JP6144821B2 - Periodic power intermittent clutch - Google Patents

Description

  The present invention relates to a periodic power interrupting clutch, and more particularly, to a variety of industrial fields that repeatedly operate at an accurate cycle by transmitting a driving force at a constant speed accurately at a constant cycle. This can be easily applied to various driving means, improve driving reliability, and can be used for various purposes in one facility by appropriate adjustment of driving speed, thus providing a more economical saving effect The present invention relates to a power intermittent clutch.

  In general, a power transmission device applied in various industrial fields reduces a driving force to a constant speed so that the reduced driving force is transmitted to a driving unit.

  The driving force output via the driving means is subjected to various speed reductions or speed changes by being combined with reduction gears having various gear ratios.

  However, since the driving force cannot be directly decelerated or shifted, the transmission of the driving force is intermittently performed using a clutch that is a normal shaft connecting device.

  The clutch is currently implemented in various systems such as a mechanical type, a hydraulic type, and an electronic type. However, since there is a difference in accuracy and manufacturing cost depending on the application method, the application method is determined mainly by the application product.

  On the other hand, in the clutch operation system, there is a case where power transmission is performed at a constant period. However, if this is performed electronically, there is a difficulty that the manufacturing cost becomes excessively high.

  In particular, in the case of an engine in which the power source is not a motor, electronic control is difficult, and this is mainly performed by complicated gear coupling.

  One example of applying a drive system that periodically interrupts power transmission in this manner is an agricultural machine seedling planting machine.

  Since the seedling planting machine is planted at regular intervals along the planting surface, the seedling planting machine is driven by a periodic power transmission method. As a conventional technique of such a seedling planting machine, Japanese Patent Registration No. 0433335 (2004) On May 18th, there is a name: Fertilizer transplanter.

  In the prior art, the stock interval adjusting device is implemented by a shift by complicated coupling between gears, and a planting clutch that conducts / cuts off electric power as power for planting by an external operation is installed.

  However, the conventional seedling planting machine has to adjust the stock interval manually, which has the disadvantage of inconvenience for the user, causing shocks during driving and shifting, and excessive maintenance and repair costs as well as breakage of parts. There are uneconomic issues that are needed.

Korean Patent Registration No. 0433335 (May 18, 2004)

  In order to solve the above-mentioned problems, the first object of the present invention is to improve the reliability of the work by accurately transmitting the power of a constant rotational speed transmitted at a constant time in a desired cycle. It is to provide a periodic power intermittent clutch.

  A second object of the present invention is to provide a periodic power interrupting clutch that can be easily applied to various facilities that perform repetitive work and can be used in various ways at a relatively low cost.

  In order to achieve the above object, the periodic power intermittent clutch of the present invention includes a clutch shaft that is rotatably supported by a shaft, one side fixed to a housing, the clutch shaft passing through the center, and ring-shaped on both sides. The cross section includes a fixed clutch that forms first and second clutch portions with a constant radius, and a fixed clutch that is elastically rotated in a corresponding direction while rotating by a standby driving force transmitted by a gear connection on the outer peripheral surface. At the moment when the first moving clutch that slides back and forth in a constant width axial direction by one spring, the second clutch portion of the fixed clutch, and the third clutch portion of the first moving clutch are engaged, the first moving clutch and the first moving clutch A second moving clutch that reciprocates by a fixed width in the axial direction in the hollow tube of the first moving clutch by two springs; and the second moving clutch. A third moving clutch coupled to the clutch shaft and spline coupled to the clutch shaft so that power transmission to the clutch shaft is interrupted while sliding with a constant width together with the second moving clutch; The third moving clutch and the ratchet gear are combined with a driving clutch gear that rotates the clutch shaft via the third moving clutch by the operating driving force transmitted via the outer peripheral gear connection.

  Both sides of the clutch shaft are axially supported by bearings, and a spline is formed on one peripheral surface so as to be splined with the third moving clutch.

  The first and second clutch portions of the fixed clutch have protrusions with a small angle and protrusions with a large angle on the corresponding peripheral surfaces of the same radius on the plate surfaces on both sides, respectively. The bottom surface or a certain height of the bottom surface is inclined at a certain angle.

  The first moving clutch is axially supported on one side of the fixed clutch so as to be slidable by a fixed width in the axial direction along the clutch shaft, and is rotated by a standby driving force via a gear coupling on the outer peripheral surface. The third clutch portion is formed on one side surface facing the fixed clutch so as to be clutched with the first clutch portion of the fixed clutch, and the inner peripheral edge portion penetrates the inside of the second moving clutch. A tubular hollow tube that is bush-coupled with the clutch shaft is formed, and a retaining ring is coupled to an end portion of the hollow tube together with a thrust bearing to prevent the thrust bearing from being detached. .

  The third clutch portion of the first moving clutch forms a protrusion with a shape corresponding to the small protrusion and the large protrusion of the first clutch portion of the fixed clutch.

  The second moving clutch is provided on an outer peripheral surface of a hollow tube that is extended from a side surface of the first moving clutch to a certain length so as to be axially movable and rotatable, and has one end at the first moving clutch. A spring guide is formed on one side, in which contact with the inner peripheral side plate surface of the hollow tube of the moving clutch is interrupted, and a second spring is elastically provided to move toward the first moving clutch. And a shape corresponding to the small protrusion and the large protrusion of the second clutch portion on the opposite surface of the fixed clutch at the other end portion corresponding to the one end portion contacting the first moving clutch of the spring guide. The fourth clutch portion for forming the protrusion is provided.

  The third moving clutch is fastened to the second moving clutch with an inter-surface bolt so as to form a first ratchet gear on the side opposite to the fastening surface, and an inner peripheral surface is splined to the clutch shaft. .

  The drive clutch gear is gear-coupled to an outer peripheral surface so that an operating driving force is transmitted, and a first ratchet gear formed on the third movement clutch is gear-coupled to an opposite surface of the third movement clutch. Two ratchet gears are formed.

  According to the periodic power intermittent clutch of the present invention, the operating driving force transmitted through the drive clutch gear while the first clutch rotates once in the state where the clutch shaft rotates once through the third moving clutch. The driving unit waits for a certain period of time while one clutch completes one rotation, and then is driven.

  There is an effect that the operation by the drive unit is accurately performed while accurately repeating such operation and standby, and the operation reliability is greatly improved.

  In addition, the present invention has an advantage that it can be effectively applied in various fields by appropriately adjusting the operation driving force and the standby driving force.

1 is an exploded perspective view illustrating an embodiment of a periodic power interrupting clutch according to the present invention. 1 is a perspective view illustrating a fixed clutch according to the present invention. 1 is a perspective view illustrating a coupling configuration of a first moving clutch according to the present invention. FIG. 6 is an exploded perspective view illustrating an assembly configuration of a second moving clutch and a third moving clutch according to the present invention. FIG. 3 is a coupling cross-sectional view illustrating a coupling structure of a first moving clutch and a second moving clutch in a periodic power intermittent clutch according to the present invention. It is the perspective view which illustrated the drive clutch gear concerning the present invention. FIG. 3 is a cross-sectional view of a periodic power interrupting clutch according to the present invention. FIG. 4 is an enlarged cross-sectional view of a main part illustrating an operating state before the first moving clutch of the periodic power interrupting clutch according to the present invention contacts the second moving clutch. FIG. 3 is an enlarged cross-sectional view of a main part illustrating an operating state at a time when a first moving clutch of a periodic power interrupting clutch according to the present invention contacts a second moving clutch. FIG. 6 is an enlarged cross-sectional view of a main part illustrating a state in which the second moving clutch of the periodic power interrupting clutch according to the present invention is rotated and the coupling with the fixed clutch is released.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

  FIG. 1 is an exploded perspective view illustrating an embodiment of a periodic power interrupting clutch according to the present invention. The present invention largely includes a clutch shaft 10, a fixed clutch 20, a first moving clutch 30, and a second moving clutch. 40, the third moving clutch 50 and the drive clutch gear 60 are combined.

  This will be described in more detail. The clutch shaft 10 of the present invention has a structure in which both sides are axially supported by the clutch housing 70 by bearings 11 and are rotatably provided. In this configuration, the spline 12 is formed in the portion by a certain length.

  On the other hand, since the clutch shaft 10 is configured to transmit the driving force of driving means (not shown), the driving force may be output through one end of the clutch shaft 10 away from the clutch housing 70. However, it may be output also in the clutch housing 70 by bevel gear coupling.

  The fixed clutch 20 provided in the middle of the clutch shaft 10 is connected to a ring-shaped configuration having a constant thickness and width so that a part of the outer peripheral surface extends outward and is fixed to the clutch housing 70. In the center of the body, the clutch shaft 10 is provided so as to penetrate therethrough.

  Accordingly, in the configuration of the present invention, the fixed clutch 20 is fixed to the clutch housing 70 together with the clutch shaft 10 rotatably connected by the bearing 11.

  FIG. 2 is a perspective view illustrating a fixed clutch according to the present invention.

  As shown in the figure, a first clutch portion 21 and a second clutch portion 22 are formed on both sides of the ring-shaped body of the fixed clutch 20, respectively. The first clutch portion 21 and the second clutch portion 22 are circular bodies. A pair of protrusions (abbreviated as projecting parts, P) that protrude by a certain width and thickness on the peripheral surfaces corresponding to each other are configured, and the pair of protrusions (P) are formed in different sizes.

  That is, the projections (P) provided as a pair are formed so that one of the formation angles from the center of the body is small (abbreviated as Small P, SP) and the other is large (abbreviated as Large P, LP). More preferably, the end of each protrusion (P) is formed so that at least the end in the rotational direction is gently inclined from the bottom surface or from a certain height of the bottom surface.

  The first clutch portion 21 and the second clutch portion 22 formed on both side surfaces of the fixed clutch 20 may be formed in the same shape, or may be formed by protrusions (P) having different sizes and angles.

  The fixed clutch 20 includes a first moving clutch 30 on the first clutch portion 21 side, and a second moving clutch 40 on the second clutch portion 22 side.

  FIG. 3 is a diagram illustrating the coupling structure of the first moving clutch according to the present invention. As illustrated, the first moving clutch 30 is always elastically supported by the first spring 32 in the opposite direction to the fixed clutch 20. The first moving clutch 30 is brought into surface contact with the fixed clutch 20.

  The first moving clutch 30 has a gear shape in which a standby driving force is transmitted by gear coupling on the outer peripheral surface and rotates at a constant speed. The surface of the first moving clutch 30 facing the fixed clutch 20 is on the surface of the fixed clutch 20. A third clutch part 31 having a shape corresponding to the protrusion (P) formed on the first clutch part 21 and a pair of protrusions (SP, LP) formed on the same radius is formed.

  When the third clutch portion 31 of the first moving clutch 30 is formed in a shape corresponding to the first clutch portion 21, the first moving clutch 30 is in a state where the third clutch portion 31 is fitted to the first clutch portion 21. It is time to make one revolution.

  A hollow tube 33 having a diameter larger than the clutch shaft 10 from one side and smaller than the inner diameter of the fixed clutch 20 is integrally formed in the first moving clutch 30 to a certain length through the fixed clutch 20. A thrust bearing 34 and a retainer ring 35 for preventing the thrust bearing 34 from being detached are fixed on the distal end side of the hollow tube 33.

  On the other hand, in order for the first moving clutch 30 to be rotatably coupled to the clutch shaft 10, it is more preferable that the bush 36 is interposed between the first moving clutch 30 and the clutch shaft 10 so as to be coupled with the bush.

  The second moving clutch 40 provided on the opposite side of the first moving clutch 30 around the fixed clutch 20 is coupled to the tip of the first moving clutch 30 so as to cover the outside of the hollow tube 33 of the first moving clutch 30. The thrust bearing 34 has a larger inner diameter.

  FIG. 4 is an exploded perspective view illustrating the assembly structure of the second moving clutch and the third moving clutch according to the present invention. As illustrated, the second moving clutch 40 has a second side of the fixed clutch 20 on one side. A fourth clutch part 41 is formed in which a pair of protrusions (SP, LP) having the same radius and shape corresponding to the protrusions (SP, LP) formed on the clutch part 22 are formed.

  When the fourth clutch part 41 is formed in a shape corresponding to the second clutch part 22, the time when the fourth clutch part 41 is coupled to the second clutch part 22 is the moment when the second moving clutch 40 rotates 360 °. It becomes.

  That is, every time the second moving clutch 40 makes one rotation, the second clutch portion 22 of the fixed clutch 20 and the fourth clutch portion 41 of the second moving clutch 40 are engaged with each other.

  From one side surface forming the fourth clutch part 41 of the second moving clutch 40, a cylindrical shape having a fixed length so that it can contact one side surface of the first moving clutch 30 with a radius smaller than the forming radius of the fourth clutch part 41. While the spring guide 42 is formed, a through hole 420 is formed at the tip of the spring guide 42 with a size approximate to the outer diameter of the hollow tube 33 of the first moving clutch 30.

  In order for the second moving clutch 40 to be coupled to the hollow tube 33 of the first moving clutch 30, before the thrust bearing 34 and the retaining ring 35 are coupled to the tip of the hollow tube 33 as shown in FIG. In a state where the spring guide 42 of the second moving clutch 40 is sandwiched, the second spring 43, the thrust bearing 34, and the retaining ring 35 are sequentially inserted and coupled through the hollow tube 33.

  When the second moving clutch 40 is thus coupled, the tip of the spring guide 42 of the second moving clutch 40 is always elastic toward the first moving clutch 30 by the second spring 43.

  However, the second moving clutch 40 is movable to a position where the fourth clutch portion 41 is fitted with the second clutch portion 22 of the fixed clutch 20.

  The third moving clutch 50 is bolted to the opposite side of the one side forming the fourth clutch portion 41 of the second moving clutch 40 as shown.

  The third movement clutch 50 is configured such that one side surface is integrally coupled to the second movement clutch 40 by bolt fastening while being in close contact with each other, and a first ratchet gear 51 is formed along the peripheral edge on the other side surface.

  However, the third moving clutch 50 is coupled so that the inner peripheral surface thereof can be splined with the spline 12 of the clutch shaft 10 so as to move a certain length in the axial direction along the spline 12 of the clutch shaft 10.

  Accordingly, the clutch shaft 10 can be rotated by the driving force transmitted through the third moving clutch 50.

  On the other hand, a drive clutch gear 60 is provided in the direction in which the first ratchet gear 51 of the third moving clutch 50 is formed.

  FIG. 6 is a perspective view illustrating a drive clutch gear according to the present invention. As shown in the drawing, the drive clutch gear 60 of the present invention has a gear formed on the outer peripheral surface thereof and is connected with other gears to install equipment. It rotates as an actuating drive force to be actuated.

  Similarly to the first moving clutch 30, the drive clutch gear 60 also rotates continuously at a constant speed regardless of the clutch shaft 10 due to bearing coupling or bush coupling.

  The drive clutch gear 60 is spaced apart from the third movement clutch 50 by a certain width, and the second ratchet gear 61 that meshes with the first ratchet gear 51 on the surface facing the first ratchet gear 51 formed on the third movement clutch 50. Is formed.

  As described above, in the configuration of the present invention, the first moving clutch 30 and the drive clutch gear 60 are transmitted to the first moving clutch 30 by the gear coupling with the other gears connected to the first moving clutch 30 and the driving clutch gear. The driving force is continuously transmitted to 60.

  However, the rotational speed of the standby driving force transmitted to the first moving clutch 30 is necessarily delayed from the rotational speed of the operating driving force transmitted to the drive clutch gear 60, and as a result, the operating point of the equipment is determined for the delayed time. It will be in a state to wait with a delay.

  In particular, in the present invention, the protrusions (P) formed on the clutch portions have different sizes in the directions corresponding to each other, so that the first moving clutch 30 and the second movement are in contact with each other between the protruding cross sections of the protrusions. When the clutch 40 rotates, a balance is established so that the opposing surfaces are stabilized. At this time, the larger the size difference between the protrusions (SP, LP), the more stable rotation is possible. Therefore, it is preferable to form the frictional force as small as possible.

  In the present invention, the standby driving force transmitted to the first moving clutch 30 and the operating driving force transmitted to the drive clutch gear 60 can be adjusted by the user according to the field to which the present invention is applied. Is most preferred.

  On the other hand, reference numeral 320 in the present invention is a spring receiver.

  Next, the operation of the periodic power interrupting clutch according to the configuration of the present invention will be described in more detail.

  FIG. 7 is a sectional view of the coupling of the periodic power interrupting clutch according to the present invention. As described above, the present invention continuously generates the standby driving force via the first moving clutch 30 and the driving clutch gear 60. Actuation driving force is transmitted.

  For this reason, the first moving clutch 30 and the driving clutch gear 60 are respectively coupled with a gear for transmitting a standby driving force and an operating driving force, and each driving force adjusts a rotation speed by a user's mechanical operation or the like. Can do.

  Actually, the driving clutch gear 60 that rotates by the driving force that drives the driving means rotates continuously by the driving force that is transmitted from the driving source, whereas the first moving clutch 30 is the user when operating the driving means. The driving force is transmitted by the operation of and rotates.

  As a result, the drive clutch gear 60 rotates by rotating the first moving clutch 30 by the user's start operation in a state where the drive clutch gear 60 is simply idling independently of the clutch shaft 10 and the drive means is operated.

  This will be described in more detail. FIG. 8 is a diagram illustrating the operation standby state of the periodic power interrupting clutch according to the present invention. The first moving clutch 30 is on one side of the fixed clutch 20. The first clutch part 21 of the first moving clutch 30 and the protrusions of the third clutch part 31 are in contact with each other, and the protrusions on the fourth clutch part 41 side of the second moving clutch 40 (P ) Is a state where it is coupled to the second moving clutch 22 side projection (P) of the fixed clutch 20.

  At this time, the tip of the spring guide 42 of the second moving clutch 40 is in a state of being separated from the opposing plate surface of the first moving clutch 30 by a certain width.

  When the present invention starts to operate in such a state, the driving clutch gear 60 is idly rotated at a constant speed by the driving force from the driving source, and at this time, the first moving clutch 30 is rotated at a certain angle and the first clutch is rotated. The third clutch part 31 on the moving clutch 30 side is brought into a state of being engaged with the first clutch part 21 of the fixed clutch 20.

  Since the first moving clutch 30 is always in the state of being moved to the fixed clutch 20 by the elasticity of the first spring 32 at the rear, the third clutch portion 31 is located between the first clutch portion 21 and the protrusion (P). In this state, the first moving clutch 30 is engaged with the fixed clutch 20 while moving by the thickness of the protrusion (P).

  When the first moving clutch 30 is engaged with the fixed clutch 20, the plate surface facing the tip of the spring guide 42 of the first moving clutch 30 pushes the second moving clutch 40 by a certain width while colliding with the tip of the spring guide 42. become.

  As shown in FIG. 9, the first moving clutch 30 causes the second moving clutch 40 to move by a constant width until the protrusion (P) of the fourth clutch portion 41 begins to the protrusion (P) side inclined surface of the second clutch portion 22. At the same time, the third ratchet gear 51 of the third moving clutch 50 and the second ratchet gear 61 of the driving clutch gear 60 are not perfect while the third moving clutch 50 bolted to the second moving clutch 40 moves. Is in a state of gear coupling.

  When the driving force of the drive clutch gear 60 idled by the ratchet gear coupling between the third movement clutch 50 and the drive clutch gear 60 is transmitted to the third movement clutch 50, the rotation of the third movement clutch 50 causes the first movement. The second clutch 40 that is bolted together with the clutch shaft 10 that is splined to the three-moving clutch 50 rotates simultaneously.

  At this time, when the second moving clutch 40 rotates, the protrusion (P) of the fourth clutch portion 41 rotates along the protrusion inclined surface of the second clutch portion 22 and the cross-sections of both protrusions (P) come into contact with each other. When the second moving clutch 40 moves further, the third moving clutch 40 and the drive clutch gear 60 are completely engaged with the ratchet gear.

  As a result, the third clutch portion 31 of the first moving clutch 30 and the fourth clutch portion 41 of the second moving clutch 40 are pushed out to the maximum on both sides of the first clutch portion 21 and the second clutch portion 22 of the fixed clutch 20, respectively. In this state, while the clutch shaft 10 is rotated by the third moving clutch 50, the driving means connected to the clutch shaft 10 by gear coupling or the like is driven.

  The driving means is driven while the clutch shaft 10 makes one rotation of 360 °. At this time, the second moving clutch 40 also makes one rotation at the same time.

  When the second moving clutch 40 makes one complete rotation, the protrusion (P) formed on the fourth clutch portion 41 is in a state where the second clutch portion 22 of the fixed clutch 20 and the protrusion (P) correspond to each other as shown in FIG. As a result, the second spring 43 is engaged with the second moving clutch 30 having moving elasticity on the first moving clutch 30 side.

  That is, at the moment when the fourth clutch portion 41 of the second moving clutch 40 and the second clutch portion 22 of the fixed clutch 20 are in a state corresponding to each other between the mutual protrusions (P), the second spring 43 elastically supporting the second moving clutch 40. Thus, the second moving clutch 40 is moved to the fixed clutch 20 side, and the fourth clutch portion 41 is accurately engaged with the second clutch portion 22.

  When the second moving clutch 40 comes into close contact with the fixed clutch 20 in this manner, the ratchet gear coupled state with the drive clutch gear 60 is disconnected while the third moving clutch 50 bolted to the second moving clutch 40 moves in the axial direction. As a result, the driving force transmitted from the driving clutch gear 60 cannot be transmitted any further to the third moving clutch 50, and the idle rotation state is resumed.

  Although the rotation of the clutch shaft 10, the second moving clutch 40, and the third moving clutch 50 is suspended, the first moving clutch 30 is not coupled to the first clutch portion 21 of the fixed clutch 20. The rotation continues due to the cross-sectional contact of the protrusion (P).

  However, when the first moving clutch 30 also rotates exactly 360 °, the third clutch portion 31 is engaged with the first clutch portion 21 of the fixed clutch 20, and thus the first moving clutch 30 is fixed to the fixed clutch 20. As shown in FIG. 8, the first moving clutch 30 repeats the action of moving the second moving clutch 40 by a certain width at the moment of coupling to the first and second clutches.

  That is, when the operation of FIGS. 8 to 10 is repeated, the driving means is driven for a certain period of time, and at the same time a standby state can be maintained for a certain period of time. When applied to agricultural equipment such as machines, it can be used more effectively and conveniently.

  In particular, as described above, if the operating driving force transmitted to the driving clutch gear 60 and the rotation speed of the standby driving force of the first moving clutch 30 are appropriately adjusted according to the application, there is a merit that can be applied in a wide range in all industrial fields. Can be provided.

DESCRIPTION OF SYMBOLS 10 Clutch shaft 12 Spline 20 Fixed clutch 21 1st clutch part 22 2nd clutch part 30 1st movement clutch 31 3rd clutch part 32 1st spring 32 Hollow pipe 40 2nd movement clutch 41 4th clutch part 42 Spring guide 43 Second spring 50 Third moving clutch 51 First ratchet gear 60 Drive clutch gear 62 Second ratchet gear

Claims (8)

A clutch shaft rotatably supported;
A fixed clutch in which the clutch shaft penetrates the center while one side is fixed to the clutch housing, and the first and second clutch portions are formed at a constant radius in the ring-shaped cross sections on both sides;
A first moving clutch that slides back and forth in a constant width axial direction by the fixed clutch and a first spring that is elastically mounted in a corresponding direction while rotating by a standby driving force transmitted by a gear coupling of an outer peripheral surface;
At the moment when the first clutch portion of the fixed clutch and the third clutch portion of the first moving clutch are engaged, the first moving clutch and the second spring slide by a constant width in the axial direction in the hollow tube of the first moving clutch. A second moving clutch that reciprocates;
The first moving clutch is coupled to the second moving clutch and is splined to the clutch shaft so that power transmission to the clutch shaft is interrupted while sliding with a constant width together with the second moving clutch. A three-movement clutch;
A drive clutch gear to rotate the clutch shaft through the third moving clutch by actuating a driving force transmitted through the gear coupling of the outer circumferential surface by the third moving clutch and ratchet gear coupling, Ri Do from binding,
When the third clutch portion of the first moving clutch is not engaged with the first clutch portion of the fixed clutch, the second moving clutch is engaged with the fixed clutch, and the third moving clutch And the ratchet gear coupling between the drive clutch gear and the drive clutch gear are broken,
When the third clutch of the first moving clutch is engaged with the first clutch of the fixed clutch by rotating the first moving clutch from the state, the second moving clutch and the The third moving clutch slides in the direction of the constant width axis, and the third moving clutch and the drive clutch gear are in a state of being coupled with a ratchet gear;
Further, the first moving clutch further rotates from the state, whereby the third clutch portion of the first moving clutch is not engaged with the first clutch portion of the fixed clutch. Power intermittent clutch.   2. The periodic shaft according to claim 1, wherein the clutch shaft has a spline formed on one circumferential surface of the clutch shaft so as to be splined with the third moving clutch while being supported by bearings on both sides. Power intermittent clutch. The first and second clutch portions of the fixed clutch form protrusions with small angles and protrusions with large angles on the corresponding peripheral surfaces of the same radius on the plate surfaces on both sides. characterized by a certain height or et inclined obliquely from the bottom or bottom, periodic power intermittent clutch according to claim 1.   The first moving clutch is axially supported on one side of the fixed clutch so as to be slidable by a fixed width in the axial direction along the clutch shaft, and is rotated by a standby driving force via a gear coupling on the outer peripheral surface. A third clutch portion that is clutched with the first clutch portion of the fixed clutch is formed on one side surface that faces the fixed clutch, and an inner peripheral edge is formed so as to penetrate the inside of the second moving clutch. A tube-shaped hollow tube that is coupled to a shaft and a bush is formed, and a retaining ring is coupled to an end portion of the hollow tube together with a thrust bearing so as to prevent the thrust bearing from being detached. The periodic power interrupting clutch according to claim 1.   5. The cycle according to claim 1, wherein the third clutch portion of the first moving clutch forms a protrusion having a shape corresponding to the small protrusion and the large protrusion of the first clutch portion of the fixed clutch. Power intermittent clutch.   The second movement clutch is provided on an outer peripheral surface of a hollow tube extending a certain length from one side of the first movement clutch so as to be axially movable and rotatable, and one end of the second movement clutch is disposed on the first movement clutch. A spring guide is formed on one side in which contact with the inner peripheral side plate surface of the hollow tube of the clutch is interrupted and a second spring is elastically provided to move toward the first moving clutch. Projections in the shape corresponding to the small and large projections of the second clutch portion are formed on the opposite end of the fixed clutch at the other end corresponding to the one end contacting the first moving clutch of the spring guide. The periodic power intermittent clutch according to claim 1, further comprising a fourth clutch portion to be formed.   The third moving clutch has a first ratchet gear on the side surface opposite to the fastening surface while being bolted to the second moving clutch with an inter-surface bolt, and an inner circumferential surface is splined to the clutch shaft. The periodic power interrupting clutch according to claim 1, wherein the clutch is a periodic power interrupting clutch.   The driving clutch gear receives an operating driving force by gear coupling on an outer peripheral surface, and a second ratchet gear that is gear-coupled to a first ratchet formed on the third moving clutch on a surface facing the third moving clutch. The periodic power interrupting clutch according to claim 1, wherein:

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