Balance adjustment mechanism capable of restarting the operation of the balance, movement and timepi

专利摘要:
The object of the invention is to provide a balance adjustment mechanism capable of gently restarting the operation of a balance with a balance spring. The balance adjustment mechanism (19) comprises a winding stem (51) carried by a plate; an adjustment lever (60) arranged to pivot relative to the plate for a displacement of the winding stem (51) in an axial direction; an adjustment wheel rocker (90) arranged to be in engagement with the adjustment lever (60) and to pivot for pivoting of this adjustment lever (60); a transmission wheel (45) carried by the adjusting wheel rocker (90) and arranged to transmit a rotation of the winding stem (51) to an indicating member when the adjusting wheel rocker (90) is placed in a predetermined position; and a balance wheel adjustment lever (100) arranged to be in engagement with the adjustment wheel rocker (90) and adapted to be movable, for pivoting of the adjustment wheel rocker (90), between an adjustment position , in which the balance adjustment lever (100) comes into contact with a balance with balance spring, and a withdrawn position, in which the balance adjustment lever (100) is away from the balance with balance spring.
公开号:CH717217A2
申请号:CH00231/21
申请日:2021-03-02
公开日:2021-09-15
发明作者:Fujieda Hisashi；Mori Yuichi；Suzuki Shigeo；Hayakawa Kazuki
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 balance adjustment mechanism, a timepiece movement and a timepiece.
2. Description of the related prior art
[0002] In general, a mechanical timepiece comprises a mechanism for adjusting the seconds hand (stop seconds) used for setting the time. The seconds hand adjustment mechanism includes a gear adjustment lever which is operated by sliding and moving a winding stem. Next, a balance wheel with balance spring is adjusted and the cog is stopped by operating the cog adjusting lever (see, for example, CN-U-87206253 (Patent Document 1)).
Moreover, when an adjustment position of the balance with balance spring is in the vicinity of a neutral position or when the amount of which is armed the balance spring is small, it is possible that the balance with balance spring cannot be restarted even when the balance spring adjustment is released (this adjustment is terminated). Therefore, it is desired to develop a mechanism capable of smoothly restarting the operation of the balance with balance spring by applying movement to the balance with balance spring when the adjustment of the balance with balance spring is released.
Summary of the invention
[0004] One aspect of the present application is to provide a balance adjustment mechanism capable of smoothly restarting operation of a balance with sprung balance, a timepiece movement comprising the balance adjustment mechanism, as well as a timepiece.
A balance adjustment mechanism according to the request comprises: a winding stem carried by a plate; an adjustment lever arranged to pivot relative to the plate for a displacement of the winding stem in an axial direction; an adjustment wheel rocker arranged to be in engagement with the adjustment lever and to pivot for pivoting of this adjustment lever; a transmission wheel carried by the adjusting wheel rocker and arranged to transmit a rotation of the winding stem to an indicating member when the adjusting wheel rocker is placed in a predetermined position; and a cog adjusting lever arranged to be in engagement with the adjusting wheel rocker and adapted to be movable, for pivoting of the adjusting wheel rocker, between an adjusting position, in which the wheel adjusting lever comes into contact with a balance with balance spring, and a withdrawn position, in which the gear adjustment lever is away from the balance with balance spring.
[0006] According to the request, the cog adjustment lever to come into contact with the balance with balance spring is provided as a separate element of the adjustment wheel rocker. Therefore, the cog adjusting lever can come into contact with and be separated from the balance wheel with balance spring with a different movement than that of the adjusting wheel rocker. Thus, it becomes easy to move the cog adjustment lever so as to apply movement to the balance with balance spring when the balance with balance spring adjustment is released (this adjustment is terminated). As a result, it is possible to restart the operation of the balance with the balance spring in a smooth manner.
In the balance adjustment mechanism defined above, the wheel adjustment lever may include a guided part (which is) guided by the plate and may be provided to be pivotable relative to the adjustment wheel rocker at level with a portion of engagement with the adjustment wheel rocker, and when the gear adjustment lever is moved from the adjustment position, to the withdrawn position, while in contact with the balance wheel with balance spring , the guided portion may be guided by the stage and moved along a path of the engaging portion between the gear adjustment lever and the adjustment wheel rocker.
[0008] According to demand, it is possible to move the cog adjustment lever in a substantially parallel manner in a state where the cog adjustment lever is in contact with the balance with balance spring. As a result, when the cog adjusting lever is moved from the adjusting position to the withdrawn position, the balance with balance spring can be rotated so as to follow the movement of the cog adjusting lever to apply. a balance movement with balance spring. As a result, it is possible to restart the operation of the balance with the balance spring in a smooth manner.
In the balance adjustment mechanism defined above, the gear adjustment lever may be located at the plate, on one side of this plate, namely on the same side as the balance with balance spring depending on the direction of the thickness of the plate, and at least part of the adjustment wheel rocker may be located at the plate, on one side of this plate, namely on the side opposite to the gear wheel adjustment lever in the direction of the thickness.
When the entire adjustment wheel rocker is located at the plate, on one side of this plate, namely on the same side as the wheel adjustment lever in the direction of the thickness, the arrangement of a finishing gear which transmits energy to the balance with balance spring is limited by the adjusting wheel rocker. Depending on the request, since the adjusting wheel rocker is located at the turntable, on one side of this turntable, namely the side opposite to the finishing gear, it is possible to avoid a decrease in the basic performance of a timepiece movement due to a decrease in the degree of freedom regarding the arrangement of the finishing gear.
In the balance adjustment mechanism defined above, in a process of being moved from the withdrawn position to the adjustment position, the wheel adjustment lever can come into sliding contact with a step of the plate to be guided according to the direction of the thickness of the plate, and can come into contact with the balance with balance spring from the direction of the thickness.
According to the request, since the trajectory of the actuation of the gear wheel adjustment lever passes in front of or behind the balance with balance spring when looking in the direction of the thickness of the plate, the degree of freedom The arrangement of the components around the cog adjusting lever can be improved. Further, since the cog adjusting lever is guided in the direction of the thickness of the plate by the step of the plate, it is possible to obtain a structure in which the cog adjusting lever can be moved according to the step. direction of the plate thickness without providing a new separate component.
A timepiece movement according to the request comprises a balance adjustment mechanism as defined above; platinum; and a balance with a balance spring pivotally carried by the plate.
A timepiece according to demand comprises a timepiece movement as defined above.
[0015] According to demand, it is possible to provide a timepiece movement and a timepiece which are able to gently restart the operation of a balance with a balance spring.
According to the request, it is possible to provide a balance adjustment mechanism, a timepiece movement and a timepiece which are able to smoothly restart operation of a balance with balance spring. .
Brief description of the drawings
FIG. 1 is a plan view showing a timepiece according to a first embodiment. Fig. 2 is a plan view of a movement according to the first embodiment as seen from the front side. Fig. 3 is a plan view of the movement according to the first embodiment as seen from the rear side. Fig. 4 is a perspective view of a balance adjusting mechanism according to the first embodiment as seen from the rear side. Fig. 5 is a perspective view of the balance adjusting mechanism according to the first embodiment as seen from the front side. Fig. 6 is a perspective view of part of the movement according to the first embodiment as seen from the front side. FIG. 7 is an explanatory view of the operation of the balance adjusting mechanism according to the first embodiment. FIG. 8 is an explanatory view of the operation of the balance adjusting mechanism according to the first embodiment. FIG. 9 is an explanatory view of the operation of the balance adjusting mechanism according to the first embodiment. Fig. 10 is an explanatory view of the operation of the balance adjusting mechanism according to the first embodiment. Fig. 11 is a plan view of a balance adjusting mechanism according to a second embodiment as seen from the front side. Fig. 12 is a view showing part of a sectional view taken along line XII-XII of Fig. 11. Fig. 13 is an explanatory view of the operation of the balance adjusting mechanism according to the second embodiment. Fig. 14 is an explanatory view of the operation of the balance adjusting mechanism according to the second embodiment. Fig. 15 is an explanatory view of the operation of the balance adjusting mechanism according to the second embodiment.
Description of the embodiments
In what follows, embodiments of the invention will be described with reference to the drawings. In the following embodiments, 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". When a dial and hands have been attached to the movement and everything has been placed in a timepiece box, the finished product is called a complete timepiece. Among the two sides of the plate which constitutes a frame plate of the timepiece, depending on the direction of the thickness, the side where the glass of the timepiece case is provided (that is, say the side where the dial is provided) is called the “back side” of the movement. Furthermore, of the two sides of the plate, the side where the bottom of the timepiece case is provided (ie the side opposite the dial) is called the “front side” of the movement. In the embodiment, the direction from the dial to the caseback is defined as the upper side and the opposite side is defined as the lower side.
First embodiment
FIG. 1 is a plan view showing a timepiece according to a first embodiment.
As shown in Figure 1, a complete timepiece 1 comprises a movement 10 (corresponding to what is called a "timepiece movement" in the appended claims), a dial 3 having a graduation for the indication at least one rotating item of time information, as well as indication elements comprising an hour hand 5, a minute hand 6 and a seconds hand 7 which are provided in a timepiece case formed by a rear watch case (not shown) and a crystal 2. The dial 3 is provided with a date window 3a to clearly show a date character 40a visible on a date indicator 40, which will be described later.
Figure 2 is a plan view of a movement according to the first embodiment as seen from the front side. In FIG. 2, certain components constituting the movement 10 have been omitted, in order to make the drawing easier to view.
As shown in Figure 2, the movement 10 includes a plate 11forming a frame plate. A winding stem 51 is incorporated in the plate 11. The winding stem 51 is carried so as to be rotatable on an axis L, in a winding stem guide hole formed in the plate 11, and to be movable in the axial direction. of this L axis (called the direction of the L axis in what follows). A crown 4 is connected to the winding stem 51, outside the timepiece case shown in FIG. 1. The movement 10 comprises a finishing gear 12 and an escapement regulator 13, on the front side of the watch. platinum 11.
The finishing gear 12 transmits a torque to the escapement regulating device 13. The finishing gear 12 comprises mainly a pair of barrel assemblies 20A and 20B, a return wheel 21, a medium-sized mobile 22, a mobile of average 23, a second mobile 24 and an intermediate escape wheel 25. The two barrel assemblies 20A and 20B are arranged side by side in a plan view when looking in the direction of the thickness of the plate. Each of the barrel assemblies 20A and 20B is pivotally carried between the plate 11 and a balance bridge (not shown). Each of the barrel assemblies 20A and 20B includes a barrel 20a which houses a mainspring therein, as well as a ratchet 20b arranged coaxially with the barrel 20a and rotatable relative to this barrel 20a. An outer end of the mainspring is fixed to the barrel 20a, while an inner end of the mainspring is fixed to the ratchet 20a. It follows that a torque linked to the unwinding (disarming, unwinding) of the mainspring rotates the barrel 20a and the ratchet 20b relative to each other, while the barrel is rotated. 20a and the ratchet 20b relative to each other in a predetermined direction to arm the mainspring.
The ratchet 20b of the first barrel assembly 20A meshes with an intermediate ratchet wheel 27. The intermediate ratchet wheel 27forms part of a manual winding gear 14. The manual winding gear 14 transmits a rotation of the winding stem 15 to the ratchet 20b of the first barrel assembly 20A. As a result, the rotation of the winding stem 51 rotates the ratchet of the first barrel assembly 20A, and the mainspring is charged. A toothing of the barrel 20a of the first barrel assembly 20A meshes with a toothing of the barrel 20a of the second barrel assembly 20B. The torque associated with unwinding (disarming, unwinding) of the mainspring of the first barrel assembly 20A rotates the barrel 20a of the second barrel assembly 20B, and the mainspring of this second barrel assembly 20B is loaded. . Then, the unwinding (disarming, unwinding) of the mainspring of the second barrel assembly 20B rotates the ratchet 20b of this other barrel assembly 20B.
The return wheel 21, the large average mobile 22, the average mobile 23, the second mobile 24 and the intermediate escape wheel 25 are pivotally retained between the plate 11 and the gear bridge (not shown) . When an elastic return force of the armed mainspring rotates the ratchet 20b of the second barrel assembly 20B, the idler wheel 21, the large average wheel 22, the average wheel 23, the seconds wheel 24 and the wheel d The intermediate exhaust 25 are rotated based on the rotation.
In other words, the return wheel 21 engages with the ratchet 20b of the second barrel assembly 20B and is rotated according to the rotation of the ratchet 20b. The large average mobile 22 engages with the return wheel 21 and is rotated according to a rotation of the return wheel 21. The average mobile 23 meshes with the large average mobile 22 and is rotated according to a rotation of the mobile of large average 22. The mobile of seconds 24 meshes with the mobile of average 23 and is driven in rotation as a function of a rotation of the mobile of average 23. The axis of rotation of the mobile of seconds 24 is orthogonal to the axis L of the winding stem 51. The seconds hand 7 visible in FIG. 1 is attached to the seconds mobile 24, and this seconds hand 7 indicates the seconds according to a rotation of the seconds mobile 24. The seconds hand 7 performs one revolution per minute, at a speed of rotation set by the escapement regulating device 13. The intermediate escape wheel 25 engages with the second mobile 24 and is rotated according to the rotation of the mobile seconds 24. The intermediate escape wheel 25 engages with an escape pinion (not shown) of an escape wheel set, which will be described later.
The escapement regulating device 13 controls the rotation of the finishing gear 12. The escapement regulating device 13 essentially comprises an escapement mobile and an anchor which are not shown, as well as a sprung balance 32 (corresponding to this which is called "balance with balance spring" in the appended claims). The torque transmitted from the driving springs of the barrel assemblies 20A and 20B, via the finishing gear 12, turns the exhaust mobile. The anchor means that the escape mobile is regularly free and driven in rotation. The sprung balance 32 makes that the mobile escapement is released at a constant speed.
The sprung balance 32 includes a balance shaft (not shown), a balance wheel 33 and a balance spring 34. The balance shaft is rotatably and pivotally retained between the plate 11 and a cock (not shown) . The balance shaft is caused to pivot alternately around a first axis O1, according to a constant cycle, with the use of the balance spring 34 as a power source. The balance wheel 33 is fixed coaxially with the balance shaft. The balance wheel 33 comprises a rim 33a surrounding the balance shaft externally in the radial direction, as well as arms 33b radially connecting the rim 33a and the balance shaft. The rim 33a is arranged coaxially with the first axis O1. Four arms 33b are provided with an interval of 90 ° between them around the first axis O1. The shape of the balance wheel 33 is not limited to the example shown and can be freely modified. The whole of the sprung balance 32 is disposed on one side of the axis L in the plan view.
Figure 3 is a plan view of the movement according to the first embodiment as seen from the rear side. In FIG. 3, in order to make the drawing easier to look at, certain components constituting the movement 10 have been omitted and only part of the date indicator 40 has been shown.
As shown in Figure 3, the movement 10 comprises a timer cog 15, a calendar mechanism 16, a time setting cog 17 and a calendar corrector adjustment mechanism 18 on the rear side of the plate 11 .
The timer gear 15 comprises essentially a center wheel 36, a minute wheel 37 and an hour wheel 38. The center wheel 36 is arranged coaxially with the seconds wheel 24 (see FIG. 2). The center wheel 36 meshes with the mean wheel 23 (see figure 2) and is rotated according to the rotation of this mean wheel 23. The minute hand 6 visible in figure 1 is attached to the center wheel 36, and this minute hand 6 indicates the minutes as a function of the rotation of the center wheel 36. The minute hand 6 performs one revolution per hour, at a speed of rotation set by the escapement regulating device 13. minutes 37 meshes with the center wheel 36 and is driven as a function of the rotation of this center wheel 36. The hour wheel 38 is arranged coaxially with the center wheel 36. The hour wheel 38 meshes with the minute wheel 37 and is driven in rotation as a function of the rotation of this minute wheel 37. The hour hand 5 visible in FIG. 1 is attached to the hour wheel 38, and this hour hand 5 indicates the hours as a function of the rotation of the wheel h eures 38. The hour hand performs one revolution in 12 hours, at a speed of rotation set by the escapement regulating device 13.
The calendar mechanism 16 includes the date indicator 40, a first intermediate date wheel 41, a second intermediate date wheel 42, and a date indicator drive wheel 43. The date indicator 40 is an element ring-shaped and is rotatably attached to plate 11. The date character 40a (see figure 1) represents one of the dates ranging from 1 to 31 arranged in order along the circumferential direction, on the indicator. date indicator 40. Teeth are provided on an inner peripheral surface of the date indicator 40. These teeth project radially inward and are provided at intervals in the circumferential direction.
The first intermediate date wheel 41, the second intermediate date wheel 42 and the date indicator drive wheel 43 are rotatably carried by the plate 11. The first intermediate date wheel 41 meshes with the hour wheel 38et is rotated as a function of the rotation of the hour wheel 38. The second intermediate date wheel 42 meshes with the first intermediate date wheel 41 and is rotated as a function of the rotation of this first intermediate date wheel 41. The date indicator drive wheel 43 includes a date tooth 43a and a date lug 43b. The date toothing 43a meshes with the second intermediate date wheel 42 and performs one revolution in 24 hours as a function of the rotation of this second intermediate date wheel 42. The date lug 43b performs a revolution in 24 hours around a center of rotation of the date toothing 43a, with this date toothing 43a as the power source. The date pin 43b engages with a tooth of the date indicator 40 once at each revolution, in order to rotate the date indicator 40 by one step (of one tooth). Thus, the calendar mechanism 16 intermittently rotates the date indicator 40.
The time setting gear 17transmets the rotation of the winding stem 51 to the hour hand 5et to the minute hand 6 at the time of the time correction. The time setting gear 17 comprises a setting wheel 45, an intermediate minute wheel 46 and a time setting transmission wheel 47. The setting wheel 45 is provided so as to mesh with a sliding pinion 52 (see FIG. 4), which will be described later. The intermediate minute wheel 46 is rotatably carried by an adjusting wheel rocker 90, which will be described later. The intermediate minute wheel 46 comprises a first intermediate minute toothing 46a (see FIG. 5) and a second intermediate minute toothing 46b. The first intermediate minute toothing 46a and the second intermediate minute toothing 46b rotate integrally. The first intermediate minute toothing 46a engages permanently with the adjusting wheel 45. Thus, the first intermediate minute toothing 46a and the second intermediate minute toothing 46b are rotated as a function of the rotation of the adjusting wheel 45. The time setting transmission wheel 47 permanently meshes with the second intermediate minute toothing 46b and is rotated as a function of the rotation of the intermediate minute wheel 46. The time adjustment transmission wheel 47 is provided so as to mesh with the 37 minute wheel.
The calendar corrector adjustment mechanism 18 transmits the rotation of the winding stem 51 to the date indicator 40 when the date is corrected. The calendar corrector adjustment mechanism 18 comprises a first date corrector adjustment transmission wheel 48 and a second date corrector adjustment transmission wheel 49, in addition to the adjustment wheel 45 and the intermediate minute wheel 46. The first date corrector adjustment transmission wheel 48 is provided so as to mesh with the first intermediate minute toothing 46a. The first date corrector adjustment transmission wheel 48 meshes with the first intermediate minute toothing 46a so as to be rotated according to the rotation of the intermediate minute wheel 46. The second date corrector adjustment transmission wheel 49 meshes with the first date corrector adjustment transmission wheel 48 and is rotated according to this first date corrector adjustment transmission wheel 48. The second date corrector adjustment transmission wheel 49 is carried by a rocker (not shown). ) which rocks around the center of rotation of the first date corrector adjustment transmission wheel 48 with the rotation of the first date corrector adjustment transmission wheel 48. The second date corrector adjustment transmission wheel 49 is moved so as to approach the date indicator 40 with the rotation of the first corrector adjustment transmission wheel of da te 48 in a predetermined direction, and meshes a tooth of the date indicator 40. Thus, the calendar corrector adjusting mechanism 18 rotates the date indicator 40.
As shown in Figures 2 and 3, the movement 10 further comprises a balance adjustment mechanism 19. The balance adjustment mechanism 19 includes a switching mechanism 50 and a balance adjustment lever 100 (corresponding to what is called “Cog adjusting lever” in the appended claims).
Figure 4 is a perspective view of the balance adjustment mechanism according to the first embodiment as seen from the rear side. Fig. 5 is a perspective view of the balance adjusting mechanism according to the first embodiment as seen from the front side. In FIG. 4, a lever holder 80 is represented by a virtual line (dashed line with two points) so that the drawing is easier to view. Further, in Fig. 5, a balance adjustment lever holder 110 is shown as a virtual line (two-dot dashed line) so that the drawing is easier to view.
As shown in Figures 3 and 4, the switching mechanism 50 switches the torque transmission path of the winding stem 51. The switching mechanism 50 includes the winding stem 51, the sliding pinion 52, an adjustment lever 60 , a lever 70, the lever holder 80 and the adjusting wheel rocker 90.
As mentioned above, the winding stem 51 is provided so as to be movable in the direction of the axis L, relative to the plate 11, accompanying a pulling actuation of the crown 4 (see Figure 1) . In the present embodiment, the winding stem 51 can be placed in three positions, namely a position without any offset which is the deepest inside the movement 10, a position with one offset pitch in which the crown 4 is. taken one step from the no-offset position, and a two-step offset position in which the crown 4 is taken one step from the one-step offset position. A thinned portion 51a for engagement with the adjustment lever 60 is provided in the winding stem 51. The following description is based on the assumption that the winding stem 51 is in the position with no offset unless the contrary is true. specified.
The winding stem 51 is provided with a winding pinion 53. The winding pinion 53 is provided at a position which is closer to a center of the movement 10 than is the thinned portion 51a. In the present embodiment, the center of the movement 10 is the center of rotation of the indicating elements and it is the axis of rotation of the seconds mobile 24, of the center wheel 36 and of the hours wheel 38. Winding pinion 53 is provided so as to be rotatable relative to the winding stem 51 and not to be movable in the direction of the axis L, relative to the winding stem 51. A crown wheel 28 (see figure 2) provided in the manual winding gear train 14 meshes with the winding pinion 53.
The sliding pinion 52est extrapolated to the winding stem 51 and is arranged coaxially with the axis L. The sliding pinion 52 is placed closer to the center of the movement 10 than is the winding pinion 53. The sliding pinion 52is rotatable integrally with the winding stem 51 and is provided so as to be movable in the direction of the axis L, relative to the winding stem 51. The sliding pinion 52 is arranged for, being moved in the direction of axis L with respect to the winding stem 51, make a change between a state of engagement with the winding pinion 53 in the direction from the inside to the outside of the movement 10 and a state of engagement with the winding wheel. adjustment 45 from the outside to the inside of the movement 10.
The adjustment lever 60 is intended to be pivoted about a second axis 02, relative to the plate 11. The adjustment lever 60 comprises an adjustment lever shaft 61 as a shaft, as well as a main body adjustment lever 62 carried by the adjustment lever shaft 61. The adjustment lever shaft 61 is placed on the same side as the sprung balance 32 (see figure 2) with respect to the axis L, in the view in plan. The adjustment lever shaft 61 is placed so as to enter the plate 11.
The main adjustment lever body 62est placed at the plate 11, on the side opposite the sprung balance 32 (rear side) in the direction of the thickness of the plate 11. The main adjustment lever body 62a la forms a thin plate and extends in a surface direction of the plate 11. The main adjustment lever body 62 includes a head 63 and a shank 64 extending from a connection portion with the lever shaft. adjustment 61. The head 63 has an elliptical shape. The head 63 is positioned so as to pass to one side of the L axis in the plan view. The head 63 is positioned in the thinned portion 51a of the winding stem 51. As a result, the adjustment lever 60 is engaged with the winding stem 51 according to the direction of the axis L and pivots for a movement of the winding stem. 51 accompanying a pulling maneuver of the crown 4. In what follows, among the directions of pivoting of the adjustment lever 60, the direction of pivoting when the winding stem 51 is moved from the position without any shift towards the position two steps away. offset is called the first direction of pivoting M1, and conversely, the direction of pivoting when the winding stem 51 is moved from the position with two offset steps to the position without any offset is called the second direction of pivoting M2 . The shank 64 extends from the connection portion with the adjustment lever shaft 61, on the side opposite the head 63. An engaging protrusion 65 is provided in the shank 64. The engaging protrusion 65 is provided at level d. 'an intermediate portion according to the direction in which the shank 64 extends. The engagement projection 65 is projecting in the first direction of pivoting M1, towards the side with the axis L in the plan view. The engaging protrusion 65 is provided so as to approximate the L axis in the plan view when the adjusting lever 60 is rotated in the first pivoting direction M1.
The adjustment lever 60 includes an adjustment lever pin 66 and an adjustment wheel rocker actuating pin 67. The adjustment lever pin 66 is disposed near the engaging projection 65 of the tail 64. The pin of adjustment lever 66 is protruding from the shank 64, in the direction opposite to the plate 11 (towards the rear side). The adjuster wheel rocker actuator pin 67 is positioned near one end at the end of the shank 64. The adjuster wheel rocker actuator pin 67 is protruding from the shank 64, toward the end. plate 11 (towards the front side). The adjustment wheel rocker actuator lever 67 engages the adjustment wheel rocker 90.
The lever 70est provided so as to be pivoting about a third axis 03, relative to the plate 11. The third axis 03est disposed on the side opposite the second 02, with the axis L sandwiched between them in the plan view. The lever 70 includes a lever main body 71 pivotally carried by a support shaft protruding from the stage 11, as well as a lever pin 72 attached to the lever main body 71. The lever main body 71 is located at the stage. 11, on the same side as the adjustment lever main body 62. The lever main body 71 has a thin plate shape and extends along the same plane as the adjustment lever main body 62. The lever main body 71 is disposed side by side with the adjustment lever main body 62 in the plan view.
The main lever body 71 comprises a head 73 extending from a connection portion with the support shaft of the plate 11. The head 73 extends so as to cross the winding stem 51 in the plan view. One end at the end of the head 73 is opposite the engagement projection 65du adjusting lever 60, from the first direction of pivot M1. When the engagement projection 65 of the adjustment lever 60 is moved in the first direction of pivoting M1, the head 73 is pushed against the engagement projection 65 and is pivoted to the side with the center of movement 10. As a result, the lever 70 is pivoted with a pivoting of the adjustment lever 60. In other words, the lever 70 is pivoted with a movement of the winding stem 51 accompanying a pulling actuation of the crown 4. More precisely, the lever 70 is pivoted when the winding stem 51 is moved between the position with no offset and the position with one offset. The lever pin 72 protrudes from the lever main body 71, in the direction opposite to the plate 11. A lever return spring 83, which will be described later, contacts the lever pin 72.
Here, an intermediate portion of the head 73du main body of lever 71, between an end end and a proximal end, is located at a thinned portion of the sliding pinion 52. In this way, the lever 70 is in engaged with the sliding pinion 52 in the direction of the L axis. When the head 73 is pushed against the engaging projection 65 of the adjusting lever 60, the lever 70 moves the sliding pinion 52 in the direction opposite to the winding pinion 53. When the winder 51 is placed in the position without any offset, the lever 70 causes the sliding pinion 52 to mesh with the winding pinion 53. When the winding stem 51 is placed in a range going from the position at one offset step to the two-step position. no offset, the lever 70 causes the sliding pinion 52 to mesh with the adjusting wheel 45.
The lever holder 80 pushes the adjustment lever 60 and the lever 70 towards the side with the plate 11. The lever holder 80 has the shape of a thin plate and extends along a surface direction of the plate. 11. The lever holder 80 comprises a base 81 attached to the plate 11, four arms 82A, 82B, 82C and 82D extending from the base 81, and the lever return spring 83, which extends to. from the base 81. The base 81 is placed on the side opposite to the plate 11, with the main lever body 71 interposed between them. The base 81 is disposed on the opposite side of the adjustment lever main body 62, relative to the L axis, in the plan view. The base 81 covers the connecting portion of the main lever body 71 with the support shaft of the plate 11, in the plan view. The base 81 is closer to the center of the movement 10 than is the lever pin 72. The base 81 is fixed to the plate 11 by two screws. The four arms 82A, 82B, 82C and 82D extend from the base 81, to the side with the axis L, in the plan view, respectively.
The first arm 82A crosses the axis L in the plan view and covers the head 63du adjustment lever 60. The first arm 82A urges a proximity of the connection portion of the main body of adjustment lever 62 with the shaft adjustment lever 61 to the side with the plate 11. The second arm 82B extends from the base 81, with a distance from the first arm 82A towards the central side of the movement 10 relative to the first arm 82A, in the view in plan. The second arm 82B is in front of the winding pinion 53, from the side with the center of the movement 10. As a result, the second arm 82B adjusts the displacement of the winding pinion 53 to the side with the center of the movement 10.
The third arm 82C extends from the base 81, with a distance from the second arm 82B towards the central side of the movement 10 with respect to the second arm 82B, in the plan view. The third arm 82C crosses the L axis in the plan view. The third arm 82C covers the head 73 of the lever 70 and the head 63 of the adjustment lever 60 in the plan view. The third arm 82C is intended to be flexibly deformable in a surface direction of the plate 11. A tip at one end of the third arm 82C is in front of and in contact with the adjustment lever pin 66 from the first direction of the arm. M1 pivoting. As a result, the third arm 82C urges the adjustment lever 60 in the opposite direction to the direction of movement of the adjustment lever 60 accompanying a pulling actuation of the crown 4. Three engagement recesses 84a, 84b and 84c are formed side by side. rib in a side surface from the tip to one end of the third arm 82C, opposite the adjustment lever pin 66 (see Figure 7). The three engagement hollows 84a, 84b and 84c follow one another with first the first engagement hollow 84a, then the second engagement hollow 84b, then the third engagement hollow 84c when one goes from end to end to a base of the third arm 82C. Adjustment lever pin 66 is provided to engage these engagement recesses 84a, 84b and 84c. A smooth first engagement ridge 85a (see Figure 7) is provided between the first engagement recess 84a and the second engagement recess 84b. A second smooth engagement ridge 85b (see Figure 7) is provided between the second engagement hollow 84b and the third engagement hollow 84c.
The fourth arm 82D extends from the base 81, with a distance from the third arm 82C towards the central side of the movement 10 with respect to the third arm 82C, in the plan view. The fourth arm 82D crosses the L axis in the plan view. The fourth arm 82D covers the head 63 of the adjustment lever 60 in the plan view. A through hole, into which a pin protruding from the plate 11 is inserted, is provided at one end at one end of the fourth arm 82D. In this way, the end at the end of the fourth arm 82D is positioned in a surface direction of the plate 11.
The lever return spring 83 extends from the base 81, with a substantially constant width. The lever return spring 83 extends from the base 81 such that one end thereof is between the base 81 and the lever pin 72, in the plan view. The tip at one end of the lever return spring 83 is in contact with the lever pin 72, from the side with the center of movement. The lever return spring 83 urges the lever 70 in the direction in which the head 73 of the lever 70 goes towards the engaging projection 65 of the adjustment lever main body 62.
The adjusting wheel rocker 90se is at the plate 11, on the same side as the adjusting lever 60. The adjusting wheel rocker 90is provided so as to be pivotable about a fourth axis 04, relative to the plate 11. The fourth axis 04 is orthogonal to the axis L, closer to the outside of the movement 10 than the axis of rotation of the second mobile 24. The adjustment wheel rocker 90 is pivoted with a pivoting of the adjustment lever 60. The adjusting wheel rocker 90 comprises a rocker shaft 91 supported by the support shaft projecting from the plate 11, as well as a rocker main body 92 carried by this rocker shaft 91. The rocker shaft 91 has a rocker shaft 91. cylindrical shape and is extrapolated to the support shaft of the plate 11 so as to be relatively rotatable. A radially outwardly projecting flange 91a is provided on an outer peripheral surface of the rocker shaft 91. The rocker main body 92 has a thin plate shape. The rocker main body 92 includes a pivoting portion 93 carried by the rocker shaft 91, an engaging portion 94 in engagement with the adjustment lever 60, as well as a connecting portion 95 which connects the pivoting portion 93 and the engaging portion. in gear 94.
The pivoting portion 93 extends along a surface direction of the plate 11. The pivoting portion 93 is disposed on the side of the center of the movement 10, relative to the fourth shaft 82D of the lever holder 80 in the plan view , and is in the same plane as this fourth shaft 82D. A through hole, in which the rocker shaft 91 is inserted, is provided in the pivoting portion 93. The pivoting portion 93 covers the flange 91a of the rocker shaft 91, on the side of the plate 11. The engaging part 94 is closer to the outside of the movement 10 than is the pivoting portion 93. The engaging portion 94 extends along a surface direction of the stage 11, on the same side as the stage with respect to. the pivoting portion 93. The engaging portion 94 is closer to the stage 11 than is the adjustment lever main body 62. The engaging portion 94 covers the adjustment lever main body 62 in the plan view. . The engaging portion 94 is disposed on the same side as the adjustment lever main body 62, with respect to the L axis, in the plan view. The connecting portion 95 extends from the pivoting portion 93, toward the engaging portion 94, with a substantially constant width in the plan view. The connection portion 95 crosses the fourth arm 82D of the lever holder 80 in the plan view. The connecting portion 95 extends from the pivoting portion 93 parallel to the pivoting portion, then bends sideways with the plate 11 so as to bypass the fourth arm 82D and extends parallel to the engaging portion 94 to connect with. the engaging portion 94. In the following, among the pivotal directions of the adjusting wheel rocker 90, the direction in which the engaging portion 94 is away from the L-axis in the plan view is called the third direction of pivoting M3 and the opposite direction of this third direction of pivoting M3 is called the fourth direction of pivoting M4.
An adjustment lever engagement window 96, in which the adjustment wheel rocker actuating pin 67 of the adjustment lever 60 is inserted, is provided in the engaging portion 94. The adjustment window adjusting lever engagement 96 extends with a substantially constant width, which is greater than an outer diameter of the adjusting wheel rocker actuating pin 67 so as to be able to guide that actuating pin adjustment wheel rocker 67. The adjustment lever engagement window 96 includes a first segment 96a, in which the adjustment wheel rocker actuator pin 67 moves when the winding stem 51 is moved between the non-stepped position. offset and position at one offset step, as well as a second segment 96b and a third segment 96c in which the adjustment wheel rocker actuator pin 67 passes when the winding stem 51 is moved between the position. position at one step offset and the position at two step offset. The first segment 96a extends in an arcuate shape along a direction parallel to the first direction of pivoting M1 and to the second direction of pivoting M2 (i.e. an arc around the second axis 02), in the view in plan. The second segment 96b extends one end of the first segment 96a in the first direction of pivoting M1. The second segment 96b extends from the first segment 96a, in the first direction of pivoting M1et in the fourth direction of pivoting M4. The third segment 96c extends one end of the second segment 96b in the first direction of pivoting M1. The third segment 96c extends in an arcuate shape, from the second segment 96b, along the first direction of pivoting M1.
The adjustment wheel rocker 90 carries the adjustment wheel 45, the intermediate minute wheel 46 and the time adjustment transmission wheel 47. The adjustment wheel 45 is rotatably carried by the rocker shaft 91 Therefore, the axis of rotation of the adjusting wheel 45 coincides with the fourth axis 04. The adjusting wheel 45 is disposed between the pivoting portion 93 of the rocker main body 92 and the plate 11. The intermediate minute wheel 46 is so carried. rotating by the pivoting portion 93. The first intermediate toothing of the minutes 46a is located on the side of the adjusting wheel 45, relative to the pivoting portion 93 according to the direction of the thickness of the plate 11. The second intermediate toothing of the minutes 46b is disposed on the side opposite to the first intermediate toothing of the minutes 46a, with the pivoting portion 93 interposed between them in the direction of the thickness of the plate 11. The first intermediate toothing of the minutes tes 46a and the second intermediate toothing of the minutes 46b are connected to one another so as to rotate as a single piece (be integral), via a rotation shaft entering the pivoting portion 93. The adjustment transmission wheel the time 47 is rotatably carried by the pivoting portion 93. The time setting transmission wheel 47 is disposed on the side of the second intermediate toothing of the minutes 46b, relative to the pivoting portion 93 according to the direction of the thickness. plate 11.
Figure 6 is a perspective view of part of the movement according to the first embodiment as seen from the front side. In FIG. 6, the balance adjustment lever support 110 has not been shown and a lever base 101 and a spring body 102 of the balance adjustment lever 100 have been shown in virtual lines (phantom with two dots) in order to make the drawing easier to view.
As shown in Figures 4 and 6, the adjustment wheel rocker 90 includes a balance adjustment lever actuation pin 97. The balance adjustment lever actuation pin 97 is positioned in the setting portion. socket 94. The balance adjustment lever actuating pin 97 protrudes from the engaging portion 94, to the side with the platen 11. The balance adjustment lever actuating pin 97 is inserted into a through hole 11a provided in the plate 11, and penetrates from the rear side to the front side of the plate 11. The through hole 11a of the plate 11 is provided so as to prevent the balance adjustment lever actuating pin 97 from being moved with a adjustment wheel rocker pivot 90. Balance wheel adjustment lever actuator pin 97 is in engagement with balance wheel adjustment lever 100 on the front side of stage 11.
As shown in Figures 4 and 5, the balance adjustment lever 100se is at the plate 11, on the same side as the sprung balance 32 (front side) in the direction of the thickness of the plate 11. The Balance wheel adjustment lever 100 is arranged to cover the rocker main body 92 with the adjustment wheel rocker 90 in the plan view. The balance adjustment lever 100 is moved with a pivoting of the adjustment wheel rocker 90. The balance adjustment lever 100 includes the lever base 101 and the spring body 102 having a proximal end connected to the lever base 101. The lever base 101 is in the form of a thin plate and extends along a surface direction of the plate 11. The lever base 101 is provided with a through hole in which the lever operating pin adjustment wheel 97 of the adjustment wheel rocker 90 is inserted. The lever base 101 engages with the adjustment wheel rocker 90 by inserting the balance adjustment lever actuator pin 97 into this through hole. The lever base 101 is pivoted with respect to the balance adjustment lever actuator pin 97. In the present embodiment, the balance adjustment lever actuator pin 97 protrudes slightly from the lever base 101. , on the side opposite to plate 11.
The spring body 102 has the shape of a thin plate. The spring body 102 is arranged such that its two major surfaces are oriented in a surface direction of the plate 11. The spring body 102 is intended to be flexible in a plane having the surface directions of the plate 11. In In this embodiment, the spring body 102 is connected to the lever base 101 via an arched portion 103 and is integrally with the lever base 101. The spring body 102 extends along of the third direction of pivot M3, from the connection portion with the lever base 101. The spring body 102 extends linearly in the plan view. The spring body 102 is disposed between the sprung balance 32 and the fourth axis 04, in the plan view, so as to pass in front of the rim 33a (see FIG. 2) of the balance wheel 33 of the sprung balance 32 when one looks along a surface direction of plate 11.
The balance adjustment lever 100 comprises a balance adjustment lever guide pin 104 (corresponding to what is called a "guided part" in the appended claims). The balance adjustment lever guide pin 104 is placed on the outside of the balance adjustment lever actuating pin 97 of the adjustment wheel rocker 90, in the radial direction centered on the fourth axis 04. The pin balance adjustment lever guide pin 104 is disposed in the third direction of pivoting M3 with respect to the balance adjustment lever actuating pin 97. The balance adjustment lever guide pin 104 lever base size 101 , to the side with the plate 11. In the present embodiment, the balance adjustment lever guide pin 104 is inserted into a through hole provided in the lever base 101, and protrudes slightly from the lever base. 101, on the side opposite to plate 11.
As shown in Figure 6, the plate 11 is provided with an adjustment lever guide window 11b, in which the balance adjustment lever guide pin 104 is inserted. The adjustment lever guide window 11b extends with a substantially constant width greater than the outer diameter of the balance adjustment lever guide pin 104 so as to be able to guide this adjustment lever guide pin balance 104. The adjustment lever guide window 11b extends outwardly in a radial direction centered on the fourth axis 04 from one end of the fourth direction of pivoting M4, towards the third direction of pivoting M3, and s' then extends in the third direction of rotation.
As shown in Figures 4 and 5, the balance adjustment lever 100 is retained on the side of the plate 11 by the balance adjustment lever support 110 fixed to the plate 11. The balance adjustment lever support 110 has the form of a thin plate and extends along a surface direction of the platen 11. The balance adjustment lever support 110 is arranged so as to avoid the spring body 102 of the balance adjustment lever 100 and passes in front of it. lever base 101 in plan view. A first exhaust window 111 to bypass the balance adjustment lever actuation pin 97 and a second exhaust window 112 to bypass the balance adjustment lever guide pin 104 are provided in the balance adjustment lever holder 110. The first exhaust window 111 has a shape approximately conformed to the shape of the through hole 11a (see Fig. 6) of the plate 11, in the plan view. The second exhaust window 112 has a shape approximately conformed to the shape of the adjustment lever guide window 11b (see Fig. 6) of the plate 11, in the plan view.
Now, we will describe the operation of the switching mechanism 50 with reference to Figures 7 to 10.
Figures 7 to 10 are explanatory views of the operation of the balance adjustment mechanism according to the first embodiment.
As shown in Figure 7, in a state where the winding stem 51 is positioned in the position without any offset, the adjustment lever pin 66 of the adjustment lever 60 is inserted into the first engagement recess 84a of the third arm 82C of the lever holder 80. As a result, the winding stem 51 is positioned in the position without any offset. The head 73 of the lever 70 retains the sliding pinion 52 in such a way that this sliding pinion 52 meshes with the winding pinion 53. Therefore, when the winding stem 51 is rotated in the position without any offset, the sliding pinion 52 is driven. rotating integrally with the winding stem 51, and the winding pinion 53 is in turn driven in rotation by means of the sliding pinion 52. When the winding stem 51 is rotated, the crown wheel 28 meshing with the winding pinion 53is driven in rotation, and the ratchet 20b of the barrel assembly 20A is driven in rotation by means of the manual winding gear 14 (see FIG. 2). As a result, the mainsprings of the barrel assemblies 20A and 20B are armed. The first intermediate minute toothing 46a meshes with the first date corrector adjustment transmission wheel 48. The adjustment wheel rocker actuating pin 67 of the adjustment lever 60 is positioned at one end, in the second pivot direction M2 , of the first segment 96a of the adjustment lever engagement window 96 of the adjustment wheel rocker 90.
When the winding stem 51est moved from the position without any offset to the position at one offset, the adjustment lever 60est pivoted in the first direction of pivoting M1. Then, as shown in Fig. 8, the adjustment lever pin 66 passes over the first engagement ridge 85a, from the first engagement recess 84a of the third arm 82C of the lever holder 80, and enters the chamber. the second engagement recess 84b. At this time, a restoring force of the third arm 82C of the lever holder 80 acts on the adjustment lever 60, and a clicking sensation is generated when a user pulls the winding stem 51 out. When the adjustment lever 60 is rotated in the first direction of rotation M1, the head 73 of the lever 70 is pushed against the engaging projection 65 of the adjustment lever 60 and rotates to the side of the center of movement 10 while resisting a biasing force from the spring. lever return 83 acting on the lever pin 72. As a result, the sliding pinion 52 coupled to the head 73 of the lever 70 is separated from the winding pinion 53 and meshes with the adjusting wheel 45. When the winding stem 51 reaches the position at one point. no offset, the head 73 of the lever 70 withdraws from a rotational path of the engaging projection 65 of the adjustment lever 60, to the side with the center of movement 10.
When the adjustment lever 60 is rotated in the first direction of rotation M1, the adjustment wheel rocker actuating pin 67 moves in the first segment 96a of the adjustment lever engagement window 96 of the adjusting wheel rocker 90, from its end in the second direction of pivoting M2 to its end in the first direction of pivoting M1. Since the first segment 96a extends in a direction parallel to the first pivoting direction M1, the adjusting lever 60 and the adjusting wheel rocker 90 are not engaged with each other, and the adjusting wheel rocker 90 is not out of place.
When the winding stem 51est moved from the position at a step offset to the position without any offset, an operation opposite to that described above is obtained.
In the state where the winding rod 51 is positioned in the one-step offset position, the adjustment lever pin 66 is engaged in the second engagement hollow 84b of the third shaft 82C of the lever holder 80. As a result, the winding stem 51 is positioned in the one-step offset position. The head 73 of the lever 70 retains the sliding pinion 52 in such a way that the sliding pinion 52 meshes with the adjusting wheel 45. Therefore, when the winding stem 51 is rotated in the one-shift position, the sliding pinion 52 is rotated integrally with the winding stem 51, and the adjusting wheel 45 is in turn rotated through the sliding pinion 52. When the adjusting wheel 45 is rotated, the date indicator 40 is rotated through the calendar corrector adjusting mechanism 18. In this way, the date indicator 40 can be rotated to correct the date. In the state where the winding stem 51 is positioned in the one-step offset position, the adjusting wheel rocker actuating pin 67 of the adjusting lever 60 is at the end, in the first direction of pivoting M1, of the first segment 96a of the adjustment lever engagement window 96 of the adjustment wheel rocker 90.
When the winding stem 51est moved from the one-step offset position to the two-step offset position, the adjustment lever 60est pivoted in the first direction of pivoting M1. Then, as shown in Fig. 9, the adjustment lever pin 66 passes over the second engagement peak 85b, from the second engagement recess 84b of the third shaft 82C of the lever holder 80, and s 'engages in the third engagement recess 84c. At this time, a return force from the third arm 82C of the lever holder 80 acts on the adjustment lever 60, and a clicking sensation is generated when a user pulls the winding stem 51 out. The lever 70 maintains a state in which the sliding gear 52 is retained so that this sliding gear 52 meshes with the adjusting wheel 45.
When the adjustment lever 60is rotated in the first direction of pivot M1, the adjustment wheel rocker actuating pin 67 moves in the second segment 96b of the adjustment lever engagement window 96 of the rocker. adjusting wheel 90, from its end in the second direction of pivoting M2 to its end in the first direction of pivoting M1. Since the second segment 96b extends from its end in the second pivoting direction M2 to the first pivoting direction M1 and the fourth pivoting direction M4, the adjusting wheel rocker 90 is pushed in the third pivoting direction M3 by the pin d '. adjustment wheel rocker actuation 67et is rotated in the third direction of pivoting M3. At this time, the adjusting wheel rocker 90 separates the first intermediate minute toothing 46a from the first date corrector adjustment transmission wheel 48, and brings the time adjustment transmission wheel 47 close to the clock wheel. minutes 37. The time setting transmission wheel 47 meshes with the minute wheel 37 when the winding stem 51 reaches the two-step offset position.
After traversing the second segment 96b of the adjustment lever engagement window 96 with the pivoting of the adjustment lever 60 in the first direction of pivoting M1, the adjustment wheel rocker actuating pin 67 moves in the third segment 96c, from its end in the second direction of pivoting M2 to its end in the first direction of pivoting M1. Since the third segment 96c extends along a direction parallel to the first pivoting direction M1, the adjusting lever 60 and the adjusting wheel rocker 90 are not engaged with each other, and this rocker switch adjusting wheel 90 is not rotated.
When the winding stem 51est moved from the two-step offset position to the one-step offset position, an operation opposite to that described above is obtained.
As shown in Figure 10, in the state where the winding stem 51 is in the two-step offset position, the adjustment lever pin 66 is engaged in the third engagement recess 84c of the third arm 82C of the lever holder 80. As a result, the winding stem 51 is positioned in the position with two offset steps. The adjusting wheel rocker actuator pin 67 of the adjusting lever 60 is at the end, in the first direction of pivot M1, of the third segment 96c of the adjusting lever engagement window 96 of the wheel rocker. 90. The head 73 of the lever 70 retains the sliding pinion 52 so that this sliding pinion 52 meshes with the adjusting wheel 45. Therefore, when rotating the winding stem 51 in the two step offset position, the sliding pinion 52 is rotated integrally with the winding stem 51, and the adjusting wheel 45 is in turn rotated through the sliding pinion 52. Since the time setting transmission wheel 47 meshes with the minute wheel 37, when the adjusting wheel 45 is driven in rotation, the minute wheel 37, the center wheel 36 and the hour wheel 38 are driven via the hour adjusting gear 17. Thus, the RO The time setting element 17 can transmit a rotation of the winding stem 51 to the hour hand 5 and the minute hand 6 to correct the hours and minutes indicated by the hour hand 5 and the minute hand 6.
Now, we will describe an operation of the balance adjustment lever 100.
With the movement of the winding stem 51 according to the direction of the axis L, the balance adjustment lever 100 is moved between an adjustment position, in which this balance adjustment lever 100 is in contact with the sprung balance 32 in order to adjust the spring balance 32, and a withdrawn position, in which the balance adjustment lever 100 is remote from the sprung balance 32. The adjustment position corresponds to the two step offset position of the winding stem 51. The withdrawn position corresponds to the one-step offset position and the non-offset position of the winding stem 51, as well as the positions between the one-step offset position and the non-offset position. The specific operation of the balance adjustment lever 100 will be described below.
As shown in Figure 8, the balance adjustment lever guide pin 104 is located at one end of the adjustment lever guide window 11b of the plate 11, in the fourth direction of pivot M4, in the state where the winding stem 51 is in the one-step offset position. In this state, the balance adjustment lever 100 is positioned in its withdrawn position.
As shown in Figure 9, when the winding stem 51 is pulled out, from the one-step offset position to the two-step offset position, the adjustment wheel rocker 90 is rotated in the third direction pivot M3. When the adjusting wheel rocker 90 is rotated in the third pivoting direction M3, a force acts in the third pivoting direction M3, on the balance adjusting lever 100, through the lever actuating pin. balance adjustment 97of the adjustment wheel rocker 90. As a result, the balance adjustment lever 100 begins to move from the withdrawn position to the adjustment position. The balance adjustment lever guide pin 104 of the balance adjustment lever 100 is guided by the adjustment lever guide window 11b of the stage 11 so as to be away from the fourth axis 04, and is then moved in the third direction of Pivot M3, i.e. the direction of movement of the balance adjustment lever actuating pin 97.
When moved away from the fourth axis 04, the balance adjustment lever guide pin 104 is moved non-parallel to the balance adjustment lever actuation pin 97. As a result, the balance lever balance adjustment 100 is moved while the spring body 102 is rotated away from the fourth axis 04. Then, the spring body 102 of the balance adjustment lever 100 comes into contact with the outer peripheral surface of the rim 33a of the wheel. balance 33du sprung balance 32, radially from the outside, and presses on this rim 33a of the balance wheel 33 in a centripetal manner, with a flexural deformation.
Then, during its movement in the third direction of pivot M3, the balance adjustment lever guide pin 104 is moved parallel to the balance adjustment lever actuating pin 97. As a result, the Balance wheel adjustment lever 100 is moved in parallel along the third direction of pivoting M3. At this time, the spring body 102 of the balance adjustment lever 100 is moved along a direction orthogonal to the direction of a straight line passing through the first axis O1 and a point of contact between the balance wheel 33 and the balance body. spring 102 in the plan view. As a result, the balance adjustment lever 100 rotates the balance wheel 33 by a frictional force. However, the direction of movement of the balance adjustment lever guide pin 104 may not be completely parallel to the direction of movement of the balance adjustment lever operating pin 97.
The spring body 102du balance adjustment lever 100 can be moved while approaching the rim 33a of the balance wheel 33 during a parallel movement of the balance adjustment lever 100 described above. In this case, the spring body 102 may be in contact with the balance wheel 33 for the first time during the parallel movement of the balance adjustment lever 100.
Then, as shown in Figure 10, when the winding stem 51 reaches the position with two offset steps, the adjustment wheel rocker 90finishes to pivot in the third direction of pivot M3. In addition, the balance adjustment lever 100 reaches the adjustment position. When the balance adjustment lever 100 reaches the adjustment position, the spring body 102 of the balance adjustment lever 100 comes into contact with the balance wheel 33 of the sprung balance 32 to stop the operation of the balance spring 32. Therefore, the torque transmission of the seconds mobile 24 to the exhaust regulating device 13 via the intermediate escape wheel 25 is controlled and the rotation of the seconds hand 7 attached to the seconds mobile 24 is stopped.
The balance adjustment lever guide pin 104 is located at the end, in the third direction of pivoting M3, of the adjustment lever guide window 11b of the plate 11, in a state where the control rod winder 51 is in the two-step offset position. When the winding rod 51est pushed from the two-step offset position to the one-step offset position, the adjustment wheel rocker 90est pivoted in the fourth direction of pivoting M4. When the adjusting wheel rocker 90 is rotated in the fourth direction of pivoting M4, a force acts in the fourth direction of pivoting M4, on the balance adjusting lever 100, via the operating pin of the balance adjusting lever 97 As a result, the balance adjustment lever 100 begins to move from the adjustment position to the withdrawn position. The balance adjustment lever guide pin 104 is guided by the adjustment lever guide window 11b of the plate 11 so as to be moved in the fourth direction of pivoting M4, that is to say the direction of movement of balance adjustment lever guide pin 97, and is then moved to approximate fourth axis 04.
When moved in the fourth direction of pivot M4, the balance adjustment lever guide pin 104 is moved parallel to the balance adjustment lever actuating pin 97. At this time, the balance adjustment lever actuator pin 97 is moved. Spring body 102 of the balance adjusting lever 100 is moved in parallel while in contact with the balance wheel 33, and rotates the balance wheel 33 by the frictional force. However, the path of the balance adjustment lever guide pin 104 may not be completely parallel to the path of the balance adjustment lever operating pin 97. As a result, torque is applied to the balance wheel. hairspring 32 at a standstill, and the escapement regulating device 13 is restarted. Then, when the balance adjustment lever guide pin 104 is moved so as to approach the fourth axis 04, the balance adjustment lever 100 is moved while the spring body 102 is rotated in the direction of approaching the fourth axis. axis 04. Then, the spring body 102 of the balance adjusting lever 100 is separated from the balance wheel 33 of the sprung balance 32 while terminating the bending deformation, and the restart of the escapement regulator 13 is completed.
The instant at which the spring body 102du balance adjustment lever 100 comes into contact with or separates from the balance wheel 33 is preferably an instant before the winding stem 51 exits the position at one offset step and reaches the position at two offset steps, and more preferably coincides with the time at which the adjustment lever pin 66 contacts a vertex of the second engaging peak 85b of the third arm 82C of the lever holder 80 As a result, it is possible to prevent the balance adjusting lever 100 from touching the balance wheel 33 and further stopping the operation of the sprung balance 32 even if the winding stem 51 goes beyond the one-shift position when The user moves the winding stem 51 from the position with no offset to the position with one offset. Further, it is also possible to prevent the balance adjusting lever 100 from being separated from the balance wheel 33 and further restarting the operation of the sprung balance 32 even if the winding stem 51 is accidentally pushed to the one-step position. offset when the user rotates the winding stem 51 in the two-step offset position.
As described above, the balance adjustment mechanism 19 according to the present embodiment comprises the balance adjustment lever 100 provided to be engaged with the adjustment wheel rocker 90 and to be movable, with a pivoting of the adjustment wheel rocker 90, between the adjustment position, in which the balance adjustment lever 100 comes into contact with the sprung balance 32, and the withdrawn position, in which the balance adjustment lever 100 is away from the balance. hairspring 32. According to this constitution, the balance adjustment lever 100 in contact with the sprung balance 32 is provided as a separate element from the adjustment wheel rocker 90. Therefore, the balance adjustment lever 100 can come into contact with and be separated from the sprung balance 32 with a different movement from that of the adjusting wheel rocker 90. Thus, it becomes easy to move the balance adjusting lever 100 so as to apply r a movement of the sprung balance 32 when the adjustment of the sprung balance 32 is finished. As a result, it is possible to smoothly restart the operation of the sprung balance 32.
When the balance adjustment lever 100 is moved from the adjustment position to the withdrawn position while in contact with the sprung balance 32, the balance adjustment lever guide pin 104 is guided by the guide window adjustment lever 11b of the plate 11, and is moved along the direction of movement of the balance adjustment lever operating pin 97 serving as an engaging portion between the balance adjustment lever 100 and the rocker arm. adjustment wheel 90. As a result, it is possible to move the balance adjustment lever 100 substantially parallel in a state where the balance adjustment lever 100 is in contact with the sprung balance 32. In a constitution in which the balance adjustment lever is provided in the adjustment wheel rocker, the balance adjustment lever is actuated only by rocking about a predetermined axis. Therefore, it is difficult to move the balance adjusting lever in a direction in which rotation of the balance is applied in a state where the balance adjusting lever is sufficiently pressed against the spring balance to maintain a frictional force. . According to the present embodiment, when the balance adjustment lever 100 is moved from the adjustment position to the withdrawn position, the sprung balance 32 is pivotally driven so as to follow the movement of the balance adjustment lever 100, so that the movement can be applied to the sprung balance 32. As a result, it is possible to restart the operation of the sprung balance 32 in a smooth manner.
The balance adjustment lever 100 is located at the plate 11, on the same side as the sprung balance 32 depending on the direction of the thickness of the plate 11. The main rocker body 92 of the adjustment wheel rocker 90 is located to plate 11, on the side opposite to the balance adjustment lever 100 according to the direction of the thickness of the plate 11. When the entire adjustment wheel rocker is at the plate, on the same side as the balance adjustment lever depending on the direction of thickness, the arrangement of the finishing gear train which transmits power to the sprung balance is limited by the adjusting wheel rocker. According to the present embodiment, since the adjusting wheel rocker 90 is located at the plate 11 on the side opposite to the finishing gear 12, it is possible to avoid a decrease in the basic performance of the movement 10 due to a decrease in the speed. degree of freedom in the arrangement of the finishing gear 12 (eg, decrease in running time and deterioration in accuracy).
In a state where the winding rod 51 is positioned at the one-step offset position and the balance adjustment lever 100 is positioned in the adjustment position, the adjustment wheel rocker actuator pin 67 of the adjustment lever. adjustment 60 is at one end, in the first direction of pivot M1, of the third segment 96c of the adjustment lever engagement window 96 of the adjustment wheel rocker 90. Since the third segment 96c of the adjustment window adjusting lever socket 96 extends in the second pivot direction M2, from its end in the first pivot direction M1, the adjusting wheel rocker actuating pin 67 is not in engagement with the setting window adjusting lever engagement 96 in an initial state when the winding stem 51 is moved from the two-step offset position to the one-step offset position. Therefore, even when the winding stem 51 in the two-step offset position is moved slightly to the one-step offset position, the adjusting wheel rocker 90 and the balance adjusting lever 100 engages this rocker lever. adjusting wheel 90 are not moved. Therefore, even when the winding stem 51 is moved due to erroneous operation or the like in a state where the spring balance 32 is set, it is possible to prevent an unwanted restart of the operation of the spring balance 32.
Since the movement 10 and the timepiece 1 according to the present embodiment include the balance adjustment mechanism 19, the operation of the sprung balance 32 can be restarted smoothly.
Second embodiment
Figure 11 is a plan view of a balance adjustment mechanism according to a second embodiment as seen from the front side.
In the first embodiment, the spring body 102du balance adjustment lever 100 comes to touch the rim 33a of the balance wheel 33du sprung balance 32, radially from the outside. On the other hand, the second embodiment is different from the first embodiment in that the spring body 102A of the balance adjustment lever 100A touches the rim 33a of the balance wheel 33 of the sprung balance 32 in one direction. axial balance-spring 32. The structures other than that described below are the same as those of the first embodiment.
As shown in Figure 11, the balance adjustment lever 100A comprises the spring body 102A instead of the spring body 102 of the first embodiment. The spring body 102A is in the form of a thin plate and is connected to the lever base 101 (see Figure 5). In the present embodiment, the spring body 102A is integral with the lever base 101. The spring body 102A extends linearly from a connecting portion with the lever base 101 as a everything in a plan view. The spring body 102A is disposed between the sprung balance 32 and the fourth axis 04 in the plan view.
Figure 12 is a view showing a portion of a cross section along the line XII-XII in Figure 11.
As shown in Figure 12, the spring body 102A comprises a proximal end portion 105connected to the lever base 101 and extending along a surface direction of the plate 11, a riser 106s' extending from one end of the proximal end portion 105 to a side remote from the plate (front side) in the direction of the thickness of the plate 11, and a balance adjusting portion 107 extending along a surface direction of the plate 11, from one end of the riser 106. The spring body 102A is positioned closer to the plate 11 than the rim 33a of the balance wheel 33 of the sprung balance 32 when looking from the direction of the spring. plate surface 11.
The plate 11 is formed with a sliding contact surface 11c with which the proximal end portion 105 of the spring body 102A of the balance adjustment lever 100A comes into sliding contact, as well as a riser 11d in front of the riser 106 of the spring body 102A of the balance adjustment lever 100A. The sliding contact surface 11c extends along the surface direction of the plate 11. The riser 11d extends from the sliding contact surface 11c and is inclined towards the front side and is opposite an inclined direction. with respect to the direction of the thickness of the plate 11. In the present embodiment, the riser 11d faces the direction of the thickness of the plate 11 and the front side. The riser 11d is formed with an angle of inclination which, with respect to the surface direction of the plate 11, is smaller than that of the riser 106 of the spring body 102A. The riser 11d is arranged to pass behind the adjusting portion 107 of the spring body 102A in the plan view (see Figure 11). The height of the riser 11d is smaller than the height of the riser 106 of the spring body 102A.
Now, an operation of the balance adjustment lever 100A according to the present embodiment will be described with reference to FIGS. 13 to 15. The operation of the adjustment lever 60, of the lever 70 and of the adjustment wheel rocker 90 is the same as in the first embodiment. The operation of the lever base 101 of the balance adjustment lever 100A is the same as in the first embodiment.
[0100] Figures 13 to 15 are explanatory views of the balance adjustment mechanism according to the second embodiment.
[0101] As shown in Figure 13, in a state where the winding stem 51 is positioned at the one-step offset position, the balance adjustment lever 100A is positioned in a withdrawn position. In particular, the spring body 102A is located between the sprung balance 32 and the fourth axis 04, in the plan view.
[0102] As shown in Figures 11 and 14, when the winding stem 51 is pulled out from the one-step offset position to the two-step offset position, the balance adjustment lever 100A is rotated by so that the spring body 102 is moved away from the fourth axis 04. At this time, the riser 106 of the spring body 102A maintains a state of being away from the riser 11d of the plate 11, and the proximal end portion 105 of the spring body 102A slides on the sliding surface 11c of the plate 11. Then, the balance adjusting portion 107 of the spring body 102A is moved to a position where the balance adjusting portion 107 passes in front of the rim 33a of the balance wheel 33 in plan view.
[0103] Then, as shown in FIGS. 11 and 15, when the balance adjustment lever 100A is moved in a parallel manner along the third direction of pivoting M3, a lower end of the riser 106 of the spring body 102A comes into sliding contact. with and mounts on the riser 11d of the plate 11. As a result, the spring body 102A is guided towards the front side, by the riser 11d, that the balance adjustment portion 107 is moved to the front side at the same time as 'bending the proximal end portion 105, and the balance adjustment portion 107 is brought into contact with the rim 33a of the balance wheel 33. At this time, the balance adjustment portion 107 rotates the balance wheel. pendulum 33 by a frictional force. When the winding stem 51 reaches the two-step offset position and the balance adjustment lever 100A is stopped, the spring body 102A contacts the balance wheel 33 to stop the operation of the sprung balance 32.
[0104] When the winding stem 51est pushed from the two-step offset position to the one-step offset position, the spring body 102A of the balance adjustment lever 100A is moved in parallel while being in contact. with the balance wheel 33, and the balance wheel 33 is rotated by the frictional force. As a result, a torque is applied to the sprung balance 32 at a standstill and the escapement regulating device 13 is restarted. Then, when the balance adjustment lever 100A is moved to the withdrawn position, the spring body 102A is separated from the balance wheel 33 while canceling the bending of the proximal end portion 105, and restarting the adjusting device. exhaust 13 is finished.
As described above, the balance adjustment mechanism 19 according to the present embodiment has the following advantageous effects in addition to the same effects as the first embodiment.
[0106] In the process of being moved from the withdrawn position to a contact position, the balance adjustment lever 100A comes into sliding contact with the step of the plate 11 so as to be guided to the front side, and comes into contact with the step. contact with the sprung balance 32from the rear side. According to this arrangement, since the path during the actuation of the balance adjustment lever 100A passes in front of the sprung balance 32 when looking in the direction of the thickness of the plate 11, the degree of freedom concerning the arrangement of the constituents around the 100A balance adjustment lever can be improved. Further, since the balance adjustment lever 100A is guided to the front side by the step of the stage 11, it is possible to obtain a structure in which the balance adjustment lever 100A can be moved in the direction of the movement. thickness of the plate 11 without providing a new separate component.
[0107] In the present embodiment, the lower end of the riser 106 of the spring body 102A is brought into sliding contact with the riser 11d of the plate 11 in order to guide the spring body 102A in the direction of the thickness of the plate 11. However, the arrangement for guiding the spring body in the direction of the thickness of the plate is not limited to this. For example, the riser of the plate may be formed with an angle of inclination which, with respect to the surface direction of the plate, is greater than that of the riser 106 of the spring body 102A, and a lower surface of the plate. riser 106of the spring body 102A comes in sliding contact with an upper end of the riser of the plate. Alternatively, one end at one end of the spring body may be brought into sliding contact with the riser of the plate so as to guide the end at the end of the spring body in the direction of the thickness of the plate.
[0108] The invention is not limited to the embodiments described with reference to the drawings, and various modifications can be considered within the technical scope of the invention.
[0109] For example, the adjusting wheel rocker 90 carries the adjusting wheel 45 in the above embodiments, but the adjusting wheel can be directly carried by a support shaft projecting from the plate. In other words, the setting wheel rocker may be a rocker which carries at least a portion of the time setting gear.
[0110] Further, the balance adjustment lever guide pin 104 of the balance adjustment lever 100 is guided in the adjustment lever guide window 11b of the stage in the previous embodiments, but a pin may be provided. on the stage and a guide window (corresponding to what is called "guided part" in the appended claims) in which this stage pin is inserted can be provided in the balance adjustment lever.
[0111] In addition, it is possible to suitably replace components present in the embodiments described above with known components without departing from the spirit of the present invention, and the embodiments mentioned above can be appropriately combined.

权利要求:
Claims (6)
[1]
1. Balance wheel adjustment mechanism, comprising:a winding stem (51) carried by a plate (11);an adjustment lever (60) arranged to pivot relative to the plate for a displacement of the winding stem in an axial direction (L);an adjustment wheel rocker (90) arranged to engage with the adjustment lever and to pivot for pivoting of that adjustment lever;a transmission wheel (45, 46, 47) carried by the adjusting wheel rocker and arranged to transmit rotation of the winding stem to an indicating member when the adjusting wheel rocker is placed in a predetermined position; anda cog adjusting lever (100; 100A) arranged to be in engagement with the adjusting wheel rocker and adapted to be movable, for pivoting of the adjusting wheel rocker, between an adjusting position, in which the lever cog adjustment lever comes into contact with a balance with balance spring (32), and a withdrawn position, in which the cog adjusting lever is away from the balance with balance spring.
[2]
2. A balance adjustment mechanism according to claim 1, whereinthe gear adjustment lever comprises a guided portion (104) guided by the plate, and is intended to be pivotable relative to the adjustment wheel rocker at an engaging portion (94) with this rocker of adjusting wheel, andwhen the cog adjustment lever is moved from the adjustment position, to the withdrawn position, while being in contact with the balance wheel with balance spring, the guided part is guided by the plate and moved along a trajectory of the engagement portion between the cog adjusting lever and the adjusting wheel rocker.
[3]
3. A balance adjustment mechanism according to claim 1 or 2, whereinthe gear adjustment lever is located on the plate, on one side of this plate, namely on the same side as the balance with balance spring according to the direction of the plate thickness, andat least part of the adjustment wheel rocker is located at the plate, on one side of this plate, namely on the side opposite to the gear wheel adjustment lever in the direction of the thickness.
[4]
4. A balance adjustment mechanism according to one of claims 1 to 3, whereinin a process of being moved from the withdrawn position to the adjustment position, the gear adjustment lever comes into sliding contact with a step of the stage to be guided in the direction of the thickness of the stage, and comes in contact with the balance with balance spring from the thickness direction.
[5]
5. Timepiece movement, comprising:a balance adjustment mechanism (19) according to one of claims 1 to 4;platinum; anda balance with a balance spring (32) pivotally carried by the plate.
[6]
6. Timepiece, comprising:a timepiece movement according to claim 5.

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同族专利:

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公开号 | 公开日

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JP2021139636A|2021-09-16|

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JP6751215B1|2020-09-02|

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CN113341675A|2021-09-03|

引用文献:

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JP6954747B2|2016-03-07|2021-10-27|セイコーインスツル株式会社|Train wheel regulation mechanism, movement and mechanical watches|

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DE202018101566U1|2018-03-21|2018-04-23|Grossmann Uhren Gmbh|clockwork|

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法律状态:

优先权:

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申请号 | 申请日 | 专利标题

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JP2020034873A|JP6751215B1|2020-03-02|2020-03-02|Balance wheel setting mechanism, clock movement and clock|

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