JPH05149352A - Rolling bearing clutch - Google Patents

Abstract

PURPOSE:To improve the function of a torque transmitting means by improving the engaging-disengaging capability of a clutch and reducing its free rotation torque. CONSTITUTION:A track 4 is formed between an inner ring 1 and an outer ring 2, and the raceway surfaces 1a, 2a of the inner and outer rings are formed into a simple hyperboloid of revolution, and plural number of rollers 3 are arrangedly provided with gradient, for instance as much as 15 degrees, given to a face containing a central axis 5 so as to come into linear contact with the raceway surfaces of the inner and outer rings. A housing 6 to transmit the torque of the outer ring 2 to an outside is provided, and the housing 6 and the outer ring 2 are severally provided with grooves inclining at the same angle from an axial face, and a ball 9 to transmit torque between both the grooves is fitted in the grooves. Thus, the outer ring can be axially moved through the ball 9 and the grooves to improve the engaging-disengaging ability and free rotation performance of a clutch.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotating body having a torque transmitting surface in which a plurality of rollers are arranged so as to linearly contact the inner and outer raceway surfaces of a single-leaf hyperboloid. The present invention relates to a rolling bearing clutch in which is coupled to an outer ring via a torque transmission means.

[0002]

2. Description of the Related Art As a rolling bearing clutch in which cylindrical rollers are arranged at an inclination, for example, by arranging the rollers at an inclination between an inner ring and an outer ring, the rollers are rotated when the inner ring and the outer ring are relatively rotated. There is known a rolling bearing clutch as a one-way clutch that acts as a sprag by moving axially in the axial direction and clutches between the inner and outer rings (see Japanese Patent Laid-Open No. 3-74641).

In this rolling bearing clutch, the inner and outer races are relatively displaced in the axial direction when the clutch state shifts to the free rotation state or vice versa. At this time, the drive side and the driven side are also displaced. There is disclosed a structure in which a power transmission rotating body is provided so that torque can be transmitted without displacement in the direction, and this is connected to the outer ring by a torque transmitting means. Further, it is described in the publication that a torque transmission pin, an involute spline, a ball spline or the like can be used as the torque transmission means.

[0004]

In the above torque transmitting means, the torque is transmitted between the power transmission rotating body and the outer ring, but the outer ring can freely move in the axial direction.
During clutching, the outer ring is moved by the pulling force of the inner and outer rings due to the spring force (the force that moves in the direction that narrows the raceway) to engage the clutch, while during free rotation, the pulling force of the inner and outer rings by the rollers causes the spring to move. The outer ring is moved against the force to widen the space between the raceways, and the inner and outer rings are relatively freely rotated. As a result, the clutch can be engaged and disengaged.

However, in such a rolling bearing clutch, the engagement and disengagement of the clutch depends on the spring force and the pulling force or pulling force between the inner and outer rings due to the rollers, and therefore the rollers rotate to pull or pull the inner and outer rings. As much play as possible is produced, and because the separating force of the rollers during free rotation is insufficient, some rotational torque was generated during free rotation. Further, the torque transmission means is used only for torque transmission, and the multifunctionalization thereof has not been achieved. SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a rolling bearing clutch which solves the above problems in the prior art, improves the fitting / disengaging properties of the clutch, reduces the free rotation torque, and improves the function of the torque transmission means. To do.

[0006]

In order to solve the above-mentioned problems, the present invention forms a raceway between an inner ring and an outer ring, and makes the inner and outer ring raceway surfaces a single-leaf rotating hyperboloid, and forms a line on the inner and outer ring raceway surfaces. A plurality of rollers that are inclined at a constant angle so as to come into contact with each other, and are rotatably attached to the inner ring at a fixed position in the central axis direction of the inner ring and face the outer surface of the outer ring. In a rolling bearing clutch in which a rotating body having a torque transmitting surface is provided at a position where the rotating body is coupled to an outer ring via a torque transmitting means, the torque transmitting means includes the central shaft on the outer surface of the outer ring. An outer ring groove that is inclined at a predetermined angle from the surface that includes the arc, and has an arc-shaped cross section, and a rotor groove that is inclined at the same angle as the predetermined angle on the inner surface of the rotor and that has an arc-shaped cross section; And a sphere that fits in the rotation groove. Rolling bearing clutch, characterized in that.

[0007]

[Operation] A rolling bearing clutch to which the present invention is applied forms a raceway between an inner ring and an outer ring, and the inner and outer ring raceway surfaces are made into single-leaf rotating hyperboloids so as to linearly contact the inner and outer raceway surfaces. Since it is configured by arranging a plurality of rollers with a certain angle of inclination, for example, when the inner ring is rotated in one direction, the rollers revolve around the inner ring while being guided by the inner ring raceway surface and rotating. Both proceed on the inner ring to one side in the central axis direction. Since the direction of rotation of the roller is opposite to the outer ring raceway surface, the roller tries to move in the opposite direction to the outer ring raceway surface in one direction. As a result, the inner and outer rings are guided by the rotation of the rollers and moved in opposite directions in the central axis direction. This moving direction is a direction in which the track spacing formed between the inner and outer rings widens or narrows, which is determined by the direction of rotation of the inner ring. For example, if the inner ring rotates in one direction so that the track spacing increases, free rotation is possible between the inner and outer rings, and if the inner ring rotates in the opposite direction and the track interval narrows, the clutch between the inner and outer rings moves. It becomes a state. On the other hand, the outer ring is rotatably attached to the inner ring at a fixed position in the central axis direction thereof, and is coupled with a rotating body having a torque transmission surface at a position facing the outer surface of the outer ring via torque transmission means. Therefore, the rotation of the outer ring is transmitted to the rotating body, and the outer ring and the rotating body rotate together.

Next, according to the present invention, the outer race groove and the rotor groove are arranged so as to be inclined at the same angle with respect to the plane including the central axis, and the spherical body is fitted in both grooves. For example, if a rotatable body is rotated between the inner ring and the inner ring at a constant axial position, a rotational force acts on the spherical body from the upstream end of the groove of the rotor and the downstream end of the outer ring groove. The force due to the resistance moment against rotation acts from. These forces are equal in magnitude and opposite in direction. Since both grooves are inclined here, the above force can be decomposed into a force perpendicular to the slope (direction of the center of the sphere) and a force parallel to the slope (direction of the tangent of the sphere). A rotational moment corresponding to the product of the couple of parallel forces and the distance between them, that is, the groove width, acts on the sphere. As a result, the sphere tends to rotate in the groove, and the rotator and the outer ring are guided by the sphere to move in directions opposite to each other in the groove direction. However, since the position of the rotary body is fixed in the axial direction, the outer ring moves in the groove direction and thus in the axial direction. Thus, when the rotating body and the outer ring are rotated in any direction by being given a rotational force, the outer ring moves in any direction in the central axis direction, and the orbit interval is widened or narrowed depending on the rotation direction. That is, due to the rotation of the outer ring accompanying the rotation of the inner ring, or the rotation of the rotating body, the above-described action occurs between the outer ring and the rotating body, and between the inner and outer rings, the movement of the outer ring due to the separation or pulling force of the rollers causes Motion will be added.

In this case, the outer ring starts to move in accordance with the inclination of the groove at the same time when the rotating body and the outer ring rotate, so that the outer ring is moved larger and faster than the movement of the outer ring when the outer ring is moved by the movement of the rollers. As a result, in the rotation on the clutch side, there is no play, and the state between the inner and outer wheels is in a clutch state quickly. Further, at the time of free rotation, the separation force generated between the inner and outer rings by the rollers can separate the inner and outer rings more than the distance between them, so that the torque at the time of free rotation is reduced. Furthermore, since the sphere can be used not only for transmitting torque but also for moving the outer ring, it is possible to achieve multiple functions with a simple configuration. Since such movement of the outer ring is brought about by the rotation of the spherical body, only rolling friction occurs without sliding friction, and therefore the movement is smooth with very little resistance. Therefore, although the force for moving the sphere acts due to the rotation of the rotating body, it does not adversely affect the clutch force or the separation force generated between the inner and outer rings due to the rotation of the rollers.

[0010]

EXAMPLE FIG. 1 is a sectional view showing the structure of a rolling bearing clutch of an example, and FIG. 2 is a perspective view of the roller portion. First, the overall structure of the rolling bearing clutch will be described with reference to these drawings. In this rolling bearing clutch, a raceway 4 is formed between an inner ring 1 and an outer ring 2, and inner and outer ring raceway surfaces 1a and 2a are made into single-leaf rotating hyperboloids, and a central shaft 5 is formed so as to linearly contact the inner and outer raceway surfaces. A plurality of rollers 3 are arranged with a certain angle β with respect to the plane including, for example, 15 ° (Fig. 2), and are rotatable relative to the inner ring 1 at a certain position in the direction of the central axis 5. And a housing 6 as a rotating body having a torque transmitting surface at a position opposed to the outer surface of the outer ring 2 attached to the outer ring 2, and the housing 6 is coupled to the outer ring 2 via a torque transmitting means described later. ..

In this embodiment, the housing 6 is arranged on the inner ring 1 via a bearing 7. However, the housing 6 may be rotatably attached to the shaft for driving the inner ring 1 via the bearing or directly. it can. The bearing 7 receives a radial load from the housing 6 coupled to the input side or the output side and a thrust load from the outer ring 2 via the housing 6.
A disc spring 8 for urging the outer ring 2 in the clutch direction is arranged between the spring receiving surface 6a of the housing 6 and one end side surface of the outer ring 2. The disc spring 8 can be omitted as described later. Further, the housing 6 is provided with a mounting bolt hole 6b so that the input side or the output side can be connected. Further, between the housing 6 and the outer ring 2, there is provided a ball 9 as a sphere which constitutes a torque transmitting means. Ball 9
Are fitted in the grooves provided in the outer ring 2 and the housing 6 shown in FIGS. 3 and 4.

The inner ring 1 and the outer ring 2 are respectively provided with a collar 10 and a stopper 11 for stopping the axial movement of the roller 3. This is because when the roller 3 advances in the axial direction in the raceway 4, the progress is stopped. In the present embodiment, the stopper 11 acts as a torque limiter that stops the roller at a fixed position when the roller is screwed in at the time of clutching so that torque above a fixed value is not applied. However, without causing such an action,
The purpose may be simply to prevent the rollers from slipping out.

In FIG. 2, the rollers 3 are arranged on the inner ring 1 at an angle β with respect to the cross section including the central axis 5, and the positions of the rollers are held by a retainer 12 so that they do not contact each other. There is. This way,
Adjacent rollers that rotate in the same direction do not collide with each other at tangential velocities in opposite directions, and the rotation and revolution of the roller 3 are smooth.

Next, the raceway surfaces 1a and 2a of the inner ring 1 and the outer ring 2 are single-leaf revolving hyperboloids obtained by rotating the hyperbola shown in the following equation around the central axis 5 so as to be in linear contact with the rollers 3. .. yi ² / ai ² −xi ² / bi ² = 1 yo ² / ao ² −xo ² / bo ² = 1 where x _i and x _o are the centers of the inner ring raceway surface 1 a and the outer ring raceway surface 2 a, respectively. Distance in the direction of axis 5, y _i , y
_o is the distance from the central axis 5 of the inner ring raceway surface 1a and the outer ring raceway surface 2a in an arbitrary cross section including the central axis 5, respectively.
Also, ai, bi, ao, and bo are constants. Now, the central axis 5 on the reference surface (the origin surface of the hyperbola) on the small diameter side of the inner and outer rings
To the center of the orbit 4 is F, the radius of the roller 3 is r,
When the inclination angle is β and the calculation is performed in the case of F = 9, r = 1.5 and β = 15 ° (the calculation is complicated, the description is omitted),
The values of ai, bi, ao, and bo are about 7.5 and 3, respectively.
0.1, 10.5 and 37 are given, and the shape of the single-leaf rotating hyperboloid of the inner and outer ring raceways is given.

With the above structure, when the inner ring 1 is rotated in the direction of arrow A, the rollers 3 are guided by the inner ring raceway surface 1a to revolve on the inner ring 1 while rotating in the direction of arrow B, and the inner ring 1 is rotated. It goes up to the left in the direction of the central axis.
Since the direction of rotation of the roller 3 is opposite to the outer ring raceway surface 2a, the roller 3 moves to the right opposite to the outer ring raceway surface 2a. As a result, the inner and outer rings 1, 2 are guided by the rotation of the rollers 3 and are moved in opposite directions in the direction of the central axis 5, the space between the raceways 9 is widened, and free rotation is possible between the inner and outer rings. On the other hand, when the inner ring 1 rotates in the direction opposite to the arrow A, the operation opposite to the above occurs, the track interval between the inner and outer rings 1 and 2 becomes narrower, and the state between the inner and outer rings becomes the clutch state. The rotation of the outer ring 2 is transmitted to the housing 6, and the outer ring and the housing 6 rotate as a unit.

3 and 4 show the structures of the grooves provided in the outer ring 2 and the housing 6, respectively. Each groove 2
As shown in the drawing, b and 6c are arcuate in cross section, and are arranged on the outer surface of the outer ring 2 and the inner surface of the housing 6 both inclined by the same constant angle, for example, about 18 ° from the cross section including the central axis 5. .. Then, as shown in FIG. 1, when the grooves 2b and 6c of the outer ring 2 and the housing 6 are at positions facing each other, the balls 9 are fitted in the grooves. The grooves 2b and 6c and the ball 9 thus fitted together form a torque transmitting means.

FIG. 5 is a diagram for explaining the operation of the above torque transmitting means. For example, when the housing 6 is rotated in the direction of arrow C, which is the direction of free rotation, the balls 9
A force F in the rotation direction due to rotation acts from the upstream end 6c-1 of the groove 6c of the housing 6, and a force F due to a resistance moment against rotation acts from the downstream end 2b-1 of the outer ring groove 2b. These forces are equal in magnitude and opposite in direction. Since both grooves are inclined by the same angle, the force R is applied in the direction perpendicular to the slope (direction toward the center of the ball 9).
And the force H in the direction parallel to the slope (the tangential direction of the ball 9) can be decomposed, and therefore the ball 9 corresponds to the product Hx of the couple force formed by the parallel force H and the distance x therebetween, that is, the groove width. Rotational moment will act. As a result, the ball 9 tries to rotate in the groove, and the housing 6 and the outer ring 2 are guided by the ball 9 and try to move in directions opposite to each other in the groove direction. However, since the housing 6 is fixed in the axial position, the outer ring 2 moves in the direction of the grooves 2b and 6c, that is, in the direction of the central axis 5 in FIG. When the clutch is engaged, the housing 6 moves in the direction opposite to the arrow C, and by the same action as described above, the outer ring 2 moves in the direction of the grooves 2b and 6c in the direction of the central axis 5 in FIG. become.

As described above, when the housing 6 and the outer ring 2 are rotated in any direction by being given a rotational force, the outer ring 2 moves in any direction in the direction of the central axis 5, and the orbit interval is widened depending on the rotating direction. Or narrow it. That is, the rotation of the outer ring 2 accompanying the rotation of the inner ring 1 or the rotation of the housing 6 causes the above-described action between the outer ring 2 and the housing 6, and the outer ring is moved by the pulling force or pulling force of the rollers 3. In addition, it is also moved by the ball 9.

In this case, since the movement of the outer ring 2 via the ball 9 starts simultaneously with the rotation of the housing 6 and the outer ring 2, it is larger and faster than the movement of the outer ring 2 when the outer ring 2 is moved by the movement of the rollers 3. As a result, when rotating to the clutch side, there is no play and the inner and outer races 1,
A clutch state is established between the two. Therefore, for example, when the housing 6 rotates to the clutch side, as shown in FIG. 6, torque is transmitted between the inner and outer races corresponding to the twist angle without play. On the other hand, at the time of free rotation, the separation force generated between the inner and outer rings by the roller 3 allows the inner and outer rings to be separated from each other more than they are separated, and the torque at the time of free rotation is reduced. Furthermore, since the ball 9 can be used not only for transmitting torque but also for moving the outer ring 2, it is possible to achieve multiple functions with a simple configuration.

Further, in the present invention, since the outer ring groove 2b and the housing groove 6c are inclined at the same angle, the balls 9 move only by rotation in the grooves 2b and 6c without causing sliding friction, and the outer ring 2 moves in the housing. For 6, it runs smoothly under rolling friction with very little resistance. Therefore, such movement of the outer ring 2 does not adversely affect the clutch force or the separation force generated between the inner and outer rings 1 and 2 due to the rotation of the rollers 3. Further, in the rolling bearing clutch, if the housing 6 on the driven side is rotated faster than the inner ring 1 on the driving side in the clutch state, the outer ring 2 is guided by the balls 9 to move to the free rotation side, and the clutch state is maintained. Can be turned off and the rolling bearing clutch can be used as an on / off clutch.

In the present embodiment, as shown in FIG. 1, a disc spring 8 is provided to urge the outer ring 2 in the clutch direction, but when torque is transmitted between the outer ring 2 and the housing 6. Since the outer ring 2 is immediately moved to the clutch side, the disc spring 8 can be omitted. Further, although the case where the rolling surface of the roller 3 has a cylindrical shape has been described above, the present invention can be applied to the case where the roller 3 has a conical shape, a drum shape, or a drum shape.

[0022]

As described above, according to the present invention, in addition to moving the outer ring in the axial direction by means of rollers, the outer ring is positively and smoothly moved in the axial direction by the combination of the inclined groove and the spherical body fitted therebetween. Therefore, improve the fitting and disengaging of the clutch,
The free rotation torque can be reduced and the function of the torque transmission means can be improved. .

[Brief description of drawings]

FIG. 1 is a sectional view of a rolling bearing clutch according to an embodiment.

FIG. 2 is a perspective view showing an arrangement of rollers of the clutch.

3A to 3C are views showing the shape of an outer ring groove of the clutch, FIG. 3A is a sectional view, FIG. 3B is a side view, and FIG. 3C is a partial plan view.

4A and 4B show the shape of a groove of the clutch housing, FIG. 4A is a sectional view, and FIG. 4B is a side view.

FIG. 5 is an explanatory view of the operation between the housing of the clutch and the outer ring.

FIG. 6 is a curve diagram showing a relationship between a twist angle and torque.

[Explanation of symbols]

 1 Inner ring 1a Inner ring raceway surface 2 Outer ring 2a Outer ring raceway surface (Outer ring raceway surface) 2b Outer ring groove 3 Roller 4 Raceway 5 Center shaft 6 Housing (rotating body) 6c Housing groove (rotating body groove) 9 Ball (sphere)

Claims (1)

[Claims] 1. A plurality of rollers that form a raceway between an inner ring and an outer ring, and make the inner and outer ring raceway surfaces a single-leaf revolving hyperboloid and incline at a constant angle so as to linearly contact the inner and outer ring raceway surfaces. And rotatably mounted relative to the inner ring at a fixed position in the central axis direction of the inner ring and provided with a torque transmission surface at a position facing the outer surface of the outer ring,
In a rolling bearing clutch in which the rotating body is coupled to an outer ring via a torque transmitting means, the torque transmitting means is provided on an outer surface of the outer ring inclined at a predetermined angle from a plane including the central axis and has an arc-shaped cross section. Outer ring groove, a rotating body groove having an arc-shaped cross section which is provided on the inner surface of the rotating body at the same angle as the predetermined angle, and a spherical body fitted into the outer ring groove and the rotating groove. A rolling bearing clutch characterized by the following.