CH703519A2 - Lift wheel drive for use in clockwork of windup clock, has spur gears meshed with one another, and cup spring for pressing lower annular frictional engagement surface against upper annular frictional engagement surface - Google Patents

Abstract

The drive (1) has spur gears (41, 42) meshed with one another for transferring rotation of a lift shaft on a ratchet wheel (37). A lower side crown wheel and an upper side crown wheel are provided with an upper annular frictional engagement surface (67) and a lower annular frictional engagement surface (72). The frictional engagement surfaces face each other and are provided in frictional engagement with one another. A cup spring (80) presses the lower annular frictional engagement surface against the upper annular frictional engagement surface.

Description

Background of the invention

1. Field of the invention

The present invention relates to an elevator gear train, equipped with the elevator gear train movement and a clock equipped with the clockwork.

2. Description of the Related Art

When in mechanical watches in a wind-up clock, the tension spring is completely wound or mounted, the elevator torque increases abruptly, which leads to a Aufwickel tension feeling is perceived. However, when an even larger lift force (torque) is applied, it is feared that the related components will be broken and it becomes impossible to perform the mounting, etc. Usually, no torque limiting function is provided which sets the upper limit of the lift torque, i. there is no safety effect or damage-limiting function.

On the one hand, in an automatic timepiece, the barrel is equipped with a sliding attachment, and an automatic tension spring winding takes place until the winding torque reaches a predetermined value determined by the attachment; On the other hand, if the lift torque exceeds a specified value determined by the attachment, slipping will slip within the barrel, causing the outer peripheral end portion of the tension spring to rotate within the barrel, thereby preventing over-tightening (see, eg, JP-A-2002- 71836 (Patent Document 1)).

Slip attachment here inevitably occupies a certain volume within the barrel, and when the thickness of the slip is reduced in view of minimizing the occupied volume, the above-mentioned torque is reduced, resulting in a lowering of Zugfeder-Aufziehgrades. On the other hand, if one tries to increase the lift torque, it becomes necessary to increase the thickness of the slip fitting, which causes the volume (the effective volume of the barrel) occupied by the tension spring within the barrel to decrease, resulting in a reduction the number of reels or time duration (amount of power reserve) of the tension spring leads.

It has also been proposed to provide the crown with a torque limiting mechanism or a torque limiting function in which the input side idles with respect to the output side (when idling) when a torque is applied, which is a set value exceeds (JP-A-2009-115 800 (Patent Document 2)).

However, in this method proposed in Patent Document 2, the upper limit of the torque is not specifically determined within the range of the movement, but its function can be performed only in the crown-attached complete state, so that it is quite difficult to perform a desired test or the like perform. Also, the structure of the crown is complicated, so that it is difficult to avoid an awkward enlargement of the crown. Moreover, if this crown is to be mass produced, it is not easy to maintain a precise slip torque (the slip torque causing slip). In addition, it is practically impossible to change the torque according to the desire of a person (user).

Summary of the invention

It is an object of the present invention to provide an elevator gear train in which the elevator torque can be adjusted to a value not higher than a desired value by means of the movement itself, as well as equipped with the gear train To provide clockwork and a clock equipped with the clockwork.

To achieve this object, an elevator-train is provided, which is equipped with a plurality of intermeshing held gears to transmit the rotation of an elevator shaft to a lock-wheel, and which comprises: an input-side member with an input side frictional engagement portion is equipped; and an output side member provided with an output side frictional engagement portion; wherein the respective frictional engagement portions of the input-side member and the output-side member are opposed to each other to frictionally engage the opposed portions with each other; and an elastic means for pressing / pressing a frictional engagement portion against the other frictional engagement portion.

In the elevator gear train of the present invention are provided an input side member provided with an input side frictional engagement portion and an output side member provided with an output side frictional engagement portion, the respective frictional engagement portions of the an input side member and the output side member are opposed to each other to hold the opposite portions in frictional engagement with each other, and an elastic means for pressing / pressing a frictional engagement portion against the other frictional engagement portion, so that a torque limiting function between the input side member and the output side member is installed; when the torque applied between the input-side member and the output-side member is not greater than a threshold torque (maximum friction torque or slip torque) determined by the frictional engagement force between the input-side and output-side friction engagement portions transmitting the torque from the input side member to the output side member via a ratchet wheel to effect the winding of the tension spring; When the torque applied between the input-side member and the output-side member exceeds the threshold torque (maximum friction torque or slip torque) determined by the frictional engagement force between the input-side and output-side frictional engagement portions, slippage occurs the input side member and the output side member, and the winding of the tension spring with a larger torque than this is prevented, thereby making it possible to reliably perform the mounting within a range which does not cause damage to the tension spring and other related components. That is, in the elevator gear train of the present invention, the torque limit value (maximum friction torque) is built into the gear train upon mounting, so that on the one hand there is no need to provide the barrel with a slide attachment, whereby it is possible to set the length maximize the tension spring to maximize the internal volume of the barrel to maximize the duration of the mainspring and use a large maximum torque spring to increase the accuracy of the timepiece to the extreme; and, on the other hand, that the torque limiting function can be completed with the movement and there is no need to insert a torque limiting function or a slip torque generating mechanism into an outer component section, such as a motor vehicle. the crown, so that it is possible to avoid a complication or enlargement of an external component, e.g. the crown, thereby allowing to minimize the fear of imposing limits on the outside. Although in an elevator train the torque limiting function is typically provided at a single position, it is also possible to provide the torque limiting function at a variety of positions.

Typically, in the elevator gear train of the present invention, the input side frictional engagement portion of the input side member and the output side frictional engagement portion of the output side member in the direction in which a rotation center axis extends face each other.

In this case, the construction is suitable for a wheel of a torque transmission gear train in which a plurality of coaxial (concentric) gear portions (spur gear portions) are present. It should be noted, however, that such a wheel may form at least part of a plurality of crown intermediate gears connecting the crown wheel and the ratchet wheel.

Instead of arranging the input side frictional engagement portion of the input side member and the output side frictional engagement portion of the output side member facing each other in the direction in which a rotation center axis extends, it is also possible in the elevator gear train of the present invention in that the input-side frictional engagement portion of the input-side member and the output-side frictional engagement portion of the output-side member are radially opposed to each other with respect to a rotation center axis.

In this case, typically, the input-side member or the output-side member includes a shaft, and the output-side member or the input-side member is provided with an elastic arm portion which is in frictional engagement with the shaft (frictional engagement). to embrace the shaft elastically. In this connection, typically, the former is integrally connected to a drive portion (a small gear / pinion portion of relatively small diameter), and the latter is integrally connected to a gear portion (large gear portion of relatively large diameter). However, this can also be the other way around. This structure is suitably used on at least one of (the plurality of) crown intermediate gears (crown transmission wheels) instead of the crown gear of the elevator gear train. It is also possible that the two gear sections have the same diameter.

In the elevator gear train of the present invention, the elastic means may be formed on a part of the input side member and / or the output side member, or the elastic means may be separate from the input side member and the output side member In addition, a pressing means is provided to elastically press the input-side member and the output-side member by the elastic force of the elastic means against each other.

Typically, the former is suitable for a radial frictional engagement, and the latter is suitable for frictional engagement in the axial direction (a direction parallel to the direction in which the axis extends). However, this can also be the other way around.

In the case where in the elevator gear train of the present invention, the elastic means is composed of a separate component, the elastic means typically consists of a plate spring, a coil spring or a wave spring, and the pressing means is with a pressing force adjusting mechanism equipped in the form of a screw.

In the case where the pressing means is provided with a press force adjusting mechanism in the form of a screw, the pressing force is adjusted only by adjusting the threaded engagement state of the screw, thereby the threshold or limit torque of the torque limiting function That is, to adjust the magnitude of the slip torque. It is therefore possible to set the slip torque to a desired value, and it is e.g. also possible that the user himself sets the slip torque. If desired, the adjustment mechanism may also take a different shape from a screw.

The elastic means may be suitably selected as long as it can exert a sufficient pressing force to produce a desired frictional engagement force. It is e.g. desirable to use a plate spring to produce a large elastic force (and correspondingly the largest possible slip torque) with the smallest possible space requirement. However, it is also possible to use a wave spring, etc.

Typically, in the elevator gear train of the present invention, the input side member consists of a lower side crown gear meshing with the elevator gear, and the output side member is a top side crown gear meshing with a crown idler gear. In this specification, the "top" side refers to the back of the case and the "bottom" side to the dial side. Depending on the arrangement of the elevator drive, however, this can be the other way round.

In this case, a space in connection with the positional relationship between the crown gear and the elevator gear and the positional relationship between the crown gear and the crown intermediate gears can be effectively utilized in the installation of the frictional engagement sections.

Typically, in the elevator gear train of the present invention, there is provided a pivot bearing hollow shaft section whose center hole is snugly engaged with a crown gear guide pin and whose distal end side is provided with a male threaded portion of small diameter, the bottom side A crown gear is snugly engaged with a proximal end-side intermediate diameter portion of the rotary shaft hollow shaft portion, and a non-cylindrical hole portion of the top side crown gear is fitted with a non-cylindrical portion in the center of the rotary shaft hollow shaft portion is such that the upper side crown gear can rotate integrally with the rotary bearing hollow shaft portion, and wherein an internally threaded member with the located at the distal end side male threaded portion of the rotary bearing hollow shaft portion is threadedly engaged and by screwing n surfaces of the lower side crown gear and the upper side crown gear n of the female screw member are frictionally engaged with each other via an elastic means between the female screw member and the upper side crown gear.

In this case, by adjusting the amount of threaded engagement of the female threaded member and the male threaded member, it is possible to reliably set the amount of frictional engagement between the upper side crown gear and the lower side crown gear. The non-cylindrical hole portion of the upper side crown gear and the non-cylindrical portion of the rotary bearing hollow shaft portion may be arbitrarily configured as long as their sectional area deviates from a circular configuration; such as e.g. the cross-sectional area may be D-shaped, as obtained by linearly cutting off a side portion of a circle, or it may have a cart-like configuration, as obtained by cutting off both side portions of a circle. As long as a fitting fit is performed such that at least those portions abut each other whose configuration deviates from a circular configuration, the cross-sectional configuration of the non-cylindrical hole portion of the top side crown gear and that of the non-cylindrical portion of the pivot hollow shaft section may be different from each other.

In the elevator gear train of the present invention, the female thread member may have a smaller diameter than the upper side crown gear and be disposed in a central recess of the upper side crown gear, or the inner threaded member may have an approximately equal or larger diameter have the top crown wheel and be located on the top crown wheel.

In the latter case, the female threaded member can be easily rotated in the assembled state, and the threshold torque, i. the slip torque of the torque limiting function can be easily adjusted in the assembled state.

Moreover, in the elevator gear train of the present invention, the rotational center shafts of the lower-side crown gear and the upper-side crown gear may consist of solid shaft portions which are formed to be guided by pin bridge portions on both end sides, and upper pin-side portions of the shaft portions may be passed through a bridge plate which is removably attached to a wheel bridge.

In this case, by removing the bridge plate, it is also possible to take the crown gear portion with the slip structure out of the movement to set the threshold torque of the torque limiting function, i. E. adjust the size of the slip torque. The top side crown wheel is here e.g. with the rotation center shaft by means of snug fit to be integrally rotatable. In this case, the center shaft shaft-shaped shaft section is a shaft section formed by integrating the crown gear guide pin and the rotary shaft hollow shaft section with the pin sections rotatably supported at both ends thereof by the pin bridge sections.

In order to achieve the above object, a movement according to the invention is equipped with an elevator train described above.

In order to achieve the above object, a timepiece according to the invention has such a timepiece, i. a movement equipped with an elevator train described above.

Brief description of the drawing

[0029] <Tb> FIG. 1 <sep> is an explanatory sectional view of a part of a timepiece equipped with an elevator gear train according to a preferred embodiment of the present invention; <Tb> FIG. Fig. 2 <sep> is an explanatory plan view of the timepiece portion of the timepiece of Fig. 1 including the elevator gear train; <Tb> FIG. 3 <sep> is an explanatory sectional view (similar to FIG. 1) illustrating a part of a timepiece equipped with an elevator train according to another preferred embodiment of the present invention (a modification of the present invention); <Tb> FIG. 4A and 4B <sep> are diagrams illustrating another modification of the crown gear structure of the gear train of Fig. 3, wherein Fig. 4A is an explanatory plan view of a modification, and Fig. 4B is an explanatory sectional view of Fig. 4A; and <Tb> FIG. 5A and 5B <sep> are figures illustrating another modification of a gear equipped with a slip mechanism of the elevator gear train of Fig. 3, Fig. 5A is an explanatory plan view of another modification, and Fig. 5B is an explanatory plan view of still another Variation is.

Description of the preferred embodiments

A preferred manner of carrying out the present invention will now be described with reference to the preferred embodiments shown in the accompanying drawings.

[Embodiments]

A wind-up watch 3 according to a preferred embodiment of the present invention has a movement 2 according to a preferred embodiment of the present invention, which is equipped with an elevator gear train 1 according to a preferred embodiment of the present invention, as in the explanatory sectional view of FIG 1 and in the explanatory plan view of Fig. 2 is shown.

As seen from the sectional view of Fig. 1, the movement 2 of the timepiece 3 is provided with a mother board 11 at the central portion in the thickness direction D, and an elevator shaft 20 is supported on the mother board 11 so as to be fixed can be extended and retracted in the directions A1 and A2, and such that it is rotatable in the directions B1 and B2 about a center axis B around.

The elevator shaft 20 is provided with a large diameter flange portion 21, a large diameter columnar portion 22, a small diameter portion 23, a medium diameter flange portion 24, a medium diameter columnar portion 25, a prismatic portion 26, a portion 27 small diameter at the distal end side, etc. equipped. A clutch gear 15 is snugly engaged with the prismatic portion 26 so as to be relatively slidable in the directions A1 and A2, and an elevator gear 18 is snugly engaged with the columnar portion 25 of medium diameter so as to be in the directions B1 and B2 is relatively rotatable. The reference numeral 16 denotes an angle lever (lever), the reference numeral 16 denotes a Kupplungsstriebhebel (yoke), and the reference numeral 14 denotes a thumbwheel (handwheel).

At the rear of the housing 7 of the motherboard 11 (in the direction D1, as can be seen in Fig. 1) there are a gear bridge 12 and a barrel bridge 13. Between the motherboard 11 and the gear train bridge 12, located on the back of the housing 7 of the motherboard 11, as well as on the dial side 19 of the motherboard 11 (in the direction D2, as seen in Fig. 1) is a tick movement / pointer movement wheel 6 (Fig. provided, which is related to the clock generation and time display of the clock 3. The gear wheel 6 includes an inhibition rotating member (wheel and drive) 6a, etc.

Between the motherboard 11 and the barrel bridge 13, a barrel 30 is arranged. The barrel 30 is provided with a tension spring body 34 within a barrel drum chamber 33 constituted by a barrel drum main body 31 and a barrel cover 32, and the tension spring body 34 in the form of a coil spring is formed on an inner peripheral surface 31a of the barrel main body 31 is locked by an outer hook 34a at an outer peripheral end portion, and an inner peripheral end portion 34b thereof is mounted to a barrel shaft 35. A gear portion 31c of the barrel drum main body 31 meshes with the gear of the tick movement / pointer movement gear wheel 6. The barrel shaft 35 is rotatably supported by the mother board 11 and the barrel bridge 13 via bearing portions 36a and 36b, and a ratchet wheel 37 is mounted by a ratchet wheel screw 37a on a protruding end portion 35a of the barrel shaft 35.

The elevator gear train 1 includes a crown wheel assembly 8 which meshes with the elevator gear 18, a crown idler mechanism 9 connected to the crown gear assembly 8, and a ratchet wheel 37 connected to the crown idler gear Mechanism 9 is connected.

In this example, the crown-intermediate mechanism 9 consists of a first crown idler 41 and a second crown idler 42, which are rotatably supported by the barrel bridge 13 and the gear train bridge 12. The first crown idler 41 includes a shaft 41a, a first crown intermediate gear 41b integral with the shaft 41a, and a first crown intermediate gear 41c integral with the shaft 41a and smaller in diameter than the first one Crown intermediate gear 41b has, wherein the first crown intermediate gear 41b meshes with an output side gear of the crown gear assembly 8 and the first crown intermediate gear 41c meshes with the second crown intermediate gear 42. The second crown idler 42 meshes with the ratchet 37.

In this example, the crown gear assembly 8 constituting the elevator gear train 1 is mounted on the gear train bridge 12 together with the crown idler mechanism 9 and the ratchet wheel 37.

More specifically, the crown gear assembly 8 has a bearing shaft assembly 50 consisting of a crown gear guide pin 51 which is snugly engaged with the gear train bridge 12 and an externally threaded member 53 connected to the crown gear guide pin 51 is snugly engaged, a lower side crown gear 60, a top side crown gear 70, an elastic member 80, and a female threaded member 90.

The crown gear guide pin 51 of the bearing shaft assembly 50 is provided with a flange portion or large diameter flange portion 51 at the proximal end, a small diameter shaft portion 51b at the distal end, and a plurality of shaft portions 51d middle Diameter and shaft portions 51 e small diameter in the middle.

The male threaded member 53 has a cylindrical main body portion 54, a flange portion 55 at the proximal end side of the main body portion 54, and an male threaded portion 56 at the distal end side of the main body portion 54. The main body portion 54 is equipped with a non-cylindrical tube section 57 at its proximal end. As shown by the dashed line 57i in FIG. 1, the non-cylindrical pipe portion 57 has a portion 57i of different diameters in a part of the outer peripheral surface so that its cross-sectional configuration is non-circular (ie, a configuration of FIG a circular configuration deviates). The non-cylindrical pipe portion 57 of the male threaded portion 53 may here have any configuration as long as its cross-sectional configuration deviates from a circular configuration; Thus, for example, a D-shaped cross-section obtained by linear cutting of a side portion of a circle or a bar-shaped cross-section obtained by cutting off both side portions of a circle may be used. The flange-like portion 55 consists of two flange-like portions of different diameters, i. a first flange-like portion 58 and a flange-like portion 59; the first flange-like portion 58 located at the proximal end side and having a maximum diameter is provided with a recess 58a at its end surface.

In an outer edge region 59a of the second flange-like portion 59 and on the surface 58b of the housing rear side of the first flange-like portion 58, the annular bottom side crown gear 60 is disposed. The annular lower side crown gear 60 is snugly engaged with the second flange portion 59 so as to be slidably movable, and a dial side surface portion 61 may also slide with respect to the surface 58 b of the first flange portion 58. From the dial-side surface portion 61 of the lower side crown gear 60, the portion containing the sliding portion 58b of the first flange-like portion 58 is formed as a circular or annular recess 62, and a bottom surface 63 of the recess 62 becomes the surface 58b the first flange-like portion 58 held in sliding contact. A cylindrical inner peripheral surface 64 of the lower-side crown gear 60 is in sliding contact with the outer peripheral surface 59a of the second flange-like portion 59. The lower side crown gear 60 is provided with a gear portion 65 extending along the outer peripheral portion thereof and the gear portion 65 meshes with the gear portion 18 a of the elevator gear 18.

In a normal position (elevator drive in zero-step position) PO, in which the elevator drive 20 has been pressed in the direction A2, the elevator drive 20 is rotated in the direction B1 about the center axis B, the elevator drive 18 whose gear portion 18b meshes with the gear portion 15a of the clutch gear 15 which is rotated in the direction B1 integrally with the elevator shaft 20 in response to the rotation of the elevator shaft 20 in the direction B1, also rotated in the direction B1, and the bottom side crown gear 60, whose gear portion 65 meshes with the gear portion 18a of the elevator gear 18 is rotated in the direction E1 about the center axis E. An annular surface portion 67 protruding toward the housing back 7 is formed on the inner peripheral side portion 66a of the surface 66 of the housing back 7 of the lower side crown wheel 60, and the surface portion 67 is roughened to be a frictional engagement surface H1 to act. In other words, the outer peripheral side portion 66b of the surface 66 of the housing back 7 of the lower side crown wheel 60 is recessed as compared with the inner peripheral side portion 66a, thereby preventing mutual obstruction of adjacent members.

The thickness of the lower side crown wheel 60 in the area where the annular surface portion 57 is located is approximately equal to the height of the outer peripheral surface 59a of the second flange portion 59; more specifically, it is slightly larger than the height of the outer peripheral surface 59a. Thus, the annular surface portion 67 of the lower side crown gear 60 projects slightly toward the case back 7 beyond the surface 59b of the second flange portion 59.

In the outer peripheral portion 57a of the middle diameter pipe portion 57 of the male threaded member 53 and on the annular surface portion 67 of the lower side crown gear 60, the annular upper side crown gear 70 is disposed.

The ring-shaped top face gear 70 is provided with an annular lower end surface 72 and a cylindrical outer peripheral gear portion 73, and has an annular main body 71 provided with a non-cylindrical inner peripheral surface 74; and in the inner peripheral side portion on the case back 7, it has a cylindrical recess 75 of large diameter and large depth. The non-cylindrical inner peripheral surface 74 of the upper side crown gear 70 has a configuration whose cross-sectional configuration is practically coincident with the cross-sectional configuration of the non-cylindrical pipe section 57 of the male screw member 53. The non-cylindrical inner peripheral surface 74 of the annular upper side crown gear 70 is snugly engaged with the non-cylindrical pipe portion 57 of the male threaded member 54 so as to be integrally rotatable with the male threaded member 54; and an annular lower end surface 72 thereof, which is roughened to act as a frictional engagement surface H2, frictionally engages with the annular surface portion 67 of the lower side crown wheel 60 (frictional engagement), and the gear portion 73 in the outer peripheral portion thereof becomes the first crown idler 41 of the crown idler mechanism 9 is held in mesh (more specifically, with the first crown gear 41b of the first crown idler 41).

In the recess 75 of the top side crown gear 70 disc springs 80a and 80b are arranged as elastic members. The Belleville springs 80a and 80b have the same configuration except that they are reversely arranged, i. the bottom and the top are reversed. The plate springs 80a and 80b are composed of main body portions 81A and 81B which form the peripheral surfaces of truncated cones; they are arranged so that their respective small-diameter end portions 82A and 82B abut each other and their respective large-diameter end portions 83A and 83B face away from each other. In this example, the large-diameter end portion 83A of the lower-side plate spring 80A abuts on the bottom surface of the recess 75 of the upper-side crown gear 70, and the large-diameter end portion 83B of the upper-side disc spring 80B located on the opposite side abuts on a lower end surface 92 of FIG Female thread member 90 as an adjusting member. Thus, under the action of the elastic force of the Belleville springs 80A and 80B, the lower side crown gear 60 is held between the annular lower end surface 72 of the upper side crown gear 70 and the case rear side surface 58a of the first flange section 58 of the male threaded member 53, that they are in frictional engagement with each other (frictional engagement).

The inner diameter of the Belleville springs 80A and 80B is sufficiently larger than the cylindrical main body portion 54 of the male screw 53, and the outer diameter of the Belleville springs 80A and 80B is sufficiently smaller than the inner diameter of the recess 75 of the upper side crown wheel 70 Therefore, it is not necessary to fear that the inner peripheral surfaces of the Belleville springs 80A and 80B will be against the outer peripheral. As shown in Figs Surface of the cylindrical main body portion 54 of the externally threaded member 53 are pressed or that the outer peripheral surfaces of the plate springs 80 A and 80 B are pressed against the inner peripheral surface of the recess 75 of the upper side Kronenrads 70.

Inside the recess 75 of the top side crown gear 70, an internal thread member 90 is attached as an insert member to the plate springs 80A and 80B.

The internal thread member 90 has on its inner peripheral surface a female threaded portion 91 which is threadedly engaged with an externally threaded portion 56 of the male threaded member 53, and has at its lower end surface 92 a pressurizing surface portion, the the diaphragm spring 80B presses. The outer diameter of the outer peripheral surface 93 of the female thread member 90 is smaller than the inner diameter of the recess 75, so that the female thread member 90 can be loosely fitted in the recess 75 of the upper side crown gear 70. Typically, the internal thread member 90 has an outside diameter not smaller than that of the maximum diameter portion of the cup spring 80B, so that the bottom end surface 92 thereof can press down the maximum diameter portion. However, it may also be designed so that when expanding the maximum diameter portion, the radially inner portion of the maximum diameter portion is pressed.

More specifically, as seen from the plan view of Fig. 2 in addition to Fig. 1, the female thread member 90 on the diametrically opposite side cut-out portions 97a and 97b (indicated by the reference numeral 97, if they did not distinguish from each other or referenced collectively) extending along parallel surfaces 95a and 95b (indicated by reference numeral 95 when they are not distinguished from or referenced collectively) and along surfaces 96a and 96b (indicated by the Reference number 96 if they are not distinguished from each other or if they are collectively referred to). The surfaces 96a and 96b are flush with each other. In this case, the female threaded member 90 can be easily rotated in directions E1 and E2 about the center axis E by a tool having a recess at its distal end which engages with a protruding portion 98 defined by the surfaces 96a and 96b to bring is. It is therefore possible to easily adjust the degree to which the female threaded member 90 is screwed into the male threaded member 53 (the screwing degree), whereby the pressurizing force (normal force) generated between the frictional engagement surface H2, i. the surface 72 of the top crown wheel 70, and the frictional engagement surface H1, i. the surface 67 of the lower side crown wheel 60, through which the plate springs 80A and 80B is applied, can be easily adjusted, thereby making it possible to easily adjust the amount of frictional engagement force exerted between the two frictional engagement surfaces 72 and 67 the torque limit determined by the frictional engagement force, ie easily adjust the threshold torque (the maximum friction torque or slip torque). In the movement 2 equipped with this elevator gear train 1, the elastic urging force of the elastic member 80, which is related to the adjustment of the magnitude of the slip torque (maximum friction torque), by the Belleville springs 80A and 80B so that it is possible to reliably perform a setting which changes, to a considerable degree, the maximum frictional force which determines the maximum frictional torque with a minimum occupying volume or space requirement. However, instead of the Belleville springs 80A and 80B, the elastic member 80 may be made of another spring or another member.

That is, it is possible to easily adjust the limit of the frictional engagement between the lower-side crown gear 60 and the upper-side crown gear 70, in other words, the upper limit of the torque transmitted between the lower-side crown gear 60 and the upper-side crown gear 70. That this crown wheel assembly 8 is equipped with a torque limit by means of which it is possible to determine the upper limit of the winding torque of the tension spring.

In the case where, in the movement 2 equipped with the elevator gear 1, the female thread member 90 has been relatively rotated as an adjusting member in the direction E1, and in which the screwing degree in the direction D2 of the female thread member 90 with respect to the male threaded member 53 is small (ie, in the case where the female threaded member 90 has been relatively rotated as an adjusting member in the direction E1 and in which the female threaded member 90 is in the direction D1 with respect to the male thread Relative to the disk springs 80A and 80B as elastic members to a small extent, so that the pressurizing force in the direction D2 is small due to the Belleville springs 80A and 80B; Pressing force exerted between the frictional engagement surface 72 located on the lower side of the lower side crown gear 70 and the upper annular frictional engagement surface 67 of the lower side crown wheel 60 and between the frictional engagement surface (surface of the housing rear side) 58b of the first flange portion 58 of the male threaded member 53 and the lower side frictional engagement surface (bottom surface) 63 of the lower side crown wheel 60 is relatively small; and the upper limit value F of the frictional torque that can be applied between the frictional engagement surface 72 located on the lower side of the upper side crown gear 70 and the upper annular frictional engagement surface 67 of the lower side crown gear 60 and between the Frictional engagement surface (surface of the case back) 58b of the first flange 58 of the male threaded member 53 and the lower frictional engagement surface (bottom surface) 63 of the lower side crown gear 60 has a relatively small value (eg, F1).

When pulling the tension spring 34 via the elevator gear train 1 by rotating the elevator shaft 20 at the zero step position PO in the direction B1, the resistance which is attributable to the torque load, the between the lower side crown 60th and the top crown wheel 70 of the crown wheel assembly 80 is exerted, as the tension spring 34 further exceeds the upper limit value F1, slippage occurs between the upper frictional engagement surface 67 of the lower side crown gear 60 and the frictional engagement surface 72 of the upper sides Crown gear 70 and between the frictional engagement surface (surface of the housing rear side) 58b of the first flange portion 58 of the male threaded member 53 and the lower side frictional engagement surface (bottom surface) 63 of the lower side crown gear 60, whereby the winding of the tension spring 34th is suppressed with another load torque.

On the other hand, in the case where the female screw member 90 is screwed deep in the direction D2 with respect to the male screw member 53 to increase the pressing force between the Belleville springs 80B and 80A, so that the upper limit value F of FIG Friction torque which exists between the frictional engagement surface 72 located on the lower side of the upper side crown gear 70 and the upper annular friction engagement surface 67 of the lower side crown gear 60 and between the frictional engagement surface (surface of the case back ) 58b of the first flange portion 58 of the male threaded member 53 and the lower surface frictional engagement surface (bottom surface) 63 of the lower side crown gear 60 can be exerted, is a relatively large value (eg, F2 (> F1)) Tension spring 34 via the elevator gear train 1 by rotating the elevator shaft 20 at the zero-step position PO in the direction B1 even if the resistance, which of the rotation oment load is applied, which is exerted between the lower side crown gear 60 and the upper side crown gear 70 of the crown wheel assembly 8, the further reaches the tension spring 34 reaches the value F1, carried out the Aufzieh, without causing a slip occurs between the Friction engagement surface 67 of the lower side crown wheel 70 and the frictional engagement surface 72 of the top side crown wheel 70, and there is no slippage between the frictional engagement surface 67 of the lower side crown wheel 60 and the frictional engagement surface 72 of the top side crown gear 70 to Resistance, which is attributable to the torque load that is exerted between the lower side crown gear 60 and the upper side crown gear 70 of the crown wheel assembly 8, further tensioning the tension spring 34 exceeds the upper limit F2, whereby the winding of the tension spring 34 with another load torque is prevented.

That is, in the latter case, the tension spring 34 can be wound up to a higher torque. Further, in the movement 2 equipped with the elevator gear 1, it is possible to adjust the winding degree by adjusting the extent to which the internal thread member 90 is screwed.

As for the elastic member 80, diaphragm spring deformation is preferable because of a large spring constant, which makes it possible to change the pressing force by a small displacement in the direction D to a great extent; However, if desired, it is also possible, instead of disc springs, to use coil springs or other types of springs or another elastic material, such as e.g. Rubber, to use.

In the movement 2 equipped with the above-described elevator gear train 1, a torque limiting mechanism or a torque limiting function or a slip torque function is incorporated in the elevator gear train T of the movement 2, so that in contrast in the case of an automatic gear train, there is no need to arrange slip-fit inside the chamber 33 of the barrel 30, so that the tension-spring body 34 can occupy a space corresponding to the volume of sliding attachment; Thus, the length of the spring body 34 is increased, whereby over a long period of time, a stable torque output is made and is allowed to increase the torque value, thereby increasing the functional accuracy of the clock 3. Further, in the movement 2 equipped with the elevator gear train 1, a torque limiting mechanism or a torque limiting function or a slip torque function is incorporated in the elevator gear train 1 so that there is no need for the crown and others To provide external components with a slip torque function, thereby avoiding an unnatural increase in the size of the crown and other external components.

In the case of the movement 2 equipped with the elevator gear train 1 described above, the gear train bridge 12 is mounted on the mother board 11 with the distal end portion 51 of the crown wheel guide pin 50 of the crown wheel assembly 8 fitted is fastened or by means of press fit, whereby the elevator gear train 1 is installed in the movement 2. Thus, the adjustment of the slip torque F by the female threaded member 90 is performed before the crown gear assembly 8 is attached to the gear train bridge 12, so that after the assembly is done once, a disassembly of the movement is required, so that it is difficult to perform adjustment of the slip torque F from a practical point of view.

On the other hand, as shown in the sectional view of Fig. 3, it is also possible to provide an elevator gear train which permits adjustment of the state of threaded engagement of the male threaded member even after installation of the movement in the main body of the movement.

In a clock 3K with a movement 2K equipped with an elevator gear train 1K, as shown in Fig. 3, the components which are substantially the same as the components (members, section, etc.) of Fig. 3 bear. 1 and 2 are the same reference numerals as the components of Figs. 1 and 2, such components substantially corresponding to the components of Figs. 1 and 2; however, those components which are partly different from those of FIGS. 1 and 2 bear the reference numerals of FIGS. 1 and 2 with an addition K.

In contrast to the elevator gear train 1 of Fig. 1, in which the crown gear assembly 8 is mounted to the gear train bridge 12, in the elevator gear train 1K of Fig. 3, a crown gear assembly 8K is attached to a motherboard 11K mounted.

The crown gear assembly 8K also has a bearing shaft assembly 50K, the bottom crown gear 60, a top crown gear 70K, the elastic member 80, and a female threaded member 90K as the adjusting member. The bearing shaft assembly 50K here consists of a crown gear guide pin 51K and an externally threaded member 53K. Although, in the following example described below, the elevator gear trains 1 and 1K use virtually the same bottom-side crown wheel 60, it is also possible to use a bottom-side crown gear 60 having a more or less discriminating configuration.

The crown gear guide pin 51K is different from the crown gear guide pin 51 in that a distal end portion 51bK thereof is press-fitted in a hole of a crown gear bearing portion 11c of the mother board 11K; however, it is substantially the same as the crown wheel guide pin 51 because it has a flange portion 51 aK, a plurality of medium diameter shaft portions 51 dK, and a small diameter shaft 51 eK whose general configuration is substantially the same as that of the crown gear. Guide pin 51 is. The configuration of the crown gear guide pin 51K may be different from that of the crown gear guide pin 51.

Substantially like the male threaded member 53, the male threaded member 53K has a cylindrical main body portion 54K and a flange-like portion 55K at the proximal end side thereof; however, it differs from the male thread member 53 of the crown gear assembly 8 in that instead of supporting the first flange portion 58 of the flange portion 55 through the flange portion 51a of the crown gear guide pin 51, regulation by the flange portion 51 aK of the crown gear Guide pin 51 K is carried out such that the first flange-like portion 58 K of the flange-like portion 55 K supported by the crown gear bearing portion 11 c of the motherboard 11 K and supported.

More specifically, substantially like the male threaded member 53, the male threaded member 53K has a first flange portion 58K provided with a surface 58bK on which the bottom surface 63 of the recess 62 of the lower side crown wheel 60 slidably disposed is a second flange-like portion 59K provided with an outer peripheral surface portion 59aK rotatably supported by the lower-side crown wheel 60, and a non-cylindrical pipe portion 57K of medium diameter provided with a non-cylindrical outer peripheral surface portion 57aK which is snugly engaged with a non-cylindrical inner peripheral surface 74 of a top side crown gear 70K so as to be integrally rotatable with the top side crown gear 70K.

The top side crown gear 70K is shaped to be substantially similar to the top side crown gear 70, except that the height (the length of axial extension) of an annular main body 71K and the depth (the axial depth ) of a cylindrical recess 75K is much smaller than the height of the annular main body 71 of the top side crown gear 70 and the depth of the cylindrical recess 75. More specifically, as seen from Fig. 3, the depth of the cylindrical recess 75K of the upper side crown gear 70K is smaller than the height of the two plate springs 80A and 80B as elastic members, and the upper portion of the upper side plate spring 80B projects over the upper end portion 77 of the top crown wheel 70K out.

In this example, an internal thread member 90K as an adjusting member has a larger diameter than the diameter of the recess 57K of the top side crown gear 70K, and a bottom end surface 92K thereof abuts the large-diameter end portion 83B of the upper plate spring 80B of the recess 75K protruding elastic members 80 on. In this example, since the female-threaded member as the adjusting member rotates in the direction E2, the female-threaded member 90K is inserted into the male-threaded portion at the portion of threaded engagement between the female threaded portion 91K and the female threaded portion 56K in the direction D2. Member 53K is screwed in, and the lower end face 92K of the female thread member 90K presses the large-diameter end portion 83B of the upper plate spring 80B of the Belleville spring 80B and 80A of the elastic members 80 in the direction D2 so as to pressurize via the Belleville springs 80B and 80A. Force between the frictional engagement surface 72K of the top side crown gear 70K and the frictional engagement surface 67 of the bottom side crown gear 60, and between the frictional engagement surface (surface of the case back side) 58bK of the first flange portion 58K and the bottom frictional engagement surface (FIG. Bottom surface) 63 of the lower side crown wheel 60, thereby increasing the threshold of torque causing slippage between the frictional engagement surfaces 72K and 67 and between the frictional engagement surfaces 58bK and 63, i. the slip torque (maximum friction torque) F is increased.

In this example, in the portion where the crown gear assembly 8K is provided, the gear train bridge 12K is provided with an opening 12c formed therein by large cutting; In the state where the housing back 7 has been removed, a head portion 99 of the female threaded member 90K is exposed as an adjusting member through the opening 12c. By merely removing the housing back 7 and engaging the projection of the rotary tool with a plurality of engagement recesses 99a of the head portion 99 of the female threaded member 90K (eg, disposed at equal peripheral intervals about the center axis E), Therefore, in order to rotate it, it is possible to adjust the degree of screwing of the female threaded member 90K to thereby adjust the slip torque.

In the case of this elevator gear train 1K, the height of the upper-side crown gear 70K is smaller than that of the upper-side crown gear 70 of the elevator gear train 1, so that the gear section 73K of the upper sides is compared with the gear section 73 of the upper-side crown gear 70 -Kronenrads 70K from the housing back 7 is further spaced. In this elevator gear train 1K, therefore, the axial length (thickness) of a first crown intermediate gear 41cK of a first crown idler 41K is large, and a first crown intermediate gear 41bK of the first crown idler 41K meshes with the gear portion 73K of the top crown wheel 70K at a position spaced further from the housing back 7 than the first crown intermediate gear 41b of the first crown idler 41. In this example, therefore, the barrel bridge 13K is deflected downwardly 13d so that the lower end portion of the shaft 41aK of the first crown idler 41K can be rotatably supported to support the first crown intermediate gear 41bK of the first crown idler 41K at a position other than the housing Rear 7 is further spaced than the first crown intermediate gear 41 b of the first crown idler 41st

In the clock 3K with the movement 2K equipped with the above-described elevator gear 1K, when the elevator shaft 20 is rotated in the zero-step position PO in the direction P1, the crown gear 8K becomes over the clutch gear 15 and the elevator gear 18 are rotated in the direction E1, and in response to the rotation of the crown gear assembly 8K, the first crown idler 41K and the second crown idler 42 of the crown idler mechanism 9K are rotated to rotate the ratchet wheel 37, whereby the mounting of the tension spring body 34 proceeds. When the mounting of the tension spring body 34 proceeds and the torque F, which is to be transmitted between the lower side crown gear 60 and the upper side crown gear 70 of the crown gear assembly 8K when the tension spring body 34 is wound, exceeds a value indicated by the The amount of screwing of the female threaded member 90K is determined as adjusting in the direction D2, a slip is generated between the frictional engagement surface 67 of the lower side crown wheel 60 and the frictional engagement surface 72K of the top side crown gear 70K of the crown gear assembly 8K, and a further mounting of the tension spring body 34 is stopped.

The upper limit of the torque F can be set here by adjusting the amount of screwing of the female threaded member 90K. That is, even in this timepiece 3K, by merely setting the state of the elevator gear 1K constituting a part of the movement 2K, the upper limit of winding of the mainspring body 34 can be set to a desired value. In particular, in the movement 2K of the timepiece 3K, the engagement recess 99a of the female threaded portion 90K is exposed to the case back 7 within the large aperture 12c of the gear train bridge 12K, so that it is possible to merely remove the case back 7 to set the upper limit value of the lift torque of the tension spring body 34 to a desired value.

Instead of supporting the crown gear assembly 8K by fittingly fitting the minor diameter lower end portion 51bK of the crown gear guide pin 50K of the crown gear assembly 8K to the hole of the bearing portion 11c of the mother board 11k, as shown in FIG. 3 shown, it is also possible, such as in Figs. 4A and 4B, to use a crown gear assembly 8M having a shaft 51M whose both ends are formed into pin portions 51 fM and 50gM, the pin portion 51 gM at the lower end side by means of a bearing 11fM of a bearing portion 11cM of the motherboard 11M is supported, and the pin portion 51 fM on the lower end side is supported by a bearing 12fM of a bridge plate 12dM detachably fixed to a wheel bridge 12M. In this case, the shaft 51M corresponds to e.g. the shaft portion formed by assembling the crown gear guide pin 51 of Fig. 1 and the externally threaded member 53 in the form of a bearing hollow shaft portion.

In this case, only by detaching the bridge plate 12dM attached to the wheel bridge 12M by a detachable fastener 12gM like a screw from the wheel bridge 12M, the crown wheel assembly 8M can be easily detached. By using a crown gear assembly 8M as a crown gear assembly 8M which is provided with a slip torque of a given size F, it is therefore possible for the slip torque F of the crown gear assembly 8M to be set to one with the crown gear assembly 8M removed set predetermined state. That For example, in the case where the crown gear assembly 8M is provided with a bottom side crown gear and a top side crown gear that allows adjustment of the slip torque by means of an insert member such as an internally threaded member, the adjustment of the slip torque is performed by means of the adjusting member with the crown gear assembly 8M removed; thereafter, the pin portion 51 gM of the shaft 51M of the crown gear assembly 8M is inserted into the bearing 11fM of the main plate 11M, and also the bridge plate 12dM is put on and fixed to the wheel bridge 12M, so that the bearing 12fM is inserted into the pin portion 51 fM of the shaft 51M, whereby the crown gear assembly 8M can be easily disposed with predetermined slip torque F at a prevailing position.

In the crown gear assembly 8M shown in FIGS. 4A and 4B, the components that are substantially the same as those of FIG. 3 are identified by the same reference numerals for the corresponding components of FIGS. 1 and 2, the suffix M is added (if a component shown in Fig. 3 is identified by a reference number with suffix K at the end, the symbol "M" is added instead of the symbol "K").

Typically, the frictional engagement between the two slip torque generating elements (which are the bottom side crown wheel and the top side crown wheel in the above examples) is between surfaces arranged with respect to each other along the shaft extension direction (for example, in the examples of Figs. 1 and 3, between face 67 and face 72 or 72K and between face 63 and face 58b or 58bK). If desired, however, such as e.g. As shown in FIGS. 5A and 5B, it is also possible that this (the frictional engagement) occurs between one member 60Q or 60R equipped with one elastic arm portion 68Q or 68R and another member 70Q or 70R with a shaft 78Q or 78R, the links being provided with surfaces radially arranged with respect to one another. In this case, combing e.g. Gear portions 65Q and 65R of the links 60Q and 60R equipped with the elastic arm portions 68Q and 68R are each connected to a gear such as a gear wheel. a gear 18a of the elevator gear 18, and driving portions (not shown) integral with the shafts 70Q and 70R mesh with gear portions (not shown), such as those shown in Figs. the first crown intermediate gear (not shown) and the first intermediate crown gear (not shown) corresponding thereto. In this case, between the elastic arm portions 68Q, 68R and the shafts 78Q, 78R which are frictionally engaged with each other by the pressurizing force previously determined by the springs 80Q and 80R of the elastic arm portions 68Q and 68R, the frictional engagement torque (FIG. Slip torque) F as a function of the pressurization force achieved. In this case, the elastic pressurizing force exerted between the elastic arm portions 68Q, 68R and the shafts 78Q, 78R is typically fixed and does not allow adjustment; however, if desired, it is also possible to add an elastic force adjusting means.

Of the members shown in Figs. 5A and 5B, the components which are substantially the same as those of Figs. 1 and 2 are denoted by the same reference numerals as those of Figs. 1 and 2 with the addition Q or R, and the components substantially the same as those of Fig. 3 are denoted by the same reference numerals as those of Figs. 1 and 2 with the suffix Q or R (in the case where the suffix K is at the end of a reference numeral designating a component of Fig. 3, the symbol Q or R is added instead of the symbol K).

Claims (14)

An elevator gear train (1) provided with a plurality of intermeshing gears (spur gears) (60, 70, 41, 42) for transmitting rotation of an elevator shaft (20) to a ratchet wheel (37), and which has: an input side member (60) provided with an input side frictional engagement portion (67, H1); and an output side member (70) provided with an output side frictional engagement portion (72, H2); wherein the respective frictional engagement portions (67, 72) of the input side member (60) and the output side member (70) are opposed to each other to frictionally engage the opposing portions (67, 72) with each other; and an elastic means (spring means) (80) for pressing a frictional engagement portion (72) against the other frictional engagement portion (67). Elevator winding machine (1) according to claim 1, characterized in that the input side frictional engagement portion (67, H1) of the input side member (60) and the output side frictional engagement portion (72, H2) of the output side member (70) in FIG the direction in which a rotation center axis extends, facing each other. The elevator gear train (1) according to claim 1, characterized in that the input side frictional engagement portion (67, H1) of the input side member (60) and the output side frictional engagement portion (72, H2) of the output side member (70) with respect to a rotational center axis are radially opposite each other. The elevator gear train (1) according to claim 3, characterized in that the input side member (60) or the output side member (70) includes a shaft (shaft), and the output side member (70) and the input side member (60), respectively ) is provided with an elastic arm portion which is in frictional engagement with the shaft (frictional engagement) to elastically engage around the shaft. 5. Elevator train (1) according to any one of claims 1 to 4, characterized in that the elastic means on a part of the input-side member (60) and / or the output-side member (70) is formed. An elevator train (1) according to any one of claims 1 to 5, characterized in that the elastic means is separate (separate) from the input side member (60) and the output side member (70), further comprising a pressing means, to press the input side member (60) and the output side member (70) elastically against each other by the elastic force of the elastic means. An elevator gear train (1) according to claim 6, characterized in that the elastic means is typically a plate spring, a coil spring or a wave spring; and the pressing means is provided with a pressing force adjusting mechanism in the form of a screw. An elevator train (1) according to any one of claims 1 and 2, and 6 and 7, characterized in that the input-side member (60) consists of a lower-side crown gear which meshes with an elevator gear; and the output side member (70) consists of a top side crown gear meshing with a crown idler gear. An elevator gear train (1) according to claim 2, characterized in that a rotary bearing hollow shaft section is provided, the central hole of which is snugly engaged with a crown gear guide pin and the distal end side of which is provided with a male threaded portion of small diameter; wherein the lower-side crown gear is fittingly engaged with a middle-diameter portion of the rotary bearing hollow shaft section located at the proximal end side, and a non-cylindrical hole section of the upper side crown gear fits snugly with a non-cylindrical section at the center of the rotary shaft hollow shaft section is engaged, so that the top side crown wheel can rotate integrally with the rotary bearing hollow shaft section; and wherein an internally threaded member is threadedly engaged with the externally threaded portion of the swivel bearing hollow shaft portion at the distal end side, and by screwing the internally threaded member axially opposing surfaces of the lower side crown gear and the upper side crown gear via an elastic means between the female thread member and the upper crown gear are frictionally engaged with each other. An elevator gear train (1) according to claim 9, characterized in that the female thread member has a smaller diameter than the upper side crown gear and is disposed in a central recess of the upper side crown gear. 11. elevator gear train (1) according to claim 9, characterized in that the internal thread member has an approximately same or larger diameter as the top side crown gear and is arranged on the top side crown gear. The elevator gear train (1) according to claim 9, characterized in that the rotational center shafts of the lower side crown gear and the upper side crown gear are made of solid shaft portions which are shaped to be guided by pin bridge portions on both end sides ; and that upper pin-side portions of the shaft portions are passed through a bridge plate detachably attached to a wheel bridge. 13. Clockwork (2), which is equipped with an elevator gear train (1) according to one of claims 1 to 12. 14 o'clock (3), which is equipped with a movement (2) according to claim 13.