JP2975133B2 - Rotation transmission device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotation transmission device mounted between a drive shaft of an automobile and wheels for switching transmission of driving force to wheels according to a rotation difference between the two.

[0002]

2. Description of the Related Art In a motor vehicle, when a rear wheel is directly connected to a front wheel drive system and a tight corner is turned in a four-wheel drive state, the front wheel slips due to a rotation difference between the front wheel and the rear wheel generated at the time of turning, and it is as if brakes. Phenomenon occurs.

Conventionally, in order to eliminate such a tight corner braking phenomenon, a viscous coupling that absorbs the rotational difference between the front and rear wheels is mounted on a drive shaft (propeller shaft), and a four-wheel drive is used only when driving is required. A switching structure is known.

However, a viscous coupling utilizing the shearing force of a high-viscosity material cannot transmit a sufficient torque to the weight of an automobile. Since it is necessary to increase the area and the number of disks to be used, the shape of the coupling becomes large, and it is difficult to make the drive system compact.

Further, in the viscous coupling, the shear resistance of a highly viscous substance set based on high-speed rotation is
Since the transmission torque is increased at the time of low-speed rotation to increase the transmission torque, the drag torque at the time of low-speed rotation does not become zero, and there is a disadvantage that the braking phenomenon of the tight corner is not completely eliminated.

In order to completely eliminate the above-described braking phenomenon, it is desirable to use a transmission joint that mechanically switches the transmission of the driving force. Conventionally, as a transmission coupling for performing this kind of mechanical switching, there is one in which an overrunning one-way clutch is incorporated in a front wheel hub.

In this structure, in order to eliminate the difference in rotation between the front and rear wheels in a tight corner, the front wheel hub is set so as to rotate faster than the propeller shaft which is the drive shaft of the rear wheel. Although the power is not transmitted to the hub, when the rear wheel slips and the rotation of the drive wheel increases, the rotation is transmitted to the front wheel hub by a wedge action of a roller or a ball inserted into a gap between the drive shaft and the front wheel hub.

However, in the above-described configuration, since only the rotation of the drive shaft in one direction (forward direction) is transmitted to the front wheel hub, only the rear wheel is driven when the vehicle retreats, and 4WD is not achieved. If the vehicle turns while moving backward, there is a problem that a braking phenomenon of a Thai corner occurs.

Further, since the driving wheels are supported in a free state with respect to the front wheel hub, if the driving wheels rotate by any force, the driving wheels are engaged with the rollers and the like and the clutch is engaged. Disadvantage.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and can reliably transmit or cut off rotation of a drive shaft in both directions, and can move forward and backward without causing a braking phenomenon at a tight corner. It is an object of the present invention to provide a rotation transmission device that enables four-wheel drive travel.

[0011]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention according to claim 1 is an F-type vehicle in which a rear wheel is a driving wheel.
Front propeller shuff for R-based four-wheel drive vehicles
Rotation transmission device mounted on the
Inside the outer ring connected to the output side of the
An input shaft that connects the input side of the propeller shaft is rotatably supported, and an engaging surface of an engaging element is formed on a surface facing the outer ring and the input shaft, and the retainer is rotatably provided between the engaging surfaces. The pocket is provided with an engagement member that engages with the engagement surfaces by the relative rotation of the input shaft and the retainer in the forward and reverse directions, and an elastic member that retains the engagement member at a position where the engagement member is not engaged. The input shaft and the control shaft arranged rotatably on the same axis as the input shaft are connected so as to be able to transmit rotational torque, a gap in the rotational direction is provided at a connection portion between the input shaft and the control shaft, and the input shaft or the control shaft is provided. A differential means for generating a speed difference between the rotation of the input shaft and the control shaft is provided between one of the
Is constituted by rolling bearings to which a preload is applied .

In the above structure, a torque reversal transmission mechanism for reversing the rotation of the control shaft and transmitting the rotation to the retainer may be provided between the control shaft and the retainer.

[0013]

In the above structure, when the drive shaft rotates with the drive shaft of the vehicle connected to the input shaft connected to the differential means and the control shaft, and the axle of the driven wheel connected to the outer wheel, By the action of the means, the input shaft and the control shaft rotate relative to each other until there is no gap in the rotational direction of the connecting portion, and the retainer moves the engagement element to the engagement operation position.

In this state, if the rotation of the outer wheel connected to the driven wheel becomes faster than the rotation of the drive shaft, the outer wheel overruns on the engaging element, and the engaging element receives a contact force in the direction of disengaging. The engagement is not established, and the driving force is not transmitted to the driven wheels.

Further, when the driving-side wheel slips, the vehicle speed decreases, and the rotation speed of the driven wheel decreases, the rotation of the input shaft exceeds the rotation of the outer wheel.
The driving force is transmitted to the driven wheels via the engagement elements and the outer wheels.

On the other hand, when the drive shaft rotates in the reverse direction, the retainer rotates in the reverse direction to move the engagement element to the engagement operation position. That is, since the direction of engagement between the engagement element and the engagement surface changes depending on the rotation direction of the drive shaft, the driving force can be transmitted or interrupted in both forward and backward directions.

The same operation as described above can be obtained by connecting the differential means to the control shaft and rotating the control shaft and the input shaft relatively.

[0018]

Embodiments of the present invention will be described below with reference to the accompanying drawings. 1 to 5 show a first embodiment of a rotation transmitting device according to the present invention. As shown in FIG.
And the input shaft 2 inserted therein are supported by two bearings 3 so as to be relatively rotatable.

On the inner diameter surface of the outer ring 1 and the outer diameter surface of the input shaft 2, cylindrical engagement surfaces 4, 5 serving as engagement surfaces of the engagement elements are provided at opposing positions. A control retainer 6 and a fixed retainer 7 having different diameters are incorporated between them.

At the end of the input shaft 2 located outside the outer ring 2, an input ring 8 connected to a propeller shaft of a motor vehicle is provided.
Are fitted. Although a flange provided with a mounting hole 8a is shown here as the input ring 8, it may be a gear or the like.

As shown in FIG. 2, a plurality of axial grooves 11 are formed on the inner periphery of the input ring 7.
The axial ridge 9 provided on the outer periphery of the input shaft 1 is inserted into
A rotational gap 10 is provided between the ridge 9 and the groove 11.

The input shaft 2 between the input ring 8 and the outer ring 1
A differential means 12 is provided between the peripheral surface and the fixed portion . The differential unit 12 includes a resistor ring 14 to be press-fitted to the input shaft 2, a bearing 13 fitted to the outer peripheral surface of the resistance ring 14, a fixing member of the differential case such that the bearing 13 (not shown ) And a fixed arm 15 supported by the arm.

The bearings 13 and 13 are fitted into the resistance ring 14 by applying a preload equal to or higher than a pressure normally set to the rolling bearing, and the preload causes the rolling elements of the bearings 13 and 13 to move heavier. The response of rotation is slow. In the above structure, the rolling resistance of the bearing 13 applies a resistance force to the input shaft 2 so as to always suppress the rotation, and the input shaft 2 is connected to the input ring 8 and the control shaft 1 described later.
6, and is held so as not to be easily rotated by an impact force or an inertial force.

A control shaft 16 is rotatably inserted into an axial insertion hole 2 a provided at one end of the input shaft 2. One end of the control shaft 16 and the input ring 8 are formed on the input shaft 2. Are connected by a pin 18 inserted into the radial pin hole 17. Between this pin 18 and the pin hole 17,
As shown in FIG. 2, a circumferential gap 19 is formed, and the gap 19 is larger than the rotational direction gap 10.

The other end of the control shaft 16 and the control retainer 6 are connected to a radial pin hole 20 formed in the input shaft 2.
Are connected by a pin 21 inserted through. A circumferential clearance larger than the rotational clearance 10 is provided between the pin 21 and the pin hole 20.

As described above, the control shaft 16 and the pins 18, 2
Control cage 6 connected to input ring 8 via
Together with the input ring 8 can rotate relative to the input shaft 2 by an angle corresponding to the rotational clearance 10 with respect to the input shaft 2.

On the other hand, as shown in FIG. 3, a plurality of pockets 22 are formed at equal intervals in the circumferential direction of the control holder 6 and the holder 7 fixed to the input shaft 2, and are opposed to each other. In each pocket 22, a sprag 2 as an engagement element is provided.
3 are inserted at both ends.

As shown in FIG. 4, the sprag 23 has arcuate surfaces 24 and 25 having a radius r on the outer diameter side and the inner diameter side, and the radius r is 1/1 / the interval δ between the engagement surfaces 4 and 5. It is larger than 2.

The length L in the direction of the center of the arcuate surfaces 24, 25 is slightly smaller than the interval δ, and the sprags 23 are shifted from the neutral state in which the sprags 23 are raised between the engagement surfaces 4, 5, to the engagement surfaces. As shown in FIG. 5, when the outer circumferential surface 24 and the inner circumferential surface 25 are engaged with the engaging surfaces 4 and 5, respectively, when the outer surfaces 4 and 5 are inclined in one of the circumferential directions with respect to FIGS. The input shaft 2 and the outer ring 1 are integrally connected.

Constrictions 26 are formed on both side surfaces of the sprag 23, and an elastic body 27 which presses the constriction 26 to hold the sprag 23 in a neutral state is supported by the control retainer 6. . As the elastic body 27, a leaf spring, a coil spring or the like can be used. In this embodiment, as shown in FIGS. 3 and 4, the elastic body 27 is formed on the outer diameter surface of the column of the control retainer 6. A leaf spring is fitted into the groove 28,
The bent pieces 27a provided at both ends of the leaf spring are
The bent portion 27a is pressed against the constricted portion 26 by fitting into the cutout portion 29 formed on the side surface of the bent portion 27a.

The rotation transmission device A of the embodiment has the above-described structure. When the rotation transmission device A is mounted on a four-wheel drive vehicle in which the front wheels serve as drive wheels, as shown in FIG. 17, a propeller shaft B and a rear differential C are provided. Attached between. In this case, adjust the gear ratio of the gear connecting the transmission and the front wheel hub to the rotation of the front wheel so that the rotation of the front wheel is higher than the rotation speed of the rear wheel and the braking phenomenon during tight corners is eliminated. The rotation of the shaft B is set to be lower by about 10%.

When the rotation transmitting device A is mounted, the end of the propeller shaft B is connected to the input ring 8 so that the driving force is transmitted, and the input gear of the differential C is inserted into the screw hole 1a at the end of the outer race 1. And the rotation of the outer wheel 1 is changed to the rear wheel E
To be communicated to

When the input ring 7 is rotated by the propeller shaft B in a state of being mounted on the automobile as described above,
The input shaft 2 is held in the direction in which the movement of the input shaft 2 stops by the rolling resistance of the bearings 13, 13 in the differential means 12. To stop. For this reason, the input ring 8 rotates relative to the input shaft 2 exactly by the clearance 10 in the rotational direction.

Thus, when the input ring 8 rotates relative to the input shaft 2, the rotation of the input ring 8
8, transmitted to the control holder 6 via the control shaft 16 and the pin 21, and the control holder 6 relatively rotates with respect to the input shaft 2 and the holder 7 fixed to the input shaft 2.

By the relative rotation of the control cage 6,
The sprag 23 is pushed in the circumferential direction via the elastic body 27 and falls down in the circumferential direction around the contact position of the retainer 7 with the side surface of the pocket. For example, when the control retainer 6 rotates relative to the input shaft 2 in the direction of the arrow in FIG.
Is tilted leftward as shown in FIG.
And the inner side arcuate surface 25 is engaged with the engagement surface 4 of the outer race and the engagement surface 5 of the input shaft, and the engagement is activated in the direction of the arrow shown in FIG.

The rotation of the input ring 8 causes the ridge 9 of the input shaft 2 to abut against the side surface of the groove 11 so that the rotational direction clearance 1
When 0 disappears, the rotation of the input ring 8 is transmitted to the input shaft 2, and the input shaft 2 rotates together with the input ring 8.

At this time, when the vehicle is running straight, the rear wheels rotate with the front wheels, so that the rotation of the rear wheel axle is higher than the rotation of the propeller shaft B, which is slower than the front wheels. In this case, the outer ring 1 rotates faster than the input ring 8 and the input shaft 2, and runs over the sprag 23. For this reason, a contact rotational force in a direction in which the sprags 23 stand is applied to the sprags 23 by the contact with the outer ring 1, and the sprags 23 do not bite into the engagement surfaces 4 and 5, and the two-wheel drive state is maintained.

On the other hand, when the front wheels slip during traveling, the vehicle speed decreases and the rotation of the rear wheels decreases, whereas the rotation of the propeller shaft A increases. Faster than the rotation of. At this time, since the sprag 23 is in the engagement operating state as shown in FIG. 5, the rotation of the input shaft immediately engages with the engagement surfaces 4 and 5, and the rotation of the input shaft 2 is 1
Is transmitted to For this reason, the rear wheels are driven by the outer wheel 1, and the state is switched to the four-wheel drive state.

In the structure of this embodiment, when the input ring 8 rotates relative to the input shaft 2, the direction in which the sprags 23 fall is opposite to the direction in which the input ring 8 rotates.
The rotation of the input shaft 2 rotating in the same direction as the input ring 8 can be reliably transmitted to the outer ring 1 without slippage.

Further, even when the sprag 23 rotates in the left or right direction of the input ring 8, the sprag 23 falls in the direction opposite to the rotation direction of the input ring 8, so that the rotation transmitting device is effective even when the vehicle moves backward. To work.

FIGS. 6 to 8 show a second embodiment of the rotation transmitting device according to the present invention. In this embodiment, the input shaft 23 penetrates the outer race 31, and the input shaft 32 is connected to the input ring 33. The input shaft 32 has a square shaft 4
0, and the flat surface of the outer periphery of the square shaft portion 40 is
A pocket 43 is formed on the retainer 42 incorporated between the engagement surface 41 and the engagement surface 4 of the outer ring 31 so as to face the engagement surface 41. In the pocket 43, a pair of rollers 44, 45 as engaging elements,
And an elastic body 46 that presses the roller 5 against an end surface of the pocket 43 that faces in the circumferential direction. When the rollers 44 and 45 abut on the end surface of the pocket 43,
A gap is formed between 45 and the engagement surfaces 4 and 41.

A control ring 35 connected to the control shaft 16 via a pin 34 is rotatably incorporated inside the outer ring 31.
6, a retainer 42 is connected.

The torque reversal transmission mechanism 36 includes an outer ring 37
The rolling element 39 incorporated between the inner ring 38 and the inner ring 38 is pressed against the two wheels, and the rolling element 39 is held by a retainer to form a rolling bearing. The outer ring 37 is fixed to the control ring 35, The inner ring 38 is fixed to the retainer 42 and the retainer 4
2 is pinned to the input shaft 32.

For this reason, when the outer ring 31 rotates together with the control ring 35 in the direction of the arrow in FIG. 8, the rolling element 39 rotates due to the contact with the outer ring 31. Further, due to the contact with the rolling elements 39, the inner ring 38 rotates in a direction opposite to the rotation direction of the outer ring 37.

The same parts as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted. In the second embodiment, when the input ring 33 rotates relative to the input shaft 32 in the direction of the arrow shown in FIG. 7, the retainer 42 rotates in the direction opposite to the above-mentioned arrow, and is incorporated into the pocket 43. Of the pair of rollers 44, 45, the left roller 44 contacts the engagement surface 41 of the input shaft 32 and the engagement surface 4 of the outer race 31 respectively. When the input ring 33 rotates in the opposite direction to the above, the right roller 45 comes into contact with each of the opposing engagement surfaces 4 and 41. Therefore, rotation of the input shaft 32 in both the left and right directions can be transmitted to the outer race 31.

FIG. 9 shows a third embodiment of the rotation transmitting device according to the present invention. In this embodiment, one roller 52 as an engaging element is incorporated in a pocket 51 of a retainer 50 incorporated between the engaging surface 4 of the outer race 31 and the flat engaging surface 41 of the input shaft 31. The roller 52 is pressed from both sides by an elastic body 54 supported by the pillar 53 of the retainer 50,
The engagement surfaces 4 and 41 are held in a neutral state where they do not engage with each other. Since other configurations are the same as those of the first and second embodiments, the same components are denoted by the same reference numerals and description thereof will be omitted.

In this embodiment, when the retainer 50 rotating in the opposite direction to the input ring in conjunction with the input ring rotates rightward or leftward, the roller 52 is rotated.
Moves in the same direction as above to abut against the opposing engaging surfaces 4, 41,
The left and right rotations of the input shaft 32 can be transmitted to the outer race 1.

As described above, by incorporating one roller 52 into one pocket 51, the number of rollers 52 can be increased as compared with the case of the second embodiment, and the two directions having a large capacity can be obtained. You can get a clutch.

FIGS. 10 and 11 show a fourth embodiment of the rotation transmitting device according to the present invention. In this embodiment, between the outer race 31 and the cylindrical engagement surfaces 4 and 59 of the input shaft 58, two retainers 60 and 61 having different sizes are formed with pockets 62 and 63 formed in the retainers 60 and 61, respectively. Are connected by a half pitch at a time, and a control ring 35 is connected to the large-diameter side retainer 60 via a torque reversal transmission mechanism 36.
The small diameter side retainer 61 is fixed to the input shaft 58.

Further, each of the retainers 60 and 61 is formed with a projection 64 and 65 which enters the pocket of the other retainer.
On both sides of the projections 64, 65, the large-diameter cage 6
The sprags 66 for normal rotation and the sprags 67 for reverse rotation are alternately assembled in the circumferential direction between the opposing portions of the pocket 62 of the No. 0 and the pocket 63 of the small diameter side retainer 61 in the circumferential direction.
Is held in a neutral state by an elastic body 68 incorporated between the projections 64 and 65. Here, the sprags 66 for normal rotation and the sprags 67 for reverse rotation are bilaterally symmetric, and the sprags 66 for normal rotation rotate the large-diameter retainer 60 relative to the small-diameter retainer 61 leftward in FIG. When the retainer 60
In the direction of rotation, the arc surfaces 69 at both ends are
Contact 9

On the other hand, when the large-diameter retainer 60 rotates rightward relative to the small-diameter retainer 61, the sprag 67 for reverse rotation falls down in the rotational direction, and the arc surfaces 70 at both ends are engaged. Engage surfaces 4,59. The same components as those in the first and second embodiments are denoted by the same reference numerals, and description thereof is omitted.

In the fourth embodiment, the input shaft 58
When the input ring 33 is relatively rotated with respect to one of the spurs 66 and 67, one of the forward sprag 66 and the reverse sprag 67
, The rotation of the input shaft 58 in both the left and right directions can be transmitted to the outer race 1.

FIGS. 12 and 13 show a fifth embodiment. In this example, one end of the control shaft 71 is integrally fixed to the input ring 72 by screwing a nut 74, and the other end is rotatably supported by the input shaft 73 via a bearing 75.

The input ring 72 and the input shaft 73 are
A spline 76 having a clearance in the rotation direction is connected, and a radial gap (rattle) is eliminated by a bush 77 incorporated between the two.

Further, the differential means 7 connected to the input shaft 73
8 is formed of a single-row deep groove ball bearing 79 and a fixing arm 80 for supporting the bearing 79 on a fixing member. The bearing 79 has a radial clearance set to be negative by press fitting of an outer ring. , The braking moment is applied to the input shaft 73 by increasing the rotational moment during rolling. The structure of the clutch incorporated between the outer race 81 and the input shaft 73 is the same as that of the first embodiment, and the same components are denoted by the same reference numerals and description thereof is omitted.

FIG. 14 shows a sixth embodiment. In this example, both ends of the control shaft 85 are rotatably supported in the internal hole of the input shaft 86 by bearings 88, 88, and a pin 89 attached to one end of the control shaft 85 is connected to the fifth embodiment. And the same differential means 78 are connected.

Further, an input ring 87 is integrally connected to the input shaft 86 via a spline 90 which is press-fitted, and the pin 89 is fitted to the input shaft 86 and the input ring 87 with a clearance in the rotational direction. Holes 91 and 92 are formed.

Further, a control retainer 94 connected to the control shaft 85 via a pin 93 is disposed on the outer diameter side of the sprag 95, and a retainer 96 disposed on the inner diameter side of the sprag 95,
It is fixed to the input shaft 86.

In the above structure, when the input shaft 86 is rotated together with the input ring 87, the control shaft 85 decelerated by the differential means 78 rotates relative to the input shaft 86. This rotation direction is opposite to that of the first and fifth embodiments, but since the control retainer 94 is arranged on the outer diameter side of the sprag 95, the sprag 95 is moved as shown in FIG. The input ring 87 is tilted in a direction opposite to the rotation direction, so that the driving force can be reliably transmitted.

[0060]

[0061]

As described above, according to the present invention, when the input shaft and the control shaft are rotated in the left and right directions, both of them rotate relative to each other, and the retainer engages the engaging member with respect to the rotational forward direction of the input shaft. Since the input shaft is moved to the combined operation state, the rotation of the input shaft in both the forward and reverse directions can be reliably transmitted to the outer ring.

Further, since the drive is switched by mechanical contact between the engaging member and the engaging surface which move relatively, the driving direction is limited to one direction from the input shaft or the outer ring, and the driving direction is changed from the opposite direction. Transmission of rotational torque can be reliably shut off ,
In addition, the differential means is formed of a preloaded rolling bearing.
So it generates heat and durable for use on fast rotating parts
It is advantageous in terms of aspect. Further, the invention according to claim 2 is characterized in that the control shaft and
The rotation of the control shaft is reversed between the cages and transmitted to the cage.
The torque reversal transmission mechanism provides
The angle of movement of the engagement element to the opposite engagement position at half
Switching drive can be performed quickly.

Therefore, by using the rotation transmitting device of the present invention, it is possible to automatically switch between two-wheel drive and four-wheel drive in both the forward and backward directions of the vehicle, and to establish tight corners in the four-wheel direct connection state. Since the braking phenomenon does not occur even if the vehicle turns, it is possible to realize a full-time, directly-coupled four-wheel drive.

[Brief description of the drawings]

FIG. 1 is a partially longitudinal front view of a first embodiment.

FIG. 2 is a sectional view taken along the line II-II in FIG.

FIG. 3 is a sectional view taken along a line III-III in FIG. 1;

FIG. 4 is an enlarged sectional view of a part of FIG. 3;

FIG. 5 is a sectional view showing an operation state of FIG. 4;

FIG. 6 is a partially longitudinal front view of the second embodiment.

FIG. 7 is a sectional view taken along the line VII-VII of FIG. 6;

FIG. 8 is a sectional view showing a part of the torque reversing mechanism according to the third embodiment;

FIG. 9 is a sectional view showing a third embodiment.

FIG. 10 is a partial longitudinal front view of the fourth embodiment.

FIG. 11 is a sectional view taken along XI-XI in FIG. 10;

FIG. 12 is a partial longitudinal front view of the fifth embodiment.

FIG. 13 is a sectional view taken along the line XIII-XIII of FIG.

FIG. 14 is a partial longitudinal front view of the sixth embodiment.

FIG. 15 is a diagram showing an example of mounting a rotation transmission device on an automobile.

[Explanation of symbols]

 1, 31, 81 Outer ring 2, 32, 58, 73, 86 Input shaft 4, 5, 41, 59 Engagement surface 6, 35, 94 Cage for control 7, 42, 50, 60, 61 Cage 12, 78 Differential means 16, 71, 85, 100 Control shaft 23, 66, 67, 95 Sprag 27, 46, 54, 68 Elastic body 36 Torque reversal transmission mechanism 44, 45, 52 Roller A Rotation transmission device

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-60-241532 (JP, A) JP-A-1-199026 (JP, A) JP-A-61-74922 (JP, A) 11133 (JP, U) JP-B 43-11603 (JP, B1) JP-B 49-5129 (JP, B1) JP-B 34-9921 (JP, B1) (58) Fields surveyed (Int. ⁶ , DB name) F16D 45/00 B60K 17/348 F16H 48/12 F16D 41/07

Claims (2)

(57) [Claims] 1. FR-based four wheels in which rear wheels are drive wheels
Mounted on the front propeller shaft of a driving car
A rotation transmission device that has a front propeller shaft
Inside the outer ring connected to the side, the front propeller shaft
The input shaft connecting the entry side of the input shaft is rotatably supported, and the engaging surface of the engaging element is formed on the outer ring and the opposing surface of the input shaft, and the retainer is rotatably provided between the engaging surfaces. An engagement member that engages with the engagement surfaces by the relative rotation of the input shaft and the retainer in the forward and reverse directions, and an elastic member that retains the engagement member at a position where the engagement member does not engage. And a control shaft, which is rotatably arranged coaxially with the input shaft, so that the rotational torque can be transmitted, a gap in the rotational direction is provided at a connecting portion between the input shaft and the control shaft, and one of the input shaft and the control shaft is provided. and between the fixed portion, provided a differential means for producing a speed difference between the rotation of both the input shaft and the control shaft, the differential means pre
A rotation transmission device formed of rolling bearings under pressure . 2. The rotation transmission device according to claim 1, further comprising a torque reversal transmission mechanism that reverses the rotation of the control shaft and transmits the rotation to the retainer between the control shaft and the retainer.