JP2003232386A - One-way clutch and pulley device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve such problems that when a wedge angle of one-way clutch is set small, a torque transmission performance becomes worse, and when the wedge angle is set great to improve the torque transmission performance, timing of intermeshing in a guide face for each roller is shifted, and intermeshing performance lowers. <P>SOLUTION: There are provided a first clutch function part 18 and a second clutch function part 19 whose wedge angles θ1 and θ2, are different respectively. The wedge angel θ1 at the first clutch function part 18 of a pulley 11 side is set small, the wedge angle θ2 at the second clutch function part 19 of a power generating driving shaft 2 side is set greater than the wedge angle θ1 at the first clutch function part 18 so that the one-way clutch 10 which is excellent in intermeshing performance and torque transmission performance can be accomplished, and rotational driving force of the pulley 11 can be securely transmitted to the power generating driving shaft 2 without loss. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a one-way clutch and a pulley device equipped with this one-way clutch.

[0002]

2. Description of the Related Art Generally, in an automobile, a part of engine output is used as a power source to drive auxiliary equipment such as a compressor for an air conditioner, a cooling fan and an alternator (generator). A pulley device for power transmission is provided on each of the crankshaft of the engine and the drive shaft of the auxiliary device, and a belt is wound between the pulley devices. The rotation of the belt transmits power from the engine to the auxiliary equipment. Fluctuations in the tension of the power transmission belt affect the efficient transmission of power. In order to suppress such tension fluctuations in the belt, a one-way clutch may be built in the pulley device of the auxiliary machine.

A pulley device will be described below with reference to FIG. 5 by taking an alternator, which is an example of an auxiliary machine, as an example. 70
Is a one-way clutch, 71 is a pulley, and 72 is a power generation drive shaft.

The one-way clutch 70 includes an inner ring member 70.
a, the outer ring member 70b, the cage 70c, and the rollers 70d
And a coil spring 70e.

The outer peripheral surface of the inner ring member 70a has a plurality of flat cam surfaces 70f. The retainer 70c has a plurality of pockets 70f formed at positions facing the cam surface 70f of the inner ring member 70a. A wedge-shaped space 70g is formed between the cam surface 70f and the inner peripheral surface of the outer ring member 70b.

The roller 70d is moved by the coil spring 70e.
It is urged toward the narrow side of the wedge-shaped space 70g. Around 7
The angle of the intersection C at which the tangent line A between 0d and the cam surface 70f and the tangent line B between the roller 70d and the inner peripheral surface of the outer ring member 70b intersect is referred to as a wedge angle θ.

The inner ring member 70a and the outer ring member 70 are in a state in which the roller 70d is engaged with the narrow side of the wedge-shaped space 70g.
b is in a locked state in which it is integrally rotated around the axis through the roller 70d. The state where the roller 70d is disengaged toward the wider side of the wedge-shaped space 70g is a free state in which the inner ring member 70a and the outer ring member 70b are relatively rotated about the axis.

In such a one-way clutch 70,
The inner ring member 70a is externally fitted and fixed to the power generation drive shaft 72, and the pulley 71 is externally fitted and fixed to the outer ring member 70b. A belt for power transmission (not shown) is wound around the pulley 71.

In the above structure, the outer ring member 70b is rotated around the axis by the rotation of the belt, and the roller 70d is engaged with the narrow side of the wedge-shaped space 70g (the roller 70d and the cam surface 70f of the inner ring member 70a and the outer ring member 70b). Of the inner ring member 70a), the inner ring member 70a and the outer ring member 70b rotate integrally with each other around the axis, and the power from the engine is transmitted to the drive shaft 72 for power generation.

By the way, when the rotation speed of the belt suddenly decreases, the outer ring member 70b rotates integrally with the belt, so that the rotation speed also rapidly decreases, but the roller 70d has a narrower side of the wedge-shaped space 70g due to inertial force. To the wide side. Since inertial force also acts on the inner ring member 70a,
The power generation drive shaft 72 is in a state in which the power from the engine is cut off, and maintains the rotation around the axis at a speed substantially equal to the rotation speed before the rotation speed of the belt decreases.

[0011]

By the way, in the one-way clutch 70 having the above-described structure, when the wedge angle θ is small, the roller 70d can be engaged with the narrow side of the wedge-shaped space 70g. Cam surface 7 of inner ring 70a
The biting property of 0f and the inner peripheral surface of the outer ring member 70b is good. On the other hand, it is inferior in power transmission to transmit rotational torque.

For example, in the pulley device as described above, it is desirable to satisfy both functions of biting property and power transmission property. However, the above conventional one-way clutch 7
Since 0 has only one wedge angle θ, it was difficult to satisfy both functions of biting property and power transmission property.

[0013]

In order to solve the above problems, a one-way clutch according to claim 1 of the present invention has a plurality of clutch function parts, and each of the clutch function parts includes:
Each includes an outer ring member, an inner ring member arranged radially inward of the outer ring member, and a wedge member arranged between the outer ring member and the inner ring member, wherein each of the clutch function parts, the wedge member is In a locked state in which the outer ring member and the inner ring member rotate in synchronism with each other around the axis by being meshed between the outer ring member and the inner ring member, and the wedge member releases the mesh and the outer ring member and the inner ring member rotate around the axis center. The clutch function parts are arranged concentrically with each other inside and outside in the radial direction, and the rotation directions in the locked state are the same direction.
The wedge angles formed by the two tangents at the point where the wedge member contacts the inner peripheral surface of the outer ring member and the outer peripheral surface of the inner ring member are set to be different.

In the above structure, for example, when the outer ring member in the radially outer clutch function portion rotates around the axis, the wedge member in this clutch function portion is locked between the outer ring member and the inner ring member by meshing. The inner ring member in the clutch function portion rotates around the axis.
Then, along with this, the outer ring member of the radially inner clutch function portion rotates around the axis, and the wedge member in this clutch function portion is caught between the outer ring member and the inner ring member to be in a locked state. The inner ring member in the clutch function unit rotates around the axis. As a result, the rotational driving force around the axis is transmitted from the radially outer clutch function portion to the radially inner clutch function portion.

Since the wedge angles of the respective clutch function parts are set to different angles, the mesh function and the torque function of the clutch function part having an excellent meshing property and the clutch function part having an excellent torque transmitting property are achieved. It is a one-way clutch with excellent transmission.

By the way, for example, when the rotational speed around the axis of the outer ring member suddenly decreases in the radially outer clutch function portion, the wedge member of the clutch function portion disengages due to inertial force, and the clutch is released. Due to the inertial force, the inner ring member of the functional portion is independently rotated from the outer ring member of the clutch functional portion to independently rotate around the axis. Further, the wedge member in the clutch function portion on the radially inner side releases the engagement, and the inner ring member is brought into a free state in which the inner ring member rotates about the axis center due to the inertial force. As a result, even if the rotational speed around the shaft center in the radially outer clutch function portion suddenly decreases, the inner ring member in the radially inner clutch function part has a rotational speed around the shaft center of the outer clutch function portion. It rotates around the axis while maintaining the same rotation speed as before it decreased.

Further, in the one-way clutch according to claim 2, in the one-way clutch according to claim 1, the wedge angle of the radially outer clutch function portion is larger than that of the radially inner clutch function portion. While being set small, the clutch function portion on the radially outer side is the driving side, and the clutch function portion on the radially inner side is the driven side.

In the above structure, when the outer ring member in the radially outer clutch function portion is driven to rotate about the axis,
The wedge member in the clutch function portion is engaged with the narrow side of the wedge-shaped space to be in a locked state, and the inner ring member in the clutch function portion rotates about the axis. Along with this, the wedge member in the radially inner clutch function part engages with the narrow side of the wedge-shaped space, and the radially inner clutch function part locks slightly behind the radially outer clutch function part. The drive side rotation is transmitted to the driven side. In this way, when the rotation on the drive side is transmitted to the driven side, the radially outer clutch function portion, which is arranged on the drive side and has an excellent meshing property, is first in the locked state, and subsequently, the torque transmission property is excellent. The clutch function portion on the inner side in the radial direction is in a locked state with a slight delay. As a result, the one-way clutch is excellent in both meshability and torque transmissibility.

Further, in the one-way clutch according to claim 3, in the one-way clutch according to claim 1, the wedge angle of the clutch function portion on the radially inner side is larger than the wedge angle of the clutch function portion on the radially outer side. While being set small, the clutch function portion on the radially inner side is the driving side, and the clutch function portion on the radially outer side is the driven side.

In the above structure, when the inner ring member in the radially inner clutch function portion is driven to rotate about the axis,
The wedge member of the clutch function portion is locked in the narrow side of the wedge-shaped space by locking, and the outer ring member of the clutch function portion rotates about the axis. Along with this, the wedge member in the radially outer clutch function part bites into the narrow side of the wedge-shaped space, and the radially outer clutch function part locks slightly behind the radially inner clutch function part. The drive side rotation is transmitted to the driven side. In this way, when the rotation on the drive side is transmitted to the driven side, the radially outer clutch function portion, which is arranged on the drive side and has an excellent meshing property, is first in the locked state, and subsequently, the torque transmission property is excellent. The clutch function portion on the inner side in the radial direction is in a locked state with a slight delay. As a result, the one-way clutch is excellent in both meshability and torque transmissibility.

The one-way clutch according to claim 4 is the one-way clutch according to any one of claims 1 to 3, wherein the inner ring member of the predetermined clutch function part has a diameter of the clutch function part. It is also used as an outer ring member of another clutch function portion arranged on the inner side in the direction.

According to this structure, since it is not necessary to provide the outer ring member and the inner ring member for each clutch function portion, the structure is simpler and the cost is lower than that of the one-way clutch in which the outer ring member and the inner ring member are separate members. Will be reduced.

In order to solve the above-mentioned problems, a pulley device according to a fifth aspect of the present invention is such that the one-way clutch and the bearing according to any one of the first to fourth aspects are wrapped around a power transmission belt. Is disposed between the pulley and the shaft body.

According to this structure, when the power transmission belt rotates and the pulley rotates about the shaft center, and the outer ring member in the radially outer clutch function portion rotates about the shaft center accordingly, The wedge member in the clutch function unit is locked between the outer ring member and the inner ring member by locking, and the inner ring member in the clutch function unit rotates around the axis. Along with this, the outer ring member of the radially inner clutch function part rotates around the axis, and the wedge member in this clutch function part is locked between the outer ring member and the inner ring member by locking. The rotational driving force around the axis is transmitted from the clutch function portion on the radially outer side to the clutch function portion on the radially inner side, and further to the shaft body such that the inner ring member in is rotated around the axis center.

Since the wedge angles of the respective clutch function parts are set to different angles, the shaft body is centered by the clutch function part having excellent meshing properties and the clutch function part having excellent torque transmission properties. Make sure to rotate without any loss.

By the way, if the rotational speed of the power transmission belt is drastically reduced and the rotational speed around the shaft center of the outer ring member in the pulley and the radially outer clutch function portion is drastically reduced, the The wedge member of the clutch function section releases the engagement due to the inertial force. In addition, the inner ring member of the clutch function section independently becomes independent of the outer ring member of the clutch function section by the inertial force and becomes a free state in which it rotates around the axis, and the wedge member of the clutch function section on the radially inner side is caught. When released, the inner ring member is in a free state in which it is rotated around the axis by the inertial force. This allows
Even if the rotational speed of the power transmission belt suddenly decreases, the shaft body rotates about the axis while maintaining the same rotational speed as before the rotational speed of the power transmission belt decreased.

Further, since the wedge angle of the radially outer clutch function portion is set smaller than the wedge angle of the radially inner clutch function portion, the rotation of the power transmission belt is transmitted to the shaft body. At this time, the clutch function part on the drive side located on the outside in the radial direction, which has excellent meshing characteristics, is locked first, and then the clutch function part on the inside in the radial direction, which has excellent torque transmission, is locked after a slight delay. Become. As a result, the shaft can be reliably rotated around the axis without loss.

[0028]

DETAILED DESCRIPTION OF THE INVENTION The details of the present invention will be described below with reference to the embodiments shown in the drawings. The one-way clutch of this embodiment is applied to a pulley device for rotationally driving a power generation drive shaft of an alternator mounted on a vehicle. (First Embodiment) With reference to FIGS. 1 and 2, a pulley device including a one-way clutch according to a first embodiment of the present invention will be described. 1 is a side sectional view of the pulley device, and FIG. 2 is a front sectional view of the pulley device.

Reference numeral 1 is a pulley device, 2 is a drive shaft (an example of a shaft) for power generation of an alternator, 3 is a belt, 4 is an alternator main body, and 5 is a rolling bearing.

The pulley device 1 is attached to the free end side end of the power generation drive shaft 2 and has a function of transmitting the driving force of the automobile engine via the belt 3 to the power generation drive shaft 2. The power generation drive shaft 2 is supported on the alternator main body 4 via the rolling bearing 5 so as to be rotatable about an axis 6.

The pulley device 1 includes a pulley 1 having a wavy circumferential groove 12 around which a belt 3 is wound.
1 and the outer ring body 7 in which the pulley 11 is press fitted.
An inner ring body 8 arranged concentrically with the outer ring body 7, a one-way clutch 10 interposed in an annular space between the two ring bodies 7, 8, and a one-way clutch 10 in the annular space.
Two rolling bearings (general deep groove ball bearings are used) 5A, 5A arranged on both sides in the axial direction of the.

The outer ring body 7 has a shaft center 6 at both ends thereof.
A thin extension portion 13 is formed extending in the direction. Both rolling bearings 5A are press-fitted into an annular space between both the extended portions 13 of the outer ring body 7 and the inner ring body 8 in the axial direction 6 direction. With this configuration, the one-way clutch 10 and the two rolling bearings 5A are unitized.

A center hole 14 is formed in the inner ring body 8, and a female screw portion 15 is formed in the middle of the center hole 14. On one side of the center hole 14, a rotary operation recess 16 into which a rotary operation tool (not shown) is fitted is formed.
On the inner peripheral surface of the rotary operation recessed portion 16, serrations which are formed of a large number of triangular teeth and which mesh with the rotary operation tool are formed.

The power generation drive shaft 2 is inserted into the center hole 14 from one side. A male screw portion 17 is formed at the tip of the drive shaft 2 for power generation, and this male screw portion 17 is the female screw portion 1 described above.
5 is screwed together.

The one-way clutch 10 has a function of interrupting or transmitting rotational power from the outer ring body 7 to the inner ring body 8 in accordance with a difference in rotational speed between the outer ring body 7 and the inner ring body 8. Have. Therefore, the one-way clutch 10 has a plurality of clutch function parts 18, 19 in this embodiment.

The first clutch function portion 18 is arranged radially outside and the second clutch function portion 19 is arranged radially inside the first clutch function portion 18. Both clutch function parts 18 and 19 are set so that the rotation directions in the locked state and the free state are the same.

Both clutch function parts 18 and 19 have cylindrical outer ring members 22 and 23 and inner ring members 25 and 26 which are arranged inside and outside in the radial direction, respectively. Both clutch function parts 18 and 19 further include rollers (an example of a wedge member) 31,
32, retainers 37 and 38, and coil springs 40 and 41.

The rollers 31, 32 are the outer ring members 22, 2
3 and the inner space of the outer ring members 25 and 26 are arranged in a plurality of circumferential directions (eight in the figure) in the annular space between the inner ring members 25 and 26. (Outer ring raceway surface) and the outer peripheral surfaces of the inner ring members 25, 26 are arranged as inner guide surfaces.

The cages 37 and 38 are respectively the inner ring member 2
5, 26 and the outer ring members 22, 23 are arranged in an annular space. These cages 37 and 38 allow the rollers 31 and 32 to roll at the circumferentially equidistant positions, respectively, in the pockets 34,
It is attached to 35.

Incidentally, the pockets 34 of the cages 37 and 38,
35 is a holder 37, 38 at a position corresponding to the cam surface.
Is formed so as to penetrate inside and outside in the radial direction.

Slit-shaped recesses 52, 5 are provided at two locations on one end face in the circumferential direction of the inner ring members 25, 26 facing each other by 180 °.
3 is formed. Both the recesses 52, 53 are open toward the shaft end and open inward and outward in the radial direction. The cages 37 and 38 have the convex portions 55 and 56 that fit into the concave portions 52 and 53, and the cages 37 and 38 have the concave portions 52 and 53.
It is fixed to the inner ring members 25 and 26 by fitting 53 and the convex portions 55 and 56, respectively. Thereby, the holders 37, 38
Is in the circumferential direction with respect to the inner ring members 25 and 26 and the axis 6
The movement in the direction is restricted.

The outer ring body 7 is also used as the outer ring member 22 of the first clutch function portion 18. First clutch function part 1
The inner ring member 25 of No. 8 is also used as the outer ring member 23 of the first clutch function part 19.

In both clutch function parts 18 and 19, the inner peripheral surfaces 43 and 44 of the outer ring members 22 and 23, which are the outer guide surfaces of the rollers 31 and 32, are formed into cylindrical surfaces. Around 3
Outer peripheral surface 4 of inner ring member 25, 26 which is a guide surface of 1, 32
6 and 47 are polygonal shapes (8 in the figure) having a flat cam surface.
It has a rectangular shape and a rectangular cylindrical surface. Wedge-shaped space 28, 2
9 is formed by the cylindrical surfaces of the outer ring members 22 and 23 and the cam surfaces of the inner ring members 25 and 26. Wedge-shaped space 2
In Nos. 8 and 29, the radial height on both sides in the circumferential direction is narrower than the radial height at the center position in the circumferential direction.

As the coil springs 40 and 41 in both the clutch function portions 18 and 19, square springs formed by winding a spring wire into a rectangular shape are used. These coil springs 4
0 and 41 are pockets 3 of the cages 37 and 38, respectively.
4 and 35 are stored in a compressed state and externally fitted to projections 58 and 59 that are integrally formed on the inner surfaces of the pockets 34 and 35 of the cages 37 and 38 toward one side in the circumferential direction.
Rollers 31, 32 in each clutch function part 18, 19
Is a clockwise direction B1, that is, the wedge-shaped spaces 28, 2 due to the extension restoring forces of the coil springs 40, 41, respectively.
It is biased to the narrow side of 9 (lock side).

The diameter of the roller 32 of the second clutch function portion 19 is smaller than the diameter of the roller 31 of the first clutch function portion 18. The wedge angles θ1 and θ2 are set to different angles. Here, the wedge angle θ1 of the first clutch function portion 18 is set to be smaller than the wedge angle θ2 of the second clutch function portion 19. Note that the wedge angles θ1 and θ2 are
Is the angle formed by the two tangents 60a, 60b, 61a, 61b at the point of contact with the outer and inner guide surfaces.

In the above-described structure, when the crankshaft (not shown) rotates with the driving of the engine and the rotation is transmitted to the drive shaft 2 for power generation through the belt 3, for example, the pulley 11 moves counterclockwise in FIG. Axis 6 in direction A1
Rotate around.

When the pulley 11 rotates in the counterclockwise direction A1 about the axis 6, the outer ring member 22 (outer ring body 7) of the first clutch function portion 18 is accordingly rotated in the counterclockwise direction. Rotate to A1. Then, the roller 31 of the first clutch function portion 18 is engaged with the narrow side of the wedge-shaped space 28, and the first clutch function portion 18 causes the outer ring member 22, the roller 31 and the inner ring member 25 to integrally form around the shaft center 6. It will be in a locked state to rotate.

Further, the first clutch function part 18 is locked and the inner ring member 25 of the first clutch function part 18 is locked.
When the (outer ring member 23 of the second clutch function part 19) rotates counterclockwise A1, the rollers 3 of the second clutch function part 19 are rotated.
2 is engaged with the narrow side of the wedge-shaped space 29 to be in a locked state, and the roller 32 and the inner ring member 26 of the second clutch function portion 19 rotate integrally around the shaft center 6. As a result, the inner ring body 8 rotates counterclockwise. By rotating the inner ring body 8 in the counterclockwise direction A1 in this manner, the rotation of the pulley 11 around the shaft center 6 is transmitted to the power generation drive shaft 2, and the alternator performs power generation drive.

By the way, in this embodiment, the diameter of the roller 32 of the second clutch function portion 19 is made smaller than the diameter of the roller 31 of the first clutch function portion 18, and the wedge angle of the second clutch function portion 19 is formed. The wedge angle θ1 of the first clutch function portion 18 is set smaller than θ2.

As described above, with respect to the wedge angle, the smaller the wedge angle, the easier the timing when the roller meshes with the outer guide surface and the inner guide surface (locking state), and the meshing of the rollers. Is excellent. However, on the other hand, if the wedge angle is small, the drive shaft 2 for power generation will start from the pulley 11 side.
The torque transmission to the side is poor.

Therefore, in the embodiment of the present invention, since the wedge angle θ1 of the first clutch function portion 18 is set to be smaller than the wedge angle θ2 of the second clutch function portion 19, the meshing of the rollers is made. The second clutch function part 19
The first clutch function part 18 is superior to the first clutch function part 18, and the torque transmissibility of the second clutch function part 19 is superior to the first clutch function part 18.

As described above, the first clutch function portion 18 and the second clutch function portion 19 having different wedge angles θ1 and θ2 are provided to reduce the wedge angle θ1 in the first clutch function portion 18 on the pulley 11 side. Wedge angle θ2 in the second clutch function section 19 on the power generation drive shaft 2 side
Is set to be larger than the wedge angle θ1 in the first clutch function portion 18. With this configuration, the rotation of the pulley 11 about the shaft center 6 is first transmitted to the first clutch function section 18 having good meshability, and slightly delayed to the second clutch function section 19 having excellent torque transferability. Will be transmitted. Therefore, the one-way clutch 10 is excellent in both meshability and torque transmissibility, and the rotational drive force of the pulley 11 can be reliably transmitted to the power generation drive shaft 2 without loss.

By the way, the belt 3 is wound around the pulley 11, and the pulley 11 rotates integrally with the rotation of the belt 3. Therefore, when the tension of the belt 11 fluctuates and the rotation speed of the belt 3 suddenly decreases, for example,
Along with this, the rotation speed of the pulley 11 around the shaft center 6 decreases.

However, the pulley 11 and the drive shaft 2 for power generation are connected via the one-way clutch 10, and the inner ring member 26 of the second clutch function portion 19 is rotationally integrated with the inner ring body 8. The rotation of the belt 3 and the rotation of the drive shaft 2 for power generation are released from the integral rotation state. That is, the pulley 1
When the rotation speed of No. 1 suddenly decreases, inertial force acts on the first clutch function portion 18, whereby the rollers 31 of the first clutch function portion 18 that are engaged with the outer guide surface and the inner guide surface are When the wedge-shaped space 28 is disengaged from the wide side, the first clutch function portion 18 is in a free state. As a result, the rotation speed of the inner ring member 25 around the shaft center 6 is higher than the rotation speed of the pulley 11 around the shaft center 6 while maintaining the rotation speed substantially equal to the rotation speed of the pulley 11 before the decrease. .

Such inertial force is generated by the drive shaft 2 for power generation.
The same applies to (the inner ring member 26 of the second clutch function portion 19), and the rollers 32 of the second clutch function portion 19 that have been engaged with the outer guide surface and the inner guide surface are disengaged to the wider side of the wedge-shaped space 29. As a result, the second clutch function section 19 becomes free. As a result, the rotation speed of the power generation drive shaft 2 around the shaft center 6 maintains a rotation speed substantially equal to the rotation speed of the pulley 11 before the reduction, and is lower than the rotation speed of the pulley 11 around the shaft center 6. Get faster

As described above, even when the rotation speed of the pulley 11 decreases, the rotation of the power generation drive shaft 2 around the axis 6 continues at a rotation speed substantially equal to that before the rotation speed of the pulley 11 decreases. As a result, the inertial force causes the belt 3 to rotate, which changes the tension of the belt 3 and causes the pulley 11 to rotate.
Even if the rotation speed of No. 2 suddenly decreases, the rotation speed around the shaft center 6 of the power generation drive shaft 2 can be maintained in a nearly constant state, and efficient and stable charging can be performed.

As described above, according to the first embodiment of the present invention, the wedge angle θ1 in the first clutch function portion 18 on the pulley 11 side (driving side) is set to be small and the power generation drive shaft 2 side ( By setting the wedge angle θ2 in the second clutch function part 19 on the driven side to be larger than the wedge angle θ1 in the first clutch function part 18, the one-way clutch 10 is excellent in both meshing property and torque transmissibility. , The rotation driving force of the pulley 11 is ensured without loss, and the power generation drive shaft 2
Can be transmitted to. Second Embodiment Next, a second embodiment of the present invention will be described based on the front sectional view of FIG. The one-way clutch 10 in the pulley device 1 of the first embodiment described above has the first clutch function part 1 on the radially outer side.
8 is provided, and the second clutch function part 19 is provided radially inside of the first clutch function part 18.
The inner peripheral surface 43 of the outer ring member 22 of No. 8 is formed into a cylindrical surface, and the outer peripheral surface 46 of the inner ring member 25 of the first clutch function portion 18 is formed.
As the cam surface, the inner peripheral surface 44 of the outer ring member 23 of the second clutch function portion 19 is formed as a cylindrical surface, and the outer peripheral surface 47 of the inner ring member 26 of the second clutch function portion 19 as the cam surface. The wedge angle θ1 of the first clutch function unit 18 is set to be smaller than the wedge angle θ2 of the function unit 19.

On the other hand, in the one-way clutch 10 used in the pulley device 1 according to the second embodiment of the present invention, the first clutch function portion 18 is provided on the radially outer side, and the diameter of the first clutch function portion 18 is increased. The second clutch function part 19 is provided on the inner side in the direction, the inner peripheral surface 43 of the outer ring member 22 of the first clutch function part 18 is used as a cam surface, and the outer peripheral surface 46 of the inner ring member 25 of the first clutch function part 18 is formed. The inner peripheral surface 4 of the outer ring member 23 of the second clutch function portion 19 is a cylindrical surface.
4 is a cam surface, and the outer peripheral surface 47 of the inner ring member 26 of the second clutch function portion 19 is a cylindrical surface.

As a result, a plurality of wedge-shaped spaces 28 are formed between the outer ring member 22 and the inner ring member 25 of the first clutch function part 18, and the outer ring member 23 and the inner ring member 26 of the second clutch function part 19 are formed. A plurality of wedge-shaped spaces 2 between
9 is formed. Therefore, in the second embodiment of the present invention, the wedge-shaped spaces 28, 29 are formed such that the radial heights on both sides in the circumferential direction are higher than the radial height at the center position in the circumferential direction. There is.

The diameter of the roller 31 of the first clutch function section 18 is different from that of the roller 32 of the second clutch function section 19.
Is formed to have a small diameter, and the two tangents 60 at the points where the rollers 31 and 32 contact the outer guide surface and the inner guide surface, respectively.
wedge angle θ formed by a, 60b, 61a, 61b
1 and θ2 are different. Here, similarly to the first embodiment, the wedge angle θ1 of the first clutch function portion 18 is set to be smaller than the wedge angle θ2 of the second clutch function portion 19.

The coil springs 40 and 41 in the clutch function portions 18 and 19 are integrally formed on the inner surfaces of the pockets 34 and 35 of the cages 37 and 38, respectively, with the projections 58, which are integrally formed toward the other side in the circumferential direction. It is externally attached to 59. In addition, the rollers 3 in the clutch function parts 18 and 19
1, 32 are biased in the same direction in the circumference (counterclockwise direction A1) by coil springs 40, 41, respectively. With such a configuration, both clutch function parts 18, 19
The rotation directions of the locked state and the free state are the same.

Further, in the first embodiment, each cage 3 is
7 and 38 are formed integrally with the inner ring members 25 and 26 so as to rotate integrally therewith. On the other hand, although not shown, in the second embodiment of the present invention, the cages 37 and 38 are attached to the outer ring members 22 and 23, respectively, so as to rotate together. Other configurations are similar to those of the first embodiment described above, and thus description thereof will be omitted.

In the above structure, when the pulley 11 rotates clockwise about the shaft center 6 in the clockwise direction B1, the first clutch function unit 1
The roller 31 of No. 8 is engaged with the narrow side of the wedge-shaped space 28 to be in the locked state, and the roller 32 of the second clutch functional section 19 is engaged with the narrow side of the wedge-shaped space 29 to be in the locked state. The inner ring member 26 (inner ring 8) of 19 rotates around the axis 6. In this way the pulley 1
The rotation about the shaft center of 1 is transmitted to the drive shaft 2 for power generation, and the power generation drive is performed.

Since the wedge angle θ1 in the first clutch function portion 18 on the pulley 11 side is smaller than the wedge angle θ2 in the second clutch function portion 19 on the power generation drive shaft 2 side, the axial direction of the pulley 11 side. The rotation of is first transmitted to the drive shaft 2 for power generation after the first clutch function portion 18 is locked and then the second clutch function portion 19 is locked with a slight delay.

A first clutch function section 18 and a second clutch function section 19 having different wedge angles θ1 and θ2 are provided to reduce the wedge angle θ1 in the first clutch function section 18 on the pulley 11 side to drive the power generation. By setting the wedge angle θ2 in the second clutch function portion 19 on the shaft 2 side to be larger than the wedge angle θ1 in the first clutch function portion 18, the one-way clutch 10 excellent in both meshability and torque transmissibility is obtained, The rotational drive force of the pulley 11 can be reliably transmitted to the power generation drive shaft 2 without loss.

By the way, for example, when the rotation speed of the pulley 11 is drastically reduced, an inertial force acts on the first clutch function portion 18 so that the rollers 31 of the first clutch function portion 18 move toward the wider side of the wedge-shaped space 28. First clutch function unit 18
Is in a free state, and its inertial force also acts on the drive shaft 2 for power generation and the second clutch function part 19, so that the rollers 32 of the second clutch function part 19 disengage to the wide side of the wedge-shaped space 29 and the second clutch function. The section 19 becomes free.

As described above, the first clutch function portion 18 and the second clutch function portion 19 are in the free state, so that even if the rotation speed of the pulley 11 is drastically reduced, the pulley for the power generation drive shaft 2 is reduced. The rotation around the axis 6 is continued at a rotation speed almost equal to that before the rotation speed of the rotation shaft 11 decreases. As a result, even if the tension of the belt 3 changes and the rotation speed of the pulley 11 suddenly decreases, the rotation speed around the shaft center 6 of the power generation drive shaft 2 is maintained in a nearly constant state and is efficiently stabilized. Can be charged. (Third Embodiment) Next, a third embodiment of the present invention will be described based on the front sectional view of FIG. In the second embodiment, the one-way clutch 10 includes the first clutch function portion 18 on the radially outer side and the second clutch function portion 19 on the radially inner side.
Is configured. On the other hand, in the one-way clutch 10 used in the pulley device 1 according to the third embodiment of the present invention, the third clutch function portion 20 is provided further inside in the radial direction than the second clutch function portion 19. .

The third clutch function section 20 has an outer ring member 24, an inner ring member 27, rollers 33, a cage 39 and a coil spring 42. Then, the outer ring member 24
Is also used as the inner ring member 26 of the second clutch function part 19, and the inner ring member 27 of the third clutch function part 20 is
It is fitted onto the inner ring 8 (see FIG. 1).

The wedge angle θ3 formed by the two tangents 62a and 62b at the point where the roller 33 in the third clutch function portion 20 contacts the outer guide surface and the inner guide surface.
, The diameter of the roller 33 is determined so as to be larger than the wedge angle θ2 in the second clutch function portion 19. The inner peripheral surface of the outer ring member 24 in the third clutch function portion 20 is a cam surface, and the outer peripheral surface of the inner ring member 27 is a cylindrical surface.

Then, in the third embodiment of the present invention, the cages 37, 38, 39 respectively include the outer ring members 22, 2 respectively.
It is attached to 3 and 24 integrally.

As the coil spring 42 in the third clutch function portion 20, a rectangular coil spring formed by winding a spring wire into a rectangular shape is used, and is integrally formed on the inner surface of the pocket 36 of the cage 39 toward one side in the circumferential direction. Is fitted onto the protrusion 60, and the rollers 33 in the third clutch function portion 20 are
Is urged in the counterclockwise direction A1 by the coil spring 42.

Further, the rotation directions in which the respective clutch function parts 18, 19, 20 are in the locked state and the free state are set to be the same. The other configurations are similar to those of the second embodiment, and therefore their explanations are omitted.

In the above-mentioned structure, the rotation of the pulley 11 in the clockwise direction B1 is transmitted to the first clutch function part 18, the second clutch function part 19 and the third clutch function part 20 with a slight delay, and the power is generated. The drive shaft 2 rotates around the shaft center 6 to drive power generation.

At this time, the wedge angle θ3 in the third clutch function portion 20 is larger than the wedge angle θ2 in the second clutch function portion 19, so that
Compared to the second embodiment described above, the pulley 11 can be more reliably connected.
It is possible to transmit the rotation driving force of the above to the power generation drive shaft 2.

When the rotation speed of the pulley 11 is reduced, the rollers 31 in the first clutch function portion 18 are disengaged from the wide side of the wedge-shaped space 28 to be in a free state, and the inertia force is generated by the power generation drive shaft 2, The second clutch function unit 19 and the third clutch function unit 20 also work, and the second clutch function unit 1
The roller 32 of 9 disengages to the wide side of the wedge-shaped space 29 and the second clutch function portion 19 becomes free, and the roller 33 of the third clutch function 20 disengages to the wide side of the wedge-shaped space 30 to cause the third clutch. The function part 20 becomes free,
Even if the rotation speed of the pulley 11 decreases, in the power generation drive shaft 2, the rotation around the axis 6 is continued in the clockwise direction B1 at a speed substantially equal to the rotation speed before the rotation speed of the pulley 11 decreases. It is possible to rotate and maintain the rotation speed around the shaft center 6 of the power generation drive shaft 2 at a substantially constant state to perform stable charging.

In each of the above-mentioned embodiments, the outer ring body 7 (pulley 11) is the driving side, and the inner ring body 8 (power generation drive shaft 2) is the driven side, and the wedge in the clutch function portion provided on the radially inner side. The angle is set to be larger than the wedge angle in the clutch function portion on the radially outer side, but the present invention is not limited to this.

That is, the present invention can be applied to a device having a structure in which the inner ring body 8 is on the driving side and the outer ring body 7 is on the driven side. In this case, for example, by changing the size of the rollers of each clutch function part, the inner side in the radial direction is changed. The wedge function is set to increase in order from the clutch function section to the radially outer clutch function section. As a result, the clutch function portion on the radially inner side is brought into the locked state, and the clutch function portion on the radially outer side is brought into the locked state with a slight delay, and both the meshing property and the torque transmissibility are brought into the same manner as in the above embodiments. The excellent one-way clutch can reliably transmit the driving force of the inner ring body 8 to the outer ring body 7 without loss.

In each of the above embodiments, the cam surface is a flat surface, but the present invention is not limited to this, and although not shown,
Form the cam surface into a curved surface with a different curvature than the cylindrical surface,
The curved surface and the cylindrical surface may be set to have different wedge angles in the clutch function portion inside and outside in the radial direction, and in this case also, the same effect as each of the above embodiments can be obtained.

Further, in each of the above embodiments, the roller is used as the wedge member, but the present invention is not limited to this, and although not shown, the present invention is a one-way clutch or pulley using a sprag as the wedge member. It can also be applied to an apparatus, and in this case as well, the same operational effects as those of the above embodiment can be obtained.

[0080]

As is apparent from the above description, according to the one-way clutch of claim 1 of the present invention, since the wedge angles in the respective clutch function parts are set to different angles,
It is possible to realize a one-way clutch excellent in meshing property and torque transmission property.

According to the one-way clutch of claim 2, the clutch function portion on the radially outer side is locked.
The clutch function portion on the radially inner side is locked with a slight delay, and the rotation of the drive side is transmitted to the driven side in this way, so that a one-way clutch with excellent meshing and torque transmissibility can be realized. .

According to the one-way clutch of claim 3, the clutch function portion on the radially inner side is in the locked state,
The clutch function portion on the radially outer side is locked with a slight delay, and the rotation of the drive side is transmitted to the driven side in this way, so that a one-way clutch with excellent meshing and torque transmissibility can be realized. .

Further, according to the one-way clutch of claim 4, since the wedge angles in the respective clutch function portions are set to different angles, a one-way clutch excellent in meshing property and torque transmission property can be realized. In addition, since it is not necessary to provide the outer ring member and the inner ring member for each clutch function portion, the configuration is simpler and the cost can be reduced as compared with the case where the inner ring member and the outer ring member are separate members.

Further, according to the pulley device of claim 5,
It is possible to realize a pulley device having excellent meshability and torque transmission with minimal loss, and the structure is simpler and the cost can be reduced as compared with the case where the outer ring member and the inner ring member of the one-way clutch are separate members.

[Brief description of drawings]

FIG. 1 is a side sectional view showing an overall configuration of a pulley apparatus showing a first embodiment of the present invention.

FIG. 2 is a front sectional view of the same.

FIG. 3 is a front sectional view of a pulley device showing a second embodiment of the present invention.

FIG. 4 is a front sectional view of a pulley device showing a third embodiment of the present invention.

FIG. 5 is a front sectional view of a conventional pulley device.

[Explanation of symbols]

1 Pulley device 2 Drive shaft for power generation 6 axis 7 Outer ring 8 Inner ring 10 one-way clutch 11 pulley 18 First clutch function 19 Second clutch function section θ1, θ2 wedge angle

Claims (5)

[Claims] 1. A plurality of clutch function parts, wherein each of the clutch function parts includes an outer ring member, an inner ring member arranged radially inward of the outer ring member, the outer ring member and the inner ring member. A wedge member disposed between the inner and outer ring members, wherein the wedge function is such that the wedge member is engaged between the outer ring member and the inner ring member, and the inner ring member and the outer ring member rotate synchronously about an axis. It is freely switchable between a state in which the wedge member releases the engagement and a free state in which the outer ring member and the inner ring member relatively rotate around the axis, and the clutch function parts are concentric with each other in diameter. The wedge angle is formed inside and outside the direction, the rotation directions in the locked state are the same direction, and the wedge angle formed by both tangents at the point where the wedge member contacts the inner peripheral surface of the outer ring member and the outer peripheral surface of the inner ring member. Is different One-way clutch, characterized in that it is so that set. 2. The wedge angle of the radially outer clutch function portion is set to be smaller than the wedge angle of the radially inner clutch function portion, and the radially outer clutch function portion is the drive side. The one-way clutch according to claim 1, wherein the clutch function portion on the inner side in the direction is a driven side. 3. The wedge angle of the clutch function portion on the radially inner side is set smaller than the wedge angle of the clutch function portion on the radially outer side, and the clutch function portion on the radially inner side is the drive side. The one-way clutch according to claim 1, wherein the clutch function portion on the outer side in the direction is a driven side. 4. The inner ring member of a predetermined clutch function part is also used as an outer ring member of another clutch function part arranged radially inside of the clutch function part. The one-way clutch according to any one of 3 above. 5. A pulley device in which the one-way clutch and the bearing according to any one of claims 1 to 4 are arranged between a pulley around which a power transmission belt is wound and a shaft body.