carrier 102 (carrier main body portion 102b) described above. The second planetary vehicle 103 is configured by disposing a second planetary kana 103b and a second planetary gear 103c at both ends of the second planetary true 103a in the front-back direction.
The second planet Shin 103a penetrates one spoke portion 112a in the front-back direction. The second planetary true 103a is rotatably supported by one spoke portion 112a via a bearing 117.

The second planet kana 103b is arranged at the front end portion (the portion located on the front side with respect to the carrier main body portion 102b) of the second planet true 103a. The second planet Kana 103b meshes with the above-mentioned Table 2 Sun Kana 101b.
The second planetary gear 103c is arranged at the back end portion (the portion located on the back side with respect to the carrier main body portion 102b) of the second planet true 103a. The second planetary gear 103c is meshed with the above-mentioned second back sun kana 104b. Therefore, the second planetary vehicle 103 of the present embodiment revolves around the second sun true 101a, 104a with the rotation of the second carrier 102, and with respect to the second carrier 102 with the rotation of the solar vehicles 101, 104. Rotate.

Here, in the present embodiment, the number of teeth of the second differential mechanism 43 is set as shown in Table 3 below.

In this case, as shown in Table 4 below, when the second carrier 102 is fixed, the gear ratio (reduction ratio) of the second front solar vehicle 101 to the second back solar vehicle 104 is "0.5". There is. On the other hand, when the second back solar vehicle 104 is fixed, the gear ratio (reduction ratio) of the second front solar vehicle 101 with respect to the second carrier 102 is "0.5". That is, the gear ratio of the second front solar vehicle 101 with respect to the second back solar vehicle 104 is set to be equal to the gear ratio of the second front solar vehicle 101 with respect to the second carrier 102.

As shown in FIG. 2, the regulation mechanism 29 alternately regulates the reciprocating rotation of the above-mentioned balances 73 and 87. Specifically, the regulation mechanism 29 includes a rotation shaft 120, a rotation lever 121, a first brake shoe 122, and a second brake shoe 123.

The rotation shaft 120 extends in the front and back directions. The rotating shaft 120 is configured to be rotatable with the front and back surfaces as the axial direction in conjunction with, for example, the rotation operation around the axis of the winding stem 19.
The rotation lever 121 is fixed to the rotation shaft 120. The rotation lever 121 extends on both sides in a direction orthogonal to the front and back surfaces with the rotation shaft 120 as the center.

The first brake shoe 122 is connected to the first end of the rotary lever 121. The second brake shoe 123 is connected to the second end of the rotary lever 121 (the end opposite to the first end of the rotary lever 121 with the rotary shaft 120 in between). The rotation (winding) of the rotation shaft 120 between the first brake shoe 122 and the first balance sheet 73 (first balance wheel 82) and between the second brake shoe 123 and the second balance sheet 87 (second balance wheel 93). As the rotation operation of the true 19), they are alternately brought in and out. Specifically, when the first brake shoe 122 and the first balance wheel 82 are in contact with each other, the second brake shoe 123 and the second balance wheel 93 are separated from each other. As a result, the rotation of the first balance sheet 73 is restricted, while the rotation of the second balance sheet 87 is allowed. Further, when the first brake shoe 122 and the first balance wheel 82 are separated from each other, the second brake shoe 123 and the second balance wheel 93 come into contact with each other. As a result, the rotation of the first balance sheet 73 is allowed, while the rotation of the second balance sheet 87 is restricted.

The regulation mechanism 29 can be appropriately changed as long as the rotation of the balance plates 73 and 87 is regulated alternately. For example, in the present embodiment, the brake shoes 122 and 123 are integrally connected to the rotating lever 121, but the present invention is not limited to this configuration, and the brake shoes 122 and 123 may be provided independently. ..
The method of regulating the balance with hairspring 73 and 87 by the brake shoes 122 and 123 is not limited to the frictional force between the balance with hairspring 73 and 87 and the brake shoes 122 and 123, and can be changed as appropriate. For example, the balance with hairspring 73, 87 and the corresponding brake shoes 122, 123 may be engaged with each other due to unevenness or the like.
In the present embodiment, the configuration in which the brake shoes 122 and 123 are brought into contact with and detached from the corresponding balance wheels 82 and 93 has been described, but the configuration is not limited to this configuration. As long as the rotation of the balance with hairspring 73 and 87 is regulated alternately, the structure may be such that the balance with or from the balance with wheels 82 and 93 (for example, balance stems 81 and 92, etc.) is connected to and separated from each other.

As shown in FIG. 4, the display train wheel 30 has a second wheel 130, a minute wheel (not shown), and an hour wheel (not shown).
The second wheel 130 meshes with the table 2 solar gear 101c of the table 2 solar wheel 101 described above. The second hand 6 described above is attached to the second wheel 130. The number of teeth of the second wheel 130 is set so as to make one rotation in 60 seconds.
The minute wheel meshes with, for example, the second wheel. A minute hand 5 is attached to the minute wheel. The number of teeth of the branch wheel is set so that it makes one rotation in 60 minutes.
The hour wheel meshes with, for example, the branch wheel. An hour hand 4 is attached to the hour wheel. The number of teeth of the hour wheel is set so that it makes one rotation in 12 hours.

[Action]
Next, the operation of the clock 1 described above will be described.
The clock 1 of the present embodiment has a high vibration mode (first state) in which the rotation of the barrel wheel 24 is controlled by the first speed governor 27, and the rotation of the barrel wheel 24 is controlled by the second speed governor 28. It can be operated by switching to the controlled low vibration mode (second state). As shown in FIG. 2, the switching of each mode is performed by operating the regulation mechanism 29 by, for example, rotating the winding stem 19 as described above. That is, in the high vibration mode, the first brake shoe 122 and the first balance wheel 82 are separated from each other, and the rotation of the first balance sheet 73 is allowed. In the low vibration mode, the second brake shoe 123 and the second balance wheel 93 are separated from each other, and the rotation of the second balance sheet 87 is allowed.

<High vibration mode>
First, the high vibration mode will be described.
As shown in FIGS. 2 and 3, when the barrel wheel 24 is rotated by the power of the royal fern, the second wheel 25 is rotated. The rotational force of the second wheel 25 is transmitted to the table 1 solar wheel 51 of the first differential mechanism 42, so that the table 1 solar wheel 51 rotates.

Here, in the high vibration mode, since the rotation of the second balance sheet 87 is restricted, the operations of the second speed governor 28, the second fourth wheel 45, and the first back solar wheel 54 are stopped. There is. Therefore, in the high vibration mode, the power of the barrel wheel 24 is not transmitted to the second balance sheet 87, but is transmitted to the first balance plate 73. Specifically, when the table 1 solar wheel 51 rotates in the high vibration mode, the first planetary wheel 53 rotates while revolving around the first sun wheels 51a and 54a, and the first carrier 52 rotates. When the first carrier 52 rotates, the first fourth wheel 44 rotates, so that the rotational force is transmitted to the first escape wheel 71.

As the first pallet fork 72 rotates with the rotation of the first escape wheel 71, the rotational force of the first escape wheel 71 is applied to the first balance sheet 73. The first balance wheel 73 reciprocates around the first balance spring 81 at a constant frequency (4 Hz) by the rotational force of the first escape wheel 71 and the spring force of the first balance spring 83. When the first balance sheet 73 reciprocates, the claw stones 74a and 74b alternately engage and disengage with the first escape gear 71a. As a result, the first escape wheel 71 rotates intermittently, so that the first fourth wheel 44 and the first differential mechanism 42 (Table 1 solar wheel 51, first carrier 52, and first planetary wheel 53) ) Works intermittently.

On the other hand, in the first differential mechanism 42, the rotational force of the first carrier 52 is transmitted to the second differential mechanism 43 via the second carrier 102. At this time, since the first back solar vehicle 54 is stopped, the second back solar vehicle 104 maintains the stopped state. As a result, when the second carrier 102 rotates in the high vibration mode, the second planetary wheel 103 rotates while revolving around the second sun true 101a and 104a. As a result, the sun wheel 101 in Table 2 rotates at half the rotation speed of the second carrier 102 (see Table 4). Table 2 The clock 1 ticks by transmitting the rotational force of the solar wheel 101 to the display train wheel 30. That is, in the high vibration mode, the first balance sheet 73 vibrates eight times, so that the second hand 6 (second wheel 130) moves one second in eight steps.

<Low vibration mode>
Next, the low vibration mode will be described. FIG. 9 is a plan view corresponding to FIG. 2 in the low vibration mode. In the following description, the description of the same operation as the high vibration mode will be omitted as appropriate.
As shown in FIGS. 3 and 9, in the low vibration mode, the rotation of the first balance sheet 73 is restricted, so that the first speed governor 27, the first fourth wheel 44, and the first carrier 52 The operation is stopped. Therefore, in the low vibration mode, the power of the barrel wheel 24 is not transmitted to the first balance sheet 73, but is transmitted to the second balance sheet 87. Specifically, in the low vibration mode, when the first front solar wheel 51 rotates with the rotation of the second wheel 25, the first planetary wheel 53 rotates, so that the first back solar wheel 54 rotates. As a result, the rotation of the second fourth wheel 45 causes the rotational force to be transmitted to the second escape wheel 85.

As the second pallet fork 86 rotates with the rotation of the second escape wheel 85, the rotational force of the second escape wheel 85 is applied to the second balance sheet 87. The second balance wheel 87 reciprocates around the second balance spring 92 at a constant frequency (2 Hz) by the rotational force of the second escape wheel 85 and the spring force of the second balance spring 94. When the second balance sheet 87 reciprocates, the claw stones 91a and 91b alternately engage and disengage with the second escape gear 85a. As a result, the second escape wheel 85 rotates intermittently, so that the second fourth wheel 45 and the first differential mechanism 42 (the first table solar wheel 51, the first planetary wheel 53, and the first back sun) The car 54) operates intermittently.

Here, the frequency of the second balance sheet 87 is set to half the frequency of the first balance sheet 73. Further, in the first differential mechanism 42, as shown in Table 2, the gear ratio of the first front solar vehicle 51 to the first back solar vehicle 54 when the first carrier 52 is fixed, and the first back solar vehicle 54. The gear ratio of the solar vehicle 51 in Table 1 with respect to the first carrier 52 when is fixed is set to "1", respectively. Therefore, the rotation speed of the barrel wheel 24 in the low vibration mode is half the rotation speed of the barrel wheel 24 in the high vibration mode.

On the other hand, in the first differential mechanism 42, as shown in Table 2, the gear ratio of the first back solar vehicle 54 with respect to the first front solar vehicle 51 when the first carrier 52 is fixed is the first back solar vehicle 54. It is twice the gear ratio of the first carrier 52 with respect to the solar wheel 51 in Table 1 when is fixed. Therefore, the rotation speed of the first back solar wheel 54 in the low vibration mode is the same as the rotation speed of the first carrier 52 in the high vibration mode. That is, the difference in the frequencies of the balance with hairspring 73 and 87 in the high vibration mode and the low vibration mode is canceled by the first differential mechanism 42, so that the first differential mechanism 42 in the low vibration mode and the high vibration mode cancels the difference. The output to the second differential mechanism 43 becomes equivalent.

Then, in the first differential mechanism 42, the rotational force of the first back solar wheel 54 is transmitted to the second differential mechanism 43 via the second back solar wheel 104. At this time, since the first carrier 52 is stopped, the second carrier 102 maintains the stopped state. As a result, when the second back solar wheel 104 rotates in the low vibration mode, the second planetary wheel 103 rotates on its axis. Therefore, the second front solar wheel 101 rotates at half the rotation speed of the second back solar wheel 104 (see Table 4). As a result, the rotation speed of the solar wheel 101 in Table 2 becomes the same in both the low vibration mode and the high vibration mode. Then, the rotational force of the solar wheel 101 in Table 2 is transmitted to the display train wheel 30, so that the clock 1 ticks. That is, in the low vibration mode, the second balance sheet 87 vibrates four times, so that the second hand 6 (second wheel 130) moves one second in four steps.

As described above, in the present embodiment, the first differential mechanism 42 rotates the barrel wheel 24 at different rotation speeds, and the power of the barrel wheel 24 is transmitted to the display train wheel 30 via the first differential mechanism 42. The configuration was set.
According to this configuration, unlike the configuration in which the display wheel train 30 is connected between the barrel wheel 24 and the first differential mechanism 42, the frequencies of the lamps 73 and 87 when the operating balance wheels 73 and 87 are switched. The rotation speed of the barrel wheel 24 can be switched according to the above. Thereby, for example, in the wearing state of the watch 1 or the situation where the disturbance is relatively easy to be input even in the wearing state (during sports), the influence on the disturbance can be suppressed by setting the high vibration mode. As a result, the timing accuracy can be improved.
On the other hand, in the non-mounted state of the clock 1 or in the situation where it is relatively difficult to input disturbance even in the mounted state, the clock 1 can be set to the low vibration mode to save energy in the barrel car 24 (Zenmai). The operating time (duration of the royal fern) can be increased. In addition, wear of each gear can be suppressed.

In the present embodiment, the switching mechanism 26 rotates the barrel wheel 24 according to the frequencies of the first balance wheel 73 and the second balance sheet 87, and shifts the power output from the barrel wheel 24 to keep the second wheel 130 constant. It was configured to rotate at the rotation speed of.
According to this configuration, the same second wheel 130 can be rotated at a constant rotation speed in each mode. Moreover, by setting the frequency of the first balance sheet 73 higher than the frequency of the second balance sheet 87, the influence on the disturbance can be surely suppressed in the high vibration mode, and the timekeeping accuracy can be improved.
On the other hand, by setting the frequency of the second balance sheet 87 to be lower than the frequency of the first balance sheet 73, in the low vibration mode, the energy saving of the barrel wheel 24 (Zenmai) is further improved, and each gear is further improved. Wear can be suppressed.

In the present embodiment, the planetary mechanism is adopted as the first differential mechanism 42.
According to this configuration, by adopting the planetary mechanism for the first differential mechanism 42, it is possible to easily switch between the high vibration mode and the low vibration mode. That is, in the high vibration mode, the rotation of the second balance sheet 87 is restricted, so that the rotation of the first back solar wheel 54 is stopped. Therefore, the power transmitted to the table 1 solar car 51 is transmitted to the display train wheel 30 after being transmitted to the first carrier 52 via the first planet car 53. On the other hand, in the low vibration mode, the rotation of the first balance sheet 73 is restricted, so that the rotation of the first carrier 52 is stopped. Therefore, the power transmitted to the first front solar vehicle 51 is transmitted to the first back solar vehicle 54 via the first planetary vehicle 53, and then is transmitted to the display train wheel 30.
In particular, in the present embodiment, the rotation speeds of the first carrier 52 and the first back solar wheel 54 can be made different by adjusting the number of teeth of the first planetary wheel 53. As a result, the difference in frequency between the first balance sheet 73 and the second balance sheet 87 can be canceled by the first differential mechanism 42. Therefore, the display wheel train 30 can be operated at a constant rotation speed regardless of the high vibration mode and the low vibration mode.

In the present embodiment, the configuration is provided with a regulation mechanism 29 that regulates the reciprocating rotation of the second balance sheet 87 in the high vibration mode and regulates the reciprocating rotation of the first balance sheet 73 in the low vibration mode.
According to this configuration, in each mode, the reciprocating rotation of the balance with hairspring 73 and 87 that does not contribute to the hand movement is restricted, so that the whiskers 83 and 94 of the balance with hairspring 73 and 87 that do not contribute to the hand movement are held in a stretched and deformed state. Can (can suppress natural length). Therefore, after the mode is switched, the balance with hairspring 73 and 87 can be quickly returned to normal operation.

Since the clock 1 of the present embodiment includes the movement 2 described above, it is possible to provide the clock 1 with high quality and excellent reliability.

(Modification example)
Next, a modified example of the above-described first embodiment will be described.
In the above-described embodiment, the configuration in which the first differential mechanism 42 and the second differential mechanism 43 are directly connected has been described, but the configuration is not limited to this configuration. For example, as shown in FIG. 10, the first differential mechanism 42 and the second differential mechanism 43 may be connected via the fourth wheels 44 and 45.
In the above-described embodiment, the configuration in which the first differential mechanism 42 is connected to the fourth wheels 44, 45 and the speed governors 27, 28 has been described, but the configuration is not limited to this configuration. For example, as shown in FIG. 11, the first differential mechanism 42 may be connected to the fourth wheels 44, 45 and the speed governors 27, 28 via the second differential mechanism 43. Absent.

In the above-described embodiment, the configuration in which the difference in frequency between the first balance sheet 73 and the second balance sheet 87 is canceled by the first differential mechanism 42 has been described, but the configuration is not limited to this configuration. For example, by adjusting the number of teeth of the gears (for example, the fourth wheels 44, 45, etc.) provided between the first differential mechanism 42 and the speed governors 27, 28, the first balance sheet 73 and A configuration that cancels the difference in frequency of the second balance with hairspring 87 may be used.
In the above-described embodiment, the front solar wheel 51 is connected to the second wheel 25, the first carrier 52 is connected to the first fourth wheel 44, and the first back solar wheel 54 is connected to the second fourth wheel 45. The connected configuration has been described, but is not limited to this configuration. That is, in the first differential mechanism 42, the second wheel 25 and the fourth wheel 44, 45 may be separately connected to the three gears.
In the above-described embodiment, the configuration in which the rotation of either the first carrier 52 or the first back solar wheel 54 is stopped according to each mode by the operation of the regulation mechanism 29 has been described, but the configuration is not limited to this configuration. .. For example, a stopper mechanism for stopping the rotation of either the first carrier 52 or the first back solar wheel 54 may be separately provided in each mode. In particular, when the regulation mechanism 29 is not provided, the power transmission to the balance with arms 73 and 87 can be switched by the stopper mechanism.

(Second Embodiment)
Next, the second embodiment of the present invention will be described. This embodiment differs from the above-described embodiment in that, for example, a clutch mechanism is adopted for the first differential mechanism 242. FIG. 12 is a cross-sectional view of the first differential mechanism 242. In the following description, the same reference numerals will be given to the same configurations as those in the first embodiment described above, and the description thereof will be omitted.
In the movement 202 shown in FIG. 12, the first differential mechanism 242 mainly includes a front gear 210, a back gear 211, an intermediate gear 212, and a clutch plate (front clutch plate 213 and back clutch plate 214).

First, the intermediate gear 212 has an intermediate true 212a and a tooth portion 212b fixed to the intermediate true 212a.
The intermediate true 212a is configured to penetrate the front gear 210 and the back gear 211 in the front and back directions and to be rotatable with the front and back directions as the axial directions. Further, the intermediate true 212a is configured to be movable in the front and back directions together with the tooth portions 212b.
The tooth portion 212b meshes with the second wheel 25 described above.

The front gear 210 is arranged on the front side with respect to the tooth portion 212b of the intermediate gear 212. The front gear 210 is rotatably supported by the intermediate true 212a via a bearing 220. The front gear 210 is connected to the second fourth wheel 45 (for example, the second fourth wheel 45a) described above, and is connected to any gear of the second differential mechanism 43 (for example, the second back solar wheel 104). It is connected to the.
The back gear 211 is arranged on the back side with respect to the tooth portion 212b of the intermediate gear 212. The back gear 211 is rotatably supported by the intermediate true 212a via a bearing 221. The back gear 211 is connected to the above-mentioned first fourth wheel 44 (for example, the first fourth kana 44a) and is connected to any gear (for example, the second carrier 102) of the second differential mechanism 43. Has been done.

The front clutch plate 213 is fixed to the front side with respect to the tooth portion 212b in the intermediate true 212a. The front clutch plate 213 is configured to be in contact with and detached from the front gear 210 as the intermediate gear 212 moves in the front and back directions. That is, in a state where the front clutch plate 213 is in contact with the front gear 210, the rotation of the front gear 210 with respect to the intermediate gear 212 is regulated by the frictional force between the front clutch plate 213 and the front gear 210. As a result, the intermediate gear 212 and the front gear 210 are configured to rotate together. On the other hand, when the front clutch plate 213 is separated from the front gear 210, the rotation of the front gear 210 with respect to the intermediate gear 212 is allowed.

The back clutch plate 214 is fixed to the back side with respect to the tooth portion 212b in the intermediate true 212a. The back clutch plate 214 is configured to be detachable from the back gear 211 as the intermediate gear 212 moves in the front and back directions. The method of engaging the clutch plates 213 and 214 with the corresponding gears 210 and 211 is not limited to friction and can be changed as appropriate. For example, the clutch plates 213 and 214 and the corresponding gears 210 and 211 may be engaged with each other due to unevenness or the like.

The movement 202 of the present embodiment includes a switching lever 230 for operating the movement of the intermediate gear 212 in the front-back direction. The switching lever 230 is configured to be able to press the intermediate gear 212 in the front and back directions via, for example, the front end and the back end of the intermediate true 212a. The switching lever 230 can be operated by, for example, a winding stem 19.

FIG. 13 is a cross-sectional view corresponding to FIG. 12 for explaining the high vibration mode.
As shown in FIG. 13, in the movement 202 of the present embodiment, in the high vibration mode, the intermediate gear is interposed via the back clutch plate 214 in a state where the reciprocating rotation of the second balance sheet 87 is restricted by the regulation mechanism 29. The 212 and the back gear 211 are connected. As a result, the power of the barrel wheel 24 is transmitted to the first differential mechanism 242 via the second wheel 25. Then, in the first differential mechanism 242, the intermediate gear 212 and the back gear 211 rotate together, so that power is transmitted to the first fourth wheel 44 and the second differential mechanism 43. As a result, the display train wheel 30 operates and the clock 1 ticks. That is, in the high vibration mode, the first balance sheet 73 vibrates eight times, so that the second hand 6 (second wheel 130) moves one second in eight steps. In the high vibration mode, the intermediate gear 212 idles with respect to the front gear 210. Therefore, the power of the barrel wheel 24 is not transmitted to the second speed governor 28.

As shown in FIG. 12, in the low vibration mode, the intermediate gear 212 and the front gear 210 are connected via the front clutch plate 213 in a state where the reciprocating rotation of the first balance wheel 73 is restricted by the regulation mechanism 29. Make it a state. As a result, the intermediate gear 212 and the front gear 210 rotate together by the power transmitted to the first differential mechanism 242 via the second wheel 25. As a result, power is transmitted to the second fourth wheel 45 and the second differential mechanism 43, so that the clock 1 ticks. In the low vibration mode, the intermediate gear 212 idles with respect to the back gear 211. Therefore, the power of the barrel wheel 24 is not transmitted to the first speed governor 27.

Here, the difference in the frequencies of the first balance sheet 73 and the second balance sheet 87 can be canceled by, for example, changing the number of teeth of the front gear 210 and the back gear 211. Specifically, the number of teeth of the front gear 210 and the back gear 211 is set so that the gear ratio of the front gear 210 to the intermediate gear 212 is half of the gear ratio of the back gear 211 to the intermediate gear 212. As a result, the difference in frequency between the first balance sheet 73 and the second balance sheet 87 can be canceled by the first differential mechanism 242. That is, the rotation speed of the front gear 210 in the low vibration mode is the same as the rotation speed of the back gear 211 in the high vibration mode. As a result, in the low vibration mode, the second balance sheet 87 vibrates four times, so that the second hand 6 (second wheel 130) moves one second in four steps. However, the difference in frequency between the first balance sheet 73 and the second balance sheet 87 may be canceled by the fourth wheels 44 and 45 and the second differential mechanism 43, respectively.

As described above, in the present embodiment, by adopting the clutch mechanism in the first differential mechanism 242, the connection between the barrel wheel 24 and the balance wheels 73 and 87 can be easily switched according to each mode. In particular, in the present embodiment, by making the front gear 210 and the back gear 211 have different numbers of teeth, the difference in frequency between the first balance sheet 73 and the second balance sheet 87 can be canceled by the first differential mechanism 242. Thereby, the same action and effect as those of the above-described embodiment can be obtained. In this embodiment, it is not necessary to have the above-mentioned regulatory mechanism 29.

In the above-described embodiment, the configuration in which the clutch mechanism is adopted for the first differential mechanism 242 has been described, but the present invention is not limited to this configuration, and the second clutch mechanism having the same configuration as the first differential mechanism 242 described above is used. It may be adopted for the differential mechanism 43.

Further, as the clutch mechanism adopted in the second differential mechanism 243, the one-way clutch mechanism shown in FIG. 14 may be adopted. The second differential mechanism 243 shown in FIG. 14 mainly includes an intermediate gear 250, a front gear 251 and a back gear 252.

The intermediate gear 250 has an intermediate true 250a and a tooth portion 250b fixed to the intermediate true 250a.
The intermediate true 250a is configured to penetrate the front gear 210 and the back gear 211 in the front and back directions and to be rotatable with the front and back directions as the axial directions.
The tooth portion 250b meshes with the second wheel 130 of the display wheel train 30 described above.

The front gear 251 is supported by the intermediate true 250a via the front clutch 260. The front clutch 260 is, for example, a cam-type one-way clutch mechanism. That is, the front clutch 260 includes an outer ring (not shown) fixed to the front gear 251 and an inner ring fixed to the intermediate true 250a, a roller (not shown) interposed between the outer ring and the inner ring, and a roller. It mainly includes a urging member (not shown). The front clutch 260 connects the inner ring and the outer ring via rollers when the front gear 251 tries to rotate in one direction with respect to the intermediate gear 250. As a result, the intermediate gear 250 and the front gear 251 rotate together. On the other hand, when the front gear 251 tries to rotate in the other direction with respect to the intermediate gear 250, the connection state between the inner ring and the outer ring is released. This allows the table gear 251 to rotate in the other direction with respect to the intermediate gear 250.

The back gear 252 is supported by the intermediate true 250a via the back clutch 261. The back clutch 261 has the same configuration as the front clutch 260 described above. The back clutch 261 connects the inner ring and the outer ring via rollers when the back gear 252 tries to rotate in one direction with respect to the intermediate gear 250. As a result, the intermediate gear 250 and the back gear 252 rotate together. On the other hand, when the back gear 252 tries to rotate in the other direction with respect to the intermediate gear 250, the connection state between the inner ring and the outer ring is released. This allows the back gear 252 to rotate in the other direction with respect to the intermediate gear 250.

According to this configuration, when the front gear 251 rotates in one direction with the power transmitted from the first differential mechanism 42 in the high vibration mode, the front gear 251 and the intermediate gear 250 are connected to each other, and the front gear 251 and the intermediate gear 250 are connected. The intermediate gear 250 rotates together. As a result, the second wheel 130 rotates in the other direction. In the high vibration mode, the intermediate gear 250 rotates in one direction with respect to the back gear 252, so that the intermediate gear 250 idles with respect to the back gear 252. Therefore, the power of the barrel wheel 24 is not transmitted to the second speed governor 28.
On the other hand, in the low vibration mode, when the back gear 252 rotates in one direction with the power transmitted from the first differential mechanism 42, the back gear 252 and the intermediate gear 250 are connected, and the back gear 252 and the intermediate gear 250 are connected. Rotate together. As a result, the second wheel 130 rotates in the other direction. In the low vibration mode, the intermediate gear 250 rotates in one direction with respect to the front gear 251 so that the intermediate gear 250 idles with respect to the front gear 251. Therefore, the power of the barrel wheel 24 is not transmitted to the first speed governor 27.

The technical scope of the present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the spirit of the present invention.
For example, in the above-described embodiment, the case where a planetary mechanism or a clutch mechanism is adopted as the switching mechanism has been described, but the present invention is not limited to this configuration. The switching mechanism may be configured so as to be able to transmit the power output from the barrel wheel 24 to either the first balance sheet 73 or the second balance sheet 87. In this case, the switching mechanism may be configured to alternately mesh with the fourth wheels 44 and 45 according to each mode, for example.

In the above-described embodiment, the case where the frequency of the first balance sheet 73 is set to 4 Hz and the frequency of the second balance sheet 87 is set to 2 Hz has been described. It can be changed as appropriate.
In the above-described embodiment, the configuration having two balances 73 and 87 has been described, but the configuration is not limited to this configuration, and a configuration having three or more balances may be used.

In the above-described embodiment, the case where the rotation speed of the barrel wheel 24 in the low vibration mode is set to half the rotation speed of the barrel wheel 24 in the high vibration mode has been described, but the present invention is not limited to this configuration. That is, in each mode, the rotation speed of the barrel wheel 24 may be different.

In the above-described embodiment, the configuration using the first balance sheet 73 and the second balance sheet 87 having different frequencies has been described, but the configuration is not limited to this configuration. That is, the rotation speed of the barrel wheel 24 may be different between the first state (high vibration mode in the above-described embodiment) and the second state (low vibration mode in the above-described embodiment). For example, in the first balance sheet 73 and the second balance sheet 87, the rotation speed of the barrel wheel 24 may be different by making at least one of the swing angle, the frequency, and the torque different.

When the torques of the first balance sheet 73 and the second balance plate 87 are different, the influence on the disturbance can be surely suppressed when the balance plate having a large torque is operated, and the timekeeping accuracy can be improved. On the other hand, when a balance with a small torque is operated, it is possible to further improve energy saving in the barrel wheel.
Further, when the swing angles of the first balance sheet 73 and the second balance sheet 87 are different, the influence on the disturbance can be surely suppressed when the balance plate having a large swing angle is operated, and the timing accuracy can be improved. Can be done. On the other hand, when the balance with a small swing angle is operated, it is possible to further improve the energy saving in the barrel wheel.

In the first balance sheet 73 and the second balance sheet 87, the magnitude relation of the swing angle, the frequency and the torque can be changed as appropriate. In this case, for example, the swing angle, frequency, and torque of the first balance sheet 73 may be larger than those of the second balance sheet 87. Further, the value of any one of the swing angle, frequency and torque of the first balance sheet 73 may be larger than that of the second balance plate 87 (other values in the first balance plate 73 may be less than or equal to the second balance sheet 87). ).

Furthermore, even when using balances with the same performance (same swing angle, frequency and torque), by changing the gear ratio in the power transmission mechanism, the first and second states can be changed. It is possible to make the rotation speed of the barrel wheel 24 different. Even in such a configuration, it is possible to save energy in the barrel wheel and increase the operating time of the clock.

In the above-described embodiment, the configuration in which the power of the power transmission mechanism is transmitted to the same display wheel train 30 (second wheel 130) in the first state and the second state has been described, but the configuration is not limited to this configuration. For example, in the first state and the second state, the power transmission mechanism may be configured to transmit power to different display train wheels 30.

In addition, it is possible to replace the constituent elements in the above-described embodiments with well-known constituent elements as appropriate without departing from the spirit of the present invention, and the above-mentioned modifications may be appropriately combined.

1 ... Clock 2 ... Movement 3 ... Dial 6 ... Second hand (pointer)
24 ... Incense box car 26 ... Switching mechanism (power transmission mechanism)
29 ... Regulatory mechanism (power transmission mechanism)
42 ... First differential mechanism (transmission mechanism)
51 ... Table 1 Solar Vehicle (1st Solar Vehicle)
52 ... 1st carrier (carrier)
53 ... 1st planetary vehicle (planetary vehicle)
54 ... 1st back solar car (2nd sun car)
73 ... 1st balance 87 ... 2nd balance 130 ... Second wheel (pointer wheel)
202 ... Movement 242 ... First differential mechanism (transmission mechanism)

Claims (7)

The first and second balances that rotate back and forth,
The first state in which the power of the barrel wheel can be transmitted to the first balance wheel and the second state in which the power of the barrel wheel can be transmitted to the second balance wheel are switched, and the first state and the second state are described. A power transmission mechanism that rotates the barrel wheel at different rotation speeds,
A movement characterized in that a pointer is attached and a pointer wheel for which power is transmitted from the barrel wheel via the power transmission mechanism is provided. The first balance and the second balance have different frequencies from each other.
The power transmission mechanism rotates the barrel wheel according to the frequencies of the first and second balance wheels, and shifts the power output from the barrel wheel to shift the pointer wheel at a constant rotation speed. The movement according to claim 1, wherein the movement is rotated. The movement according to claim 1 or 2, wherein the first balance and the second balance have different torques from each other. The power transmission mechanism includes a transmission mechanism connected to the first balance and the second balance.
The transmission mechanism is
The first solar car and
The second solar wheel, which is arranged coaxially with the first solar wheel,
It has three gears, a carrier that supports the first solar wheel and the planetary wheel that meshes with the second solar wheel so as to rotate and revolve.
Of the three gears, the first gear transmits power to the first balance in the first state.
The second gear transmits power to the second balance in the second state.
The movement according to any one of claims 1 to 3, wherein the third gear is a movement in which power is transmitted from the barrel wheel. The movement according to claim 4, wherein the planetary vehicle rotates the first gear and the second gear at different rotation speeds according to the frequencies of the first balance and the second balance. The power transmission mechanism includes a regulation mechanism that regulates the reciprocating rotation of the second balance in the first state and regulates the reciprocating rotation of the first balance in the second state. The movement according to any one of claims 1 to 5, wherein the movement is characterized by. A timepiece comprising the movement according to any one of claims 1 to 6.

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