CH713779A2 - Movement and timepiece with two balance springs. - Google Patents

Abstract

The present invention relates to a movement and a timepiece intended to make possible the realization of energy savings. The movement comprises: a first sprung balance (73) and a second sprung balance (87) performing reciprocating rotational movements in a back and forth motion; a power transmission mechanism (26) switching between a high-oscillation mode in which the energy of a movement barrel (24) can be transmitted to the first balance-spring (73), and a low-oscillation mode in wherein the energy of the movement barrel (24) can be transmitted to the second balance spring (87), and rotating the motion barrel (24) at different rotational speeds in the high oscillation mode and the low oscillation mode ; and a seconds wheel (130) to which a second hand (6) is mounted, and to which energy is transmitted from the movement barrel (24) via the energy transmission mechanism.

Description

Description

BACKGROUND OF THE INVENTION FIELD OF THE INVENTION

The present invention relates to a movement and a timepiece.

PRIOR ART

[0002] As a mechanical timepiece movement, architectures having a plurality of regulators are known. For example, Japanese Patent No. 4,846,781 discloses an architecture in which each of the vortex cages in which regulators are respectively mounted operates alternately during the day and during the night.

In the architecture disclosed in Japanese Patent No. 4,846,781, however, the display of time is based on the rotation of a center mobile in gear engagement with a movement barrel, so that It is necessary to maintain the rotational speed of the movement barrel at a constant level independently of the cage to be employed. This means that in the architecture disclosed in Japanese Patent No. 4,846,781, the energy consumption of the motion barrel remains unchanged even if one passes from one cage to another. Therefore, there is still room for improvement compared to the architecture mentioned above in terms of energy saving at the barrel of the movement (that is to say the barrel spring) and to increase the time of operation of the timepiece (lifetime of the mainspring, also commonly called power reserve).

SUMMARY OF THE INVENTION

According to one aspect of the present invention, the patent application seeks to provide a movement and a timepiece making it possible to achieve energy savings.

In order to obtain the advantage mentioned above, a movement according to one embodiment of the present patent application comprises: a first balance-spring and a second balance-spiral rotating alternately according to a movement of va -and-forth; a power transmission mechanism switching between a first state in which the energy of a barrel of movement can be transmitted to the first sprung balance, and a second state in which the energy of the barrel of the movement can be transmitted to the second sprung balance, and rotating the barrel of the movement at different speeds of rotation depending on whether one is in the first state or the second state; and an indicator needle wheel to which an indicator needle is mounted, and to which energy is transmitted by the movement barrel via the energy transmission mechanism.

According to the present embodiment, the first sprung balance and the second sprung balance are kinematically connected to the cylinder of the movement via the energy transmission mechanism, so that, for example, by adjusting the quantity of the number of teeth of the energy transmission mechanism, it is possible to rotate the barrel of the movement at different speeds of rotation in the first state and in the second state. Therefore, it is possible to achieve energy savings for the barrel movement (barrel spring) and increase the operating time of the timepiece (the power reserve conferred by the mainspring).

[0007] Furthermore, according to the present embodiment, energy is transmitted by the barrel of the movement to the indicator needle wheel via the energy transmission mechanism, so that, unlike a configuration according to FIG. the indicator needle wheel is disposed between the movement barrel and the energy transmission mechanism, it is possible to dissociate the oscillation amplitudes (i.e. the maximum angle according to which turns the sprung balance during its movement back and forth), frequencies, couples, etc. the first sprung balance and the second sprung balance as required. Moreover, by dissociating oscillation amplitudes, etc. the first sprung balance and the second sprung balance, it is possible to change the rotational speed of the barrel of the movement according to the amplitude of oscillation, etc. the sprung balance when the sprung balance to be used is switched by changing the amplitude of oscillation etc. the first sprung balance relative to the second sprung balance. Thus, in the state where the timepiece is not worn, or in a state where it is worn but in which it can hardly be affected by disturbances, etc., the balance-spring whose amplitude of oscillation, etc. is smaller is operated, thanks to which it is possible to achieve energy savings for the movement barrel, and increase the operating time of the timepiece.

On the other hand, for example, when the timepiece is worn, in a state in which it is relatively exposed to disturbances, etc. (for example, during the practice of a sport), the sprung balance whose amplitude of oscillation, etc. is the largest is operated, thanks to which it is possible to remove the influence of such disturbances. Therefore, it is possible to achieve an improvement in the accuracy of the time measurement (i.e., minimizing gapping).

In the embodiment mentioned above, the first sprung balance may have a higher frequency than the second sprung balance, and the energy transmission mechanism can rotate the barrel of the movement according to the frequency of the first sprung balance and that of the second sprung balance, and vary the speed generated by the output energy of the movement barrel so as to rotate the indicator needle wheel at a fixed rotational speed.

According to the present embodiment, the energy transmission mechanism varies the energy of the movement cylinder depending on whether one is in the first state or the second state, while making it possible to do so. turn the same indicator needle wheel at a fixed rotational speed regardless of whether it is in the first state or the second state.

In addition, in the present embodiment, the frequency of the first sprung balance is chosen to be different from that of the second sprung balance, thanks to which it is possible to reliably suppress the influence of disturbances. and to realize an improvement in the accuracy of time measurement when the sprung balance having the higher frequency of the two is used.

On the other hand, when the sprung balance having the lowest frequency of the two is used, it is possible to achieve additional energy savings for the movement barrel (i.e. the barrel spring).

In the embodiment mentioned above, the first sprung balance and the second sprung balance can also have different pairs.

In the present embodiment, by choosing different pairs of the other for the first sprung balance and the second sprung balance, when the sprung balance having the highest torque is used, it It is possible to reliably suppress the influence of disturbances, thus making it possible to achieve an improvement in terms of time measurement accuracy.

On the other hand, when the sprung balance whose torque is the lower of the two functions, it is possible to achieve an additional improvement in terms of energy saving for the barrel movement (it is for the barrel spring).

In the embodiment mentioned above, the energy transmission mechanism may be equipped with a transmission mechanism connected to the first balance-spring and the second balance spring-spiral; the transmission mechanism may have three gear elements formed by a first sun gear, a second sun gear arranged coaxially with the first sun gear, and a support carriage carrying a gear wheel geared to the first sun gear. and the second sun wheel, so as to allow rotation and complete revolution; among the three gears mentioned above, the first gear is capable of transmitting energy to the first balance-spring in the first state, the second gear is capable of transmitting energy to the second balance-spring in the second state, and the gear is capable of receiving energy from the motion barrel.

According to the present embodiment, a satellite mechanism is adopted as the first transmission mechanism, whereby it is possible to easily switch between the first state and the second state. In other words, in the first state, the rotation of the second gear is stopped, the energy transmitted to the third gear being transmitted to the first gear via the satellite wheel, and then transmitted to the indicator handwheel. On the other hand, in the second state, the rotation of the first gear is stopped, the energy transmitted to the third gear being transmitted to the second gear via the satellite wheel, and then transmitted to the indicator hand wheel. .

In the embodiment above, the satellite wheel can rotate the first gear and the second gear at different rotational speeds depending on the frequencies of the first balance-spring and the second balance-spiral.

According to the present embodiment, by adjusting the number of teeth of the satellite wheel, it is possible to make the rotational speeds of the first gear and the second gear different from each other. Therefore, it is possible to cancel the frequency difference between the first balance-spring and the second balance-spring via the first transmission mechanism. Thus, regardless of whether one is in the first state or the second state, it is possible to operate the indicator needle wheel at a fixed rotational speed.

In the embodiment mentioned above, the energy transmission mechanism may be equipped with a regulation mechanism which stops the alternating rotation of the second balance spring when in the first state, and which stops the alternating rotation of the first sprung balance when one is in the second state.

According to the present embodiment, in the first state and in the second state, the alternating rotation of the sprung balance not contributing to the movement of the needle is stopped both in the first state and in the second state. thanks to which it is possible to maintain the spiral of the sprung balance not contributing to the needle movement in an extended or contracted state (it is possible to prevent it from reaching its nominal length at rest). Thus, after switching between the first state and the second state, it is possible for the sprung balance to quickly return to a normal operating mode.

[0022] A timepiece according to a preferred embodiment of the present patent application may be equipped with a movement according to the embodiment described above.

According to the present embodiment, it is possible to provide a superior timepiece in quality and reliability.

According to the teachings provided in this patent application, it is possible to achieve energy savings.

BRIEF DESCRIPTION OF THE DRAWINGS

[0025]

Fig. 1 is an external view of a timepiece according to a first embodiment.

Fig. 2 is a plan view, seen from the bottom, of the main part of a movement according to the first embodiment.

Fig. 3 is a diagram illustrating the movement according to the first embodiment.

Fig. 4 is a perspective view of the main part of the movement according to the first embodiment.

Fig. 5 is an exploded perspective view of a first differential mechanism.

Fig. 6 is a sectional view of the first differential mechanism.

Fig. 7 is an exploded exploded perspective view of a second differential mechanism.

Fig. 8 is a sectional view of the second differential mechanism.

Fig. 9 is a plan view illustrating a low oscillation mode corresponding to FIG. 2.

Fig. 10 is a diagram illustrating a movement according to a variant of the first embodiment.

Fig. 11 is a diagram illustrating a movement according to a variant of the first embodiment.

Fig. 12 is a sectional view of a first differential mechanism in a movement according to a second embodiment

Fig. 13 is a sectional view to illustrate a high oscillation mode corresponding to FIG. 12.

Fig. 14 is a sectional view of a second differential movement having another architecture according to this embodiment.

DETAILED DESCRIPTION OF THE INVENTION

In the following, embodiments of the present invention will be described with reference to the drawings. First embodiment

Timepiece [0027] FIG. 1 is an external view of a timepiece 1. In the following drawings, to facilitate understanding of the invention, some components of the timepiece will not be voluntarily represented and simplified in some cases.

As shown in FIG. 1, the timepiece 1 according to the present embodiment is made by inserting a movement 2, a dial 3, various indicator hands 4 to 6, etc. in a housing 7.

The housing 7 of the timepiece is equipped with a middle part 11, a housing cover (that is to say a bottom, not shown), and a protective glass (ice). 15 is disposed at 3 o'clock (on the right side of Fig. 1) of the side surface of the middle part 11. The ring 15 is used to actuate the movement 2 from outside the middle part 11 of the housing. The ring 15 is fixed to a winding stem 19 inserted into the middle part 11.

Movement [0030] In motion 2, a plurality of gears, etc. are rotatably mounted on a plate 21 constituting the base plate of the movement 2. The winding stem mentioned above 19 is inserted in the plate 21. The winding stem 19 is used when it is desired to correct the date and the hour. The winding stem 19 is rotatably mounted about its axis, and is movable in the axial direction. In the following description, reference is made to the "back side" of movement 2 to designate the side of the protective glass 12 (i.e., the dial side 3) of the timepiece case 7 relative to to the main plate 21, and reference is made to the "front side" of the movement 2 to designate the side of the housing cover (i.e. the opposite side to that of the dial 3, which is usually referred to as the "Bottom side"). The axial direction of each of the gears described below extends from the front to the rear of the movement 2.

FIG. 2 is a plan view from the rear (dial side) of the main part of the movement 2. FIG. 3 is a diagram of the movement 2. The numbers in parentheses of FIG. 3 indicate the ratio of the operating speed in the low oscillation mode to that of the high oscillation mode, in the case where the operating speed of the high oscillation mode described below is conventionally chosen to be equal to 1.

As shown in FIGS. 2 and 3, a movement cylinder 24, a center mobile 25, a switching mechanism (energy transmission mechanism) 26, a first exhaust / regulator 27, a second exhaust / regulator 28, a control mechanism (mechanism energy transmission) 29, a display gear train 30, etc. are mounted on the plate 21 of the movement 2 (see Fig. 1).

The barrel of the movement 24 contains a mainspring (that is to say the mainspring, not shown) serving as a power supply source for the timepiece 1. The barrel spring is wound by, for example, the rotation of the winding rod 19. The barrel of the movement 24 is rotated by the rotational force (return force) when the mainspring is raised (rewound).

A center pinion 25a of the center wheel 25 meshes with the barrel of the movement 24. A center wheel 25b of the center wheel 25 is connected to the switching mechanism 26. Switching mechanism [0035] FIG. 4 is a perspective view of the main part of the movement 2.

As shown in FIG. 4, the switching mechanism 26 is equipped with a first differential mechanism (transmission mechanism) 42, a second differential mechanism 43, a second mobile 44 of a first kinematic chain, a second mobile 45 of a second kinematic chain, etc.

The first differential mechanism 42 transmits the energy transmitted from the barrel of the movement 24 via the mobile center 25 is the first of the second mobile 44 or the second of the second mobile 45.

FIG. 5 is an exploded perspective view of the first differential mechanism 42. FIG. 6 is a sectional view of the first differential mechanism 42.

As shown in FIGS. 5 and 6, the first differential mechanism 42 has a first front sun gear (first sun gear constituting the third gear) 51, a first support carriage (constituting the first gear) 52, and a first planet wheel 53 and a first wheel rear solar panel (second sun gear, constituting the second gear) 54. The first differential mechanism 42, the first front sun gear 51, the first support carriage 52, and the first sun gear 54 are arranged coaxially with each other. others, their axial direction extending from the front to the back, and they are constituted so as to allow relative rotation with respect to each other.

First, the first support carriage 52 has a shaft 52a, and a body 52b attached to the shaft 52a.

The shaft 52a extends both through the first sun gear 51 and the first sun gear 54 in the front-rear direction.

The body of the support carriage 52b is arranged between the first sun gear 51 and the first sun gear 54 in the front-rear direction. The body of the support carriage 52b has a hub 61 fixed to the shaft of the first support carriage 52a, a serge 62 surmounting the hub 61, and arms 63 connecting the hub 61 to the serge 62.

On the outer peripheral surface of the serge 62 is formed a gear teeth 52c of the first support carriage.

On the first sun gear 51 are respectively arranged a first sun gear 51b and a front sun gear 51c at both front and rear ends of a first sun shaft 51a before.

The first sun shaft 51a before has a tubular configuration. The front end (bottom side) of the shaft of the first support carriage 52a is inserted into the first sun shaft 51a via a bearing 64. Therefore, the first sun front wheel 51 is rotatably mounted relative to the first support carriage 52 .

The first sun gear 51b is located at the front end (bottom side) of the first sun shaft before 51a. The first sun gear 51b meshes with the center wheel 25b of the center wheel 25.

In the first sun gear 54 are respectively arranged a first sun gear 54b and a first sun gear gear 54c at the two front and rear ends of a first sun shaft 54a.

The first solar rear shaft 54a has a tubular configuration. The rear end (dial side) of the shaft of the first support carriage 52a is inserted into the first rear sun shaft 54a via a bearing 65. Therefore, the first sun rear wheel 54 is rotatably mounted relative to the first support carriage 52 .

The first satellite wheel 53 is rotatably mounted on an arm 63a chosen from the set of arms (radial portions) 63 of the first support carriage mentioned above 52 (that is to say the body of the support carriage 52b). . In the first satellite wheel 53 are respectively arranged a first planet gear 53b and a first gear gear 53c at both the front and rear ends of a first planet shaft 53a.

The first satellite shaft 53a extends through an arm 63a in the front-rear direction. The first satellite shaft 53a is rotatably mounted on an arm 63a via a bearing 66.

The first planet gear 53b is arranged at the front end (the part located on the bottom side relative to the body of the support carriage 52b) of the first satellite shaft 53a. The first planet gear 53b meshes with the first sun gear 51c mentioned above.

The first gear gear 53c is arranged at the rear end (the portion located on the dial side relative to the body of the support carriage 52b) of the first satellite shaft 53a. The first gear gear 53c meshes with the first sun gear 54b mentioned above. Thus, the first satellite wheel 53 of the present embodiment performs complete revolutions around the first sun shafts 51a and 54a during the rotation of the first carriage 52, and rotates relative to the first carriage 52 via the rotation of the wheels. solar cells 51 and 54.

Here, according to the present embodiment, the number of teeth of the first differential mechanism 42 is defined as indicated in Table 1.

Table 1

In this case, as shown in Table 2, when the first support carriage 52 is stationary, the transmission gear ratio (rate of increase in speed) between the first sun wheel 54 and the first sun gear before 51 is "3." On the other hand, when the first sun rear wheel 54 is stationary, the transmission gear ratio (rate of increase in speed) between the first support carriage 52 and the first sun gear before 51 is "1.5." In other words, the transmission gear ratio between the first sun gear 54 and the first sun gear 51 when the first support carriage 52 is stationary is equal to twice that between the first truck support 52 and the first sun gear 51 when the first sun gear 54 is stationary.

[0056] Table 2

As illustrated in FIG. 4, a first second gear 44a of the first of the second mobiles 44 meshes with the gear teeth of the first support carriage 52c mentioned above. A first second wheel 44b of the first of the second mobiles 44 is kinematically connected to the first regulator exhaust 27.

A second second gear 45a of the second of the second movable 45 meshes with the first rear sun gear toothing 54c mentioned above. A second second wheel 45b of the second of the second mobiles 45 is kinematically connected to the second regulator escapement 28. In the present embodiment, the second gears 44a and 45a of the second mobiles 44 and 45, and its second wheels 44b and 45b respectively possess the same number of teeth.

As illustrated in FIGS. 2 and 4, the first regulator escapement 27 comprises a first escape wheel 71, a first anchor 72, and a first spiral balance 73.

The first exhaust movable 71 has a first escape wheel 71a and a first exhaust pinion 71b. The first exhaust pinion 71b meshes with the first second wheel 44b mentioned above of the first of the second mobiles 44. In other words, the first mobile escapement 71 is rotated following that of the first second mobile 44.

The first anchor 72 is able to perform an alternating rotation in reciprocating movements, its axial direction extending from the front to the rear. The first anchor 72 is equipped with a pair of vanes 74a and 74b. In response to the alternating rotation of the first anchor 72, the vanes 74a and 74b are alternately engaged with the first escape wheel 71a of the first escape mobile 71. When a pallet of the pair of vanes 74a and 74b is engaged with the first escape wheel 71a, the first exhaust movable 71 temporarily stops its rotation. When the pair of vanes 74a and 74b are disengaged from the first escape wheel 71a, the first escape wheel 71 rotates. These operations are repeated successively, so that the first mobile exhaust 71 rotates intermittently. And through the intermittent rotation of the first exhaust movable 71, the aforementioned switching mechanism 26 also operates intermittently.

The first sprung balance 73 regulates the speed of the first exhaust movable 71 (that is to say, makes the first exhaust movable 71 is rotated at a fixed speed). The first sprung balance 73 has mainly a first balance shaft 81, a first balance wheel 82, and a first balance spring 83.

The first balance shaft 81 performs rotary movements in the normal direction and the opposite direction to a fixed frequency determined by the energy transmitted by the first balance spring 83, the axial direction of which extends from the front to the right. 'back. In synchronization with the alternating rotation of the first balance-spring 73, the first balance shaft 81 repeats an engagement movement with the pallet carrier (not shown) of the first anchor 72 followed by a release thereof. Therefore, the first anchor 72 rotates alternately, through which the vanes 74a and 74b repeat a movement of engagement with the first movable 71 exhaust and clearance relative thereto.

The first balance wheel 82 is fixed to the first balance shaft 81 by driving or the like.

The first hairspring 83 is a spiral spring flat configured spiral, as can be seen in the plan view in the front-rear direction. The inner end of the first balance spring 83 is connected to the first balance shaft 81, and its outer end is connected to a peak (not shown).

The second escapement / regulator 28 has a second escapement mobile 85, a second anchor 86, and a second balance spring 87. The second regulator exhaust 28 is configured according to an architecture equivalent to that of the first exhaust / regulator 27 so that the description of some of its parts will not be systematically repeated as needed.

The second mobile exhaust 85 has a second escape wheel 85a and a second exhaust pinion 85b. The second exhaust pinion 85a meshes with the second wheel 45b of the second second mobile 45 mentioned above. In other words, the second escapement mobile 85 is rotated following that of the second second mobile 45. The number of teeth of the second exhaust pinion 85b is configured to be twice that of the first exhaust pinion 71b of the first escape mobile 71.

The second anchor 86 is equipped with a pair of vanes 91a and 91b. In response to the alternating rotation of the second anchor 86, the vanes 91a and 91b alternately engage with the second escape wheel 85a of the second escapement 85, and thus rotate intermittently. And, through the intermittent rotational movement of the second exhaust movable 71, the aforementioned switching mechanism 26 also operates intermittently.

The second sprung balance 87 regulates the speed of the second exhaust movable 85 (that is to say, makes the second movable exhaust 85 is rotated at a fixed speed). The second balance spring 87 has mainly a second balance shaft 92, a second balance wheel 93, and a second balance spring 94.

Here, the frequency of the first sprung balance 73 and that of the second sprung balance 87 are different from each other. In the present embodiment, the frequency of the first sprung balance 73 is set at 4 Hz (8 oscillations per second). The frequency of the second balance-spring 87 is defined as being equal to half the frequency of the first sprung balance 73 (2 Hz, or 4 oscillations per second). The frequency F of the sprung balance 73, 87 is expressed by the following equation (1), in which "I" represents the moment of inertia of the sprung balance, and "K" represents the spring constant of the spiral spring.

[0071]

As seen in equation (1), the frequency F of the sprung balance 73, 87 varies in accordance with the moment of inertia "I" of the sprung balance 73, 87 and the restoring constant "K Spiral 83, 94. More specifically, the smaller the moment of inertia "I", the higher the frequency F, and the higher the return weight K, the higher the frequency F is. In the present embodiment, the moment of inertia "I" of the first balance-spring 73 (the outer diameter of the first balance wheel 82) is smaller than the moment of inertia "I" of the second balance-spring. 87 (the outer diameter of the second balance wheel 93), because of which the frequencies F of the balance springs 73, 87 differ. The moment of inertia "I" can be adjusted by changing the material, etc. of the balance wheel 82, 93.

In addition, the frequency of the sprung balance 73 and that of the sprung balance 87 can be made different from each other by taking a restoring constant "K" of the spiral 83 different from that of the hairspring 94. Moreover, the frequency F of the sprung balance 73 and that of the sprung balance 87 can be changed as necessary as long as they remain different from each other.

FIG. 7 is an exploded perspective view of the second differential mechanism 43. FIG. 8 is a sectional view of the second differential mechanism 43.

As shown in FIGS. 7 and 8, the second differential mechanism 43 transmits the energy of the first differential mechanism 42 to the display train 30. More specifically, the second differential mechanism 43 has a second sun wheel 101, a second support carriage 102, a second wheel 103, and a second sun gear 104. The second differential mechanism 43, the second sun gear 101, the second support carriage 102, and the second sun gear 104 are arranged coaxially relative to each other, their axial direction extending from front to back. At the same time, they can rotate relative to each other. In the following, the description of the configuration elements that are identical to those of the first differential mechanism 42 will not be repeated in detail.

First, the second support carriage 102 has a second shaft 102a, and a support carriage body 102b attached to the second shaft 102a.

The second shaft 102a extends respectively through the second front sun gear 101 and the second sun rear wheel 104 from front to rear.

The body of the support carriage 102b is arranged between the second sun gear 101 and the second sun rear wheel 104. The body of the support carriage 102b has a hub 110 fixed to the second shaft 102a of the support carriage, a serge 111 surmounting the hub 110, and a set of arms 112 connecting the hub 110 to the serge 111.

At the outer peripheral surface of the serge 111 is formed a second gear teeth 102c. The second gear gear 102c is engaged with the first gear gear 52c of the first carrier carriage 52 mentioned above.

In the second sun gear 101 before, a second sun front gear 101b and a second sun gear gear before 101c are respectively arranged at both ends at the front and rear of a second sun shaft before 101a. .

The second sun shaft before 101a has a tubular configuration. The rear end (dial side) of the second shaft 102a of the second support carriage mentioned above is inserted into the second sun shaft before 101a via a bearing 115.

In the second rear sun gear 104, a second rear sun gear 104b and a second sun gear gear 104c are respectively arranged at the two front and rear ends of a second rear sun shaft 104a.

The second rear sun shaft 104a has a tubular configuration. The rear end (dial side) of the second shaft 102a of the second support carriage mentioned above is inserted into the second rear sun shaft 104a via a bearing 116.

The second rear sun gear gear 104c is engaged with the first rear sun gear gear 54c mentioned above.

The second satellite wheel 103 is rotatably mounted on an arm 112a selected from the set of arms (radial portions) 112 of the second support carriage 102 (that is to say the body of the support carriage 102b) mentioned above. . In the second satellite wheel 103, a second planet gear 103b and a second gear 103c are arranged at both the front and rear ends of a second planet shaft 103a.

The second satellite shaft 103a extends through an arm 112a in the front-to-back direction. The second satellite shaft 103a is rotatably mounted on an arm 112a via a bearing 117.

The second planet pinion 103b is arranged at the front end of the second satellite shaft 103a (the bottom side portion relative to the body of the support carriage 102b). The second planet gear 103b meshes with the second sun gear before 101b mentioned above.

The second gear gear 103c is arranged at the rear end of the second planet shaft 103a (the portion located on the dial side relative to the body of the support carriage 102b). The second gear gear 103c meshes with the second sun gear 104b mentioned above. Thus, the second satellite wheel 103 of the present embodiment rotates around the second sun shaft 101a, 104a in response to a rotation of the second carriage 102, and rotates relative to the second carriage 102 as the sun wheels 101 and 104 rotate.

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

[0089] Table 3

In this case, as shown in Table 4 below, when the second support carriage 102 is stationary, the transmission gear ratio (rate of reduction of speed) between the second sun wheel 101 and the second before rear sun wheel 104 is "0.5." On the other hand, when the second sun rear wheel 104 is stationary, the transmission gear ratio (speed reduction ratio) between the second sun wheel 101 and the second truck support 102 is also "0.5." In other words, the transmission gear ratio between the second front sun gear 101 and the second sun rear wheel 104 is set to be equal to that between the second sun wheel 101 and the second support cart 102.

[0091] Table 4

As shown in FIG. 2, the regulating mechanism 29 alternately stops the alternating rotation of the sprung balance 73, 87. More specifically, the regulating mechanism 29 is equipped with a rotation rod 120, a rotation lever 121, a first brake shoe 122, and a second brake shoe 123.

The rotation shaft 120 extends from the front to the back. The rotation rod 120 is rotatable about the axial direction extending in the forward-back direction together, for example, with the rotational actuation of the winding stem 19 about its axis.

The rotation lever 121 is fixed to the rotation rod 120. The rotation lever 121 extends on either side of the rotation rod 120 in the direction orthogonal to that extending from the 'front to back.

The first brake shoe 122 is connected to a first end of the rotation lever 121. The second brake shoe 123 is connected to a second end of the rotation lever 121 (the end opposite the first end of the lever of rotation). rotation 121, the rotation rod 120 being interposed between these two ends). When the rotation rod 120 is rotated (rotational actuation of the winding rod 19), the first brake shoe 122 alternately comes into contact with the first balance-spring 73 and then moves away from it (first balance wheel 82) ; similarly, the second brake shoe 123 alternately comes into contact with the second balance spring 87 (second balance wheel 93) and moves away from it. More specifically, when the first brake shoe 122 and the first rocker wheel 82 are brought into mutual contact, the second brake shoe 123 and the second rocker wheel 93 are spaced from each other. Therefore, the rotation of the first sprung balance 73 is stopped, while the rotation of the second sprung balance 87 is permitted. When the first brake shoe 122 and the first rocker wheel 82 are spaced from each other, the second brake shoe 123 and the second rocker wheel 93 are brought into mutual contact. Therefore, the rotation of the first sprung balance 73 is permitted, while the rotation of the second sprung balance 87 is stopped.

The regulation mechanism 29 allows modifications as needed as its configuration ensures that the rotation of the balance springs 73 and 87 is alternately stopped. For example, in the present embodiment, the brake shoes 122 and 123 are integrally arranged with respect to the rotation lever 121. This, however, such a configuration should not be interpreted restrictively. The brake shoes 122 and 123 may be arranged independently of one another.

The method of regulating the sprung balance 73, 87 by the brake shoe 122, 123 is not limited to the frictional force between the sprung balance 73, 87 and the brake shoe 122, 123 as shown in FIG. 'illustrated, but allows to consider modifications as needed. For example, an architecture may be adopted in which the sprung balance 73, 87 and the corresponding brake shoe 122, 123 are brought into engagement with each other by means of protrusions and recesses, or the like.

While the present embodiment described above adopts an architecture in which the brake shoe 122, 123 is brought into contact with the balance wheel 82,93 and away from it, such a configuration should not be interpreted restrictively either. It is also possible to adopt an architecture according to which the brake shoe comes into contact and moves away from a part other than the rocker wheel 82, 93 (for example, the balance shaft 81, 92) as long as the rotations of the brake shoes balance-springs 73, 87 are alternately stopped.

As shown in FIG. 4, the display platen wheel 30 has a second wheel 130, a minute wheel (not shown), and an hour wheel (not shown).

The seconds wheel 130 meshes with the second front sun gear 101c of the second front sun gear 101. The seconds hand 6 mentioned above is mounted at the seconds wheel 130. The number of teeth of the seconds wheel 130 is set to rotate in 60 seconds.

The minute wheel meshes, for example, with the wheel of seconds. The minute hand 5 is mounted to the minute wheel. The number of teeth of the minute wheel is adjusted so that it rotates in sixty minutes.

The hour wheel meshes, for example, with the minute wheel. The hour hand 4 is mounted at the hour wheel. The number of teeth of the hour wheel is set so that it rotates 12 hours.

Operation [0103] In what follows, we will describe the operation of the timepiece.

The timepiece 1 of the present embodiment can be switched between two modes of operation, namely a high oscillation mode (first state), in which the rotation of the barrel of the movement 24 is controlled by the first exhaust regulator 27, and a low oscillation mode (second state) in which the rotation of the barrel of the movement 24 is controlled by the second regulator escapement 28. As illustrated in FIG. 2, the switching between the modes is effected by the actuation of the regulating mechanism 29, for example, by the actuation in rotation of the winding rod 19 described above. In other words, the high-oscillation mode corresponds to a state in which the first brake shoe 122 and the first rocker wheel 82 are spaced from each other, and in which the rotation of the first spiral balance 73 is thus permitted. The low oscillation mode is a state in which the second brake shoe 123 and the second balance wheel 93 are spaced from each other, and wherein the rotation of the second balance spring 87 is thus permitted.

High Oscillation Mode [0105] First, the high oscillation mode is described.

As illustrated in FIGS. 2 and 3, when the cylinder of the movement 24 is rotated by the energy of the mainspring, the center wheel 25 is rotated in turn. The rotational force of the center wheel 25 is transmitted to the first front sun gear 51 of the first differential mechanism 42, so that the first sun gear 51 also rotates.

Here, in the high-oscillation mode, the rotation of the second balance spring 87 is stopped, so that the operation of the second regulator exhaust 28, the second of the second mobile 45, and the first sun gear 54 is put to rest. Thus, in the high oscillation mode, the energy of the movement barrel 24 is not transmitted to the second balance-spring 87, but is transmitted to the first balance-spring 73. More specifically, in the high-oscillation mode, when the first sunwheel 51 rotates, the first sun gear 53 rotates by rotating about the first sun shaft 51a, 54a, and at the same time the first sunk carriage 52 rotates. When the first support carriage 52 rotates, the first of the second mobiles 44 is rotated, whereby the rotational force is transmitted to the first escape wheel 71.

By the action of the rotation of the first escapement 71, the second anchor 72 rotates, thereby transmitting the rotational force of the first escapement 71 to the first balance-spring 73. Due to the force of rotation of the first escapement mobile 71 and the restoring force exerted by the spring of the first balance spring 83, the first balance-spring 73 rotates alternately around the first balance shaft 81 at a fixed frequency (4 Hz). Due to the alternating rotation of the first balance-spring 73, the vanes 74a and 74b alternately engage with the first escape wheel 71a and disengage. Consequently, the first escapement mobile 71 rotates intermittently, while the first of the second mobiles 44 and the first differential mechanism 42 (the first front sun wheel 51, the first support carriage 52, and the first satellite wheel 53) operate. intermittently.

On the other hand, in the first differential mechanism 42, the rotational force of the first support carriage 52 is transmitted to the second differential mechanism 43 via the second support carriage 102. At the same time, the first rear sun gear 54 is at rest, so that the second rear sun wheel 104 is kept at rest. Therefore, in the high-oscillation mode, when the second support carriage 102 rotates, the second planet wheel 103 rotates by rotating around the second sun shaft 101a, 104a. Therefore, the second sunwheel 101 rotates at a rotation speed equal to half that of the second support carriage 102 (see Table 4). The rotational force of the second front sun gear 101 is transmitted to the display gear train 30, through which the timepiece 1 scans and displays the time. In other words, in the high oscillation mode, the first balance-spring 73 makes 8 oscillations, through which the seconds hand 6 (seconds wheel 130) is made to perform a needle movement in 8 steps each second.

Low Oscillation Mode [0110] In what follows, the low oscillation mode will be described. Fig. 9 is a plan view corresponding to FIG. 2 illustrating the low oscillation mode. In what follows, the description of the same principles of operation as those of the high oscillation mode will not be repeated.

As shown in FIGS. 3 and 9, in the low oscillation mode, the rotation of the first sprung balance 73 is stopped, so that the first regulator exhaust 27, the first of the second mobiles 44, and the first support carriage 52 are at rest. Thus, in the low oscillation mode, the energy of the movement barrel 24 is not transmitted to the first balance-spring 73 but is transmitted to the second balance-spring 87. More specifically, in the low-oscillation mode, when the first sunwheel 51 rotates in response to the rotation of the center wheel 25, the first planet wheel 53 rotates, driving the first sun wheel 54. Therefore, the second second wheel 45 rotates, and thus the rotational force is transmitted to the second mobile 85 exhaust.

Following the rotation of the second mobile 85 exhaust, the second anchor 86 rotates, which allows to transmit the rotational force of the second movable exhaust 85 to the second sprung balance 87. Due to the strength of rotation of the second escapement 85 and the return force of the spring of the second balance spring 94, the second balance-spring 87 rotates alternately around the second balance shaft 92 at a fixed frequency (2 Hz). By means of the alternating rotation of the second balance spring 87, the vanes 91a and 91b alternately engage with the second escape wheel 85a and disengage from the latter. Therefore, the second escapement wheel 85 rotates intermittently, and the second of the second movable 45, the first differential mechanism 42 (the first sun gear 51, the first sun gear 53, and the first sun gear 54) operate also intermittently.

Here, the frequency of the second balance-spring 87 is determined to be equal to half that of the first balance-spring 73. In addition, as indicated in Table 2, in the first differential mechanism 42, the ratio of transmission gear between the first front sun gear 51 and the first sun gear 54 when the first support carriage 52 is fixed, and that between the first sun gear 51 and the first carriage 52 when the first sun gear 54 is fixed are each set by convention to be equal to "1." Thus, the rotational speed of the motion barrel 24 in the low oscillation mode is half that in the high oscillation mode.

On the other hand, as shown in Table 2, in the first differential mechanism 42, the transmission gear ratio between the first sun gear 54 and the first sun gear 51, when the first carriage 52 is fixed, is equal to twice the ratio of transmission gear between the first support carriage 52 and the first sun gear 51 when the first sun gear 54 is fixed. Thus, the rotational speed of the first sun gear 54 in the low oscillation mode is the same as that of the first support carriage 52 in the high oscillation mode. Therefore, the frequency difference of the balance wheels 73 and 87 in the high oscillation mode and the low oscillation mode is canceled by the first differential mechanism 42, whereby, in the low oscillation mode and the high oscillation mode, the output from the first differential mechanism 42 to the second differential mechanism 43 is equivalent.

In addition, in the first differential mechanism 42, the rotational force of the first sun gear 54 is transmitted to the second differential mechanism 43 via the second sun wheel 104. At this time, the first support carriage 52 is at rest, so that the second support carriage 102 is kept at rest. Therefore, in the low oscillation mode, when the second sun wheel 104 rotates, the second planet wheel 103 rotates. Thus, the second sunwheel 101 rotates at a rotation speed equal to half that of the second sunwheel 104 (see Table 4). Therefore, in both the low oscillation mode and the high oscillation mode, the rotation speed of the second front sun gear 101 is the same. And the rotational force of the second front sun gear 101 is transmitted to the display gear train 30, through which the timepiece 1 displays and times the time. In other words, in the low oscillation mode, the second balance spring 87 performs 4 oscillations, which cause a movement of the seconds hand 6 (seconds wheel 130) in 4 steps per second.

In this way, in the present embodiment, the first differential mechanism 42 rotates the barrel of the movement 24 at different speeds of rotation (rpm), and the energy of the barrel of the movement 24 is transmitted to the gear wheel. display 30 via the first differential mechanism 42.

In this architecture, unlike a configuration in which the display plate wheel 30 is interposed between the barrel of the movement 24 and the first differential mechanism 42, when the balance springs 73 and 87 to be actuated are switched, it is possible to switch the speed of rotation of the barrel of the movement 24 according to the frequency, etc. Thus, for example, in the state where the timepiece 1 is worn, and in particular in a situation in which disturbances can relatively easily occur (for example, during the practice of the spring balance 73, 87). of a sport), the timepiece is set in the high-oscillation mode, through which it is possible to suppress the influence of disturbances. Therefore, it is possible to achieve an improvement in the accuracy of time measurement.

On the other hand, in an unworn state of the timepiece 1, or in a state in which the timepiece is worn but in which it is relatively unlikely to be affected by disturbances , the timepiece is set in the low oscillation mode, through which it is possible to save energy for the barrel of the movement 24 (that is to say the mainspring), making thus possible an increase in the time of operation of the timepiece 1 without the need for reassembly (that is to say the power reserve of the barrel). In addition, it is possible to eliminate unwanted wear of all gear elements.

In the present embodiment, the switching mechanism 26 rotates the barrel of the movement 24 according to the frequency of the first balance-spring 73 and the second balance-spring 87, and, at the same time, the energy supplied. by the barrel of the movement 24 is adjusted in terms of speed so as to ensure that the seconds wheel 130 rotates at a fixed rotational speed.

In this architecture, in each of the modes, it is possible to rotate the same seconds wheel 130 at a fixed rotational speed. In addition, the frequency of the first balance-spring 73 is determined to be higher than that of the second balance-spring 87; thus, thanks to the latter, it is possible to reliably remove, in the high-oscillation mode, the influence of any disturbance, which allows an improvement in terms of accuracy of time measurement.

On the other hand, the frequency of the second balance spring 87 is determined to be lower than that of the first balance-spring 73; thus thanks to the latter, it is possible to achieve, in the low oscillation mode, additional energy savings for the barrel of the movement 24 (barrel spring), and to reduce the wear of each of the gear elements. .

In the present embodiment, the first differential mechanism 42 adopts a planetary mechanism, that is to say using solar wheels and satellites.

In the architecture corresponding to this embodiment, the first differential mechanism 42 adopts a planetary mechanism by means of which the switching between the high oscillation mode and the low oscillation mode can be easily performed. In other words, in the high-oscillation mode, the rotation of the second balance-spring 87 is stopped, so that the rotation of the first sun-wheel 54 is at rest. Thus, the energy transmitted to the first front sun gear 51 is transmitted to the first support carriage 52 via the first planet wheel 53, and is then transmitted to the display train 30. On the other hand, in the low oscillation mode the rotation of the first balance-spring 73 is stopped, so that the rotation of the first support carriage 52 is at rest. Thus, the energy transmitted to the first front sun gear 51 is transmitted to the first sun gear 54 via the first sun gear 53, and is then transmitted to the display gear train 30.

In particular, in the present embodiment, by adjusting the number of teeth of the first planet wheel 53, it is possible to make the speed of rotation of the first support carriage 52 different from that of the first rear sun wheel 54 Therefore, it is possible to cancel the difference in frequency between the first balance-spring 73 and the second balance-spring 87 by means of the first differential mechanism 42. Thus, independently of the fact that the timepiece is in in the high oscillation mode or in the low oscillation mode, it is possible to operate the display train 30 at a fixed rotational speed.

In the present embodiment, there is provided a regulating mechanism 29 which stops the alternating rotation of the second balance spring 87 in the high-oscillation mode, and which stops the alternating rotation of the first balance-spring 73 in the mode. at low oscillation.

In this configuration, in each mode, the alternating rotation of the sprung balance 73, 87 does not contribute to the needle movement is stopped, thanks to which it is possible to maintain the spiral 83, 94 of the balance- spiral 73, 87 not contributing to the needle movement in the extended or contracted state (it is possible to prevent it from reaching its nominal length, that is to say normal at rest). Thus, after a mode switch, it is possible for the sprung balance 73, 87 to quickly return to normal operation.

The timepiece 1 of the present embodiment is equipped with the movement 2 mentioned above, so that it is possible to provide a timepiece 1 of high quality and better reliability.

Variations of implementation [0128] In the following, we will describe implementation variants for the first embodiment described above.

While in the embodiment described above the first differential mechanism 42 and the second differential mechanism 43 are directly connected to each other, this should not be interpreted restrictively. For example, as shown in FIG. 10, the first differential mechanism 42 and the second differential mechanism 43 can be kinematically connected to one another via the second mobiles 44, 45.

Furthermore, while in the embodiment described above the first differential mechanism 42 is kinematically connected to the second mobile 44, 45 and the escapement regulators 27, 28, this should not be interpreted restrictively either. For example, as shown in FIG. 11.1e first differential mechanism 42 can be kinematically connected to the second mobiles 44, 45 and the control exhausts 27, 28 via the second differential mechanism 43.

Similarly, while in the embodiment described above the frequency difference between the first sprung balance 73 and the second sprung balance 87 is canceled by the first differential mechanism 42, this should not be interpreted limitatively no more. For example, the difference in frequency between the first sprung balance 73 and the second sprung balance 87 can be canceled by adjusting the number of teeth of the gear element (for example that of the second mobiles 44, 45) arranged between the first differential mechanism 42 and the regulator exhausts 27, 28.

Similarly, while in the embodiment described above, the first front sun wheel 51 is connected to the center mobile 25, the first support carriage 52 is connected to the first of the second mobiles 44, the first sun gear rear 54 is connected to the second of the second mobile 45, such a configuration should not be interpreted restrictively. Indeed, in the first differential mechanism 42, it is only necessary that the center wheel 25, and the second movable 44, 45 are separately connected to the three gears.

While in the embodiment described above, the rotation of the first support carriage 52 and the first sun gear 54 is stopped according to the operating modes via the control mechanism 29, this should not be interpreted restrictively either. For example, it is possible to separately provide a stop mechanism for rotating the first support carriage 52 and for that of the first sun gear 54 in each mode. In particular, in the case where no regulation mechanism 29 is provided, it is possible to switch the transmission of energy to the sprung balance 73, 87 by such a stop mechanism.

Second Embodiment [0134] In what follows, the second preferred embodiment for the present invention will be described. This embodiment differs from the embodiment described above, for example, in that a first differential mechanism 242 adopts a clutch mechanism. Fig. 12 is a sectional view of the first differential mechanism 242. In the following, the components which are identical to those of the first embodiment described above are indicated by the same reference numerals, and their description will not be repeated.

In a movement 202 shown in FIG. 12, the first differential mechanism 242 has primarily a front gear 210, a rear gear 211, an intermediate gear 212, and clutch plates (a front clutch plate 213 and a rear clutch plate 214).

First, the intermediate gear 212 has an intermediate shaft 212a, and a toothed portion 212b attached to the intermediate shaft 212a.

The intermediate shaft 212a extends through the front gear 210 and the rear gear 211 in the forward-to-back direction, and is rotatable about the front-to-back axial direction. In addition, the intermediate shaft 212a and its toothed portion 212b can be moved together from front to rear.

The toothed portion 212b meshes with the center mobile 25 mentioned above.

The front gear 210 is arranged in front of the toothed portion 212b of the intermediate gear 212, that is to say the bottom side relative thereto. The front gear 210 is rotatably mounted on the intermediate shaft 212a via a bearing 220. The front gear 210 is connected to the second of the second movers 45 mentioned above (for example, to the second second gear 45a), and is connected to one of the gears (for example, at the second rear sun gear 104) of the second differential mechanism 43.

The rear gear 211 is arranged at the rear of the toothed portion 212b of the intermediate gear 212, that is to say the dial side relative thereto. The rear gear 211 is rotatably mounted on the intermediate shaft 212a via a bearing 221. The rear gear 211 is kinematically connected to the first of the second movers 44 mentioned above (for example, to the first second gear 44a), and is also connected kinematically to one of the gears (for example, to the second support carriage 102) of the second differential mechanism 43.

The front clutch plate 213 is fixed to the front of the toothed portion 212b of the intermediate shaft 212a, that is to say bottom side relative thereto. With the movement of the intermediate gear 212 in the forward-to-back direction, the front clutch plate 213 can be brought into contact with the forward gear 210 and away from the latter. In other words, in the state in which the front clutch plate 213 is in contact with the front gear 210, the rotation of the front gear 210 relative to the intermediate gear 212 is blocked by the frictional force between the front clutch plate 213 and the front gear 210. Therefore, the intermediate gear 212 and the front gear 210 rotate together. By cons, in the state in which the front clutch plate 213 is spaced from the front gear 210, the rotation of the front gear 210 relative to the intermediate gear 212 is permitted.

The rear clutch plate 214 is attached to the rear of the toothed portion 212b of the intermediate shaft 212a, that is to say the dial side with respect thereto. Following a movement of the intermediate gear 212 in the front-to-rear direction, the rear clutch plate 214 can be brought into contact with and away from the rear gear 211. The engagement method of the clutch plates 213 and 214 with the corresponding gears 210 and 211 is not left to a friction but allows variations as needed. For example, the clutch plates 213 and 214 and the corresponding gears 210 and 211 can be brought into engagement by recesses and projections, or the like.

The movement 202 according to the present embodiment is equipped with a switching lever 230 actuating the movement of the intermediate gear 212 in the front-rear direction. The switching lever 230 may exert a compressive force on the intermediate gear 212 in the forward-to-back direction via, for example, the front end and the rear end of the intermediate rod 212a. The switching lever 230 can be actuated, for example, by the winding stem 19.

[0144] FIG. 13 is a sectional view corresponding to FIG. 12 to illustrate the high oscillation mode.

As shown in FIG. 13, in the high oscillation mode of the motion 202 of the present embodiment, the intermediate gear 212 and the rear gear 211 are positioned in a "mutually connected" state, that is, where they are secured together. rotation relative to each other, via the rear clutch plate 214 in the state in which the alternating rotation of the second sprung balance 87 is stopped by the control mechanism 29. Therefore, the energy of the barrel of movement 24 is transmitted to the first differential mechanism 242 via the center wheel 25. And in the first differential mechanism 242, the intermediate gear 212 and the rear gear 211 rotate together, whereby the energy is transmitted to the first of the second mobiles 44 and the second differential mechanism 43. Therefore, the display gear 30 operates, and the timepiece 1 displays and shimmers the time that passes. In the high oscillation mode, the first balance-spring 73 effects 8 oscillations, so that the movement of the seconds hand 6 (seconds wheel 130) is performed by a sequence of 8 steps per second. In the high oscillation mode, the intermediate gear 212 does not rotate relative to the front gear 210. Thus, the energy of the movement barrel 24 is not transmitted to the second regulator escapement 28.

As illustrated in FIG. 12, in the low oscillation mode, the intermediate gear 212 and the front gear 210 are placed in a "mutually connected" state where they are rotationally fixed relative to one another via the clutch plate before 213 in the state in which the alternating rotation of the first balance-spring 73 is stopped by the control mechanism 29. Therefore, due to the energy transmitted to the first differential mechanism 242 via the center mobile 25, the intermediate gear 212 and the front gear 210 rotate together. As a result, the energy is transmitted to the second of the second mobiles 45 and the second differential mechanism 43, which allows the timepiece 1 to display and time slice. In the low oscillation mode, the intermediate gear 212 does not rotate relative to the rear gear 211. Thus, the energy of the movement barrel 24 is not transmitted to the first regulator escapement 27.

Here, the frequency difference between the first sprung balance 73 and the second sprung balance 87 can be eliminated, for example, by taking a number of teeth of the front gear 210 different from that of the rear gear. 211. More specifically, the number of teeth of the front gear 210 and that of the rear gear 211 are defined so that the transmission gear ratio between the front gear 210 and the intermediate gear 212 is equal. to half that between the rear gear 211 and the intermediate gear 212. Therefore, it is possible to eliminate the difference in frequency between the first balance-spring 73 and the second balance spring 87 through the first Differential mechanism 242. In other words, the speed of rotation of the front gear 210 in the low oscillation mode is the same as the speed of rotation of the rear gear 211 in the motor. of high oscillation. Thus, in the low oscillation mode, the second balance spring 87 performs 4 oscillations, and the seconds hand 6 (the seconds wheel 130) makes a movement at a rate of 4 steps per second. The difference in frequency between the first balance spring 73 and the second balance spring 87 can however be suppressed by the second mobile 44, 45 and the second differential mechanism 43.

In this way, according to the present embodiment, the first differential mechanism 242 adopts a clutch mechanism, by means of which the connection between the movement barrel 24 and each sprung balance 73, 87 can be easily switched when each mode change. In particular, in the present embodiment, the number of teeth of the front gear 210 and that of the rear gear 211 are chosen to be different from each other, but at the same time the difference in frequency between the gear and the gear. first sprung balance 73 and the second sprung balance 87 can be suppressed by the first differential mechanism 242. Therefore, it is possible to obtain the same effects as those of the embodiment described above. In the present embodiment, the control mechanism 29 described above may nevertheless not be employed.

While in the embodiment described above, the first differential mechanism 242 adopts a clutch mechanism, this should not be interpreted in a limiting manner. A clutch mechanism made in the same manner as for the first differential mechanism 242 described above can be adopted in the second differential mechanism 43.

As a clutch mechanism adopted for the second differential mechanism 243, the one-way clutch mechanism shown in FIG. 14 can be adopted. The second differential mechanism 243 shown in FIG. 14 is mainly equipped with an intermediate gear 250, a front gear 251, and a rear gear 252.

The intermediate gearing 250 has an intermediate shaft 250a and a toothed portion 250b attached to the intermediate shaft 250a.

The intermediate shaft 250a extends through the front gear 210 and the rear gear 211 from front to rear, and is rotatable about its axis which extends in the forward-to-back direction. .

The toothed portion 250b meshes with the seconds wheel 130 of the display gear 30 mentioned above.

The front gear 251 is supported by the intermediate shaft 250a via a front clutch 260. The front clutch 260 is, for example, a cam-type one-way clutch mechanism. The front clutch 260 is mainly equipped with an outer ring (not shown) attached to the front gear 251, an inner ring attached to the intermediate shaft 250a, a roller (not shown) provided between the outer ring and the outer ring. inner ring, and a compression member (not shown) acting against the roller. In the front clutch 260, the inner ring and the outer ring are "connected", that is, integral with each other via the roll when the front gear 251 tends to rotate in a direction in relation to the intermediate gear 250. In such a situation, the intermediate gear 250 and the front gear 251 rotate together. However, on the contrary, when the front gear 251 tends to rotate in the other direction relative to the intermediate gear 250, the "connected" state of the inner ring relative to the outer ring is suppressed and these are no longer integral in rotation. Therefore, in this case the rotation of the front gear 251 with respect to the intermediate gear 250 is then allowed.

The rear gear 252 is supported by the intermediate shaft 250a via a rear clutch 261. The rear clutch 261 is of a configuration equivalent to the architecture of that of the front clutch 260 mentioned above. In the rear clutch 261, when the rear gear 252 tends to rotate in a direction relative to the intermediate gear 250, the inner ring and the outer ring are connected to each other via a roller. Therefore, the intermediate gear 250 and the rear gear 252 then rotate together. However, when the rear gear 252 tends to rotate relative to the intermediate gear 250, the state connected between the inner ring and the outer ring is eliminated. Therefore, rotation of the rear gear 252 in the other direction relative to the intermediate gear 250 is then allowed.

In this architecture, in the high oscillation mode, when the front gear 251 rotates in one direction with the energy transmitted from the first differential mechanism 42, the front gear 251 and the intermediate gear 250 are placed in a "connected" state where they rotate together, and the front gear 251 and the intermediate gear 250 then rotate together. As a result, the seconds wheel 130 rotates in the other direction. In the high oscillation mode, the intermediate gear 250 rotates in a direction relative to the rear gear 252 and in doing so the intermediate gear 250 does not rotate with respect to the rear gear 252. Thus, the energy of the movement barrel 24 is not transmitted to the second regulator escapement 28.

In contrast, in the low oscillation mode, when the rear gear 252 rotates in one direction with the energy transmitted from the first differential mechanism 42, the rear gear 252 and the intermediate gear 250 are placed in the same direction. 'connected' state where they are rotationally secured, and thus the rear gear 252 and the intermediate gear 250 rotate together. As a result, the seconds wheel 130 rotates in the other direction. In the low oscillation mode, the intermediate gear 250 rotates in a direction relative to the front gear 251, and in doing so, the intermediate gear 250 does not rotate with respect to the forward gear 251. Thus, the energy of the movement barrel 24 is not transmitted to the first regulator escapement 27.

The technical teachings of the present invention are not limited to those of the embodiments mentioned above, but allow for various variations without departing from the scope of the spirit of the present invention.

For example, while in the embodiments described above, we adopt a planetary mechanism and a clutch mechanism to achieve the switching mechanism, such implementations should not be interpreted restrictively. Any other type of switching mechanism is likely to do the job as long as the energy supplied by the barrel of the movement 24 can be transmitted to one or the other of the first balance-spring 73 or the second balance-spring 87 In this case, the switching mechanism may, for example, have an architecture that is alternately geared to each second mobile 44, 45 according to the modes.

While in the embodiments described above, the frequency of the first sprung balance 73 is set at 4 Hz, and the frequency of the second sprung balance 87 is set at 2 Hz, this should not be interpreted as restrictive way either. The frequency of each sprung balance 73, 87 could be changed as needed.

While in the embodiments described above, two balance springs 73 and 87 are employed, this should not be interpreted restrictively either. Three or more balance gears may also be provided.

While in the embodiments described above, the rotational speed of the barrel of the movement 24 in the low oscillation mode is defined as being equal to half the rotation speed of the barrel of the movement 24 in the operating mode. at high oscillation, this should not be interpreted restrictively either. It is only necessary that the rotational speed of the barrel of the movement 24 is different in each mode.

While in the embodiments described above, the first sprung balance 73 and the second sprung balance 87 of different frequency are used, this should not be interpreted restrictively either. Any other architecture will do the job as long as the rotation speed of the movement barrel 24 is different between a first state (the high oscillation mode according to the embodiments described above) and a second state (the low oscillation mode). according to the embodiments described above). For example, the rotational speed of the barrel of the movement 24 can be made different by choosing at least one parameter among the angle of oscillation, the frequency, and the torque as being different in the first balance-spring 73 compared to the second balance spring 87.

In the case where the pairs of the first sprung balance 73 and the sprung balance 87 are made different, when the sprung balance of the larger torque is actuated, it is possible to reliably remove the influence of any disturbance, which allows an improvement in the accuracy of time measurement. On the other hand, when the balance spring of the smaller torque is actuated, it is possible to achieve additional energy savings for the motion cylinder.

In the case where the oscillation amplitudes of the first balance-spring 73 and balance spring 87 are made different, when the sprung balance having the largest amplitude of oscillation is actuated, it is possible to reliably suppress the influence of disturbances, which allows an improvement in the accuracy of time measurement. On the other hand, when the sprung balance whose oscillation amplitude is the smallest is actuated, it is possible to achieve additional energy savings for the movement barrel.

In the first sprung balance 73 and the second sprung balance 87, the magnitude ratio between the oscillation angle, the frequency, and the torque makes it possible to make modifications as needed. For example, the amplitude of oscillation, the frequency, and the torque of the first balance-spring 73 may be greater than those of the second balance-spring 87. Alternatively, alternatively the value of a single parameter among the amplitude oscillation, the frequency, and the torque of the first sprung balance 73 can be chosen larger than that of the second sprung balance 87 (the other values of the first sprung balance 73 may not be larger than those of the second balance -spiral 87), [0167] Moreover, even in the case where spiral balances of the same performance (that is to say, of the same amplitude of oscillation, frequency, and torque) are used, by changing the number teeth, etc. in the energy transmission mechanism, it is possible to make the rotation speed of the movement barrel 24 different between the first state and the second state. Also according to such an embodiment, it is possible to achieve energy savings for the movement barrel, and to achieve an increase in the time of operation of the timepiece.

[0168] While in the embodiments described above, the energy of the energy transmission mechanism is transmitted to the same display gear (the seconds wheel 130) both in the first state and in the first gear. second state, this should not be interpreted restrictively either. For example, an architecture may be adopted in which the energy transmission mechanism transmits energy to different display cogs according to whether in the first state or in the second state.

Apart from the foregoing, it is possible to replace components of the embodiments described above with other well-known components as required without departing from the scope conferred by the present invention nor of to move away from his mind. In addition, the modifications and variants described above can be mutually combined without restrictions as needed.

Claims (7)

claims A movement (2) comprising: a first balance spring (73) and a second balance spring (87) alternately rotating in a reciprocating motion; an energy transmission mechanism (26) switching between a first state in which the energy of a movement barrel (24) can be transmitted to the first balance-spring (73), and a second state in which the energy the movement barrel (24) can be transmitted to the second balance spring (87), and rotating the movement barrel (24) at different rotational speeds in the first state and in the second state; and an indicator needle wheel (130), to which an indicator needle is mounted, and to which energy is transmitted from the movement barrel (24) via the energy transmission mechanism. 2. Movement (2) according to claim 1, wherein the first balance-spring (73) and the second balance spring (87) differ from each other in terms of frequency; and the energy transmission mechanism (26) rotates the movement barrel (24) in accordance with the frequencies of the first balance spring (73) and the second balance spring (87), and varies the amount of energy supplied. at the output of the movement barrel (24) in terms of speed for rotating the indicator needle wheel (130) at a fixed rotational speed. 3. Movement (2) according to claim 1 or 2, wherein the first balance-spring (73) and the second balance spring (87) differ from each other in terms of torque. 4. Movement (2) according to one of claims 1 to 3, wherein the energy transmission mechanism (26) is equipped with a transmission mechanism connected to the first balance-spring (73) and the second balance- spiral (87); the transmission mechanism comprises three gears: a first sun gear (51), a second sun gear (54) arranged coaxially with the first sun gear (51), and a support carriage (52) carrying a sun gear (53) meshing with the first sun gear (51) and the second sun gear (54) to allow rotation and complete revolution; among the three gears above, the first gear transmits energy to the first balance-spring (73) in the first state, the second gear transmits energy to the second balance-spring (87) in the second state, and the third gear receives energy from the motion barrel (24). 5. Movement (2) according to claim 4, wherein the satellite wheel (53) rotates the first gear and the second gear at different speeds of rotation at the frequencies of the first balance-spring (73) and the second balance-spiral (87). 6. Movement (2) according to one of claims 1 to 5, wherein the energy transmission mechanism (26) is equipped with a regulating mechanism (29) which stops the alternating rotation of the second balance-spring (87). ) when it is in the first state, and stops the alternating rotation of the first balance-spring (73) when it is in the second state. 7. Timepiece (1) equipped with the movement (2) as claimed in one of claims 1 to 6.