JP3472003B2 - Rotary parts with built-in clutch - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary component having a built-in clutch, such as a bearing having a built-in clutch and a pulley unit.

[0002]

2. Description of the Related Art Generally, in a fully automatic washing machine, the rotation of a main shaft driven by a motor is transmitted to a first output shaft to rotate a pulsator attached to the first output shaft or the first output shaft. And a cylindrical second provided outside thereof
By transmitting to each of the output shafts, the pulsator and the washing tub attached to the second output shaft are rotated together.

In a fully automatic washing machine as described above, since the second output shaft is normally rotatably supported by the bearing mounted on the housing, the second output shaft moves when the first output shaft rotates. There is a risk of turning. There is known a fully automatic washing machine in which a one-way clutch and a band brake are used together to prevent rotation of the second output shaft in order to prevent such a whirling.

The one-way clutch and the bearing for rotatably supporting the second output shaft are mounted close to each other, and if the two parts are designed to be assembled separately, it takes time and effort to assemble them.

In Japanese Laid-Open Patent Publication No. 54-109557, as shown in FIGS. 14 and 15, a ball 52 and a sprag 53 are incorporated between an outer ring 50 and an inner ring 51,
The sprag 53 is connected to the cylindrical surface 5 of the outer ring 50 and the inner ring 51.
A clutch built-in type bearing which is disengaged from and engaged with the clutches 4 and 55 is disclosed. By using such a clutch built-in type bearing, the above problems can be solved.

Further, Japanese Patent Laid-Open No. 61-228153 discloses a belt transmission for transmitting the rotation of a crankshaft of an automobile to a rotating shaft of an engine accessory such as an alternator which has a large inertial force and tries to rotate at a substantially constant value. The device is described.

In the above belt transmission device, a one-way clutch is incorporated between the rotary shaft of the engine accessory and the pulley supported by the rotary shaft, and the angular velocity of the crankshaft whose angular velocity slightly changes during one revolution. When the crankshaft increases, the rotation of the crankshaft is transmitted to the rotation shaft, and when the angular velocity of the crankshaft decreases, the rotation transmission to the rotation shaft is interrupted.

That is, when the angular velocity of the crankshaft increases, the rotation shaft of the engine accessory is connected to the pulley by engagement of the one-way clutch to transmit the rotation of the crankshaft to the rotation shaft, and the rotation of the rotation shaft rotates the pulley. Faster,
The rotation shaft is freely rotated by releasing the engagement of the one-way clutch.

The above-described belt transmission device is characterized in that slippage can be prevented from occurring between the pulley and the belt, so that the life of the belt can be reduced and the slip noise of the belt can be suppressed.

By the way, in the above belt transmission,
When the one-way clutch is directly assembled between the rotary shaft and the pulley, the radial load and the moment load acting on the pulley directly act on the one-way clutch, and the one-way clutch cannot be operated with high accuracy. It also shortens the life of the clutch.

Although such a problem can be solved by supporting the pulley with a bearing, if the design is such that the one-way clutch and the bearing are incorporated separately, it takes a lot of time to assemble.

Therefore, if a clutch built-in type pulley unit in which a pulley is fitted is used instead of the bearing outer ring 50 of the clutch built-in type bearing shown in FIGS. 14 and 15, the assembling can be facilitated.

[0013]

By the way, in the clutch built-in type bearing shown in FIGS. 14 and 15, since the balls 52 and the sprags 53 are arranged in series in the axial direction, the clutch built-in type bearing and the clutch built-in type are provided. There is a problem that the axial length of the shaped pulley unit is long.

An object of the present invention is to reduce the axial length of rotating parts such as a clutch built-in bearing and a clutch built-in pulley unit.

[0015]

In order to solve the above-mentioned problems, in the first invention, an outer diameter surface of an inner member fixed to a shaft and a cylindrical shape provided on the outer side of the inner member. A raceway groove is provided on each inner diameter surface of the outer member, and cylindrical surfaces are provided on both sides thereof, and a plurality of rolling elements are incorporated between the raceway grooves, and the rolling elements straddle between the cylindrical surfaces on both sides of the raceway groove. A cage having a sprag having a length and having a pocket for accommodating the rolling element and a sprag accommodating portion for accommodating the sprag is incorporated between an inner member and an outer member, and the inside / outside of the sprag is A structure is adopted in which the sprag is pressed by an elastic member in a direction in which the arc surface at the end engages with the cylindrical surfaces on both sides of the inner member and the outer member.

As the elastic member, a spring ring formed by cutting and raising the same number of spring pieces as the sprags can be used. The elastic member fixes the spring ring to the end surface of the retainer, and inserts each spring piece into the sprag housing through a window formed in the end surface of the retainer to press the sprag.

Further, in the second invention, instead of the sprags in the first invention, the inside of the inner wall is raised by centrifugal force.
An engagement type sprag in which a part of the arcuate surface at the outer end contacts the cylindrical surfaces on both sides of the inner member and the outer member is used, and the assembly of the elastic member in the first invention is omitted.

Here, a clutch built-in type bearing can be obtained by using an outer race for a bearing as the outer member, and a clutch built-in type pulley unit can be obtained by using a pulley as the outer member.

In the case of the clutch built-in type pulley unit, it is preferable to increase the rigidity of angular runout of the pulley with respect to the inner member in order to stably guide the belt. As a method of increasing the rigidity of angular runout, a method of making the radial clearance between the rolling element and the inner / outer raceway groove that guides the movement negative, and contacting each of the inner and outer raceway grooves with the rolling element at four points There is a method of adopting an angular contact type raceway groove.

[0020]

As described above, a sprag having a length that extends over the cylindrical surfaces on both sides of the raceway groove is used, and the sprag is arranged between the rolling elements, so that the rolling element and the sprag are arranged in the axial direction. It is possible to make the axial length compact as compared with.

[0021]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to FIGS.

1 to 4 show a bearing with a built-in clutch. This bearing has an inner race 1 as an inner member attached to a shaft, an outer race 2 as an outer member provided on the outer side thereof, and a cage 3 incorporated between both races 1 and 2.

On the outer diameter surface of the inner race 1, a raceway groove 4 is provided at the center in the axial direction, and cylindrical surfaces 5 are provided on both sides of the raceway groove 4.

On the other hand, the inner diameter surface of the outer race 2 is provided with a raceway groove 6 at the center in the axial direction and cylindrical surfaces 7 on both sides thereof.

The cage 3 comprises a cylindrical cage body 3a,
It is composed of a ring-shaped lid 3b, and a plurality of pins 8 are formed at one axial end of the cage body 3a. On the other hand, a pin hole 9 is provided in the lid 3b, and the pin 8 is inserted into the pin hole 9. The cage main body 3a and the lid 3b are integrated by melting the ends of the pins 8.

As shown in FIG. 10, a pin 8 may be provided on the lid 3b and the pin 8 may be press-fitted into a pin hole 9 formed in the retainer body 3a, or the retainer may be used without using the pin. You may fuse | melt and integrate the contact part of the main body 3a and the lid 3b.

Pockets 10 opening at one axial end of the cage body 3a and sprag accommodating portions 11 are alternately formed in the cage body 3a in the circumferential direction, and rolling elements 12 are accommodated in the pockets 10. There is.

The rolling element 12 can be freely rolled along the raceway grooves 4 and 6 of the inner race 1 and the outer race 2,
The protrusion 13 formed on the lid 3b prevents the pocket 10 from being axially pulled out from the open end.

As the rolling element 12, rollers can be used instead of balls.

A sprag 14 is provided in the sprag storage portion 11.
a is stored. This sprag 14a has a raceway groove 4,
6 has a length that straddles the cylindrical surfaces 5 and 7 on both sides of 6, and an arcuate surface 15 that can engage with the cylindrical surface 5 of the inner race 1 and the cylindrical surface 7 of the outer race 2 at the inner and outer ends. It is provided.

The sprag 14a may be engaged or disengaged.

This sprag 14a is a sprag storage unit 1
1 is in contact with the inner diameter side end of one wall surface 11a that is opposed to the front and rear in the circumferential direction, and the rear surface side with respect to the contact portion is the elastic member 16.
Pressed by the inner and outer circular arc surfaces 15 of the inner race 1
It is in contact with the cylindrical surfaces 5 and 7 of the outer race 2.

Although the elastic member 16 is composed of a thin metal plate in which a pair of elastic pieces 16b are formed at both ends of the U-shaped bent portion 16a, a coil spring or a rubber-like elastic body may be used. Good. In addition, the cage body 3
Alternatively, a resin elastic body integrated with a or the lid 3b may be used.

The bent portion 16a of the elastic member 16 is a support groove 17 formed on the other wall surface 11b of the sprag housing portion 11.
, And is prevented from moving in the axial direction by the protruding piece 18 provided on the lid 3b.

When the inner race 1 is rotated in the direction of the arrow in FIG. 2, the cylindrical surface 5 of the inner race 1 and the arcuate surface 15 at the inner end of the sprag 14a come into contact with each other, so that the sprag 14a is in the state shown in FIG. In the circular arc surface 1 at the inner and outer ends of sprag 14a
A part of 5 is engaged with the cylindrical surfaces 5 and 7 of the inner race 1 and the outer race 2.

Therefore, if the outer race 2 is fixed to the housing or the like, the inner race 1 can be prevented from rotating, and if the outer race 2 is used as a free support, the rotation of the inner race 1 can be prevented from rotating.
It can be transmitted to the outer race 2 via 4a.

When the inner race 1 is rotated in the direction opposite to the direction shown by the arrow in FIG. 2, the sprags 14a are rotated in the direction in which the elastic member 16 is elastically deformed, and the inner circular surface 15 and the inner race 1 are rotated. The inner race 1 can be freely rotated by causing a slip between the inner race 1 and the cylindrical surface 5.

The above-mentioned clutch built-in type bearing can be used as a bearing for supporting the second output shaft which supports the washing tub of the fully automatic washing machine.

By the way, in the bearing with a built-in clutch, the sprag 14a having a length extending over the cylindrical surfaces 5, 7 on both sides of the raceway grooves 4, 6 of the inner race 1 and the outer race 2 is provided along the raceway grooves 4, 6. Since the structure is provided between rolling rolling elements 12, the axial length can be made smaller than that of rolling elements and sprags connected in series in the axial direction.

Further, since the radial load acting on the inner race 1 and the outer race 2 can be supported by the rolling elements 12, the radial load hardly acts on the sprags 14a, and the clutch can function accurately. By using rollers as the rolling elements 12, a relatively large radial load can be applied.

FIG. 5 shows a second embodiment of the present invention. In the second embodiment, a belt guide pulley 30 is used in place of the outer race 2 of the first embodiment described above. The raceway groove 3 is formed on the inner diameter surface of the pulley 30.
1 and a cylindrical surface 32 on both sides thereof.

FIG. 6 shows an example of use of the clutch built-in type pulley unit shown in FIG. 5, in which the inner race 1 is fixed to the rotating shaft 41 of the alternator 40 which has a large inertial force and is about to rotate at a substantially constant speed. A belt 44 is stretched between the pulley 30 on the inner race 1 and the pulley 43 attached to the crankshaft 42.

In the above-described use, when the pulley 30 corresponding to the outer race 2 of FIG. 2 is rotated clockwise in the state of FIG. 2 by the rotation of the crankshaft 42 whose angular velocity slightly changes, the crankshaft is rotated. When the angular velocity of 42 increases, the sprag 14a engages with the inner race 1 and the cylindrical surfaces 5 and 32 of the pulley 30, and the rotation of the crankshaft 42 causes the rotation shaft 4 of the alternator 40 to rotate.
1 is transmitted.

When the angular speed of the crankshaft 42 decreases and the rotation speed of the crankshaft 42 decreases below the rotation speed of the rotating shaft 41 of the alternator 40, the sprag 14a slides on the cylindrical surfaces 5 and 32, and the pulley 30 moves. The rotation is not transmitted to the rotating shaft 41, and the rotating shaft 41 rotates freely. Therefore, slippage does not occur between the pulley 30 and the belt 44, and wear of the belt 44 and slip noise of the belt 44 can be suppressed.

In the example of use of the clutch built-in type pulley unit shown in FIG. 5, a positive radial clearance is provided between the inner and outer raceway grooves 4 and 31 for guiding rolling of the rolling element 12 made of balls and the rolling element 12. If it is formed, the axial clearance is several times to several tens of times the radial clearance, and the pulley 30 is easy to move in the axial direction. Therefore, the pulley 30
The angular deviation easily occurs with respect to the inner race 1, and the belt 44 cannot be guided stably.

In FIG. 7 (I), the rolling element 1 consisting of a ball
The radial clearance between the inner and outer raceway grooves 4 and 31 and the ball 12 is a negative radial clearance. With this structure, the axial clearance between the ball 12 and the raceway grooves 4 and 31 becomes small, The rigidity of the angular runout of the pulley 30 with respect to the inner race 1 can be increased, and the belt 44 can be guided stably.

Further, in FIG. 7 (II), each of the inner and outer raceway grooves 4 and 31 of the rolling element 12 made of a ball is an angular contact type raceway groove which contacts the rolling element at two points at a total of four points. There is. When the angular contact type raceway grooves 4 and 31 as described above are adopted, the axial clearance formed between the rolling element 12 and the raceway grooves 4 and 31 is as shown in FIG.
Since the value can be suppressed to a value smaller than that shown in (I), the amount of axial movement of the pulley 30 is small, and the rigidity of the angular runout of the pulley 30 with respect to the inner race 1 can be further increased.

Further, raceway grooves 4, 31 for the ball 12
Since the contact angle of is large, the rigidity against thrust load can also be increased.

8 and 9 show the cage 3 and the elastic member 1.
6 shows another example. The cage 3 includes a cage body 3a and a ring-shaped lid 3b attached to one end surface thereof.

Since the same means as that shown in FIG. 3 is used for attaching the lid 3b, the same parts are designated by the same reference numerals and the description thereof will be omitted.

The cage main body 3a is provided with pockets 10 open at one end face in the axial direction and sprag accommodating portions 11 alternately in the circumferential direction, and the rolling elements 12 incorporated in the pockets 10 are provided.
Is prevented from coming off by a protrusion 13 provided on the lid 3b. A sprag 14a is incorporated in the sprag storage portion 11.

The elastic member 16 is composed of a spring ring 16A, and the spring ring 16A is provided with a plurality of holes 18, while a projecting portion 19 is formed on the other end surface of the retainer body 3a.

The spring ring 16A is attached to the other end surface of the retainer body 3a by press-fitting the hole 18 into the protrusion 19 or melting the tip of the protrusion 19 after press-fitting.

On the spring ring 16A, the same number of spring pieces 20 as the sprags 14a are formed by cutting and raising.
0 is inserted into the sprag housing portion 11 through a window 21 formed on the other end surface of the cage body 3a, and presses the sprags 14a in the circumferential direction of the cage 3.

As described above, by using the spring ring 16A having the plurality of spring pieces 20 as the elastic member 16, the number of parts is small and the assembly is easy as compared with the case where the elastic members are individually assembled in the sprag accommodating portion 11. It is simple and the cost can be reduced.

10 to 12 show a third embodiment of the present invention. In this embodiment, an engagement type sprag 14b is used in place of the disengagement type sprag 14a in the first embodiment, and the other configurations are the same as those in the first embodiment. Since the shape is slightly changed and only the elastic member 16 is absent, the same reference numerals are given to the same components and the description thereof will be omitted.

Here, the engagement type sprag 14
As shown in FIG. 12, b is the circumferential direction of the cage 3 at a distance δ from the straight line connecting the contact points a and b with the inner race 1 and the outer race 2 of the arc surface 15 at the inner and outer ends of the sprag 14b. A sprag which has a center of gravity G at a position distant from and is erected by centrifugal force.

In the third embodiment, when the outer race 2 is rotated in the direction of the arrow in FIG. 10, the cage 3 and the outer race 2 are rotated by the contact rotation of the rolling elements 12 with the raceway grooves 6 of the outer race 2. It rotates in the same direction at a lower rotational speed than the outer race 2.

As a result, the sprag 14b revolves at the same number of revolutions as the retainer, but the contact b with the outer race 2 tries to rotate the same as the outer race 2 due to the action of centrifugal force. That is, since the rotation speed of the contact b is faster than that of the contact c with the cage 3, the sprag 14b stands up.

Since it is an engagement type sprag, it automatically stands up when centrifugal force acts on the sprag 14b, and the sprag 14b makes strong contact with the contact point b with the outer race 2 and the contact point a with the inner race 1. As a result, the rotation of the outer race 2 is transmitted to the inner race 1.

When the rotation speed of the inner race 1 becomes faster than the rotation speed of the outer race 2, the sprags 14b fall down to disengage the sprags 14b from the races 1 and 2 and rotate from the outer race 2 to the inner race 1. Transmission is cut off.

When the outer race 2 is rotated in the direction opposite to the arrow in FIG. 10, the rotation of the cage 3 causes the arcuate surfaces 15 at the inner and outer ends of the sprag 14b to form the cylindrical surface 5 of the inner race 1 and the outer race 2. Although the outer race 2 is rotated, the outer race 2 rotates in a direction in which the sprag 14b is tilted. Therefore, the sprag 14b does not engage with the cylindrical faces 5 and 7, and the outer race 2 rotates freely.

By using the engagement type sprag 14b as in the third embodiment, the elastic member 16 in the first embodiment can be omitted, and since the elastic member 16 can be omitted, the clutch can be omitted. The built-in rotating parts can be easily assembled and the cost can be reduced.

Further, since the elastic member 16 can be dispensed with, the contact surface pressure of the sprag 14b against the inner race 1 and the outer race 2 is reduced, the torque during idling can be reduced, and the cage 3 can be reduced. Since it is not necessary to secure a space in which the elastic member 16 is incorporated, it is possible to increase the number of sprags 14b to be incorporated and increase the torque capacity.

Furthermore, since the elastic member 16 is not provided, it is possible to prevent the occurrence of a malfunction due to the resonance of the elastic member 16.

Instead of the outer race 2, a pulley shown in FIG. 5 may be used, or a roller may be used.

FIG. 13 shows a fourth embodiment of the present invention. In this embodiment, a spring accommodating groove 22 is formed in one wall surface 11a of the sprag accommodating portion 11 formed in the cage 3, and an elastic member 16 is incorporated in the spring accommodating groove 22. The sprag 14c is suppressed in the direction in which the sprag 14c is raised, that is, in the direction in which the sprag 14c rotates in the locking direction.

Although the sprag 14c is an engagement type sprag, it may be a disengage type sprag.

As the elastic member 16, the elastic member shown in FIG. 3 may be used, or the elastic member shown in FIG. 9 may be used. When the elastic member 16 shown in FIG. 3 is used,
When the tip of the elastic piece 16b is made to project from the spring housing groove 22 and the elastic member 16 shown in FIG.
The tip of 0 is projected from the spring accommodating groove 22.

As described above, when the rotation speed of the outer race 2 exceeds the rotation speed of the inner race 1 by pressing the sprags 14c by the elastic members 16 in the rising direction, the sprags 14c generate centrifugal force and the elastic members 16 when the rotation speed of the outer races 2 exceeds the rotation speed of the inner race 1.
By both actions due to the pressing of, the inner race 1 and the outer race 2 are immediately locked to the cylindrical surface 5 and the outer race 2, so that the locking performance can be improved.

Further, since the elastic member 16 is provided on the front side in the direction in which the sprag 14c is locked, the sprag 14c tilts in the direction away from the elastic member 16 when the inner race 1 spins above the rotation speed of the outer race 2. The number of times the elastic member 16 bends and bends is reduced, and the durability of the elastic member 16 can be improved.

Further, by inserting the elastic member 16 into the spring accommodating groove 22, it is possible to prevent the elastic member 16 pushed by the sprag 14c from flexing more than necessary during idling.

[0073]

As is evident from the foregoing description, in the invention described in claim 1, the raceway groove provided on the respective inner diameter surface of the outer diameter surface and the outer member of the inner member, forming a cylindrical surface on both sides of the raceway groove However, since the sprag whose length extends over the cylindrical surface is placed between the rolling elements that roll along the raceway groove, the axial length is longer than that in which the rolling element and the sprag are connected in series in the axial direction. Can be made compact.

Further, since the radial load acting on the inner member and the outer member is supported by the rolling elements, almost no radial load acts on the sprags, the clutch can function accurately, and the life of the clutch is increased. It can be extended.

Further, since the rolling element and the sprag can be supported by the common cage, the number of parts is small and the cost can be reduced.

According to the second aspect of the invention, since the spring ring having a plurality of spring pieces is used as the elastic member, the number of parts is smaller than that in the case where the sprag is pressed by each elastic member, and the assembly is performed. It is easy and cost can be reduced.

In the invention described in claim 3, the same effect as in claim 1 can be obtained, and since the engagement type sprag is used as the sprag,
Since the elastic member can be omitted, the assembly of the rotary component with a built-in clutch becomes easy, the cost can be reduced, and the number of sprags to be incorporated into the cage can be increased, resulting in a large torque capacity. The rotating parts can be obtained.

According to the invention described in claim 4, it is possible to obtain a bearing with a built-in clutch which is compact in axial length.

According to the fifth aspect of the present invention, it is possible to obtain a compact clutch built-in type rotary component having an axial length.

In the invention according to claim 6, since the radial runout between the ball and the raceway groove is made negative, the rigidity of the angular runout of the outer member can be increased, and when the outer member is a pulley, the belt Can be guided stably.

According to the seventh aspect of the invention, since the guide raceway axial groove of the rolling element made of a ball has an angular contact type, the angular runout rigidity of the outer member and the rigidity against the thrust load can be increased.

[Brief description of drawings]

FIG. 1 is a first rotary component with a built-in clutch according to the present invention
Sectional view showing an embodiment of

FIG. 2 is a sectional view taken along line II-II in FIG.

FIG. 3 is a partially cutaway plan view of FIG.

FIG. 4 is an exploded perspective view showing a part of the same cage.

FIG. 5 is a cross-sectional view showing a second embodiment of the rotary component with a built-in clutch of the same.

FIG. 6 is a schematic view showing an example of use of the above.

7 (I) and (II) are sectional views showing another example of a raceway groove for guiding the movement of the rolling elements.

FIG. 8 is a partially cutaway front view showing another example of the above retainer and elastic member.

9 is an exploded perspective view of FIG.

FIG. 10 is a sectional view showing a third embodiment of a rotary component with a built-in clutch according to the present invention.

FIG. 11 is an exploded perspective view showing the same cage.

FIG. 12 is a front view showing the same sprag.

FIG. 13 is a sectional view showing a fourth embodiment of a rotary component with a built-in clutch according to the present invention.

FIG. 14 is a sectional view showing a conventional example of a bearing with a built-in clutch.

FIG. 15 is a sectional view taken along line XV-XV in FIG.

[Explanation of symbols]

1 inner race 2 outer race 3 cage 4 orbit grooves 5 Cylindrical surface 6 orbit grooves 7 Cylindrical surface 10 pockets 11 Sprag storage 12 rolling elements 14a, 14b sprag 15 arc surface 16 Elastic member 16A spring ring 20 spring pieces 21 window 30 pulley 31 Track groove 32 cylindrical surface

─────────────────────────────────────────────────── ─── Continuation of the front page (56) Reference JP-A-50-102756 (JP, A) JP-A-2-195029 (JP, A) JP-A-63-285336 (JP, A) JP-A-2- 221744 (JP, A) JP-A-3-282039 (JP, A) Actually open 62-829 (JP, U) Actually open 4-63828 (JP, U) Actually open 5-81523 (JP, U) Actual Development Sho 51-9146 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16D 41/00-47/06

Claims (7)

(57) [Claims] 1. An outer diameter surface of an inner member fixed to a shaft, a raceway groove on each inner diameter surface of a cylindrical outer member provided outside the inner member, and a cylindrical surface on both sides of the raceway groove. And a plurality of rolling elements are incorporated between the raceway grooves, and a sprag having a length that extends between the cylindrical surfaces on both sides of the raceway groove is arranged between the rolling elements, and a pocket in which the rolling element is accommodated And a cage having a sprag accommodating portion for accommodating the sprag are incorporated between the inner member and the outer member, and the arcuate surfaces of the inner and outer ends of the sprag engage with the cylindrical surfaces on both sides of the inner member and the outer member. A rotating part with a built-in clutch that presses the sprags in the mating direction with an elastic member. 2. A window in which the elastic member comprises a spring ring attached to the end surface of the retainer, and spring pieces of the same number as the sprags are cut and raised on the spring ring, and each spring piece is provided on the end surface of the retainer. The rotary component with a built-in clutch according to claim 1, wherein the sprag is pressed by inserting the sprag into the sprag storage portion. 3. An outer diameter surface of an inner member fixed to a shaft, a raceway groove on each inner diameter surface of a cylindrical outer member provided outside the inner member, and cylindrical surfaces on both sides thereof. A plurality of rolling elements are incorporated between the raceway grooves, and a sprag having a length spanning between the cylindrical surfaces on both sides of the raceway groove is arranged between the rolling elements, and a pocket for accommodating the rolling element and a sprag. A cage having a sprag accommodating portion for accommodating is housed between an inner member and an outer member, and the sprag is erected by centrifugal force so that a part of the arcuate surface at the inner and outer ends is an inner member and an outer member. Both sides of
Rotating parts with a built-in clutch consisting of an engagement type sprag that contacts the cylindrical surface of. 4. The clutch built-in rotating component according to claim 1, wherein the outer member is an outer race for a bearing. 5. The clutch-embedded rotary component according to claim 1, wherein the outer member is a belt guide pulley having a raceway groove and a cylindrical surface. 6. The clutch-embedded rotary component according to claim 1, wherein the rolling element is a ball, and the radial clearance between the ball and the inner and outer raceway grooves is negative. 7. The rolling element comprises a ball, and each of the inner and outer raceway grooves for guiding the movement of the ball is an angular contact type raceway groove which comes into contact with the ball at four points. The rotating part with a built-in clutch described in 1 above.