JP7141239B2 - one way clutch - Google Patents

Description

The present invention relates to a one-way clutch used for torque transmission, backstop, etc. in vehicles and industrial machinery.

In a hybrid vehicle having a drive device that uses both an internal combustion engine and an electric motor (hereinafter simply referred to as "engine" and "motor", respectively), an oil pump for circulating lubricating oil to the drive-related devices. uses both an engine and a motor as power sources for Patent Literatures 1 and 2 describe clutch devices that selectively transmit the driving force input from each of these two power sources to an output member connected to the drive shaft of an oil pump.

In such a clutch device, two one-way clutches are coaxially arranged side by side in the axial direction, the outer rings of the two one-way clutches are driven by drive members on the engine side or the motor side, respectively, and the rotation of each outer ring rotates in two directions. It is configured to be transmitted to the inner ring, which is a common output member of the one-way clutch.

JP-A-10-67238 JP 2012-67862 A

2. Description of the Related Art In recent years, in hybrid vehicles, there has been a demand for higher rotation speed and higher output of a motor, which is a driving device. However, when a high-speed motor is used as the power source on the input side of a conventional one-way clutch, when the maximum value of the high-speed motor is input to the one-way clutch, durability problems such as increased friction resistance and seizure occur. Occur. In addition, the one-way clutch may not reach a stable locked state and may slip. If the one-way clutch slips, torque transmission becomes unstable. On the other hand, in order to stabilize the transmission of torque, if a control device for controlling the input rotation speed from the high-speed motor that is input to the one-way clutch is provided separately from the one-way clutch, the entire device including the one-way clutch becomes larger. invites

Furthermore, if the one-way clutch, which transmits the driving force of the engine to the oil pump, is also used to control the input rotational speed, the control device will become even larger.

SUMMARY OF THE INVENTION The present invention has been made in view of such circumstances, and provides a one-way clutch capable of controlling the input rotation speed input to the one-way clutch from an input shaft on the power source side without increasing the size of the one-way clutch. The challenge is to

In order to solve the above problems, the one-way clutch according to the present invention includes:
an outer ring to which rotation from the outside is input;
an inner ring disposed on the inner diameter side of the outer ring so as to be relatively rotatable with the outer ring, and having a plurality of cam surfaces on the outer peripheral surface at predetermined intervals in the circumferential direction;
a plurality of first rollers disposed on each of the plurality of cam surfaces and movable between a torque transmission position where the outer ring and the inner ring are coupled and a torque non-transmission position where the coupling is released;
a plurality of elastic members that bias the plurality of first rollers to the torque transmission position and hold the coupling between the outer ring and the inner ring when the rotation from the outside is within a predetermined number of rotations;
a release mechanism that moves the plurality of first rollers to the torque non-transmission position to release the coupling when the rotation from the outside exceeds the predetermined number of rotations;
The release mechanism is
a concave portion provided in the portion of the outer peripheral surface of the inner ring adjacent to each of the cam surfaces and having an inclined portion inclined toward the first roller as it goes radially outward; a second roller movably in a direction and disposed in contact with the first roller;
The recessed portion and the inclined portion have a shape that holds the second roller so that the second roller is always in contact with the first roller,
The first roller is moved to the torque non-transmission position by moving the recessed portion along the inclined portion by centrifugal force generated by the rotation of the second roller together with the inner ring.

ADVANTAGE OF THE INVENTION According to this invention, the one-way clutch which can control the input rotation speed input into a one-way clutch from the input shaft by the side of a power source can be provided, without causing enlargement.

FIG. 1 is a cross-sectional view along the central axis of the one-way clutch according to the embodiment. FIG. 2 is a cross-sectional view taken along line XX in FIG. 1, showing a state in which the outer ring and the inner ring are coupled. FIG. 3 is a cross-sectional view taken along line XX in FIG. 1, showing a state in which the outer ring and inner ring are disengaged. 4 is a partially enlarged view of FIG. 3. FIG.

A one-way clutch according to one embodiment of the present invention will be described below with reference to the drawings.

First, the direction of the one-way clutch in this embodiment will be defined. In this embodiment, the term "center axis" means the center axis of the one-way clutch, and the terms "axial direction", "radial direction" and "circumferential direction" mean the axial direction, radial direction and circumferential direction with respect to the central axis. Regarding the axial direction, in FIG. 1, the right side of the paper surface is defined as one axial direction side, and the left side of the paper surface is defined as the other axial direction side. is the other side in the axial direction. Regarding the circumferential direction, in FIGS. 2 and 3, the direction of rotation to the right in the plane of the paper is the direction toward one side of the circumferential direction or the clockwise direction, and the direction of rotation to the left toward the plane of the paper is the direction toward the other side in the circumferential direction. Or counterclockwise.

FIG. 1 is a cross-sectional view along the central axis of the one-way clutch according to the embodiment.
FIG. 2 is a cross-sectional view taken along line XX in FIG. 1, showing a state in which the outer ring and the inner ring are coupled.

Here, in a hybrid vehicle having a drive system using both an engine and a motor, the present embodiment transmits the driving force of the engine or the motor to the drive shaft of an oil pump for circulating lubricating oil to drive-related devices. is an example of a one-way clutch. Illustrations of the engine, motor, and oil pump are omitted in the following description.

The hybrid vehicle uses two one-way clutches 1 (see FIGS. 1 and 2) according to the present embodiment to drive the oil pump. That is, one is for transmitting the driving force of the engine to the oil pump, and the other is for transmitting the driving force of the motor to the oil pump. The two one-way clutches 1 are arranged axially side by side on a common output shaft 13 (see FIGS. 1 and 2), and transmit the rotation of the outer ring 3 driven by the drive member on the engine side or the motor side to the inner ring 5. there is Each inner ring 5 of the two one-way clutches 1 is fitted to the common output shaft 13, and is configured such that either the driving force of the engine or the motor is transmitted to the output shaft 13. As shown in FIG.

Since these two one-way clutches 1 have the same structure, in the following description, the one for transmitting the driving force of the motor to the oil pump will be explained, and the one for transmitting the driving force of the engine to the oil pump will be explained. Description is omitted. The configuration of the one-way clutch 1 according to this embodiment will be described in detail below.

A one-way clutch 1 according to this embodiment includes an outer ring 3 and an inner ring 5 that is spaced apart from the outer ring 3 in the radial direction and arranged coaxially with the outer ring 3 so as to be relatively rotatable. A spline 7 is formed on the outer peripheral portion of the outer ring 3 . The spline 7 is fitted with a spline 11 formed on the inner circumference of the input shaft 9 . Rotation of an output shaft of a motor, which is a driving device, is transmitted to the input shaft 9 via a gear mechanism (not shown). A shaft hole 12 is formed in the central portion of the inner ring 5, and an output shaft 13 is fitted in the shaft hole 12 with serrations. The output shaft 13 is connected to a drive shaft of an oil pump (not shown).

The one-way clutch 1 includes a plurality of (four in this embodiment) rollers 17 interposed at predetermined intervals in the circumferential direction between the inner peripheral surface of the outer ring 3 and the outer peripheral surface of the inner ring 5, and the rollers 17 on the outer ring. A coil-shaped or accordion-shaped spring 19 that biases the roller 3 and the inner ring 5 in a direction to join them, a block bearing 21, and a resin retainer 23 that holds the roller 17 and the block bearing 21 are provided. The roller 17 is a torque transmission member for connecting the outer ring 3 and the inner ring 5 and transmitting torque between the outer ring 3 and the inner ring 5 .

The one-way clutch 1 further moves a plurality of rollers 17 arranged between the outer ring 3 and the inner ring 5 and connecting the outer ring 3 and the inner ring 5 in a direction to release the connection between the outer ring 3 and the inner ring 5. A plurality of auxiliary rollers 24 are provided for the purpose. The auxiliary rollers 24 are provided in the same number as the rollers 17 . As will be described later, the auxiliary roller 24 is provided on the outer ring 3 so that when the number of rotations of the input shaft 9 connected to the output shaft of the motor exceeds a predetermined number of rotations, torque transmission at higher rotations than that does not occur. and a release mechanism for releasing the connection with the inner ring 5.

A plurality of cam portions 27 having cam surfaces 25 with which the rollers 17 are engaged are formed on the outer peripheral portion of the inner ring 5 . In this embodiment, four cam portions 27 are formed. These cam portions 27 are formed at predetermined intervals in the circumferential direction. The cam portion 27 is formed as a concave portion in which the outer peripheral surface of the inner ring 5 is recessed radially inward. The cam surface 25 of the cam portion 27 is an inclined surface that is inclined in a direction in which the radial distance from the inner peripheral surface of the outer ring 3 increases from one circumferential end of the recess toward the other circumferential end.

The roller 17 is a cylindrical member. The roller 17 is arranged on the cam portion 27 so that the axial direction of the roller 17 itself is parallel to the axial directions of the outer ring 3 and the inner ring 5 . The roller 17 slides or rolls on the cam surface 25 of the cam portion 27 .

The block bearing 21 has a circumferential dimension that gradually decreases from radially upper and lower ends toward a radially central portion, and the central portions of both circumferential surfaces are constricted. A plurality of block bearings 21 (four in the present embodiment) are arranged at predetermined intervals in the circumferential direction, maintain the radial distance between the outer ring 3 and the inner ring 5, and hold the outer ring 3 and the inner ring 5 concentrically. ing.

As shown in FIGS. 1 and 2, the retainer 23 includes a first annular portion 31 arranged on one side of the roller 17 in the axial direction and a second annular portion 33 arranged on the other side of the roller 17 in the axial direction. , and a plurality of pillars 35 axially connecting the first annular portion 31 and the second annular portion 33 . A plurality of (four in this embodiment) pillars 35 are provided along the entire circumference of the retainer 23 .

A concave portion 37 is formed on one circumferential side surface of the column portion 35 of the retainer 23 . A spring 19 is arranged in the concave portion 37 to urge the roller 17 in the engagement direction with the cam surface 25 , that is, in the circumferential direction. The surface of the column portion 35 on the other side in the circumferential direction is formed into a curved surface corresponding to the concave shape of the surface on the one side in the circumferential direction of the block bearing 21, and is in full contact with the surface on the one side in the circumferential direction of the block bearing 21. .

As shown in FIG. 1 , a flange 39 protruding radially inward is formed on the inner diameter side edge of the first annular portion 31 of the retainer 23 , and the surface on the other side in the axial direction of the flange 39 is in contact with the end face on one side in the axial direction of the A flange 40 protruding radially outward is formed on the outer diameter side edge of the first annular portion 31 of the retainer 23 , and the surface on the other axial side of the flange 40 is formed on the one axial side of the outer ring 3 . in contact with the end face. An end surface on one side in the axial direction of the first annular portion 31 is rotatably held by a peripheral member 44 of the one-way clutch 1 .

A flange 41 protruding radially inward is formed on the inner diameter side edge of the second annular portion 33 of the retainer 23 , and the surface of the flange 41 on one side in the axial direction corresponds to the end surface on the other side in the axial direction of the inner ring 5 . are in contact with A flange 43 protruding radially outward is formed on the outer diameter side edge of the second annular portion 33 of the retainer 23 . in contact with the end face. The end surface of the second annular portion 33 on the other side in the axial direction is rotatably held by a peripheral member 44 of the one-way clutch 1 . With such a configuration, the retainer 23 is restricted from moving in the axial direction.

A protruding portion 45 protruding radially inward and extending in the axial direction is formed on the inner peripheral portion of the column portion 35 of the retainer 23 . The projecting portion 45 engages with an axial groove 29 formed in the outer peripheral surface of the inner ring 5 . Due to this engagement, relative rotation of the retainer 23 with the inner ring 5 is restricted, and the retainer 23 rotates together with the inner ring 5 .

A concave surface portion 51 having an arcuate cross-sectional shape is formed adjacent to one circumferential end of each cam surface 25 on the outer peripheral portion of the inner ring 5 . The concave surface portion 51 axially penetrates the outer peripheral portion of the inner ring 5 . Further, on the outer peripheral portion of the inner ring 5, a protruding portion 53 is formed adjacent to one circumferential side of each concave portion 51 and protruding radially outward. The surface of the projecting portion 53 on one side in the circumferential direction is formed into a curved surface corresponding to the concave shape of the surface on the other side in the circumferential direction of the block bearing 21 , and is in full contact with the surface on the other side in the circumferential direction of the block bearing 21 . Circumferential movement of the block bearing 21 is restricted by the protruding portion 53 and the column portion 35 of the retainer 23, and rattling in the radially outward direction is also suppressed.

The surface of the projecting portion 53 of the inner ring 5 on the other side in the circumferential direction and the surface of the column portion 35 of the retainer 23 on the one side in the circumferential direction face each other in the circumferential direction with a predetermined gap therebetween. One roller 17 is arranged in a space 38 formed by a surface on one side in the circumferential direction of the column portion 35 and a surface on the other side in the circumferential direction of the projecting portion.

A protruding portion 55 protruding to the other circumferential direction is formed on the outer diameter side portion of the surface on the other circumferential direction side of the protruding portion 53 . The outer peripheral surface of the projecting portion 53 and the outer peripheral surface of the protruding portion 55 form one curved surface having the same radius of curvature as the radius of curvature of the inner peripheral surface of the outer ring 3 . The inner peripheral surface of the protruding portion 55 forms an inclined surface 57 inclined in a direction in which the radial distance from the outer peripheral surface of the inner ring 5 increases toward the other side in the circumferential direction, that is, toward the tip of the protruding portion 55 . In other words, the inner peripheral surface of the protruding portion 55 is an inclined surface 57 that is inclined in a direction in which the radial distance from the outer peripheral surface of the inner ring 5 increases as it extends radially outward, that is, in a direction toward the roller 17 . .

The inner diameter side portion of the surface on the other side in the circumferential direction of the projecting portion 53 is a curved surface portion 59 having an arcuate cross-sectional shape. The curved surface portion 59 forms a continuous portion between the concave surface portion 51 and the inclined surface 57 of the projecting portion 55 . The circular arc of the cross-sectional shape of the curved surface portion 59 has the same radius of curvature as the circular arc of the cross-sectional shape of the concave surface portion 51 of the inner ring 5, and is continuous with the circular arc of the cross-sectional shape of the concave surface portion 51 to form a substantially semicircular arc. .

A concave groove 61 extending in the axial direction and having a substantially U-shaped or J-shaped cross section is formed by the concave surface portion 51 of the inner ring 5, the curved surface portion 59 of the projecting portion 53, and the inclined surface 57 of the projecting portion 55. ing. The curved surface portion 59 and the curved surface portion 59 side portion of the concave surface portion 51 constitute the bottom portion of the concave groove 61 , and the cam surface 25 side portion of the concave surface portion 51 and the inclined surface 57 face each other with respect to the bottom portion of the concave groove 61 . It forms a pair of walls. The inclined surface 57 constitutes one circumferential wall of the groove 61 and extends radially outward of the concave portion 51 . That is, the inclined surface 57 covers the concave surface portion 51 radially outward through a space. Since the inclined surface 57 has such a configuration, the concave groove 61 is open radially outward and on the other side in the circumferential direction.

The radius of curvature of the bottom of the groove 61 is formed smaller than the radius of curvature of the roller 17 . An auxiliary roller 24 is arranged in the concave groove 61 . The auxiliary roller 24 is arranged on one circumferential side of the roller 17 . The auxiliary roller 24 is a columnar member, and the radius of curvature of its cross-sectional circle is slightly smaller than the radius of curvature of the bottom of the groove 61 . The auxiliary roller 24 has substantially the same axial length as the roller 17 and is arranged in the groove 61 so that the axial direction of the auxiliary roller 24 itself is parallel to the axial directions of the outer ring 3 and the inner ring 5 .

The auxiliary roller 24 has a diameter slightly smaller than the width between the pair of walls facing each other with respect to the bottom of the groove 61 . With such a configuration, the auxiliary roller 24 can move substantially radially along the inclined surface 57 of the groove 61 . As shown in FIG. 2 , when the auxiliary roller 24 is positioned at the bottom of the groove 61 , a part on the other side in the circumferential direction protrudes from the opening of the groove 61 , and the other part is accommodated in the groove 61 . ing. A portion of the auxiliary roller 24 protruding from the opening of the recessed groove 61 on the other side in the circumferential direction is in contact with a portion on the one side in the circumferential direction of the roller 17 . Thus, the recessed groove 61 constitutes an accommodating portion for the auxiliary roller 24 .

In the one-way clutch 1 of this embodiment having the configuration described above, when the outer ring 3 rotates to one side in the circumferential direction, that is, clockwise, the roller 17 engages the cam surface 25 of the inner ring 5 and the inner peripheral surface of the outer ring 3 . Together, the outer ring 3 and the inner ring 5 rotate together, and the rotation is transmitted from the outer ring 3 to the inner ring 5 . That is, the rotation of the output shaft of the motor input from the input shaft 9 to the outer ring 3 is transmitted to the inner ring 5 via the roller 17, which is a torque transmission member, and output as the rotation of the output shaft 13 fitted to the inner ring 5. ing. On the other hand, when the outer ring 3 rotates counterclockwise, the roller 17 does not engage with the cam surface 25 of the inner ring 5 and the outer ring 3 idles with respect to the inner ring 5 . Rotation is not transmitted from the outer ring 3 to the inner ring 5 in this state.

Next, the operation of the one-way clutch 1 of this embodiment will be described.
The one-way clutch 1 of this embodiment prevents transmission of rotation at higher rotation speeds when the number of rotations per unit time of the input shaft 9 connected to the output shaft of the motor exceeds a predetermined number of rotations. The coupling between the outer ring 3 and the inner ring 5 is released immediately, and the transmission of rotation from the outer ring 3 to the inner ring 5 is cut off.

When the motor is stopped, the outer ring 3 of the one-way clutch 1 is stopped. In this state, the roller 17 is biased to one side in the circumferential direction by the spring 19 , but the roller 17 is not engaged with the cam surface 25 . In this state, the auxiliary roller 24 is in contact with the one circumferential side of the roller 17 at the other side in the circumferential direction. It is located at the bottom of 61.

When the motor starts in this state and the rotation of the output shaft of the motor is transmitted to the input shaft 9, the rotation of the input shaft 9 is transmitted to the outer ring 3 of the one-way clutch 1, and the outer ring 3 rotates clockwise. When the outer ring 3 rotates, the roller 17 rolls or slides on the inner peripheral surface of the outer ring 3 and the cam surface 25 to move to one side in the circumferential direction and engage the cam surface 25 . As a result, the outer ring 3 and the inner ring 5 are coupled, and the outer ring 3 and the inner ring 5 rotate together.

At this time, the spring 19 prevents the roller 17 from moving to the other side in the circumferential direction by urging the roller 17 to the one side in the circumferential direction. Thus, the spring 19 maintains engagement with the cam surface 25 of the roller 17 and maintains the coupled state between the outer ring 3 and the inner ring 5 . In this state, the rotation of the output shaft of the motor input from the input shaft 9 to the one-way clutch 1 is transmitted to the inner ring 5 via the roller 17 and output as the rotation of the output shaft 13 .

In this state, as shown in FIG. 2, the auxiliary roller 24 is pushed to one side in the circumferential direction by the movement of the roller 17 and pressed against the bottom of the groove 61 .

When the inner ring 5 rotates together with the outer ring 3 , centrifugal force acts on the auxiliary rollers 24 arranged in the concave grooves 61 . When the number of revolutions per unit time of the input shaft 9 increases and the number of revolutions per unit time of the inner ring 5 accordingly increases, the centrifugal force acting on the auxiliary roller 24 also increases.

In this embodiment, the number of rotations per unit time of the input shaft 9 is equal to or less than a predetermined number of rotations in the range of the number of revolutions of the motor from the low speed range to the range of revolutions corresponding to the normal running state of the vehicle. . In this state, the centrifugal force acting on the auxiliary roller 24 does not exceed the engaging force between the roller 17 and the outer ring 3 and between the roller 17 and the inner ring 5 generated by the rotational torque from the outer ring 3 . Therefore, each auxiliary roller 24 remains pressed against the roller 17 and does not move from the bottom of the groove 61 . The outer ring 3 and the inner ring 5 rotate together, and the rotation is transmitted from the input shaft 9 to the output shaft 13 .

When the number of rotations of the motor increases and enters a high-speed rotation range, the number of rotations per unit time of the input shaft 9 exceeds a predetermined number of rotations. That is, the rotation speed of the inner ring 5 per unit time exceeds the predetermined rotation speed. In this state, the centrifugal force acting on the auxiliary roller 24 exceeds the engaging force between the roller 17 and the outer ring 3 and between the roller 17 and the inner ring 5 generated by the rotational torque from the outer ring 3 . Then, since centrifugal force exerts radially outward force on the auxiliary roller 24, the auxiliary roller 24 tries to move radially outward. However, since the inclined surface 57, which is the wall surface of the groove 61 on one side in the circumferential direction, is disposed radially outward of the groove 61, the auxiliary roller 24 rolls or slides on the inclined surface 57 and is inclined. It moves radially outward and circumferentially on the other side along the surface 57 . When the auxiliary roller 24 moves along the inclined surface 57, the auxiliary roller 24 further protrudes from the opening of the recessed groove 61, presses the contacting roller 17 to the other side in the circumferential direction, and pushes the inner ring 5 to the one side in the circumferential direction. By pressing, the engaging force between the roller 17 and the cam surface 25 of the inner ring 5 is reduced.

As described above, the roller 17 is pressed to the other side in the circumferential direction by the auxiliary roller 24 and moves on the cam surface 25 to the other side in the circumferential direction. Thus, the engagement between the roller 17 and the cam surface 25 is released, and at the same time the connection between the outer ring 3 and the inner ring 5 is also released. Thus, the auxiliary roller 24 and the inclined surface 57 that is the wall of the groove 61 constitute a release mechanism for releasing the connection between the outer ring 3 and the inner ring 5 .

FIG. 3 is a cross-sectional view taken along line XX in FIG. 1 and shows a state in which the coupling between the outer ring 3 and the inner ring 5 is released by the auxiliary roller 24. FIG. 4 is a partially enlarged view of FIG. 3. FIG.
In a state where the outer ring 3 and the inner ring 5 are disengaged, the outer ring 3 is idle with respect to the inner ring 5 . Therefore, the high-speed rotation of the motor input from the input shaft 9 to the outer ring 3 is not transmitted to the inner ring 5 . On the other hand, even if the coupling between the outer ring 3 and the inner ring 5 is released, the inner ring 5 continues to rotate due to rotational inertia until the coupling is released. Therefore, rotation of the inner ring 5 is output as rotation of the output shaft 13 . That is, the driving of the drive shaft of the oil pump is continued.

As shown in FIGS. 3 and 4, when the outer ring 3 and the inner ring 5 are disengaged by centrifugal force, the auxiliary roller 24 is positioned at the opening of the groove 61 and substantially half of the groove 61 is positioned. protruding from the opening. In this state, the auxiliary roller 24 is in contact with the roller 17 , the edge of the concave portion 51 of the inner ring 5 , and the inclined surface 57 of the concave groove 61 .

Here, as shown in FIG. 4, when viewed from one side in the axial direction, a straight line A connecting the contact point between the auxiliary roller 24 and the roller 17 and the center C of the auxiliary roller 24, the auxiliary roller 24 and the inclined surface 57 between the contact point and the straight line B connecting the center C of the auxiliary roller 24 is an obtuse angle. By configuring the roller 17 , the auxiliary roller 24 , and the inclined surface 57 of the concave groove 61 in this way, the centrifugal force acting on the auxiliary roller 24 is applied to the roller 17 arranged on one circumferential side of the auxiliary roller 24 . effectively. As a result, the number of revolutions per unit time of the input shaft 9 for moving the auxiliary roller 24 can be appropriately set.

When the number of revolutions of the motor decreases and the number of revolutions per unit time of the input shaft 9 becomes equal to or less than a predetermined number of revolutions from the state in which the outer ring 3 and the inner ring 5 are disengaged, a centrifugal force acting on the auxiliary roller 24 is applied. The force is smaller than the engaging force between the roller 17 and the outer ring 3 and between the roller 17 and the inner ring 5 generated by the rotational torque from the outer ring 3 . Then, the roller 17 is pressed to one side in the circumferential direction and moves on the cam surface 25 to the one side in the circumferential direction. Due to this movement of the roller 17 , the auxiliary roller 24 is pushed to one side in the circumferential direction and moves to the bottom of the groove 61 . The roller 17 then engages the cam surface 25 . As a result, the outer ring 3 and the inner ring 5 are connected again, and the outer ring 3 and the inner ring 5 rotate together.

As described above, in the one-way clutch 1 of the present embodiment, the rotation of the output shaft of the motor transmitted to the input shaft 9 is transmitted from the outer ring 3 when the number of revolutions per unit time of the input shaft 9 is equal to or less than a predetermined number of revolutions. While the rotation is transmitted to the inner ring 5, the transmission of rotation from the outer ring 3 to the inner ring 5 is cut off when the number of rotations per unit time of the input shaft 9 exceeds a predetermined number of rotations. As described above, according to the present embodiment, the input rotation speed input to the one-way clutch 1 from the power source side input shaft 9 can be controlled without providing a control device separate from the one-way clutch 1 . As a result, the size of the one-way clutch 1 can be suppressed, and stable torque transmission can be achieved even when a high-speed motor is used as the power source on the input side.

The number of rotations per unit time of the input shaft 9 for connecting and disconnecting the outer ring 3 and the inner ring 5 is determined by the diameter and number of the rollers 17 of the one-way clutch 1, the diameter of the auxiliary roller 24, the outer ring 3 and the inner ring 5. It is designed by comprehensively considering the size of the motor, the size of the motor output, etc.

It should be noted that the one-way clutch 1 according to this embodiment is not limited to the above embodiment, and can be modified. For example, the number of rollers 17 and auxiliary rollers 24 can be appropriately adjusted according to the required torque capacity. Moreover, although the cam surface 25 is provided on the inner ring 5 in the above embodiment, the cam surface 25 may be provided on the outer ring 3 . Alternatively, one or a plurality of balls having the same diameter as the auxiliary roller 24 may be arranged instead of the auxiliary roller 24 by covering both ends of the concave groove 61 in the axial direction.

1 One-Way Clutch 3 Outer Ring 5 Inner Ring 9 Input Shaft 12 Shaft Hole 13 Output Shaft 17 Roller 19 Spring 21 Block Bearing 23 Cage 24 Auxiliary Roller 25 Cam Surface 27 Cam Section 51 Concave Section 53 Protruding Section 55 Overhang Section 57 Inclined Surface 59 Curved Surface Section 61 groove

Claims (2)

an outer ring to which rotation from the outside is input;
an inner ring disposed on the inner diameter side of the outer ring so as to be relatively rotatable with the outer ring, and having a plurality of cam surfaces on the outer peripheral surface at predetermined intervals in the circumferential direction;
a plurality of first rollers disposed on each of the plurality of cam surfaces and movable between a torque transmission position where the outer ring and the inner ring are coupled and a torque non-transmission position where the coupling is released;
a plurality of elastic members that bias the plurality of first rollers to the torque transmission position and hold the coupling between the outer ring and the inner ring when the rotation from the outside is within a predetermined number of rotations;
a release mechanism that moves the plurality of first rollers to the torque non-transmission position to release the coupling when the rotation from the outside exceeds the predetermined number of rotations;
The release mechanism is
a concave portion provided in the portion of the outer peripheral surface of the inner ring adjacent to each of the cam surfaces and having an inclined portion inclined toward the first roller as it goes radially outward; a second roller movably in a direction and disposed in contact with the first roller;
The recessed portion and the inclined portion have a shape that holds the second roller so that the second roller is always in contact with the first roller,
The one-way roller is characterized in that the first roller is moved to the torque non-transmitting position by moving the recessed portion along the inclined portion by centrifugal force generated by rotation of the second roller together with the inner ring. clutch. When the coupling between the outer ring and the inner ring is released by the release mechanism, the point of contact between the first roller and the second roller and the center of the second roller are aligned when viewed from the axial direction. and a straight line connecting the point of contact between the inclined portion and the second roller and the center of the second roller form an obtuse angle. one way clutch.

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