JP2013053644A - One-way clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a one-way clutch in which a fastening-releasing state is switched if a torque input direction is changed, even though a rotating direction is not changed.SOLUTION: In the one-way clutch, a lock member 103 is disposed between an input member 101 and an output member 102. When the lock member 103 is displaced to one side in a circumferential direction with respect to the input member 101, the lock member 103 is sandwiched between the input member 101 and the output member 102 to thereby achieve a fastening state. The one-way clutch includes a holder 100, which allows a relative rotational displacement to the input member and the output member, and which displaces the lock member 103 to one side in the circumferential direction with respect to the input member 101 by performing the relative rotational displacement to the input member 101, when the input direction of torque to the input member 101 is changed from one to the other direction.

Description

  The present invention relates to a torque-sensitive one-way clutch.

  As an example of a one-way clutch, Patent Document 1 discloses a configuration in which a plurality of sprags are arranged at predetermined intervals in the circumferential direction between an outer race as an input member and an inner race as an output member. In this one-way clutch, when the outer race rotates in a predetermined direction, the sprag contacts the outer race and the inner race. When the outer race rotates in the opposite direction, the sprag contacts the outer race but is not in contact with the inner race. . Thereby, torque is transmitted only when rotating in a predetermined direction.

JP 2009-156212 A

  The one-way clutch of Patent Document 1 is a rotation sensitive type in which engagement and release are switched according to the rotation direction of the input member. Therefore, when a rotation in one direction is input, a fastening state is established, and when a rotation in the opposite direction is input, a release state is established. However, if the rotation direction does not change, for example, even if the magnitude of the input torque is changed, the fastening and the release are not switched.

  Consider a case in which such a one-way clutch is interposed, for example, to transmit a drive torque input from the drive source side of the vehicle to the drive wheel side and to block a coast torque input from the drive wheel side. In this case, if the moment of inertia of the input member is large, even if the direction of torque input changes from coast torque input to drive torque input, the input member does not switch from the released state to the engaged state until the rotation direction of the input member changes. For this reason, drive torque input cannot be transmitted to the drive wheel side until the rotation direction of the input member changes.

  Therefore, an object of the present invention is to provide a one-way clutch in which the engaged state and the released state are switched when the torque input direction is changed even if the rotational direction is not changed.

  In the one-way clutch of the present invention, the lock member is disposed between the input member and the output member, and when the lock member is displaced to one side in the circumferential direction with respect to the input member, the lock member is sandwiched between the input member and the output member. Will be in a fastened state. Then, the lock member can be changed to the input member by being relatively rotatable with respect to the input member and the output member, and when the torque input direction to the input member is changed from one to the other, the relative rotation is displaced with respect to the input member. On the other hand, a cage is provided that is displaced to one side in the circumferential direction.

  According to the present invention, since the cage can be rotated relative to both the input member and the output member, even if the direction of torque input to the input member is switched, the cage continues to rotate due to the action of inertial force. To do. In addition, when the torque input direction to the input member changes from one to the other, the cage displaces the lock member to one side in the circumferential direction with respect to the input member by performing relative rotational displacement with respect to the input member. Let That is, in the one-way clutch of the present invention, when the torque input direction to the input member changes from one to the other, the cage causes the lock member to rotate relative to the input rotation member by the action of inertial force, and is in the engaged state. It becomes. In this way, the released state is switched to the engaged state in accordance with the change in the torque input direction.

It is a block diagram of the one-way clutch which concerns on 1st Embodiment of this invention, (A) shows a releasing state, (B) shows a fastening state. It is a block diagram which shows the releasing state of the other example of the one-way clutch which concerns on 1st Embodiment. It is a figure which shows an example of the torque transmission device which applies the one-way clutch which concerns on 1st Embodiment. It is a front view of the weight part of a torque transmission device. It is a figure for demonstrating a motion of a torque transmission device. (A) is a figure for demonstrating about the torque in case (theta) is zero-180 degree | times, (B) is a figure for demonstrating about the torque in case (theta) is 180-360 degree | times, respectively. It is a figure for demonstrating the effect | action of a torque transmission device, (A) is the rotation speed of an input member, (B) is the vibration torque which generate | occur | produces by rotation of a weight, (C) is about the output shaft torque taken out by a one-way clutch. FIG. It is a block diagram which shows the further another example of the one-way clutch which concerns on 1st Embodiment of this invention, (A) shows a releasing state, (B) shows a fastening state. It is a block diagram of the one-way clutch which concerns on 2nd Embodiment of this invention, (A) shows a releasing state, (B) shows a fastening state. It is the figure which looked at the input member of the one-way clutch which concerns on 2nd Embodiment of this invention from the axial direction. It is a block diagram of the one-way clutch which concerns on 3rd Embodiment of this invention, (A) shows a releasing state, (B) shows a fastening state.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
FIG. 1 is a configuration diagram showing an example of a one-way clutch according to a first embodiment of the present invention, in which FIG. 1 (A) shows a released state and FIG. 1 (B) shows an engaged state.

  The one-way clutch is released when a clockwise torque is input to the input member 101, and is engaged when a counterclockwise torque is input. Specifically, the configuration is as described below.

  The input member 101 is a member whose outer peripheral portion is formed by a plurality of inclined portions 101A. Each inclined portion 101A is provided so as to gradually approach the output member 102 as it proceeds in the clockwise direction. A wall surface 101B is provided at the boundary between adjacent inclined portions 101A.

  The output member 102 is a member provided with a predetermined gap on the outer peripheral side of the input member 101.

  Between the input member 101 and the output member 102, a ball 103 and an annular cage 100 are provided. One ball 103 is arranged on each inclined portion 101A. Both the ball 103 and the cage 100 are freely movable with respect to the input member 101 and the output member 102. The ball 103 is rotatably held by the cage 100. The diameter of the ball 103 is a size between the minimum value and the maximum value of the interval between the inclined portion 101 </ b> A and the inner peripheral surface of the output member 102. A cylindrical roller may be used in place of the ball 103.

  The cage 100 includes a plurality of protrusions 100A that protrude radially inward. The protrusions 100A are provided at the same interval as the wall surface 101B of the input member 101. The cage 100 is provided such that the protrusion 100A is positioned between the wall surface 101B and the ball 103.

  A mechanism for switching between the engaged state and the released state of the one-way clutch as described above will be described. Here, description will be made assuming that an input side rotating member for torque input is connected to the input member 101 and an output side rotating member for torque output is connected to the output member 102.

  When torque in the clockwise direction is input to the input member 101, the input member 101 rotates in the clockwise direction. At this time, the wall surface 101B pushes the ball 103 through the protrusion 100A. That is, the input member 101, the cage 100, and the ball 103 rotate together around the axis of the input member 101 in a state where one surface of the protrusion 100A is in contact with the wall surface 101B and the other surface is in contact with the ball 103. . Therefore, the ball 103 is not in contact with the output member 102 and is in a released state. Even if the ball 103 moves in the radial direction by centrifugal force and moves away from the input member 101 and comes into contact with the output member 102, the ball 103 rotates while being held by the cage 100, The differential rotation of the output member 102 is absorbed.

  On the other hand, when a counterclockwise torque is input to the input member 101, only the input member 101 rotates counterclockwise. As a result, the protrusion 100A moves away from the wall surface 101B and pushes up the ball 103 along the inclined portion 101A. When the ball 103 is sandwiched between the inclined portion 101 </ b> A and the output member 102, a fastening state is established, and torque is transmitted from the input member 101 to the output member 102.

  By the way, in the one-way clutch of this embodiment, in order to switch from the released state to the engaged state, it is not necessary for the input member 101 to rotate counterclockwise, and it is sufficient if the torque input direction is switched. For example, consider the case where the torque input direction is switched to the counterclockwise direction from the released state where the torque in the clockwise direction is input and the input member 101 rotates in the clockwise direction.

  When the input direction of the torque is reversed, the rotation speed of the input member 101 immediately decreases, but the cage 100 and the ball 103 that are not fixed to the input member 101 continue to rotate as they are due to the action of the inertial force. Thereby, the ball 103 is pushed up along the inclined portion 101 </ b> A by its own inertial force and the cage 100, and is sandwiched between the input member 101 and the output member 102. As a result, there is no relative rotation between the input member 101 and the output member 102 and a fastening state is established.

  That is, when the torque input direction to the input member 101 is switched from the clockwise direction to the counterclockwise direction, the input member 101 is switched from the released state to the fastening state even if the rotation direction of the input member 101 remains the clockwise direction.

  Further, when the torque input direction to the input member 101 is switched again in the clockwise direction in the fastened state, only the input member 101 rotates in the clockwise direction, so that the pinching of the ball 103 is released and the released state is released. Switch to

  If the one-way clutch switches between the engaged state and the released state according to the change in the torque input direction as described above, even if the input member has a large inertia, the released state changes from the released state according to the change in the torque input direction. You can switch to

  FIG. 2 is a diagram showing an example of a one-way clutch that has the same function as the one-way clutch shown in FIGS. 1A and 1B but is different in the positional relationship between the input member 101 and the output member 102. FIG. 2 shows the released state.

  1A and 1B, the input member 101 has an inner peripheral side and the output member 102 has an outer peripheral side. However, in FIG. 2, the input member 101 has an outer peripheral side and the output member 102 has an opposite side. Is on the inner circumference side. For this reason, the inclined portion 101A is formed so as to gradually approach the output member 102 on the inner peripheral side.

  The mechanism for switching between the fastening state and the releasing state is the same as the structure shown in FIGS. 1 (A) and 1 (B). That is, when the input member 101 is rotated by the clockwise torque, the wall surface 101B pushes the ball 103 in the circumferential direction via the protrusion 100A. At this time, since the input member 101, the cage 100, and the ball 103 rotate at the same rotational speed, the ball 103 does not contact the output member 102 and is in a released state.

  When the torque input to the input member 101 changes in the counterclockwise direction, the ball 103 is sandwiched between the input member 101 and the output member 102 due to the inertia of the cage 100 and is in a fastening state. When the torque input direction is switched clockwise in the engaged state, the pinching of the ball 103 is released and the state is switched again to the released state. Such a one-way clutch is referred to as a torque-sensitive one-way clutch in the following description. In contrast, a one-way clutch having a structure in which the engaged state and the released state are not switched unless the rotation direction is switched is referred to as a rotation-sensitive one-way clutch.

  Next, a usage example of the above-described one-way clutch will be described.

  FIG. 3 is a cross-sectional view of a torque transmission device OTC that transmits a driving force input from a driving source such as an internal combustion engine or an electric motor to wheels via a drive shaft or the like. FIG. 4 is a front view of the weight 7 portion of the torque transmission device OTC.

  The torque transmission device OTC includes a yoke 4 that rotates around a rotation shaft by torque input from a drive source, and a cylindrical fixed shaft 31 that is fixed to a transmission or a vehicle body. A cylindrical torque transmission shaft 10 is rotatably supported by the yoke 4 via a bearing 13 and coaxially with the rotation shaft of the yoke 4. On the inner peripheral side of the fixed shaft 31, an output shaft 30 is rotatably supported via a bearing 32 and is supported coaxially with the rotating shaft of the yoke 4. The output shaft 30 is also rotatable on the inner peripheral side of the torque transmission shaft 10 via the bearing 20 and is supported coaxially with the rotation shaft of the yoke 4. In addition to the bearing 20, a first one-way clutch 11 is interposed between the output shaft 30 and the torque transmission shaft 10. At least a part of the fixed shaft 31 and the torque transmission shaft 10 overlap in the direction of the rotation axis of the yoke 4, and the fixed shaft 31 has a smaller diameter than the torque transmission shaft 10 in the overlapping portion. In the overlapping portion, the second one-way clutch 12 is interposed between the fixed shaft 31 and the torque transmission shaft 10. As the second one-way clutch 12, a torque-sensitive one-way clutch is used. Specifically, the torque transmission shaft 10 and the input member 101, and the fixed shaft 31 and the output member 102 are fitted to each other with the configuration shown in FIG. The first one-way clutch 11 may be a rotation sensitive type.

  The first one-way clutch 11 is engaged when vibration torque described later acts in the same direction as input rotation (hereinafter, this direction is referred to as a positive direction), and transmits the vibration torque to the output shaft 30. When the vibration torque acts in a negative direction, the second one-way clutch 12 is engaged and the torque transmission shaft 10 is fixed to the fixed shaft 31 to stop the rotation, and the engagement of the first one-way clutch 11 is released. Therefore, the output shaft 30 continues to rotate with the inertia of the rotation so far.

  An eccentric shaft 9 </ b> A and an eccentric shaft 9 </ b> B are fixed to the outer periphery of the torque transmission shaft 10 side by side in the direction of the rotation axis of the yoke 4. The eccentric directions of the eccentric shaft 9A and the eccentric shaft 9B are shifted by 180 °. A weight 7A is rotatably supported on the eccentric shaft 9A via a bearing 16A. Similarly, a weight 7B is rotatably supported on the eccentric shaft 9B via a bearing 16B.

  The weight 7 </ b> A includes a pin hole 33 that penetrates the weight 7 </ b> A in the direction of the rotation axis of the yoke 4. Then, both ends of the pin 19 </ b> A inserted through the pin hole 33 are fixed to the yoke 4. Similarly, the pin 19B is inserted through the weight 7B.

  The opening of the pin hole 33 viewed from the direction of the rotation axis of the yoke 4 has a long hole shape in which the pins 19A and 19B can slide as shown in FIG.

  Although the eccentric amounts of the eccentric shafts 9A and 9B with respect to the rotation shaft of the torque transmission shaft 10 are equal, the eccentric direction is the opposite direction across the torque transmission shaft 10. In other words, when the number of weights 7 is N, a plurality of weights 7 are provided so that the magnitude of the inertia around the rotation axis distributed in each direction of 360 / N degree intervals in the rotation direction of the yoke 4 is equal. .

  In this description, when individual weights or eccentric shafts are shown, they are distinguished as 7A, 7B, or 9A, 9B, respectively, and when both are collectively referred to as 7 or 9. The same applies to a yoke shaft 5 and a link 6 described later.

  The weight 7 is a thin portion 17A having a relatively short axial length on the side fitted to the bearing 16, and a thick portion 17B having a relatively long axial length on the side connected to the link 6. Yes.

  The weights 7A and 7B have the same shape, and are arranged so that the thick portions 17B are located on opposite sides of the central axis of the eccentric shaft 9 when the torque transmission device OTC is stopped. Further, the weight 7A is arranged so that the thick portion 17B extends to the load side, and the weight 7B is arranged so that the thin portion 17A faces each other in the axial direction so that the thick portion 17B extends to the drive source side. . However, the thick portion 17B is set so as not to interfere with the other thin portion 17A when the pair of weights 7 are brought close to each other in the direction of the torque transmission shaft 10.

  Next, the operation of the torque transmission device OTC will be described.

  When rotation is input from the drive source, the yoke 4 rotates about the rotation axis, and the weight 7 connected to the yoke 4 via the pin 19 also rotates. However, the weight 7 rotates about the center of the eccentric shaft 9 as a rotation axis. That is, the centrifugal force generated by the rotation of the weight 7 acts in a direction deviated from the radial direction of the torque transmission shaft 10, and torque for rotating the torque transmission shaft 10 is generated. The mechanism of torque generation will be described later.

  Here, the movement of each component will be described with reference to FIG. FIG. 5 is a view of the weight 7 portion seen from the front as in FIG. The rotational axis of the torque transmission shaft 10 is O, the central axis of the pin 19 is B, the center of gravity of the weight 7 is C, and the center of the eccentric shaft 9 is D. A vector in the C to B direction is R2, a vector in the D to C direction is R3, a vector in the O to D direction is R4, and an angle between the vector R3 and the vector R4 is θ.

  The center axis B of the pin 19 moves at an angular velocity ωin2 different from the input rotation, and its locus does not become a perfect circle when the rotation axis O is the center. The same applies to the center of gravity C of the weight 7. The reason why these trajectories do not become a perfect circle is that the centers of the torque transmission shaft 10 and the eccentric shaft 9 are eccentric. The reason why the torque transmission shaft 10 and the eccentric shaft 9 can rotate despite the eccentricity is that the pin 19 slides along the pin hole 33 to absorb the amount of eccentricity. The locus of the central axis B and the center of gravity C is a perfect circle when the center D of the eccentric shaft 9 is the center.

  The center D of the eccentric shaft 9 moves at an angular velocity equal to the rotation of the torque transmission shaft 10, and its locus is a perfect circle centered on the rotation axis O.

  Since the angle θ is an angle formed by the vector R3 and the vector R4, it can be obtained from the equation (1) of the inner product of the vectors.

  Next, a mechanism for generating torque for rotating the torque transmission shaft 10 will be described.

  6A and 6B are diagrams showing the relationship between the centrifugal force F and the torque T. FIG. Here, for simplicity, it is assumed that the weight 7 can rotate without being restricted by the link 6.

  Centrifugal force generated by the rotation of the weight 7 is expressed by Expression (2).

  As shown in FIGS. 6A and 6B, the centrifugal force F acts on the center D of the eccentric shaft 9 in the vector R3 direction. And the torque T represented by Formula (3) acts on the rotating shaft O.

  When θ in the state in which the vector R3 coincides with the Y axis in the figure is zero degrees and the clockwise direction in the figure is positive, when θ is between zero and 180 degrees, FIG. As shown, the torque T acts in the clockwise direction in the figure, that is, in the positive direction. On the other hand, when θ is between 180 degrees and 360 degrees, the torque T acts counterclockwise, that is, in a negative direction, as shown in FIG. 6B.

  FIG. 7A, FIG. 7B, and FIG. 7C are time charts for explaining the torque transmitted by the torque transmission device OTC. 7A is a chart for the rotation input to the torque transmission device OTC, FIG. 7B is a chart for the torque T generated thereby, and FIG. 7C is a chart for the torque transmitted to the output shaft 30. .

  As shown in FIG. 7A, when the rotation at a constant speed is input and the weight 7 rotates, the magnitude and direction of the torque T change periodically. This change can be represented by a sine wave as shown in FIG. 7B, as is apparent from the equation (3).

  The first one-way clutch 11 and the second one-way clutch 12 described above transmit torque to the output shaft 30 only when the torque T acts in the positive direction as shown in FIG.

  More specifically, when a positive torque T is input, the first one-way clutch 11 prohibits relative rotation between the torque transmission shaft 10 and the output shaft 30, and the second one-way clutch 12 is a torque transmission shaft. 10 is freely rotated with respect to the fixed shaft 31. As a result, torque is transmitted from the output shaft 30 to the drive wheels.

  On the other hand, when the torque T in the negative direction is input, the first one-way clutch 11 freely rotates the output shaft 30 with respect to the torque transmission shaft 10, and the second one-way clutch 12 transmits torque to the fixed shaft 31. The differential rotation of the shaft 10 is prohibited. Thereby, the output shaft 30 continues to rotate with the inertia of the rotation so far. Further, the output shaft 30 is allowed to rotate by the rotation of the wheels.

  In the torque transmission device OCT that converts the centrifugal force F generated by the rotation of the weight 7 into the torque T and transmits the torque T, friction is generated in the torque transmission path by the bearings 13 and 16, the first one-way clutch 11 and the second one-way. Only the clutch 12 is provided. For this reason, the transmission efficiency is higher than that of a general vehicle clutch. Further, since the centrifugal force of the weight 7 is used, the driving force amplifying function is provided in the same manner as a general torque converter. Further, as with a general torque converter, the speed ratio can be covered from zero to 1 without requiring control.

  By the way, even if a rotation sensitive type is used as the second one-way clutch 12, the torque transmission device OCT can perform its function. However, as described below, the transmission efficiency can be further increased if the second one-way clutch 12 is torque sensitive.

  When the second one-way clutch 12 is rotationally sensitive, it remains in the released state until the direction of operation of the torque T is switched negatively until the direction of rotation of the torque transmission shaft 10 is switched. Until the rotation direction of the torque transmission shaft 10 is switched, the rotation-sensitive first one-way clutch 11 remains in the engaged state. For this reason, the torque input to the output shaft 30 via the first one-way clutch 11 gradually decreases from when the direction of action of the torque T becomes negative until the second one-way clutch 12 switches to the engaged state. Become. In other words, the rotation of the output shaft 30 is braked until the second one-way clutch 12 is engaged. In particular, in the configuration in which torque is generated by the rotation of the weight 7 as in the torque transmission device OCT shown in FIG. 3, since the inertial force acting on the torque transmission shaft 10 is large, the torque after the input direction of the torque T is switched to a negative value. It takes time until the rotation direction of the transmission shaft 10 is switched.

  On the other hand, the torque transmission device OCT blocks torque transmission between the torque transmission shaft 10 and the output shaft 30 when the torque T input to the torque transmission shaft 10 is negative as described above. While the torque transmission is interrupted, the output shaft 30 rotates due to the inertial force. Therefore, in order to keep the rotational speed of the output shaft 30 high while the torque transmission is interrupted, the output shaft 30 of the output shaft 30 at the timing when the torque transmission is interrupted, that is, the timing when the first one-way clutch 11 is released. It is desirable that the rotation speed be higher. However, if the second one-way clutch 12 is rotationally sensitive, the rotation of the output shaft 30 is braked before the second one-way clutch 12 is engaged as described above.

  On the other hand, if the second one-way clutch 12 is a torque sensitive type, when the input direction of the torque T is switched to the negative direction, it is quickly engaged and the torque transmission shaft 10 is fixed to the fixed shaft 31. On the other hand, since the output shaft 30 continues to rotate due to the inertial force, the relative rotation directions of both are reversed, and the first one-way clutch 11 is released. Thereby, after the input direction of the torque T is switched to negative, it can be avoided that the rotation of the output shaft 30 is braked. As a result, it is possible to suppress a decrease in the rotation speed of the output shaft 30 during a period in which the input direction of the torque T to the torque transmission shaft 10 is negative, and to exhibit higher transmission efficiency.

  In the torque-sensitive one-way clutch shown in FIG. 1, a wedge 104 as shown in FIGS. 8A and 8B may be used instead of the ball 103. 8 (A) and 8 (B) show the configuration of the one-way clutch as in FIGS. 1 (A) and 1 (B), FIG. 8 (A) shows the released state, and FIG. 8 (B). Indicates a fastening state. The only difference from FIGS. 1A and 1B is that the ball 103 is a wedge 104.

  The wedge 104 is configured to include a base end surface 104A that faces the protruding portion 100A, a sliding surface 104B that faces the inclined portion 101A, and an inclined surface 104C that faces the inner peripheral surface of the output member 102.

  Even in such a configuration, the fastening state and the releasing state are switched by the same mechanism as in the case of the ball 103. That is, when a clockwise torque is input to the input member 101, the wall surface 101B pushes the proximal end surface 104A of the wedge 104 via the protrusion 100A, and these rotate integrally. As a result, the wedge 104 does not contact the output member 102 and is released. When the input direction of the torque is switched counterclockwise, the cage 100 pushes up the wedge 104 along the inclined portion 101A, and the wedge 104 is sandwiched between the input member 101 and the output member 102 to be in a fastening state.

  As described above, the one-way clutch of the present embodiment can be displaced relative to the input member 101 and the output member 102, and the ball 103 is moved when the direction of torque input to the input member 101 changes from one to the other. A cage 100 is provided that is displaced to one side in the circumferential direction with respect to the input member 101. Thereby, when the direction of torque input to the input member 101 changes, the release state is switched to the fastening state even if the rotation direction does not change.

  More specifically, the retainer 100 rotates integrally with the input member 101 while being biased by the input member 101 when the torque input direction to the input member 101 is one. When the direction of torque input to the input member 101 is reversed, the ball 103 is displaced to one side in the circumferential direction with respect to the input member 101 by an inertial force.

  Such a one-way clutch having sensitivity in the torque input direction is particularly useful when it is desired to quickly switch between the released state and the engaged state in response to a change in the torque input direction in a device having a large inertia of the input member 101.

(Second Embodiment)
9 (A) and 9 (B) are views of the one-way clutch according to the second embodiment of the present invention as viewed from the side, FIG. 9 (A) is in the released state, and FIG. 9 (B) is the fastening state. Indicates the state. FIG. 10 is a cross-sectional view taken along line XX in FIG.

  In the one-way clutch of this embodiment, a disc-shaped input member 101 attached to the tip of the input-side rotating member 200 and a disc-like output member 102 attached to the tip of the output-side rotating member 201 are opposed to each other. It is the same as in the first embodiment that the ball 103 is sandwiched between surfaces facing each other (hereinafter, this surface is referred to as a surface) and the fastening state is achieved.

  The surface of the input member 101 is divided into a predetermined number (6 in FIG. 10) of sections in the circumferential direction, and each section is an inclined portion 101A that approaches the output member 102 as it proceeds in the same circumferential direction. A wall surface 101B is provided at the boundary of each inclined portion 101A.

  Between the input member 101 and the output member 102, the cage 100 is disposed so as to be freely rotatable with respect to both. The cage 100 has a branch portion 100B extending in the radial direction of each section, and each branch portion 100B holds a ball 103. The ball 103 is held on the side opposite to the wall surface 101B of the branch part 100B.

  When torque in the counterclockwise direction in FIG. 10 is input to the input member 101 and the input member 101 rotates in the clockwise direction, the wall surface 101B passes through the cage 100 as shown in FIG. The ball 103 is pushed, and the ball 103 and the output member 102 do not contact each other. Thereby, it will be in a release state.

  On the other hand, when the input direction of torque to the input member 101 is switched clockwise in FIG. 10 while rotating in the released state, the rotational speed of the input member 101 decreases, but the cage 100 and the ball 103 are moved by inertial force. It tries to keep rotating as it is. As a result, the cage 100 pushes up the ball 103 along the inclined portion 101A, and the ball 103 is sandwiched between the input member 101 and the output member 102 as shown in FIG. Further, when the input direction of the torque to the input member 101 is switched counterclockwise in the fastening state, the input member 101 is rotated in the input direction of the torque, so that the pinching of the ball 103 is eliminated and the input state is switched to the released state. .

  As described above, according to the present embodiment, similarly to the first embodiment, the release state and the fastening state are quickly switched according to the switching of the torque input direction.

  Also in this embodiment, a wedge 104 may be used instead of the ball 103.

(Third embodiment)
11 (A) and 11 (B) are views of the one-way clutch according to the third embodiment of the present invention as viewed from the side, FIG. 11 (A) is in a released state, and FIG. 11 (B) is a fastening state. Indicates the state.

  The input member 101 is a member having a plurality of inclined portions 101A on the outer peripheral portion. The inclined portion 101A is provided so as to gradually approach the output member 102 as it proceeds in the clockwise direction. A wall surface 101B is provided at the boundary between adjacent inclined portions 101A. The angle formed by the inclined portion 101A and the wall surface 101B is an acute angle.

  The output member 102 is a member provided with a predetermined gap on the outer peripheral side of the input member 101.

  A wedge 105 and an annular cage 100 are provided between the input member 101 and the output member 102. One wedge 105 is disposed on each inclined portion 101A, and each wedge 105 is held by the cage 100 so as to be rotatable about the pin 106 as an axis. The pin 106 is preferably located near the right end of the wedge 105 in FIG.

  The cage 100 can freely move with respect to the input member 101 and the output member 102. The cage 100 also includes a mechanism that presses the wedge 105 in the outer circumferential direction. For example, by engaging one end of a helical spring wound around the pin 106 with the wedge 105 and the other end with the cage 100, the elastic force of the helical spring is applied to the wedge 105 in the outer circumferential direction. You can A leaf spring may be used, or a hydraulic mechanism or the like may be used.

  An end surface 105A (hereinafter referred to as a rear end surface) of the wedge 105 opposite to the side supported by the pin 106 is inclined so as to face the wall surface 101B. Further, it is desirable that the outer peripheral surface of the wedge 105 has a shape that increases the contact area with the inner peripheral surface of the output member 102 when sandwiched between the input member 101 and the output member 102.

  Next, a mechanism for switching between the engaged state and the released state of the one-way clutch of this embodiment will be described.

  When the clockwise torque is input to the input member 101 and rotates, and the wall surface 101B contacts the rear end surface 105A of the wedge 105, the wall surface 101B and the rear end surface 105A of the wedge 105 are inclined so as to face each other. As shown in FIG. 11A, the wedge 105 is pressed toward the inner peripheral side. As a result, the wedge 105 and the output member 102 are not in contact with each other, and a released state is established.

  When the input direction of the torque to the input member 101 is switched to the counterclockwise direction, the rotation speed of the input member 101 decreases, whereas the cage 100 continues to rotate as it is due to the inertial force. As a result, the wedge 105 is sandwiched between the input member 101 and the output member 102. Further, when the rear end surface 105A of the wedge 105 is separated from the wall surface 101B, the wedge 105 is pressed in the outer peripheral direction with the pin 106 as an axis, and the outer peripheral surface of the wedge 105 and the inner peripheral surface of the output member 102 come into contact with each other. Thereby, it will be in a fastening state.

  In addition, a friction material may be affixed to the mutual contact surface of the wedge 105 and the output member 102, or the process which raises a friction coefficient may be given. By increasing the friction coefficient of the contact surface, it is possible to ensure the fastening force even if the contact area is reduced, and thus the one-way clutch can be reduced in size while securing the fastening capacity.

  As described above, also in the present embodiment, as in the first embodiment, the release state and the fastening state are quickly switched according to the switching of the torque input direction. Further, the one-way clutch can be reduced in size by attaching a friction material or the like.

  The present invention is not limited to the above-described embodiments, and it goes without saying that various modifications can be made within the scope of the technical idea described in the claims.

DESCRIPTION OF SYMBOLS 1 Drive source 2 Load 3 Case 4 Yoke 5 Yoke shaft 6 Link 7 Weight 9 Eccentric shaft 10 Torque transmission shaft 11 1st one-way clutch 12 2nd one-way clutch 16 Bearing 19 Pin 30 Output shaft 31 Fixed shaft 100 Cage 101 Input member 102 Output member 103 Ball (lock member)
104 Wedge (locking member)
105 Wedge (locking member)
106 pins

Claims (5)

A lock member is disposed between the input member and the output member, and when the lock member is displaced to one side in the circumferential direction with respect to the input member, the lock member is sandwiched between the input member and the output member and fastened. In the one-way clutch that becomes a state,
The lock member can be relatively rotated and displaced with respect to the input member and the output member, and when the direction of torque input to the input member changes from one to the other, the relative rotation is displaced with respect to the input member. A one-way clutch comprising a cage that is displaced toward one side in a circumferential direction with respect to the input member.   The one-way clutch according to claim 1, wherein the lock member is a rolling element that rotates to absorb a rotation difference between the input member and the output member.   The one-way clutch according to claim 1, wherein the lock member is a wedge-shaped member.   The one-way clutch according to any one of claims 1 to 3, wherein a friction material is provided on a contact surface between the lock member and the output member, or a process of increasing a friction coefficient is performed.   When the torque input direction to the input member is one, the cage rotates integrally with the input member, and when the torque input direction to the input member changes from one to the other, the lock member is caused by inertial force. The one-way clutch according to claim 1, wherein the one-way clutch is displaced toward one side in a circumferential direction with respect to the input member.

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