JPH07167170A - Reversible clutch - Google Patents

Abstract

(57) [Summary] [Purpose] To generate intermittent motion in both forward and reverse directions with a simple configuration. [Configuration] An internal space 1a penetrating in the direction of the axis A is provided,
An actuator 1 to which a reciprocating motion is given from a prime mover, a driven body 2 loosely fitted in an inner space 1a of the actuator 1 and movably supported in the same reciprocating direction of the prime mover, and a follower 2 A plurality of rolling elements 5 arranged in a gap 3 formed between an outer surface of the driven element 2 and an inner wall surface 1b forming the inner space 1a of the actuator 1 and circumscribing the driven element 2. , Rolling element 5
A rolling element holder 4 for rotatably holding the rolling element holder, and biasing means 10, 11 for biasing the rolling element holder 4 in one of the reciprocating motions of the actuator 1. The inner wall surface 1b of the device 1 is formed so as to narrow the gap 3 and become smaller than the diameter of the rolling element 5 when the actuator 1 moves in the direction opposite to the urging direction. The urging direction can be switched freely.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reversible clutch, and more particularly to a reversible clutch that converts reciprocating motion into intermittent motion and transmits it.

[0002]

2. Description of the Related Art Conventionally, for example, in sewing machines and the like, a one-way clutch for giving intermittent motion has been used in various mechanisms. For example, a cloth feeding mechanism is provided with a one-way clutch for intermittently feeding cloth. ing.

[0003]

By the way, depending on the sewing, it is necessary to feed the cloth in the reverse direction as in the case of sewn seams. However, the one-way clutch can feed the cloth only in the forward direction. Although a mechanism is provided to enable reverse feed, such a reverse feed mechanism has a problem that the number of parts is large and the structure is complicated.

Further, in the device described in Japanese Patent Laid-Open No. 63-139593, there is described a mechanism that enables forward and reverse intermittent feed using a clutch, but this also has a large number of parts and has a complicated structure. There is a problem that becomes.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a reversible clutch which has a simple structure and which causes intermittent motion in both forward and reverse directions.

[0006]

In order to achieve the above object, a reversible clutch of the first means has an internal space penetrating in the axial direction, and an actuator to which a reciprocating motion is given from a prime mover, A driven body that is loosely fitted in the internal space of the actuator and movably supported in the same direction as the reciprocating direction of the driving body, and an outer surface of the driven body and an inner wall surface that forms the internal space of the actuator. A plurality of rolling elements arranged in a gap formed between the rolling elements and circumscribing the driven elements, a rolling element retainer for rotatably holding these rolling elements, and this rolling element Urging means for urging the cage in one of the directions of movement of the reciprocating motion of the actuator, the inner wall surface of the actuator moving in a direction opposite to the urging direction of the actuator. Then, the gap is narrowed so that the diameter is smaller than the diameter of the rolling element. Ri, is characterized by being freely switch the urging direction of the urging means.

In order to achieve the above object, the reversible clutch of the second means has a through hole penetrating in the axial direction, and an outer ring to which the oscillating motion from the prime mover is given and a through hole of this outer ring. The driven body is loosely fitted and rotatably supported, and is disposed in a gap formed between the outer surface of the driven body and the inner surface of the outer ring, and is circumscribed to the driven body. Energizing a plurality of cams having a maximum diameter larger than the gap and a position eccentric from the rotation center of the cam in one of the swinging movement directions with the rotation center of the cam as a fulcrum. The cam is formed such that when the outer ring swings in the same direction as the urging direction, the outer surface of the cam is pressed against the inner surface of the outer ring, and the urging direction of the urging means. The feature is that it can be switched.

[0008]

According to the reversible clutch in the first means, for example, when the rolling element holder is biased in one direction during the reciprocating motion of the actuator by the biasing means,
When the actuator moves in the other direction during movement of the actuator, the rolling element is biased in one direction by the biasing means, and the inner wall surface of the actuator moves in the direction opposite to the biasing direction of the actuator. Then, since it is formed so as to narrow the gap and become smaller than the diameter of the rolling element, the rolling element is locked between the outer surface of the driven element and the inner wall surface of the actuator, and the driven element together with the actuator and the rolling element. Exercise in the other direction. Here, when the movement direction of the actuator is reversed, the gap between the outer surface of the driven body and the inner wall surface of the actuator becomes large, the lock of the rolling element is released, and the driven body stops during that time. Then, when the actuator is inverted again and moves in the other direction, the rolling element is locked between the outer surface of the driven body and the inner wall surface of the actuator, the driven body moves in the other direction, and these movements are repeated. Then, the driven body intermittently moves in the other direction. On the other hand, if the rolling element retainer is biased in the other direction during the reciprocating motion of the actuator by the biasing means, when the actuator moves in one direction during the reciprocating motion of the actuator, the rolling element It is biased in the other direction by the biasing means, and the inner wall surface of the actuator is formed so as to narrow the gap and become smaller than the rolling element diameter when the actuator moves in the direction opposite to the biasing direction. Therefore, the rolling element is locked between the outer surface of the driven body and the inner wall surface of the actuator, and the driven body moves in one direction together with the actuator and the rolling body. Here, when the movement direction of the actuator is reversed, the gap between the outer surface of the driven body and the inner wall surface of the actuator becomes large, the lock of the rolling element is released, and the driven body stops during that time. Then, when the actuator reverses again and moves in one direction, the rolling element is locked between the outer surface of the driven body and the inner wall surface of the actuator, the driven body moves in one direction, and these movements are repeated. Then, the driven body makes an intermittent motion in one direction.

According to the reversible clutch in the second means, for example, a position eccentric from the rotation center of the cam by the urging means is set in one direction during the swing motion of the outer ring with the rotation center of the cam as a fulcrum. If the outer ring swings in one direction when the outer ring swings, the outer surface of the cam is pressed against the inner surface of the outer ring, and the cam is locked between the outer surface of the driven body and the inner surface of the outer ring. The driven body swings in one direction together with the outer ring and the cam. Here, when the swinging direction of the outer ring is reversed, the cam is unlocked and the driven body stops during that time. When the outer ring is inverted again and swings in one direction, the cam is locked between the outer surface of the driven body and the inner surface of the outer ring, the driven body swings in one direction, and these swings are repeated. As a result, the driven body intermittently moves in one direction. On the other hand, when the urging direction of the urging means is reversed, the same operation as the above is performed, and the driven body intermittently moves in the other direction.

[0010]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is an exploded perspective view of a reversible clutch according to a first embodiment of the present invention. The reversible clutch of this embodiment is provided, for example, in a cloth feed mechanism of a sewing machine. In the figure, reference numeral 1 denotes an outer ring as an actuator that is synchronized with a lower shaft (not shown) and is given an oscillating motion about an axis A. At the center of the outer ring 1, for example, A through hole 1a that forms an internal space having a regular hexagonal cross-sectional shape is formed along the axis A direction. Then, female screws 1b, 1b that are screwed into pressurizer fulcrum pins 7, 7, which will be described later, are formed on both end surfaces of the outer ring 1. In addition, in FIG. 1, the female screw 1b on the back side is not drawn.

A cloth feed shaft (driven body) is provided in the through hole 1a.
A cylindrical shaft 2 is inserted so that its axis coincides with the axis A of the outer ring 1, and the shaft 2 is rotatably supported by a bearing (not shown).

In the gap 3 (see FIGS. 2 and 3) between the outer peripheral surface of the shaft 2 formed by inserting the shaft 2 into the through hole 1a and the inner surface (inner wall surface) 1b of the outer ring 1. A roller retainer 4 as a rolling element retainer having a hollow cylindrical shape is inserted therein. The roller retainer 4 is formed with rectangular through holes 4a, which are equidistantly arranged in the circumferential direction in the cylindrical portion, and each of the through holes 4a serves as a rolling element slightly smaller than the through hole 4a. Each roller 5 is arranged. These rollers 5 are arranged so that a part thereof respectively protrudes into and out of the cylindrical portion (see FIGS. 2 and 3), and is further rotatably supported by the roller holder 4. The diameter of the roller 5 is larger than the minimum clearance 3a of the clearance 3 and smaller than the maximum clearance 3b, and the roller 5 is circumscribed on the shaft 2 with the roller holder 4 inserted in the clearance 3. Has become. Then, on both end surfaces of the roller holder 4, projecting portions 4b, 4b which are respectively loosely fitted in crotch portions 6a, 6a of a pressurizer 6 which will be described later are formed.

A U-shaped pressurizer 6 is arranged so as to sandwich the outer ring 1 from both ends, and the pressurizer 6 is connected to both side portions forming the U-shape and the both side portions. It is composed of a portion 6c. Through holes 6b, 6b are formed substantially in the center of both side portions, and crotch portions 6a, 6a are formed at the tip portions of both side portions. Through hole 6b,
Pressurizer fulcrum pins 7 and 7 are inserted in 6b, and these pressurizer fulcrum pins 7 and 7 are in a state of being screwed into the female screws 1b and 1b of the outer ring 1, that is, the pressurizer 6 is a pressurizer. The fulcrum pin 7 can be rotated about the fulcrum, and the crotch portion 6a,
The protrusions 4b, 4b of the roller holder 4 are loosely fitted in 6a.

A pressure spring retainer 8 is arranged on the back surface of the outer ring 1. The pressure spring retainer 8 is composed of a ring-shaped portion 8a into which the shaft 2 is inserted, and a projecting portion 8b projecting upward from the ring-shaped portion 8a in the figure. Long holes 8d, 8d cut out in a circular arc shape are formed in each. Pressure spring retainer stepped screws 9, 9 are inserted into the elongated holes 8d, 8d, and the pressure spring retainer stepped screws 9, 9 are respectively attached to female threads (not shown) formed on the back surface of the outer ring 1. It is in a screwed state. That is, the pressure spring retainer 8 is rotatable about the axis A within the range regulated by the elongated hole 8d.

Both upper side surfaces of the protruding portion 8b of the pressure spring retainer 8 are respectively bent toward the front side of the outer ring 1, and the inner surfaces of these bent portions 8c, 8c are first biased. One end of the pressure spring 10 forming the means and the pressure spring 11 forming the second urging means are fixed to each other. The other ends of the pressure springs 10 and 11 are separated from each other by a predetermined length, and the connecting portion 6c of the pressurizer 6 is arranged between the other ends, and the initial position is, for example, the pressure spring 10. The other end side is set so as to contact the connecting portion 6c of the pressurizer 6 (see FIG. 2).

Next, the operation of the reversible clutch thus constructed will be described below with reference to FIG.
First, when the cloth is sequentially fed, as described above, the pressure spring retainer 8 is set so that the other end side of the pressure spring 10 contacts the connecting portion 6c of the pressure device 6. That is, the pressurizer 6 is biased clockwise in the drawing with the pressurizer fulcrum pin 7 as a fulcrum, and the roller retainer 8 having the protruding portion 4b loosely fitted in the crotch portion 6a is centered on the axis A. It is biased counterclockwise. Therefore, the roller 5 is also urged counterclockwise about the axis A.

In this state, the outer ring 1 is given a swinging motion about the axis A in synchronism with the lower shaft.
The swinging range B shown in FIG.

Here, the counterclockwise swing direction around the axis A of the outer ring 1 is defined as one direction X, and the clockwise swing direction is defined as the other direction Y. When the outer ring 1 swings in the other direction Y,
As described above, since the roller 5 is biased counterclockwise about the axis A, the roller 5 is locked between the outer peripheral surface of the shaft 2 and the inner surface of the outer ring 1 as shown in the figure. Therefore, the shaft 2 swings in the other direction Y together with the outer ring 1 and the roller 5.

Then, when the swinging direction of the outer ring 1 is reversed and swings in the one direction X, the gap between the outer peripheral surface of the shaft 2 and the inner surface of the outer ring 1 becomes large, and the roller 5 is unlocked. Axis 2
Meanwhile stops.

Then, when the outer ring 1 is inverted again and swings in the other direction Y, the roller 5 is locked between the outer peripheral surface of the shaft 2 and the inner surface of the outer ring 1 in the same manner as described above, and the shaft 2 moves in the other direction. The shaft 2 swings in Y and these movements are repeated, so that the shaft 2 intermittently rotates in the other direction Y.

On the other hand, for example, when reverse stitching or the like is required and it is necessary to reverse feed the cloth, an external force is applied to slide the pressure spring retainer 8 about the axis A within the elongated hole 8d. Rotate to the position shown in FIG. That is, the pressure spring retainer 8 is rotated so that the other end of the pressure spring 11 contacts the connecting portion 6c of the pressure device 6. Then, the pressurizer 6 is biased counterclockwise in the figure with the pressurizer fulcrum pin 7 as a fulcrum, and the roller retainer 8 having the protruding portion 4b loosely fitted in the crotch portion 6a has the axis A. It is urged clockwise around the center. Therefore, the roller 5 is also urged clockwise about the axis A.

In this state, when the outer ring 1 is given a swinging motion about the axis A and the outer ring 1 swings in one direction X, as shown in FIG. 3, the outer peripheral surface of the shaft 2 and the outer ring 1 are rotated. The roller 5 is locked between it and the inner surface of the shaft 1, and the shaft 2 swings in the one direction X together with the outer ring 1 and the roller 5.

Next, when the swinging direction of the outer ring 1 is reversed and swings in the other direction Y, the gap between the outer peripheral surface of the shaft 2 and the inner surface of the outer ring 1 becomes large, and the lock of the roller 5 is released. Axis 2
Meanwhile stops.

When the outer ring 1 is inverted again and swings in the one direction X, the roller 5 is locked between the outer peripheral surface of the shaft 2 and the inner surface of the outer ring 1 in the same manner as described above, and the shaft 2 moves in the one direction. The shaft 2 swings in X, and these movements are repeated, so that the shaft 2 rotates intermittently in one direction X.

As described above, in this embodiment, it is possible to generate the intermittent rotary motion in both the forward and reverse directions with a simple structure.

FIG. 4 is a front view of a reversible clutch according to a second embodiment of the present invention. Only the outer ring 21, the rollers 5 and the shaft 2 are shown in order to avoid complication of the drawing. Since the structure not shown is the same as that of the first embodiment, the description thereof is omitted here.

The reversible clutch of the second embodiment is different from that of the first embodiment in that the shape of the through hole formed in the outer ring is changed.

Here, the inner wall surface forming the through hole 21a of the outer ring 21 is composed of a curved surface 21b and an arc surface 21c which are alternately arranged in the circumferential direction. The curved surface 21b is
It is formed symmetrically about its central portion (symmetrical along the axial direction), and at the center thereof, the gap 23 with respect to the outer peripheral surface of the shaft 2 is curved with a curvature larger than the diameter of the roller 5. At both ends thereof (portions provided continuously with the arcuate surface 21c), the gap 23 is narrowed and curved with a curvature smaller than the diameter of the roller 5.

Therefore, also in the second embodiment, when the outer ring 21 swings in the direction opposite to the urging direction of the roller 5 (for example, the one direction X), the roller 5 has a curved surface 21b and an arc surface 21c.
In the vicinity of the boundary portion between and, the curved surface 21b is locked between the outer peripheral surface of the shaft 2 and the outer ring 21 swings in the same direction as the biasing direction of the roller 5 (for example, the one direction X). When it moves, the lock of the roller 5 will be released.

Further, when the urging direction for the rollers 5 is switched, when the outer ring 21 swings in the direction opposite to the urging direction of the rollers 5 (the other direction Y), the rollers 5 are indicated by the one-dot chain line. As described above, the curved surface 21b and the arcuate surface 21c during the above operation
In the vicinity of the boundary on the side opposite to the boundary with the curved surface 21
When the outer ring 21 is swung in the same direction as the biasing direction of the roller 5 (the other direction Y), the lock of the roller 5 is released. It will be. That is, also in the second embodiment, as with the first embodiment, it is possible to generate the intermittent rotary motion in both the forward and reverse directions with a simple structure.

In this embodiment, the curved surface 21b
Since the number of rollers is 4, the number of rollers 5 is also 4.

FIG. 5 is a front view of a reversible clutch showing a third embodiment of the present invention. The reversible clutch of the third embodiment is different from that of the second embodiment in that the shape of the through hole formed in the outer ring is further changed.

Here, the inner wall surface forming the through hole 31a of the outer ring 31 is composed of a curved surface 31b which is alternately arranged in the circumferential direction and an inclined surface 31c which is inclined substantially linearly. At the center of the curved surface 31b, the gap 33 with respect to the outer peripheral surface of the shaft 2 is curved with a curvature that is larger than the diameter of the roller 5, and at one end, the gap 33 is narrowed to make it smaller than the diameter of the roller 5. It is curved with a small curvature, and at the other end, it is connected to the inclined surface 31c while being curved. That is, in the third embodiment, the curved surface 31
b is not formed symmetrically with the center part as the center.

However, also in the third embodiment, the inner wall surface of the outer ring 31 is formed so as to narrow the gap 33 and become smaller than the diameter of the roller 5 when the outer ring 31 moves in the direction opposite to the urging direction. Therefore, it is needless to say that the same operational effect as that of the second embodiment is obtained.

FIG. 6 is an exploded perspective view of a reversible clutch according to a fourth embodiment of the present invention, and FIG. 7 is a front view of the reversible clutch shown in FIG. The reciprocating linear motion is intermittent linear motion, unlike the rocking motion which is intermittent rotary motion as in the first to third embodiments.

6 and 7, reference numeral 40 denotes an actuator to which a reciprocating linear motion along the axis A is applied from a driving body (not shown). The actuator 40 has a cross section perpendicular to the axis A. It is formed to have a letter shape.
A plurality of concave arc surfaces 40d are continuously provided along the axis A on the inner surfaces of the side plates 40b and 40c forming the U-shape of the actuator 40. In the internal space 40a formed by the U-shape, the shaft 4 having a rectangular rod shape as a driven body is formed.
1 is inserted, and the shaft 41 is inserted into through-angled holes 42a, 42a formed in the standing portions at both ends of the base 42, and is supported slidably in the direction of the axis A.

In the gaps 43, 43 between the outer surface (upper and lower surfaces in FIG. 7) of the shaft 41 formed by inserting and arranging the shaft 41 in the inner space 40a and the side plates 40b, 40c of the actuator 40. The roller holders 44, 44 as rolling element holders each having a flat plate shape and having a length in the axis A direction longer than that of the actuator 40 in the axis A direction are inserted. The roller holder 44 has a rectangular through hole 44a whose longitudinal direction is perpendicular to the axis A,
Rollers 45, which are formed at positions facing the arc surface 40d and are slightly smaller than the through holes 44a, are arranged in the through holes 44a. These rollers 45 are arranged such that a part thereof protrudes in the vertical direction of the roller holder 44 (see FIG. 7), and is further rotatably supported by the roller holder 44.

The diameter of the roller 45 is the minimum clearance 4 of the clearance 43.
It is larger than 3a and smaller than the maximum gap 43b, and the roller 45 is in a state of being circumscribed on the shaft 41 with the roller holder 44 inserted in the gap 43.

Actuator 40 and upright portions of both ends of the base 42.
Pressure springs 46, 46 spirally wound in a square shape are arranged between the both end surfaces of the pressure spring 46 so as to surround the shaft 41. The pressure spring 46 has its actuator-side upper and lower portions opposed to the side surfaces of the roller holders 44, 44, and its upright portion side is fixed to the upright portion.

An elongated hole 42b is formed along the axis A in the lower portion of the base 42. An actuator holding step screw 47 is inserted in the elongated hole 42b, and the actuator holding step screw 4 is inserted.
7 are in a state of being respectively screwed into female screws (not shown) formed in the lower portion of the actuator 40. That is,
The actuator 40 is slidable along the axis A within the range regulated by the long hole 42b.

Next, the operation of the reversible clutch thus constructed will be described below. First, the roller holder 44 and the actuator 40 are set so that the actuator 40 side of the left pressure spring 46 shown in FIG. 7 contacts the left side surface of the roller holder 44 in the figure. That is, the roller retainer 44 is biased rightward in FIG.
Therefore, the roller 45 is also biased to the right.

In this state, the actuator 40 is given a reciprocating linear motion along the axis A. Here, the right direction of the actuator 40 in FIG. 7 is one direction M, and the left direction is the other direction N. When the actuator 40 linearly moves in the other direction N, as described above, the roller 45 is urged in the right direction, that is, the one direction M. Therefore, as shown in the drawing, the outer surface of the shaft 41 and the actuator 40 are urged. The roller 45 is locked between it and the right end of the arc surface 40d of the shaft 40, and the shaft 41 moves the actuator 40 and the roller 4
5 and linearly move in the other direction N.

Next, when the direction of the linear motion of the actuator 40 is reversed and linearly moves in the one direction M, the gap between the outer surface of the shaft 41 and the arc surface 40d of the actuator 40 becomes large, and the roller 45 is locked. Is released, and the shaft 41 stops during that time.

When the actuator 40 is turned over again and linearly moved in the other direction N, the roller 45 is locked between the outer surface of the shaft 41 and the right end of the arc surface 40d of the actuator 40 in the same manner as above. The shaft 41 linearly moves in the other direction N, and these motions are repeated, so that the shaft 41 makes intermittent linear motion in the other direction N.

On the other hand, when the shaft 41 is to be intermittently moved linearly in the one direction M, an external force is applied to the actuator 40 so that the actuator 40 is elongated.
The roller holder 44 is slid to the right within the range, and the right side surface of the roller holder 44 in the drawing is brought into contact with the actuator 40 side of the right pressure spring 46. Then, the roller holder 44 is biased to the left side in the figure, and thus the roller 45 is also biased to the left side.

In this state, when the actuator 40 is given a reciprocating linear motion along the axis A and the actuator 40 linearly moves in the one direction M, the outer surface of the shaft 41 and the arc surface 40 of the actuator 40.
The roller 45 is locked between the left end portion of d and the shaft 41, and the shaft 41 moves in one direction M together with the actuator 40 and the roller 45.
Linearly move to.

Next, when the direction of the linear motion of the actuator 40 is reversed and linearly moves in the other direction N, the gap between the outer surface of the shaft 41 and the arcuate surface 40d of the actuator 40 becomes large, and the roller 45 is locked. Is released, and the shaft 41 stops during that time.

When the actuator 40 is inverted again and moves linearly in the one direction M, the roller 45 is locked between the outer surface of the shaft 41 and the arc surface 40d of the actuator 40 in the same manner as above.
The shaft 41 makes a linear motion in the one direction M, and these motions are repeated, so that the shaft 41 makes an intermittent linear motion in the one direction M.

As described above, in this embodiment, it is possible to generate an intermittent linear motion in both the forward and reverse directions with a simple structure.

8 to 11 show a reversible clutch according to the fifth embodiment of the present invention. 8 to 11, reference numeral 51 denotes an outer ring that is given a swinging motion about the axis A in synchronization with a driving body (not shown), and the central portion of the outer ring 51 has an inner space with a circular cross section. Is formed along the axis A direction.

On both end surfaces of the outer ring 51, a plurality of pins 51d for locking lock cam support plates 54, 54, which will be described later, are provided in a protruding manner. Further, a protrusion 51b protruding outward is formed on a part of the outer peripheral surface of the outer ring 51, and a hole 51c is formed in the protrusion 51b. This hole 5
A protruding portion 56a protruding from one end of a flat plate-shaped rotary spring hook 56 is rotatably inserted in 1c. A protrusion 56b is provided on the back surface of the other end of the rotary spring hook 56, and one end of the pressure spring 61 is locked to the protrusion 56b.

The same shaft 2 as that of the first embodiment described above is inserted into the through hole 51a so that its axis coincides with the axis A of the outer ring 51, and the shaft 2 is not shown. It is rotatably supported by bearings.

In the gap 53 between the outer peripheral surface of the shaft 2 and the inner peripheral surface of the outer ring 51 formed by inserting and arranging the shaft 2 in the through hole 51a, a long boot-shaped lock cam 55 is provided in the longitudinal direction thereof. Are arranged at equal intervals in the circumferential direction along the axis A direction. The lock cam 55 is composed of a cam 55a forming a shaft portion and a bottom portion 55b. The cam 55a is arranged in the gap 53, and the bottom portion 55 is formed.
b is arranged so as to project outward from the outer peripheral surface of the outer ring 51. A pin 55c is provided on the end face of the cam 55a and a pin 55d is provided on the bottom face of the bottom portion 55b with their axes aligned, and a pressure pin 55e is provided on the top face end of the bottom portion 55b. ing. The cam 55a is in a state of being in contact with the shaft 2 while being inserted into the gap 53, and the maximum diameter of the cam 55a is larger than that of the gap 53.

Ring-shaped lock cam support plates 54, 54 are arranged so as to sandwich the outer ring 51 from both ends. A plurality of protrusions 54 a protruding outward are formed on the outer peripheral surface of the lock cam support plate 54.
The tip of 4a is cut out in an arc shape. The pin 51d of the outer ring 51 is fitted in the arcuate notch, and the lock cam support plates 54, 54 are fixed to the outer ring 51 in the circumferential direction. A plurality of through holes 54b are formed in the ring portion, and the pin 55c of the lock cam 55 is formed in the through hole 54b of the left lock cam support plate 54 in FIG.
Pins 55d of the lock cam 55 are rotatably inserted into the through holes 54b.

A ring-shaped lock cam pressurizer 58 is loosely fitted on the outer peripheral surface of the outer ring 51. A protrusion 58c is provided on the surface of the ring portion of the lock cam pressurizer 58 on the side of the rotary spring hook 56, and the other end of the pressure spring 61 is locked to the protrusion 58c.

A plurality of protrusions 58a protruding outward are formed on the outer peripheral surface of the lock cam pressurizer 58.
Elongated holes 58b are formed in 8a along the line connecting the projection 58a and the axis A. The pressure pin 55e of the lock cam 55 is inserted into the elongated hole 58b.

Next, the operation of the reversible clutch thus configured will be described below with reference to FIG. First, the lock cam pressurizer 58 is biased counterclockwise by the biasing force of the pressure spring 61, and the cam 55a
Is urged counterclockwise about the pin 55c (55d) as a fulcrum as shown in the figure, and the outer peripheral surface on the right side is the outer ring 5
It is set so as to contact the inner peripheral surface of 1a.

In this state, the outer ring 51 is given a swinging motion about the axis A. Here, the axis A of the outer ring 51
The counterclockwise swinging direction centering around is the one direction X, and the clockwise swinging direction is the other direction Y. When the outer ring 51 swings in the one direction X, as shown in FIG. 9, the cam 55a
Is urged in one direction X about the pin 55c (55d) as a fulcrum, the cam 55a tends to rotate in one direction X due to the frictional resistance. Then, since the diameter of the cam 55a becomes larger than the gap 53, the cam 55a is locked between the outer peripheral surface of the shaft 2 and the inner peripheral surface of the outer ring 51, so that the shaft 2 can rotate the outer ring 51 and the cam 55a. With one direction X
Rock to.

Next, when the swinging direction of the outer ring 51 is reversed and swings in the other direction Y, the cam 55a is unlocked by the principle opposite to the above, and the shaft 2 stops during that period.

Then, the outer ring 51 is reversed again and the one direction X
When it is swung to, the cam 55a is locked between the outer peripheral surface of the shaft 2 and the inner peripheral surface of the outer ring 51 in the same manner as described above, the shaft 2 swings in one direction X, and these movements are repeated, The shaft 2 rotates intermittently in one direction X.

On the other hand, when the shaft 2 is intermittently rotated in the other direction Y, an external force is applied to the rotary spring hook 56 so that the protrusion 56a.
Is rotated about its center, and its position is inverted with respect to that shown in FIG. 10, as shown in FIG. Then, the lock cam pressurizer 58 is rotated along the other direction Y by the amount of movement of the protrusion 58c, and is biased in the other direction Y by the biasing force of the pressure spring 61. Therefore, the cam 55a
As shown in FIG. 11, the pin 55c (55d) is urged clockwise around the fulcrum, and the left outer peripheral surface is set so as to contact the inner peripheral surface of the outer ring 51a. Incidentally, since the pressure spring 61 is beyond the dead center, it does not return to its original position.

In this state, when the outer ring 51 is given a swinging motion about the axis A and the outer ring 1 swings in the other direction Y, the outer peripheral surface of the shaft 2 and the outer ring 51 are guided by the same principle as described above. The cam 55a is locked between it and the inner surface of the shaft 2
Swings in the other direction Y together with the outer ring 51 and the cam 55a.

Then, when the swinging direction of the outer ring 51 is reversed and swings in the one direction X, the lock of the cam 55a is released,
Axis 2 stops during that time.

Then, the outer ring 51 is reversed again and the other direction Y
When the shaft 2 is swung to, the cam 55a is locked between the outer peripheral surface of the shaft 2 and the inner surface of the outer ring 51 in the same manner as described above, the shaft 2 swings in the other direction Y, and these movements are repeated, so that the shaft 2 Will intermittently rotate in the other direction Y.

As described above, in this embodiment, it is possible to generate the intermittent rotary motion in both the forward and reverse directions with a simple structure.

Although the invention made by the present inventor has been specifically described based on each embodiment, the present invention is not limited to each embodiment described above, and various modifications can be made without departing from the scope of the invention. Needless to say, for example, although the rollers are used as the rolling elements in the first to fourth embodiments, they may be spherical bodies (balls).

The pressure spring 6 shown in the fifth embodiment is also used.
1 and the biasing means by the rotary spring hook 56, etc.
It is also possible to apply to the embodiment.

Further, in each of the above-mentioned embodiments, the driven member is used as the shaft, but of course the inner ring may be used.

Furthermore, in each of the above embodiments, the reciprocating motion from the prime mover is always transmitted to the follower as an intermittent motion. However, the rollers of the first to fourth embodiments and the fifth embodiment. The cam can be forcibly stopped at a neutral position, that is, a position where the roller and the cam do not contact the inner surface of the actuator or the outer ring, and the transmission of the motion can be interrupted.

Needless to say, the reversible clutch of the present invention can be applied not only to the sewing machine but also to other mechanisms and devices.

[0071]

As described above, according to the reversible clutch of the present invention, it is possible to generate an intermittent motion in both forward and reverse directions with a simple structure.

[Brief description of drawings]

FIG. 1 is an exploded perspective view of a reversible clutch according to a first embodiment of the present invention.

FIG. 2 is a front view of a reversible clutch for explaining an intermittent motion in a positive direction.

FIG. 3 is a front view of a reversible clutch for explaining intermittent motion in the reverse direction.

FIG. 4 is a front view of a reversible clutch showing only an outer ring, a rolling element, and a driven element of a reversible clutch according to a second embodiment of the present invention.

FIG. 5 is a front view of a reversible clutch showing only an outer ring, rolling elements, and driven elements of a reversible clutch according to a third embodiment of the present invention.

FIG. 6 is an exploded perspective view of a reversible clutch according to a fourth embodiment of the present invention.

FIG. 7 is a front view of the reversible clutch shown in FIG.

FIG. 8 is an exploded perspective view of a reversible clutch showing a fifth embodiment of the present invention.

FIG. 9 is an enlarged development view of the portion showing the relationship between the cam, the outer ring, and the driven body when the cam is locked.

FIG. 10 is a front view of the reversible clutch for explaining the intermittent motion in the forward direction.

FIG. 11 is a front view of a reversible clutch for explaining intermittent motion in the reverse direction.

[Explanation of symbols]

1,1,21,31,40 actuator 1a, 21a, 31a, 40a internal space 1b, 21b, 31b, 31c, 40d inner wall surface of actuator 2,41 follower 3,23,33,43,53 gap 4,44 Rolling element cage 5,45 Rolling element 10, 11, 46, 61 Pressure spring 51 Outer ring 51a Through hole 55a Cam 55c, 55d Center of rotation of cam 55e Position eccentric from the center of rotation of the cam A Axis

Claims (2)

[Claims] 1. An actuator having an internal space penetrating in the axial direction, to which a reciprocating motion is applied from a prime mover, and a reciprocating motion direction of the prime mover that is loosely fitted in the inner space of the actuator. And a follower movably supported in the inner surface of the follower, and an outer surface of the follower and an inner wall surface forming an inner space of the actuator. A plurality of rolling elements provided, a rolling element retainer that rotatably holds these rolling elements, and this rolling element retainer is urged in either one of the reciprocating motions of the actuator. Urging means, and the inner wall surface of the actuator is formed so as to narrow the gap and become smaller than the rolling element diameter when the actuator moves in a direction opposite to the urging direction. A reversible clutch in which the urging direction of the urging means can be switched. . 2. An outer ring having a through hole penetrating in the axial direction and to which a swinging motion is applied from a driving body, a driven body loosely fitted in the through hole of the outer ring and rotatably supported. A plurality of cams that are arranged in a gap formed between the outer surface of the driven body and the inner surface of the outer ring and that are arranged so as to circumscribe the driven body and have a maximum diameter larger than the gap; Urging means for urging a position of the cam that is eccentric from the center of rotation of the cam in one of the swinging motion directions about the center of rotation of the cam as a fulcrum. A reversible clutch, the outer surface of which is formed so as to be pressed against the inner surface of the outer ring when swinging in the same direction as the biasing direction, and the biasing direction of the biasing means is switchable.