CN112486004A - Switching transmission wheel, automatic winding mechanism, movement for clock and watch and clock and watch - Google Patents

Switching transmission wheel, automatic winding mechanism, movement for clock and watch and clock and watch Download PDF

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Publication number
CN112486004A
CN112486004A CN202010952195.5A CN202010952195A CN112486004A CN 112486004 A CN112486004 A CN 112486004A CN 202010952195 A CN202010952195 A CN 202010952195A CN 112486004 A CN112486004 A CN 112486004A
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CN
China
Prior art keywords
switching
wheel
engagement
axis
pawl
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Granted
Application number
CN202010952195.5A
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Chinese (zh)
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CN112486004B (en
Inventor
木村怜次
早川和树
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Seiko Chronometer Co ltd
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Seiko Chronometer Co ltd
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Publication of CN112486004A publication Critical patent/CN112486004A/en
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    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch
    • G04B5/10—Automatic winding up by self-winding caused by the movement of the watch by oscillating weights the movement of which is not limited
    • G04B5/14—Automatic winding up by self-winding caused by the movement of the watch by oscillating weights the movement of which is not limited acting in both directions
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B11/00—Click devices; Stop clicks; Clutches
    • G04B11/006—Clutch mechanism between two rotating members with transfer of movement in only one direction (free running devices)

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
  • Medicines Containing Material From Animals Or Micro-Organisms (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Abstract

The present invention can reduce the rotational load and lead to an improvement in the windup performance. Provided is a switching transmission wheel (60), wherein the switching transmission wheel (60) is provided with: a rotating shaft section (65) having a switching transmission pinion gear (73); a switching wheel (61) that rotates by power transmitted from a power source; a rotating plate (62) combined with the rotating shaft; and a switching claw portion (63) which is combined with the rotating plate in a swinging manner, wherein the switching wheel is provided with a switching tooth portion (102), the switching tooth portion (102) is provided with an engaging surface (102a) facing one side of the circumferential direction and an inclined surface (102b) facing the other side of the circumferential direction, the switching claw portion is provided with a switching arm portion (122) extending from the second axis to one side of the circumferential direction and an engaging portion (124) engaged from one side of the circumferential direction relative to the engaging surface, and the switching claw portion is biased by a spring member (140).

Description

Switching transmission wheel, automatic winding mechanism, movement for clock and watch and clock and watch
Technical Field
The invention relates to a switching transmission wheel, an automatic winding mechanism, a clock movement and a clock.
Background
As a mechanism for winding up a power spring, a mechanical timepiece including an automatic winding mechanism is known. Generally, an automatic winding mechanism includes: a rotary hammer capable of rotating in two directions; and a switching transmission wheel for switching the two-directional rotation of the rotary hammer to one-directional rotation.
As such a switching transmission wheel, various types of switching transmission wheels have been known, and for example, a switching transmission wheel using a clutch wheel shown in patent document 1 below is known. The clutch wheel is provided with: a rotation shaft portion rotatable about an axis; a ratchet wheel fixedly connected to the rotating shaft part; a gear rotatably combined with the rotary shaft portion; a switching claw portion having a click claw swingably coupled to the gear and clicked to the ratchet; and a spring portion integrally combined with the gear and pushing the engaging pawl toward the ratchet wheel side.
According to the clutch wheel configured as described above, when the gear rotates in one direction about the axis line with respect to the rotating shaft portion, the switching pawl portion can swing so that the engagement of the engagement pawl falls off. Thus, the rotation shaft does not rotate, and the gear can rotate only in one direction. In contrast, when the gear rotates in the other direction around the axis with respect to the rotation shaft, the ratchet and the rotation shaft can be rotated in the other direction together with the gear while maintaining the engagement state between the engagement pawl and the ratchet.
In this way, by using the clutch wheel, even if the gear rotates in both the one direction and the other direction around the axis line due to the rotation of the rotary hammer, the rotary shaft portion can be rotated always in the same direction. As a result, the large wheel can be rotated in the same direction all the time via the rotation shaft, and the spring can be wound up.
Documents of the prior art
Patent document
Patent document 1: japanese Kokoku publication No. 46-9887.
Disclosure of Invention
Problems to be solved by the invention
However, the clutch wheel of the above-described conventional art is a so-called pawl type in which the engagement pawl rotates to push out the ratchet wheel. Specifically, from a state in which the engagement claw of the switching claw portion and the engagement face of the tooth portion of the ratchet are engaged with each other, the gear rotates so that the engagement claw pushes the engagement face in the circumferential direction, whereby the engagement state of the engagement claw and the engagement face can be maintained while the switching claw portion and the ratchet are rotated together.
In the above configuration, when the ratchet wheel rotates from the engagement pawl in the rotation direction toward the swing center of the switching pawl portion from the viewpoint that the ratchet wheel rotates first, the switching pawl portion and the ratchet wheel can be rotated together while maintaining the engagement state of the engagement pawl and the engagement surface. That is, the switching pawl portion is formed to extend from the swing center toward the upstream side in the rotation direction of the ratchet. The engagement pawl formed at the distal end portion of the switching pawl portion engages with the engagement surface of the tooth portion of the ratchet from the downstream side in the rotation direction of the ratchet. Thus, when the ratchet wheel rotates, the engagement claw and the engagement surface can be engaged with each other so that the switching claw portion is acted on by the compressive force and the switching claw portion and the ratchet wheel can be rotated together.
As described above, since the clutch wheel of the conventional art is of a so-called pusher-pawl type, if the switching pawl portion is formed so that the arm length from the swing center to the engagement pawl becomes long, the engagement (meshing) between the engagement pawl and the engagement surface of the tooth portion in the ratchet wheel tends to become insufficient, and the engagement tends to become disengaged. Therefore, it is difficult to make the arm length long.
However, when the switching pawl portion is freely rotated with respect to the ratchet by releasing the engagement between the engagement pawl and the engagement surface, it is required to reduce the load on the ratchet as much as possible. In order to respond to such a demand, it is conceivable to, for example, make the arm length of the switching pawl part long, and to secure a large distance from the swing center to the engaging pawl (i.e., the length of the arm that determines the rotational torque). This can reduce the load on the ratchet when the engaging pawl is pushed open against the spring portion.
However, as described above, the conventional clutch wheel is of a so-called pusher dog type, and it is difficult to extend the arm length of the switching pawl itself. Therefore, it is difficult to reduce the rotational load applied to the clutch wheel. As a result, the automatic winding mechanism using the clutch wheel has poor winding efficiency and leaves room for improvement in winding performance.
The present invention has been made in view of such circumstances, and an object thereof is to provide a switching transmission wheel, an automatic winding mechanism, a timepiece movement, and a timepiece, which can reduce a rotational load and can improve winding performance.
Means for solving the problems
(1) The switching transmission wheel according to the present invention is characterized by comprising: a rotation shaft portion rotatably disposed around a first axis and having a switching transmission pinion gear for transmitting power to a transmitted gear train; a switching wheel which is combined with the rotating shaft portion so as to be relatively rotatable and rotates around the first axis by power transmitted from a power source; a rotating plate integrally combined with the rotating shaft; and a switching claw portion which is combined with the rotating plate in an integrated manner and can swing around a second axis, wherein the switching wheel is provided with a plurality of switching tooth portions, each switching tooth portion is provided with an engaging surface facing one side of the circumferential direction rotating around the first axis and an inclined surface facing the other side of the circumferential direction, the switching claw portion is provided with a switching arm portion and an engaging portion, the switching arm portion is formed to extend from the second axis to one side of the circumferential direction, the engaging portion is formed at the top end portion of the switching arm portion and is engaged with the engaging surface in a manner of being capable of being separated from one side of the circumferential direction, and the switching claw portion is biased by a spring component so that the engaging portion is pressed against the engaging surface.
According to the switching transmission wheel of the present invention, when the switching wheel rotates about the first axis toward one side in the circumferential direction by the power transmitted from the power source, the plurality of switching teeth rotate in the same direction along with this. At this time, the engagement portion of the switching pawl portion is engaged with the engagement surface of the switching tooth portion from one side in the circumferential direction, and thus the engagement state between the engagement surface and the engagement portion can be maintained. Therefore, the switching claw portion can be rotated toward one side in the circumferential direction in accordance with the rotation of the switching wheel. In addition, the switching claw portion is rotated, so that the rotating shaft portion can be rotated toward one side in the circumferential direction via the rotating plate. Therefore, the power transmitted to the switching wheel can be transmitted to the transmitted train wheel via the switching transmission pinion of the rotating shaft portion.
Next, in contrast to the above case, when the switching wheel rotates about the first axis toward the other side in the circumferential direction by the power transmitted from the power source, the plurality of switching teeth portions rotate in the same direction along with this. In this case, the inclined surface in the switching tooth portion moves over the engaging portion of the switching pawl portion, and thus the switching pawl portion swings about the second axis while resisting the biasing force (urging force) by the spring member. Thus, the engagement of the engagement portion with respect to the engagement surface is released, and the switching wheel can be caused to idle about the first axis toward the other side in the circumferential direction.
Therefore, when power is transmitted to the switching wheel such that the switching wheel is rotated toward one side in the circumferential direction, the entire rotating plate and the rotating shaft portion can be rotated in the same direction while maintaining the state in which the engagement surface of the switching tooth portion is engaged with the engagement portion, and power can be transmitted to the transmission target gear train. In contrast, when power is transmitted to the switching wheel such that the switching wheel rotates toward the other side in the circumferential direction, only the switching wheel can be idled, and power can be prevented from being transmitted to the transmitted gear train. Therefore, even if the switching wheel rotates in both directions, power can be transmitted so that the transmitted gear train always rotates in one direction. Therefore, the switching transmission wheel can be used in, for example, an automatic winding mechanism.
In particular, the switching claw portion has a switching arm portion formed to extend from a second axis line as a swing center toward one side in the circumferential direction, and an engagement portion is formed at a tip end portion of the switching arm portion. Therefore, when the switching wheel is rotated to one side in the circumferential direction, the switching arm portion can be pulled by rotating the switching pawl portion. Therefore, unlike the conventional art, the switching claw portion can function as a so-called claw-type switching claw portion that causes a tensile force to act on the switching arm portion.
In this case, even if the arm length of the switching arm portion is made long, unlike the pusher-claw type of the related art, the engagement state between the engagement surface and the engagement portion can be easily maintained, and a state in which the engagement is hard to come off can be secured. Therefore, the length of the switching arm portion can be made longer than in the related art, and accordingly the engaging portion can be pushed open with a small force against the biasing force of the spring member. Therefore, the rotational load at the time of idling of the switching wheel can be reduced, and the windup performance can be improved when the switching wheel is used for an automatic winding mechanism or the like.
(2) The engaging portion may maintain an engaged state with respect to the engaging surface when the switching wheel rotates about the first axis toward one side in the circumferential direction, and may release engagement with respect to the engaging surface by the inclined surface when the switching wheel rotates about the first axis toward the other side in the circumferential direction.
In this case, the above-described effects can be more reliably achieved. That is, even if the switching wheel rotates in both directions, power can be transmitted, the transmitted gear train can always rotate in one direction, and the switching transmission wheel can be used in, for example, an automatic winding mechanism.
(3) The rotating plate may be provided with a regulating member that regulates the swing of the switching claw portion about the second axis when the engagement of the engaging portion with respect to the engaging surface is released.
In this case, when the engagement of the engagement portion with respect to the engagement surface is released and the switching wheel idles, the swing of the switching claw portion about the second axis can be restricted by a restricting member such as an abutment member. This can prevent the switching claw portion from being excessively swung, and thus, for example, the spring member can be prevented from being greatly deformed and plastically deformed. This enables stable operation over a long period of time, and improves the operational reliability. In particular, when a drop impact is applied or when a manual string winding operation is performed, it is assumed that the switching claw portion is excessively swung. However, even in such a case, the spring member can be effectively prevented from being largely deformed.
(4) The spring member may be formed separately from the switching claw portion and may be combined with the rotating plate.
In this case, since the spring member is formed separately from the switching claw portion, the spring member can be designed separately, and for example, a material, a plating layer, or the like different from that of the switching claw portion can be selected.
(5) The spring member may be formed integrally with the switching claw portion and may be combined with the rotating plate.
In this case, since the switching claw portion and the spring member are integrally formed, the number of parts can be reduced, and weight reduction, cost reduction, and improvement in assembling performance can be achieved.
(6) The automatic winding mechanism according to the present invention is characterized by comprising: the switching transmission wheel; a rotary hammer that can rotate in two directions about a third axis and functions as the power source; and a transmitted gear train for connecting the switching transmission pinion and a large steel wheel for winding up a spring, wherein a pair of the switching wheels and the switching claw portions are provided so as to be disposed on both sides in the first axial direction with the rotating plate interposed therebetween, a switching wheel positioned on the switching transmission pinion side with respect to the rotating plate among the pair of switching wheels is a first switching wheel that rotates in accordance with rotation of the rotary hammer, a remaining switching wheel among the pair of switching wheels is a second switching wheel that rotates in a direction opposite to the first switching wheel in accordance with rotation of the rotary hammer, a switching claw portion positioned on the switching transmission pinion side with respect to the rotating plate among the pair of switching claw portions is a first switching claw portion that operates in association with the first switching wheel, and a remaining switching claw portion among the pair of switching claw portions is a second switching claw portion that operates in association with the second switching wheel.
According to the automatic winding mechanism of the present invention, if the rotary hammer rotates in both directions about the third axis, the first switching wheel and the second switching wheel rotate in opposite directions to each other about the first rotation axis along with the rotation thereof. Therefore, in the case where, for example, the first switching wheel is rotated toward one side in the circumferential direction due to the rotation of the rotary hammer, the second switching wheel is rotated toward the other side in the circumferential direction.
If the first switching wheel is rotated toward one side in the circumferential direction, the first switching claw portion is rotated in the same direction together with the first switching wheel, as in the case described previously, whereby the rotating plate and the rotating shaft portion are rotated in the same direction. Therefore, the power transmitted to the first switching wheel can be transmitted to the transmitted gear train via the switching transmission pinion, and can be transmitted to the large steel wheel via the transmitted gear train, winding up the power spring.
At the time of the above-described rotation of the first switching wheel, the second switching wheel rotates toward the other side in the circumferential direction. At this time, the second switching claw portion rotates toward one side in the circumferential direction as the rotating plate rotates. Therefore, the second switching wheel rotates toward the other side in the circumferential direction with respect to the second switching pawl rotating toward the one side in the circumferential direction. Thus, as in the case described above, since the engagement surface of the switching tooth portion in the second switching wheel and the engagement portion in the second switching pawl portion are not engaged with each other, the second switching wheel is in an idling state. Therefore, the rotation shaft portion is not rotated by the rotation of the second switching wheel.
Next, contrary to the above case, when the first switching wheel rotates toward the other side in the circumferential direction along with the rotation of the rotary hammer and the second switching wheel rotates toward one side in the circumferential direction, the movement becomes opposite to the above case, and therefore, the power transmitted to the second switching wheel can be transmitted to the bull wheel via the switching transmission pinion, and the bull wheel can be rotated in the same direction as before to wind up the power spring. Further, since the first switching wheel is idly rotated, the rotation shaft portion is not rotated by the rotation of the first switching wheel.
Therefore, the rotation shaft portion having the switching pinion gear can be always rotated in the same direction by the power generated by the rotary hammer rotating in both directions, and the large steel wheel can be rotated to wind up the power spring. In particular, the rotational load at the time of idling of the first switching wheel and the second switching wheel can be reduced, and thus the windup performance can be improved.
(7) The movement for a timepiece according to the present invention is characterized by including the automatic winding mechanism.
(8) The timepiece according to the present invention is characterized by including the timepiece movement.
In this case, since the automatic winding mechanism is provided, the timepiece movement and the timepiece with improved winding performance and high reliability can be provided.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the present invention, the rotational load can be reduced, and the wind-up performance can be improved.
Drawings
Fig. 1 is a view showing a first embodiment according to the present invention, and is an external view of a timepiece.
Fig. 2 is a perspective view of the automatic winding mechanism in the movement of fig. 1.
Fig. 3 is a perspective view of the switching transmission wheel shown in fig. 2.
Fig. 4 is a perspective view of a state in which the upper stage switching gear is detached from the state shown in fig. 3.
Fig. 5 is a longitudinal sectional view of the switching transmission wheel shown in fig. 3, which is a longitudinal sectional view taken along line a-a shown in fig. 6.
Fig. 6 is a plan view showing a relationship among the upper switching pawl wheel, the upper switching pawl portion, and the spring member shown in fig. 5.
Fig. 7 is a plan view taken along line B-B shown in fig. 5, and is a diagram showing a relationship between the lower switching claw wheel, the lower end switching claw portion, and the spring member.
Fig. 8 is a diagram illustrating a second embodiment according to the present invention, and is a plan view illustrating a relationship among the upper switching pawl wheel, the upper switching pawl portion, and the spring member.
Fig. 9 is a diagram illustrating a third embodiment according to the present invention, and is a plan view illustrating a relationship among the upper switching pawl wheel, the upper switching pawl portion, and the spring member.
Fig. 10 is a diagram illustrating a fourth embodiment according to the present invention, and is a plan view illustrating a relationship among the upper switching pawl wheel, the upper switching pawl portion, and the spring member.
Detailed Description
(first embodiment)
Hereinafter, a first embodiment according to the present invention will be described with reference to the drawings. In the present embodiment, an automatic winding mechanical timepiece is described as an example of a timepiece.
(basic constitution of timepiece)
In general, a mechanical body including a driving portion of a timepiece is referred to as a "movement". The state in which the dial and the pins are attached to the movement and put in the timepiece case to be completed is referred to as "completed product" of the timepiece. Of the two sides of the bottom plate constituting the base plate of the timepiece, the side on which the glass of the timepiece case is present (i.e., the side on which the dial is present) is referred to as the "back side" of the movement. Of the two sides of the bottom plate, the side on which the case back cover of the timepiece case is present (i.e., the side opposite to the dial) is referred to as the "front side" of the movement. In the present embodiment, a direction from the dial plate to the case back cover is described as an upper side, and an opposite side is described as a lower side.
As shown in fig. 1, the finished timepiece 1 of the present embodiment includes, in a timepiece case 2 including a case back cover and a glass 3, not shown: a movement (movement for a timepiece relating to the present invention) 10; a dial 4 having a scale or the like indicating information at least relating to time; and hands including an hour hand 5 representing a clock, a minute hand 6 representing minutes, and a second hand 7 representing seconds.
The movement 10 includes a bottom plate not shown, a train wheel bridge not shown disposed on the front side of the bottom plate, a balance spring bridge, and the like. Between the bottom plate, the train wheel bridge, and the balance spring mechanism bridge, a meter-side train wheel, an escapement for controlling the rotation of the meter-side train wheel, a speed governor for adjusting the speed of the escapement, a manual winding mechanism, and an automatic winding mechanism 11 shown in fig. 2 are mainly disposed. In the present embodiment, the watch-side gear train, the escapement, the speed governor, and the manual winding mechanism are not shown. A back-side wheel train or the like, not shown, is disposed on the back side of the base plate, and the dial 4 is disposed so as to be visible through the glass 3.
A stem guide hole, not shown, is formed in the bottom plate, and the stem 12 shown in fig. 1 is fitted into the stem guide hole so as to be rotatable about the axis. The stem 13 is coupled to the stem 12. Thereby, the stem 12 can be rotationally operated via the stem 13.
The stem 12 is provided with a switching device, not shown, such as a needle lever, a clutch lever, and a clutch lever spring, to determine the position in the axial direction. A vertical wheel, not shown, is attached to the guide shaft portion of the stem 12 so as to be rotatable with respect to the stem 12 and immovable in the axial direction. A clutch wheel, not shown, is attached to a portion of the stem 12 on the tip end side of the stem than the vertical wheel so as to be non-rotatable with respect to the stem 12 and movable in the axial direction.
For example, when the stem 12 is set at a position (zero-order position) of the stem 12 closest to the movement 10 in the axial direction, the capstan and the clutch can be meshed with each other. Therefore, in this state, the stem 12 can be rotated via the stem 13, and the vertical wheel can be rotated about the axis coaxial with the stem 12 via the clutch wheel.
The vertical wheel rotates, so that the large steel wheel 20 shown in fig. 2 can be rotated via the manual winding mechanism. Further, the large steel wheel 20 rotates, and the mainspring (power source of the movement) housed inside the barrel wheel 21 can be wound up.
The front wheel system mainly comprises a barrel wheel 21, a second wheel, a third wheel and a fourth wheel. In the present embodiment, the second, third, and fourth wheels are not shown. These second, third, and fourth wheels rotate in sequence in accordance with the rotation of barrel wheel 21 rotated by the elastic restoring force of the wound spring.
Further, the second hand 7 shown in fig. 1 rotates based on the rotation of the fourth wheel, and rotates at a rotational speed regulated by the escapement and the governor, i.e., rotates by 1 turn in 1 minute. The minute hand 6 rotates based on the rotation of the second wheel or the rotation of a not-shown minute wheel that rotates along with the rotation of the second wheel, and rotates at a rotation speed regulated by the escapement and the governor, that is, 1 revolution within 1 hour. The hour hand 5 rotates via a not-shown jumper wheel based on rotation of a not-shown hour wheel that rotates in accordance with rotation of the second wheel, and rotates at a rotation speed regulated by an escapement and a governor, that is, rotates 1 turn in 12 hours or 24 hours.
The escapement includes: an escape wheel that meshes with the winding wheel and rotates by power transmitted from the winding spring; and a pallet for regularly rotating the escape wheel, the escape controlling the train wheel by regular vibration from the balance spring mechanism. The governor mainly includes a balance spring mechanism, and reciprocates (rotates forward and backward) at a stable amplitude (swing angle) corresponding to the output torque of the barrel drum 21 using a balance spring (not shown) as a power source.
As shown in fig. 2, the barrel wheel 21 includes: a barrel shaft 23 rotatably supported by the bottom plate and the train wheel bridge; and a barrel case 22 rotatably combined with the barrel shaft 23 and accommodating the power spring therein. A barrel gear 22a that meshes with the second gear is formed in the barrel case 22.
The power spring is housed in the barrel case 22 in a state of being wound in a spiral shape with respect to the barrel shaft 23. The power spring is wound up by the rotation of the barrel shaft 23, and the barrel case 22 is rotated by the elastic restoring force at the time of unwinding, and the power (rotational torque) is transmitted to the case side train wheel via the second wheel.
The large steel wheel 20 is disposed between the barrel case 22 and the train wheel bridge, and is fixed to the barrel shaft 23 by, for example, press fitting. The large steel pulley 20 has a large steel pulley gear 20a that meshes with a transmission gear, not shown, constituting a manual winding mechanism, and is rotatable about an axis O1 in a predetermined direction. In addition, in the present embodiment, the following case is exemplified: the large steel wheel 20 rotates in a clockwise direction (hereinafter, simply referred to as a clockwise direction) as viewed from above (the housing rear cover side) as indicated by an arrow in fig. 2.
Thereby, the clockwise rotation of the large steel wheel 20 can wind up the mainspring via the barrel shaft 23. Further, a second transmission gear 52a of a second transmission gear 52 in the automatic winding mechanism 11 described later meshes with the large steel wheel gear 20 a. Therefore, the large steel wheel 20 can be rotated in the clockwise direction via the second transmission wheel 52, and the mainspring can be wound up by the automatic winding mechanism 11.
Further, a pawl, not shown, which restricts the reverse rotation of the large steel wheel 20 engages with the large steel wheel 20 so as to prevent the wound spring from loosening. By the pawls, the large steel wheel 20 is allowed to rotate in a clockwise direction, and is restricted from rotating in a counter-clockwise direction (hereinafter, simply referred to as a counter-clockwise direction) opposite thereto.
(automatic winding mechanism)
The automatic winding mechanism 11 is a mechanism that automatically winds up a spring by rotation of a rotary hammer 30 that operates in accordance with, for example, movement of a user's wrist, and includes the rotary hammer 30, a switching transmission wheel 60, a center gear train 40 disposed between the rotary hammer 30 and the switching transmission wheel 60, and a transmission gear train (a transmitted gear train according to the present invention) 50 disposed between a large steel wheel 20 and the switching transmission wheel 60.
The rotary hammer 30 is rotatable in two directions about an axis (third axis according to the present invention) O2, and functions as a power source for operating the automatic winding mechanism 11. Specifically, the rotary weight 30 includes the ball bearing 31, the rotary weight body 35, and the rotary weight 36, and rotates in both the clockwise direction and the counterclockwise direction about the axis O2 in accordance with the movement of the wrist of the user or the like.
The ball bearing 31 includes: an inner ring 32 fixed to a not-shown cleat member; an outer ring 33 surrounding the inner ring 32; and a plurality of balls, not shown, rotatably interposed between the inner race 32 and the outer race 33. Thereby, the outer race 33 is rotatable relative to the inner race 32 about the axis O2 via the balls. A rotary hammer pinion gear 33a is formed on the outer peripheral surface of the outer race 33 over the entire circumference.
The rotary weight 35 is formed in a fan shape in plan view and is externally fitted to the outer ring 33. The rotary weight 36 is fixed to the outer peripheral edge of the rotary weight body 35. Therefore, the rotary weight 36, the rotary weight 35, and the outer race 33 can rotate integrally about the axis O2.
The centering train 40 includes: a first centering wheel 41, rotating about axis O3; a second centering wheel 42, rotating about axis O4; and a third centering wheel 43, rotating about axis O5. The first centering wheel 41, the second centering wheel 42, and the third centering wheel 43 are rotatably supported by a not-shown bridge member, respectively.
The first centering wheel 41 includes a first centering gear 41a and a first centering pinion 41b that mesh with the rotary hammer pinion 33 a. Thereby, the first centering wheel 41 can rotate about the axis O3 with the rotation of the rotary hammer 30, and rotate in the opposite direction with respect to the rotation direction of the rotary hammer 30.
The second centering wheel 42 includes a second centering gear 42a and a second centering pinion 42b that mesh with the first centering pinion 41 b. Thereby, the second centering wheel 42 can rotate about the axis O4 in accordance with the rotation of the first centering wheel 41, and rotate in the same direction as the rotation direction of the rotary hammer 30.
The third centering wheel 43 includes a third centering gear 43a that meshes with the second centering pinion 42 b. Thereby, the third centering wheel 43 can rotate about the axis O5 in conjunction with the rotation of the second centering wheel 42, and rotate in the opposite direction with respect to the rotation direction of the rotary hammer 30.
The drive train 50 includes a first drive wheel 51 rotating about an axis O6 and a second drive wheel 52 rotating about an axis O7. The first transmission wheel 51 and the second transmission wheel 52 are rotatably supported by respective not-shown bridge members.
The first transmission wheel 51 includes: a first transmission gear 51a meshed with a switching transmission pinion 73 described later in the switching transmission wheel 60; and a drive pinion 51 b. Thereby, the first transmission wheel 51 can rotate about the axis O6 in accordance with the rotation of the switching transmission pinion 73. Specifically, the switching transmission pinion 73 is configured to rotate in the counterclockwise direction at all times, as will be described in detail later. Therefore, the first transmission wheel 51 can always rotate around the axis O6 in the clockwise direction in accordance with the rotation of the switching transmission pinion 73.
The second transmission wheel 52 includes a second transmission gear 52a meshing with the first transmission pinion 51b and the large steel wheel gear 20 a. Accordingly, the second transmission wheel 52 can rotate counterclockwise about the axis O7 in accordance with the rotation of the first transmission wheel 51. Therefore, the second transmission wheel 52 can always rotate the large steel wheel 20 clockwise as described above.
(switching driving wheel)
As shown in fig. 2, the switching transmission wheel 60 functions as follows: the rotary hammer 30 is rotated about the axis (first axis) O8 by the power of the rotary hammer 30 transmitted through the above-described centering train wheel 40, and the power of the rotary hammer 30 is transmitted to the large steel wheel 20 through the transmission train wheel 50 in a state in which the rotation of the rotary hammer 30 in both directions is switched to the rotation in one direction.
As shown in fig. 3 to 5, the switching transmission wheel 60 includes: a hub (a rotating shaft portion according to the present invention) 65 rotatable about an axis O8; a pair of switching wheels 61, relatively rotatably combined with respect to the wheel shaft 65, and rotated about the axis O8 by power transmitted from the rotary hammer 30 via the centering train wheel 40; a rotating plate 62 integrally combined with the wheel shaft 65; and a pair of switching claw portions 63 integrally combined with the rotating plate 62 so as to be swingable about a swing axis (second axis according to the present invention) O9.
In a plan view of the switching pulley 60 in the direction of the axis O8, which is the central axis thereof, the direction intersecting the axis O8 is referred to as a radial direction, and the direction revolving around the axis O8 is referred to as a circumferential direction.
The upper tenon portion 70 and the lower tenon portion 71 of the axle 65 are rotatably supported by unillustrated cleat members, respectively. In a portion of the wheel shaft 65 located lower than the tenon portion 70, a switching transmission pinion 73 is formed, and the first transmission gear 51a of the first transmission gear 51 engages with the switching transmission pinion 73. Further, a first step portion 74 is formed in a portion of the wheel shaft 65 located below the switching transmission pinion gear 73, and a second step portion 75 is formed in a portion located below the first step portion 74.
A cylindrical upper seat 80 is fixed to the first step portion 74 of the wheel shaft 65 by press fitting or the like. The upper seat 80 includes: a first upper seat cylinder 81 fixed to the first stage portion 74; a second upper seat cylinder 82 extending downward from the lower end of the first upper seat cylinder 81 and having a diameter smaller than that of the first upper seat cylinder 81; and an annular upper seat flange portion 83 extending outward in the radial direction from the upper end portion of the first upper seat cylinder 81. The upper seat 80 configured as described above is fixed to the first stage portion 74 in a state where the upper seat flange portion 83 is in contact with the switching transmission pinion gear 73 from below.
A cylindrical lower seat 85 is fixed to the second step portion 75 of the hub 65 by press fitting or the like. The lower seat 85 includes: a lower seat tube 86 fixed to the second stage portion 75; and an annular lower seat flange portion 87 extending radially outward from the lower end of the lower seat cylinder 86. The lower seat 85 configured in this manner is fixed to the second stage portion 75 in a state of being located below the upper seat 80.
The rotating plate 62 is fixed to the second upper sleeve 82 by press fitting or the like. Thereby, the rotating plate 62 is integrally combined with the wheel shaft 65 via the upper seat 80. In the illustrated example, the rotating plate 62 is formed in a disc shape having a diameter larger than the upper and lower flange portions 83 and 87. However, the present invention is not limited to this case, and the upper flange portion 83 and the lower flange portion 87 may be formed to have a larger diameter than the rotating plate 62. The rotating plate 62 is fixed by press-fitting or the like with three coupling pins 90, 91, and 92 arranged at intervals in the circumferential direction on the outer peripheral edge portion side. These coupling pins 90, 91, and 92 are formed in a cylindrical shape so as to protrude toward the upper surface side and the lower surface side of the rotating plate 62.
The pair of switching wheels 61 are disposed on both upper and lower sides of the rotating plate 62. Of the pair of switching wheels 61, the switching wheel 61 positioned closer to the switching transmission pinion 73 than the rotating plate 62 is an upper switching wheel (first switching wheel according to the present invention) 100. Further, the switching wheel 61 positioned below the rotating plate 62 out of the pair of switching wheels 61 is a lower switching wheel (second switching wheel according to the present invention) 110.
The pair of switching claw portions 63 are disposed on both upper and lower sides of the rotating plate 62. Of the pair of switching pawls 63, the switching pawl 63 located closer to the switching drive pinion 73 than the rotating plate 62 is an upper switching pawl (first switching pawl according to the present invention) 120 that operates in association with the upper switching wheel 100. Further, the switching claw portion 63 located below the rotating plate 62 of the pair of switching claw portions 63 is a lower switching claw portion (a second switching claw portion according to the present invention) 130 that operates in association with the lower switching wheel 110.
The relationship between the upper switching wheel 100 and the upper switching claw 120 will be described in detail. As shown in fig. 5 and 6, the upper switching wheel 100 includes: an upper stage switching pawl wheel 101 combined to be relatively rotatable with respect to the first upper seat cylinder 81 in the upper seat 80; and an upper switching gear 105 fixed to the upper switching pawl wheel 101.
The upper stage switching dog wheel 101 has a plurality of switching teeth 102 over the entire circumference, and has an upper stage coupling cylinder 103 projecting upward from the inner circumferential edge. The switching tooth portion 102 is a tooth portion having an engaging face 102a and an inclined face 102b, the engaging face 102a faces in a counterclockwise direction which is one side of a circumferential direction about the axis O8, and the inclined face 102b faces in a clockwise direction which is the other side of the circumferential direction.
As shown in fig. 3 and 5, the upper switching gear 105 is fixed to the upper coupling cylinder 103 by press fitting or the like. Thereby, the entire upper stage switching wheel 100 is combined via the upper seat 80 so as to be relatively rotatable with respect to the wheel shaft 65. Further, the upper switching gear 105 has an upper switching tooth portion 105a that meshes with the second centering pinion 42b in the second centering wheel 42. Therefore, the entire upper stage switching wheel 100 can rotate about the axis O8 with the rotation of the second centering pinion 42b, and can rotate in the opposite direction with respect to the rotation direction of the second centering wheel 42 (i.e., rotate in the opposite direction with respect to the rotation direction of the rotary hammer 30).
As shown in fig. 5 and 6, the upper switching claw portion 120 is carried on the upper surface side of the rotating plate 62 so as to be disposed in the gap between the rotating plate 62 and the upper switching gear 105. Therefore, the upper switching claw 120 is disposed radially outward of the upper switching claw wheel 101.
The upper stage switching pawl portion 120 is formed in a substantially circular arc shape extending in the circumferential direction, and a central portion 121 thereof is combined relatively rotatably with respect to the coupling pin 90 fixed to the rotating plate 62. Thereby, the upper switching pawl 120 can swing in the radial direction about the coupling pin 90. Further, the center axis of the coupling pin 90 is a swing axis O9. Therefore, the upper switching pawl portion 120 is integrally combined with the rotating plate 62 via the coupling pin 90 so as to be swingable about the swing axis O9.
The upper switching claw portion 120 includes: a first switching arm portion (switching arm portion according to the present invention) 122 formed to extend in a counterclockwise direction from a central portion 121 combined with the coupling pin 90; and a second switching arm portion 123 formed to extend clockwise from the central portion 121. An engaging portion 124 is formed at a distal end portion of the first switching arm portion 122, and the engaging portion 124 is provided to protrude inward in the radial direction and detachably engages with the switching tooth portion 102 of the upper switching pawl wheel 101.
The engagement portion 124 is engaged with the engagement surface 102a of the switching tooth 102 so as to be able to disengage from the counterclockwise direction in a state of being in contact with the inclined surface 102b of the switching tooth 102. Thus, the engagement portion 124 engages with the switching tooth portion 102 adjacent to each other in the circumferential direction from the outside in the radial direction.
The upper switching pawl 120 configured as described above is biased by the spring member 140 about the swing axis O9 such that the engaging portion 124 is pressed against the engaging surface 102a of the switching tooth 102.
The spring member 140 is formed separately from the upper switching pawl portion 120, and is combined with the upper surface side of the rotating plate 62 by the remaining two coupling pins 91 and 92 so as to be disposed in the gap between the rotating plate 62 and the upper switching gear 105.
The spring member 140 includes: a base portion 141 disposed on the opposite side in the radial direction from the upper switching pawl portion 120 across the axis O8; and a spring main body 142 formed to extend in the circumferential direction, a base end portion 142a being connected to the base portion 141, and a tip end portion 142b pressing the second switching arm portion 123 of the upper stage switching pawl portion 120 toward the outside in the radial direction.
The base portion 141 is formed in a substantially arc shape so as to extend in the circumferential direction, and both ends in the circumferential direction are fitted to the coupling pins 91 and 92, respectively. Thereby, the entire spring member 140 is integrally fixed to the rotating plate 62 by the two coupling pins 91 and 92.
The spring main body 142 is, for example, a plate spring extending in the circumferential direction, and as described above, the base end portion 142a is connected to the base portion 141. Further, in the present embodiment, the spring main body 142 is integrally formed with the base portion 141. The spring main body 142 is formed to extend counterclockwise in the circumferential direction so as to extend from the base end portion 142a to the outside of the base portion 141, and the tip end portion 142b thereof is in contact with the second switching arm portion 123 of the upper switching pawl portion 120 from the inside in the radial direction.
Thereby, the spring main body 142 presses the second switching arm portion 123 outward in the radial direction by its own elastic restoring force. Therefore, the upper switching pawl 120 is always biased, so that the engaging portion 124 is pressed toward the switching tooth 102.
Since the upper switching wheel 100 and the upper switching pawl 120 are configured as described above, the engagement portion 124 of the upper switching pawl 120 maintains the engagement state with respect to the engagement surface 102a when the upper switching wheel 100 rotates in the counterclockwise direction about the axis O8, and releases the engagement state with respect to the engagement surface 102a by the inclined surface 102b when the upper switching wheel 100 rotates in the clockwise direction about the axis O8. This point will be described in detail later.
Further, in the base portion 141 of the spring member 140, an abutting portion (a restricting member according to the present invention) 143 is formed, and the abutting portion 143 protrudes in the clockwise direction so as to be positioned radially outward of the distal end portion of the first switching arm portion 122 in the upper switching pawl portion 120.
When the engagement of the engagement portion 124 with respect to the engagement surface 102a is released, the contact portion 143 can restrict the swing of the upper switching pawl 120 about the swing axis O9. Specifically, when the engagement of the engagement portion 124 with respect to the engagement face 102a is released, the upper stage switching pawl portion 120 swings about the swing axis O9 against the urging force (biasing force) by the spring member 140, so that the first switching arm portion 122 moves toward the outside in the radial direction. At this time, when the upper-stage switching pawl portion 120 swings by a certain amount, the first switching arm portion 122 can be brought into contact with the contact portion 143. Therefore, the contact portion 143 can restrict the swing of the upper switching pawl 120, and prevent the upper switching pawl 120 from swinging excessively.
Next, the relationship between the lower switching wheel 110 and the lower switching claw 130 will be described. The lower switching wheel 110 and the lower switching claw 130 are configured similarly to the upper switching wheel 100 and the upper switching claw 120 described above, and have the same relative positional relationship.
However, in the present embodiment, the lower switching pawl 130 is disposed at a position shifted by 120 ° in the circumferential direction about the axis O8 with respect to the position of the upper switching pawl 120. Therefore, the lower switching claw portion 130 is combined with the coupling pin 91 instead of the coupling pin 90 to which the upper switching claw portion 120 is coupled. In addition, without being limited to this case, the lower switching claw portion 130 may be combined by the same coupling pin 90 so as to be disposed opposite to each other below the upper switching claw portion 120 with the rotating plate 62 therebetween.
As shown in fig. 4, 5, and 7, the lower switching wheel 110 includes: a lower switching claw wheel 111 rotatably combined with the lower seat cylinder 86 of the lower seat 85; and a lower switching gear 115 fixed to the lower switching pawl wheel 111.
The lower switching dog wheel 111 has a plurality of switching teeth 112 over the entire circumference, and has a lower coupling cylinder 113 projecting downward from the inner circumferential edge. The switching tooth portion 112 is a tooth portion having an engagement face 112a and an inclined face 112b, the engagement face 112a being directed in a counterclockwise direction which is one side of a circumferential direction about the axis O8, and the inclined face 112b being directed in a clockwise direction which is the other side of the circumferential direction.
The lower switching gear 115 is fixed to the lower coupling cylinder 113 by press fitting or the like. Thereby, the entire lower switching wheel 110 is combined via the lower seat 85 so as to be relatively rotatable with respect to the wheel shaft 65. In addition, the lower switching gear 115 has a lower switching tooth portion 115a that meshes with the third centering gear 43a in the third centering wheel 43. Therefore, the entire lower switching wheel 110 can rotate about the axis O8 with the rotation of the center third wheel 43, and can rotate in the opposite direction with respect to the rotation direction of the center third wheel 43 (i.e., rotate in the same direction as the rotation direction of the rotary hammer 30).
The lower switching claw portion 130 is placed on the upper surface side of the lower switching gear 115 so as to be disposed in the gap between the rotating plate 62 and the lower switching gear 115. The lower switching claw portion 130 is combined to be relatively rotatable with respect to the coupling pin 91 fixed to the rotating plate 62, and is swingable in the radial direction about the coupling pin 91. Therefore, the lower switching pawl portion 130 is integrally combined with the rotating plate 62 via the coupling pin 91 so as to be swingable about a swing axis O10 that is a central axis of the coupling pin 91.
The lower switching claw 130 includes: a first switching arm portion (switching arm portion according to the present invention) 132 formed to extend in a counterclockwise direction from a central portion 131 combined with the coupling pin 91; and a second switching arm 133 formed to extend clockwise from the central portion 131. An engaging portion 134 is formed at a distal end portion of the first switching arm portion 132, and the engaging portion 134 is provided to protrude radially inward and detachably engage with the switching tooth portion 112 of the lower switching pawl wheel 111.
The engagement portion 134 is engaged with the engagement surface 112a of the switching tooth portion 112 so as to be able to disengage from the counterclockwise direction in a state of being in contact with the inclined surface 112b of the switching tooth portion 112. Thereby, the engagement portion 134 is engaged from the outside in the radial direction to the switching tooth portions 112 adjacent to each other in the circumferential direction.
The lower switching pawl 130 configured as described above is biased about the swing axis O10 by the spring member 150 such that the engagement portion 134 is pressed against the engagement surface 112a of the switching tooth portion 112. The spring member 150 is formed separately from the lower switching pawl 130, and is combined with the upper surface side of the lower switching gear 115 by two coupling pins 90 and 92.
The spring member 150 includes a base 151 and a spring body 152. The base portion 151 is formed in a substantially arc shape so as to extend in the circumferential direction, and both ends in the circumferential direction are fitted into the coupling pins 90, 92, respectively. Thereby, the entire spring member 150 is integrally fixed to the rotating plate 62 by the two coupling pins 90, 92.
The spring main body 152 is, for example, a plate spring extending in the circumferential direction, and is formed to extend counterclockwise in the circumferential direction so as to go around from the base end portion 152a to the outside of the base portion 151, and the tip end portion 152b thereof is in contact with the second switching arm portion 133 of the lower switching pawl portion 130 from the inside in the radial direction.
Thereby, the spring main body 152 presses the second switching arm portion 133 outward in the radial direction by its own elastic restoring force. Thereby, the lower switching pawl 130 is constantly biased about the swing axis O10, so that the engagement portion 134 is pressed toward the switching tooth portion 112.
Since the lower switching wheel 110 and the lower switching pawl 130 are configured as described above, the engagement portion 134 of the lower switching pawl 130 maintains the engagement state with respect to the engagement surface 112a when the lower switching wheel 110 rotates in the counterclockwise direction about the axis O8, and releases the engagement state with respect to the engagement surface 112a by the inclined surface 112b when the lower switching wheel 110 rotates in the clockwise direction about the axis O8.
Further, an abutting portion (a restricting member according to the present invention) 153 is formed in the base portion 151 of the spring member 150, and the abutting portion 153 protrudes in the clockwise direction so as to be positioned radially outward of the distal end portion of the first switching arm portion 132 in the lower switching pawl portion 130.
(action of automatic winding mechanism)
Next, the operation of the automatic winding mechanism 11 including the switching transmission wheel 60 configured as described above will be described. As shown in fig. 2, the rotary hammer 30 is appropriately rotated in two directions around the axis O2 in accordance with, for example, the movement of the wrist of the user. The rotary hammer 30 rotates so that its power (rotational torque) is transmitted to the switching transmission wheel 60 via the first centering wheel 41, the second centering wheel 42, and the third centering wheel 43, thus enabling the upper stage switching wheel 100 and the lower stage switching wheel 110 to rotate in opposite directions to each other about the axis O8.
Specifically, the description is given. In the case where the rotary hammer 30 shown in fig. 2 rotates in the clockwise direction, the first centering wheel 41 can be rotated in the counterclockwise direction, the second centering wheel 42 can be rotated in the clockwise direction, and the third centering wheel 43 can be rotated in the counterclockwise direction. Therefore, the upper stage switching wheel 100 meshing with the second centering pinion 42b can be rotated in the counterclockwise direction, and the lower stage switching wheel 110 meshing with the third centering pinion 43a can be rotated in the clockwise direction. Therefore, the upper stage switching wheel 100 and the lower stage switching wheel 110 can be rotated in opposite directions to each other. Further, even in the case where the rotary weight 30 is rotated in the counterclockwise direction, only the rotational directions of the above-described wheels become opposite, and thus, as a result, the upper stage switching wheel 100 and the lower stage switching wheel 110 can be rotated in the opposite direction to each other.
For example, when the rotary hammer 30 rotates in the clockwise direction and the upper stage switching wheel 100 rotates in the counterclockwise direction, as shown in fig. 6, the upper stage switching dog wheel 101 having the switching teeth 102 rotates in the counterclockwise direction along with this. At this time, since the engaging portion 124 of the upper switching pawl 120 is engaged with the engaging surface 102a of the switching tooth 102 from the counterclockwise direction, the engaged state between the engaging surface 102a and the engaging portion 124 can be maintained. Therefore, as indicated by an arrow F1 shown in fig. 6, the rotational torque of the upper switching wheel 100 can be transmitted to the upper switching pawl portion 120, and the upper switching pawl portion 120 can be rotated so as to be pulled in the counterclockwise direction.
Then, since the upper switching claw portion 120 rotates and the rotating plate 62 rotates, as a result, as shown in fig. 2, the wheel shaft 65 can be rotated in the counterclockwise direction. Therefore, the power transmitted to the upper switching wheel 100 can be transmitted to the gear train 50 side via the switching pinion gear 73, and can be transmitted to the large steel wheel 20 via the gear train 50, winding up the power spring. That is, the wheel shaft 65 and the switching transmission pinion 73 rotate in the counterclockwise direction, so that the first transmission wheel 51 can be rotated in the clockwise direction and the second transmission wheel 52 can be rotated in the counterclockwise direction. Therefore, the large steel wheel 20 can be rotated clockwise, and the mainspring can be wound up.
However, as the rotating plate 62 rotates counterclockwise, the lower switching pawl portion 130 also rotates counterclockwise as shown in fig. 7. In addition to this, the rotary weight 30 rotates in the clockwise direction, and thus rotates in the clockwise direction with respect to the lower stage switching wheel 110 as described above. In conjunction with this, the lower switching wheel 110 rotates in the clockwise direction with respect to the lower switching pawl 130 rotating in the counterclockwise direction. In this case, the engagement surface 112a of the switching tooth portion 112 of the lower switching gear 115 and the engagement portion 134 of the lower switching pawl portion 130 are not engaged with each other, and thus the lower switching wheel 110 is in an idling state. Therefore, the wheel shaft 65 and the switching transmission pinion 73 are not rotated by the rotation of the lower switching wheel 110.
Described in detail. In the case where the lower switching wheel 110 is rotated in the clockwise direction with respect to the lower switching pawl 130 that is rotated in the counterclockwise direction, the inclined surface 112b in the switching tooth portion 112 pushes the engagement portion 134 of the lower switching pawl 130 outward in the radial direction while moving beyond the engagement portion 134 in the circumferential direction as indicated by an arrow F2 shown in fig. 7. Thereby, the lower switching pawl 130 swings about the swing axis O10 while resisting the biasing force (urging force) by the spring member 150. Thereby, the engagement of the engagement portion 134 with respect to the engagement surface 112a is released. As a result, the lower stage switching wheel 110 can be idly rotated in the counterclockwise direction.
As described above, when the upper switching wheel 100 is rotated counterclockwise by the rotation of the rotary hammer 30, the entire rotating plate 62, the wheel shaft 65, and the switching transmission pinion 73 can be rotated counterclockwise while the engagement surface 102a of the switching tooth portion 102 is engaged with the engagement portion 124 of the upper switching pawl portion 120, and the power can be transmitted to the transmission train 50. In addition, at the same time, even if the lower switching wheel 110 rotates in the clockwise direction, the lower switching wheel 110 can be idly rotated in the clockwise direction, and thus power can be prevented from being transmitted from the lower switching wheel 110 to the gear train 50.
Therefore, even if the upper stage switching wheel 100 and the lower stage switching wheel 110 rotate in opposite directions to each other, power can be transmitted so that the power train 50 always rotates in one direction. Therefore, as shown in fig. 2, the large steel wheel 20 can be rotated clockwise to wind up the mainspring.
Next, a case where the rotary hammer 30 shown in fig. 2 is rotated in the counterclockwise direction will be described. In this case, contrary to the above case, the upper stage switching wheel 100 rotates in the clockwise direction and the lower stage switching wheel 110 rotates in the counterclockwise direction along with the rotation of the rotary weight 30. Therefore, since the movement is reversed from the above, the entire rotating plate 62, the wheel shaft 65, and the switching transmission pinion 73 can be rotated counterclockwise while maintaining the state in which the engagement surface 112a of the switching tooth portion 112 of the lower switching wheel 110 is engaged with the engagement portion 134 of the lower switching pawl portion 130, and the power can be transmitted to the transmission train 50. In addition, at the same time, the upper stage switching wheel 100 can be idled in the clockwise direction, and thus power transmission from the upper stage switching wheel 100 to the power train 50 can be prevented. Therefore, in this case as well, power can be transmitted so that the gear train 50 always rotates in one direction, and therefore the large steel wheel 20 can be rotated in the clockwise direction to wind up the spring.
In view of the above, the wheel shaft 65 having the switching transmission pinion 73 can be always rotated in the counterclockwise direction, which is the same direction, by the power of the rotary hammer 30 rotating in both directions, and thus the large steel wheel 20 can be rotated in the clockwise direction to perform the automatic winding of the mainspring.
In particular, according to the switching transmission wheel 60 of the present embodiment, as shown in fig. 6 and 7, the upper switching pawl 120 and the lower switching pawl 130 have the first switching arm portions 122 and 132 formed to extend counterclockwise from the swing axes O9 and O10, and have the engagement portions 124 and 134 formed at the tip end portions thereof.
Therefore, for example, when the upper switching pawl 120 is described as an example, as shown in fig. 6, when the upper switching wheel 100 is rotated in the counterclockwise direction, the first switching pawl 63 can be rotated so as to pull the first switching arm portion 122. Therefore, unlike the conventional art, the switching claw portion can function as a so-called claw-type switching claw portion in which a tensile force acts on the first switching arm portion 122.
In this case, even if the arm length H of the first switching arm portion 122 is formed long, unlike the pusher-claw type of the related art, the engagement state between the engagement surface 102a and the engagement portion 124 can be easily maintained, and a state in which the engagement is hard to come off can be secured. Therefore, the arm length H of the first switching arm portion 122 can be made longer than in the related art, and the load on the upper switching wheel 100 when the engaging surface 102a pushes the first switching claw portion 63 open against the biasing force of the spring member 140 can be reduced accordingly. Therefore, the rotational load when the upper switching wheel 100 and the lower switching wheel 110 idle can be reduced, and the windup performance can be improved.
As described above, according to the automatic winding mechanism 11 including the switching transmission wheel 60 of the present embodiment, the movement 10 including the automatic winding mechanism 11, and the timepiece 1, the rotational load can be reduced, and the winding performance can be improved.
As shown in fig. 6 and 7, the switching power transmission wheel 60 of the present embodiment includes contact portions 143 and 153 for restricting the swing of the upper switching pawl 120 and the lower switching pawl 130. Therefore, when the upper switching wheel 100 and the lower switching wheel 110 idle, the contact portions 143 and 153 can restrict the swing of the upper switching claw 120 and the lower switching claw 130, and excessive swing can be prevented. This can prevent, for example, the spring main bodies 142, 152 of the spring members 140, 150 from being greatly deformed and plastically deformed. Therefore, the switching transmission wheel 60 can be operated stably for a long period of time, and the operational reliability can be improved.
In particular, in the case of a drop impact, a manual winding operation by hand using the stem 13, or the like, it is assumed that the upper switching claw 120 and the lower switching claw 130 excessively swing. In particular, in the case where the large steel wheel 20 is rotated in the clockwise direction by the manual winding operation, the axle 65 of the switching transmission wheel 60 is forcibly rotated in the counterclockwise direction via the transmission train 50. In this case, since the rotary hammer 30 is in a stopped state, the upper-stage switching pawl 120 and the lower-stage switching pawl 130 are rotated in the counterclockwise direction with respect to the stopped upper-stage switching wheel 100 and lower-stage switching wheel 110, and the upper-stage switching pawl 120 and the lower-stage switching pawl 130 are easily shifted by the switching tooth portions 102, 112 while largely swinging. Therefore, the spring main bodies 142, 152 tend to be plastically deformed easily. Even in such a case, the spring main bodies 142, 152 can be effectively prevented from being largely deformed by the abutting portions 143, 153.
Further, since the spring members 140 and 150 are formed separately from the upper switching claw 120 and the lower switching claw 130, the spring members 140 and 150 can be designed separately, and for example, a material, a plating layer, or the like different from those of the upper switching claw 120 and the lower switching claw 130 can be selected.
(second embodiment)
Next, a second embodiment according to the present invention will be described with reference to the drawings. In the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
In the first embodiment, the spring main bodies 142, 152 are configured to press the engagement portions 124, 134 toward the switching tooth portions 102, 112 by biasing the second switching arm portions 123, 133 of the upper-stage switching pawl portion 120 and the lower-stage switching pawl portion 130 outward in the radial direction, but in the second embodiment, the spring main bodies are configured to bias the first switching arm portions 122, 132 of the upper-stage switching pawl portion 120 and the lower-stage switching pawl portion 130 inward in the radial direction.
In the present embodiment, the upper switching claw portion 120 is exemplified. As shown in fig. 8, the switching transmission wheel 160 of the present embodiment includes a spring member 161, and the spring member 161 has a spring body 162 extending in a clockwise direction from a base end portion 162a connected to the base 141.
The spring main body 162 extends clockwise from the base end portion 162a toward the tip end portion 162b so as to wind the base portion 141 and the first switching arm portion 122 of the upper switching pawl portion 120 from the outside. Also, the tip end portion 162b of the spring main body 162 biases the first switching arm portion 122 from the outside toward the inside in the radial direction. Thereby, the engagement portion 124 formed at the tip end of the first switching arm portion 122 is pressed toward the switching tooth portion 102.
In addition, the abutting portion 143 is formed to protrude from the base portion 141 in the counterclockwise direction so as to be located more inward in the radial direction than the tip end portion of the second switching arm portion 123 in the upper stage switching pawl portion 120.
Even the switching transmission wheel 160 of the present embodiment configured as described above can provide the same operational advantages as those of the first embodiment.
(third embodiment)
Next, a third embodiment according to the present invention will be described with reference to the drawings. In the third embodiment, the same components as those in the second embodiment are denoted by the same reference numerals, and the description thereof is omitted. In the second embodiment, one upper switching claw portion 120 and one lower switching claw portion 130 are provided, but in the present embodiment, a plurality of upper switching claw portions 120 and a plurality of lower switching claw portions 130 are provided.
In the present embodiment, the upper switching claw portion 120 is exemplified. As shown in fig. 9, the switching transmission wheel 170 of the present embodiment includes two upper switching claws 120. The number of the upper switching claws 120 is not limited to two, and may be, for example, three or more.
The upper switching pawl portions 120 are symmetrically arranged so as to oppose each other in the radial direction with the axis O8 therebetween. Therefore, the two upper switching claw portions 120 are combined with the rotating plate 62 via the coupling pins 90, respectively.
Further, a leaf spring-like spring member 171 is integrally formed with the upper-stage switching pawl portion 120. The spring member 171 is formed in a substantially circular arc shape extending in the circumferential direction, and a base end portion 171a is connected to the second switching arm portion 123. Further, the spring member 171 is formed so as to wind the outer side of the second switching arm portion 123 while extending more clockwise than the second switching arm portion 123 and disposed more outward in the radial direction than the first switching arm portion 122 in another upper stage switching claw portion 120 adjacent in the circumferential direction.
Also, the tip end portion 171b of the spring member 171 biases the first switching arm portion 122 in the other upper stage switching pawl portion 120 adjacent in the circumferential direction from the outside toward the inside in the radial direction. Thereby, the engagement portions 124 formed at the tip ends of the first switching arm portions 122 are pressed toward the switching tooth portions 102, respectively.
Further, the tip end of the second switching arm portion 123 in the upper stage switching pawl portion 120 functions as an abutment portion (a restricting member according to the present invention) 173 located on the radially outer side with respect to the first switching arm portion 122 in the other upper stage switching pawl portion 120 adjacent in the circumferential direction.
The switching transmission wheel 170 of the present embodiment configured as described above can also provide the same operational advantages as those of the first embodiment.
In addition, in the present embodiment, the number of teeth of the switching teeth 102 is set to an odd number. Therefore, when the engagement portion 124 of one upper switching pawl 120 engages with the engagement surface 102a of the switching tooth 102, the engagement of the engagement portion 124 of the other upper switching pawl 120 with the engagement surface 102a of the switching tooth 102 is released.
Thus, while the engagement portion 124 of one upper switching pawl 120 is disengaged from the engagement surface 102a of the switching tooth 102 and engaged with the engagement surface 102a of the adjacent switching tooth 102, the engagement portion 124 of the other upper switching pawl 120 can be engaged with the engagement surface 102a of the switching tooth 102. As a result, the so-called non-operating angle can be reduced. That is, the rotation angle of the rotary weight 30 required from the start of the reverse rotation of the rotary weight 30 to the restart of the counterclockwise rotation of the hub 65 is reduced, and the large steel wheel 20 can be rotated more efficiently to wind up the power spring.
In the third embodiment, the following configuration is exemplified: the two upper switching pawl portions 120 are symmetrically arranged so as to oppose each other in the radial direction across the axis O8, and the number of teeth of the switching tooth portion 102 is odd, so that when the engagement portion 124 of one upper switching pawl portion 120 engages with the engagement surface 102a of the switching tooth portion 102, the engagement portion 124 of the other upper switching pawl portion 120 does not engage with the engagement surface 102a of the switching tooth portion 102. However, this is not a limitation. For example, the two upper switching pawl portions 120 may be arranged at an angle that is shifted from a position point-symmetrical about the axis O8 by half of one tooth of the switching tooth portion 102 in the circumferential direction, and the number of teeth of the switching tooth portion 102 may be even. In this case, the so-called non-operating angle can be reduced as in the above case, and the same operational effects as described above can be obtained.
(fourth embodiment)
Next, a fourth embodiment according to the present invention will be described with reference to the drawings. In the fourth embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
In the first embodiment, the spring members 140 and 150 are provided separately from the upper switching claw portion 120 and the lower switching claw portion 130, but in the present embodiment, the spring members are formed integrally with the upper switching claw portion 120 and the lower switching claw portion 130.
In the present embodiment, the upper switching claw portion 120 is exemplified. As shown in fig. 10, the switching transmission wheel 180 of the present embodiment includes an upper switching pawl portion 120 integrally formed with a plate spring-like spring member 181. The upper switching claw portion 120 is a structure in which a spring member 181 is integrally formed in place of the second switching arm portion 123 in the first embodiment, and is swingably combined with respect to the coupling pin 190 fixed to the rotating plate 62.
The coupling pin 190 is formed in a planar elliptical shape having a pair of flat cut surfaces 191 opposed to each other and a pair of circular arc surfaces 192 opposed to each other. On the other hand, a coupling hole 195 through which the coupling pin 190 is inserted is formed in the central portion 121 of the upper stage switching pawl 120. The coupling hole 195 is formed in an elliptical shape in plan view having a pair of linear portions 196 opposed to each other and a pair of circular arc portions 197 opposed to each other, corresponding to the shape of the coupling pin 190.
Thereby, the upper switching pawl 120 can swing within an angular range in which the connecting portion P1 of the straight line portion 196 and the circular arc portion 197 contacts the connecting portion P2 of the tangential surface 191 and the circular arc surface 192, centering on the swing axis O9 as the center axis of the coupling pin 190.
The spring member 181 is formed such that a base end portion 181a is connected to the central portion 121 of the upper stage switching pawl portion 120 and extends clockwise from the base end portion 181a toward a tip end portion 181 b. Further, the tip portion 181b of the spring member 181 is fitted to the coupling pin 200 fixed to the rotating plate 62. Thereby, the spring member 181 biases the upper switching pawl 120 by its own elastic restoring force, and presses the engagement portion 124 of the upper switching pawl 120 against the switching tooth portion 102.
Even the switching transmission wheel 180 of the present embodiment configured as described above can provide the same operational advantages as those of the first embodiment. In addition, in the case of the present embodiment, since the upper stage switching claw portion 120 and the spring member 181 are integrally formed, the number of parts can be reduced, and weight reduction, cost reduction, improvement in assemblability, and the like of the switching transmission wheel 180 can be achieved.
The embodiments of the present invention have been described above, but these embodiments are provided as examples and are not intended to limit the scope of the invention. The embodiments may be implemented in various other ways, and various omissions, substitutions, and changes may be made without departing from the spirit of the invention. Examples, substantially the same examples, examples of equivalent ranges, and the like, which can be easily conceived by those skilled in the art, are included in the embodiments or the modifications thereof.
For example, in the above embodiments, the case where the switching transmission wheel is used in the automatic winding mechanism has been described as an example, but the present invention is not limited to the automatic winding mechanism and may be applied to other timepiece mechanisms. In particular, in each of the above embodiments, in order to be adopted in the automatic winding mechanism, the switching transmission wheel is provided with the upper switching wheel, the lower switching wheel, the upper switching claw, and the lower switching claw by providing a pair of switching wheels and switching claws, respectively.
Description of the symbols
O2 … … Axis (third Axis)
O8 … … Axis (first Axis)
O9, O10 … … swing axis (second axis)
1 … … clock
10 … … movement (movement for clock)
11 … … automatic winding mechanism
20 … … large steel wheel
30 … … rotary hammer (Power source)
60. 160, 170, 180 … … switching transmission wheel
61 … … switching wheel
65 … … axle (rotating shaft)
62 … … rotating plate
63 … … switching claw part
73 … … switching drive pinions
100 … … Upper switching wheel (first switching wheel)
102. 112 … … switching teeth
102a, 112a … … engagement surface
102b, 112b … … inclined surface
110 … … lower switching wheel (second switching wheel)
120 … … Upper stage switching claw part (first switching claw part)
122. 132 … … first switching arm (switching arm)
124. 134 … … snap-fit part
130 … … lower switching claw part (second switching claw part)
140. 150, 161, 171, 181 … … spring element
143. 153, 173 … … abutment (restricting means).

Claims (8)

1. A switching transmission wheel is characterized by comprising:
a rotation shaft portion rotatably disposed around a first axis and having a switching transmission pinion gear for transmitting power to a transmitted gear train;
a switching wheel which is combined to be relatively rotatable with respect to the rotation shaft portion and rotates around the first axis by power transmitted from a power source;
a rotating plate integrally combined with the rotating shaft; and
a switching claw portion which is combined to the rotating plate in an integral manner around a second axis in a swinging manner,
the switching wheel includes a plurality of switching teeth having an engaging surface facing one side in a circumferential direction around the first axis and an inclined surface facing the other side in the circumferential direction,
the switching claw portion includes:
a switching arm portion formed to extend from the second axis toward one side in the circumferential direction; and
an engaging portion formed at a distal end portion of the switching arm portion and engaging with the engaging surface so as to be detachable from one side in the circumferential direction,
the switching claw portion is biased by a spring member so that the engaging portion is pressed against the engaging surface.
2. The switching transmission wheel according to claim 1, wherein the engagement portion maintains an engagement state with respect to the engagement surface when the switching wheel rotates about the first axis toward one side in the circumferential direction, and releases the engagement with respect to the engagement surface by the inclined surface when the switching wheel rotates about the first axis toward the other side in the circumferential direction.
3. The switching transmission wheel according to claim 1 or 2, wherein a regulating member is provided on the rotation plate, and the regulating member regulates the swing of the switching claw portion about the second axis when the engagement of the engagement portion with respect to the engagement surface is released.
4. The switching transmission wheel according to any one of claims 1 to 3, wherein the spring member is formed separately from the switching claw portion, combined with respect to the rotation plate.
5. The switching transmission wheel according to any one of claims 1 to 3, wherein the spring member is formed integrally with the switching claw portion, combined with respect to the rotation plate.
6. An automatic winding mechanism is characterized by comprising:
a switching transmission wheel according to any one of claims 1 to 5;
a rotary hammer that can rotate in two directions about a third axis and functions as the power source; and
the transmitted gear train connects the switching transmission pinion with a big steel wheel for winding up the spring,
a pair of the switching wheels and the switching claw portions are provided so as to be disposed on both sides of the rotating plate in the first axial direction,
a switching wheel located on the switching transmission pinion side of the pair of switching wheels than the rotating plate is a first switching wheel that rotates in association with rotation of the rotary hammer,
the remaining switching wheel of the pair of switching wheels is a second switching wheel that rotates in the opposite direction to the first switching wheel as the rotary hammer rotates,
a switching pawl portion of the pair of switching pawl portions located on the switching transmission pinion side than the rotating plate is a first switching pawl portion that operates in association with the first switching wheel,
the remaining switching claw portion of the pair of switching claw portions is a second switching claw portion that operates in association with the second switching wheel.
7. A timepiece movement including the automatic winding mechanism according to claim 6.
8. A timepiece provided with the timepiece movement according to claim 7.
CN202010952195.5A 2019-09-12 2020-09-11 Switching drive wheel, automatic winding mechanism, movement for timepiece and timepiece Active CN112486004B (en)

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JP2019166503A JP7260446B2 (en) 2019-09-12 2019-09-12 Transmission wheel, self-winding mechanism, watch movement and watch
JP2019-166503 2019-09-12

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CH719254A1 (en) * 2021-12-15 2023-06-30 Richemont Int Sa Planetary gear rectifier and automatic winding for clocks.

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CN112486004B (en) 2024-02-23
JP2021043110A (en) 2021-03-18
CH716597A2 (en) 2021-03-15
JP7260446B2 (en) 2023-04-18
CH716597B1 (en) 2023-12-29

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