JPH081224B2 - Rolling bearing 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 body having a torque transmitting surface, in which a plurality of rollers are arranged so as to be in linear contact with 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 rotate when the inner ring and the outer ring rotate relative to each other. There is known a rolling bearing clutch that acts as a sprag by moving axially in the axial direction and clutches between the inner and outer races (see Japanese Unexamined Patent Publication No. 3-74641).

In this rolling bearing clutch, the inner and outer races are axially displaced relative to each other when the clutch state is shifted 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 being displaced in the direction, and this is connected to an outer ring by a torque transmitting means. Further, the publication discloses 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 transmission means, torque is transmitted between the power transmission rotating body and the outer ring, but the outer ring can move freely in the axial direction.
When the clutch is engaged, the outer ring is moved due to the pulling force of the inner and outer rings (the force that moves in the direction of narrowing the raceway) due to the spring force to cause the clutch, while at the time of 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 track spacing, and the inner ring and the outer ring rotate relatively freely. As a result, the clutch can be engaged and disengaged.

However, in such a rolling bearing clutch, since 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, the rollers rotate to pull or pull the inner and outer rings. As much play as possible is produced, and because the roller separation force 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 Therefore, it is an object of the present invention to solve the above-mentioned problems in the prior art, to provide a rolling bearing clutch with improved clutch engagement / disengagement, reduced free rotation torque, and improved function of torque transmission means. To do.

[0006]

In order to solve the above-mentioned problems, the present invention is arranged so that the outer surface of the inner ring and the inner surface of the outer ring face each other.
The inner ring raceway surface and the outer ring raceway surface to form a raceway.
The inner and outer ring raceways are formed as single-leaf rotating hyperboloids, and the center axis of the inner ring is included so as to linearly contact the inner and outer raceways.
By a predetermined angle inclined from the free surface is disposed a plurality of rollers, the torque transmitted to the position opposed to the outer surface of the outer ring mounted for relative rotation at a constant position of the center axis direction with respect to the inner ring the rotating body having a surface provided, in the rolling bearing clutch coupled with the outer ring via the torque transmission means the rotating body, the torque transmission means, said outer of said outer ring
Sectional provided inclined at a predetermined angle from the plane including the central axis and an arc-shaped outer ring groove on the side surface, the rotating body rotating member the predetermined angle and the same angle inclined provided sectional inside surface of the arc-shaped It is characterized by having a groove and a spherical body fitted in the outer ring groove and the rotating body groove.

[0007]

Rolling bearing clutch [created for the present invention is applied, provided the inner ring raceway surface and the outer ring raceway surface so as to form a raceway to face to the inner ring of the outer and inner surfaces of the outer ring, the inner and outer ring raceway Since the surface is a single-leaf rotating hyperboloid, and it is configured by arranging a plurality of rollers inclined at a constant angle from the surface including the center axis of the inner ring so as to linearly contact the inner and outer ring raceways, for example, When the inner ring is rotated in one direction, the rollers revolve around the inner ring while being rotated by being guided by the inner ring raceway surface, and also move on the inner ring in one direction 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 races are guided by the rotation of the rollers and moved in opposite directions in the central axis direction. This moving direction is defined by the distance between the inner ring raceway surface and the outer ring raceway surface.
The direction in which the track spacing increases or decreases, which is determined by the direction of rotation of the inner ring. For example, if the inner ring moves in such a way that the track spacing increases when it rotates in one direction, 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 ring 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 sphere 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 the rotation works. 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 in the direction perpendicular to the slope (center direction of the sphere) and a force in the direction parallel to the slope (tangential direction of the sphere). A rotating 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 tries to rotate in the groove, and the rotating body and the outer ring are guided by the sphere and try to move in directions opposite to each other in the groove direction. However, since the position of the rotating 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, the rotation of the outer ring accompanying the rotation of the inner ring or the rotation of the rotating body causes the above-described action 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 as 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 rotation on the clutch side, there is no play, and a clutch state is quickly established between the inner and outer wheels. Further, during free rotation, the separation force generated between the inner and outer rings by the rollers allows the inner and outer rings to be separated from each other more than they are separated, so that the torque during 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 is generated without sliding friction, so that the outer ring is smoothly moved with very little resistance. Therefore, although the force of 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. The present rolling bearing clutch, the inner ring raceway surface 1a and the outer ring raceway surface 2a as to face to the outer surface and the inner surface of the outer ring 2 of the inner ring 1 forming the trajectories <br/> canal 4
Are provided, and the inner and outer ring raceways 1a and 2a are made into single-leaf rotating hyperboloids, and the inner race 1 is made to linearly contact the inner and outer ring raceways.
A plurality of rollers 3 are arranged at an angle β of, for example, 15 ° with respect to the plane including the mandrel 5 (Fig. 2), and rotate relative to the inner ring 1 at a certain position in the direction of the central axis 5. A housing 6 as a rotating body having a torque transmitting surface is provided at a position that is freely attached and faces the outer surface of the outer ring 2, and the housing 6 is connected to the outer ring 2 via a torque transmitting means described later. There is.

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, a ball 9 is provided between the housing 6 and the outer ring 2 as a sphere that 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 provided with a collar 10 and a stopper 11, respectively, which stop the axial movement of the roller 3. This is because when the roller 3 advances axially 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 respective positions between the rollers are held by a retainer 12 so that they do not contact each other. There is. In the figure,
3-1 of which is a surface including the central axis 5 and in a direction perpendicular to the paper surface.
The angle β is inclined with respect to. In this way, adjacent rollers that rotate in the same direction do not collide with each other at tangential velocities in the opposite directions,
The rotation and revolution of roller 3 become smooth.

Next, the raceway surfaces 1a and 2a of the inner ring 1 and the outer ring 2 are single-leaf rotating hyperboloids obtained by rotating the hyperbola shown in the following equation around the central axis 5 so as to make 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 in the reference plane (the origin plane 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 tilt angle is β and the calculation is performed in the case of F = 9, r = 1.5 and β = 15 ° (the calculation is complicated, it 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 in the opposite direction 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 4 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 orbital interval between the inner and outer rings 1 and 2 is narrowed, and a clutch state is established between the inner and outer rings. 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. the above
The operation will be further described with reference to FIG. 7. Figure 7 shows inside and outside
The state in which the roller 3 is interposed between the ring raceways 1a, 2a is a plane
It is shown in a simulated manner. That is, it is actually close to a conical surface
The inner and outer ring raceways 1a and 2a, which are uniplane rotating hyperboloids, are partially
Is indicated by a solid line frame 1P, 2P on a plane, and the inner ring raceway surface 1
There is a roller 3 shown by a chain line on a, and the outer ring raceway surface 2 is on it.
The state in which a is covered is shown. And Y and Y'are inside
The rotation direction of the outer ring is shown, and X and X'show the direction of the central axis 5.
You. When the outer ring raceway surface 2a is rotated in the Y direction, the inner ring raceway is
Assuming that the surface 1a does not move, the outer ring raceway surface 2a is inclined.
It is guided by the rotation of the roller 3 and rotates in the Y direction.
It also moves in the X direction and moves to the position of the frame 2P 'shown by the thick two-dot chain line.
Moving. Thick two points that are displayed as Coro 3 and Coro 3 '
Move to the position of the chain line. The position of this roller 3'is the inner ring gauge.
On the road surface 1a, it is a position moved as shown by arrow D,
On the ring raceway surface 2a ', the first position shown by the rollers 3
This is the position moved from the position as indicated by arrow E. like this
By the movements of the outer ring raceway surface 2a and the rollers 3, the outer ring raceway surface 2
a is the distance x in the direction of arrow X, that is, in the direction of the central axis 5 (see FIG. 1)
Only displaced. The direction of this displacement is to the left in FIG.
If so, the space between the orbits 4 widens and the inner and outer rings freely
Can pair times rolling, if it is the opposite, the interval of the track 4 is narrow or
, The roller 3 locks between the inner and outer wheels, and the clutch between the inner and outer wheels
To be done.

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 a large number of them are arranged on the outer surface of the outer ring 2 and the inner surface of the housing 6 at the same constant angle of 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 above force is applied to the force R in the direction perpendicular to the slope (the direction of 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 the outer ring 2 moves toward the grooves 2b and 6c in the direction of the center axis 5 in FIG. become.

Thus, 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 orbital 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 the 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 wheels corresponding to the twist angle without play. On the other hand, during 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 during free rotation is reduced. Further, 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 multi-functionality 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 ball 9 moves in the grooves 2b and 6c only by rotation without sliding friction, and the outer ring 2 moves in the housing. For 6, it is moved 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 present rolling bearing clutch, in the clutch state, for example, if the housing 6 on the driven side is rotated faster than the inner ring 1 on the driving side, 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, the disc spring 8 is provided to urge the outer ring 2 in the clutch direction. However, 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.

[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, it improves the fitting and dismounting 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.

3 (a) to (c) show shapes of outer ring grooves of the clutch, (a) is a sectional view, (b) is a side view, and (c) 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.

[Figure 7] Planes the relative movement between the inner and outer rings through the rollers
It is explanatory drawing shown in a simulation.

[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. The outer surface of the inner ring and the inner surface of the outer ring face each other.
The inner ring raceway surface and the outer ring raceway surface to form a raceway.
Provided, said inner ring raceway surface and monoplane rotational hyperboloid, a plane including the central axis of the inner ring in contact linearly within said outer ring raceway surface
They were allowed a certain angle inclined disposed a plurality of rollers, a torque transmission surface in a position facing the outer surface of the outer ring mounted for relative rotation at a constant position of the center axis direction with respect to the inner ring the rotating body having provided, in the rolling bearing clutch coupled with the outer ring via the torque transmission means the rotating body, the torque transmitting means is a predetermined angle from the plane containing the central axis to the outer surface of the outer ring An outer ring groove that is provided with an inclination and has an arc-shaped cross section;
A rolling bearing clutch, comprising: a spherical body fitted in the outer ring groove and the rotating body groove.