JP2021001674A - Rotation transmission device and manufacturing method of the same - Google Patents

Abstract

To provide a rotation transmission device which enables stable operation of engagement elements between an inner ring and an outer ring.SOLUTION: A rotation transmission device has: a first radial bearing 49 rotatably supporting an input shaft 2; a second radial bearing 51 rotatably supporting an output shaft 3; and a third radial bearing 56 connecting the inner ring 4 with the outer ring 5 so as to enable relative rotation therebetween. The rotation transmission device is provided with a thrust bearing 62 having rolling elements 60, axially sandwiched between an input shaft end surface 9 and an output shaft end surface 10, and an annular retainer 61 retaining the rolling elements 60. The input shaft end surface 9 is provided with an input shaft side positioning part which prevents radial displacement of the rolling elements 60 relative to the input shaft 2. The output shaft end surface 10 is provided with an output shaft side positioning part which prevents radial displacement of the rolling elements 60 relative to the output shaft 3.SELECTED DRAWING: Figure 1

Description

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

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 tubular housing with both ends open, an input shaft arranged with one end housed in the housing, and coaxial with the input shaft with one end housed in the housing. The output shafts arranged side by side on the top, the inner ring provided in the housing portion of the input shaft in the housing, and the inner ring provided in the housing portion of the output shaft so as to rotate integrally with the output shaft are connected to the housing portion. It has a pair of rollers incorporated between the outer ring, a cylindrical surface on the inner circumference of the outer ring, and a cam surface on the outer circumference of the inner ring, and a roller cage for holding the pair of rollers.

The roller cage consists of two split cages that are supported relative to rotation. The two split cages are in charge of engaging positions for engaging the pair of rollers between the cylindrical surface on the inner circumference of the outer ring and the cam surface on the outer circumference of the inner ring, and disengaging each roller. It is possible to move to and from the release 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 radial bearing (deep groove ball 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 radial bearing (deep groove ball bearing) incorporated between the outer circumference of the output shaft and the inner circumference of the housing. Further, a third radial bearing (deep groove ball bearing) is incorporated between the radial facing surfaces of the inner ring and the outer ring, and the inner ring and the outer ring are connected so as to be relatively rotatable by the third radial bearing.

Japanese Unexamined Patent Publication No. 2013-199993

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, it is a case where the operation of engaging the roller between the outer ring and the inner ring of the rotation transmission device and disengaging the engagement can be stably performed. Even if there is, after assembling the rotation transmission device to the automobile, the operation of engaging the roller between the outer ring and the inner ring of the rotation transmission device and disengaging the engagement may become unstable. It turned out that there was.

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 are set. 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 causing 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 relative positions of the inner ring provided on the input shaft and the outer ring provided on the output shaft are slightly displaced, the operation of the roller incorporated between the inner ring and the outer ring may become unstable (for example). When the gap between the outer ring and the inner ring becomes narrower than it should be, the roller misengages between the outer ring and the inner ring, or the roller bites excessively strongly between the outer ring and the inner ring, and the roller is disengaged. It turns out that there is a possibility that you will not be able to do it.

An object to be solved by the present invention is to provide a rotation transmission device in which an engager between an inner ring and an outer ring operates stably.

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 that is arranged so that one end is housed in the housing and has an input shaft end face at the end on the side housed in the housing.
It is arranged coaxially with the input shaft with one end housed in the housing, and has an output shaft end face axially opposed to the input shaft end face at the end on the side housed in the housing. Output axis and
An inner ring provided in a housing portion of the input shaft so as to rotate integrally with the input shaft.
An outer ring formed in an annular shape, which is provided by being connected to a housing portion of the output shaft so as to rotate integrally with the output shaft and surrounds the inner ring.
An engaging element incorporated between the inner circumference of the outer ring and the outer circumference of the inner ring,
An engaging element cage movably supported between an engaging position for engaging the engaging element between the outer ring and the inner ring and an engaging disengaging position for disengaging the engaging element.
A cage actuator that moves the engager cage between the engagement position and the disengagement position,
A first radial bearing that rotatably supports the input shaft,
A second radial bearing that rotatably supports the output shaft,
In a rotation transmission device having a third radial bearing that connects the inner ring and the outer ring so as to be relatively rotatable.
A thrust bearing having a plurality of rolling elements sandwiched in the axial direction between the input shaft end surface and the output shaft end surface and an annular cage for holding the plurality of rolling elements is provided.
The input shaft end surface is provided with an input shaft side positioning portion for preventing the plurality of rolling elements from being displaced in the radial direction with respect to the input shaft.
A rotation transmission device characterized in that the output shaft end surface is provided with an output shaft side positioning portion that prevents the plurality of rolling elements from being displaced in the radial direction with respect to the output shaft.

In this way, the input shaft side positioning portion provided on the input shaft end face prevents the thrust bearing rolling element sandwiched between the input shaft end face and the output shaft end face from being displaced in the radial direction with respect to the input shaft. As a result, the output shaft side positioning portion provided on the output shaft end face prevents the rolling element of the thrust bearing sandwiched between the input shaft end face and the output shaft end face from being displaced in the radial direction with respect to the output shaft. , The misalignment between the shaft ends of the input shaft and the output shaft is prevented. Therefore, even when a radial load in a direction that causes the axis to tilt is applied between the input shaft and the output shaft, the shaft is less likely to tilt between the input shaft and the output shaft, and the inner ring provided on the input shaft is provided. It is possible to stabilize the operation of the engager incorporated between the outer ring and the outer ring provided on the output shaft.

When the plurality of rolling elements are balls, as the input shaft side positioning portion, a track groove having an arcuate cross section formed on the end surface of the input shaft and in which the rolling elements are in rolling contact can be adopted. As the output shaft side positioning portion, a track groove having an arcuate cross section formed on the end surface of the output shaft and with which the rolling elements roll and contact can be adopted.

Further, when the plurality of rolling elements are cylindrical rollers, the input shaft side positioning portion is an annular shape provided on the inner diameter side or the outer diameter side of the region of the input shaft end surface where the rolling elements roll and contact. A brim can be adopted, and as the output shaft side positioning portion, an annular brim provided on the inner diameter side or the outer diameter side of the region of the output shaft end face where the rolling element rolls and contacts can be adopted. it can.

As the input shaft end face, the end face of the input shaft side track board fitted in the shaft end recess formed at the end of the input shaft is adopted, and the output shaft end face is formed at the end of the output shaft. It is preferable to adopt the end face of the output shaft side track board fitted in the shaft end recess.

In this way, the accuracy of the input shaft end face and the output shaft end face is lower than that of adopting the input shaft end face in which the end of the input shaft is directly machined or the output shaft end face in which the end of the output shaft is directly machined. It can be processed well.

It is preferable that the input shaft or the elastic member that urges the output shaft is incorporated in a state of being compressed in the axial direction in a direction that narrows the axial distance between the input shaft end surface and the output shaft end surface.

In this way, a preload is applied to the thrust bearing by the elastic restoring force of the elastic member, so that the operation of the rolling element of the thrust bearing becomes stable.

Further, in the present invention, as a method for manufacturing the above-mentioned rotation transmission device, those having the following configurations are also provided.
A track board preparation process in which a plurality of types of track boards having different axial thickness dimensions are classified into a plurality of groups according to the axial thickness dimensions of the track board and prepared.
In the housing, the input shaft, the output shaft, the inner ring, the outer ring, the engaging element, the engaging element cage, the cage actuator, the first radial bearing, the second radial bearing, and the third radial bearing are provided. The track board having an axial thickness dimension that does not cause axial play inside the thrust bearing when the thrust bearing and the thrust bearing are incorporated is selected from the plurality of groups, and the selected track board is selected as described above. The track board assembly process of assembling as the input shaft side track board or the output shaft side track board,
A method for manufacturing a rotation transmission device having.

When a rotation transmission device is manufactured by this manufacturing method, the tolerances are accumulated in the axial direction regardless of the axial dimensional variation (tolerance) that inevitably occurs when each component constituting the rotation transmission device is manufactured. By selecting and using a track board having an axial thickness dimension corresponding to dimensional fluctuations, it is possible to stabilize the contact of the rolling elements with the track board of the thrust bearing.

In the rotation transmission device of the present invention, the input shaft side positioning portion provided on the input shaft end surface prevents the rotational body of the thrust bearing sandwiched between the input shaft end surface and the output shaft end surface from being displaced in the radial direction with respect to the input shaft. In addition, the output shaft side positioning portion provided on the output shaft end face prevents the thrust bearing rolling element sandwiched between the input shaft end face and the output shaft end face from being displaced in the radial direction with respect to the output shaft. As a result, it is possible to prevent misalignment between the shaft ends of the input shaft and the output shaft. Therefore, even when a radial load in a direction that causes the axis to tilt is applied between the input shaft and the output shaft, the shaft is less likely to tilt between the input shaft and the output shaft, and the inner ring provided on the input shaft is provided. It is possible to stabilize the operation of the engager incorporated between the outer ring and the outer ring provided on the output shaft.

Sectional drawing which shows the rotation transmission device which concerns on 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. An enlarged cross-sectional view of the vicinity of a thrust bearing that rotatably connects the shaft end of the input shaft and the shaft end of the output shaft shown in FIG. Sectional view taken along line IX-IX in FIG. Cross-sectional view showing a modified example in which a thrust roller bearing is used instead of the thrust ball bearing shown in FIG. Sectional view taken along line XI-XI in FIG. A cross-sectional view illustrating a method of manufacturing the rotation transmission device shown in FIG. 1 using a plurality of types of output shaft side track boards having different axial thickness dimensions. A cross-sectional view showing a modified example in which the raceway groove of the rolling element of the thrust bearing shown in FIG. 8 is directly machined on the shaft end of the input shaft and the shaft end of the output shaft.

FIG. 1 shows a rotation transmission device according to an embodiment of the present invention. This rotation transmission device is coaxial with the cylindrical housing 1 having both ends open, the input shaft 2 arranged with one end housed in the housing 1, and the input shaft 2 with one end housed in the housing 1. The output shafts 3 arranged side by side, the inner ring 4 provided in the housing 1 of the input shaft 2 in the housing 1, and the output shaft 3 into the housing 1 so as to rotate integrally with the output shaft 3. An outer ring 5 provided connected to the housing portion, a plurality of rollers 6a and 6b incorporated between the inner circumference of the outer ring 5 and the outer circumference of the inner ring 4, and a roller cage for holding these rollers 6a and 6b. It has a cage 7 and a cage actuator 8 for moving the roller cage 7.

The input shaft 2 and the inner ring 4 are formed as a seamless integrated member so that both can rotate integrally. The input shaft 2 and the inner ring 4 may be formed as separate members, and may be connected by serration fitting or the like so that both of them rotate integrally. The input shaft 2 has an input shaft end surface 9 (see FIG. 8) at an end on the side housed in the housing 1.

The output shaft 3 and the outer ring 5 are also formed as a seamless integrated member so that both can rotate integrally. The outer ring 5 is a portion formed in an annular shape surrounding the inner ring 4. Here, the outer ring 5 and the output shaft 3 are integrally formed, but the output shaft 3 and the outer ring 5 may be formed as separate members and connected by serration fitting or the like so that both of them rotate integrally. The output shaft 3 has an output shaft end surface 10 (see FIG. 8) that faces the input shaft end surface 9 in the axial direction at the end on the side housed in the housing 1.

As shown in FIGS. 2 and 3, a plurality of cam surfaces 11 are provided on the outer periphery of the inner ring 4 at equal intervals in the circumferential direction. The cam surface 11 includes a front cam surface 11a and a rear cam surface 11b arranged behind the front cam surface 11a in the normal rotation direction of the inner ring 4. A cylindrical surface 12 facing the cam surface 11 in the radial direction is provided on the inner circumference of the outer ring 5.

A pair of rollers 6a and 6b facing each other in the circumferential direction with a roller release spring 13 sandwiched between the cam surface 11 and the cylindrical surface 12 are incorporated. Of the pair of rollers 6a and 6b, the front roller 6a in the forward rotation direction is incorporated between the front cam surface 11a and the cylindrical surface 12, and the rear roller 6b in the forward rotation direction is the rear cam surface 11b and the cylindrical surface 12. It is built in between. The roller release spring 13 presses the rollers 6a and 6b in a direction that widens the distance between the pair of rollers 6a and 6b.

The front cam surface 11a is formed so that the radial distance from the cylindrical surface 12 gradually decreases from the position of the roller 6a toward the front in the normal rotation direction. The rear cam surface 11b is formed so that the radial distance from the cylindrical surface 12 gradually decreases from the position of the roller 6b toward the rear in the normal rotation direction. In FIG. 3, the front cam surface 11a and the rear cam surface 11b are formed so as to be separate planes inclined in opposite directions, but the front cam surface 11a and the rear cam surface 11b 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 11a and the rear side portion is the rear cam surface 11b. Further, the front cam surface 11a and the rear cam surface 11b 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 7 is a first split retainer that supports one of the pair of rollers 6a and 6b facing each other in the circumferential direction with the roller release spring 13 in between. It consists of a 7A and a second split cage 7B that supports the other roller 6b. The first split cage 7A and the second split cage 7B are supported so as to be relatively rotatable, and the pair of rollers 6a and 6b are supported so that the distance between the pair of rollers 6a and 6b changes according to the relative rotation. Are individually supported.

The first split cage 7A has a plurality of pillar portions 14a arranged at intervals in the circumferential direction, and an annular flange portion 15a connecting the ends of the pillar portions 14a. Similarly, the second split cage 7B also has a plurality of pillar portions 14b arranged at intervals in the circumferential direction, and an annular flange portion 15b that connects the ends of these pillar portions 14b to each other.

The pillar portion 14a of the first split cage 7A and the pillar portion 14b of the second split cage 7B have a pair of rollers 6a and 6b facing each other in the circumferential direction with the roller separation spring 13 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 inner ring 4 so as to sandwich it.

As shown in FIG. 1, the flange portion 15a of the first split cage 7A and the flange portion 15b of the second split cage 7B have the flange portion 15b of the second split cage 7B as the first split cage. It is arranged so as to face the inner ring 4 in the axial direction with respect to the flange portion 15a of the 7A. The flange portion 15b of the second split cage 7B is provided with a plurality of notches 16 at intervals in the circumferential direction in order to avoid interference with the pillar portion 14a of the first split cage 7A. ..

The inner circumference of the flange portion 15a of the first split cage 7A and the inner circumference of the flange portion 15b of the second split cage 7B are rotatably supported by a cylindrical surface 17 provided on the outer circumference of the input shaft 2. ing. As a result, the first split cage 7A and the second split cage 7B engage the rollers 6a and 6b between the cylindrical surface 12 and the cam surface 11 by widening the distance between the pair of rollers 6a and 6b. Disengagement of the rollers 6a and 6b between the cylindrical surface 12 and the cam surface 11 by narrowing the distance between the engaging position (see FIG. 3) and the pair of rollers 6a and 6b. It can be moved to and from the position (see FIG. 2). The flange portion 15a of the first split cage 7A is supported in the axial direction by an annular convex portion 19 provided on the outer periphery of the input shaft 2 via a thrust bearing 18, whereby the movement in the axial direction is restricted. There is.

As shown in FIG. 4, a spring holder 20 is fixed to the side surface of the inner ring 4. The spring holder 20 has a stopper piece 21 located between the pillar portions 14a and 14b facing each other in the circumferential direction with the pair of rollers 6a and 6b sandwiched between them. In the stopper piece 21, when both pillar portions 14a and 14b move in a direction in which the distance between the pair of rollers 6a and 6b is narrowed, the edges on both sides of the stopper piece 21 receive the pillar portions 14a and 14b. As a result, the roller release spring 13 between the pair of rollers 6a and 6b is prevented from being excessively compressed and damaged, and each roller 6a with respect to the inner ring 4 when the distance between the pair of rollers 6a and 6b is narrowed is prevented. , 6b can be fixed in position.

As shown in FIG. 5, the spring holder 20 has a spring holding piece 22 that holds the roller release spring 13. The spring holding piece 22 is integrally formed with the stopper piece 21 so as to extend axially between the inner circumference of the outer ring 5 and the outer circumference of the inner ring 4. The spring holding piece 22 is arranged so as to face the spring support surface 23 (see FIG. 2) formed between the front cam surface 11a and the rear cam surface 11b on the outer periphery of the inner ring 4 in the radial direction. A recess 24 for accommodating the roller release spring 13 is formed on the surface of the spring holding piece 22 facing the spring support surface 23. The roller release spring 13 is a compression coil spring. The spring holding piece 22 regulates the movement of the roller release spring 13 by the recess 24, thereby preventing the roller release spring 13 from falling off in the axial direction from between the inner circumference of the outer ring 5 and the outer circumference of the inner ring 4. ing.

As shown in FIG. 1, this rotation transmission device places a roller cage 7 (that is, a first split cage 7A and a second split cage 7B) between the cylindrical surface 12 and the cam surface 11 with the roller 6a, Move between the engagement position for engaging 6b (see FIG. 3) and the disengagement position for disengaging the rollers 6a and 6b between the cylindrical surface 12 and the cam surface 11 (see FIG. 2). As the cage actuator 8, 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 for attracting the armature 30 to the rotor 31 by energization. It has a ball lamp mechanism 33 that converts an operation in which the armature 30 is attracted to the rotor 31 into an operation in which the first split cage 7A and the second split cage 7B 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 circumference of the flange portion 15b of the second split cage 7B 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 7B so as to move integrally with the second split cage 7B in the axial direction. Further, the armature 30 is supported by a cylindrical surface 37 provided on the annular convex portion 19 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 7B) 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 15a of the first split cage 7A facing the flange portion 15b of the second split cage 7B. The inclined groove 42a provided, the inclined groove 42b provided on the surface of the flange portion 15b of the second split cage 7B facing the flange portion 15a of the first split cage 7A, 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 15b of the second split cage 7B moves axially toward the flange portion 15a of the first split cage 7A, 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 7A and the second split cage 7B rotate relative to each other, and as a result, the pillar portions 14a and the first split cage 7A of the first split cage 7A are rotated. The pillar portion 14b of the split cage 7B of 2 operates so as to move in a direction of narrowing the distance between the pair of rollers 6a and 6b.

The armature 30 is urged away from the rotor 31 by the force of the roller release spring 13. That is, the force with which the roller release spring 13 shown in FIG. 2 presses the rollers 6a and 6b in the direction of widening the distance between the pair of rollers 6a and 6b is applied to the first split cage 7A and the second split cage 7B. introduce. Then, the circumferential force received by the first split cage 7A and the second split cage 7B 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 7B. Here, as shown in FIG. 1, since the armature 30 is fixed to the second split cage 7B, the armature 30 is eventually subjected to the force transmitted from the roller release spring 13 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 8 (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 3 side. From the large-diameter tubular portion 1a, the end portion of the input shaft 2 opposite to the side of the input shaft end surface 9 protrudes, and from the small-diameter tubular portion 1b, the side opposite to the side of the output shaft end surface 10 of the output shaft 3 The end is in a protruding state. 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 a support member (not shown) by inserting and tightening a bolt (not shown) into the through hole 47. You can do it.

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 radial 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 radial bearing 49 is, for example, a deep groove ball bearing. A retaining ring 50 for preventing the first radial bearing 49 from coming off is mounted on the inner circumference of the first radial bearing 49.

As shown in FIG. 8, a second radial bearing 51 that rotatably supports the output shaft 3 is incorporated in the inner circumference of the small diameter tubular portion 1b of the housing 1. The second radial bearing 51 is, for example, a deep groove ball bearing. Further, on the inner circumference of the small-diameter tubular portion 1b, an inward-facing annular protrusion 52 is provided on the side far from the large-diameter tubular portion 1a (see FIG. 1) with respect to the position where the second radial bearing 51 is fitted. An elastic member 53 is incorporated between the annular protrusion 52 and the second radial bearing 51. The elastic member 53 is incorporated in a state of being compressed in the axial direction, and the output shaft 3 is urged in a direction in which the axial distance between the input shaft end surface 9 and the output shaft end surface 10 is narrowed by the elastic restoring force. In the figure, an example in which a disc spring is used as the elastic member 53 is shown, but it is also possible to use a compression coil spring or a wave washer instead of the disc spring.

On the outer circumference of the inner ring 4, a cylindrical surface 54 having a diameter smaller than that of the cam surface 11 is formed adjacent to the cam surface 11 on the side of the output shaft 3. On the inner circumference of the outer ring 5, a cylindrical surface 55 having a diameter smaller than that of the cylindrical surface 12 is formed adjacent to the output shaft 3 with respect to the cylindrical surface 12. Here, the cylindrical surface 54 of the inner ring 4 and the cylindrical surface 55 of the outer ring 5 face each other in the radial direction. A third radial bearing 56 that connects the inner ring 4 and the outer ring 5 so as to be relatively rotatable is incorporated between the cylindrical surface 54 and the cylindrical surface 55 (between the radial facing surfaces of the inner ring 4 and the outer ring 5). .. The third radial bearing 56 is, for example, a deep groove ball bearing.

Further, a ring plate-shaped washer 57 is mounted on the cylindrical surface 54 of the inner ring 4 on the cam surface 11 side with respect to the third radial bearing 56. The washer 57 is formed to have a diameter larger than that of the cam surface 11 so as to have a portion facing the axial end faces of the rollers 6a and 6b, and by restricting the axial movement of the rollers 6a and 6b, the rollers 6a and 6b can be moved. It prevents the cam surface 11 from protruding in the axial direction.

Between the input shaft 2 and the output shaft 3, a plurality of rolling elements 60 sandwiched in the axial direction between the input shaft end surface 9 and the output shaft end surface 10 and an annular cage for holding the plurality of rolling elements 60. A thrust bearing 62 having 61 and is incorporated.

The rolling element 60 is a ball. The input shaft end surface 9 is an end surface of the input shaft side track board 64 fitted into the shaft end recess 63 provided at the end of the input shaft 2, and the output shaft end surface 10 is provided at the end of the output shaft 3. It is an end surface of the output shaft side track board 66 fitted into the shaft end recess 65.

The input shaft end surface 9 is formed with a raceway groove 67 having an arcuate cross section with which the rolling elements 60 roll and contact. Further, the output shaft end surface 10 is also formed with a raceway groove 68 having an arcuate cross section with which the rolling elements 60 roll and contact. Here, the raceway groove 67 of the input shaft end surface 9 constitutes an input shaft side positioning portion for preventing the positional deviation of the plurality of rolling elements 60 with respect to the input shaft 2, and the raceway groove 68 of the output shaft end surface 10 is formed. The output shaft side positioning portion for preventing the positional deviation of the plurality of rolling elements 60 with respect to the output shaft 3 in the radial direction is configured.

As shown in FIG. 9, the plurality of rolling elements 60 are arranged side by side on the same circumference at intervals in the circumferential direction. A plurality of pockets 69 for accommodating the rolling elements 60 are formed in the cage 61 at equal intervals in the circumferential direction. The cage 61 holds each rolling element 60 so that the rolling elements 60 do not fall out of the pocket 69 even in a state before the thrust bearing 62 is incorporated between the input shaft 2 and the output shaft 3.

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

As shown in FIG. 1, 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 outer ring 5 and the inner ring 4. That is, when the energization of the electromagnet 32 is stopped, the armature 30 is separated from the rotor 31 by the force of the roller separation spring 13. At this time, due to the force of the roller separation spring 13 that presses the rollers 6a and 6b in the direction in which the distance between the pair of rollers 6a and 6b is widened, the roller 6a on the front side in the forward rotation direction is a cylinder on the inner circumference of the outer ring 5. The roller 6b, which is engaged between the surface 12 and the front cam surface 11a on the outer circumference of the inner ring 4, and is rearward in the normal rotation direction, is a cylindrical surface 12 on the inner circumference of the outer ring 5 and a rear cam on the outer circumference of the inner ring 4. It is in a state of being engaged with the surface 11b. When the inner ring 4 rotates in the forward rotation direction in this state, the rotation is transmitted from the inner ring 4 to the outer ring 5 via the roller 6b on the rear side in the forward rotation direction. Further, when the inner ring 4 rotates in the reverse direction, the rotation is transmitted from the inner ring 4 to the outer ring 5 via the roller 6a on the front side in the forward rotation direction.

On the other hand, when the electromagnet 32 is energized, the rotation transmission device is in an disengaged state (idling state) in which rotation transmission between the outer ring 5 and the inner ring 4 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 15b of the second split cage 7B becomes the flange portion 15a of the first split cage 7A. 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 7A and the second split cage 7B rotate relative to each other. .. Then, due to the relative rotation of the first split cage 7A and the second split cage 7B, the pillar portion 14a of the first split cage 7A and the pillar portion 14b of the second split cage 7B are paired. The rollers 6a and 6b are pressed in a direction in which the distance between the rollers 6a and 6b is narrowed, and as a result, the front roller 6a in the normal rotation direction is in an engagement standby state (the front roller 6a and the cylindrical surface 12 in the normal rotation direction). Although there is a small gap between them, when the inner ring 4 rotates in the reverse direction, the roller 6a is immediately disengaged between the cylindrical surface 12 and the front cam surface 11a), and the rear roller in the normal rotation direction is released. 6b is in an engagement standby state (there is a minute gap between the roller 6b on the rear side in the normal rotation direction and the cylindrical surface 12, but when the inner ring 4 rotates in the forward rotation direction, the roller 6b immediately moves to the cylindrical surface 12 and the rear cam surface 11b. The state of being engaged between the two) is also released. In this state, even if rotation is input to the inner ring 4, the rotation is not transmitted from the inner ring 4 to the outer ring 5, and the inner ring 4 idles.

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 3 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 (not shown) with bolts or the like. At this time, due to 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 3, and the position of the support member fixing the housing 1, the rotation transmission device , A radial load in a direction that causes an inclination of the axis line may act between the input shaft 2 and the output shaft 3.

When the axial line is tilted between the input shaft 2 and the output shaft 3 due to this radial load, the relative positions of the inner ring 4 and the outer ring 5 are displaced, so that the rollers 6a and 6b between the inner ring 4 and the outer ring 5 are displaced. (For example, a part of the gap between the outer ring 5 and the inner ring 4 becomes narrower than it should be, so that the rollers 6a and 6b are misengaged between the outer ring 5 and the inner ring 4 or the rollers 6a and 6b are misengaged. If the rollers 6a and 6b are excessively strongly bitten between the outer ring 5 and the inner ring 4, the rollers 6a and 6b may not be able to be disengaged).

In response to this problem, in the rotation transmission device described above, the raceway groove 67 provided on the input shaft end surface 9 prevents the rolling element 60 from being displaced in the radial direction with respect to the input shaft 2, and is provided on the output shaft end surface 10. The raceway groove 68 prevents the rolling element 60 from being displaced in the radial direction with respect to the output shaft 3, and as a result, it is possible to prevent the positional deviation between the shaft ends of the input shaft 2 and the output shaft 3. Therefore, even when a radial load in the direction of causing the inclination of the axis line acts between the input shaft 2 and the output shaft 3, the inclination of the axis line is less likely to occur between the input shaft 2 and the output shaft 3, and the input shaft 2 It is possible to stabilize the operation of the rollers 6a and 6b incorporated between the inner ring 4 provided in the above and the outer ring 5 provided in the output shaft 3.

Further, since this rotation transmission device incorporates an elastic member 53 that urges the output shaft 3 in a direction that narrows the axial distance between the input shaft end surface 9 and the output shaft end surface 10, the elastic restoring force of the elastic member 53 causes the rotation transmission device. Preload can be applied to the thrust bearing 62. Therefore, the operation of the rolling element 60 of the thrust bearing 62 is stable.

In the above embodiment, the elastic member 53 for urging the output shaft 3 has been described as an example, but the elastic member 53 for urging the input shaft 2 can also be adopted. For example, an elastic member 53 is incorporated between the retaining ring 41 and the field core 40 in a state of being compressed in the axial direction, and the elastic member 53 presses the input shaft 2 via the field core 40 and the second radial bearing 51. Therefore, it is also possible to urge the input shaft 2 in a direction that narrows the axial distance between the input shaft end surface 9 and the output shaft end surface 10.

As shown in FIG. 13, the input shaft end face 9 may be directly machined on the end of the input shaft 2, and the output shaft end face 10 may be directly machined on the end of the output shaft 3, as in the above embodiment. As the input shaft end surface 9, the end surface of the input shaft side track board 64 fitted in the shaft end recess 63 formed at the end of the input shaft 2 is adopted, and as the output shaft end surface 10, the end surface of the output shaft 3 is used. By adopting the end face of the output shaft side track board 66 fitted in the formed shaft end recess 65, the input shaft end face 9 and the output shaft end face 10 can be machined with low cost and accuracy.

In the above embodiment, a ball using a ball as the rolling element 60 has been described as an example, but as shown in FIGS. 10 and 11, a cylindrical roller may be adopted as the rolling element 60.

As shown in FIG. 10, on the input shaft end surface 9, an annular flat surface 70 on which the rolling elements 60 roll and contact, an annular outer brim 71 formed on the outer diameter side of the flat surface 70, and an inner diameter of the flat surface 70 are provided. An annular inner brim 72 formed on the side is formed. Further, the output shaft end surface 10 is also formed on the annular flat surface 73 on which the rolling elements 60 roll and contact, the annular outer brim 74 formed on the outer diameter side of the flat surface 73, and the inner diameter side of the flat surface 73. An annular inner brim 75 is formed.

Here, the outer brim 71 and the inner brim 72 of the input shaft end surface 9 form an input shaft side positioning portion that prevents the plurality of rolling elements 60 from being displaced in the radial direction with respect to the input shaft 2. Here, although both the inner brim 72 and the outer brim 71 are provided, only one of the inner brim 72 and the outer brim 71 may be provided. Similarly, the outer brim 74 and the inner brim 75 of the output shaft end face 10 form an output shaft side positioning portion that prevents the plurality of rolling elements 60 from being displaced in the radial direction with respect to the output shaft 3.

As shown in FIG. 11, the plurality of rolling elements 60 are arranged side by side on the same circumference at intervals in the circumferential direction. A plurality of pockets 69 for accommodating the rolling elements 60 are formed in the cage 61 at equal intervals in the circumferential direction. The cage 61 holds each rolling element 60 so that the rolling elements 60 do not fall out of the pocket 69 even in a state before the thrust bearing 62 is incorporated between the input shaft 2 and the output shaft 3.

As shown in FIGS. 10 and 11, when a thrust roller bearing is adopted as the thrust bearing 62, it is possible to secure the life of the thrust bearing 62 even when a large radial load is applied to the rotation transmission device.

By the way, each component constituting the above-mentioned rotation transmission device inevitably has an axial dimensional variation (tolerance). Therefore, when the rotation transmission device is assembled, the tolerances of the respective parts are accumulated in the axial direction, so that the contact of the rolling element 60 with respect to the racetracks 64 and 66 of the thrust bearing 62 may become unstable.

Therefore, when the rotation transmission device is manufactured as described below, it is possible to stabilize the contact of the rolling elements 60 with respect to the racetracks 64 and 66 of the thrust bearing 62.

First, a plurality of types of output shaft-side track boards 66 having different axial thickness dimensions t shown in FIG. 12 are classified into a plurality of groups according to the axial thickness dimension t of the output shaft-side track boards 66. Prepare (track board preparation process).

Next, in the housing 1 shown in FIG. 1, the input shaft 2, the output shaft 3, the inner ring 4, the outer ring 5, the rollers 6a, 6b, the roller cage 7, the cage actuator 8, the first radial bearing 49, and the second radial bearing When the 51, the third radial bearing 56, and the thrust bearing 62 are incorporated, a track board having an axial thickness dimension that does not cause backlash in the axial direction inside the thrust bearing 62 is selected from a plurality of groups and selected. The track board is assembled as the output shaft side track board 66 (track board assembly step).

When the rotation transmission device is manufactured in this way, the tolerances are accumulated in the axial direction regardless of the variation (tolerance) of the axial dimensions that inevitably occurs when manufacturing each component constituting the rotation transmission device. By selecting and using a track board having an axial thickness dimension corresponding to dimensional fluctuations, it is possible to stabilize the contact of the rolling element 60 with the track board of the thrust bearing 62.

Here, a case where a plurality of types of output shaft side track boards 66 having different axial thickness dimensions t are classified into a plurality of groups and prepared has been described as an example, but a plurality of output shaft side racetracks 66 having different axial thickness dimensions have been described as an example. The type of input shaft side track board 64 may be classified into a plurality of groups and prepared.

In the above embodiment, an example in which rollers 6a and 6b are incorporated as engagement elements between the inner circumference of the outer ring 5 and the outer circumference of the inner ring 4 has been described, but the present invention uses a ball, a sprag, or the like as the engagement element. The same can be applied to the rotation transmission device.

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 Output shaft 4 Inner ring 5 Outer ring 6a, 6b Roller 7 Roller cage 8 Cage actuator 9 Input shaft end face 10 Output shaft end face 49 1st radial bearing 51 2nd radial bearing 53 Elastic member 56 3rd radial bearing 60 Rolling element 61 Cage 62 Thrust bearing 63 Shaft end recess 64 Input shaft side track board 65 Shaft end recess 66 Output shaft side track board 67 Track groove 68 Track groove 70 Flat surface 71 Outer brim 72 Inner brim 73 Flat surface 74 Outer brim 75 Brim t Axial thickness dimension

Claims (6)

A tubular housing (1) with both ends open and
An input shaft (2) arranged in a state in which one end is housed in the housing (1) and having an input shaft end face (9) at an end on the side housed in the housing (1).
The input shaft end face (9) is arranged coaxially with the input shaft (2) in a state where one end is housed in the housing (1), and is arranged at the end on the side housed in the housing (1). ) And the output shaft (3) having the output shaft end face (10) facing in the axial direction.
An inner ring (4) provided in a housing portion of the input shaft (2) into a housing (1) so as to rotate integrally with the input shaft (2).
An outer ring (4) formed in an annular shape, which is provided by being connected to a housing portion of the output shaft (3) so as to rotate integrally with the output shaft (3) and surrounds the inner ring (4). 5) and
Engagement elements (6a, 6b) incorporated between the inner circumference of the outer ring (5) and the outer circumference of the inner ring (4), and
An engaging position for engaging the engaging element (6a, 6b) between the outer ring (5) and the inner ring (4), and an engaging disengaging position for disengaging the engaging element (6a, 6b). An engager cage (7) movably supported between and
A cage actuator (8) that moves the engager cage (7) between the engagement position and the disengagement position,
A first radial bearing (49) that rotatably supports the input shaft (2) and
A second radial bearing (51) that rotatably supports the output shaft (3) and
In a rotation transmission device having a third radial bearing (56) that connects the inner ring (4) and the outer ring (5) so as to be relatively rotatable.
A plurality of rolling elements (60) sandwiched in the axial direction between the input shaft end surface (9) and the output shaft end surface (10), and an annular cage (61) for holding the plurality of rolling elements (60). ) Is provided with a thrust bearing (62).
The input shaft end surface (9) is provided with an input shaft side positioning portion for preventing the plurality of rolling elements (60) from being displaced in the radial direction with respect to the input shaft (2).
The output shaft end surface (10) is provided with an output shaft side positioning portion for preventing the plurality of rolling elements (60) from being displaced in the radial direction with respect to the output shaft (3). Transmission device. The plurality of rolling elements (60) are balls.
The input shaft side positioning portion is a raceway groove (67) having an arcuate cross section formed on the input shaft end surface (9) and in which the rolling element (60) rolls and contacts.
The rotation transmission device according to claim 1, wherein the output shaft side positioning portion is a raceway groove (68) having an arcuate cross section formed on the output shaft end surface (10) and in which the rolling element (60) rolls and contacts. .. The plurality of rolling elements (60) are cylindrical rollers.
The input shaft side positioning portion is an annular brim (71, 72) provided on the inner diameter side or the outer diameter side of the region of the input shaft end surface (9) where the rolling element (60) rolls and contacts.
The output shaft side positioning portion is an annular brim (74, 75) provided on the inner diameter side or the outer diameter side of the region of the output shaft end surface (10) where the rolling element (60) rolls and contacts. Item 2. The rotation transmission device according to item 1. The input shaft end face (9) is an end face of an input shaft side track board (64) fitted in a shaft end recess (63) provided at the end of the input shaft (2).
The output shaft end face (10) is the end face of the output shaft side track board (66) fitted in the shaft end recess (65) provided at the end of the output shaft (3), according to claims 1 to 3. The rotation transmission device according to any one. Axial compression of the elastic member (53) that urges the input shaft (2) or the output shaft (3) in a direction that narrows the axial distance between the input shaft end face (9) and the output shaft end face (10). The rotation transmission device according to any one of claims 1 to 4, which is incorporated in this state. The method for manufacturing a rotation transmission device according to claim 4.
A track board preparation step in which a plurality of types of track boards having different axial thickness dimensions (t) are classified into a plurality of groups according to the axial thickness dimension (t) of the track board and prepared.
In the housing (1), the input shaft (2), the output shaft (3), the inner ring (4), the outer ring (5), the engagers (6a, 6b), and the engager cage (7). When the cage actuator (8), the first radial bearing (49), the second radial bearing (51), the third radial bearing (56), and the thrust bearing (62) are incorporated, the said The track disc having an axial thickness dimension (t) that does not cause backlash in the axial direction inside the thrust bearing (62) is selected from the plurality of groups, and the selected race disc is selected from the input shaft side race disc ( 64) or the track board assembly step of assembling as the output shaft side track board (66),
A method for manufacturing a rotation transmission device having.

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