JP2021008937A - Rotation transmission device - Google Patents

Abstract

To provide a rotation transmission device in which an engagement element assembled between an outer peripheral engagement surface of an outer periphery of an input shaft and an inner peripheral engagement surface of an inner periphery of an outer ring, is stably operated.SOLUTION: A rotation transmission device having an outer ring 5 having a cylindrical surface 4 radially opposed to a cam surface 3 of an outer periphery of an input shaft 2, an outer ring end plate 7 formed integrally with the outer ring 5, an output shaft 8 formed integrally with the outer ring end plate 7, rollers 11a, 11b assembled between the cam surface 3 and the cylindrical surface 4, a first bearing 49 rotatably supporting the input shaft 2, a second bearing 51 rotatably supporting the output shaft 8, and a third bearing 58 relatively rotatably connecting the input shaft 2 and the outer ring 5, further has a connection pin 60 for relatively rotatably connecting a shaft end 6 of the input shaft 2 and the outer ring end plate 7 in a state of restricting relative movement in an axial rectangular direction.SELECTED DRAWING: Figure 1

Description

The present invention relates to a rotation transmission device used for switching between transmission and interruption of rotation.

As a rotation transmission device used for switching between a state in which rotation is transmitted from an input shaft to an output shaft and a state in which rotation is cut off, for example, the one described in Patent Document 1 is known.

The rotation transmission device described in Patent Document 1 has a cylindrical housing with both ends open, an input shaft arranged in a state where one end is housed in the housing, and a cam surface on the outer periphery of the input shaft facing each other in the radial direction. It has an outer ring having a cylindrical surface on the inner circumference. An outer ring end plate facing the shaft end of the input shaft in the axial direction is integrally formed on the outer ring, and an output shaft extending from the outer ring end plate to the side opposite to the input shaft side is integrally formed on the outer ring end plate. Has been done. Further, a pair of rollers are incorporated between the cam surface on the outer circumference of the input shaft and the cylindrical surface on the inner circumference of the outer ring, and the pair of rollers are held by the roller cage.

The roller cage consists of two split cages that are supported relative to rotation. The two split cages disengage the pair of rollers from the engaging position where the pair of rollers engages between the cylindrical surface on the inner circumference of the outer ring and the cam surface on the outer circumference of the input shaft, and the engagement between the rollers. It can be moved to and from the disengagement position.

Further, this rotation transmission device serves as a cage actuator that moves two split cages between an engaging position and an engaging disengaging position, and includes an armature that is movably supported in the axial direction and an armature that is axially supported. The rotors arranged facing each other, the electromagnet that attracts the armature to the rotor by energization, and the operation of attracting the armature to the rotor are changed to the operation of moving the two split cages from the engaging position to the disengaging position. It has a ball lamp mechanism to convert.

In this rotation transmission device, the input shaft is rotatably supported by a first bearing incorporated between the outer circumference of the input shaft and the inner circumference of the electromagnet. Further, the output shaft is rotatably supported by a second bearing incorporated between the outer circumference of the output shaft and the inner circumference of the housing. Further, a third bearing is incorporated between the outer circumference of the input shaft and the inner circumference of the outer ring, and the input shaft and the outer ring are connected so as to be relatively rotatable by the third bearing.

JP-A-2014-025483

By the way, when assembling the above rotation transmission device to an automobile, the input shaft is connected to the drive side shaft, the output shaft is connected to the driven side shaft, and the housing of the rotation transmission device is fixed to the support member with bolts or the like. And use it.

Here, before assembling the rotation transmission device to the automobile, an operation of engaging or disengaging the roller between the cam surface on the outer circumference of the input shaft and the cylindrical surface on the inner circumference of the outer ring is performed. Even if it can be performed stably, after assembling the rotation transmission device to the automobile, the roller may be engaged between the cam surface on the outer circumference of the input shaft and the cylindrical surface on the inner circumference of the outer ring. , It was found that the operation of disengaging the engagement may become unstable.

That is, when assembling the rotation transmission device to the automobile, the position of the drive side shaft connecting the input shaft of the rotation transmission device, the position of the driven side shaft connecting the output shaft of the rotation transmission device, and the housing of the rotation transmission device Due to the relative positional relationship with the position of the support member to be fixed, the rotation transmission device may be subjected to a radial load in a direction that causes an inclination of the axis line between the input shaft and the output shaft.

Then, due to this radial load, a slight inclination of the axis line may occur between the input shaft and the output shaft of the rotation transmission device. At this time, since the distance between the cam surface on the outer circumference of the input shaft and the cylindrical surface on the inner circumference of the outer ring formed integrally with the output shaft changes slightly, the roller incorporated between the cam surface and the cylindrical surface Operation may be unstable (for example, the distance between the cam surface and the cylindrical surface may be narrower than it should be, causing the rollers to misengage between the cam surface and the cylindrical surface, or between the cam surface and the cylindrical surface. It was found that there is a possibility that the roller may not be able to be disengaged due to excessively strong biting of the roller.

The problem to be solved by the present invention is to provide a rotation transmission device in which an engager incorporated between an outer peripheral engaging surface on the outer circumference of an input shaft and an inner peripheral engaging surface on the inner circumference of an outer ring operates stably. It is to be.

In order to solve the above problems, the present invention provides a rotation transmission device having the following configuration.
A tubular housing with open ends and
An input shaft whose one end is housed in the housing and which has an outer peripheral engaging surface on the outer periphery of the housed portion in the housing.
An outer ring having an inner peripheral engaging surface that faces the outer peripheral engaging surface in the radial direction on the inner circumference.
An outer ring end plate formed integrally with the outer ring and facing the shaft end of the input shaft in the axial direction,
An output shaft that is integrally formed with the outer ring end plate and extends from the outer ring end plate to a side opposite to the side of the input shaft.
An engaging element incorporated between the outer peripheral engaging surface and the inner peripheral engaging surface,
It is movably supported between an engaging position in which the engaging element is engaged between the outer peripheral engaging surface and the inner peripheral engaging surface and an engagement disengaging position in which the engaging element is disengaged. Engagement cage and
A cage actuator that moves the engager cage between the engagement position and the disengagement position,
A first bearing that rotatably supports the input shaft,
A second bearing that rotatably supports the output shaft,
In a rotation transmission device having a third bearing incorporated between the outer circumference of the input shaft and the inner circumference of the outer ring and connecting the input shaft and the outer ring so as to be relatively rotatable.
A rotation transmission device provided with a connecting pin for connecting the shaft end of the input shaft and the outer ring end plate so as to be relatively rotatable while the relative movement in the direction perpendicular to the shaft is restricted.

In this way, the connecting pin connecting the shaft end of the input shaft and the outer ring end plate prevents relative movement in the direction perpendicular to the axis between the shaft end of the input shaft and the outer ring end plate, so that the input shaft and the output Even when a radial load in a direction that causes an axis tilt is applied between the shafts, the axis tilt is unlikely to occur between the input shaft and the output shaft. Therefore, even when a radial load in a direction that causes an inclination of the axis line acts between the input shaft and the output shaft, the outer peripheral engaging surface on the outer circumference of the input shaft and the inner circumference of the outer ring integrally formed with the output shaft are applied. The distance from the inner peripheral engaging surface of the input shaft does not change easily, and the operation of the engager incorporated between the outer peripheral engaging surface on the outer circumference of the input shaft and the inner peripheral engaging surface on the inner circumference of the outer ring can be stabilized. It will be possible.

As the connecting pin, a columnar protrusion seamlessly formed with the shaft end of the input shaft so as to project from the shaft end of the input shaft toward the outer ring end plate is adopted to accommodate the connecting pin. It is preferable that a pin accommodating hole is formed in the outer ring end plate, and the connecting pin is rotatably supported by a rolling bearing press-fitted into the pin accommodating hole.

In this way, as the connecting pin, a columnar protrusion formed seamlessly with the shaft end of the input shaft so as to protrude from the shaft end of the input shaft is adopted, so that the outer circumference of the connecting pin can be machined. , Can be performed at the same time in the process of processing the outer circumference of the input shaft. Therefore, it is possible to process the outer circumference of the connecting pin at low cost and in a state where the axis is completely aligned with the input shaft.

When a cylindrical second bearing fitting surface into which the second bearing is fitted is provided on the outer circumference of the output shaft, the inner diameter of the pin accommodating hole is larger than the outer diameter of the second bearing fitting surface. It is preferable that the diameter is also small.

In this way, since the inner diameter of the pin accommodating hole is small, the outer ring end plate and the output shaft can be thinned to the same level as or close to the axial depth of the pin accommodating hole. It is possible to secure the strength of the connection part of. Therefore, the axial thickness of the outer ring end plate can be suppressed, and the axial dimension of the rotation transmission device can be suppressed.

When a cylindrical third bearing fitting surface into which the third bearing is fitted is provided on the outer periphery of the input shaft, the outer diameter of the connecting pin is larger than the outer diameter of the third bearing fitting surface. It is preferable that the diameter is also small.

In this way, since the outer diameter of the connecting pin is small, it is possible to set the inner diameter of the pin accommodating hole accommodating the connecting pin to be small. Therefore, the axial thickness of the outer ring end plate can be suppressed, and the axial dimension of the rotation transmission device can be suppressed.

It is preferable to use a needle roller bearing as the rolling bearing.

In this way, since the needle roller bearing is thinner in the radial direction than other bearings (ball bearings and the like), it is possible to set the inner diameter of the pin accommodating hole for press-fitting the rolling bearing to be small. Therefore, the axial thickness of the outer ring end plate can be suppressed, and the axial dimension of the rotation transmission device can be suppressed.

As the connecting pin, one end is housed in an input shaft side pin accommodating hole formed at the shaft end of the input shaft, and the other end is accommodated in an outer ring end plate side pin accommodating hole formed in the outer ring end plate. A columnar member is adopted, one end side portion of the connecting pin is rotatably supported by a rolling bearing press-fitted into the input shaft side pin accommodating hole, and the other end side portion of the connecting pin is accommodating the outer ring end plate side pin. It is preferable to press-fit it into the hole.

In this way, since the connecting pin is directly press-fitted into the outer ring end plate side pin accommodating hole without using a rolling bearing, the inner diameter of the outer ring end plate side pin accommodating hole can be suppressed. Therefore, the axial thickness of the outer ring end plate can be suppressed, and the axial dimension of the rotation transmission device can be suppressed. Further, since a columnar member independent of both the input shaft and the outer ring end plate is used as the connecting pin, the connecting pin can be manufactured at low cost.

It is preferable that the third bearing and the rolling bearing are arranged so as to have a portion overlapping in the axial direction.

In this way, the axial length of the rotation transmission device can be effectively suppressed.

When a cylindrical second bearing fitting surface into which the second bearing is fitted is provided on the outer circumference of the output shaft, the inner diameter of the outer ring end plate side pin accommodating hole is the second bearing fitting surface. It is preferable that the diameter is smaller than the outer diameter of.

In this way, since the inner diameter of the outer ring end plate side pin accommodating hole is small, the axial thickness of the outer ring end plate is reduced to the same level as or close to the axial depth of the outer ring end plate side pin accommodating hole. However, it is possible to secure the strength of the connecting portion between the outer ring end plate and the output shaft. Therefore, the axial thickness of the outer ring end plate can be suppressed, and the axial dimension of the rotation transmission device can be suppressed.

It is preferable to use a needle roller bearing as the rolling bearing.

In this way, the needle roller bearing is thinner in the radial direction than other bearings (ball bearings, etc.), so the inner diameter of the input shaft side pin accommodating hole for press-fitting the rolling bearing can be set small. It becomes. Therefore, the outer diameter of the shaft end of the input shaft can be suppressed, and the radial dimension of the rotation transmission device can be suppressed.

As the connecting pin, one end is housed in an input shaft side pin accommodating hole formed at the shaft end of the input shaft, and the other end is accommodated in an outer ring end plate side pin accommodating hole formed in the outer ring end plate. A columnar member is adopted, one end side portion of the connecting pin is rotatably supported by an input shaft side rolling bearing press-fitted into the input shaft side pin accommodating hole, and the other end side portion of the connecting pin is supported by the outer ring end. It can be rotatably supported by an outer ring end plate side rolling bearing press-fitted into the plate side pin accommodating hole.

In this way, the shaft end of the input shaft and the outer ring end plate are connected by the connecting pin via the two rolling bearings, the input shaft side rolling bearing and the outer ring end plate side rolling bearing, and thus the connecting pin is used. The transmission of rotation can be prevented very effectively. Therefore, it is possible to suppress the rotational torque transmitted from the input shaft to the output shaft via the connecting pin to be extremely small in the idling state in which the transmission of rotation from the input shaft to the output shaft is cut off.

It is preferable that the third bearing and the input shaft side rolling bearing are arranged so as to have a portion overlapping in the axial direction.

In this way, the axial length of the rotation transmission device can be effectively suppressed.

When a cylindrical second bearing fitting surface into which the second bearing is fitted is provided on the outer circumference of the output shaft, the inner diameter of the pin accommodating hole on the outer ring end plate side is the fitting of the second bearing. It is preferable that the diameter is smaller than the outer diameter of the surface.

In this way, since the inner diameter of the outer ring end plate side pin accommodating hole is small, the axial thickness of the outer ring end plate is reduced to the same level as or close to the axial depth of the outer ring end plate side pin accommodating hole. However, it is possible to secure the strength of the connecting portion between the outer ring end plate and the output shaft. Therefore, the axial thickness of the outer ring end plate can be suppressed, and the axial dimension of the rotation transmission device can be suppressed.

It is preferable to use needle roller bearings as the input shaft side rolling bearing and the outer ring end plate side rolling bearing.

In this way, the needle roller bearing is thinner in the radial direction than other bearings (ball bearings, etc.), so the inner diameter of the input shaft side pin accommodating hole for press-fitting the input shaft side rolling bearing is set small. It becomes possible. Therefore, the outer diameter of the shaft end of the input shaft can be suppressed, and the radial dimension of the rotation transmission device can be suppressed. In addition, since needle roller bearings are thinner in the radial direction than other bearings (ball bearings, etc.), the inner diameter of the outer ring end plate side pin accommodating hole for press-fitting the outer ring end plate side rolling bearing should be set small. Is possible. Therefore, the axial thickness of the outer ring end plate can be suppressed, and the axial dimension of the rotation transmission device can be suppressed.

The input shaft is preferably formed as a seamless integrated member from the protruding portion from the housing to the outer peripheral engaging surface on the outer periphery of the accommodating portion in the housing.

In this way, the portion of the input shaft from the protruding portion from the housing to the outer peripheral engaging surface is seamlessly integrated. Therefore, for example, the input shaft is accommodated in the housing from the protruding portion from the housing. The position accuracy of the outer peripheral engaging surface is higher than that of the case where the main body portion penetrating in the axial direction and the annular member fitted to the outer periphery of the main body portion are provided and the outer peripheral engaging surface is provided on the outer peripheral surface of the annular member. Can be enhanced. Therefore, it is possible to effectively stabilize the operation of the engaging element incorporated between the outer peripheral engaging surface on the outer circumference of the input shaft and the inner peripheral engaging surface on the inner circumference of the outer ring.

In the rotation transmission device of the present invention, the connecting pin connecting the shaft end of the input shaft and the outer ring end plate prevents the relative movement of the input shaft between the shaft end and the outer ring end plate in the direction perpendicular to the axis. Even when a radial load in a direction that causes an axis tilt is applied between the shaft and the output shaft, the axis tilt is unlikely to occur between the input shaft and the output shaft. Therefore, even when a radial load in a direction that causes an inclination of the axis line acts between the input shaft and the output shaft, the outer peripheral engaging surface on the outer circumference of the input shaft and the inner circumference of the outer ring integrally formed with the output shaft are applied. The distance from the inner peripheral engaging surface of the input shaft does not change easily, and the operation of the engager incorporated between the outer peripheral engaging surface on the outer circumference of the input shaft and the inner peripheral engaging surface on the inner circumference of the outer ring can be stabilized. It is possible.

Sectional drawing which shows the rotation transmission device which concerns on 1st Embodiment of this invention. Sectional view taken along line II-II of FIG. An enlarged cross-sectional view of the vicinity of a pair of rollers showing a state in which the roller cage shown in FIG. 2 has moved from the disengagement position to the engagement position. Sectional view taken along line IV-IV of FIG. Sectional view along the VV line of FIG. Sectional view along the VI-VI line of FIG. (A) is a cross-sectional view taken along the line VII-VII of FIG. 6, and (b) is a relative rotation of the first divided cage and the second divided cage shown in (a), so that the ball is formed into each inclined groove. Cross-sectional view showing a state in which the axial distance between the first split cage and the second split cage is expanded by rolling in the direction away from the deepest portion of the above. Enlarged cross-sectional view of the vicinity of the connecting pin that rotatably connects the shaft end of the input shaft and the outer ring end plate of FIG. Enlarged sectional view of the vicinity of the connecting pin that rotatably connects the shaft end of the input shaft of the rotation transmission device according to the second embodiment and the outer ring end plate. Enlarged sectional view of the vicinity of the connecting pin that rotatably connects the shaft end of the input shaft of the rotation transmission device according to the third embodiment and the outer ring end plate.

FIG. 1 shows a rotation transmission device according to a first embodiment of the present invention. This rotation transmission device has a cylindrical housing 1 having both ends open, an input shaft 2 arranged so that one end is housed in the housing 1, and a cam surface 3 formed on the outer periphery of the input shaft 2 in the radial direction. It has an outer ring 5 having a cylindrical surface 4 facing the inner circumference.

On the outer ring 5, an outer ring end plate 7 facing the shaft end 6 of the input shaft 2 in the axial direction is formed seamlessly and integrally with the outer ring 5. The outer ring end plate 7 closes one end in the axial direction of the tubular outer ring 5 formed so as to surround the outer diameter side of the accommodating portion of the input shaft 2 in the housing 1. In the outer ring end plate 7, an output shaft 8 extending from the outer ring end plate 7 to the side opposite to the side of the input shaft 2 is formed seamlessly and integrally with the outer ring end plate 7.

The output shaft 8 is arranged side by side on the same straight line as the input shaft 2. The input shaft 2 has a spline shaft portion 9 to which rotational torque is input from the outside in a protruding portion from the housing 1. Here, the input shaft 2 is seamlessly integrated from the spline shaft portion 9 in the protruding portion of the input shaft 2 from the housing 1 to the cam surface 3 on the outer periphery of the accommodating portion of the input shaft 2 in the housing 1. It is formed as a member. The output shaft 8 also has a spline shaft portion 10 that outputs rotational torque transmitted from the outer ring 5 to the outside via the outer ring end plate 7 at a protruding portion from the housing 1.

This rotation transmission device includes a plurality of rollers 11a and 11b incorporated between the cam surface 3 and the cylindrical surface 4, a roller cage 12 for holding these rollers 11a and 11b, and a holder for moving the roller cage 12. It has an instrument actuator 13.

As shown in FIGS. 2 and 3, a plurality of cam surfaces 3 are provided at equal intervals in the circumferential direction on the outer periphery of the accommodating portion of the input shaft 2 in the housing 1. The cam surface 3 includes a front cam surface 3a and a rear cam surface 3b arranged behind the input shaft 2 in the normal rotation direction with respect to the front cam surface 3a. A cylindrical surface 4 facing the cam surface 3 in the radial direction is provided on the inner circumference of the outer ring 5.

A pair of rollers 11a and 11b facing each other in the circumferential direction with a roller release spring 14 sandwiched between the cam surface 3 and the cylindrical surface 4 are incorporated. Of the pair of rollers 11a and 11b, the front roller 11a in the forward rotation direction is incorporated between the front cam surface 3a and the cylindrical surface 4, and the rear roller 11b in the forward rotation direction is the rear cam surface 3b and the cylindrical surface 4. It is built in between. The roller release spring 14 presses the rollers 11a and 11b in a direction that widens the distance between the pair of rollers 11a and 11b.

The front cam surface 3a is formed so that the radial distance from the cylindrical surface 4 gradually decreases from the position of the roller 11a toward the front in the normal rotation direction. The rear cam surface 3b is formed so that the radial distance from the cylindrical surface 4 gradually decreases from the position of the roller 11b toward the rear in the normal rotation direction. In FIG. 3, the front cam surface 3a and the rear cam surface 3b are formed so as to be separate planes inclined in opposite directions, but the front cam surface 3a and the rear cam surface 3b are positive on a single plane. It is also possible to form them on the same plane so that the front side portion in the rolling direction is the front cam surface 3a and the rear side portion is the rear cam surface 3b. Further, the front cam surface 3a and the rear cam surface 3b can be curved, but if they are flat as shown in FIG. 3, the processing cost can be reduced.

As shown in FIGS. 1 to 3, the roller cage 12 is a first split cage that supports one of the pair of rollers 11a and 11b facing each other in the circumferential direction with the roller release spring 14 in between. It consists of a 12A and a second split cage 12B that supports the other roller 11b. The first split cage 12A and the second split cage 12B are supported so as to be relatively rotatable, and the pair of rollers 11a and 11b are supported so that the distance between the pair of rollers 11a and 11b changes according to the relative rotation. Are individually supported.

The first split cage 12A has a plurality of pillar portions 15a arranged at intervals in the circumferential direction, and an annular flange portion 16a that connects the ends of the pillar portions 15a to each other. Similarly, the second split cage 12B also has a plurality of pillar portions 15b arranged at intervals in the circumferential direction, and an annular flange portion 16b that connects the ends of these pillar portions 15b to each other.

The pillar portion 15a of the first split cage 12A and the pillar portion 15b of the second split cage 12B have a pair of rollers 11a and 11b facing each other in the circumferential direction with the roller separation spring 14 in between from both sides in the circumferential direction. It is inserted between the inner circumference of the outer ring 5 and the outer circumference of the input shaft 2 so as to be sandwiched.

As shown in FIG. 1, the flange portion 16a of the first split cage 12A and the flange portion 16b of the second split cage 12B have the flange portion 16b of the second split cage 12B as the first split cage. It is arranged so as to face the cam surface 3 in the axial direction with respect to the flange portion 16a of the 12A. The flange portion 16b of the second split cage 12B is provided with a plurality of notches 17 at intervals in the circumferential direction in order to avoid interference with the pillar portion 15a of the first split cage 12A. ..

The inner circumference of the flange portion 16a of the first split cage 12A and the inner circumference of the flange portion 16b of the second split cage 12B are rotatably supported by a cylindrical surface 18 provided on the outer circumference of the input shaft 2. ing. As a result, the first split cage 12A and the second split cage 12B engage the rollers 11a and 11b between the cylindrical surface 4 and the cam surface 3 by widening the distance between the pair of rollers 11a and 11b. Disengagement of the rollers 11a and 11b between the cylindrical surface 4 and the cam surface 3 by narrowing the distance between the engaging position (see FIG. 3) and the pair of rollers 11a and 11b. It can be moved to and from the position (see FIG. 2). The flange portion 16a of the first split cage 12A is supported in the axial direction by the annular convex portion 20 provided on the outer periphery of the input shaft 2 via the thrust bearing 19, whereby the movement in the axial direction is restricted. There is.

As shown in FIG. 4, the spring holder 21 is fixed at a position axially adjacent to the cam surface 3 on the outer circumference of the input shaft 2. The spring holder 21 has a stopper piece 22 located between the pillar portions 15a and 15b facing each other in the circumferential direction with the pair of rollers 11a and 11b sandwiched between them. In this stopper piece 22, when both pillar portions 15a and 15b move in a direction in which the distance between the pair of rollers 11a and 11b is narrowed, the edges on both sides of the stopper piece 22 receive the pillar portions 15a and 15b. As a result, the roller release spring 14 between the pair of rollers 11a and 11b is prevented from being excessively compressed and damaged, and each roller with respect to the cam surface 3 when the distance between the pair of rollers 11a and 11b is narrowed. It is possible to keep the positions of 11a and 11b constant.

As shown in FIG. 5, the spring holder 21 has a spring holding piece 23 that holds the roller release spring 14. The spring holding piece 23 is integrally formed with the stopper piece 22 so as to extend axially between the cylindrical surface 4 and the cam surface 3. The spring holding piece 23 is arranged so as to face the spring support surface 24 (see FIG. 3) formed between the front cam surface 3a and the rear cam surface 3b on the outer periphery of the input shaft 2 in the radial direction. .. A recess 25 for accommodating the roller release spring 14 is formed on the surface of the spring holding piece 23 facing the spring support surface 24. The roller release spring 14 is a compression coil spring. The spring holding piece 23 prevents the roller release spring 14 from falling off from between the cylindrical surface 4 and the cam surface 3 in the axial direction by restricting the movement of the roller release spring 14 by the recess 25.

As shown in FIG. 1, this rotation transmission device places the roller cage 12 (that is, the first split cage 12A and the second split cage 12B) between the cylindrical surface 4 and the cam surface 3 with the roller 11a, Move between the engagement position for engaging 11b (see FIG. 3) and the disengagement position for disengaging the rollers 11a and 11b between the cylindrical surface 4 and the cam surface 3 (see FIG. 2). As the cage actuator 13, an armature 30 movably supported in the axial direction, a rotor 31 arranged so as to face the armature 30 in the axial direction, and an electromagnet 32 that attracts the armature 30 to the rotor 31 by energization. It has a ball lamp mechanism 33 that converts the operation in which the armature 30 is attracted to the rotor 31 into an operation in which the first split cage 12A and the second split cage 12B move from the engaging position to the disengaging position. ..

The armature 30 has an annular disk portion 34 and a cylindrical portion 35 integrally formed so as to extend axially from the outer circumference of the disk portion 34. A cylindrical portion 36 integrally formed so as to extend axially from the outer periphery of the flange portion 16b of the second split cage 12B is press-fitted into the cylindrical portion 35 of the armature 30, and the armature 30 is pressed into the cylindrical portion 35. It is connected to the second split cage 12B so as to move integrally with the second split cage 12B in the axial direction. Further, the armature 30 is supported by a cylindrical surface 37 provided on the annular convex portion 20 on the outer periphery of the input shaft 2 so as to be rotatable and axially movable. Here, the armature 30 is supported in the axial direction at two positions separated from each other in the axial direction (that is, the inner circumference of the armature 30 and the inner circumference of the second split cage 12B) so that the armature 30 can be moved in the posture of the armature 30. Is prevented from tilting in the direction perpendicular to the axis.

The rotor 31 is supported on the outer circumference of the input shaft 2 so as not to move relative to either the axial direction or the circumferential direction by fitting the rotor 31 on the outer circumference of the input shaft 2 with a tightening margin. The rotor 31 and the armature 30 are made of a metal having ferromagnetism. On the surface of the rotor 31 facing the armature 30, a plurality of elongated holes 38 that penetrate the rotor 31 in the axial direction and extend in the circumferential direction are formed at intervals in the circumferential direction.

The electromagnet 32 has a solenoid coil 39 and a field core 40 around which the solenoid coil 39 is wound. The field core 40 is inserted into the end of the housing 1 on the input shaft 2 side and is prevented from coming off by a retaining ring 41. By energizing the solenoid coil 39, the electromagnet 32 forms a magnetic path through the field core 40, the rotor 31, and the armature 30, and attracts the armature 30 to the rotor 31.

As shown in FIGS. 6 and 7 (a) and 7 (b), the ball lamp mechanism 33 is provided on the surface of the flange portion 16a of the first split cage 12A facing the flange portion 16b of the second split cage 12B. The inclined groove 42a provided, the inclined groove 42b provided on the surface of the flange portion 16b of the second split cage 12B facing the flange portion 16a of the first split cage 12A, and the inclined groove 42a and the inclined groove 42b. It consists of a ball 43 incorporated between the two. The inclined groove 42a and the inclined groove 42b are formed so as to extend in the circumferential direction, respectively. Further, the inclined groove 42a has a shape having a groove bottom 45a inclined so as to gradually become shallower in one direction in the circumferential direction from the deepest portion 44a having the deepest axial depth, and the inclined groove 42b also has an axial direction. The shape has a groove bottom 45b that is inclined so as to gradually become shallower in the other direction in the circumferential direction from the deepest portion 44b having the deepest depth. The ball 43 is arranged so as to be sandwiched between the groove bottom 45a and the groove bottom 45b.

In the ball lamp mechanism 33, when the flange portion 16b of the second split cage 12B moves axially toward the flange portion 16a of the first split cage 12A, the balls 43 move in the inclined grooves 42a, respectively. By rolling toward the deepest portions 44a and 44b of 42b, the first split cage 12A and the second split cage 12B rotate relative to each other, and as a result, the pillar portions 15a and the first split cage 12A of the first split cage 12A are rotated. The pillar portion 15b of the split cage 12B of 2 operates so as to move in a direction of narrowing the distance between the pair of rollers 11a and 11b.

The armature 30 is urged away from the rotor 31 by the force of the roller release spring 14. That is, the force with which the roller separation spring 14 shown in FIG. 2 presses the rollers 11a and 11b in the direction of widening the distance between the pair of rollers 11a and 11b is applied to the first split cage 12A and the second split cage 12B. introduce. Then, the circumferential force received by the first split cage 12A and the second split cage 12B is in the direction away from the rotor 31 by the ball lamp mechanism 33 shown in FIGS. 6 and 7 (a) and 7 (b). Is converted into an axial force of and transmitted to the second partition cage 12B. Here, as shown in FIG. 1, since the armature 30 is fixed to the second split cage 12B, the armature 30 is eventually subjected to the force transmitted from the roller release spring 14 via the ball lamp mechanism 33. , It is in a state of being urged away from the rotor 31.

As shown in FIG. 1, the housing 1 includes a large-diameter tubular portion 1a formed in a cylindrical shape for accommodating a cage actuator 13 (armature 30, rotor 31, electromagnet 32, ball lamp mechanism 33) and an outer ring 5. It is composed of a cylindrical small-diameter tubular portion 1b having an inner diameter smaller than the inner diameter of the large-diameter tubular portion 1a, and a connecting portion 1c that connects the large-diameter tubular portion 1a and the small-diameter tubular portion 1b. The large-diameter cylinder portion 1a and the small-diameter cylinder portion 1b are arranged so that the large-diameter cylinder portion 1a is located on the input shaft 2 side and the small-diameter cylinder portion 1b is located on the output shaft 8 side. The end of the input shaft 2 opposite to the shaft end 6 side protrudes from the large diameter cylinder portion 1a, and the side opposite to the side connected to the outer ring end plate 7 of the output shaft 8 from the small diameter cylinder portion 1b. The end of the is protruding. Further, the large-diameter tubular portion 1a faces the outer circumference of the outer ring 5 and the outer ring end plate 7 in the radial direction, the small-diameter tubular portion 1b faces the outer circumference of the output shaft 8 in the radial direction, and the connecting portion 1c faces the outer ring end. It is in a state of facing the plate 7 in the axial direction. The connecting portion 1c is formed so that the inner diameter decreases from the large-diameter tubular portion 1a side toward the small-diameter tubular portion 1b side.

The large-diameter tubular portion 1a is formed with a fixing flange 46 that projects radially outward from the outer circumference of the large-diameter tubular portion 1a. A through hole 47 in the axial direction is formed in the fixing flange 46, and the fixing flange 46 can be fixed to the support member 68 by inserting a bolt 67 into the through hole 47 and tightening the bolt 67. There is.

The field core 40 is fitted to the inner circumference of the large-diameter tubular portion 1a of the housing 1. A retaining ring 41 for preventing the field core 40 from coming off is mounted on the inner circumference of the end of the large-diameter tubular portion 1a opposite to the small-diameter tubular portion 1b. A bearing fitting cylinder 48 is fixedly provided on the surface of the field core 40 opposite to the side on which the armature 30 is attracted. The bearing fitting cylinder 48 may be provided by fixing the bearing fitting cylinder 48 formed separately from the field core 40 to the field core 40 by welding or the like, and the bearing fitting cylinder 48 is jointed with the field core 40. It may be formed integrally without.

A first bearing 49 that rotatably supports the input shaft 2 is incorporated between the inner circumference of the bearing fitting cylinder 48 and the outer circumference of the input shaft 2. The first bearing 49 is, for example, a deep groove ball bearing. A retaining ring 50 for preventing the first bearing 49 from coming off is mounted on the inner circumference of the bearing fitting cylinder 48.

As shown in FIG. 8, a second bearing 51 that rotatably supports the output shaft 8 is incorporated in the inner circumference of the small diameter tubular portion 1b of the housing 1. The second bearing 51 is, for example, a deep groove ball bearing. A cylindrical second bearing fitting surface 52 into which the second bearing 51 is fitted is provided on the outer periphery of the output shaft 8. The second bearing 51 has an outer ring 53 fitted to the inner circumference of the small-diameter tubular portion 1b, an inner ring 54 fitted to the second bearing fitting surface 52, and an interval in the circumferential direction between the outer ring 53 and the inner ring 54. It has a plurality of rolling elements 55 provided therein. The second bearing 51 is assembled so that the axial end surface of the inner ring 54 contacts the outer ring end plate 7, and the inner peripheral surface of the inner ring 54 contacts the outer circumference of the output shaft 8.

As shown in FIG. 1, on the outer periphery of the accommodating portion of the input shaft 2 in the housing 1, a third cylindrical shape having a diameter smaller than that of the cam surface 3 adjacent to the cam surface 3 on the output shaft 8 side. A bearing fitting surface 56 is formed. On the inner circumference of the outer ring 5, a cylindrical surface 57 having a diameter smaller than that of the cylindrical surface 4 is formed adjacent to the output shaft 8 with respect to the cylindrical surface 4. Here, the third bearing fitting surface 56 and the cylindrical surface 57 of the outer ring 5 are opposed to each other in the radial direction. A third bearing 58 that connects the input shaft 2 and the outer ring 5 so as to be relatively rotatable is incorporated between the third bearing fitting surface 56 and the cylindrical surface 57. The third bearing 58 is, for example, a deep groove ball bearing.

Further, a ring plate-shaped washer 59 is mounted on the third bearing fitting surface 56 on the cam surface 3 side with respect to the third bearing 58. The washer 59 is formed to have a diameter larger than that of the cam surface 3 so as to have a portion facing the axial end faces of the rollers 11a and 11b, and by restricting the axial movement of the rollers 11a and 11b, the rollers 11a and 11b can be moved. It prevents the cam surface 3 from protruding in the axial direction.

As shown in FIG. 8, between the shaft end 6 of the input shaft 2 and the outer ring end plate 7, the relative movement of the shaft end 6 of the input shaft 2 and the outer ring end plate 7 in the direction perpendicular to the axis is restricted. A connecting pin 60 that connects the shaft end 6 of the input shaft 2 and the outer ring end plate 7 so as to be relatively rotatable is incorporated. Here, the connecting pin 60 is a columnar protrusion seamlessly and integrally formed with the shaft end 6 of the input shaft 2 so as to project from the shaft end 6 of the input shaft 2 toward the outer ring end plate 7.

A pin accommodating hole 61 for accommodating the connecting pin 60 is formed in the outer ring end plate 7, and the connecting pin 60 is rotatably supported by a rolling bearing 62 press-fitted into the pin accommodating hole 61. The pin accommodating hole 61 is a bottomed cylindrical hole having a cylindrical inner circumference. The rolling bearing 62 is a needle roller bearing having a plurality of needle rollers 63 arranged at intervals in the circumferential direction and a cage 64 for holding the needle rollers 63. The needle-shaped roller 63 has a diameter of 4 mm or less (preferably 3 mm or less), and the length is set in the range of 3 to 10 times the diameter. On the outer diameter side of the needle-shaped roller 63, a shell-shaped outer ring 65 with which the needle-shaped roller 63 rolls and contacts is mounted. The shell-shaped outer ring 65 is a thin outer ring having a thickness of 1 mm or less (preferably 0.8 mm or less), and an inward flange portion 66 that regulates the axial movement range of the needle-shaped rollers 63 at both ends in the axial direction. Is formed. The shell-shaped outer ring 65 is inserted into the pin accommodating hole 61 with a tightening allowance. The needle-shaped roller 63 is in rolling contact with the outer peripheral surface of the connecting pin 60.

The inner diameter D ₁ of the pin accommodating hole 61 is smaller than the outer diameter d ₁ of the second bearing fitting surface 52. Specifically, the inner diameter D ₁ of the pin accommodating hole 61 is set to a size of 75% or less (preferably 70% or less) of the outer diameter d ₁ of the second bearing fitting surface 52. The outer diameter d ₂ of the connecting pin 60 is smaller than the outer diameter d ₃ of the third bearing fitting surface 56. Specifically, the outer diameter d ₂ of the connecting pin 60 is set to a size of 50% or less (preferably 40% or less) of the outer diameter d ₃ of the third bearing fitting surface 56.

An operation example of this rotation transmission device will be described.

As shown in FIG. 1, when the electromagnet 32 is energized, the rotation transmission device is in an disengaged state (idling state) in which rotation transmission between the input shaft 2 and the output shaft 8 is cut off. That is, when the electromagnet 32 is energized, the armature 30 is attracted to the rotor 31, and in conjunction with the operation of the armature 30, the flange portion 16b of the second split cage 12B becomes the flange portion 16a of the first split cage 12A. Move in the axial direction toward. At this time, the ball 43 of the ball lamp mechanism 33 rolls toward the deepest portions 44a, 44b of the inclined grooves 42a, 42b, so that the first split cage 12A and the second split cage 12B rotate relative to each other. .. Then, due to the relative rotation of the first split cage 12A and the second split cage 12B, the pillar portion 15a of the first split cage 12A and the pillar portion 15b of the second split cage 12B are paired. The rollers 11a and 11b are pressed in the direction in which the distance between the rollers 11a and 11b is narrowed, and as a result, the front roller 11a in the normal rotation direction is in an engagement standby state (the front roller 11a and the cylindrical surface 4 in the normal rotation direction). Although there is a small gap between them, when the input shaft 2 rotates in the reverse direction, the roller 11a immediately engages between the cylindrical surface 4 and the front cam surface 3a), and the rear side in the normal rotation direction is released. The roller 11b is in an engagement standby state (there is a minute gap between the roller 11b on the rear side in the forward rotation direction and the cylindrical surface 4, but when the input shaft 2 rotates in the forward rotation direction, the roller 11b immediately moves to the cylindrical surface 4 and the rear cam. The state of being engaged between the surfaces 3b) is also released. In this state, even if rotation is input to the input shaft 2, the rotation is not transmitted from the input shaft 2 to the outer ring 5, and the input shaft 2 idles.

On the other hand, when the energization of the electromagnet 32 is stopped, the rotation transmission device is in an engaged state in which rotation is transmitted between the input shaft 2 and the output shaft 8. That is, when the energization of the electromagnet 32 is stopped, the armature 30 moves axially in the direction away from the rotor 31 by the force of the roller separation spring 14. At this time, due to the force of the roller separation spring 14 that presses the rollers 11a and 11b in the direction in which the distance between the pair of rollers 11a and 11b is widened, the roller 11a on the front side in the forward rotation direction is a cylinder on the inner circumference of the outer ring 5. The roller 11b, which is engaged between the surface 4 and the front cam surface 3a on the outer circumference of the input shaft 2 and is on the rear side in the normal rotation direction, is formed on the cylindrical surface 4 on the inner circumference of the outer ring 5 and the outer circumference of the input shaft 2. It is in a state of being engaged with the rear cam surface 3b. When the input shaft 2 rotates in the forward rotation direction in this state, the rotation is transmitted from the input shaft 2 to the outer ring 5 via the roller 11b on the rear side in the forward rotation direction. Further, when the input shaft 2 rotates in the reverse direction, the rotation is transmitted from the input shaft 2 to the outer ring 5 via the roller 11a on the front side in the forward rotation direction.

By the way, when the above rotation transmission device is assembled to an automobile, the protruding portion of the input shaft 2 from the housing 1 is connected to a drive side shaft (not shown), and the protruding portion of the output shaft 8 from the housing 1 is not shown. Further, the fixing flange 46 on the outer periphery of the housing 1 is fixed to a support member 68 (not shown) with bolts 67. At this time, depending on the relative positional relationship between the position of the drive side shaft connecting the input shaft 2, the position of the driven side shaft connecting the output shaft 8, and the position of the support member 68 fixing the housing 1, the rotation transmission device can be used. May have a radial load acting between the input shaft 2 and the output shaft 8 in a direction that causes the axis to tilt.

Then, due to this radial load, a slight inclination of the axis line may occur between the input shaft 2 and the output shaft 8 of the rotation transmission device. At this time, since the distance between the cam surface 3 on the outer periphery of the input shaft 2 and the cylindrical surface 4 on the inner circumference of the outer ring 5 integrally formed with the output shaft 8 changes slightly, the cam surface 3 and the cylindrical surface 4 The operation of the rollers 11a and 11b incorporated between them may become unstable (for example, the distance between the cam surface 3 and the cylindrical surface 4 becomes narrower than it should be, so that the roller between the cam surface 3 and the cylindrical surface 4 becomes unstable. It is possible that the rollers 11a and 11b are mis-engaged, or that the rollers 11a and 11b are excessively strongly engaged between the cam surface 3 and the cylindrical surface 4 so that the rollers 11a and 11b cannot be disengaged. There is sex).

In response to this problem, in the above rotation transmission device, the connecting pin 60 that connects the shaft end 6 of the input shaft 2 and the outer ring end plate 7 is a shaft between the shaft end 6 of the input shaft 2 and the outer ring end plate 7. Since the relative movement in the perpendicular direction is prevented, the inclination of the axis line is tilted between the input shaft 2 and the output shaft 8 even when a radial load in a direction causing the inclination of the axis line is applied between the input shaft 2 and the output shaft 8. Is unlikely to occur. Therefore, even when a radial load in a direction that causes an inclination of the axis line acts between the input shaft 2 and the output shaft 8, the outer ring formed integrally with the cam surface 3 on the outer periphery of the input shaft 2 and the output shaft 8. The distance between the inner circumference of the 5 and the cylindrical surface 4 is difficult to change, and the operation of the rollers 11a and 11b incorporated between the outer cam surface 3 of the input shaft 2 and the inner peripheral cylindrical surface 4 of the outer ring 5 is stable. It is possible to make it.

Further, since this rotation transmission device employs, as the connecting pin 60, a columnar protrusion seamlessly formed integrally with the shaft end 6 of the input shaft 2 so as to protrude from the shaft end 6 of the input shaft 2. , The outer circumference of the connecting pin 60 can be machined at the same time in the step of machining the outer circumference of the input shaft 2. Therefore, it is possible to process the outer circumference of the connecting pin 60 at low cost and in a state where the axis is completely aligned with the input shaft 2.

Further, in this rotation transmission device, since the inner diameter D ₁ of the pin accommodating hole 61 is smaller than the outer diameter d ₁ of the second bearing fitting surface 52, the axial thickness of the outer ring end plate 7 can be accommodated by the pin. It is possible to secure the strength of the connecting portion between the outer ring end plate 7 and the output shaft 8 even if the hole 61 is thinned to a thickness as low as or close to the axial depth of the hole 61. Therefore, the axial thickness of the outer ring end plate 7 can be suppressed, and the axial dimension of the rotation transmission device can be suppressed.

Further, in this rotation transmission device, since the outer diameter d ₂ of the connecting pin 60 is smaller than the outer diameter d ₃ of the third bearing fitting surface 56, the inner diameter of the pin accommodating hole 61 accommodating the connecting pin 60 is set. It is possible to set D ₁ small. Therefore, the axial thickness of the outer ring end plate 7 can be suppressed, and the axial dimension of the rotation transmission device can be suppressed.

Further, since this rotation transmission device employs a needle roller bearing whose radial thickness is thinner than other bearings (ball bearings, etc.) as the rolling bearing 62, a pin accommodating hole for press-fitting the rolling bearing 62. It is possible to set the inner diameter D ₁ of 61 to be small. Therefore, the axial thickness of the outer ring end plate 7 can be suppressed, and the axial dimension of the rotation transmission device can be suppressed.

Further, in this rotation transmission device, the portion of the input shaft 2 protruding from the housing 1 from the spline shaft portion 9 to the cam surface 3 is formed as a seamless integral body. Therefore, for example, the input shaft 2 is housed. It is composed of a main body portion that penetrates axially from the protruding portion from 1 to the accommodating portion in the housing 1 and an annular member that fits on the outer periphery of the main body portion, and a cam surface 3 is provided on the outer periphery of the annular member. The position accuracy of the cam surface 3 is higher than in the case. Therefore, it is possible to effectively stabilize the operation of the rollers 11a and 11b incorporated between the cam surface 3 and the cylindrical surface 4.

FIG. 9 shows a second embodiment of the present invention. The second embodiment differs from the first embodiment only in the configuration of the connecting pin 60, and the other configurations are the same. Therefore, the parts corresponding to the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

Between the shaft end 6 of the input shaft 2 and the outer ring end plate 7, the shaft end 6 of the input shaft 2 is restricted from the relative movement of the shaft end 6 of the input shaft 2 and the outer ring end plate 7 in the direction perpendicular to the axis. A connecting pin 60 for connecting the outer ring end plate 7 and the outer ring end plate 7 so as to be relatively rotatable is incorporated. Here, the connecting pin 60 is a columnar member having a constant outer diameter over the entire length in the axial direction.

One end of the connecting pin 60 is housed in an input shaft side pin accommodating hole 70 formed in the shaft end 6 of the input shaft 2, and the other end of the connecting pin 60 is an outer ring end plate side pin formed in the outer ring end plate 7. It is housed in the storage hole 71. The input shaft side pin accommodating hole 70 is a bottomed cylindrical hole having a cylindrical inner circumference. The outer ring end plate side pin accommodating hole 71 is also a bottomed cylindrical hole having a cylindrical inner circumference. The inner diameter D ₂ of the outer ring end plate side pin accommodating hole 71 is smaller than the inner diameter D ₃ of the input shaft side pin accommodating hole 70.

One end side portion of the connecting pin 60 is rotatably supported by a rolling bearing 72 press-fitted into the input shaft side pin accommodating hole 70. Here, the third bearing 58 and the rolling bearing 72 are arranged so as to have a portion overlapping in the axial direction. The other end of the connecting pin 60 is press-fitted into the outer ring end plate side pin accommodating hole 71. That is, the connecting pin 60 is inserted into the outer ring end plate side pin accommodating hole 71 with a tightening allowance. The inner diameter D ₂ of the outer ring end plate side pin accommodating hole 71 is smaller than the outer diameter d ₁ (see FIG. 8) of the second bearing fitting surface 52. Specifically, the inner diameter D ₂ of the outer ring end plate side pin accommodating hole 71 has a size of 65% or less (preferably 55% or less) of the outer diameter d ₁ (see FIG. 8) of the second bearing fitting surface 52. Is set to.

The rolling bearing 72 is a needle roller bearing having a plurality of needle rollers 73 arranged at intervals in the circumferential direction and a cage 74 for holding the needle rollers 73. The needle roller 73 has a diameter of 4 mm or less (preferably 3 mm or less), and the length is set in the range of 3 to 10 times the diameter. On the outer diameter side of the needle-shaped roller 73, a shell-shaped outer ring 75 with which the needle-shaped roller 73 rolls and comes into contact is mounted. The shell-shaped outer ring 75 is a thin outer ring having a thickness of 1 mm or less (preferably 0.8 mm or less), and an inward flange portion 76 that regulates the axial movement range of the needle-shaped rollers 73 at both ends in the axial direction. Is formed. The shell type outer ring 75 is inserted into the input shaft side pin accommodating hole 70 with a tightening allowance. A needle-shaped roller 73 is in rolling contact with the outer peripheral surface of the connecting pin 60.

By the way, the input shaft 2 side and the outer ring end plate 7 side having the configuration shown in FIG. 9 are exchanged, the connecting pin 60 is press-fitted into the input shaft side pin accommodating hole 70, and the rolling bearing 72 is inserted into the outer ring end plate side pin accommodating hole 71. It is also possible to press-fit. On the other hand, in this rotation transmission device, as shown in FIG. 9, the connecting pin 60 is directly press-fitted into the outer ring end plate side pin accommodating hole 71 without using a rolling bearing, so that the outer ring end plate side It is possible to more effectively suppress the inner diameter D ₂ of the pin accommodating hole 71. Therefore, the axial thickness of the outer ring end plate 7 can be suppressed, and the axial dimension of the rotation transmission device can be suppressed. Further, since the connecting pin 60 uses a columnar member independent of both the input shaft 2 and the outer ring end plate 7, the connecting pin 60 can be manufactured at low cost.

Further, since this rotation transmission device is arranged so that the third bearing 58 and the rolling bearing 72 have a portion where they overlap in the axial direction, it is possible to effectively suppress the axial length of the rotation transmission device. It has become.

Further, in this rotation transmission device, since the inner diameter D ₂ of the outer ring end plate side pin accommodating hole 71 is smaller than the outer diameter d ₁ (see FIG. 8) of the second bearing fitting surface 52, the shaft of the outer ring end plate 7 Even if the directional thickness is reduced to the same level as or close to the axial depth of the outer ring end plate side pin accommodating hole 71, the strength of the connecting portion between the outer ring end plate 7 and the output shaft 8 can be secured. is there. Therefore, the axial thickness of the outer ring end plate 7 can be suppressed, and the axial dimension of the rotation transmission device can be suppressed.

Further, since this rotation transmission device employs a needle roller bearing whose radial thickness is thinner than that of other bearings (ball bearings, etc.) as the rolling bearing 72, the input shaft side into which the rolling bearing 72 is press-fitted is adopted. it is possible to set small the inner diameter D ₃ of the pin receiving hole 70. Therefore, the outer diameter of the shaft end 6 of the input shaft 2 can be suppressed, and the radial dimension of the rotation transmission device can be suppressed.

FIG. 10 shows a third embodiment of the present invention. The third embodiment differs from the first embodiment only in the configuration of the connecting pin 60, and the other configurations are the same. Therefore, the parts corresponding to the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

Between the shaft end 6 of the input shaft 2 and the outer ring end plate 7, the shaft end 6 of the input shaft 2 is restricted from the relative movement of the shaft end 6 of the input shaft 2 and the outer ring end plate 7 in the direction perpendicular to the axis. A connecting pin 60 for connecting the outer ring end plate 7 and the outer ring end plate 7 so as to be relatively rotatable is incorporated. Here, the connecting pin 60 is a columnar member having a constant outer diameter over the entire length in the axial direction.

One end of the connecting pin 60 is housed in an input shaft side pin accommodating hole 80 formed in the shaft end 6 of the input shaft 2, and the other end of the connecting pin 60 is an outer ring end plate side pin formed in the outer ring end plate 7. It is housed in the storage hole 81. The input shaft side pin accommodating hole 80 is a bottomed cylindrical hole having a cylindrical inner circumference. The outer ring end plate side pin accommodating hole 81 is also a bottomed cylindrical hole having a cylindrical inner circumference. The inner diameter D ₄ of the outer ring end plate side pin accommodating hole 81 has the same diameter as the inner diameter D ₅ of the input shaft side pin accommodating hole 80.

One end side portion of the connecting pin 60 is rotatably supported by an input shaft side rolling bearing 82 press-fitted into the input shaft side pin accommodating hole 80. Here, the third bearing 58 and the input shaft side rolling bearing 82 are arranged so as to have a portion overlapping in the axial direction. The other end side portion of the connecting pin 60 is rotatably supported by the outer ring end plate side rolling bearing 83 press-fitted into the outer ring end plate side pin accommodating hole 81. The inner diameter D ₄ of the outer ring end plate side pin accommodating hole 81 is smaller than the outer diameter d ₁ (see FIG. 8) of the second bearing fitting surface 52. Specifically, the inner diameter D ₄ of the outer ring end plate side pin accommodating hole 81 has a size of 65% or less (preferably 55% or less) of the outer diameter d ₁ (see FIG. 8) of the second bearing fitting surface 52. Is set to.

The input shaft side rolling bearing 82 is a needle roller bearing having a plurality of needle rollers 84 arranged at intervals in the circumferential direction and a cage 85 for holding the needle rollers 84. The needle-shaped roller 84 has a diameter of 4 mm or less (preferably 3 mm or less), and the length is set in the range of 3 to 10 times the diameter. On the outer diameter side of the needle-shaped roller 84, a shell-shaped outer ring 86 with which the needle-shaped roller 84 rolls and comes into contact is mounted. The shell-shaped outer ring 86 is a thin outer ring having a thickness of 1 mm or less (preferably 0.8 mm or less), and an inward flange portion 87 that regulates the axial movement range of the needle-shaped rollers 84 at both ends in the axial direction. Is formed. The shell type outer ring 86 is inserted into the input shaft side pin accommodating hole 80 with a tightening allowance. A needle-shaped roller 84 is in rolling contact with the outer peripheral surface of the connecting pin 60. The outer ring end plate side rolling bearing 83 is a needle roller bearing having the same configuration as the input shaft side rolling bearing 82.

In this rotation transmission device, the shaft end 6 of the input shaft 2 and the outer ring end plate 7 are connected by the connecting pin 60 via two rolling bearings, an input shaft side rolling bearing 82 and an outer ring end plate side rolling bearing 83. Therefore, the transmission of rotation via the connecting pin 60 can be prevented extremely effectively. Therefore, it is possible to suppress the rotational torque transmitted from the input shaft 2 to the output shaft 8 via the connecting pin 60 to be extremely small in the idling state in which the transmission of rotation from the input shaft 2 to the output shaft 8 is cut off.

Further, since this rotation transmission device is arranged so that the third bearing 58 and the input shaft side rolling bearing 82 have a portion where they overlap in the axial direction, the axial length of the rotation transmission device can be effectively suppressed. Is possible.

Further, in this rotation transmission device, since the inner diameter D ₄ of the outer ring end plate side pin accommodating hole 81 is smaller than the outer diameter d ₁ (see FIG. 8) of the second bearing fitting surface 52, the shaft of the outer ring end plate 7 Even if the directional thickness is reduced to the same level as or close to the axial depth of the outer ring end plate side pin accommodating hole 81, the strength of the connecting portion between the outer ring end plate 7 and the output shaft 8 can be secured. is there. Therefore, the axial thickness of the outer ring end plate 7 can be suppressed, and the axial dimension of the rotation transmission device can be suppressed.

Further, since this rotation transmission device employs a needle roller bearing that is thinner in the radial direction than other bearings (ball bearings, etc.) as the input shaft side rolling bearing 82, the input shaft side rolling bearing 82 It is possible to set the inner diameter D ₅ of the input shaft side pin accommodating hole 80 for press-fitting to be small. Therefore, the outer diameter of the shaft end 6 of the input shaft 2 can be suppressed, and the radial dimension of the rotation transmission device can be suppressed. Further, as the outer ring end plate side rolling bearing 83, a needle roller bearing having a thinner radial thickness than other bearings (ball bearings, etc.) is adopted, so that the outer ring for press-fitting the outer ring end plate side rolling bearing 83. It is possible to set the inner diameter D ₄ of the end plate side pin accommodating hole 81 to be small. Therefore, the axial thickness of the outer ring end plate 7 can be suppressed, and the axial dimension of the rotation transmission device can be suppressed.

In the above embodiment, the cam surface 3 is used as the outer peripheral engaging surface of the input shaft 2, the cylindrical surface 4 is used as the inner peripheral engaging surface of the outer ring 5, and the outer peripheral engaging surface (cam surface 3) is engaged with the inner circumference. An example in which rollers 11a and 11b are used as engaging elements to be engaged between the surfaces (cylindrical surface 4) has been described, but the present invention includes a rotation transmission device using a ball as an engaging element and outer peripheral engagement. The same can be applied to a rotation transmission device in which both the surface and the inner peripheral engaging surface are cylindrical surfaces and a sprag is adopted as an engaging element that engages between the two cylindrical surfaces.

It should be considered that the embodiments disclosed this time are exemplary in all respects and not restrictive. The scope of the present invention is shown by the scope of claims rather than the above description, and is intended to include all modifications within the meaning and scope equivalent to the scope of claims.

1 Housing 2 Input shaft 3 Cam surface 4 Cylindrical surface 5 Outer ring 6 Shaft end 7 Outer ring end plate 8 Output shaft 11a, 11b Roller 12 Roller cage 13 Cage actuator 49 1st bearing 51 2nd bearing 52 2nd bearing fitting surface 56 Third bearing fitting surface 58 Third bearing 60 Connecting pin 61 Pin accommodating hole 62 Rolling bearing 70 Input shaft side pin accommodating hole 71 Outer ring end plate side pin accommodating hole 72 Rolling bearing 80 Input shaft side pin accommodating hole 81 Outer ring end plate Side pin accommodating hole 82 Input shaft side rolling bearing 83 Outer ring end plate side rolling bearing d ₁ Outer diameter d ₂ Outer diameter d ₃ Outer diameter D ₁ Inner diameter D ₂ Inner diameter D ₄ Inner diameter

Claims (14)

A tubular housing (1) with both ends open and
An input shaft (2) having one end accommodated in the housing (1) and having an outer peripheral engaging surface (3) on the outer periphery of the accommodating portion in the housing (1).
An outer ring (5) having an inner peripheral engaging surface (4) facing the outer peripheral engaging surface (3) in the radial direction on the inner circumference.
An outer ring end plate (7) formed integrally with the outer ring (5) and facing the shaft end (6) of the input shaft (2) in the axial direction.
An output shaft (8) formed integrally with the outer ring end plate (7) and extending from the outer ring end plate (7) to a side opposite to the side of the input shaft (2).
With the engaging elements (11a, 11b) incorporated between the outer peripheral engaging surface (3) and the inner peripheral engaging surface (4),
The engagement position at which the engaging elements (11a, 11b) are engaged between the outer peripheral engaging surface (3) and the inner peripheral engaging surface (4) and the engagement of the engaging elements (11a, 11b) are engaged. An engager cage (12) movably supported between the disengagement position to be disengaged and
A cage actuator (13) that moves the engager cage (12) between the engagement position and the disengagement position.
A first bearing (49) that rotatably supports the input shaft (2) and
A second bearing (51) that rotatably supports the output shaft (8) and
A third bearing (58) that is incorporated between the outer circumference of the input shaft (2) and the inner circumference of the outer ring (5) and connects the input shaft (2) and the outer ring (5) so as to be relatively rotatable. In the rotation transmission device having
It is characterized by providing a connecting pin (60) for connecting the shaft end (6) of the input shaft (2) and the outer ring end plate (7) so as to be relatively rotatable in a state where relative movement in the direction perpendicular to the shaft is restricted. Rotation transmission device. The connecting pin (60) is jointed with the shaft end (6) of the input shaft (2) so as to project from the shaft end (6) of the input shaft (2) toward the outer ring end plate (7). There are no integrally formed columnar protrusions,
A pin accommodating hole (61) accommodating the connecting pin (60) is formed in the outer ring end plate (7), and the connecting pin (60) is formed by a rolling bearing (62) press-fitted into the pin accommodating hole (61). The rotation transmission device according to claim 1, which is rotatably supported. A cylindrical second bearing fitting surface (52) into which the second bearing (51) is fitted is provided on the outer periphery of the output shaft (8).
The rotation transmission device according to claim 2, wherein the inner diameter (D ₁ ) of the pin accommodating hole (61) is smaller than the outer diameter (d ₁ ) of the second bearing fitting surface (52). A cylindrical third bearing fitting surface (56) into which the third bearing (58) is fitted is provided on the outer periphery of the input shaft (2).
The rotation transmission device according to claim 2 or 3, wherein the outer diameter (d ₂ ) of the connecting pin (60) is smaller than the outer diameter (d ₃ ) of the third bearing fitting surface (56). .. The rotation transmission device according to any one of claims 2 to 4, wherein a needle roller bearing is used as the rolling bearing (62). One end of the connecting pin (60) is housed in an input shaft side pin accommodating hole (70) formed at the shaft end (6) of the input shaft (2), and the other end is housed in the outer ring end plate (7). It is a columnar member accommodated in the formed outer ring end plate side pin accommodating hole (71).
One end side portion of the connecting pin (60) is rotatably supported by a rolling bearing (72) press-fitted into the input shaft side pin accommodating hole (70), and the other end side portion of the connecting pin (60) is said. The rotation transmission device according to claim 1, wherein the rotation transmission device is press-fitted into the outer ring end plate side pin accommodating hole (71). The rotation transmission device according to claim 6, wherein the third bearing (58) and the rolling bearing (72) are arranged so as to have a portion that overlaps in the axial direction. A cylindrical second bearing fitting surface (52) into which the second bearing (51) is fitted is provided on the outer periphery of the output shaft (8).
The sixth or seven claim, wherein the inner diameter (D ₂ ) of the outer ring end plate side pin accommodating hole (71) is smaller than the outer diameter (d ₁ ) of the second bearing fitting surface (52). Rotation transmission device. The rotation transmission device according to any one of claims 6 to 8, wherein a needle roller bearing is used as the rolling bearing (72). One end of the connecting pin (60) is housed in an input shaft side pin accommodating hole (80) formed at the shaft end (6) of the input shaft (2), and the other end is housed in the outer ring end plate (7). It is a columnar member accommodated in the formed outer ring end plate side pin accommodating hole (81).
One end side portion of the connecting pin (60) is rotatably supported by an input shaft side rolling bearing (82) press-fitted into the input shaft side pin accommodating hole (80), and the other end side of the connecting pin (60). The rotation transmission device according to claim 1, wherein the portion is rotatably supported by an outer ring end plate side rolling bearing (83) press-fitted into the outer ring end plate side pin accommodating hole (81). The rotation transmission device according to claim 10, wherein the third bearing (58) and the input shaft side rolling bearing (82) are arranged so as to have a portion overlapping in the axial direction. A cylindrical second bearing fitting surface (52) into which the second bearing (51) is fitted is provided on the outer periphery of the output shaft (8).
The method according to claim 10 or 11, wherein the inner diameter (D ₄ ) of the outer ring end plate side pin accommodating hole (81) is smaller than the outer diameter (d ₁ ) of the second bearing fitting surface (52). Rotation transmission device. The rotation transmission device according to any one of claims 10 to 12, wherein a needle roller bearing is adopted as the input shaft side rolling bearing (82) and the outer ring end plate side rolling bearing (83). The input shaft (2) is formed as a seamless integral member from the protruding portion from the housing (1) to the outer peripheral engaging surface (3) on the outer periphery of the accommodating portion in the housing (1). The rotation transmission device according to any one of claims 1 to 13.

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