瑞士专利CH703483B1 Winding gear with torque limitation, movement and timepiece equipped with such a gear.

专利PDF首页>>瑞士专利

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 winding train of a cylinder of a timepiece with torque limitation. The gear train (1) is equipped with a plurality of gear wheels transmitting the rotation of a winding stem to a ratchet wheel, two wheels (60 and 70) formed coaxially connected to each other to through a torque limiting mechanism (5). The torque limiting mechanism includes an engagement arm (82) having a proximal end portion attached to the first wheel (70) and extending peripherally from the proximal end portion to a distal end portion equipped with one engagement portion (83), and one engaged portion (66) formed on the other wheel (60) and with which the engagement portion is resiliently engaged by pressure, the engaging portion (83) being detached from the engaged portion (66) to allow relative rotation of the two wheels (60 and 70) when a torque exceeding a threshold value is exerted.
公开号:CH703483B1
申请号:CH01254/11
申请日:2011-07-27
公开日:2017-05-15
发明作者:Mori Yulchi；Fujieda Hisashi
申请人:Seiko Instr Inc；
IPC主号:

专利说明:

Description
BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a winding train, a timepiece movement equipped with the gear train, and a timepiece equipped with the movement. 2. Description of the Prior Art [0002] With regard to mechanical timepieces, in a timepiece for winding up, when the mainspring is fully armed, the winding torque increases abruptly, and feeling of tightness is felt. However, if a stronger force (a couple) of winding is still exerted, there is a danger for the related elements to break, which makes reassembly, etc., impossible. That is, in a timepiece of winding, the torque limiting function is not normally provided to determine an upper limit of the maximum winding torque, and therefore there is no effect safety or function to prevent damage.
However, in an automatic timepiece, typically, the barrel drum is equipped with a sliding fastener, and the automatic winding of the mainspring is performed until the winding torque reaches a maximum of predetermined level due to fixation; on the other hand, when the winding torque exceeds a fixed level determined by a fixed level determined by the fixing, the sliding fastener slides in the barrel drum and the end portion of the outer peripheral side of the mainspring is prevented from over-winding in the barrel drum (see, for example, JP-A-2002-71,836 (patent document 1)).
Here, the sliding attachment inevitably occupies a certain degree of volume in the barrel drum; when the thickness of the sliding attachment is reduced in order to reduce the area of occupancy, the torque mentioned above decreases and the level on which the mainspring is raised is lowered. On the other hand, if the winding torque is increased, it is necessary to increase the thickness of the sliding fastener, with a result that the volume occupied by the mainspring in the barrel drum (the effective volume of the drum of barrel) is reduced, resulting in a reduction in the degree of arming or the life (power reserve) of the mainspring. In addition, in this case, the feeling of tightening is given by fluctuations in the torque due to the sliding of the motor-spring body along the inner wall of the barrel drum, which is pressed against this inner wall by the fixing by slip, so that the user feels a feeling of drag and heaviness to use.
Also in connection with an automatic timepiece, it has been proposed to grant a torque limiting function to the mechanical part of a one-way clutch of the automatic gear instead of providing a mechanism for limiting the speed of rotation. torque in the barrel drum (see JP-A-51-90859 (Patent Document 2)).
In the proposed automatic gear, are provided a C-shaped spring mounted to a gear on the input side extending the automatic winding weight, a star whose rotation shaft is rotatably supported by both ends a shape spring C which can be moved radially along an elongated hole in the radial direction of the entry-side gear and a ratchet wheel engageable with the star; in a state in which the winding of a motor-spring body (power-motor spring) has not yet been completed and in which the winding torque is small, the rotation in one direction of the rotations in both directions the input side sprocket is transmitted to the ratchet wheel through star engagement and the ratchet wheel to remount the mainspring; when the winding of the barrel drum motor spring body has been completed and the tightening torque increases abruptly, even when rotating in the direction mentioned above, the star rotation shaft radially escapes outwardly, at the same time, elastically deforming the spring shape C, with the result that the transmission of the rotation of the star to the impeller stops.
In the torque limitation mechanism incorporated in the automatic work of the patent document 2, not only are a complicated structure and a precise configuration necessary to materialize a one-way rotation clutch mechanism and a limitation function of the invention. torque by a combination of a ratchet wheel and a star, but are required an even more complicated structure and precise configuration to guide the star shaft through the elongated hole so that, from the pair of arm parts "C", the portion of the arm extending in a direction opposite to the direction of relative rotation may effect an appropriate elastic deformation. In addition, there is a danger that unnatural stress is applied to one arm arm portion C in the direction from the distal end portion to the proximal end portion of the arm portion.
However, it has also been proposed to provide the crown with a torque limiting mechanism or with a function causing the input side to be inactive with respect to the output side in the case where a torque exceeding a fixed value is applied (JP-A-2009-115 800 (Patent Document 3)).
However, in the method proposed in patent document 3, the upper limit of the torque is not intrinsically determined by the movement of a timepiece itself, but its function can only be exerted in a complete assembly state where the crown has been mounted, which means that a desired test or the like is quite difficult to implement. In addition, the structure of the crown is inevitably rather complicated, with the size of the crown increased to an unnatural level. In addition, in the case of mass production of such a ring, it is not easy to properly maintain a predetermined slip torque (i.e. threshold torque causing slip). SUMMARY OF THE INVENTION [0010] An object of the present invention is to provide a winding train capable of reliably not to put the winding torque to a higher level than to a desired level by the movement itself. , a timepiece movement equipped with said gear and a timepiece equipped with said movement.
To achieve the above purpose, it is provided, according to the present invention, a winding gear which is equipped with a plurality of gear wheels meshing with each other to transmit the rotation of a rod of winder with a ratchet wheel and wherein two of the plurality of coaxially formed gears are connected to each other through a torque limiting mechanism, wherein the torque limiting mechanism includes an engagement arm (a grip arm portion) having a proximal end portion attached to one of the two wheels and extending peripherally from the proximal end portion to a distal end portion provided with an engagement portion, and a engaged part (one engaging part) which is formed on the other of the two wheels and with which the engaging part is elastically engaged by the pressure, the engaging part being detachable the portion engaged to allow relative rotation of the two wheels when a torque exceeding a threshold value (threshold level) is exerted; and when a manual winding torque is applied to the torque limiting mechanism, a force directed from the proximal end portion to the distal end portion of the arm is applied to the engagement arm engagement portion. engagement and adapted to separate the engagement portion from the engaged portion.
In the winding train of the present invention, in the winding train itself which is equipped with a plurality of gear wheels engaged with each other to transmit the rotation of a winding stem to the two of the plurality of coaxially formed gears are connected to each other through a torque limiting mechanism, so that the winding torque of the mainspring can not exceed one level. threshold without the need for a sliding attachment in the barrel drum to avoid damaging the mainspring and other elements of the timepiece, etc .; in addition, it is possible to allocate the inner volume of the barrel drum to the mainspring in a maximum manner in order to increase the length of the mainspring maximally so that it is possible to maximize the level of the mainspring. power reserve and to improve the torque of the mainspring, thereby improving the running accuracy of the timepiece. In addition, in the winding train of the present invention, the winding train itself is provided with a torque limiting function, so that it is not necessary to provide the outer elements, such as the crown, d a torque limiting function, and it is possible to avoid an unnatural increase in the size of the crown, etc., thus preserving the external appearance, etc., of the outer elements as appropriately as possible.
In addition, in the winding train of the present application, are provided "a part of the engagement arm having a proximal end portion attached to one of the two wheels and extending peripherally of the end portion proximal to a distal end portion provided with an engagement portion, and an engaged portion formed on the other of the two wheels and with which the engagement portion is resiliently engaged, the engaging portion being detached the engaged part to allow a relative rotation of the two wheels when a torque exceeding a threshold value is exerted; when a manual winding torque is applied to the torque limiting mechanism, a force directed from the proximal end portion to the distal end portion of the pressure arm is applied to the engagement arm engagement portion. engagement and adapted to separate the engagement portion from the engaged portion, such that the force applied to the engagement arm to separate the engagement portion at the distal end of the arm portion of the portion engaged to a member directed from the proximal end portion to the distal end portion of the engagement arm, which means that there is no fear that such unnatural compression stress will cause the part of the engagement arm for deforming such as buckling (a force directed from the distal end portion to the proximal end portion of the engagement arm); therefore, engagement and release between the engagement portion and the engaged portion can be performed in a reliable and stable manner for a long period of time. Here, the torque exceeding the threshold value is the torque needed to release the engagement between the engagement portion and the engaged portion; In what follows, it will also be called the commitment release threshold couple. That is, when the winding torque is not higher than a predetermined threshold level (engagement release threshold torque), the winding torque applied to the input side wheel two wheels constituting the winding train is transmitted as such to the wheel on the output side of the two wheels via the engagement between the engagement portion and the engaged portion of the torque limiting mechanism, and the winding of the mainspring is performed according to this couple. On the other hand, when the winding of the mainspring has been practically finished, the load torque related to the additional compression of the mainspring increases abruptly, and exceeds the level of engagement threshold necessary to release the engagement between the part of the mainspring. engagement and the engaged part, in this way the winding torque exceeds the engagement release threshold level, and the engagement between the engagement portion and the engaged portion of the torque limiting mechanism is released by the couple. winding applied to the wheel on the input side of the two wheels constituting the winding train; therefore, the winding torque is not transmitted to the wheel on the output side of these two wheels but is released, thus completing the winding of the mainspring. Here, of course, the threshold level related to the release of the commitment (the commitment release threshold level or engagement release threshold torque) is higher than the minimum threshold reassembly torque required to terminate. the winding (tread) of the mainspring, and is lower than the threshold level required to prevent damage to the motor-spring body, etc.
Here, one of the engagement portion and the engaged portion includes a projection or a convex portion, and the other of the engagement portion and the engaged portion includes a recess or concave portion with or wherein the protrusion (convex part) is comfortably engaged or housed. This recess (concave portion) may include a small protrusion (convex portion) on both or only one of its sides. In the above construction, the height of the projection (convex portion), the angle of inclination of a lateral surface defining the convex portion, the depth of the recess (concave portion) and the angle of inclination of a lateral surface defining the recess (concave portion) are defined as desired, the threshold level of the torque that can be transmitted between the input-side wheel and the output-side wheel (the release threshold level). commitment or engagement release threshold torque) that can be defined as being equal to a desired intensity. When the engagement portion and the engaged portion are in a mutually engaged state, it is typically desirable to allow the engaged state to be maintained also with respect to the reverse rotation so that the engaged state can be maintained also when the crown is rotated alternately in the winding direction and in the reverse direction at the time of the winding of the mainspring.
In the above construction, the engagement portion and the engaged portion are mutually engaged with each other, and one is designated as the engaging portion and the other is designated as the committed part corresponding to the commitment part; however, it is also possible for these two elements to be designated as the commitment parts or for these two elements to be designated as the engaged parts.
Typically, the wheels on the input and output side acting as the two wheels constituting the winding train consist respectively of a crown wheel on the lower side meshing with a winding pinion and a crown wheel on the upper side engaged with an intermediate crown wheel. In this case, the space having attraction to the relative positional relationship between the crown wheel and the winding pinion, and the relative positional relationship between the crown wheel and the crown intermediate wheel can be effectively used for the incorporation of a part of engagement by friction. In this text, the "upper" side refers to the back side of the watch case, and the "lower" side refers to the side of the dial. However, depending on the configuration of the winding stem, this can also be the opposite.
However, the two wheels mentioned above constituting the winding train can be part of the intermediate ring wheels instead of the crown wheels.
Typically, in the winding train of the present application, of the two wheels, the input side wheel has a small diameter portion equipped with the part engaged in its outer periphery, and, among the two wheels, the exit-side wheel has the engagement arm whose distal end portion is provided with the engaging portion so that it can oppose the engaged portion of the small-diameter portion for mutual engagement radially. .
In this case, an arcuately curved arm portion is used as the engagement arm, and engagement by the engagement portion may be released by applying a directed force to eliminate the curvature. of the bow, so that commitment and release from engagement can be done in a stable manner; even in a case where the engagement is carried out radially between the engaging portion and the engaged portion or wherein the release of the engagement is effected radially, the output-side wheel may be provided with a small diameter portion at the place of the input side wheel to be equipped with a small diameter part. In addition, as described below, instead of the engagement portion and the engaged portion of these two wheels which are radially opposite each other, it is also possible that they are opposite each other. other in the axial direction (that is, a direction parallel to the direction in which the centers of rotation of these two wheels extend).
Typically, in the winding train of the present application, the output side wheel has a plurality of engagement arm portions as mentioned above at peripheral intervals.
In this case, typically, the engagement zones between the engagement portion and the engaged portion may be disposed at equal peripheral intervals, so that engagement and release can be stably performed. . However, if desired, it is also possible to provide only one engagement arm.
In the winding train according to the present invention, the proximal end portion of each engagement arm, for example, is attached to the output side wheel.
In this case, the support of the engagement arm can be achieved easily.
In the winding train according to the present invention, each engagement arm is equipped with a portion of auxiliary pressure arm by elastic deformation extending peripherally from the proximal end portion in a reverse direction of that of the distal end portion, with an extension end portion of the auxiliary pressurizing arm portion by resilient deformation of each engagement arm radially exerting pressure on the engagement portion of a another engagement arm adjacent peripherally thereto toward the engaged portion.
In this case, the auxiliary arm portion holds the distal end portion of the engagement arm, so that the engagement arm is reliably pressurizable. In this case, the elastic force with which the distal end portion is pressurized may be provided not by the arm portion with the distal end portion but by the auxiliary pressurizing arm portion by elastic deformation. In addition, it is only necessary to balance by the engagement arm and the auxiliary pressurizing arm portion by elastic deformation extending in reverse directions on both sides of the proximal end portion, so that not only is the support of the proximal end side of the engagement arm carried out in a stable manner, but the engagement release threshold torque can be easily increased if it is relatively small. In accordance with the present invention, the engagement arm may be provided with a center-supporting auxiliary arm portion extending peripherally in a direction opposite to that of the proximal end portion from the distal end portion, with another engagement arm and another center support arm portion configured similarly to the engagement arm and the center support arm portion is integrally formed to form a continuous elastic ring as a whole.
In this case, the engagement portion is supported in the center, so that a relatively large pressure force can be easily applied at the same time, reliably avoiding the application of a deformation stress of type buckling.
In this case, typically, of the elastic ring, a connecting portion between the proximal end portion of the engagement arm and the proximal end portion of the center support arm portion is freely adjusted. to the output side wheel to allow radial movement.
In this case, the support of the ring (the regulation of rotation) and the elastic deformation permit causing the displacement of the engagement portion can be performed simultaneously. Here, in order to facilitate production, etc., a radially elongate hole is typically formed in the ring, with a pin for free insertion into the elongate hole being implanted on the side of the main wheel body. However, in some cases this may be the opposite.
In the winding train according to the present invention, the engagement portion and the engaged portion may be opposed axially to each other instead of being radially opposed to each other; in this case, typically, of the two wheels, the input-side wheel has an annular portion having the portion engaged on an axial end surface thereof, and of these two wheels, the output-side wheel has the arm engagement member provided with the engagement portion at its distal end portion to be able to be axially opposed to the engaged portion of the annular portion to engage therewith.
In this case also, typically, the output side wheel has a plurality of engagement arm portions as mentioned above at peripheral intervals; in addition, typically, the proximal end portion of each engagement arm is attached to the exit-side wheel.
To achieve the above purpose, a watch movement according to the present invention is equipped with a winding train as described above.
In addition, to achieve the above purpose, a timepiece according to the present invention is equipped with such a timepiece movement.
Brief description of the drawings [0033]
Fig. 1 shows an explanatory transverse view illustrating a part of a mechanical timepiece according to a preferred embodiment of the present invention having a timepiece movement according to a preferred embodiment of the present invention equipped with a cog winding according to a preferred embodiment of the present invention;
Fig. 2 shows an explanatory plan view of a part including the winding train of the movement of the timepiece of the timepiece of FIG. 1;
Figs. 3A and 3B show diagrams illustrating a wheel of the winding train of the movement of the timepiece of the timepiece of FIGS. 1 and 2 including a stored torque limiting mechanism, of which FIG. 3A is a detailed plan view, and FIG. 3B is an explanatory transverse view taken along the line INB-INB of FIG. 3A;
Figs. 4A and 4B show diagrams to further illustrate the wheel including the torque limiter shown in FIG. 3, of which FIG. 4A is an explanatory transverse view taken along the line IVA-IVA of FIG. 3B, and FIG. 4B is a graph schematically illustrating the relationship between the torque setting and the rotation angle of the input side wheel in the torque limiting mechanism;
Figs. 5A and 5B show diagrams illustrating a modified example (another preferred embodiment) of the wheel including the torque limiting mechanism shown in FIG. 3, of which fig. 5A is an explanatory transverse view similar to FIG. 4A (but seen towards the side of the dial), and FIG. 5B is a graph schematically illustrating, as FIG. 4B, the relationship between the torque setting and the rotation angle of the input side wheel in the torque limiting mechanism;
Figs. 6A and 6B show diagrams illustrating another modified example (yet another preferred embodiment) of the wheel including the torque limiting mechanism shown in FIG. 3, of which fig. 6A is an explanatory plan view similar to FIG. 3A, and FIG. 6B is a cross sectional view of FIG. 6A;
Fig. 7 shows an explanatory transverse view, similar to FIG. 4A, illustrating yet another modified example (yet another preferred embodiment) of the wheel including the torque limiter shown in FIG. 3; and
Fig. 8 shows an explanatory transverse view, similar to FIG. 1, illustrating part of a modification of the winding train of FIG. 1.
DESCRIPTION OF THE PREFERRED EMBODIMENTS [0034] Some preferred embodiments for practicing the present invention will be described with reference to some preferred embodiments illustrated in the accompanying drawings.
[Embodiments] [0035] A winding timepiece 3 according to a preferred embodiment of the present invention has a movement 2 according to a preferred embodiment of the present invention equipped with a winding gear according to a preferred embodiment of the invention. preferred embodiment of the present invention as shown in the explanatory transverse view of FIG. 1 and in the explanatory plan view of FIG. 2.
As can be seen from the transverse view of FIG. 1, the movement 2 of the timepiece 3 is equipped with a main plate 11 in the central portion in the direction of thickness D, and the winding stem 20 is supported on the main plate 11 to project out of the middle and retract in the directions A1 and A2, and to be rotatable about a central axis B in the directions B1 and B2.
The winding stem 20 is equipped with a large-diameter columnar portion 22, a small-diameter portion 23, a neck-like portion 24, a medium-diameter columnar portion 25, a prism portion 26, and the like. A sliding pinion 15 is fixed with the prism portion 26 to be able to effect a relative movement in the directions A1 and A2, and a winding pinion 18 is attached to the middle diameter part 25 to be able to perform. a relative rotation in the directions B1 and B2. Reference 16 indicates a control lever, and reference 17 indicates a toggle.
On the rear side 7 of the box (in the direction D1 as seen in Fig. 1) of the main plate 11, a bridge 12 of the third wheel is provided and a barrel bridge 13. Between the plate 11 and the third wheel bridge 12 located on the rear side 7 of the deck 11 box, and on the side of the dial 19 of the deck 11 (in the direction D2 as seen in Fig. 1), a finishing gear 6 generating a step-by-step needle movement is provided (Fig. 2), related to the ticking and timekeeping of the timepiece 3. The finishing gear train 6 includes a wheel exhaust & pinion 6a (Fig. 2).
Between the plate 11 and the barrel bridge 13, is disposed a movement cylinder 30. The movement barrel 30 is equipped with a body 32 of the motor spring inside a main body 31 of drum barrel, and the spring body 32 as a spiral spring is locked to an inner peripheral surface 31a of the main barrel body 31 at the outer peripheral end 32a, with the peripheral end inside the barrel. this one, mounted on a barrel shaft 33 (Fig. 2). A gear portion 31b of the main barrel movement body 31 is engaged with the gear wheel of the work train 6. The barrel shaft 33 is rotatably supported by the platen 11 and the barrel bridge 13 through a bearing portion, with a ratchet wheel 35 mounted at a projecting barrel shaft end portion 33.
The winding train 1 includes a crown gear structure 8 engaged with the winding pinion 18, a mechanism 9 of the crown intermediate wheel connected to the crown wheel structure 8, and the wheel gear 35 connected. to the mechanism 9 of intermediate wheel crown.
In this example, the mechanism 9 of the intermediate wheel crown is composed of a first wheel 41 intermediate crown and a second wheel 42 intermediate crown rotatably supported by the barrel bridge 13 and the bridge 12 third wheel. The first intermediate crown wheel 41 includes a shaft 41a, a first intermediate crown toothed wheel 41b integral with the shaft 41a, and a first intermediate crown gear 41c integral with the shaft 41a and of smaller diameter than the first wheel. 41b intermediate crown gear; the first intermediate crown gear wheel 41b is engaged with the gear wheel on the output side of the crown wheel structure 8, and the first intermediate crown gear 41c is engaged with the second intermediate crown wheel 42. The second intermediate crown wheel 42 is engaged with the ratchet wheel 35.
In this example, the crown wheel structure 8, which constitutes the winding gear 1 with the mechanism 9 of intermediate wheel crown and the wheel ratchet 35, is mounted to the bridge 12 of the third wheel.
Specifically, the crown wheel structure 8 has a support shaft structure 50 including a crown wheel guide pin 51 installed at the third wheel deck 12, a lower side crown wheel 60, and a crown wheel 70 on the upper side. Between the lower side crown wheel 60 and the upper side crown wheel 70, there is a torque limiting mechanism 5 linking the lower and upper side wheel 60 and 70. Here, the torque limiting mechanism 5 consists of a lower side torque limiting mechanism portion 5a and a top side torque limiting mechanism portion 5b constituting a portion of the lower side crown wheel 60. As shown in FIG.
The crown wheel guiding pin 51 of the support shaft structure 50 is equipped with a large diameter collar portion 51a at the proximal end, a shaft adjustment portion 51b of small diameter at the distal end, and a plurality of shaft portions 51 d of average diameter and small shaft portions 51e in the center.
As can be seen in Figs. 3A and 3B, and FIG. 4A in addition to figs. 1 and 2, the lower side crown wheel 60 has a ring-type lower side ring crown gear body 61, and a lock pinion 64 as a cylindrical pin wheel inserted in the main body 61 crown gear on the lower side. As will be described later, the cylindrical pinch wheel 64 is a ratchet wheel equipped in the outer perimeter of an engaged part giving a ratchet feeling in cooperation with a click spring, and consists of a gear type of smaller diameter than the main gear body 61; therefore, in this text, it will be referred to as the "ratchet gear" in the sense of being the smallest of the ratchet gears (ratchet wheel).
The main body 61 of the lower side crown gear is provided with a gear portion 61a in the outer perimeter and a hole 61b in the center. In addition, the lower side crown gear body 61 is provided with a recess 62 in the center of the dial-side surface, and receives the large-diameter collar portion 51a of the wheel guide pin 51. crown at the bottom surface 62a of the recess 62 (Fig. 1).
The latching pinion 64 is provided with small diameter portions 64a and 64b on the dial side and the rear side of the box, and the small diameter portion 64a on the dial side is inserted into the central hole 61b of the body 61. Crown gear wheel on the lower side. In addition, the click gear 64 is provided with engaging portions 66 at equal circumferential intervals in the outer perimeter of the cylindrical portion 65 at the center (the engaged portions are mutually engaged with engaging portions 83 described below; instead of being designated as engaged parts, they may be designated as engaging parts). The engaged portions 66 are of the same configuration, and each consists of a recess 67 and projections 68 and 69 on both sides of the recess 67. The protrusions 68 and 69 may, for example, be designated as protrusions or parts convex or chevron shaped parts. The recess 67 is defined by sidewalls 67a and 67b joined by a bottom portion 67c. The projection 68 is defined by an inner and outer side wall 68a and 68b, and the projection 69 is also defined by an inner and outer sidewall 69a and 69b. Here, the side wall 67a of the recess 67 is continuously and harmonically connected with the inner side wall 68b of the projections 68, and the side wall 67b of the recess 67 is continuously and harmonically connected with the inner side wall. 69b of the projection 69. On the other hand, the outer side wall 68a of the projection 68 and the outer side wall 69a of the projection 69 are harmoniously bonded with the cylindrical peripheral wall portion 65a of the cylindrical portion 65.
Here, the configurations of the protrusion 67 and projections 68 and 69 (the depth or the height and the inclination stiffness, that is to say, the depth or the height and the degree of the inclination , the manner in which the sidewalls are inclined, etc.) are defined as desired, by determining the threshold torque of the torque limiting mechanism 5, i.e., the engagement release threshold torque T max (Fig. 4B) and the maximum engagement release torque Tu (Fig. 4B).
The crown wheel 70 of the upper side is composed of a main crown gear body 71 of the upper side of the annular plate type, and two latching springs 80A and 80B (indicated by the reference 80 when they are designated collectively or when they are not distinct from each other) rotatably secured to the upper crown crown gear body 71.
More specifically, the crown wheel 70 of the upper side has a guide pin 75A supporting the locking spring 80A to allow rotation in the directions E1A and E2A around a central axis EA and a guide pin 75B supporting the snap-in spring 80B to allow rotation in the directions E1B and E2B about a central axis EB, and has an annular support plate portion or a space-determining seat 76 (see Fig. 1, etc.) supporting the latching springs 80A and 80B. As described later, the springs 80A and 80B consist of springs providing a "snap" snap-in sense in cooperation with a ratchet gear 64, so that in this text they are referred to as "springs". The guide pins 75A and 75B are of the same configuration and are designated 75 when referred collectively or when they are not distinct from each other. Specifically, the guiding pegs 75A and 75B have upper end small diameter portions 75aA and 75aB, lower end small diameter portions 75bA and 75bB, and central columnar portions 75cA and 75cB. The top end small diameter portions 75aA and 75aB of the guide pins 75A and 75B are inserted into the holes 71aA and 71aB opposite to each other in the diametric direction of the main body 51 of the crown gear wheel. upper side (located so as to be peripherally deflected from each other 180 degrees), and the lower end small diameter portions 75bA and 75bB are inserted or secured with hole portions 76aA and 76aB of the portion 76 of annular support plate.
The latching spring portion 80A has a central bulge 81A which is fixedly secured in rotation with the central columnar portion 75cA of the guide pin 75A, and has an engagement arm 82A extending from the central bulge 81A in a substantial direction J1 along the circumferential direction of the lower side crown wheel 60 and equipped with an engagement projection 83A as an engagement portion at the distal end thereof, and a an elastic arm portion 85A extending from the central inflated portion 81A in an opposite direction J2 substantially along the circumferential direction of the lower side crown wheel 60 and provided with a pressure applying portion 86A at the end distal to that one. Like the snap-in spring 80A, the snap-in spring 80B has a central bulge 81B which is rotatably attached to a central columnar portion 75cB of the guide pin 75B, and has an engagement arm 82B. extending from the central bulge 81B in the direction J1 substantially along the circumferential direction of the lower side crown wheel 60 and which is provided with an engagement projection 83B as an engagement portion at its distal end, and a an elastic arm portion 85B extending from the central bulge 81B in the opposite direction J2 substantially along the peripheral direction of the lower side crown wheel 60 and which is provided with a pressure applying portion 86B at its distal end.
The engagement portions 83A and 83B of the engagement arms 82A and 82B of the latching springs 80A and 80B can be engaged with the recesses 67, 67 of the engaged parts 66, 66 of the ratchet gear 64 on the sides. diametrically opposed to each other, and can be released or releasable (engagement release) from the recesses 67, 67. The pressure application portions 86A and 86B of the elastic arm portions 85A and 85B snap-in springs 80A and 80B urge the distal end engaging portions 83B and 83A of the resilient engagement arms 82A and 82B against the ratchet gear 64 through the portions 84B and 84A behind the end portions. distal from the engagement arm 82A and 82B of the latching springs 80B and 80A located so as to be diametrically opposed to each other.
That is, in the case where the distal end engaging portions 83B and 83A of the engagement arms 82A and 82B are engaged in the recesses 67, 67 of the engaged portions 66, 66 of the pinion 64, the distal end engaging portions 83B and 83A of the engagement arms 82B and 82A are elastically compressed in the directions E1B and E1A against the recesses 67, 67 of the engaged parts 66, 66 of the pinion gear. Thus, the state in which the load torque is relatively small, when a rotational force in the direction J1 is applied to the crown wheel 60 of the lower side, the crown wheel 70 of the upper side, which is resiliently engaged in the recesses 67, 67 of the engaged parts 66, 66 of the detent pinion 64 via the distal end portions 83B and 83A of the engagement arms 82B and 82A, is also rotated inthe direction J1 when the crown wheel 60 of the lower side rotates in the direction J1. On the other hand, in the case where the rotational load in the J1 direction of the upper side crown wheel 70 is greater than the engagement release threshold level Tmax, even when a rotational force in the J1 direction is applied. at the crown wheel 60 of the lower side, and the recesses 67, 67 of the engaged portions 66, 66 of the click gear 64 of the lower side crown wheel 60 are rotated in the direction J1, the parts 85A and 85B of resilient arms of the latching springs 80A and 80B rise along the inclined side surfaces 67b, 67b of the recesses 67 of the latch gear 64, and the engagement projections 83A and 83B extend from the recesses 67, 67 of the engaged parts 66, 66 That is, the engagement arms 82B and 82A of the latching springs 80A and 80B escape through the rotation in the directions E2A and E2B to allow the ratchet gear 64 to rotate in the direction of rotation. J1, so that the crown wheel 60 of the lower side does not rotate in the direction J1 relative to the crown wheel 70 of the upper side. That is, a torque that exceeds the engagement release threshold level is applied to the crown wheel 70 from the upper side downstream in the torque limiting mechanism 5 between the crown wheel 60 on the opposite side. lower and upper side crown wheel 70, that is, at the upper side (downstream side) torque limiting mechanism portion 5b relative to the downstream upper side crown wheel 70, and the transmission of the Rotation of the crown wheel 60 from the lower side to the upper side crown wheel 70 is released, with the result that the lower side crown wheel 60 does not rotate relative to the upper side crown wheel 70.
In the above construction, portion 5a of the lower side torque limiting mechanism is that the ratchet gear 64, and the upper side torque limiting mechanism portion 5b consists of pins. guide 75A and 75B and click springs 80A and 80B.
In the timepiece 3 having the winding gear 1 equipped with the crown wheel structure 8 provided with the torque limiting mechanism 5 constructed as described above, the state in which the winding stem 20 was pushed by pushing in a direction in the direction A2 to the position O of the winding stem, when the ring (not shown) is rotated in the direction B1 to rotate the stem winding 20 in the direction B1, the winding pinion 18 in engagement with the sliding pinion 15 is also rotated in the direction B1, and, as the winding pinion 18 rotates in the direction B1, the crown wheel 60 on the side lower part whose toothed portion 61a is in engagement with the toothed portion 18a of the winding pinion 18, is also rotated in the direction J1 around the central axis J.
In the state in which the tightening of the turns of the motor spring 32 of the movement barrel 30 has not been completed, the torque load is smaller than the engagement release threshold level, so that that rotation in the J1 direction of the lower side crown wheel 60 is transmitted to the upper side crown wheel 70 through the torque limiting mechanism 5. That is to say, when the tightening of the turns of the motor spring 32 of the movement barrel 30 has not yet been completed, the torque load is smaller than the winding threshold torque Te, and is, therefore, smaller than the engagement release threshold torque Tmax (> Te), so that under the effect of the resilient arm portions 80A and 85B of the latching springs 80A and 80B, the springs of 80B and 80A of the torque limiting mechanism 5 are held in the engaged state with respect to the engagement recesses 67, 67 of the engaged parts 66, 66 which the detent spring 64 opposes due to the engagement protrusions 83B and 83A, so that rotation in the J1 direction of the lower side crown wheel 60 is transmitted to the upper side crown wheel 70 through the torque limiting mechanism 5, and the crown wheel 70 the upper side is also driven rotating in direction J1. Rotation in the J1 direction of the upper side crown wheel 70 is transmitted to the ratchet wheel 35 through the crown intermediate wheel mechanism 9 engaged with the upper side crown wheel 70, and the ratchet wheel. 35 is rotated in the direction C1 around the central axis C, with the result that the winding or tightening of the turns of the motor spring 32 progresses.
On the other hand, when the winding of the turns of the motor spring 32 is more or less complete and the winding torque or the torque load increases, the portion 85 of the elastic arm of the detent spring 80 is deflected so as to that the engagement projection 83 of the click spring 80 rises along the projection 69 near the engagement recess 67 of the engaged portion 66 that the ratchet gear 64 opposes; when the tightening of the turns of the motor spring 32 of the movement barrel 30 has been substantially completed, the torque load increases abruptly to exceed the engagement release threshold torque T max, so that the engagement projection 83 of the snap-in spring 80 completely overcomes the summit portion of the projection 69 in the vicinity of the engagement recess 67 of the engaged portion 66 the opposed snap gear 64, and engagement between the engagement projection 83 acting as engagement part, and the engaged part 66 is released, so that the torque that the user has applied through the ring gear is released without being transmitted to the motor-spring body 32. By therefore, the engagement projection 83 of the snap-in spring 80 descends completely from the projection 69 towards the cylindrical portion 65. Normally, the torque in the direction B1 applied by the end of the The user's eye through the crown can not be changed instantly, so that a state is maintained in which the user applied winding torque T is higher than the engagement release threshold torque. Tmax; therefore, during this time, the engagement projection 83 of the snap-in spring 80 moves along the cylindrical peripheral wall portion 65a before one by one the protrusion 68 consecutive to the peripheral wall portion 65a is overcome. cylindrical, the projection 69 consecutive to the recess 67 located after that, etc., with the result that the user can feel a feeling of click cracking as a fluctuation in the torque load (in some cases accompanied by a sound corresponding), which means that it can, reliably, feel the reassembly (feeling of tightening during Γ arming).
In this case too, when, to wind the winding stem 20 using the crown, the user repeatedly rotates the crown in the direction B1 held between the thumb and the index finger to rotate it along the inch before reversing it in the direction B2, the projection 68 near the recess 67 reliably prevents the relative rotation of the ratchet pinion 64 and the ratchet spring 80 in this manner preventing positional deflection (Reverse rotation in the direction B2 of the winding stem 20 is permitted due to the one-way clutch connection portion between the sliding pinion 15 and the winding pinion 18).
On the other hand, when the tightening of the turns of the motor spring 32 of the movement barrel 30 has been practically finished, the torque load is abruptly increased, and the engagement release threshold torque T max is exceeded. so that even if the lower side crown wheel 60 rotates in the J1 direction, the torque limiting mechanism 5 can not transmit the rotation; therefore, the crown wheel 70 on the upper side does not rotate, and no further rotation of the ratchet wheel 35 and the movement cylinder 30 is effected, and the winding of the motor spring body 32 is stopped, ending thus the winding or arming. That is, when the winding of the motor spring body 32 and the motion barrel 30 has been substantially completed, the torque load exceeds the engagement release threshold torque Tmax, so that the engagement arm 82B and 82A of the latch springs 80B and 80A of the torque limiting mechanism 5 are turned against the compressive force of the resilient arm portions 80A and 85B of the latching springs 80A and 80B, and the engagement between the engagement projections 83B and 83A and the engagement recesses 67, 67 of the non-engaged portions 66, 66 that the opposed click spring 64 is released. Therefore, the transmission of the rotation of the crown wheel 60 from the lower side is interrupted at the torque limiting mechanism 5, and the rotation of the upper side crown wheel 70, the crown intermediate wheel mechanism 9 and the ratchet wheel 35 stops being driven; no further winding or winding of the turns of the motor spring 32 is performed, thereby completing the winding or winding of the turns of the motor spring 32. In this case, as the ratchet gear 64 rotates in the direction J1, the engaging portions 83A and 83B of the latching springs 80A and 80B successively overlap the projections 68 and 69, and at this point the user turning the winding stem 20 using the crown can feel a click feeling "snap crunches".
In the movement 2 equipped with the winding gear 1 as described above, the torque limiter 5 is incorporated in the winding gear 1 itself of the movement 2, so that, unlike the case of an automatic gear, it is not necessary to arrange a sliding attachment in the chamber of the movement cylinder 30; therefore, the motor spring body 32 can occupy a space corresponding to the volume occupied by such a sliding attachment, so that the length of the motor spring body 32 is increased, and it is possible to provide an output stable torque for a long period, and to improve the torque level to thereby improve the operational accuracy of the timepiece 3. In addition, in the movement 2 equipped with the winding gear 1, the limiting mechanism 5 torque is incorporated in the winding train 1 itself of the movement 2, so that it is not necessary to provide the crown and other external elements with a torque limiting mechanism, and it is possible to avoid an unnatural increase in the size of the crown and other external elements.
Specifically, suppose that a very large torque load is applied to the crown wheel 70 of the upper side, and the crown wheel 70 of the upper side is substantially fixed in one position; the change in the torque (the torque applied to the ratchet gear 64) T with respect to the rotation angle q of the ratchet gear 64 is as shown in FIG. 4B. In the following, the state, in which the engagement projections 83 of the engagement arm 82 of the click spring 80 have been inserted into the recesses 67 of the click pinion 64, will be designated as the initial state SO (where 0k = 0r = 0 degrees, with the torque load T being 0). Here, the symbol qr indicates the angle of rotation of the crown or winding stem 20, and the symbol 0k indicates the angle of rotation of the pinion 64.
When the engagement projection 83 of the engaging arm portion 80 of the snap-in spring 80 rises along the side surface 67b (the inner side surface 69b of the projection 69) of the recess 67 of the pinion 64, with its lateral surface 83a thereof in contact with the lateral surface 67b, the torque load T as indicated by segments K1 and K2 in FIG. 4B is applied to the ratchet gear 64. When the distal end portion of the engaging projection 83 of the engagement arm 82 overcomes the root portion of the projection 69 in the J2 direction of the recess 67 along the lateral surface 67b of the recess 67, this load torque T is reduced to 0 after a state S1 in which the maximum value Tmax is reached (the state S2 in which the distal end portion of the engagement projection 83 has just reached the summit of projection 69).
When the engagement projection 83 of the engagement arm 82 of the click spring 80 passes below the top portion of the projection 69 of the detent pinion 64, the engagement projection 83 of the engagement arm 80 of the snap-in spring 80 moves and thereby exerts a compressive force towards the lateral surface 69a in the direction J1, its top part or its lateral surface 83b being in contact with the lateral surface 69a of the projection 69 of the pinion. 64. That is to say that even if no rotational force is applied in the direction J1 to the ratchet pinion 64 of the winding stem 20, the ratchet pinion 64 is rotated in the J1 direction by the elastic force of the elastic shaft portion 85 of the snap-in spring 80 until the state S3 is reached in which the engagement portion 83 of the snap-in spring 80 is lowered along the lateral surface 69a of the sailli e 69 of the ratchet gear 64 (thus forming a one-way clutch in which, even if the articulation or engagement between the sliding pinion 15 and the winding pinion 18 transmits the rotation in the direction B1 of the sliding pinion 15 towards the winding pinion 18, the rotation in the direction B2 of the sliding pinion 15 is not transmitted to the winding pinion 18). The fluctuation of the torque during this period of time is, for example, as indicated by the segments K3a, K3b, and K4 in FIG. 4B.
After that, when the engagement projection 83 of the engagement arm 82 of the snap-in spring 80 moves along the cylindrical peripheral surface 65a of the ratchet gear 64, no torque T is substantially applied. (With the exception of the small torque corresponding to frictional resistance) (i.e., T is approximately equal to 0), and a change occurs along segment K5.
Then, after the state S4 has been reached, in which the engagement portion 83 of the engagement arm 82 of the snap-in spring 80 comes into abutment against the end of the outer lateral surface 68a of the protrusion 68 of the ratchet gear 64, also when the engagement projection 83 of the engagement arm 82 of the ratchet spring 80 rises along the lateral surface 68a of the projection 68 of the ratchet gear 64 to pass through above the top part of the projection 68, the load torque T as indicated by the segments K6 and K7 is applied to the snap-in spring 64 as in the case where the apex of the projection 69 is franked. When the distal end portion of the engagement projection 83 of the engagement arm 82 rises to the top of the projection 68, the load torque T is reduced to 0 via the state S5 in which the maximum value Tu is reached (the state S6 in which the distal end portion of the engagement projection 83 has just reached the top of the projection 68).
Substantially as in the case in which the top of the projection 69 is crossed, in the case where the engagement projection 83 of the engagement arm 82 of the snap-in spring 80 passes the summit portion of the projection 68 of the pinion 64, the engagement projection 83 of the engagement arm 82 of the snap-in spring 80 moves at the same time as pushing the lateral surface 66a in the direction J1, with its top or side surface 83b being in contact with the lateral surface 68b or the top of the projection 68 of the ratchet pinion 64, until the initial state SO is restored where the engagement portion 83 of the ratchet spring 80 descends. along the lateral surface 68b of the protrusion 68 of the ratchet gear 64 to be fully inserted into the recess 67, the ratchet gear 64 is rotated in the J1 direction by the elastic force of the arm portion 85 devel The fluctuation of the torque T during this period of time is as indicated, for example, by segments K8 and K9 in FIG. 4B.
In the above construction, under the action of the elastic force of the elastic arm portion 85, the projection 83 of the snap spring 80 passes the projections 69 and 68, so that the spring snap 80 operates as a jumper (a jump control element) to perform a jump control operation or jump operation. That is, during the transition from the segment K2 to the segment K5, the protrusion 83 of the snap-on spring 80 barely passes the top of the projection 69 between the side surfaces 69b and 69a of the projection 69 under the action of the elastic force of the resilient arm portion 85, and immediately thereafter, the resilient members 85A and 85B of the latching springs 80A and 80B push the elements 84B and 84A behind the engagement arms 82B and 82A. other latching springs 80B and 80A, and the engagement portions 83B and 83A of the engagement arms 82B and 82A push the outer lateral surfaces 69a, 69a of the projections 69, 69 of the recesses 67, 67 located in front of the pinion. latching 64 to rotate the ratchet gear 64.
For example, the winding threshold pair Te, which is the minimum torque required to complete the winding (winding) of the spring-motor body, is slightly smaller than the maximum engagement release torque Tu when the engagement projection 83 passes the projection 68 on the cylindrical portion side 65a as indicated by the symbol Tel in FIG. 4B. However, as indicated by the phantom line Tc2 in FIG. 4B, the winding threshold torque Te may be higher than the maximum engagement release torque Tu as long as it is sufficiently smaller than the engagement release threshold torque Tmax when the engagement projection 83 passes the projection 69 of the engaged portion 66 of the recess side 67.
In the above example, the cylindrical peripheral wall portion 65a is between the recesses 67 of the engaging portions 66, and the gap between the recesses 67, 67 is wide, and the recesses 67 are held between the independent projections 68 and 69, so that the gap between the recesses 67, 67 is even wider; however, by changing the peripheral length of the cylindrical peripheral wall portion 65a, it is possible to change the snap-on feeling at the time of setting. It is also possible to remove the cylindrical peripheral wall portion 65a, and to share the projections 68 and 69 on both sides of the recess 67 by the peripherally adjacent recess 67 (as in the example of Fig. 5A described below).
Even if in the example described above the crown wheel 60 of the lower side is connected to the input side (that is, with the winding stem 20 through the winding pinion 18) and the upper side crown wheel 70 is connected to the output side (i.e., with the ratchet wheel 35 through the intermediate crown gear mechanism 9), it is also possible for the crown wheel 70 on the side upper to be connected to the input side and for the crown wheel 60 of the lower side to be connected to the output side. In this case, however, the ratchet pinion 64, for example, is connected to the crown wheel 70 on the upper side and the ratchet spring 80 is connected to the lower side crown wheel 60; or the snap-in spring 80 is arranged in an inverted state so that the engagement portion 83 of the snap-in spring 80 can receive a peripheral torque remote from the central bulge, which is the proximal end portion, of the engagement portion 66 of the ratchet gear 64.
In addition, even if in the example described above the snap spring is rotatably mounted relative to the main body 71 of the crown wheel 70 of the upper side and the snap spring is elastically compressed. by another similar snap-in spring, it is also possible, as shown in FIG. 5A, for the latching springs 80D to be secured to each other at the main body 71D of the crown wheel 70D of the upper side.
In the torque limiting mechanism 5D shown in FIGS. 5A and 5B, the elements which are substantially the same as those of the torque limiting mechanism shown in FIGS. 1 to 4A or FIG. 4B are indicated by the same references, and are similar to the elements of the torque limiting mechanism; however, the elements which are somehow different from the elements of the torque limiter 5 are indicated by the same references with the suffix D added.
The torque limiter 5D is equipped with a ratchet pinion 64D inserted into a main crown wheel body 61D on the lower side of a crown wheel 60D on the lower side. The ratchet gear 64D has, instead of the ratchet gear 64 (provided with the recess 67 and the engaging portion consisting of projections 68 and 69 on both sides of the latter arranged at an interval determined by the wide cylindrical portion 65a), a star-shaped structure in which the projections 68D and 69D on both sides consist of projections 68D of the same configuration, with the recesses 67D and the projections 68D being arranged alternately in the peripheral direction . Consequently, the side wall 67aD of the recess 67D corresponds to the side wall 68bD of the projection 68D, and the side wall 67bD of the recess 67D corresponds to the side wall 68aD of the protrusion 68.
The crown wheel 70D of the upper side has two latching springs 80AD and 80BD (indicated by the reference 80D when designated collectively or when they are not distinguished from each other) arranged at an interval of 180 degrees in the peripheral direction.
The proximal end portion 81D of the snap-in spring 80D is put in place and secured to the main crown wheel body 71D of the upper side by guide pins 77 and 78, and the engagement projection 83D is disposed at the distal end portion of an arm portion 89. Here, the arm portion 89 is similar to the engaging arm 82 in that it is provided with the engaging projection 83D at its distal end, and is similar to the elastic arm portion 85 in that the arm portion itself is provided with deflection elasticity or spring property.
As described above, the snap-in spring 80D consists of two click springs 80AD and 80BD separated from each other. In contrast to the latching springs 80A and 80B, the respective proximal end portions 81 AD and 81 BD of the latch springs 80AD and 80BD are attached to the upper side crown wheel body 71D, and unlike the main springs 80A and 80B latch, they operate independently of one another.
The operation of the torque limiting mechanism 5D, constructed as described above, is essentially the same as the operation of the torque limiting mechanism 5 shown, for example, in FIG. 5B except that the snap spring still functions as a jumper. More precisely, between the initial state SOD in which, as shown in FIG. 5A, the engagement projection 83D is inserted and engaged in the recess 67D of the ratchet gear 64D (qk = qr = 0, with T being 0) and the S2D state in which the top of the projection of engagement 83D reaches the top of projection 68D, and when, near state S2D, there is assumed a state S1D in which the torque is the maximum Tmax; then, until the SO condition is restored, where the engaging projection 83D is inserted into the recess 67D of the ratchet gear 64D, the projection 68D of the ratchet gear 64D is urged in the direction J1 by the engagement projection 83D.
In this case, the latching springs 80AD and 80BD are mounted to the main crown wheel body 71D of the upper side separately from each other, so that the structure is simpler; however, high accuracy is required in that it is necessary for the engagement arm portions themselves to have latching springs 80AD and 80BD with deflection elasticity, and their portions 81 AD and 81 BD The respective proximal endpieces shall be attached to the main crown wheel body 71D of the upper side.
Instead of having projections 68D on both sides of each recess 67D of the latching pinion 64D identical to each other, they may consist of different projections 68 and 69 as in the case of the mechanism 5 of FIG. torque limitation.
In the example described above, the lower side torque limiting mechanism portion and the upper side torque limiting portion constituting the torque limiting mechanism are radially opposite one another. and radially engaged with each other; however, instead of the lower and upper side torque limiting mechanism parts being radially opposite to each other and radially engaged with each other, it is also possible for them to being opposed to each other in the directions D1 and D2 in which the axis J of the center of rotation extends and to be engaged with each other in the directions D1 and D2 in which the axis J extends as in the case of the torque limiting mechanism 5E shown in FIGS. 6A and 6B.
In the torque limiting mechanism 5E of FIGS. 6A and 6B, the elements which are substantially the same as those of the torque limiting mechanism shown in FIGS. 1 to 4A and 4B are indicated by the same references, and the elements which are similar to those of the torque limiter 5 but different from them in one way or another are indicated by the same references with the suffix E added. In the case where the elements correspond essentially to those of the torque limiter 5D of FIG. 5, they are indicated by the same references with the suffix E added (with the suffix D removed in the case where the elements are indicated by references with the suffix D, and by the same references in the case where the elements are indicated by references without the suffix D).
In FIGS. 6A and 6B, the crown wheel structure 8E has a support shaft structure 50E, a lower side crown wheel 60E, an upper side crown wheel 70E, and a ratchet spring 80E.
The lower side crown wheel 60E has a lower side crown wheel body 61E and a ratchet gear 64E, and the ratchet wheel 64E consists of a large diameter annular surface 61c, in one 61E main crown wheel body of the lower side, opposite the crown wheel 70E of the upper side, and an annular body 64d integrally arranged 61c annular surface of large diameter. On the side facing the crown wheel 70E of the upper side in the direction D1 in which the axis J extends, the ratchet gear 64E is provided with recesses 67E arranged at equal peripheral intervals. Each recess 67E corresponds to a sidewall portion 67aE inclined on one side (downstream see the corresponding walls inclined to the left in FIG 6B) of the recess 67E relative to the peripheral direction, and corresponds to a portion 67bE vertical side wall 67bE on the other side of the recess 67E with respect to the peripheral direction. Around the central hole 61bE, the lower side crown wheel main body 61E is provided with a recess 61d formed in the large diameter annular surface 61c.
The crown wheel 70E of the upper side has a main crown crown body 71E of the upper side and the cylindrical spacing portion 73. The cylindrical spacer portion 73 is arranged between the main wheel body 71E. the crown of the upper side of the crown wheel 70E of the upper side and the main body 61E of the crown wheel of the lower side; in this example, it is inserted in the recess 61 d of the crown wheel 61E of the lower side. Even though the cylindrical spacer part 73 is typically attached to the upper crown crown body 71E, it is also possible that it is not secured in this way as long as it remains held in a position. predetermined.
The snap-in spring 80E has an annular plate-shaped main body portion 81E, and a plurality of (four, in this example) resilient engagement arms 89E disposed at peripheral intervals and extending from the part 81E of main body. Each elastic 89E engaging arm has a proximal end arm portion 89aE extending radially from the main body portion 81E, and a distally extending end arm portion 89bE extending peripherally in the J1 direction and in the direction axial D2 from an extension end of the proximal end arm portion 89aE, with the distal end portion 89bE of the distal end arm portion constituting an engaging end portion 83E. Typically, the proximal end arm portion 89aE is attached to the annular plate main body portion 81E; instead, however, it can be shaped like a spring.
As shown in FIG. 6B, in the initial state, the distal end engagement portion 83E of each resilient engagement arm 89E of the snap-in spring 80E assumes a position in which it is properly inserted into the sprocket recess 67E. 64E, and the distal end engagement portion 83E of each elastic engaging arm portion 89E of the snap-in spring 80E is resiliently urged against the inclined lateral surface 67aE of the recess 64E of the pinion gear 64E.
Therefore, in the range of values in which the torque T exerted on the click pinion 64E in the direction J1 is smaller than the maximum frictional engagement torque or the engagement release threshold torque (the torque threshold level) Tmax attributable to the frictional engagement force between the distal end engagement portion 83E of each resilient engagement arm 89E of the snap spring 80E and the recessed lateral surface 67aE of the recess 67E of the ratchet gear 64E, when the ratchet gear 64E is rotated in the J1 direction, the main body 81E of the ratchet spring 80E engaged with the recess 67E of the ratchet gear 64E to the portion 83E The distal end engagement of each resilient engagement arm 89E is also rotated in the direction J1 integrally with the click gear 64E. In other words, in the case where the torque exerted between the torque limiting mechanism portion 5aE of the crown wheel 60E on the lower side and the torque limiting mechanism portion 5bE of the crown wheel 70E on the other side. upper is smaller than the engagement release threshold torque Tmax, depending on the torque received in the J1 direction by the lower-side crown wheel 60E, the torque is transmitted integrally to the upper-side crown wheel 70E. through the torque limiting mechanism 5E and is transmitted to the downstream side part of the winding gear 1E. Here, the engagement release threshold torque T max is naturally greater than the winding threshold pair Te, which is the minimum torque required to complete the winding (winding) of the spring-motor windings, and is sufficiently smaller the level of torque that could damage the elements connected to the winding train.
On the other hand, when the torque T acting on the ratchet gear 64E in the direction J1 exceeds the engagement release threshold torque Tmax determined by the distal end engagement portion 83E of each arm of FIG. 89E resilient engagement of the snap-in spring 80E and the inclined lateral surface 67aE of the recess 67E of the ratchet gear 64E, in the case where the lower-side rudder wheel 60E is rotated in the J1 direction; 83E of distal end engagement of each resilient engagement arm portion 89E of the snap-in spring 80E rises along the inclined lateral surface 67aE of the recess 67E of the ratchet gear 64E in the J2 direction, and the torque ceases to be transmitted from the ratchet gear 64E to the ratchet spring 80E, resulting in the generation of a slip in the winding gear 1E to complete the reassembly of the motor spring body.
Although in the example described above the engagement arm extends in a peripheral direction from the proximal end portion to the distal end portion where the engagement portion is located, and the part of engagement is arranged cantilevered on the engagement arm relative to the proximal portion, instead of the engagement portion being supported in such a manner, it is also possible for the part of commitment to be supported centrally as shown, for example, in fig. 7.
In the torque limiting mechanism 5F of FIG. 7, the elements which are substantially the same as those of the torque limiting mechanism 5 shown in FIGS. 1 to 4A and 4B are indicated by the same references, and elements which are similar to those of the torque limiter but different from them, in one way or another are indicated by the same references with the suffix F added. In the case where the elements substantially correspond to those of the torque limiter 5D of FIG. 5, they are indicated by the same references with the suffix F added (with the suffix D deleted in the case where the elements are indicated by references with the suffix D at the end of the references indicating the element, and by the same references in the case where the elements are indicated by references without suffix D at the end of the references indicating the element).
In the structure 8F of the crown wheel of FIG. 7, the lower side crown wheel 60F has a lower side crown wheel body 61F and a ratchet pin mechanism 64F. The ratchet pin mechanism 64F consists of three ratchet pins 67pF, 67qF, and 67rF (indicated by reference 67F when referred to collectively as designated or when they are not distinct from one another). protruding in the main body 61F axle body direction D1 from the lower side. The three click pins 67pF, 67qF, and 67rF are arranged around the central axis J at equal peripheral intervals along a ghost circle M.
The crown wheel 70F of the upper side has a main crown wheel body 71F of the upper side, 75fF and 75gF guide pins (indicated by reference 75F when referred collectively or when are not distinct from each other), and a ring-shaped snap-spring structure 80F. The guide pins 75fF and 75gF protrude in the direction D2 towards the main crown wheel body 61F from the lower side to the surface of the upper crown crown body body 71F in a position deflected by 180 degrees around the central axis J.
[0094] The snap-spring structure 80F has a ring-shaped or annular main body portion 87, bulges 81F and 81GF (indicated by reference 81F when referred to collectively or when they are not distinct from each other), and two engagement parts 83uF and 83vF (indicated by reference 83F when referred to collectively or when they are not distinct from each other). The bulges 81 fF and 81 gF protrude radially outwardly to provide projections in two diametrical positions of the outer periphery of the main body portion 87 (positions peripherally spaced apart from each other by 180 degrees around the periphery. central axis J); elongated holes 88f and 88g (indicated by reference 83F when referred to collectively or when not distinct from each other), which extend radially and in which the guide pins 75fF and 75gF are freely inserted, formed in the bulge or protrusions 81fF and 81gF. The engagement portions 83uF and 83vF are in the form of recesses 90u and 90v (indicated by reference 90 when referred to collectively or when they are not distinct from each other), with projections 91, 91 formed on both sides of each recess 90.
Here, the torque limiting mechanism portion 5aF of the lower side of the torque limiting mechanism 5F consists of three latching pins 67pF, 67qF, and 67rF. In contrast, the upper torque limiting mechanism portion 5bF of the upper torque limiting mechanism torque limiting portion 5bF of the torque limiting mechanism 5F consists of a snap spring structure 80F and the 75fF guiding pins. and 75gF.
As shown in FIG. 7, a click pin 67F of three ratchet pins 67pF, 67qF, and 67rF constituting the lower side torque limiting mechanism portion 5aF (for example, the ratchet pin 67pF in the case of FIG. , which is applicable to the following description) is engaged with an engagement portion 83F of the two engagement portions 83uF and 83vF of the ratchet spring structure 80F of the upper-side torque limiting mechanism portion 5bF. (For example, the engagement part 83uF in the case of Fig. 7, which applies to the following description), and the two detent pins 67qF and 67rF which remain of the three detent pins 67pF, 67qF and 67rF are held in contact with the inner peripheral surface 87a of the ring-shaped main body portion 87, with the guide pins 75fF and 75gF located at the radially inner end portions 88fa and 88ga. al 88fa and 88ga elongate holes 88f and 88g; in this case, when a torque in the J1 direction is applied to the lower side crown wheel structure 60F, and the lower side crown wheel structure 60F is rotated in the J1 direction, engagement takes place between the snap pin 67pF and the recess-shaped engagement portion 83uF 90, and the snap-in spring 80F whose inner peripheral surface 87a is supported by the two remaining ratchet pins 67qF and 67rF is also driven. rotating in direction J1 with latching pins 67pF, 67qF, and 67rF; the upper side crown wheel structure 70F is rotated in the direction J1 substantially integrally with the lower side crown wheel 60F, with a torque transmitted to the ratchet wheel 35 through the crown wheel structure 70F of the upper side.
On the other hand, when the torque load increases, and the torque in the direction J1 applied to the crown wheel structure 60F of the lower side increases, the force with which the detent pin 67pF pushes the lateral surface 90a of the recess 90 of the engaging part 83uF of the snap-spring structure 80F increases, and pushes the part 92 of the snap-spring structure 80F in the direction N1, and the part 92 where the part is arranged. engagement 83F is moved radially outward in the direction N2. At this time, the bulges 81 fF and 81 gF deflected approximately 90 degrees from the engagement portion 83uF, receive a force moved radially inwardly, and the guide pins 75f and 75g move relatively radially outwardly along the elongated holes 88f and 88g. The degree of displacement above in the direction N2 increases if the torque load increases; when the displacement reaches the engagement depth of the detent pin 67pF, the detent pin 67pF exits the recess 90u of the engagement portion 83uF, and moves in the direction J1 along the surface 87a arcuate inner peripheral of ring-shaped body portion 80F of ring spring structure 80F, so that torque transmission ceases to be effected.
As can be seen from the description above, in this torque limiter 5F, the engagement portion 83F of the snap-in spring 80F is due to the ring-shaped annular configuration in which the spring 80F is formed, held not only by the elastic arm portion 93 but also by the elastic arm portion 94. That is, the engagement portion 83F is not held cantilevered by the resilient arm portion 93, but is centrally held between the elastic arm portion 93 and the elastic arm. Here, the elastic arm portion 94 may be considered as an auxiliary arm portion. Here, it is possible, for example, to consider the proximal end portion as the bulges 81 fF and 81 qF (i.e., not fixed in one position to the portion

权利要求:
Claims (12)
[1]
A winding gear (1) comprising a plurality of gear wheels (60; 70) engaged with each other for transmitting the rotation of a winding stem (29) to a gear wheel (35) and wherein two of the plurality of coaxially mounted gears (60; 70) are connected to each other through a torque limiting mechanism (5), wherein the torque limiting mechanism (5) includes a torque arm engagement (82) having a proximal end portion attached to one of the two gears (60; 70) and extending peripherally from the proximal end portion to a distal end portion provided with a portion of engagement (83), and an engaged portion (66) which is formed on the other of the two gears (60; 70) and with which the engagement portion (83) is elastically engaged by the pressure, the portion of engagement (83) being capable of disassociating itself from the engaged portion (66) for allowing re a relative rotation of the two wheels when a torque exceeding a predetermined threshold value Tmax is exerted during reassembly; and when a manual winding torque greater than Tmax is applied to the torque limiting mechanism (5), a force directed from the part d is applied to the engagement portion (83) of the engagement arm (82). proximal end toward the distal end portion of the engagement arm (82) and adapted to separate the engagement portion (83) from the engaged portion (66).
[2]
The winding gear (1) according to claim 1, wherein of said two coaxial gear wheels, the input side wheel (60) has a smaller diameter portion (64) than the output side wheel (70). said smaller diameter portion (64) being provided with the engaged portion (66) in its outer periphery; and, the exit-side wheel (70) carries the engagement arm (82) whose distal end portion is provided with the engagement portion (83) so that it can oppose radially to the engaged portion (66) of the small diameter portion (64) for engagement therewith.
[3]
The winding gear (1) according to claim 2, wherein the output-side wheel (70) has a plurality of engagement arms (82A; 82B) at regular peripheral intervals.
[4]
The winding gear (1) according to claim 3, wherein the proximal end portion of each engagement arm (82) is attached to the output side wheel (70).
[5]
5. The winding gear (1) according to claim 3, wherein each engagement arm (82A; 82B) is provided with a portion of auxiliary pressure arm by elastic deformation (85A; 85B) extending peripherally. from its proximal end portion in a direction opposite to that of its distal end portion, with an extension end portion of the auxiliary pressurizing arm portion by elastic deformation (86A; 86B) of each engagement arm (82A; 82B) exerting radial pressure on the engagement portion (83) of another engagement arm (82A; 82B) adjacent peripherally thereto toward the engaged portion (66) .
[6]
The winding gear (1) according to claim 2, wherein the engagement arm (93) is provided with a center support auxiliary arm (94) extending peripherally in a direction opposite to that of the portion proximal end portion from the distal end portion where the engagement portion (83uF) is located, with another engagement arm (93) provided with another engagement portion (83vF) at its distal end and another center support auxiliary arm (94 '), the center support auxiliary arm (94) extending peripherally from the engagement portion (83uF) to the proximal end portion of the other arm 93 ") and the other center support arm (94 ') extending peripherally from the other engagement portion (83vF) to the proximal portion of the engagement arm (93). ), said engagement arm (93) and the center support auxiliary arm (94) ), and the other engagement arm (93 ') and the other center support arm (94') being integrally formed to form a continuous elastic ring as a whole (80F).
[7]
The winding gear (1) according to claim 6, wherein, in the resilient ring (80F), a connecting portion between the proximal end portion of the engagement arm (93) and the end portion. proximal of the center support arm (94) is freely fitted to the output side wheel (70) to allow radial movement.
[8]
The winding gear (1) according to claim 1, wherein the input-side wheel (60) has an annular portion (64d) having the engaged portion disposed on an axial end surface thereof; and the output-side wheel (70) is provided with the engagement arm (89E) provided with the engagement portion (83E) at its distal end portion so that it axially faces the engaged portion of the annular portion (64d) and can be mutually engaged with the latter.
[9]
The winding gear (1) according to claim 8, wherein the output-side wheel (70) has a plurality of engagement arms (89E) at regular peripheral intervals.
[10]
The winding gear (1) according to claim 9, wherein the proximal end portion of each engagement arm (89E) is attached to the output wheel (70).
[11]
11. Movement of a timepiece with a winding gear (1) according to one of claims 1 to 10.
[12]
12. Timepiece with a timepiece movement according to claim 11.

类似技术:

公开号 | 公开日 | 专利标题

EP2392975B1|2019-05-15|Wheel-organwith one-way clutch

EP2214065B1|2017-02-08|Timepiece movement equipped with a vibrating alarm

EP2350745B1|2012-10-31|Driving mechanism for a clock movement

CH703483B1|2017-05-15|Winding gear with torque limitation, movement and timepiece equipped with such a gear.

CH709508B1|2018-07-13|Watch movement with a drive mechanism of an analogue indicator with periodic or intermittent movement.

EP2560054B1|2017-11-15|Winding of a clock mechanism by pressing or pulling

EP2360535A1|2011-08-24|Power reserve indicator built into the oscillating weight of a movement with automatic winding

EP2073076A1|2009-06-24|Alarm clock control mechanism

EP2264551B1|2013-08-07|Differential gear for a timepiece movement

CH704710A2|2012-09-28|Slip structure of vehicle for timepieces comprises bush made from ceramic and gear fitted with respect to the bush in elastic engagement part

EP2919077B1|2019-08-07|Device for driving an analogue indicator, in particular a date ring

EP2226687A1|2010-09-08|Disengaging device for timepiece mechanism, and watch movement comprising this device

EP2957964B1|2017-02-01|Tilting coupling device for timepiece

EP3705949A1|2020-09-09|Torque limiter mechanism for a timepiece

EP3278183B1|2021-09-15|Mechanism for rewinding and/or correcting at least one clock function and device for selecting a clock function

EP3602202B1|2021-05-05|Device for adjusting functions of a timepiece

EP2615505A1|2013-07-17|Mechanism for indicating on request information for a timepiece movement

EP3739393A1|2020-11-18|Self-winding watch movement

WO2012127036A1|2012-09-27|Mechanical watch movement comprising an energy storage element capable of deformation under bending or torsion

CH706701B1|2016-10-31|Automatic winding mechanism.

EP2710433A1|2014-03-26|Actuating mechanism for a timepiece movement and corresponding timepiece movement

EP3686694B1|2021-08-18|Alarm clock mechanism and timepiece comprising such a mechanism

EP2977827A1|2016-01-27|Clock barrel with improved force transmission

CH700035A2|2010-06-15|Clockwork for wristwatch, has clutch-engaging mechanism comprising inertial ratchets integrated to hub of one of mobile engagement mechanisms and engaged with stop integrated to other mobile engagement mechanism

CH715905A2|2020-09-15|Clockwork torque limiter mechanism.

同族专利:

公开号 | 公开日

JP2012032300A|2012-02-16|

CN102346425A|2012-02-08|

JP5411081B2|2014-02-12|

CH703483A2|2012-01-31|

引用文献:

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

US2563112A|1947-09-11|1951-08-07|Hill Charles|Spring winding device|

US2632993A|1948-05-18|1953-03-31|Hill Charles|Spring winding device for watches|

FR1207713A|1957-08-20|1960-02-18|Otero|Automatic winding mechanism, especially for wristwatches|

JP3496544B2|1998-04-17|2004-02-16|セイコーエプソン株式会社|Mainspring device and clock|

EP1586960A1|2004-04-14|2005-10-19|Meco S.A.|Crown for a watch with a disconnecting mechanism|

AT437388T|2007-11-08|2009-08-15|Meco Sa|CLOCK FOR THE WATCH, INCLUDING A MECHANISM WITH TORQUE CLUTCH|

EP2058713B1|2007-11-08|2010-02-03|Meco S.A.|Crown for a timepiece|JP6787098B2|2016-12-13|2020-11-18|セイコーエプソン株式会社|How to disengage watch movements, mechanical watches and claw levers|

JP6951855B2|2017-03-30|2021-10-20|セイコーインスツル株式会社|Torque generation mechanism, constant torque mechanism, watch movement and watch|

CN110083044B|2018-01-26|2021-10-29|精工电子有限公司|Movement and timepiece|

EP3705949A1|2019-03-05|2020-09-09|ETA SA Manufacture Horlogère Suisse|Torque limiter mechanism for a timepiece|

法律状态:

优先权:

申请号 | 申请日 | 专利标题

JP2010172703A|JP5411081B2|2010-07-30|2010-07-30|Hand-wound wheel train, watch movement equipped with the train wheel, and watch equipped with the movement|

[返回顶部]