JPH05118355A - Clutch - Google Patents

Abstract

PURPOSE:To provide a structure wherein a position relation can be held constant of retainers for controlling an engaging piece to a meshing position and further to relax force applied to the retainers at the time of a high torque load, in a clutch. CONSTITUTION:The first/second retainers 3, 4 are provided between an outer ring 1 and an inner member 2 to press attach the first retainer 3 to an end face 2a of the inner member 2 by pressing of an elastic member 14. A stopper pin 22 mounted on the first retainer 3 is fitted to float in an angular hole 23 of the second retainer 4, and a differential means 15 for decelerating this retainer is connected to the second retainer. When force is applied to the first retainer 3 from a sprag 5 at the time of a torque load, the first retainer is slip rotated against the inner member to relax the face. The second retainer is turned together with the first retainer by the stopper pin 22 to maintain a position relation between both the retainers.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch, and more particularly to a connecting structure for a retainer that holds an engaging element.

[0002]

2. Description of the Related Art As shown in FIG. 5, a two-way clutch using a sprag as an engaging element incorporates a first cage 3 and a second cage 4 having different diameters between an outer ring 1 and an inner member 2. By the action of the retainers 3 and 4 and the spring member 6, the sprag 5 is positioned for meshing.

That is, in the conventional clutch, the first cage 3 is integrally fixed to the inner member 2 or the outer ring 1 by the pin 31, and the pin 31 is provided in the square hole 32 of the second cage 4 in the rotational direction. The second retainer 4 into the first retainer 3
By rotating the sprag 5 relative to and moving it to a predetermined position, the sprag 5 is tilted to stand by at the meshing position.

From this state, when the inner member 2 rotates in the direction of the arrow, the sprags 5 are caught in the raceway surfaces 7 and 8 to rotate the inner member 2 and the outer ring 1 integrally.

Further, when the clutch is idling, the sprag 5
Is pulled up by the idling inner member 2 or the outer ring 1 and rises up, but when the amount is large, the first and second cages 3 and 4 in the standby state serve as stoppers to prevent reverse spragging.

In such a clutch that meshes in the forward and reverse rotation directions, it is necessary to rotate the first retainer 3 and the second retainer 4 relative to each other to make them stand by. It has a structure to fix the vessel 3 to the raceway surface.

[0007]

By the way, in the clutch having the above structure, when a high torque is applied to the sprag, the sprag 5 and the raceway surfaces 7 and 8 are elastically displaced by the contact stress, and the sprag 5 is shown in FIG. As shown by the dashed line
Inclination by the amount of elastic displacement with respect to the standby position.

In this case, if there is no slippage between the sprag 5 and the raceway surfaces 7 and 8, the first cage 3 and the sprag 5 will interfere with each other, but in reality, the sprag will be separated by the interference amount δ. Sliding occurs between the raceway surfaces, which relieves the force applied to the first cage 3.

However, when a large number of sprags are installed, or when the raceway surface for sliding the sprags is on the inner member side and the sprags do not slide, the force applied to the first cage 3 becomes large. The pillar portion between the pockets of the cage 3 and the fixing pin 31 may be damaged.

Further, since the sprag 5 slides on the raceway surfaces 7 and 8 in a high torque state, there is a problem that the wear of the contact surface becomes large and the life is shortened.

Therefore, the present invention provides a clutch capable of maintaining a constant positional relationship between the cage and a stable operation even under a high load condition by devising a structure for connecting the cage and the raceway surface. The purpose is to

[0012]

In order to solve the above problems, the present invention provides a first retainer and a second retainer incorporated between an outer ring and an inner member through a clearance in the rotational direction. The structure is provided with an elastic member that is rotatably connected and has its first retainer slidably contacting one of the outer ring and the inner member, and that provides the contact portion with an urging force in the crimping direction.

[0013]

In the above structure, when the first cage is brought into sliding contact with one of the outer ring or the inner member on the drive side and a high torque load is applied to the engaging element in that state, the first engaging element causes interference with the engaging element. A force acts on the cage. When this acting force exceeds the crimping force of the elastic member, the first retainer slides by the amount of interference with the engagement element, and relaxes the force applied to the retention element and the engagement element.

Further, when the first retainer moves, the second retainer rotates together, and the engaging element is put in the standby position at the engaging position with a gap in the rotation direction.

[0015]

1 to 4 show a clutch according to an embodiment. As shown in FIG. 1, an inner member 2 composed of a hollow shaft is fitted inside the outer ring 1, and both of them are incorporated into a bearing 9 arranged at the end of the outer ring 1 and an inner and outer two-layer structure. It is rotatably supported via a pair of bearings 10 and 11.
Further, a support case 17 of a differential means 15 described later is rotatably supported on a peripheral surface of the inner member 2 protruding from the outer ring 1 via a bearing 29, and a rear end portion of the inner member 2 is The input ring 12 is attached by fitting the serration groove.

As shown in FIGS. 1 and 2, raceway surfaces 7 and 8 forming concentric cylindrical surfaces are formed on the inner diameter surface of the outer ring 1 and the outer diameter surface of the inner member 2 facing the outer ring 1, respectively. Between the raceway surfaces 7 and 8, the first cage 3 and the second cage 4 having different diameters are provided.
Is incorporated.

The first cage 3 has a bent portion 3a formed at its front end portion and bent toward the inner diameter side.
a is in sliding contact with the end surface 2a of the inner member 2 so as to be rotatable. An elastic member 14 made of a disc spring is incorporated between the bent portion 3a and the retaining ring 13 of the bearing 9. The elastic member 14 gives an urging force in a direction in which the bent portion 3a is pressed against the end surface 2a of the inner member 2.
The pressing force causes a frictional force in the contact area between the two,
The first retainer 3 is fixed to the inner member 2 by the frictional force.

On the other hand, as shown in FIG. 1, the second cage 4 is integrally formed at its rear end with an extension portion 4a which is inserted between the bearings 10 and 11 having a two-layer structure. , 11
It is rotatably supported by the outer ring 1 and the inner member 2 by the guide.

A differential means 15 for decelerating the second cage 4 is connected to the end of the extension 4a. The differential means 15 comprises a rolling bearing 16 in which the inner ring is press-fitted and fixed to the extension portion 4 a, and a support case 17 supporting the rolling bearing 16, and the support case 17 is externally fixed via a connecting rod 18. It is connected to a member (not shown).

Further, the rolling bearing 16 is fitted into the support case 17 by applying a preload so that the radial clearance becomes zero or less, and the bearings 9 and 1 for supporting the inner member 2 at the time of rolling.
Rotational resistance greater than 0 and 11 is imparted.

In this structure, the rotation resistance of the rolling bearing 16 applies a force to the second retainer 4 to stop the rotation, decelerates the second retainer 4 from the rotation of the inner member 2, and the impact force and Hold it so that it will not easily rotate due to inertial forces.

Further, the first cage 3 and the second cage 4 are
As shown in FIG. 4, a plurality of pockets 1 facing each other in the circumferential direction are provided.
9 and 20 are formed, and the sprag 5 as an engaging element and the spring member 6 for holding the sprag are incorporated in the pockets 19 and 20, respectively.

The sprag 5 is formed by an arcuate surface 21 having an outer diameter side and an inner diameter side with a center of curvature on the center line of the sprag. When the sprag 5 is inclined at a predetermined angle in both left and right directions, the sprag 5 engages with both raceway surfaces 7 and 8 to form an outer ring. 1 and the inner member 2 are integrated. The spring member 6 has one end supported by the second retainer 4 and presses the sprags 5 from both sides, and gives an elastic force for facilitating the engagement of the sprags with the raceway surfaces 7 and 8.

As shown in FIGS. 2 and 3, a stopper pin 22 is attached to the front end portion of the first cage 3, and the stopper pin 22 is provided in the second cage 4 to form a square hole 23. It is loosely fitted in and has a clearance X in the rotational direction between the pin 22 and the peripheral wall of the square hole 23.

This rotation direction clearance X determines the delay angle of the second cage 4 with respect to the first cage 3, and its magnitude is such that the stopper pin 22 and the peripheral wall of the square hole 23 contact each other. When the cages 3 and 4 rotate relative to each other, the sprags 5 tilt and come into contact with both raceway surfaces 7 and 8 as shown in FIG.
It is set to stand by in a meshed state.

The clutch of this embodiment has the structure as described above, and its operation will be described below. When rotation is applied to the inner member 2 from the input ring 12, the first cage 3 is
The elastic member 14 is pressure-bonded to rotate integrally with the inner member 2. On the other hand, the rotation of the second cage 4 is delayed from the inner member 2 by the gap X in the rotation direction due to the action of the differential means 15,
It rotates relative to the first cage 3. Both cages 3,
Due to the relative rotation of 4, the sprag 5 tilts in the opposite direction to the rotation direction (arrow direction) of the inner member 2 as shown in FIG. 4, and stands by at the meshing position.

When the sprags are tilted, the pressing force of the spring member 6 attached to the second cage 4 causes all the sprags to move to the meshing position before the stopper pin 22 and the peripheral wall of the square hole 23 come into contact with each other. Then, the inner member 2 and the second cage 4 rotate together.

When the inner member 2 continues to rotate from the above state and a difference in rotation occurs between the inner member 2 and the outer ring 1, the sprag 5
Engage with the raceways 7, 8 and the rotation of the inner member 2 is transmitted to the outer ring 1 via the sprags 5.

In this driving state, when a large braking force is applied to the outer ring 1 and a high torque is applied to the sprags 5, the sprags 5 and the raceway surfaces 7 and 8 are elastically deformed, and the sprags 5 interfere with each other. As a result, a large force acts on the first cage 3.

When this acting force exceeds the frictional force generated at the contact portion between the first retainer 3 and the inner member 2 due to the crimping of the elastic member 14, the first retainer 3 slips with respect to the inner member 2. At the beginning, it rotates by the amount of interference δ with the sprag.

As a result, the above acting force is alleviated, an unreasonable force is not applied to the first cage 3 and the sprags 5, and damage to the cage and wear of the sprags are suppressed.

Further, since there is no fixing pin forcibly fixing the first retainer 3 and the inner member 2 to each other, the fixing pin is not damaged as in the conventional structure.

When the first retainer 3 slips and rotates with respect to the inner member 2 as described above, the second retainer 4 does not move for a slight amount of movement, but the amount of movement is the stopper pin. When it becomes larger than the gap X in the rotation direction between the square holder 22 and the square hole 23, the second cage 4 is driven by the stopper pin 22 and rotates together with the first cage 3. Therefore, the positional relationship between the first retainer 3 and the second retainer 4 is kept substantially the same, and the switch function for operating the clutch is not impaired.

On the other hand, when the rotation of the inner member 2 is reversed, the action of the differential means 15 causes the second retainer 4 to rotate in the opposite direction with respect to the first retainer 2, so that the sprag 5 is moved to the position shown in FIG. The state is moved to the biting position on the opposite side of the raceway surfaces 7 and 8. Therefore, the same action as described above can be performed in both forward and reverse directions.

Although the first and second cages are connected to the inner member in the above-mentioned embodiment, the same effect can be obtained by connecting them to the outer ring side.

Further, although the sprag 5 engaging in the forward and reverse directions is shown as the engaging element, a sprag engaging in only one direction may be used symmetrically instead of this.

Further, the inner member may not be a hollow shaft as shown, but may be a solid shaft or a structure in which a shaft is combined with an inner ring for a clutch.

Further, although the rolling bearing having a large rotational resistance is used as the differential means for providing the rotational difference between the both cages, the present invention is not limited to this, and the speed reducing mechanism using the gears and the friction member are not limited thereto. It is possible to use a brake mechanism or the like that decelerate due to sliding contact with.

[0039]

As described above, according to the present invention, the force generated in the cage due to the interference with the engaging element is alleviated by the sliding rotation of the retaining element, so that damage to the retainer and wear of the engaging element can be prevented. This can be prevented, and the durability of the clutch can be greatly improved.

Further, since the first and second cages are rotated together through the clearance in the rotational direction, the positional relationship between both cages can be kept constant, and the clutch operation is stable and reliable. Can be done.

[Brief description of drawings]

FIG. 1 is a vertical sectional front view of an embodiment.

FIG. 2 is an enlarged cross-sectional view showing a main part of FIG.

FIG. 3 is a view seen from the line III-III in FIG.

FIG. 4 is a sectional view showing a meshed state of sprags.

FIG. 5 is a sectional view showing a conventional example.

[Explanation of symbols]

 1 outer ring 2 inner member 3 first retainer 4 second retainer 5 sprag 6 spring material 7, 8 raceway surface 14 elastic member 15 differential means 22 stopper pin 23 square hole

Claims (1)

[Claims] 1. A first retainer and a second retainer having different diameters are provided between an outer ring and an inner member fitted to the outer race, and pockets of the both retainers are provided in pockets provided opposite to the retainers. In the clutch incorporating the engaging element that engages between the facing surfaces of the outer ring and the inner member by relative rotation, and the spring material that holds the engaging element in a position that does not engage with the facing surface, the first cage The second retainer is rotatably connected through a gap in the rotational direction, and the first retainer is brought into sliding contact with one of the outer ring and the inner member so as to be able to rotate, and an urging force in the crimping direction is applied to the contact portion. A clutch comprising an elastic member.