• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a spiral spring for a timepiece generating a desired torque. It comprises: a spring main body (91) which extends in a spiral shape; and an engaging portion (93) integrally molded with an outer end (91a) of the spring main body (91) and engaged with a driver at at least two points. The spiral spring can be, for example, a date actuating spring (90) and the drive element a date gear unit.
    公开号:CH717216A2
    申请号:CH00227/21
    申请日:2021-03-02
    公开日:2021-09-15
    发明作者:Kawauchiya Takuma；Mori Yuichi；Suzuki Shigeo
    申请人:Seiko Watch Kk；
    IPC主号:
    专利说明:

    BACKGROUND OF THE INVENTION
    1. Field of the invention
    The present invention relates to a spiral spring, a torque generator, a timepiece movement and a timepiece.
    2. Description of the state of the art
    Mechanical timepieces are known provided with a torque generator comprising a spiral spring which applies a torque to a rotating body (cf. for example JP-A-2020-008560 (reference patent 1)) . The coil spring is attached to a first component at an outer end and attached to a second component at an inner end, the coil spring is wound on itself by rotation of the first component and the second component. relative to each other and, accordingly, a torque is generated between the first component and the second component.
    However, it is possible that the torque generated by the spiral spring fluctuates due to a deformation accompanying the winding during reassembly. For example, when the spiral spring is wound and fixed to generate a torque, not only a force in the peripheral direction but also an internal force in the radial direction is applied to the outer end of the spiral spring when the diameter of the peripheral portion external spiral spring is reduced. When the spiral spring unwinds to generate a torque, not only a force in the peripheral direction but also an outward force in the radial direction is applied to the outer end of the spiral spring. Here, in a configuration in which the outer end of the spiral spring is supported by a single pin, when the pin has a column shape, or when the recess in which the pin is inserted has a circular shape, when the force in the peripheral direction and the force in the radial direction act on the outer end of the spiral spring, the outer end of the spiral spring can rotate with respect to the pin taken as the center. As the outer end of the spiral spring rotates, the outer peripheral portion of the spiral spring is displaced more than in the case where the outer end of the spiral spring is fixed and, thus, it is possible for contact to occur between adjacent springs. in the radial direction; and when such contacts occur in the spiral spring, the spiral spring may not be able to generate a desired torque due to the frictional force at the contact portions.
    SUMMARY OF THE INVENTION
    The present application relates to a spiral spring, a torque generator, a timepiece movement and a timepiece capable of generating a desired torque.
    According to one aspect of the present application, a spiral spring for a timepiece which is wound around an axis to generate torque is provided, which comprises: a spring main body which extends in the form of a spiral; and an engaging portion integrally molded with an outer end of the spring main body and engaged with a drive member at at least two points.
    [0006] According to the present application, the rotation of the engagement part relative to the drive element can be suppressed. Therefore, even if the spiral spring is wound and the force in the radial direction as well as the force in the peripheral direction act on the engaging part, any unintentional deformation of the spiral spring can be suppressed. In this way, mutual contact of turns due to the winding and fixing of the spiral spring or contact with surrounding components due to the unwinding of the spiral spring during its unwinding can be suppressed. Also in this way, the reduction of the torque generated by the spiral spring due to the frictional force accompanying the contact of the spiral spring in a state where it is wound on itself in the armed state can be suppressed. Therefore, the spiral spring can generate a desired torque.
    In the spiral spring described above, the engagement part may have a first contact portion and a second contact portion which are brought into contact with the drive element, a first normal vector at the level of the first contact portion being able to point in a direction which deviates from the axis according to a view taken in the axial direction of the axis and a second normal vector at the level of the second contact portion being able to point in a direction which s 'departs from the first contact portion seen from the axial direction.
    According to the present application, the displacement of the engagement part due to the force in the peripheral direction acting on the engagement part can be limited at the level of the first contact portion. Further, the rotation of the engaging portion centered on the first contact portion due to the force in the radial direction acting on the engaging portion can be limited at the second contact portion. In this way, the rotation of the engaging part with respect to the driving member is regulated and thus, the effect described above can be obtained.
    In the spiral spring described above, the engaging part may have a pair of recesses in which a pair of protrusions located on the drive member are arranged one by one.
    According to the present application, the engagement part and the drive element are in mutual engagement at two points by a contact between a protruding part and the internal surface of a recess, and by the contact between the other protruding part and the inner surface of the other recess. Therefore, the effect described above can be obtained.
    In the spiral spring described above, each pair of recesses may comprise a first extension portion in which the protruding part is arranged and which extends in a peripheral direction around the axis and a second portion of 'extension which is connected to the first extension portion, which extends in a radial direction centered on the axis and which opens to a side surface of the engagement portion.
    According to the present application, in order for the protruding part positioned at the level of the first extension portion to reach the opening on the lateral surface of the engagement part, the protruding part must be moved in the radial direction after its displacement relative to the engagement portion in the peripheral direction. Thus, it is possible to prevent the protrusion from coming out of the recess from a configuration in which the recess extends linearly when viewed from the axial direction. Therefore, the engaging part and the driving member can be reliably engaged with each other.
    In the spiral spring described above, each pair of recesses can pass through the engagement part in the axial direction corresponding to the axis of the spiral spring and each pair of recesses can include a narrow portion where the protruding part is arranged and a wide portion which is connected with the narrow portion in the peripheral direction around the axis and which is formed larger in the radial direction centered on the axis than the narrow portion.
    According to the present application, even when the protruding part is provided with a collar through which the narrow portion cannot be inserted, by the displacement of the protruding part towards the narrow portion after the insertion of the protruding part in the wide portion, the protruding part can be arranged in the narrow portion. Thus, by engaging the protruding part provided with the collar with the engaging part, it is possible to avoid the fact that the protruding part cannot come out of the recess. Therefore, the engaging part and the driving member can be reliably engaged with each other.
    In the spiral spring described above, the engaging part can have a recess in which the first protrusion formed on the driving member is arranged and a side surface of the engaging part can be formed. so as to be in contact with a second protrusion formed on the driving member.
    According to the present application, the engagement part and the drive element are in mutual engagement at two points via contact between the first protruding part and the internal surface of the recess and by contact between the second protruding part and the side surface of the engaging part. Therefore, the effect described above can be obtained. In addition, compared to the configuration that the second protrusion is arranged in the recess provided in the engaging part, it is possible to use a configuration that the positional deviation due to a manufacturing error of the second part protruding from the first protruding part is tolerable.
    In the spiral spring described above, the engagement part may have a recess in which is arranged a protruding part formed on the drive element and which has a non-circular shape when viewed from the corresponding axial direction to the axis of the spiral spring.
    When a single recess is formed so as to have a circular shape when the latter is viewed from the axial direction, the engagement part and the driving member cannot come into mutual engagement at two points. or more regardless of the shape of the protrusion and the rotation of the engaging part with respect to the driving member cannot be suppressed.
    According to the present application, for example, thanks to the formation of the protruding part in a non-circular shape when the latter is seen in the axial direction or by the arrangement of the plurality of protruding parts in the recess, the the engaging part and the driving element may engage each other at at least two points. Therefore, the effect described above can be obtained.
    In the spiral spring described above, the external shape of the engagement part may be non-circular when viewed from the axial direction of the axis.
    When the outer shape of the engagement portion has a circular shape when viewed in the axial direction of the spiral spring, the engagement portion and the drive member cannot engage in mutual engagement. two or more points simply by bringing the driving member into contact with the side surface of the engaging part and the rotation of the engaging part relative to the driving member cannot be suppressed .
    According to the present application, by the mutual contacting of the drive element and the lateral surface of the engagement part, the engagement part and the drive element can come into mutual engagement. in at least two points. Therefore, the effect described above can be obtained.
    Another aspect of the present application relates to a torque generator comprising not only the spiral spring, but also the drive element with which the engaging part of the spiral spring is engaged; and a fixing member to which an inner end of the spiral spring is fixed.
    According to the present application, since the spiral spring generates a desired torque, any insufficient torque applied between the drive element and the fixing element can be eliminated.
    In the torque generator, it is also possible to provide a date gear mobile which comprises one of the two elements chosen from the drive element and the fixing element and which rotates in synchronization. with the rotation of an hour wheel; a date finger unit which comprises the other of the two elements among the drive element and the fixing element, and a date finger provided to be able to engage and disengage from a toothing of an indicator date on which the date values are displayed and which is rotatably arranged with respect to the date mobile gear and coaxial with the latter; and a calendar mechanism which switches the specified date character in an aperture of a dial.
    According to the present application, any insufficiency of a rotational force transmitted to the date indicator due to the insufficiency of the torque applied to the date finger unit can be eliminated. Therefore, a torque generator having a calendar mechanism in which a reliable date advancing operation is possible can be employed.
    In the torque generator described above, one can also provide a constant force mechanism which comprises an input rotary body, which comprises one of the two elements chosen from the drive element and the fixing element, which is rotated by energy from an energy source and which recharges the spiral spring with energy; an output rotary body which comprises the other member selected from the driving member and the fixing member, which is rotated by the energy from the spiral spring and which transmits the energy from the spiral spring to a exhaust regulator; and a cycle control mechanism which intermittently rotates the input rotary body relative to the output rotary body according to the rotation of the output rotary body.
    According to the present application, since the torque applied between the input rotary body and the output rotary body is stabilized, any torque fluctuation transmitted from the output rotary body to the exhaust can be suppressed.
    In the torque generator described above, it is possible to further provide a rotating part which comprises one of the two elements chosen from the drive element and the fixing element, and which rotates from synchronized manner with an indicator; and a supporting part which comprises the other member of the driving member and the fixing member and which rotatably supports the rotating part; and a retrograde mechanism which drives the indicator back and forth between an initial position and a final position.
    According to the present application, it is possible to eliminate any insufficient torque applied to the rotating component and any disturbance of repetitive movement of the indicator.
    The present application also relates to a timepiece movement comprising the torque generator described above.
    The present application also relates to a timepiece comprising the timepiece movement described above.
    The present application makes it possible to obtain a timepiece movement and a timepiece able to stabilize the operation thanks to the spiral spring.
    The present application makes it possible to obtain a spiral spring, a torque generator, a timepiece movement and a timepiece capable of generating a desired torque.
    BRIEF DESCRIPTION OF THE DRAWINGS
    FIG. 1 is a plan view illustrating a timepiece according to a first embodiment. Fig. 2 is a plan view of a movement according to the first embodiment, seen from the front. Fig. 3 is a plan view of the movement according to the first embodiment viewed from a rear face. Fig. 4 is a plan view of the main part of a calendar mechanism according to the first embodiment viewed from the rear face of the movement. Fig. 5 is a plan view of a date indicator drive wheel according to the first embodiment seen from below. Fig. 6 is a plan view of the date indicator drive wheel according to the first embodiment seen from above. FIG. 7 is a plan view of a date gear mobile and of a date indicator actuating spring according to the first embodiment, when the latter are seen from above. Figure 8 is a sectional view taken along line VIII-VIII of Figure 6. Figure 9 is an explanatory view of the operation of the calendar mechanism and is a plan view of part of the calendar mechanism, viewed from the top. below. Fig. 10 is an explanatory view of the operation of the calendar mechanism and is a plan view of part of the calendar mechanism, viewed from below. Fig. 11 is an explanatory view of the operation of the calendar mechanism and is a plan view of part of the calendar mechanism, seen from below. Fig. 12 is a plan view of the main part of the date indicator actuating spring according to the first embodiment, seen from above. FIG. 13 is a plan view of the date gear mobile and of the date indicator actuating spring according to a first variant of the first embodiment, when the latter are seen from above. Fig. 14 is a plan view of the main part of the date indicator actuating spring according to the first variant of the first embodiment, seen from above. FIG. 15 is a plan view of the date gear mobile and of the date indicator actuating spring according to a second variant of the first embodiment, when the latter are seen from above. FIG. 16 is a plan view of the main part of the date indicator actuating spring according to the second variant of the first embodiment, seen from above. FIG. 17 is a plan view of the date gear mobile and of the date indicator actuating spring according to a third variant of the first embodiment, when the latter are seen from above. Fig. 18 is a plan view of a main part of the date indicator actuating spring according to the third variation of the first embodiment, seen from above. FIG. 19 is a plan view of the date gear mobile and of the date indicator actuating spring according to a fourth variant of the first embodiment, seen from above. Fig. 20 is a plan view of a main part of the date indicator actuating spring according to the fourth variant of the first embodiment, viewed from above. FIG. 21 is a plan view of the date gear mobile and of the date indicator actuating spring according to a fifth variant of the first embodiment, when the latter are seen from above. Fig. 22 is a plan view of a main part of the date indicator actuating spring according to a fifth variation of the first embodiment, viewed from above. FIG. 23 is a plan view of the date gear mobile and of the date indicator actuating spring according to a sixth variant of the first embodiment, when the latter are seen from above. Fig. 24 is a plan view of a main part of the date indicator actuating spring according to the sixth variation of the first embodiment, seen from above. Fig. 25 is a block diagram of a movement according to a second embodiment. Fig. 26 is a perspective view of part of the movement of the second embodiment, viewed from above. Fig. 27 is a sectional view showing part of the movement according to the second embodiment. Fig. 28 is a plan view of part of the movement according to the second embodiment in top view. FIG. 29 is an external view of a timepiece according to a third embodiment. Figure 30 is a plan view of a retrograde mechanism. Figure 31 is a plan view of the retrograde mechanism.
    DESCRIPTION OF EMBODIMENTS
    In the following, embodiments according to the present invention will be described, with reference to the drawings. In addition, in the description which follows, the same reference numbers will be given to configurations having identical or similar functions. In the present embodiment, a mechanical timepiece will be described as an example of a timepiece.
    In general, a mechanical body comprising a drive part of the timepiece is called a "movement". A state in which a dial and a hand are attached to the movement, placed in a timepiece case and made into a finished product is called a "complete movement" of the timepiece.
    Among the two sides of a plate which constitutes a main board of a timepiece, the side where the crystal of the timepiece case is located (that is to say the side where the dial) is called the “back” of the movement. In addition, among the two sides of the plate, the side where the bottom of the timepiece case is located (that is to say the side opposite to that where the dial is located) is called the „front. " some movement.
    Furthermore, in this embodiment, the description is given by defining the direction from the dial to the bottom is defined as an upward direction and the direction opposite to it is defined as a downward direction. low. Moreover, considering each axis of rotation as a center, the clockwise direction of rotation seen from above is called clockwise and the counterclockwise direction of rotation seen from above is called counterclockwise.
    [First embodiment]
    FIG. 1 is a plan view showing a timepiece according to a first embodiment.
    As illustrated in Figure 1, in the timepiece case comprising a back (not shown) and a crystal 2, the complete movement of a timepiece 1 of this embodiment comprises a movement 10 ( timepiece movement), a dial 3 having a scale indicating at least information relating to the time and an indicator comprising an hour hand 5, a minute hand 6 and a seconds hand 7. The dial 3 is provided with a date window 3a to clearly indicate a date value 40a displayed on a date indicator 40, which will be described later.
    Figure 2 is a plan view of a movement according to the first embodiment, seen from the front. In FIG. 2, certain components which configure the movement 10 are omitted from the drawings in order to make the latter more readable.
    As illustrated in Figure 2, the movement 10possède a plate 11 which constitutes a board. An adjusting rod 9 for the hands is incorporated in the plate 11. A crown 4 is connected to the adjusting rod 9 for the hands on the outside of the timepiece case illustrated in FIG. 1. The movement 10 comprises a finishing gear 12 and a exhaust regulator 13 at the front of the plate 11.
    The finishing gear 12 transmits the torque to the exhaust regulator 13. The finishing gear 12 mainly comprises a pair of barrel drums 20A and 20B, a spacer gear mobile 21, a second mobile 22, a third mobile 23, a fourth mobile 24 and an intermediate exhaust mobile 25. The barrel drums 20A and 20B are arranged side by side in a plan view, when viewed in the up-down direction. Each of the barrel drums 20A and 20B is pivotally supported between the plate 11 and the barrel bridge (not shown). Each of the barrel drums 20A and 20B comprises a movement barrel 20a intended to house a barrel spring therein, and a ratchet wheel 20b arranged coaxially and in relative rotation with respect to the movement barrel 20a. The outer end of the barrel spring is attached to the movement barrel 20a and the inner end of the barrel spring is attached to the ratchet wheel 20b. Accordingly, the movement barrel 20a and the ratchet wheel 20b are driven in relative rotation with respect to each other by the torque accompanying the unwinding (unwinding) of the barrel spring and the movement barrel 20a and the wheel to ratchet 20b are relatively rotated in a predetermined direction to wind the barrel spring.
    The ratchet wheel 20b of said barrel drum 20A meshes with the intermediate ratchet wheel 27. The intermediate ratchet wheel 27 configures part of the manual winding gear 14. The manual winding gear 14 transmits the rotation of the rod adjusting 9des needles to the ratchet wheel 20b of said barrel drum 20A. Accordingly, the ratchet wheel 20b of said barrel drum 20A is rotated via that of the needle adjusting rod 9 and the barrel spring of said barrel drum 20A is wound up. The toothing of the movement barrel 20a of said barrel drum 20A meshes with the teeth of the movement barrel 20a of the other barrel drum 20B. The movement barrel 20a of the other barrel drum 20B is rotated by the torque accompanying the unwinding / unwinding of the barrel spring of said barrel drum 20A and coils / arms the barrel spring of the other barrel drum 20B . The ratchet wheel 20b of the other barrel drum 20B rotates with the unwinding of the barrel spring of the other barrel drum 20B.
    The spacer gear mobile 21, the second mobile 22, the third mobile 23, the fourth mobile 24 and the intermediate exhaust mobile 25 are pivotally supported between the plate 11 and the gear bridge (not shown) . When the spacer gear mobile 21, the second mobile 22, the third mobile 23, the fourth mobile 24 and the intermediate exhaust mobile 25 are rotated by the elastic return force of the barrel spring on which the wheel is driven. ratchet 20b of the other barrel drum 20B is wound, the rotation is performed on the basis of this rotation.
    In other words, the spacer gear mobile 21 engages with the ratchet wheel 20b of the other barrel drum 20B and rotates based on the rotation of the ratchet wheel 20b. The second mobile 22 meshes with the spacer gear mobile 21 and rotates based on the rotation of the spacer gear mobile 21. The third mobile 23 meshes with the second mobile 22 and rotates based on the rotation of the second. mobile 22. The fourth mobile 24 engages with the third mobile 23 and rotates on the basis of the rotation of the third mobile 23. The seconds hand 7 shown in FIG. 1 is fixed to the fourth mobile 24 and the seconds hand 7 displays the current seconds on the base of the rotation of the fourth mobile 24. The seconds hand 7 rotates once in one minute at a speed of rotation regulated by the exhaust regulating member 13. The intermediate exhaust mobile 25 engages with the fourth mobile 24 and rotates. on the basis of the rotation of the fourth mobile 24. The intermediate exhaust mobile 25 engages with an exhaust pinion (not shown) of the exhaust mobile which will be described later.
    The exhaust regulator 13 controls the rotation of the finishing gear 12. The exhaust regulator 13 comprises mainly an exhaust mobile and an anchor, which are not shown, and a balance 32. The exhaust mobile is rotated via the torque transmitted by the barrel spring of the barrel drums 20A and 20B via the finishing gear 12. The anchor ensures the regularity of the exhaust and of the rotation of the mobile. exhaust. The balance 32 escapes the escape wheel set at a constant speed.
    Figure 3 is a plan view of a movement according to the first embodiment seen from the rear. In FIG. 3, certain parts which configure the movement 10 are omitted in the drawings in order to make the latter more readable.
    As illustrated in Figure 3, the movement 10 comprises a rear gear 15, a calendar mechanism 16, a time correction gear 17 and a calendar correction mechanism 18 at the rear of the plate 11.
    The rear wheel 15 comprises mainly a central wheel 36, a minute wheel 37 and an hour wheel 38. The central wheel 36 is arranged coaxially with the fourth mobile 24 (see FIG. 2). The central wheel 36 meshes with the third mobile 23 (see Figure 2) and rotates on the basis of the rotation of the third mobile 23. The minute hand 6 shown in Figure 1 is fixed to the central wheel 36 and the minute hand 6 displays the minutes via the rotation of the central wheel 36. The minute hand 6 rotates once an hour at a speed of rotation regulated by the exhaust regulator 13. The minute wheel 37 meshes with the central wheel 36 and turns on the base of the rotation of the central wheel 36. The hour wheel 38 is arranged coaxially with the central wheel 36. The hour wheel 38 meshes with the minute wheel 37 and rotates on the basis of the rotation of the minute wheel 37 The hour hand 5 shown in Fig. 1 is attached to the hour wheel 38 and the hour hand 5 displays the hours via the rotation of the hour wheel 38. The hour hand 5 rotates once every 12 hours at a speed of rotation reg ulated by the exhaust regulator 13.
    The calendar mechanism 16 comprises a date indicator 40, a first intermediate date wheel 41, a second intermediate date wheel 42, a date indicator drive wheel 43, a regulator spring 44 of the drive wheel The date indicator (see Figure 4) and a date jumper 45. The date indicator 40 is an annular element rotatably fixed to the plate 11. In the date indicator 40, the date values 40a (cf. FIG. 1) showing the dates from 1 to 31 are displayed sequentially in the peripheral direction. A plurality of teeth 40b are formed on the inner peripheral surface of the date indicator 40. The plurality of teeth 40b are formed so as to protrude inwardly in the radial direction and some distance in the peripheral direction.
    The first intermediate date wheel 41, the second intermediate date wheel 42 and the date indicator drive wheel 43 are rotatably supported by the plate 11. The first intermediate date wheel 41 meshes with the hour wheel 38 and rotates based on the rotation of the hour wheel 38. The second intermediate date wheel 42 engages with the first intermediate date wheel 41 and rotates based on the rotation of the first intermediate date wheel 41.
    The date indicator drive wheel 43 comprises a date gear mobile 60 and a date finger 75. The date gear mobile 60 engages with the second intermediate date wheel 42 and rotates once in 24 hours on the base of the rotation of the second intermediate date wheel 42. The date finger 75 rotates once in 24 hours around the center of rotation of the date gear mobile 60. The date finger 75 is in engagement with the toothing 40b of the The date indicator 40 once during each rotation in order to rotate the date indicator 40 by exactly one tooth. Thus, the calendar mechanism 16 rotates the date indicator 40 intermittently. The detailed configuration of the date indicator drive wheel 43 will be described later, together with the configuration of the regulator spring 44 of the date indicator drive wheel.
    The date jumper 45 corrects the position of the date indicator 40 in the rotational direction. A distal end 45a of the date jumper 45 is positioned inside the date indicator 40 according to a plan view and is pushed towards the date indicator 40 to be able to engage with the teeth 40b of the date indicator 40 The date jumper 45 corrects the rotation of the date indicator 40 by engaging the distal end 45a with the teeth 40b of the date indicator 40. Thus, the date indicator 40 can rotate by indexing from one step to the next. both in one day, at the same angular pitch as that of the plurality of teeth 40b.
    The time correction gear 17transmits the rotation of the adjustment rod 9des hands to the hour hand 5et to the minute hand 6 when correcting the time. The time correcting gear 17 comprises an adjusting wheel 50, an intermediate minute wheel 51, and a time correcting transmission wheel 52. The adjusting wheel 50 is arranged to mesh with a clock wheel. clutch (not shown) which rotates integrally with the needle adjustment rod 9. The intermediate minute wheel 51 meshes with the adjusting wheel 50. Accordingly, the first intermediate minute wheel 51 rotates on the basis of the rotation of the adjusting wheel 50. The hour correcting transmission wheel 52 is always meshed with the clock. Intermediate minute wheel 51 and rotates on the basis of the rotation of the intermediate minute wheel 51. The hour correcting transmission wheel 52 is arranged to mesh with the minute wheel 37.
    The calendar correction mechanism 18 transmits the rotation of the adjustment rod 9des needles to the date indicator 40 when correcting the date. The calendar correction mechanism 18 comprises a first date correction transmission wheel 53 and a second date correction transmission wheel 54 in addition to the adjustment wheel 50 and the intermediate minute wheel 51 described above. The first date correction transmission wheel 53 is arranged to mesh with the intermediate minute wheel 51. The first date correction transmission wheel 53 meshes with the intermediate minute wheel 51 to rotate based on the rotation of the wheel. intermediate minute 51. The second date correction transmission wheel 54 engages with the first date correction transmission wheel 53 and rotates on the basis of the first date correction transmission wheel 53. The second date correction transmission wheel date 54 is supported by a lever (not shown) which oscillates around the center of rotation of the first date correction transmission wheel 53 with the rotation of the first date correction transmission wheel 53. The second date correction transmission wheel date 54 is moved so as to approach the date indicator 40 when the first The first date correction transmission wheel 53 rotates in a predetermined direction, and meshes with the toothing 40b of the date indicator 40. Thus, the calendar correction mechanism 18 rotates with the date indicator 40.
    The date indicator drive wheel 43 and the date indicator drive wheel regulator spring 44 of the calendar mechanism 16 will be described in detail below.
    Figure 4 is a plan view of an essential part of the calendar mechanism according to the first embodiment seen from the rear of the movement. In addition, part of the date indicator drive wheel 43 is cut off and shown in the drawing of Fig. 4.
    As illustrated in Figure 4, the date indicator drive wheel 43 rotates in the direction of the arrow A illustrated in the drawing about an axis of rotation P extending in the up-down direction during of the normal operation of the hands of the movement 10. In the following, the peripheral direction around the axis of rotation P is simply called the peripheral direction and in the peripheral direction, the rotational direction of the date indicator drive wheel 43 during the normal operation of the hands is called the normal direction of rotation. The radial direction centered on the axis of rotation P is simply called the radial direction. The date indicator drive wheel 43 comprises: the date wheel mobile 60 which rotates once a day in synchronization with the rotation of the hour wheel 38; a date finger unit 70 rotatably disposed about the axis of rotation P with respect to the date mobile gear 60; and a date indicator actuating spring 90 (cf. FIG. 6) which applies a driving torque between the date gear mobile 60 and the date finger unit 70.
    FIG. 5 is a plan view of a date indicator drive wheel according to the first embodiment seen from below. Fig. 6 is a plan view of a date indicator drive wheel according to the first embodiment, viewed from above.
    As illustrated in Figures 5 and 6, the date gear mobile 60 comprises a main body 61de gear mobile which meshes with the second intermediate date wheel 42 (Figure 3) and a first elastic pin 62A, a second spring pin 62B and a regulating release pin 66 projecting upwardly from the gear movable main body 61. The main gear body 61 is rotatably disposed about the axis of rotation P. A through-hole through which a date pin 71 described later is inserted is formed in the center of the main body 61 of the gear set.
    [0063] FIG. 7 is a plan view of the date gear mobile and of the date indicator actuating spring according to the first embodiment in top view.
    As illustrated in Figure 7, the first elastic pin 62A and the second elastic pin 62B are supported by the main body 61de gear mobile respectively in eccentric positions relative to the axis of rotation P. The first pin elastic 62A and the second elastic pin 62B are arranged side by side in the peripheral direction around the axis of rotation P. The first elastic pin 62A is positioned in the normal direction of rotation relative to the second elastic pin 62B. In the present embodiment, the first spring pin 62A and the second spring pin 62B are identically formed and thus, when one of the first spring pin 62A and the second spring pin 62B is not specified, the first Spring pin 62A and the second spring pin 62B are simply called spring pin 62. Spring pin 62 is formed to have a circular cross section. The spring pin 62 comprises a portion having a columnar shape 63 protruding upwardly from the gear movable main body 61 and a flange 64 protruding outwardly from the portion having a columnar shape 63 in the radial direction from the portion. having a columnar shape 63. The columnar shape portion 63 has a constant outer diameter and extends in the up-down direction. The flange 64 is located at the upper end of the columnar shaped part 63. The flanges 64 are arranged at a distance from the upper surface of the main body 61 of the gear mobile.
    The release pins 66de regulation are arranged at a certain distance in the normal direction of rotation with respect to the first elastic pin 62A and to the second elastic pin 62B. The regulating release pin 66 includes a rod 67 attached to the movable gear main body 61 and a flange 68 projecting outwardly of the rod 67 in the radial direction from the rod 67. The lower end of the rod 67 is driven out. in the through hole formed in the main body 61de gear mobile. The flange 68 is disposed in the middle portion in the up-down direction in the shank 67. In other words, the upper end of the shank 67 protrudes upward from the flange 68. The flange portions 68 are arranged. at a distance from the upper surface of the main body 61 of the gear movable and are arranged so as to avoid interference with the actuating spring 90 of the date indicator.
    Figure 8 is a sectional view along the line VIII-VIII of Figure 6.
    As illustrated in Figures 5 and 8, the date finger unit 70 comprises the date axis 71, the date finger 75, a date finger spring 80, a plate 82 holding the finger and a plate 83 holding the spring .
    As illustrated in Figure 8, the date axis 71 comprises a central tube 72 disposed coaxially with the main body 61 of the date gear mobile 60 and a seat 73de finger projecting out of the central tube 72. The central tube 72 is inserted so as to keep a rotational degree of freedom in the through hole of the main body 61 of the gear movable. The central tube 72 protrudes from both the upper side and the lower side with respect to the main body 61 of the gear mobile. The finger seat 73 is arranged to overlap the lower surface of the gear movable main body 61. The finger seat 73 has an annular shape which protrudes outward in the radial direction from the central tube 72 and extends all the way around in the peripheral direction.
    As illustrated in Figure 5, the date finger 75est arranged to overlap the seat 73de finger in a plan view. The date finger 75 is rotatably supported by the finger seat 73 in the intermediate portion in the peripheral direction around the axis of rotation P. In particular, the date finger 75 is rotatably supported by a pin which projects towards down from the finger seat 73. Date finger 75 comprises a finger main body 76 which extends in the normal direction of rotation from the center of rotation and an arm 77 which extends in a direction opposite to the normal direction of rotation from the center of rotation. The arm 77 is formed so as to be able to come into contact with the outer peripheral surface of the central tube 72 of the date axis 71. A distal end 76a of the main body 76 of the finger is formed so as to be able to protrude towards the end. exterior in the radial direction from the finger seat 73 in a plan view. The state in which the distal end 76a of the finger main body 76 protrudes most from the finger seat 73 is the state in which the arm 77 is in contact with the outer peripheral surface of the central tube 72 of the date axis. 71. In other words, the arm 77 regulates the protrusion distance of the finger main body 76 from the finger seat 73.
    The main finger body 76 is arranged in a position in which the distal end 76a can come into contact with the toothing 40b of the date indicator 40 when the date finger unit 70 rotates in the normal direction of rotation ( see also figure 4). When the date finger unit 70 rotates in the opposite direction to the normal direction of rotation, the part positioned in the direction opposite to the normal direction of rotation from the distal end 76a contacts the toothing 40b of the indicator. date 40, and correspondingly, the main finger body 76 is moved inwardly in the radial direction.
    The date finger spring 80 pushes the date finger 75. The date finger spring 80 is arranged to overlap the finger seat 73 in a plan view. The date finger spring 80 includes a base portion 80a fixedly supported by the finger seat 73 and a spring body 80b which extends from the base portion 80a in the normal direction of rotation of the wheel. date indicator drive 43 and comes into contact with the date finger arm 77 75. The base portion 80a is supported by a pin which projects downward from the finger seat 73. The spring body 80b is brought into contact with the arm 77 of the date finger 75 via the outside in the radial direction. The spring body 80b compresses the arm 77 inwardly in the radial direction via an elastic deformation restoring force. Correspondingly, the date finger 75 is pushed in a direction in which the arm 77 comes into contact with the outer peripheral surface of the central tube 72 of the date axis 71. In other words, the date finger 75 is pushed into the middle. direction in which the distal end 76a of the finger main body 76 projects outwardly in the radial direction from the finger seat 73 in a plan view.
    The plate 82 now the finger limits the downward movement of the date finger 75 and of the spring 80 of the date finger. The plate 82 now the finger is arranged on the side opposite to the seat 73de finger across the date finger 75 and the spring 80de date finger. The pad 82 holding the finger has a disc shape having substantially the same diameter as the outer diameter of the finger seat 73 and is arranged coaxially with the finger seat 73. A through-hole, in which the lower end of the central tube 72 of the date axis 71 is inserted, is formed in the center of the plate 82 holding the finger. The plate 82 now the finger has a through hole to avoid each pin which supports the date finger 75 and the spring 80 of the date finger. The plate 82 now the finger is arranged in a fixed manner with respect to the date axis 71.
    As illustrated in Figure 6, the plate 83maintaining the spring maintains the actuating spring 90d'indicator date between the plate 83maintaining the spring and the main body 61du date gear wheel 60. The plate 83maintaining the spring is arranged above the main body 61 of the date mobile gear 60. The plate 83 now has the spring has a disc shape having a diameter smaller than that of the main body 61 of the date mobile gear 60 and is arranged coaxially with the spring. main body 61 of the mobile date gear 60. A through hole in which the upper end of the central tube 72 of the date axis 71 is inserted is arranged in the center of the plate 83 holding the spring. The plate 83 now the spring is arranged in a fixed manner with respect to the date axis 71.
    The plate 83maintain the spring is provided with a guide hole 84de pin and an engagement part 85 with the regulating spring. The upper end of the rod 67 of the regulating release pin 66 in the date gear mobile 60 is inserted into the guide hole 84 of the pin. The pin guide hole 84 extends in an arc shape around the axis of rotation P so as to allow movement of the regulating release pin 66 about the axis of rotation P. The guide hole 84 of pin comprises a downstream end 84a disposed in the normal direction of rotation and an upstream end 84b disposed in the direction opposite to the normal direction of rotation of the date indicator drive wheel 43. The upper end of the rod 67 of the regulating release pin 66 is positioned at the upstream end 84b of the guide pin hole 84. The engaging portion 85 of the regulator spring is a notch formed on the outer peripheral surface of the pad 83 holding the spring. The engaging portion 85 of the regulator spring is formed near the downstream end 84a of the pin guide hole 84. The regulating spring engaging portion 85 includes a spring engaging surface 85a oriented in the normal direction of rotation of the date indicator drive wheel 43. The spring engagement surface 85a is located in a position which overlaps the flange 68 of the regulating release pin 66 in a plan view, in a state in which the upper end of the rod 67 of the regulating release pin 66 is. positioned at the downstream end 84a of the pin guide hole 84.
    As illustrated in Figures 6 and 8, the date indicator actuating spring 90 is arranged between the main body 61 of the date gear mobile 60 and the plate 83 maintaining the spring of the date finger unit 70. The date indicator actuating spring 90 is a spiral spring made of a metal such as iron or nickel or a non-metal such as silicon. The date indicator actuating spring 90 is wound by relative rotation of the outer end and the inner end and by winding and fixing the outer end and the inner end so as to reduce the diameter. The wound date indicator actuating spring 90 elastically deforms to generate torque between the outer end and the inner end. In the following description of the shape of the date indicator operating spring 90, unless otherwise indicated, it is assumed that the amount of winding of the date indicator operating spring 90 is the smallest among all the states of the date indicator. date indicator drive wheel 43 when the movement 10 operates.
    As illustrated in Figure 7, the date indicator actuating spring 90 comprises a spring main body 91 extending in a spiral shape, an attachment portion 92 positioned at the inner end and a portion engagement 93 positioned at the outer end. The main spring body 91 extends in a spiral shape with constant width in plan view. In particular, the main spring body 91 extends along an Archimedean curve centered on the axis of rotation P. The main spring body 91 extends in the normal direction of rotation from the fixing portion 92 towards the axis. engagement party 93.
    The fixing portion 92est molded integrally with the inner end which is a peripheral end of the main body 91de spring. The fixing portion 92 has an annular shape and is arranged coaxially with the axis of rotation P. The fixing portion 92 is fixed to the date finger unit 70 (cf. FIG. 6). In particular, the fixing portion 92 is extrapolated towards the central tube 72 of the date axis 71 and is supported in a fixed manner by the date axis 71 (cf. FIG. 8).
    The engagement portion 93 is integrally molded with an outer end 91a which is the other peripheral end of the main body 91de spring. In other words, the connecting part between the engaging part 93 and the main spring body 91 has continuity. The engaging portion 93 is arranged on the outer side of the outer peripheral portion of the spring main body 91 in the radial direction at a distance in the peripheral direction from the release pin 66 for regulating. The engagement portions 93 are arranged at a distance in the radial direction from the main spring body 91. The engaging portion 93 extends in the normal direction of rotation from the outer end 91a of the spring main body 91 with a constant thickness with respect to the up-down direction as the thickness direction. The engagement part 93is in engagement with the date mobile gear 60 in at least two points. In particular, the engagement part 93 is engaged with the first elastic pin 62A and the second elastic pin 62B of the date gear mobile 60. The displacement of the engagement part 93 in the direction opposite to the normal direction of rotation by relative to the date mobile gear 60 is regulated.
    The engagement structure between the engagement part 93 and the date mobile gear 60 now described in detail in the following. The engaging portion 93 has a pair of through holes 94A and 94B into which the first spring pin 62A and the second spring pin 62B are inserted one by one from below. The pair of through holes 94A and 94B consists of a first through hole 94A in which the columnar shaped portion 63 of the first spring pin 62A is positioned and a second through hole 94B in which the column shaped portion 63of the second elastic pin 62B is positioned. The first through hole 94A is arranged in the normal direction of rotation with respect to the second through hole 94B. Since the first through hole 94A and the second through hole 94B are formed identically, when a hole among the first through hole 94A and the second through hole 94B is not specified, the first through hole 94A and the second through hole 94B are simply referred to as through hole 94.
    [0080] The through-hole 94 comprises a narrow portion 94a in which the columnar-shaped portion 63 of the elastic pin 62 is positioned and a wide portion 94b which is connected to the narrow portion 94a in the peripheral direction and which has a wider shape. in the radial direction than the narrow portion 94a. The width of the narrow portion 94a in the radial direction is equivalent to the outer diameter of the columnar-shaped portion 63 of the spring pin 62. The narrow portion 94a maintains the columnar-shaped portion 63 of the elastic pin 62 at the level of the spring pin 62. end in the normal direction of rotation. The wide portion 94b is connected to the end of the narrow portion 94a in the direction opposite to the normal direction of rotation. The wide portion 94b is made wider than the spring pin 62 in a plan view. In the present embodiment, the wide portion 94b has a circular shape having a diameter larger than that of the collar 64 of the elastic pin 62 in a plan view. Accordingly, the wide portion 94b allows the passage of the collar 64 of the elastic pin 62 in the up-down direction. The engagement portion 93 slidably moves with respect to the date gear mobile 60 in the direction opposite to the normal direction of rotation in a state in which the spring pin 62 is inserted into the wide portion 94b of the through-hole 94 and by the positioning of the spring pin 62. with the spring pin 62 at the end in the normal direction of rotation in the narrow portion 94a of the through hole 94, the engaging portion 93 is engaged with the spring pin 62. The lower surface of the flange 64 of the spring pin 62 is opposite to the upper surface of the engaging portion 93. Thus, the upward movement of the engaging portion 93 is limited by the flange 64 of the spring pin 62.
    The date indicator actuating spring 90 is wound or respectively armed following the displacement of the engagement part 93 in the normal direction of rotation of the date indicator drive wheel 43 with respect to the portion of fixing 92and generates the torque in the normal direction of rotation in the fixing portion 92. In this way, the date indicator actuating spring 90 pushes the date finger unit 70 in the normal direction of rotation.
    As illustrated in Figure 4, the regulator spring 44de date indicator drive wheel has the shape of a beam and is arranged in cantilever. The base end of the regulator spring 44 of the date indicator drive wheel is fixedly disposed on the plate 11 or the like. A distal end 44a of the date indicator drive wheel regulator spring 44 is slidably disposed on the outer peripheral surface of the pad 83 holding the spring. The distal end 44a of the regulator spring 44 of the date indicator drive wheel is oriented in the direction opposite to the normal direction of rotation. The distal end 44a of the date indicator drive wheel regulator spring 44 engages the engaging surface 85a with the spring of the engaging portion 85 with the spring of the plate 83 holding the spring. The regulator spring 44 of the date indicator drive wheel is formed such that the flange 68 of the regulating release pin 66 of the date movable wheel 60 can come into contact with the distal end 44a in a state that the distal end 44a engages the engaging portion 85 with the regulator spring of the pad 83 holding the spring.
    (Operation of the calendar mechanism)
    In the following, the operation of the calendar mechanism 16conceived as described above will be described with reference to FIGS. 4 and 9 to 11.
    Figures 9 to 11 are explanatory views of the operation of the calendar mechanism and are plan views of part of the calendar mechanism seen from below.
    As described above, the date mobile gear 60 of the date indicator drive wheel 43 rotates once a day in the normal direction of rotation in synchronization with the rotation of the hour wheel 38. When the date mobile gear 60 rotates in the normal direction of rotation, the rotational force is transmitted to the date finger unit 70 via the date indicator actuating spring 90 and, accordingly, the date indicator unit 70. date finger also rotates in the normal direction of rotation.
    As illustrated in Figure 4, as the date finger unit 70 rotates, the distal end 44a of the regulator spring 44 of the date indicator drive wheel is engaged with the engagement portion 85 of the regulating spring of the plate 83 maintaining the spring in an indexed increment position for each rotation. Thus, a state is employed in which the rotation of the date finger unit 70 is regulated in the normal direction of rotation. Consequently, the date mobile gear 60 rotates in the normal direction of rotation with respect to the date finger unit 70. At this time, the date gear mobile 60 rotates while moving the rod 67 of the regulating release pin 66 in the normal direction of rotation from the proximity of the upstream end 84b of the guide hole 84 of the pin. of the date finger unit 70 (see also FIG. 6). The date mobile gear 60 rotates in the normal direction of rotation while winding the actuating spring 90 of the date indicator. Therefore, the date indicator operating spring 90 is wound while increasing the torque to urge the date finger unit 70 in the normal direction of rotation.
    As illustrated in FIG. 9, when the rotation of the date mobile gear 60 evolves further, the rod 67 of the regulating release pin 66 reaches the proximity of the downstream end 84a (cf. FIG. 6) of the hole. pin guide 84. Then, the flange 68 of the regulator release pin 66 contacts the distal end 44a of the regulator spring 44 of the date indicator drive wheel and presses the distal end 44a of the regulator spring 44 of the date indicator drive wheel. date indicator outward in the radial direction. The engagement between the date indicator drive wheel regulator spring 44 and the engagement portion 85 with the pad regulator spring 83 now released the spring. At midnight, at the time at which the engagement between the regulator spring 44 of the date indicator drive wheel and the engagement part 85 with the regulator spring of the plate 83, maintaining the spring is released, the indicator of the timepiece 1 indicates approximately midnight.
    Thus, the actuating spring 90d'indicator of the date which has been armed by winding on itself suddenly disarms and the date finger unit 70 rotates rapidly in the normal direction of rotation. As illustrated in Fig. 10, the main body 76 of the date finger 75 moves rapidly in the normal direction of rotation and the distal end 76a can contact the teeth 40b of the date indicator 40 and rotate the indicator. date 40. Thus, the date indicator 40 can be rotated instantaneously while the engagement while the engagement with the date jumper 45 is released.
    As illustrated in FIG. 11, when the date indicator 40 rotates, the distal end 45a of the date jumper 45 is again engaged with the following toothing 40b of the date indicator 40. Accordingly, the position of the date indicator 40 in the rotational direction is again corrected. Therefore, the date specified in the date window 3a of the dial 3 can be instantly advanced by one unit corresponding to one day.
    (Action of the date indicator actuating spring)
    [0090] Below, the action of the actuating spring 90 of the date indicator of the present embodiment will be described with reference to FIG. 12.
    FIG. 12 is a plan view of an essential part of the date indicator actuating spring according to the first embodiment in top view.
    As illustrated in FIG. 12, when the date indicator actuating spring 90 is armed, that is to say wound up by the date gear mobile 60, the engagement part 93 is pulled in the direction normal rotation by the spring pin 62 and rotates in the normal direction of rotation with respect to the fixing portion 92. Therefore, when the date indicator operating spring 90 is wound up, the urging force of the spring main body 91 acts on the engagement part 93 in the opposite direction to the normal direction of rotation. Further, when the date indicator operating spring 90 is wound up, the spring main body 91 is wound on itself and fixed so as to reduce the diameter, and thus the pushing force of the spring main body 91 acts. on the engaging portion 93 inwardly in the radial direction. Thus, an inward force acts on the engaging portion 93 in the direction opposite to the normal direction of rotation and in the radial direction in a state in which the date indicator operating spring 90 is wound. The engagement part 93 is in contact with the elastic pins 62A and 62B of the date mobile gear 60 at the level of a first contact portion 95 and of a second contact portion 96.
    The first contact portion 95est a part in which the engagement part 93 comes into contact with the date mobile gear 60 by the fact of being pulled in the direction opposite to the normal direction of rotation. In the present embodiment, the first contact portion 95 is positioned on the inner surface defining the first through hole 94A and is in contact with the first spring pin 62A. For example, the first contact portion 95 is a portion on the inner surface defining the first through hole 94A where the surface pressure due to contact with the first spring pin 62A takes an extreme value (the same applies to the other portions as well. contact details described below). The first contact portion 95 is oriented in a direction inclined in the direction opposite to the normal direction of rotation with respect to the radial direction in a plan view. In other words, a first normal vector V1 at the level of the first contact portion 95 points in a direction which deviates from the axis of rotation P (cf. FIG. 7) according to a plan view in a direction opposite to the direction. normal rotation. Thus, the engagement portion 93 exerts a tensile force by the main spring body 91 in the direction opposite to the normal direction of rotation on the first elastic pin 62A at the first contact portion 95, and restricts any displacement in the direction opposite to the direction of rotation. normal direction of rotation thanks to the resistance force.
    The second contact portion 96 is a part in which the engagement part 93 comes into contact with the date mobile gear 60 by being pulled inward in the radial direction. In the present embodiment, the second contact portion 96 is positioned on the inner surface defining the second through hole 94B and is in contact with the second spring pin 62B. A second normal vector V2 at the second contact portion 96 points in a direction away from the first contact portion 95 in a plan view. Thus, the engaging portion 93 exerts a force to rotate around the first contact portion 95 on the second resilient pin 62B at the second contact portion 96, and the rotation is limited by the resistance force.
    According to the present embodiment, the first contact portion 95 is positioned on the inner surface of the first through hole 94A and the second contact portion 96 is positioned on the inner surface of the second through hole 94B, but the present invention does not apply. do not limit it. For example, the first contact portion may be positioned on the inner surface of the second through hole 94B and the second contact portion may be positioned on the inner surface of the first through hole 94A. In other words, depending on the relation between the actual size of the relative positions of the first through hole 94A and the second through hole 94B and the actual size of the relative positions of the first spring pin 62A and the second spring pin 62B, it is determined that the first contact portion is positioned at any one of the first through hole 94A and the second through hole 94B. In all cases, the second normal vector at the second contact portion may point in a direction which deviates from the first contact portion in a plan view.
    As described above, the date indicator actuating spring 90 of the present embodiment is integrally molded with the outer end 91a of the main spring body 91 and includes the engagement portion 93 which engages the date gear mobile 60 in two points. According to this configuration, the rotation of the engagement part 93 with respect to the date mobile gear 60 can be suppressed. Therefore, even if the date indicator operating spring 90 is wound up and the force in the radial direction as well as the force in the peripheral direction act on the engaging portion 93, any unintentional deformation of the spring of the date indicator is wound. 90th actuation of the date indicator can be omitted. Therefore, the mutual contact between turns due to winding and fixing of the date indicator operating spring 90 can be avoided. Accordingly, any reduction in the torque generated by the date indicator operating spring 90 due to frictional forces accompanying the contact of the date indicator operating spring 90 in a state in which it is wound can be avoided. Therefore, the date indicator actuating spring 90 can generate a desired torque.
    The engagement part 93 has the first contact portion 95 and the second contact portion 96 which come into contact with the date gear mobile 60. The first normal vector V1 at the level of the first contact portion 95 points in one direction which deviates from the axis of rotation P in a plan view. A second normal vector V2 at the second contact portion 96 points in a direction away from the first contact portion 95 in a plan view. According to this configuration, the displacement of the engaging portion 93 due to the force in the peripheral direction acting on the engaging portion 93 can be regulated at the first contact portion 95. Further, the rotation of the portion of the device. engagement 93 centered on the first contact portion 95 due to the force in the radial direction acting on the engagement portion 93 can be regulated at the second contact portion 96. Thus, any rotation of the engagement portion 93 with respect to the mobile. date gear 60 is prevented and thus, the effect described above can be obtained.
    The engagement part 93possède a pair of through holes 94A and 94B in which a pair of elastic pins 62A and 62B arranged on the date mobile gear 60 are arranged one by one. According to this configuration, the engagement part 93 and the date gear mobile 60 are in mutual engagement at two points by a contact between the first elastic pin 62A and the internal surface of the first through hole 94A and by the contact between the second spring pin 62B and the inner surface of the second through hole 94B. Therefore, the effect described above can be obtained.
    The through hole 94 comprises the narrow portion 94a in which the elastic pin 62 is arranged and the wide portion 94b which is connected to the narrow portion 94a in the peripheral direction and which has a wider shape in the radial direction than the narrow portion. 94a. According to this configuration, by moving the elastic pin 62 provided with the collar 64 towards the narrow portion 94a after the insertion of the elastic pin 62 in the wide portion 94b, the elastic pin 62 can be arranged in the narrow portion 94a. Therefore, the elastic pin 62 provided with the flange 64 can engage with the engaging part 93 to suppress the fact that the elastic pin 62 comes out of the through hole 94. Therefore, the engaging part 93 and the date gear mobile. 60 can reliably engage each other.
    [0100] Since the calendar mechanism 16 of the present embodiment comprises the actuating spring 90d'indiceur de date which generates the desired torque, any insufficient torque applied between the mobile date gear 60 and the unit 70de date finger can be omitted. Thus, the insufficiency of the rotational force transmitted to the date indicator 40 due to insufficient torque applied to the date finger unit 70 can be eliminated. Therefore, a calendar mechanism 16 in which a reliable date advancing operation is possible can be employed.
    [0101] Since the timepiece 1 and the movement 10 of the present embodiment comprise the calendar mechanism 16 described above, a movement and a timepiece, in which the date advancing operation is stabilized. and a very precise schedule are included, can be obtained.
    [0102] According to the present embodiment, the date indicator 40 displays the number corresponding to the date as a date value 40a, but the present invention is not limited to such a configuration. In the date indicator 40, the day of the week could be displayed as the date value.
    (First variant of the first embodiment)
    [0103] FIG. 13 is a plan view of the date gear mobile and of the date indicator actuating spring according to a first variant of the first embodiment in top view.
    [0104] In the first embodiment, the elastic pin 62 has a flange 64 of the part having a column shape 63 projecting outwardly in the radial direction from the part having a column shape 63. On the other hand, the part having a column shape 63 first variant of the first embodiment is different from the first embodiment in that the elastic pin 162 does not have a collar. In addition, the configuration other than that described below is the same as that of the first embodiment.
    [0105] As illustrated in FIG. 13, the date mobile gear 60 comprises a first elastic pin 162A and a second elastic pin 162B, instead of the first elastic pin 62A and the second elastic pin 62B of the first embodiment. . In the present embodiment, the first spring pin 162A and the second spring pin 162B are identically formed and thus, when one of the first spring pin 162A and the second spring pin 162B is not specified, the first Spring pin 162A and the second spring pin 162B are simply referred to as spring pin 162. Spring pin 162 has a circular cross section. The spring pin 162 includes a columnar shaped portion 163 which protrudes upward from the gear movable main body 61. The spring pin 162 is formed so that the part above that having a column shape 163 has the same diameter as that of the part having a column shape 163 or a smaller diameter than the part having a column shape. column 163.
    [0106] An engaging portion 93A is formed with a pair of through holes 104A and 104B into which the first spring pin 162A and the second spring pin 162B are inserted one by one from below. The pair of through-holes 104A and 104B are made up of a first through-hole 104A in which the column-shaped portion 163 of the first spring pin 162A is positioned and a second through-hole 104B in which the column-shaped portion 163 of the second elastic pin 162B is positioned. A first spring pin 162A is fitted into the first through hole 104A. The first through hole 104A is larger in shape than the second spring pin 162B in a plan view and extends uniformly in the up and down direction. In particular, the first through hole 104A has an oval shape (rounded rectangular shape). The first through hole 104A is formed such that its longitudinal axis extends in the peripheral direction. The small diameter of the first through hole 104A is approximately the same as the outer diameter of the columnar shaped portion 163 of the first spring pin 162A. The columnar-shaped portion 163of the first spring pin 162A is positioned separately from the two ends in the longitudinal direction of the first through hole 104A. The second spring pin 162B is fitted into the second through hole 104B. The second through-hole 104B is circular in shape in a plan view and extends in the up-down direction with a constant internal diameter. The inner diameter of the second through hole 104B is approximately the same as the outer diameter of the columnar shaped portion 163 of the second spring pin 162B.
    [0107] Below, the action of the date indicator actuating spring 90 of the present variant will be described with reference to FIG. 14.
    [0108] FIG. 14 is a plan view of an essential part of the date indicator actuating spring according to the first variant of the first embodiment in top view.
    [0109] As illustrated in FIG. 14, when the date indicator actuating spring 90 is wound up, the engagement part 93A comes into contact with the elastic pins 162A and 162B of the date mobile gear 60 at the level of 'a first contact portion 95A and a second contact portion 96A.
    [0110] The first contact portion 95A is a part in which the engagement part 93A comes into contact with the date mobile gear 60 by being pulled in the direction opposite to the normal direction of rotation. The first contact portion 95A is positioned on the inner surface defining the second through hole 104B and is in contact with the second spring pin 162B. The first normal vector V1 at the level of the first contact portion 95A points in a direction which deviates from the axis of rotation P (cf. FIG. 13) in a plan view in the direction opposite to the normal direction of rotation. Thus, the engaging portion 93A exerts a tensile force by the spring main body 91 in the direction opposite to the normal direction of rotation on the second spring pin 162B at the first contact portion 95A and prevents movement in the direction. opposite to the normal direction of rotation thanks to the resistance force.
    [0111] The second contact portion 96A is a part in which the engagement part 93A comes into contact with the date gear mobile 60 by being pulled inward in the radial direction. The second contact portion 96A is positioned on the inner surface defining the first through hole 104A and is in contact with the first spring pin 162A. The second normal vector V2 at the second contact portion 96A points in a direction away from the first contact portion 95A in a plan view. Thus, the engaging portion 93A exerts a force to rotate around the first contact portion 95A on the first spring pin 162A at the second contact portion 96A, and the rotation is prevented by the resistance force.
    [0112] As described above, given that the date indicator actuating spring 90 of the present variant comprises an engagement part 93A in engagement with the date mobile gear 60 at two points, it is possible to can achieve the same effect as that of the first embodiment.
    [0113] Further, the first through hole 104A is configured to have a shape larger than the first elastic pin 162A in plan view. According to this configuration, even when the first spring pin 162A is moved relative to the first through hole 104A due to a manufacturing error, the first spring pin 162A can be arranged in the first through hole 104A.
    [0114] In the present variant, the engagement portion 93A is formed with the first through hole 104A and the second through hole 104B in which the spring pin 162 is inserted, but the engagement portion may be formed with the recess in which the elastic pin 162 is inserted, instead of the through hole. In the present variant, among the first through hole 104A and the second through hole 104B, the first through hole 104A positioned in the normal direction of rotation is an elongated hole, but the first through hole 104A is not limited to this configuration. In other words, among the first through hole and the second through hole, the second through hole positioned in the direction opposite to the normal direction of rotation can be an elongated hole.
    (Second variant of the first embodiment)
    [0115] FIG. 15 is a plan view of the date gear mobile and of the date indicator actuating spring according to a second variant of the first embodiment in top view.
    [0116] In the first embodiment, the through hole 94 in which the elastic pin 62 is inserted is formed in the engagement part 93. On the other hand, the second variant of the first embodiment is different from the first embodiment in that that a slot 114 in which the elastic pin 62 is inserted is provided in the engagement portion 93B. In addition, the configuration other than that described below is the same as that of the first embodiment.
    [0117] As illustrated in Fig. 15, the engaging portion 93B is has a pair of slots 114A and 114B for receiving the first spring pin 62A and the second spring pin 62B. The pair of slits 114A and 114B pass through the engagement portion 93B in the up-down direction and are open to the side surface of the engagement portion 93B. The pair of slots 114A and 114B consists of a first slot 114A in which the columnar-shaped portion 63 of the first spring pin 62A is positioned and a second slot 114B in which the columnar-shaped portion 63 of the second pin elastic 62B is positioned. The first slot 114A is arranged in the normal direction of rotation with respect to the second slot 114B. Since the first slit 114A and the second slit 114B are identically formed, when a slit among the first slit 114A and the second slit 114B is not specified, the first slit 114A and the second slit 114B are simply referred to as slot 114.
    [0118] The slot 114 is formed so that the columnar shaped portion 63 of the spring pin 62 can pass through the entire length. The slot 114 extends with a width similar to the outer diameter of the columnar shaped portion 63 of the spring pin 62 in a plan view. The slot 114 includes a first extension portion 114a in which the columnar shaped portion 63 of the spring pin 62 is positioned and which extends in the peripheral direction and a second extension portion 114b which is connected to the first portion d. extension 114a, which extends in the radial direction and which is open to the side surface of the engagement portion 93B. The second extension portion 114b is connected to a part of the first extension portion 114a in the direction opposite to the normal direction of rotation from the end in the normal direction of rotation. In the present variant, the second extension portion 114b is connected to the end of the first extension portion 114a in the direction opposite to the normal direction of rotation. The second extension portion 114b extends inwardly in the radial direction from the first extension portion 114a. During the assembly of the actuating spring 90 of the date indicator to the date gear mobile 60, by the sliding movement of the engagement part 93B relative to the date gear mobile 60 and by the passage of the elastic pin 62 through the second extension portion 114b and by positioning the elastic pin 62 at the end in the normal direction of rotation in the first extension portion 114a, the engaging portion 93B engages the elastic pin 62.
    Next, the action of the actuating spring 90 of the date indicator of the present variant will be described with reference to FIG. 16.
    [0120] FIG. 16 is a plan view of an essential part of the date indicator actuating spring according to the second variant of the first embodiment, seen from above.
    [0121] As illustrated in FIG. 16, when the date indicator actuating spring 90 is wound on itself and thus armed, the engagement part 93B comes into contact with the elastic pins 62A and 62B of the mobile d date gear 60 at the first contact portion 95B and the second contact portion 96B.
    [0122] The first contact portion 95B is a part in which the engagement part 93B comes into contact with the date mobile gear 60 by being pulled in the direction opposite to the normal direction of rotation. The first contact portion 95B is positioned on the inner surface defining the first slot 114A and is in contact with the first spring pin 62A. The first normal vector V1 at the level of the first contact portion 95B points in a direction which deviates from the axis of rotation P (cf. FIG. 15) in a plan view in the direction opposite to the normal direction of rotation. Thus, the engagement portion 93B exerts a tensile force by the spring main body 91 in the direction opposite to the normal direction of rotation on the first spring pin 62A at the first contact portion 95B and prevents displacement in the direction. opposite to the normal direction of rotation via this resistance force.
    [0123] The second contact portion 96B is a part in which the engagement part 93B comes into contact with the date mobile gear 60 by being pulled inwards in the radial direction. The second contact portion 96B is positioned on the inner surface defining the second slot 114B and is in contact with the second elastic pin 62B. The second normal vector V2 at the second contact portion 96B points in a direction which deviates from the first contact portion 95B in plan view. Accordingly, the engaging portion 93B exerts a force to rotate around the first contact portion 95B on the second spring pin 62B at the second contact portion 96B, and the rotation is regulated by the resistance force.
    In the present variant, the first contact portion 95B is positioned in the first slot 114A and the second contact portion 96B is positioned in the second slot 114B, but the present invention is not limited to this configuration. Similar to the first embodiment, for example, the first contact portion may be positioned in the second slot 114B and the second contact portion may be positioned in the first slot 114A.
    [0125] As described above, given that the date indicator actuating spring 90 of the present variant comprises the engagement part 93B in engagement with the date mobile gear 60 at two points, it is possible to can achieve the same effect as that of the first embodiment.
    [0126] In addition, the slot 114 comprises a first extension portion 114a in which the elastic pin 62 is arranged and which extends in the peripheral direction and a second extension portion 114b which is connected to the first extension portion. 114a, which extends in the radial direction and which is open towards the side surface of the engagement portion 93B. According to this configuration, so that the elastic pin 62 positioned at the first extension portion 114a reaches the opening on the side surface of the engaging portion 93B, after the elastic pin 62 has moved in the peripheral direction with respect to the engagement portion 93B, a displacement in the radial direction is required. Thus, the fact that the spring pin 62 exits the slot 114 can be omitted from the configuration in which the slot extends linearly in a plan view. Therefore, the engaging part 93B and the date gear mobile 60 can reliably engage with each other.
    [0127] In addition, according to the present variant, since the elastic pin 62 is provided with the collar 64, even when the width of the slot 114 is smaller than the outer diameter of the collar 64, the elastic pin 62 can be inserted into it. the slot 114from the opening on the side surface of the engagement portion 93B. Thus, by engaging the spring pin 62 provided with the flange 64 with the engaging portion 93B, the fact that the spring pin 62 exiting the slot 114 can be omitted. Therefore, the engaging portion 93B and the date gear mobile 60 can reliably engage with each other.
    [0128] In the present variant, the engagement portion 93B has the slot 114, but the engagement portion may have a groove-shaped recess which does not pass through the engagement portion instead of the slot. In this case, it is desirable that the date mobile gear 60 is provided with the elastic pin 162 not having a collar, instead of the elastic pin 62.
    [Third variant of the first embodiment]
    [0129] FIG. 17 is a plan view of the date gear mobile and of the date indicator actuating spring according to a third variant of the first embodiment in top view.
    [0130] In the first embodiment, the part having a columnar shape 63 of the first elastic pin 62A is positioned in the first through hole 94A of the engagement part 93. In contrast, the third variant of the first embodiment is different from the first embodiment in that the columnar-shaped part 63of the first elastic pin 62A is arranged on the side of an engaging part 93C. In addition, the configuration other than that described below is the same as that of the first embodiment.
    [0131] As illustrated in FIG. 17, the date mobile gear 60 comprises the first elastic pin 62A and the second elastic pin 162B. The second spring pin 162B is inserted into the engaging portion 93C from below, and a second through hole 104B, in which the columnar shaped portion 163 of the second spring pin 162B is positioned, is formed. The end of the engaging part 93C in the normal direction of rotation is arranged inside the columnar-shaped part 63 of the first spring pin 62A in the radial direction. The side surface 93a of the end of the engaging part 93C in the normal direction of rotation is arranged to contact the column-shaped part 63 of the first spring pin 62A from the inside according to the radial direction. The lower surface of the flange 64 of the first spring pin 62A is opposed to the upper surface of the engaging portion 93C. Thus, the upward movement of the engaging portion 93C is prevented by the flange 64 of the spring pin 62A.
    In what follows, the action of the date indicator actuating spring 90 of the present variant will be described with reference to FIG. 18.
    [0133] FIG. 18 is a plan view of a main part of the date indicator actuating spring according to the third variant of the first embodiment, seen from above.
    [0134] As illustrated in FIG. 18, when the date indicator actuating spring 90 is wound up, the engagement part 93C comes into contact with the elastic pins 62A and 162B of the date mobile gear 60 at level d. 'a first contact portion 95C and a second contact portion 96C.
    [0135] The first contact portion 95C is a part in which the engagement part 93C is brought into contact with the date gear mobile 60 after having been pulled in the direction opposite to the normal direction of rotation. The first contact portion 95C is positioned in the second through hole 104B and is in contact with the second elastic pin 162B. The first normal vector V1 at the level of the first contact portion 95C points in a direction which deviates from the axis of rotation P (cf. FIG. 17) in a plan view in the direction opposite to the normal direction of rotation. Thus, the engagement portion 93C exerts a tensile force by the spring main body 91 in the direction opposite to the normal direction of rotation on the second elastic pin 162B at the first contact portion 95C and prevents movement in the direction. opposite to the normal direction of rotation via the resistance force.
    [0136] The second contact portion 96C is a part in which the engagement part 93C comes into contact with the date mobile gear 60 by being pulled inwards in the radial direction. The second contact portion 96C is positioned on the side surface 93a of the end in the normal direction of rotation of the engagement portion 93C and is in contact with the first spring pin 62A. The second normal vector V2 at the second contact portion 96C points in a direction which deviates from the first contact portion 95C in a plan view. Thus, the engaging portion 93C exerts a force to rotate around the first contact portion 95C on the first spring pin 62A at the second contact portion 96C, and the rotation is prevented by the resistance force.
    [0137] As described above, given that the date indicator actuating spring 90 of the present variant comprises the engagement part 93C in engagement with the date mobile gear 60 at two points, it is possible to can achieve the same advantageous technical effect as that of the first embodiment.
    [0138] Further, the side surface 93a of the engagement portion 93C is made so as to be in contact with the first elastic pin 62A. According to this configuration, the engagement part 93C and the date gear mobile 60 are engaged with each other at two points by the contact between the second elastic pin 162B and the internal surface of the second through hole. 104B and by the contact between the first elastic pin 62A and the side surface 93a of the engaging portion 93C. Therefore, the advantageous technical effect described above can be obtained.
    [0139] In addition, compared to the configuration in which the first elastic pin 62A is arranged in the recess, such as a through hole formed in the engaging part, it is possible to employ a configuration in which a deflection positional due to a manufacturing error of the first spring pin 62A relative to the second spring pin 162B is allowed. In addition, the area of the engaging portion 93C can be reduced in plan view compared to a configuration in which the recess such as a through hole is formed in the engaging portion. Thus, space savings for the engagement part 93C can be achieved.
    [Fourth variant of the first embodiment]
    [0140] FIG. 19 is a plan view of the date gear mobile and of the date indicator actuating spring according to a fourth variant of the first embodiment seen from above.
    [0141] In the first variant of the first embodiment, the first through hole 104A and the second through hole 104B are formed in the engagement portion 93A. On the other hand, the fourth variation of the first embodiment is different from the first embodiment in that a single through hole 124 is formed in an engagement portion 93D. In addition, the remaining configuration according to this variant and which is not described below is identical to that of the first variant of the first embodiment.
    [0142] As illustrated in Fig. 19, the engaging portion 93D has a through hole 124 in which the first spring pin 162A and the second spring pin 162B are inserted from below. Each of the first spring pin 162A and the second spring pin 162B is fitted into the through hole 124. The through hole 124 has a non-circular shape in plan view and extends uniformly in the up and down direction. In particular, the through hole 124 has an oval shape (rounded rectangular shape) in plan view. The through hole 124 is formed such that its longitudinal axis extends in the peripheral direction. The small diameter of the through hole 124 is approximately the same as the outer diameter of the columnar shaped portion 163 of the spring pin 162. A column shaped portion 163 of the first elastic pin 162A is positioned at the end of the through hole. 124 in the normal direction of rotation. The columnar shaped portion 163 of the second spring pin 162B is positioned at the end of the through hole 124 in the direction opposite to the normal direction of rotation.
    Next, the action of the actuating spring 90 of the date indicator of the present variant will be described with reference to FIG. 20.
    [0144] FIG. 20 is a plan view of an essential part of the date indicator actuating spring according to the fourth variant of the first embodiment in top view.
    [0145] As illustrated in FIG. 20, when the date indicator actuating spring 90 is wound up and respectively cocked, the engagement part 93D is brought into contact with the elastic pins 162A and 162B of the mobile gearbox. date 60 at the level of the first contact portion 95D and of the second contact portion 96D.
    [0146] The first contact portion 95D is a part in which the engagement part 93D comes into contact with the date mobile gear 60 after having been pulled in the direction opposite to the normal direction of rotation. The first contact portion 95D is positioned on the inner surface defining the single through hole 124, and is in contact with the first spring pin 162A. The first normal vector V1 at the level of the first contact portion 95D points in a direction which deviates from the axis of rotation P (cf. FIG. 19) in a plan view in a direction opposite to the normal direction of rotation. Thus, the engagement portion 93D exerts a tensile force by the spring main body 91 in the direction opposite to the normal direction of rotation on the first spring pin 162A at the first contact portion 95D and prevents movement in the direction. opposite to the normal direction of rotation thanks to the resistance force.
    [0147] The second contact portion 96D is a part in which the engagement part 93D comes into contact with the date mobile gear 60 by being pulled inwards in the radial direction. The second contact portion 96D is positioned on the inner surface defining the through hole 124 and is in contact with the second spring pin 162B. The second normal vector V2 at the second contact portion 96D points in a direction away from the first contact portion 95D in a plan view. Accordingly, the engaging portion 93D exerts a force to rotate around the first contact portion 95D on the second spring pin 162B at the second contact portion 96D, and the rotation is regulated by the resistance force.
    [0148] As described above, given that the date indicator actuating spring 90 of the present variant comprises the engagement part 93D in engagement with the date mobile gear 60 at two points, it is necessary to can achieve the same beneficial effect as that of the first embodiment.
    [0149] Further, the engaging portion 93D is provided with a through hole 124 having a non-circular shape in plan view in which the first spring pin 162A and the second spring pin 162B are arranged. When a single through-hole has a circular shape in plan view, the engaging part and the date gear mobile cannot engage with each other at two or more points regardless of the shape of the pin. elastic and the rotation of the engagement part with respect to the date gear mobile cannot be suppressed. According to the present variant, the engagement part 93D and the date mobile gear 60 can come into mutual engagement at two points. Therefore, the technical effect described above can be obtained.
    [Fifth variant of the first embodiment]
    [0150] FIG. 21 is a plan view of the date gear mobile and of the date indicator actuating spring according to a fifth variant of the first embodiment, seen from above.
    [0151] In the first embodiment, the date mobile gear 60 is provided with a pair of elastic pins 62. On the other hand, the fifth variant of the first embodiment differs from the first embodiment in that a only protruding part 172 is formed on the date mobile gear 60. In addition, the configuration other than that described below is identical to that of the first embodiment.
    [0152] As illustrated in FIG. 21, the date mobile gear 60 presents the projecting part 172 instead of the first elastic pin 62A and the second elastic pin 62B of the first embodiment. The protrusion 172 is configured in a non-circular shape according to a plan view. In particular, the protruding part 172 has a rectangular shape in plan view. The protrusion 172 is integrally molded with the main gear movable body 61. The protrusion 172 is, for example, formed by a machining process when molding the main body 61 of the gear mobile, by a cutting process when performing a press process or the like. The protrusion 172 extends uniformly upward from the upper surface of the main body 61 of the gear movable.
    [0153] An engagement portion 93E is provided with a through hole 134 into which the protrusion 172 is inserted from below. The protrusion 172 is fitted into the through hole 134. The through hole 134 has a rectangular shape so as to match the shape of the protrusion 172 in plan view and extends uniformly in the up-down direction.
    Next, the action of the actuating spring 90 of the date indicator of the present variant will be described with reference to FIG. 22.
    [0155] FIG. 22 is a plan view of an essential part of the date indicator actuating spring according to a fifth variant of the first embodiment in top view.
    [0156] As illustrated in FIG. 22, when the date indicator actuating spring 90 is wound up and respectively cocked, the engagement part 93E comes into contact with the protruding part 172 of the date mobile gear 60 at the level of 'a first contact portion 95E and a second contact portion 96E.
    [0157] The first contact portion 95E is a part in which the engagement part 93E comes into contact with the date mobile gear 60 after having been pulled in the direction opposite to the normal direction of rotation. The first contact portion 95E is positioned on the inner surface defining the through-hole 134 and is in contact with the protrusion 172. The first normal vector V1 at the first contact portion 95E points in a direction away from it. axis of rotation P (see figure 21) in a plan view in a direction opposite to the normal direction of rotation. Thus, the engagement portion 93E exerts a tensile force by the main spring body 91 in the direction opposite to the normal direction of rotation on the protrusion 172 at the first contact portion 95E and prevents any displacement in the direction opposite to the direction of rotation. normal direction of rotation thanks to the resistance force.
    [0158] The second contact portion 96E is a part in which the engagement part 93E is brought into contact with the date gear mobile 60 after having been pulled inwards in the radial direction. The second contact portion 96E is positioned on the inner surface defining the through hole 134, and is in contact with the protrusion 172. The second normal vector V2 at the second contact portion 96E points in a direction which deviates from the first. contact portion 95E according to a plan view. Thus, the engaging portion 93E exerts a force to rotate around the first contact portion 95E on the protrusion 172 at the second contact portion 96E, and the rotation is prevented by the resistance force.
    [0159] As described above, given that the date indicator actuating spring 90 of the present variant comprises the engagement part 93E in engagement with the date mobile gear 60 at two points, it is possible to can achieve the same beneficial technical effect as that of the first embodiment.
    [0160] Further, the engaging portion 93E is provided with a through hole 134 having a non-circular shape in plan view in which the protruding portion 172 is arranged. According to this configuration, since the shape of the protruding part 172 has a non-circular shape according to a plan view, the engagement part 93E and the date gear mobile 60 can come into mutual engagement at two points. Therefore, the above described beneficial technical effect can be obtained.
    [Sixth variant of the first embodiment]
    [0161] FIG. 23 is a plan view of the date gear mobile and of the date indicator actuating spring according to a sixth variant of the first embodiment, seen from above.
    [0162] In the fifth variant of the first embodiment, a configuration in which the engagement part 93E of the date indicator actuating spring 90 surrounds the projecting part 172 located on the date mobile gear 60 is used. On the other hand, the sixth variant of the first embodiment is different from the fifth variant of the first embodiment in that a wall 182 located on the date gear mobile 60 surrounds an engagement part 93F of the actuating spring 90d. 'date indicator. Moreover, the remainder of the configuration other than that described below is identical to that of the first embodiment.
    [0163] As illustrated in Fig. 23, the outer shape of the engagement portion 93F has a non-circular shape in plan view. In particular, the engagement portion 93F has a rounded rectangular shape in plan view. The engagement portion 93F extends with a constant thickness with respect to the up-down direction as a direction of thickness.
    [0164] The date mobile gear 60 includes the wall 182 which projects upwardly from the main body 61de mobile gear. The wall 182 extends to surround the engagement portion 93F. The space defined by the wall 182 is configured to take a rounded rectangular shape to match the shape of the engagement portion 93F in plan view. The engagement portion 93F is fitted within the wall 182. The wall 182 includes a wall surface 183 opposite the side surface of the engagement portion 93F. The wall surface 183 includes a stop surface 183a oriented in the normal direction of rotation. The stop surface 183a is opposed to the engaging portion 93F from the direction opposite to the normal direction of rotation. The wall 182 has an opening portion 184 which bypasses the main body 91 of the date indicator actuating spring 90. The opening portion 184 opens towards the intermediate portion in the radial direction on the stop surface 183a. Thus, the stop surface 183a is divided into two by the opening portion 184. The opening edge of the opening portion 184 is separated from the main spring body 91.
    In what follows, the action of the date indicator actuating spring 90 of the present variant will be described with reference to FIG. 24.
    [0166] FIG. 24 is a plan view of a main part of the date indicator actuating spring according to the sixth variant of the first embodiment, seen from above.
    [0167] As illustrated in FIG. 24, when the date indicator actuating spring 90 is wound up and respectively cocked, the engagement part 93F comes into contact with the wall 182 of the date mobile gear 60 at the level of. a first contact portion 95F, a second contact portion 96F and a third contact portion 97F.
    [0168] The first contact portion 95F and the second contact portion 96F are parts with which the engagement part 93F is brought into contact with the date gear mobile 60 after having been pulled in the direction opposite to the normal direction. of rotation. The first contact portion 95F is positioned on the side surface of the engagement portion 93F and is in contact with the stop surface 183a of the wall 182. The first contact portion 95F and the second contact portion 96F are in contact. contact with both sides of the stop surface 183a through the opening portion 184. The first contact portion 95F is positioned within the opening portion 184 in the radial direction. The first normal vector V1 at the level of the first contact portion 95F and the second normal vector V2 at the level of the second contact portion 96F point in a direction which deviates from the axis of rotation P (cf. FIG. 23) according to a plan view in the opposite direction to the normal direction of rotation. Thus, the engagement part 93F exerts a tensile force by the main spring body 91 in the direction opposite to the normal direction of rotation on the wall 182 at the level of the first contact portion 95F and prevents any displacement in the direction opposite to the direction. normal rotation via the corresponding resistance force. Further, the second normal vector V2 at the second contact portion 96F points in a direction away from the first contact portion 95F in a plan view. Thus, the engaging portion 93F exerts a force to rotate around the first contact portion 95F by pulling the engaging portion 93F inwardly in the radial direction on the wall 182 at the second contact portion 96F. and the rotation is prevented by the resistance force.
    [0169] The third contact portion 97F is a part in which the engagement part 93F is brought into contact with the date gear mobile 60 after having been pulled inward in the radial direction. The third contact portion 97F is positioned on the side surface of the engagement portion 93F and is in contact with the wall surface 183 of the wall 182. The third normal vector V3 at the third contact portion 97F points towards the wall. interior in the radial direction from the first normal vector V1 and from the second normal vector V2. Thus, the engagement portion 93F exerts an inward displacement force in the radial direction on the wall 182 at the third contact portion 97F, and the inward displacement in the radial direction is prevented by the force. resistance.
    [0170] As described above, given that the date indicator actuating spring 90 of the present variant comprises the engagement part 93F in engagement with the date mobile gear 60 at two points, it is possible to can achieve the same effect as that of the first embodiment.
    [0171] In addition, the outer shape of the engagement portion 93F has a non-circular shape in plan view. When the outer shape of the engagement part has a circular shape in plan view, the engagement part and the date gear mobile cannot engage with each other at two points or more simply by bringing the date mobile gear into contact with the lateral surface of the engagement part and the rotation of the engagement part with respect to the date gear mobile cannot be suppressed. According to the present variant, by bringing the wall 182 of the date gear mobile 60 into contact with the lateral surface of the engagement part 93F, the engagement part 93F and the date gear mobile 60 can engage. with each other at two points. Therefore, the beneficial technical effect described above can be obtained.
    [Second embodiment]
    [0172] In the following description, a second embodiment will be described with reference to Figures 25 to 28. The second embodiment is different from the first embodiment in that a spiral spring is used in a force mechanism. constant 230 which suppresses fluctuations in energy transmitted to an exhaust regulator 214. The same reference numerals will be given to the same configurations as those of the embodiment described above.
    [0173] Fig. 25 is a block diagram of the movement of the second embodiment.
    [0174] As illustrated in FIG. 25, the movement 210 (movement of a timepiece) of the present embodiment comprises a movement barrel 211 which is a source of energy, a gear 212 disposed on the side of this source of energy. and which is connected to the movement barrel 211, an exhaust regulating member 214, a gear 215 on the exhaust side connected to the exhaust - regulating member 214 and a constant force mechanism 230 arranged between the gear 212 on the source side of energy and the cog on the exhaust side.
    [0175] In addition, the constant force mechanism 230 is generally an integral part of a finishing gear comprising a second mobile or a third mobile, a fourth mobile and the like. The power source gear 212 in the present embodiment is referred to as a gear positioned further downstream with respect to the movement barrel 211, which is a power source, than the constant force mechanism 230vu taking the mechanism to. constant force 230 as a reference. Similarly, the escapement side gear 215 according to the present embodiment is designated by a gear positioned closer to the exhaust regulator 214 than the constant force mechanism 230, still seen from the constant force mechanism 230.
    [0176] A barrel spring 216est housed inside the movement barrel 211. The barrel spring 216est wound up following the rotation of the adjusting rod 9 of the needles (see FIG. 1). The movement barrel 211 rotates under the impulse of the energy (torque) accompanying the unwinding (unwinding) of the barrel spring 216 and transmits the energy to the constant force mechanism 230 via the gear 212 on the energy source side. Further, in the present embodiment, although a case in which the energy from the movement barrel 211 is transmitted to the constant force mechanism 230 via the gear 212 on the power source side is described as an example, the present invention is not limited to such a case. For example, the energy coming from the movement barrel 211 could be transmitted directly to the constant force mechanism 230 without passing through the cog 212 on the energy source side.
    For example, the gear 212 on the energy source side comprises a first transmission wheel 218. The first transmission wheel 218 is for example a third mobile. The first transmission wheel 218 is pivotally supported between a plate 223 (see Figure 27) and a gear bridge (not shown). The first transmission wheel 218 rotates based on the rotation of the movement barrel 211. Additionally, when the first transmission wheel 218 rotates, a roadway (not shown) rotates based on this rotation. The minute hand 6 shown in FIG. 1 is fixed to the roadway. As the first transmission wheel 218 rotates, a minute wheel (not shown) rotates based on this rotation, and then an hour wheel (not shown) rotates based on the rotation of the minute wheel.
    The gear 215 on the exhaust side mainly comprises a second transmission wheel 219. The second transmission wheel 219 is for example a fourth mobile. The second transmission wheel 219 is pivotally supported between the plate 223 and the gear bridge and rotates based on the rotation of a lower stage wheel 260 at constant force (cf. figure 26) which will be described later, in the figure. constant force mechanism 230.
    The exhaust regulator 214est made in the same way as the exhaust regulator 13 of the first embodiment. The exhaust regulator 214 controls the rotation of the gear 215 on the exhaust side.
    (Configuration of constant force mechanism)
    [0180] The constant force mechanism 230 is a mechanism which suppresses the fluctuation (torque fluctuation) in the level of energy transmitted to the exhaust regulator 214.
    [0181] Fig. 26 is a perspective view when part of the movement of the second embodiment is viewed from above.
    [0182] As illustrated in FIG. 26, the constant force mechanism 230 comprises: a fixed gear mobile 231 of which a first axis of rotation O1 which extends upwards and downwards is the line corresponding to a central shaft; a constant force upper stage wheel 240 (input rotary body) which rotates about the first axis of rotation 01; a constant force lower stage wheel 260 (output rotating body) which is arranged coaxially with the constant force upper stage wheel 240 and which is rotatable relative to the constant force upper stage wheel 240 about the first axis of O1 rotation; a coupling / uncoupling lever assembly 280 which connects the constant force upper stage wheel 240 and the constant force lower stage wheel 260 to each other; a constant force spring 300for transmitting the stored energy to the constant force upper stage wheel 240 and to the constant force lower stage wheel 260; and a torque adjustment mechanism 310 which adjusts the torque of the constant force spring 300. The first axis of rotation O1 is arranged in a position which deviates, along the plane of the plate 223 (cf. FIG. 27) with respect to the axis of rotation of the first transmission wheel 218 and of the second transmission road 219 (see Figure 25) which are described above.
    [0183] Fig. 27 is a sectional view showing part of the movement of the second embodiment.
    [0184] As illustrated in FIG. 27, the fixed gear mobile 231est arranged between the plate 223 and a bridge 224d'unit at constant force. The constant force unit bridge 224 is arranged above the platen 223. The fixed gear mobile 231 comprises a tubular body 232 arranged coaxially with respect to the first axis of rotation 01 and a main body 233 of the gear mobile formed. integral with the tubular body 232.
    [0185] The tubular body 232 is secured to a lower surface of the constant force unit bridge 224 by a fixed gear movable pin 234 which projects downward from the constant force unit bridge 224. A central hole 235 and a window 236 are formed in the tubular body 232. The central hole 235 extends upward and downward with an internal diameter relative to the first axis of rotation O1 as a center and passes through the tubular body 232 upward and downward. the bottom. The window 236 is adjacent to the central hole 235 in a direction in which the first axis of rotation O1 and the axis of rotation of the first transmission wheel 218 are arranged in a plan view (see Fig. 26). The window 236 traverses the tubular body 232 in the up-and-down direction and is connected to the central hole 235. Thus, the hole which passes through the fixed gear mobile 231 up and down is an elongated hole in a plan view. .
    [0186] The main body 233de movable gear is arranged coaxially with respect to the first axis of rotation O1 and projects outwardly in the radial direction from a lower end of the tubular body 232. Fixed teeth 233a are formed. over the entire periphery of the outer peripheral surface of the main body 233de movable gear. In other words, the fixed gear wheel 231 is an external tooth type gear wheel.
    [0187] The constant force upper stage wheel 240 is pivotally supported between the plate 223 and the constant force unit bridge 224. The constant force top stage wheel 240 includes a rotational shaft 241 which rotates about the first rotational axis O1, a planetary wheel 243 which gravitates around the first rotational axis 01, and a driver 247 (first component) which pivotally supports the wheel. planetary 243.
    The rotation shaft 241 extends along the first axis of rotation O1. The rotation shaft 241 is pivotally supported by the plate 223 and the constant force unit bridge 224 through the perforated stones 225A and 225B. The stones with holes 225A and 225B are made of an artificial gemstone, such as synthetic ruby. The holed stones 225A and 225B are not limited to the case where the holed stones are formed from artificial gemstones and may be formed, for example, from other brittle materials or from metallic materials, such as iron-based alloys. A constant force top stage gear 241a is formed in an upper portion of the rotating shaft 241. The constant force top stage gear 241a meshes with the first transmission wheel 218. Thus, the energy coming from the movement barrel 211 (see figure 25) is transmitted to the rotation shaft 241 via the gear train 212 on the energy source side. The energy of the torque Tb is transmitted from the movement barrel 211 to the rotation shaft 241. In the following, the torque Tb is called the rotation torque Tb of the movement barrel 211. The rotation shaft 241 rotates in the direction. clockwise under the impulse of the energy coming from the movement barrel 211.
    [0189] The driver 247 is fixedly supported by the rotation shaft 241. The torque Tb in the clockwise direction of the rotation shaft 241 is transmitted to the driver 247. Thus, the The driver 247 rotates together with the rotation shaft 241 around the first axis of rotation 01 clockwise under the impulse of energy from the movement barrel 211. The driver 247 includes a lower seat 248 connected to it. integrally attached to the rotation shaft 241 and an upper seat 254 arranged above the lower seat 248 and fixed to the lower seat 248.
    [0190] The lower seat 248 is arranged under the fixed gear mobile 231. The lower seat 248 comprises a planetary wheel support portion 249 which supports the planetary wheel 243, a spring support portion 250 which supports the constant force spring 300, and a connecting part 251 which connects the planetary wheel support part 249 and the spring support part 250 to each other.
    [0191] Fig. 28 is a plan view of part of the movement of the second embodiment in top view. In Figure 26, part of the fixed gear mobile 231 is cut off and shown in the drawing.
    [0192] As illustrated in Figures 26 and 28, the planetary wheel support portion 249 extends in the form of an arc in the peripheral direction around the first axis of rotation O1 according to a plan view. The planetary wheel support portion 249 is formed such that an intermediate portion viewed from the up-down direction is one stage below the two ends.
    As illustrated in Figure 27, the support part 250de spring is located on the opposite side with respect to the support part 249de planetary wheel through the first axis of rotation O1. A pair of pin insertion holes 250a, through which a pair of elastic constant force pins 303 are inserted, are formed in the spring support portion 250. In Fig. 27, the pin insertion hole 250a and the constant force spring pin 303 are shown separately. The constant force spring pin 303 protrudes downward from the spring support portion 250. Similar to the spring pin 62 of the first embodiment, the columnar shaped portion 63 and the flange 64 are located at the lower end of the constant force spring pin 303. A central hole through which the shaft 241 is inserted is provided in the connecting portion 251. The connecting portion 251 is fixed to a lower portion of the upper stage pinion 241a at constant force in the rotating shaft 241. Accordingly, the lower seat 248 rotates by a constant force. integral with the rotation shaft 241. A driver window 252 is formed in the lower seat 248. The driver window 252 is formed on the side of the first rotation axis 01 with respect to the planetary wheel support portion 249. Coach window 252 passes through lower seat 248 up and down. The driver window 252 avoids contact between the lower seat 248 and the engagement claw stone 286 which will be described later.
    [0194] As illustrated in Figure 26, the upper seat 254 is arranged above the planetary wheel support portion 249 of the lower seat 248 and above the main body 233 of the fixed gear mobile 231. The upper seat 254 extends in the form of an arc in the peripheral direction around the first axis of rotation O1 according to a plan view. The upper seat 254 is stacked in a state that it has a spacing gap from the planetary wheel support portion 249 of the lower seat 248 through a plurality of cylindrical pillars 255. Both ends of the upper seat 254 are attached to both ends of the planetary wheel support portion 249 by a plurality of bolts 256 inserted through the plurality of pillars 255.
    [0195] As illustrated in Fig. 27, the sun gear 243 is rotatably supported by the driver 247. In particular, the sun gear 243 is pivotally supported by the sun gear support portion 249 of the lower seat 248 and by the upper seat. 254via the perforated stones 259A and 259B so as to be rotatable about a second axis of rotation 02. The second axis of rotation 02 is arranged in a position which deviates, according to a view in the plane of the plate 223, with respect to the first axis of rotation 01 is in a fixed position with respect to the driver 247. The sun gear 243 is arranged between the intermediate portion of the sun gear support portion 249 of the lower seat 248 viewed from the up-down direction and the bottom. intermediate portion of the upper seat 254 viewed in the direction from top to bottom (see Figure 26). The planetary wheel 243 includes a planetary pinion 244 and a planetary gear wheel 245.
    [0196] The planetary gear 244 meshes with the fixed teeth 233a of the fixed gear mobile 231. Since the fixed gear mobile 231 is of the external tooth type, since the planetary gear 244 and the fixed gear mobile 231s 'mesh with each other, in accordance with the rotation of the driver 247 clockwise, the planetary wheel 243 gravitates clockwise around the first axis of rotation 01 while rotating clockwise around the second axis of rotation 02.
    [0197] The planetary gear wheel set 245 is disposed under the planetary gear 244 and can rotate (can rotate and gravitate) without coming into contact with the fixed gear wheel set 231. The planetary gear wheel set 245 has a plurality of teeth of stop 245a which may engage with engagement claw stone 286 and disconnect therefrom. The number of stop teeth 245a is eight. However, the present invention is not limited to this number and the number of teeth can be suitably changed as needed.
    [0198] As illustrated in FIG. 28, the stop teeth 245a extend in the direction of clockwise around the second axis of rotation 02 while being separated from the second axis of rotation 02 according to a plan view. The tips of the stop teeth 245a are considered to be a functional surface which engages and disengages from the engagement claw stone 286. In the following, a trajectory of rotation M traced by the tip of the stop teeth 245a according to the rotation of the planetary wheel 243 is called the trajectory of rotation M of the planetary gear wheel set 245.
    [0199] As illustrated in FIG. 27, the constant force lower stage wheel 260 is rotatably supported by the rotation shaft 241 of the constant force upper stage wheel 240 between the plate 223 and the force unit bridge 224. constant. The constant force lower stage wheel 260 is arranged below the driver 247 of the constant force upper stage wheel 240 and between the driver 247 and the stage 223. The constant force lower stage wheel 260 includes a stage cylinder 261. constant force lower (second component) added to the rotation shaft 241 and a constant force lower stage gear mobile 262 integrally connected to the constant force lower stage cylinder 261. The constant force lower stage wheel 260 is rotated clockwise about the first axis of rotation 01 by the energy transmitted from the constant force spring 300.
    [0200] The rotating shaft 241 is inserted from above into the constant force lower stage cylinder 261 and protrudes below the constant force lower stage cylinder 261. Ring shaped pierced stones 269A and 269B are driven into the upper end and lower end of the lower stage cylinder 261 at constant force. The rotation shaft 241 is inserted through the perforated stones 269A and 269B.
    The mobile gear 262d'étage lower constant force is assembled at the lower end of the cylinder 261d'étage lower constant force. Constant force lower stage teeth 262a with which the second transmission wheel 219 meshes are formed all around the periphery of the outer peripheral surface of the constant force lower stage gear motor 262. Thus, the constant force lower stage wheel 260 can transmit the energy of the constant force spring 300 to the second transmission wheel 219 connected to the exhaust regulator 214, that is to say the gear 215 on the exhaust side. .
    [0202] Further, in the present embodiment, although a case in which the energy from the constant force spring 300 is transmitted to the exhaust regulator 214 via the gear 215 on the exhaust side is described as For example, the present invention is not limited to such a case. For example, the gear 215 on the exhaust side could not be used and the energy from the constant force spring 300 could be transmitted directly to the exhaust regulator 214.
    [0203] The coupling / uncoupling lever assembly 280 comprises an engaging claw stone 286 in engagement with the stop teeth 245a of the planetary gear mobile 245 and uncoupled therefrom and rotatably supports the claw stone. engagement 286 around the first axis of rotation O1. The coupling / uncoupling lever assembly 280 includes a lever plug 281 arranged in such a manner that it cannot be rotated relative to the lower stage cylinder 261 at constant force and a coupling / uncoupling lever 284 rotatably disposed in the direction. clockwise according to the rotation of the lever cap 281 clockwise.
    The lever plug 281 has a cylindrical shape coaxial with respect to the first axis of rotation O1. The lever plug 281 extends the upper end of the constant force lower stage cylinder 261 from the constant force lower stage wheel 260 and is integrally connected with the constant force lower stage cylinder 261. Thus, the lever plug 281 rotates clockwise around the first axis of rotation O1 in synchronization with the rotation of the lower stage wheel 260 at constant force.
    [0205] The coupling / uncoupling lever 284 includes a lever main body 285 and an engaging claw stone 286 supported by the lever main body 285.
    [0206] The main lever body 285 is arranged under the planetary gear mobile 245 of the planetary wheel 243. The lever main body 285 is supported by the lever plug 281. The engagement claw stone 286 is attached to one end of the lever. main lever body 285.
    [0207] The engagement claw stone 286 is made of an artificial gemstone, such as synthetic ruby. In addition, the 286 engagement claw stones are not limited to a case where the pierced stones described above are formed of artificial gemstones and may be formed, for example, of other brittle materials or metallic materials, such as. than iron-based alloys. The engagement claw stone 286 may be integrally formed with the lever main body 285 instead of being separated from the lever main body 285. The engagement claw stone 286 is held by the lever main body 285 in a state that it protrudes towards the planetary gear movable 245 (upper side) from the lever main body 285. The engagement claw stone 286 is arranged inside the window 252 of the driver 247 of the constant force upper stage wheel 240.
    [0208] As illustrated in Fig. 28, among the protrusions of the engagement claw stone 286, the tips of the stop teeth 245a of the planetary gear mobile 245 may engage the side surface facing the opposite side. to the first axis of rotation O1, and respectively disconnect therefrom. The engagement claw stone 286 engages with the planetary gear mobile 245 within the rotational path M of the planetary gear mobile 245 and thus prevents rotation of the planetary gear 243. By being moved in the direction. clockwise around the first axis of rotation 01 relative to the planetary wheel 243 and withdrawn from the trajectory of rotation M of the planetary gear mobile 245, the engagement claw stone 286 is uncoupled from the stop teeth 245a and the engagement with the planetary gear wheel 245 is released.
    [0209] As illustrated in FIG. 26, the constant force spring 300 is a spiral spring. As illustrated in Fig. 27, the constant force spring 300 has the same configuration as that of the date indicator actuating spring 90 of the first embodiment. In other words, the constant force spring 300 comprises the main spring body 91, the fixing portion 92, and the engaging portion 93. The constant force spring 300 is arranged under the engagement / disconnect lever assembly 280 and between. the engagement / disengagement lever assembly 280 and the constant force lower stage gear mobile 262.
    [0210] The fixing portion 92est arranged coaxially with respect to the first axis of rotation O1. The attachment portion 92 is assembled to a constant force spring plug 311 which will be described later in the torque adjustment mechanism 310. The attachment portion 92 is attached to the constant force lower stage cylinder 261 of the lower stage wheel 260. constant force via the torque adjustment mechanism 310. The engaging portion 93 is arranged under the spring support portion 250 of the constant force upper stage wheel 240. The engagement portion 93 engages with the constant force spring pin 303 by inserting the lower end of the constant force spring pin 303 into the through hole 94 from above. The engagement structure between the engagement portion 93 and the constant force spring pin 303 is the same as the engagement structure between the engagement portion 93 and the spring pin 62 of the date movable wheel 60 of the first embodiment. The engagement portion 93 is fixed to the lower seat 248 of the constant force upper stage wheel driver 247 via the constant force spring pin 303. Thus, the constant force spring 300 can transmit the accumulated energy respectively to the wheel. 240 of the upper stage at constant force and the wheel 260 of the lower stage at constant force.
    [0211] The main body 91du constant force spring 300 extends clockwise from the inner end to the outer end. Preload is applied to the constant force spring 300 by the winding, which results in its winding. Therefore, the energy of a torque Tc is generated in the constant force spring 300, and this energy is accumulated there. In the present embodiment, the constant force spring 300 is elastically deformed so as to reduce the diameter by winding and fixing and generates such torque.
    [0212] The energy accumulated in the constant force spring 300 is transmitted to the upper stage wheel 240 at constant force and to the lower stage wheel 260 at constant force in accordance with the elastic return deformation of the constant force spring 300. Thus, the constant force upper stage wheel 240 and the constant force lower stage wheel 260 can rotate in opposite directions with respect to each other about the first axis of rotation 01 under the impulse of the energy transmitted from the constant force spring 300. In particular, the constant force lower stage wheel 260 can rotate clockwise and the constant force upper stage wheel 240 can rotate clockwise. counterclockwise. In the following, the torque Tc is referred to as the rotational torque Tc of the constant force spring 300. When the barrel spring 216 is wound by a predetermined amount of winding in the movement barrel 211, the rotational torque Tc is set to a torque lower than the torque Tb of the rotation shaft 241.
    [0213] The torque adjustment mechanism 310 applies the preload to the constant force spring 300 and adjusts the rotational torque Tc of the constant force spring 300. The torque adjustment mechanism 310 comprises: the constant force spring plug 311 supported by the constant force lower stage cylinder 261 of the constant force lower stage wheel 260; a first torque adjustment gear movable 312 integrally connected to the constant force spring cap 311; a second torque adjustment gear movable 313 integrally connected to the constant force lower stage cylinder 261; and a torque adjustment jumper 314 which connects the first torque adjustment gear mobile 312 and the second torque adjustment gear mobile 313 to each other.
    [0214] The constant force spring cap 311 has a cylindrical shape arranged coaxially with respect to the first axis of rotation O1. The constant force spring plug 311 is added to the constant force lower stage cylinder 261 between the constant force lower stage gear motor 262 and the coupling / uncoupling lever assembly 280. The constant force spring plug 311 is located so as to be able to rotate about the first axis of rotation 01 with respect to the lower stage cylinder 261 at constant force. The fixing portion 92 of the constant force spring 300 is directed towards the middle portion in the top-down direction of the constant force spring cap 311, and the constant force spring cap 311 and the fixing portion 92 are assembled together. one to another to form a single piece.
    [0215] The first torque adjustment gear mobile 312 is integrally connected to the lower end of the constant force spring plug 311. First torque adjustment teeth 312a are formed all around the periphery on the peripheral surface. outside of the first torque adjustment gear motor 312. A torque adjustment gear motor (not shown) meshes with the first torque adjustment teeth 312a.
    [0216] The second torque adjustment gear mobile 313 is arranged between the constant force lower stage gear mobile 262 and the constant force spring plug 311 and the first torque adjustment gear mobile 312. The second torque adjustment gear mobile 313 is integrally connected to the constant force lower stage cylinder 261. The second torque adjustment gear mobile 313 configured to have a smaller diameter than the first torque adjustment gear mobile 312. Second torque adjustment teeth 313a are formed all around the periphery on the surface. external peripheral of the second torque adjustment gear mobile 313. The torque adjustment jumper 314 is in reversible engagement with the second torque adjustment teeth 313a.
    [0217] The torque adjustment jumper 314 is supported by the first torque adjustment gear mobile 312 and is able to gravitate around the first axis of rotation 01 around the second torque adjustment gear mobile 313. The torque adjustment jumper 314 can regulate the rotation of the first torque adjustment gear mobile 312 clockwise with respect to the second torque adjustment gear mobile 313. Further, the Torque adjustment jumper 314 can allow rotation of the first torque adjustment gear mobile 312 in a counterclockwise direction relative to the second torque adjustment gear mobile 313.
    [0218] Thus, when the constant force spring plug 311 and the first torque adjustment gear movable 312 receive clockwise energy from the constant force spring 300, this energy is transmitted to the second torque adjustment gear mobile 313 via the torque adjustment jumper 314. Then, the torque adjustment jumper 314 prevents the rotation of the first torque adjustment gear mobile 312 in the direction of. clockwise with respect to the second torque adjustment gear mobile 313, and the first torque adjustment gear mobile 312 and the second torque adjustment gear mobile 313 rotate integrally clockwise. Therefore, the constant force lower stage wheel 260 also rotates clockwise, together with the second torque adjustment gear movable 313.
    [0219] By applying a preload to the constant force spring 300, by causing the torque adjustment gear mobile (not shown) to mesh with the first torque adjustment gear mobile 312 and rotating the gear mobile for torque adjustment, the first torque adjusting gear mobile 312 is rotated counterclockwise. Then, since the torque adjustment jumper 314 allows the first torque adjustment gear mobile 312 to be rotated counterclockwise with respect to the second torque adjustment gear mobile 313, the spring cap to constant force 311 is rotated counterclockwise without rotating the lower stage wheel 260 at constant force. Thus, the attachment portion 92 of the constant force spring 300 can be rotated counterclockwise. Therefore, the winding of the constant force spring 300 can be realized, and by increasing the preload of the constant force spring 300, the torque Tc can be adjusted so as to increase.
    (Operation of constant force mechanism)
    In what follows, we will describe the operation of the constant force mechanism 230conceived as described above.
    [0221] In addition, in an initial state, the barrel spring 216 in the movement barrel 211 is wound up by a predetermined amount of winding and the energy of the torque Tb is transmitted from the movement barrel 211 to the driver 247 of the upper stage wheel 240 at constant force via the gear 212 on the energy source side. In addition, the constant force spring 300 is wound by a predetermined amount of winding, and the energy of the rotating torque Tc, less than that of the rotating torque Tb, is transmitted from the constant force spring 300 to the driver 247 of the machine. constant force upper stage wheel 240 and constant force lower stage wheel 260.
    [0222] According to the constant force mechanism 230 of the present embodiment, since a constant force spring 300 is used, the energy accumulated in the constant force spring 300 is transmitted to the lower stage wheel 260 at constant force, and the constant force lower stage wheel 260 can be rotated clockwise about the first axis of rotation O1. In particular, the energy from the constant force spring 300 is transmitted to the torque adjustment mechanism 310 via the fixing portion 92. The energy transmitted to the torque adjustment mechanism 310 is transmitted to the lower stage wheel 260 by force. constant. Thus, the constant force spring 300 transmits energy to the lower stage wheel 260 at constant force so that it rotates clockwise around the first axis of rotation O1 under the impulse of the torque. of rotation Te. Further, the energy of the constant force spring 300 can be transmitted from the constant force lower stage wheel 260 to the second transmission wheel 219, and the second transmission wheel 219 can be rotated in accordance with the rotation of the wheel 260d '. lower stage at constant force. In other words, the energy of the constant force spring 300 can be transmitted to the exhaust side gear 215 via the constant force lower stage wheel 260 and the exhaust regulator 214 can be turned on.
    [0223] Further, since the energy from the constant force spring 300 is also transmitted to the constant force upper stage wheel 240 via the constant force spring pin 303 from the engagement portion 93, the upper stage wheel 240 constant force is rotated counterclockwise around the first axis of rotation O1 under the impulse of the torque Te.
    [0224] However, the torque Tb is transmitted to the upper stage wheel 240d'étage at constant force so as to rotate about the first axis of rotation O1 from the gear 212 on the energy source side in the direction of clockwise. Since the torque Tb is greater than the torque Tc, the rotation of the upper stage wheel 240 at constant force is prevented counterclockwise about the first axis of rotation O1.
    [0225] In addition, the energy (torque Tb - torque Te) of the difference between the torque Tb transmitted from the gear 212 on the energy source side and the torque Tc transmitted from the spring at constant force 300 acts on the upper stage wheel 240 at constant force. However, since the engagement claw stone 286 of the coupling / uncoupling lever assembly 280 engages the planetary gear wheel 245 within the rotational path M of the planetary gear wheel 245 of the upper stage wheel 240 at constant force, the rotation and the gravitation of the planetary wheel 243 are regulated, that is to say respectively inhibited. Thus, the constant force upper stage wheel 240 and the constant force lower stage wheel 260 can be linked to each other and the rotation of the constant force upper stage wheel 240 is prevented about the first axis. of rotation 01 clockwise.
    [0226] From the above, at the stage where the planetary gear mobile 245 and the engagement claw stone 286 are in mutual engagement, the rotation of the upper stage wheel 240 at constant force about the first axis of rotation O1 is prevented. . Since the energy of the difference described above acts on the upper stage wheel 240 at constant force, the tip of the stop teeth 245a of the planetary gear mobile 245 is in engagement with the engagement claw stone. 286 in a state of strong compression.
    [0227] As the constant force lower stage wheel 260 rotates under the energy of the constant force spring 300, in accordance with the rotation, the lever plug 281 and the coupling / uncoupling lever 284 of the set 280of coupling / uncoupling levers rotate around the first axis of rotation O1 in a clockwise direction. As the mating / disconnecting lever 284 rotates clockwise, the engaging claw stone 286 in the mating / disconnecting lever 284 is moved clockwise around the clockwise direction. first axis of rotation O1. Hence, the engagement / disengagement lever assembly 280 can be gradually decoupled from the planetary gear mobile 245 so as to withdraw the engagement claw stone 286 from the rotational path M of the planetary gear mobile 245. Thus, As the tips of the stop teeth 245a slide on the engagement claw stone 286 following disengagement of the engagement claw stone 286, the tooth tips move counterclockwise around the first axis of rotation O1 relative to to the engagement claw stone 286. As the tips of the stop teeth 245a pass the claw tip of the engagement claw stone 286, the engagement between the stop teeth 245a and the engagement claw 286 is released. Thus, the connection between the constant force upper stage wheel 240 and the constant force lower stage wheel 260 via the engagement claw stone 286 and the planetary wheel 243 is released.
    [0228] Consequently, the upper stage wheel 240 at constant force rotates clockwise around the first axis of rotation O1 under the impulse of energy (torque Tb - torque Tc) corresponding to the difference between the torque Tb transmitted from the gear train 212 on the energy source side and the torque Tc transmitted from the constant force spring 300.
    [0229] When the constant force upper stage wheel 240 rotates clockwise about the first axis of rotation O1, the constant force spring 300 can be wound via the constant force elastic pin 303 attached to the constant force spring. trainer 247 and the constant force spring 300 can be recharged with energy. In other words, the loss of energy lost in transmitting energy to the constant force lower stage wheel 260 can be recharged using the energy transmitted from the motion barrel 211 which is the main one. energy source. Thus, the energy of the constant force spring 300 can be kept constant and the exhaust regulator 214 can be operated at a constant torque.
    [0230] Even in the case of energy reloading with respect to the constant force spring 300, the constant force lower stage wheel 260 rotates under the impulse of energy from the constant force spring 300 and the energy from the constant force spring 300 is transmitted to the gear 215 on the exhaust side.
    [0231] When the energy is recharged with respect to the constant force spring 300described above, during the rotation around the second axis of rotation 02 in the clockwise direction in accordance with the rotation around the first axis of rotation 01de the constant force top-stage wheel 240, the planet wheel 243 gravitates clockwise about the first axis of rotation O1 and follows the engagement claw stone 286. The planet wheel 243 follows the claw stone of engagement 286 by indexed rotation of an amplitude corresponding to a stop tooth 245a and the tips of the stop teeth 245a again engage the engagement claw stone 286.
    [0232] Thus, given that the upper stage wheel 240 at constant force and the lower stage wheel 260 at constant force are again integral with each other, the rotation of the upper stage wheel 240 at constant force constant is prevented and the energy recharging of the constant force spring 300 is completed.
    [0233] By repeating the preceding cycles, the coupling and subsequent uncoupling between the planetary gear wheel set 245 and the engagement claw stone 286 can be carried out intermittently. In other words, the planetary gear mobile 245 and the engagement claw stone 286 may intermittently rotate the upper stage wheel 240 at constant force relative to the lower stage wheel 260 at constant force on the basis of. the rotation of the lower stage wheel 260 at constant force. Thus, the energy recharging of the constant force spring 300 can be carried out intermittently.
    [0234] As described above, similarly to the engagement structure between the actuating spring 90 of the date indicator and the date mobile gear 60 of the first embodiment, the constant force spring 300 of the present This embodiment engages the constant force top stage wheel 240 via the constant force spring pin 303 at two points and the same beneficial technical effects can be achieved as in the first embodiment.
    [0235] Since the constant force mechanism 230 of the present embodiment includes a constant force spring 300 which generates a desired torque, the insufficient torque applied between the upper stage wheel 240 at constant force and the stage wheel 260 lower than constant force can be suppressed and the fluctuation of the torque transmitted from the lower stage constant force wheel 260 to the exhaust regulator 214 can be suppressed.
    [0236] Since the timepiece and the movement 210of the present embodiment include the constant force mechanism 230, in which the fluctuation of the torque transmitted to the exhaust regulator 214 is suppressed, the movement and the workpiece. Watchmaking exhibiting high precision of time measurement can be obtained.
    [Third embodiment]
    [0237] In what follows, a third embodiment will be described with reference to Figures 29 to 31. The third embodiment is different from the first embodiment in that a spiral spring is used in a retrograde mechanism 411 which actuates the date hand 8. The same reference numerals will be given to the same configurations as those in the first embodiment or in the second embodiment.
    [0238] FIG. 29 is an external view of the timepiece according to a third embodiment.
    [0239] As illustrated in FIG. 29, a timepiece 1A of the present embodiment is provided with a calendar display portion 401a which displays the date. The display portion of the calendar 401a comprises the date hand 8 and a fan-shaped scale extending over a predetermined angular sector situated on the dial 3. The date hand 8 is situated so as to be able to turn on a predetermined angular range around an axis different from that of hour hand 5, minute hand 6 and second hand 7. The fan-shaped scale is provided with the numbers "1" to „31“ representing the date. The fan-shaped scale is located in accordance with the range of rotation of the date hand 8 and is indicated by the date hand 8.
    [0240] Figures 30 and 31 are plan views of the retrograde mechanism.
    [0241] As illustrated in FIG. 30, the movement 410 (movement of a timepiece) comprises the retrograde mechanism 411 which drives the date hand 8. The retrograde mechanism 411 drives the date hand 8 with a reverse movement. back and forth over a predetermined angular range. The retrograde mechanism 411 comprises a date indicator drive wheel 412, a date transmission wheel 420, a date hammer 440, a date hand wheel 450 and a return spring 460.
    [0242] The date indicator drive wheel 412 rotates once a day (24 hours) in connection with the gear 212 on the energy source side described above (cf. FIG. 25). A date finger 413 is located in the date indicator drive wheel 412. The date finger 413 has a spring portion 414 configured in the form of an arc according to a plan view and a stop portion 415 located at a distal end of the spring portion 414. The date finger 413 is arranged to overlap the wheel. date indicator drive 412 in a plan view. The date finger 413 is located integrally with the date indicator drive wheel 412 and rotates in synchronization with the date indicator drive wheel 412. The spring portion 414est elastically deformable in the peripheral direction and in the radial direction of the date indicator drive wheel 412. By rotating around the axis of rotation of the date indicator drive wheel 412 in accordance with the rotation of the date indicator drive wheel 412, the stopper portion 415 engages the gear transmission wheel. date 420 only once in each rotation and rotates the date transmission wheel 420.
    [0243] The date transmission wheel 420 has a disc shape and a plurality of teeth 421 are formed on an outer peripheral edge thereof. The plurality of teeth 421 are formed as thirty-one teeth corresponding to 31 days which is the maximum number of days in a month. One of the plurality of teeth 421 is urged in compression once in a day by the stop portion 415 of the date finger 413 which rotates once in a day. Thus, the date transmission wheel 420 rotates in one-step increments every day and rotates once in a month (i.e., 31 days) at the same angular pitch as the angular pitch of the plurality of teeth 421.
    [0244] A date column wheel 425 is located in the date transmission wheel 420. The date column wheel 425 rotates once in a month in synchronization with the date transmission wheel 420. The outer peripheral surface of the wheel calendar column 425 is a "snail" type cam surface 426 formed in such a way that the radius increases in a spiral shape oriented in the direction opposite to the direction of rotation of the date transmission wheel 420. The surface to cam 426 has an outermost portion 426a where the separation distance from the axis of rotation of the date transmission wheel 420 is maximum and an innermost portion 426b where the separation distance from the axis of rotation of the date transmission wheel 420 is minimum.
    A date jumper 430 comes into abutment against the date transmission wheel 420. The date jumper 430 corrects the position of the date transmission wheel 420 in the rotational direction. The date jumper 430 is provided with an elastically deformable date jumper spring portion 431, a distal end of which is a free end. The distal end of the spring portion 431 of the date jumper can engage with the teeth 421 of the date transmission wheel 420. The date jumper 430 corrects the rotation of the date transmission wheel 420 by engaging the end. distal with the teeth 421 of the date transmission wheel 420. Thus, the date transmission wheel 420 can rotate indexed one step at a time each day according to the same angular step as that of the plurality of teeth 421.
    [0246] The date hammer 440 is located so as to be able to perform a reciprocating movement around the axis of rotation which deviates from the axis of rotation of the date transmission wheel. 420. The date hammer 440 comprises a fan-shaped gear portion 441 which meshes with the date needle wheel 450 and a cam arm portion 442 which rotates integrally with the fan-shaped gear portion 441. The cam arm portion 442 is a cam follower whose distal end abuts against the cam surface 426 of the date column wheel 425. In the following, the position of the date hammer 440 when the distal end of the Cam arm portion 442 abuts against the innermost portion 426b of the cam surface 426 of the date column wheel 425 is called the "initial position". The position of the date hammer 440, when the distal end of the cam arm portion 442 abuts against the outermost portion 426a of the cam surface 426 of the date column wheel 425, is called the "end position". . As described above, the date column wheel 425 rotates once in a month. Therefore, the date hammer 440 performs a reciprocating movement once a month between the initial position and the final position. In Fig. 30, the state in which the date hammer 440 is in the initial position is shown. In Fig. 31, the state in which the date hammer 440 is in the final position is shown.
    [0247] The date hand wheel 450 is connected to the date hand 8 to rotate the date hand 8. The date hand wheel 450 rotates around the axis of rotation 03 in synchronization with the rotation of the hammer. date 440. When the date hammer 440 is in the initial position, the date hand wheel 450 is in a state where it is rotated in a given direction (counterclockwise in the figure). At this time, the date hand 8 indicates “1” of the scale of the calendar display portion 401a (see figure 29). When the date hammer 440 is in the final position, the date hand wheel 450 is in a state where it is capable of being rotated in the opposite direction. At this time, the date hand 8 indicates "31" of the scale of the calendar display portion 401a. Thus, the date hand 8 is actuated step by step each day in response to the rotation of the date column wheel 425 and to the movement of the date hammer 440.
    [0248] The return spring 460 pushes the date hammer 440 via the date hand wheel 450 in a direction tending to approach the date column wheel 425. The return spring 460 is a spiral spring. The return spring 460 has the same configuration as that of the date indicator actuating spring 90 of the first embodiment. In other words, the return spring 460 comprises the main spring body 91, the attachment portion 92, and the engaging portion 93. The attachment portion 92 of the return spring 460 is attached to the date hand wheel 450 and located at the same time. fixed manner on the date hand wheel 450. The engaging portion 93 of the return spring 460 is fixed to the platen. The engagement structure between the engagement portion 93 and the plate is identical to the engagement structure between the engagement portion 93 and the date gear mobile 60 of the first embodiment. In other words, the engagement portion 93 engages with a pair of spring pins 462 located on the platen. The element with which the engaging portion 93 engages is not limited to the plate and may be a member which rotatably supports the date hand wheel 450.
    [0249] A preload is applied to the return spring 460 following the winding which generates its winding. In the present embodiment, the return spring 460 is elastically deformed so as to reduce the diameter by winding and fixing and generates the torque. The return spring 460 is wound in a state in which the date hammer 440 is in the initial position. The return spring 460 is further wound from a state in which the date hammer 440 is in the initial position to a state in which the date hammer 440 is in the final position. Thus, the return spring 460 generates the rotational driving torque even in a state in which the date hammer 440 is in any position from the initial position to the final position and is pushed in a direction that the date hammer 440 tends to approach the date column wheel 425.
    (Operation of the retrograde mechanism)
    [0250] In the following, the operation of the retrograde mechanism 411 designed as described above will be described.
    [0251] As described above, the date indicator drive wheel 412 performs one complete revolution once a day. The date finger 413 located in the date indicator drive wheel 412 rotates once in a day in synchronization with the date indicator drive wheel 412.
    The stop portion 415 of the date finger 413 comes into abutment against the teeth 421 of the date transmission wheel 420 by rotation and then presses the teeth 421 with the evolution of the time. The time at which the stop portion 415 of the date finger 413 abuts against the teeth 421 of the date transmission wheel 420 is generally set at a predetermined time before midnight when the day changes (for example the time from 23 pm to midnight of the day. next day). When the teeth 421 of the date transmission wheel 420 are urged in compression by the stop portion 415 of the date finger 413 and are rotated at a predetermined angle, the distal end of the spring portion 431 of the date jumper passes over the tooth 421 and engages the next tooth 421. Thus, the date transmission wheel 420 rotates one step at a time each day according to a predetermined angular step and performs a complete revolution once every month.
    [0253] The date column wheel 425 rotates step by step, one step every day in synchronization with the date transmission wheel 420 and performs a complete revolution once every month.
    [0254] Here, the date hammer 440 moves from the initial position to the final position with the relative displacement of the cam arm portion 442 from the innermost portion 426b of the cam surface 426 to the outermost portion. 426a by the rotation of the date column wheel 425. Thus, the date hand wheel 450 which meshes with the fan-shaped gear portion 441 of the date hammer 440 rotates one step at a time each day. The date hand 8 fixed to the date hand wheel 450 is incremented by one each day around midnight when the day changes corresponding to the rotation of the date hand wheel 450. In this way, the retrograde mechanism 411 actuates the date hand 8 one step at a time from the first day to the last day of the month.
    [0255] As described above, similarly to the engagement structure between the actuating spring 90 of the date indicator and the date mobile gear 60 of the first embodiment, the return spring 460 of this embodiment The embodiment is engaged with the stage via the pair of spring pins 462 at two points and the same beneficial technical effects can be obtained as those of the first embodiment.
    [0256] Since the retrograde mechanism 411 of the present embodiment comprises the return spring 460 which generates a desired torque, any insufficient torque applied to the date hand wheel 450 can be eliminated. Thus, any insufficiency in terms of the torque applied to the date hand wheel 450 and the disturbance of the repetitive movement of the date hand 8 can be avoided.
    [0257] In addition, the invention is not limited to the embodiment described above, described with reference to the drawings, and different variations can be considered to be within the technical scope.
    [0258] For example, in the embodiments described above, the spiral spring of the present invention is used such that the outer end and the inner end are rotatable relative to each other. , on the one hand, and rolled up and tightened at the time of winding. However, the present invention can be applied to a spiral spring used for winding and expanding the diameter at the time of unwinding. In this case, contact with surrounding components due to unwinding of the spiral spring can be eliminated. Thus, any reduction in the torque generated by the spiral spring due to frictional forces accompanying the contact of the spiral spring in a state in which it is wound can be avoided.
    [0259] In the embodiments described above, the spiral spring engaging portion engages the drive member at two points, but could be engaged at three or more points.
    [0260] In the embodiments described above, the engagement part of the spiral spring and the driving element are engaged by adjustment, but can be engaged by driving (tightening-adjustment), by intermediate adjustment. or the like. However, engagement by fit is effective since simple assembly is possible.
    [0261] In addition, it is possible to replace the configuration element in the embodiments described above by a known configuration element without departing from the spirit of the present invention defined by the claims and each of them. The embodiments described above as well as each of the example variations may be suitably combined with all the others. For example, each variation of the first embodiment can be combined with the teachings of the second embodiment and the third embodiment.
    权利要求:
    Claims (14)
    [1]
    1. Spiral spring for timepiece (1), which is wound around an axis (P) to generate torque, comprising:a spring main body (61) which extends in the form of a spiral; andan engaging portion (93) integrally molded with an outer end (91a) of the spring main body (61) and engaged with a drive member at at least two points.
    [2]
    2. Spiral spring according to claim 1,the engagement portion (93) having a first contact portion (95) and a second contact portion (96) arranged to come into contact with the drive member,a first normal vector (V1) at the first contact portion (95) pointing in a direction which deviates from the axis according to an axial view of said axis (P), anda second normal vector (V2) at the level of the second contact portion (96) pointing in a direction which deviates from the first contact portion (95) according to a view taken in the axial direction.
    [3]
    3. Spiral spring according to claim 1 or 2,the engagement part (93) having a pair of recesses in which a pair of protrusions located on the driving member are arranged one by one.
    [4]
    4. Spiral spring according to claim 3,each of the recesses comprisinga first extension portion (114a) in which the protrusion is arranged and which extends in a peripheral direction around the axis (P) anda second extension portion (114b) which is connected to the first extension portion, which extends in a radial direction centered on the axis (P) and which opens to a side surface of the part of engagement (93B).
    [5]
    5. Spiral spring according to claim 3,each of the recesses passing through the engagement part (93) in the axial direction of the axis (P) andeach of the recesses comprisinga narrow portion (94a) where the protruding part is arranged anda wide portion which is connected to the narrow portion (94a) in the peripheral direction around the axis (P) and which has a wider shape in the radial direction centered on the axis (P) than the narrow portion.
    [6]
    6. Spiral spring according to claim 1 or 2,the engagement part (93) having a recess in which a first protrusion formed on the driving member is arranged anda side surface of the engaging portion (93) being formed so as to be in contact with the second protrusion formed on the driving member.
    [7]
    7. Spiral spring according to claim 1 or 2,the engagement part (93) having a recess in which is arranged a protrusion formed on the driving member and which has a non-circular shape when viewed in the axial direction of the axis.
    [8]
    8. Spiral spring according to claim 1 or 2,the external shape of the engagement part (93), when the latter is seen in the axial direction of the axis (P), being non-circular.
    [9]
    9. Torque generator comprising:a spiral spring according to any one of claims 1 to 8;a drive member with which the engaging portion (93) of the spiral spring engages; anda fastener to which an inner end of the spiral spring is attached.
    [10]
    10. A torque generator according to claim 9, further comprising:a date gear mobile (60) which comprises one of the two elements selected from the driving element and the fixing element, and which rotates in a manner synchronized with the rotation of an hour wheel (38 );a date finger unit which comprises the other element of the drive element and the fixing element, and a date finger (75) adapted to be able to engage and disengage from a toothing (40b) of a date indicator on which the date is displayed, and which is arranged so as to be rotatable relative to the date gear mobile (60) and coaxial with respect to said date gear mobile (60 ); anda calendar mechanism (16) which is arranged to increment the date values specified in an aperture of a dial.
    [11]
    11. A torque generator according to claim 9, further comprising a constant force mechanism (230) which comprisesan input rotary body which comprises one of two elements selected from the driving element and the fixing element, which is rotated by energy from an energy source and which recharges the spiral spring in energy;an output rotary body which comprises the other of the drive member and the fixing member, which is rotated by the energy from the spiral spring and which transmits the energy from the spiral spring to a member exhaust regulation (214); anda cycle control mechanism which intermittently rotates the input rotary body relative to the output rotary body according to the rotation of the output rotary body.
    [12]
    12. A torque generator according to claim 9, further comprising:a rotating part which comprises one of the two elements selected from the driving element and the fixing element, and which rotates in synchronization with an indicator; anda supporting part (249) which comprises the other member of the driving member and the fixing member and which rotatably supports the rotating parta retrograde mechanism (411) which drives the indicator back and forth between an initial position and a final position.
    [13]
    13. Movement (10) of a timepiece (1) comprising:a torque generator according to any one of claims 9 to 12.
    [14]
    14. Timepiece (1) comprising:a movement (10) of a timepiece (1) according to claim 13.
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    同族专利:
    公开号 | 公开日
    JP2021139638A|2021-09-16|
    CN113341673A|2021-09-03|
    JP6766284B1|2020-10-07|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    JP2020034875A|JP6766284B1|2020-03-02|2020-03-02|Swirl springs, torque generators, watch movements and watches|
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