JP4536354B2 - Rotation actuated one-way clutch - Google Patents

Description

  The present invention relates to a rotationally actuated one-way clutch that is used in motorcycles, snowmobiles, and the like, and that exhibits a function of a one-way clutch only when a predetermined rotational speed is exceeded.

  Generally, a one-way clutch has an outer ring and an inner ring that rotate relative to each other, and sprags and rollers that transmit torque between the outer ring and the inner ring mesh with a cam surface provided on a raceway surface of the outer ring or the inner ring, thereby Only the rotational torque is transmitted. In addition, it is configured to idle in the reverse direction.

  In such a one-way clutch, a roller is disposed in a pocket (recess) provided in the inner ring or outer ring, and the rotation is locked by a wedge action in which the roller engages a wedge portion of the pocket depending on the rotation direction. What is known.

  For example, in Patent Document 1, when a roller is disposed in a recess provided in an outer ring (outer race) and the outer ring rotates clockwise, the roller is locked in the recess by a wedge action, and the outer ring is A configuration for locking the rotation is disclosed.

  In Patent Document 2, a roller and an auxiliary roller are arranged between an outer ring (outer race) and an input coupling, and when the rotation speed exceeds a predetermined value, the auxiliary roller can engage the roller with the cam surface by centrifugal force. Press to the correct position. A structure is disclosed in which the roller and the outer inner ring can be locked by this pressing force, and when the outer inner ring attempts to rotate relative to each other in the meshing direction, the wedge action is activated and the rotation is locked.

Prior art document information related to the invention of this application includes the following.
Japanese Examined Patent Publication No. 53-8019 (page 1-2, Fig. 1 etc.) Japanese Patent Laid-Open No. 52-100045 (page 2-3, FIG. 3, etc.)

The above-described prior art discloses a configuration in which a roller is locked in a recess or the like. In particular, Patent Document 2 states that an auxiliary roller presses the roller by centrifugal force, and the roller and the outer inner ring can be locked by this pressing force. Thus, when the outer and inner rings try to rotate relative to each other in the meshing direction, the wedge action is activated and the rotation is locked.
However, since there is no specific relationship between the size of the auxiliary roller or roller and the space in which they are accommodated, the movement of the auxiliary roller or roller, that is, the operation may not be smooth.

  Accordingly, an object of the present invention is to provide a rotary operation type one-way clutch in which the operation of the weight body and the rolling element is made smooth.

In order to achieve the above object, the rotationally actuated one-way clutch of the present invention comprises:
An outer ring having an inner peripheral cylindrical surface, an inner ring formed with a cam surface, a rolling element that transmits torque between the outer and inner rings, a biasing spring that biases the rolling element, and a biasing force that receives centrifugal force In a rotary operation type one-way clutch comprising a weight body that presses the rolling element in an engagement direction against a biasing force of a spring, and a weight operation surface that guides the operation of the weight body, the weight body includes the weight It is characterized by being larger than the space surrounded by the weight body, rolling element, and weight operation surface.

In order to achieve the above object, the rotationally operated one-way clutch of the present invention is
An outer ring having an inner peripheral cylindrical surface, an inner ring formed with a cam surface, a rolling element that transmits torque between the outer and inner rings, a biasing spring that biases the rolling element, and a biasing force that receives centrifugal force In the rotary operation type one-way clutch, comprising: a weight body that presses the rolling element in an engaging direction while resisting a biasing force of a spring; and a weight operation surface that guides the operation of the weight body, the rolling element and the weight body Is always located on the inner diameter side as the center reference of the inner ring or the outer ring from the center of the rolling element.

According to the present invention, the following effects can be obtained.
Since the weight body is larger than the space surrounded by the weight body, the rolling element, and the weight operation surface, malfunction caused by the biting body and the rolling element biting is prevented, and the weight body and the rolling element Smooth operation. (Claims 1 and 2)

  The size of the weight body is configured to be larger than a space surrounded by the weight body, the rolling element, and the weight operation surface. The rolling element and the weight body are configured to be held so that the contact point between the rolling element and the weight body is always on the inner diameter side of the center of the rolling element.

  In this specification, “rotation operation type” means that the function as a one-way clutch operates reliably during rotation in a range exceeding the predetermined rotation speed. Even if the rotation is less than the number of rotations, it may function as a one-way clutch.

  Further, in this specification, the “weight operating surface” is a surface that is guided by rolling or sliding a weight body that has received centrifugal force to the outer diameter side along this surface, and is in contact with the roller. The roller is provided to move the roller to the meshing position. The “weight operation surface” is preferably inclined so that the circumferential width of the pocket gradually decreases in the outer diameter direction.

    Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. In the drawings, the same parts are denoted by the same reference numerals.

(First embodiment)
FIG. 1 is a front view of a rotary actuated one-way clutch showing a first embodiment of the present invention, and FIG. 2 is an axial sectional view taken along line AA in FIG. The rotationally actuated one-way clutch 1 has an inner ring 2 that is a hollow shaft fitted with a drive shaft (not shown) with a spline 2a formed on the inner periphery, coaxially on the outer side in the radial direction of the inner ring 2, and the inner ring 2 and an outer ring 3 arranged to be relatively rotatable. For convenience of explanation, hereinafter, the “rotation actuated one-way clutch” will be simply referred to as “one-way clutch”.

  As shown in detail in FIG. 3, a plurality of pockets 9 opened to the inner peripheral surface 3 a of the outer ring 3 are equally provided in the circumferential direction on the outer peripheral portion of the inner ring 2. The outer peripheral surface of the inner ring 2 between the pockets 9 is a bearing portion 13 that rubs against the inner peripheral surface 3 a of the outer ring 3.

  Each pocket 9 is formed with a cam surface 11 (see FIGS. 3 and 4) on a part of its inner peripheral surface, and a substantially cylindrical roller 7 and a substantially cylindrical weight 8 are arranged. Further, the roller 7 is not engaged with the pocket 9 in the direction in which the cam surface 11 is deeper, that is, between the cam surface 11 and the cylindrical inner peripheral surface of the outer ring 3, and the one-way clutch 1 is idled. A biasing spring 5 for biasing in the non-engaging direction is provided.

  An accordion spring is used as the urging spring 5, and as shown in detail in FIG. 5, the urging spring 5 is sandwiched between the return portion 14 of the retainer column 10 by the attachment portion 15 of the urging spring 5. Is attached to the cage pillar 10 of the cage 4. One end of the biasing spring 5 on the side opposite to the attachment portion 15 is a pressing portion 16 for pressing the roller 7.

  FIG. 2 is an axial sectional view showing the relationship between the inner ring 2, the outer ring 3, the cage 4, and the biasing spring 5, and shows that the biasing spring 5 is held by the cage 4. The inner ring 2 is fitted to a drive shaft (not shown) and is rotatable.

  Next, the operation of the one-way clutch 1 of the first embodiment will be described with reference to FIGS. 3 is a front view showing the main part of FIG. 1, showing a state before the rollers are engaged (when not engaged), and FIG. 4 is a front view showing the main part of FIG. The state at the time of meshing (at the time of engagement) is shown.

  In the one-way clutch 1 having the above-described configuration, the roller 7 does not transmit torque in any direction of the relative rotation direction of the inner and outer rings from the non-rotating period to the low-speed rotating range. FIG. 3 shows this state, and a slight gap d 1 exists between the inner peripheral surface 3 a of the outer ring 3 and the roller 7. Moreover, even if a slight misalignment occurs between the outer ring and the outer ring due to vibrations such as engine rotation, it is possible to prevent a malfunction that the roller is dragged by the inner ring surface of the outer ring and bites into the cam surface. The operation of the weight body and the rolling element becomes smooth. Also, drag torque during idling can be reduced. Further, the weight body 8 is located almost at the innermost part of the pocket 9.

  When the rotational speed rises from the non-engaged state of FIG. 3, the weight 8 receives centrifugal force and is formed on the side of the pocket 9 so that the circumferential width of the pocket gradually decreases toward the outer diameter direction. The roller 7 moves to the outer diameter side along the inclined circumferential end surface, that is, the weight actuating surface 12, and in addition to the centrifugal force received by the roller 7 itself, the centrifugal force (Fc) received by the weight 8 is applied to the roller 7. A force (Fw) is applied that pushes the roller 7 in the engagement direction to the position where it can engage with the cam surface 11 and presses it in the circumferential direction to the meshing position. FIG. 4 shows such an engaged state, in which the roller 7 is engaged between the inner peripheral surface 3 a of the outer ring 3 and the cam surface 11.

  Further, when the rotational speed exceeds a predetermined value, a sufficient pressing force is applied to the roller 7, and a state where the function of the one-way clutch 1 can be exhibited, that is, a state where lock-up is possible. That is, in this state, when the inner ring 2 is considered to be fixed in FIG. 4, when the outer ring 3 rotates in the left direction in the figure, it is in an idle state (non-engagement state), and when it rotates in the right direction in the figure, it is engaged. Torque (engaged state), and torque is transmitted between the inner and outer rings.

  By the way, in order to prevent the weight 8 from being caught between the roller 7 and the weight operating surface 12, a predetermined inclination angle is set on the weight operating surface 12. This inclination angle is an angle formed between the tangent line at the contact point between the weight body 8 and the roller 7 and the weight body working surface 12, and the set angle varies depending on the ratio of the diameters of the weight body 8 and the roller 7. A non-wedge action surface 21 that is inclined more greatly than the cam surface 11 is formed on the outer diameter side of the cam surface 11 and on the opposite side of the weight body 8.

  In FIG. 4, a circle C <b> 1 passing through the center of the roller 7 is positioned on the outer diameter side of a circle C <b> 2 passing through the contact point between the roller 7 and the weight body 8. Furthermore, a weight operating surface 12 is provided on one of the radially extending surfaces constituting the pocket 9. A space 20 (FIG. 3) formed by the roller 7 that is a rolling element, the weight body 8, and the weight operation surface 12 is formed smaller than the weight body 8. That is, the contact point between the roller 7 and the weight body 8 is always located on the inner diameter side as the center reference of the inner ring 2 or the outer ring 3 from the center of the roller 7.

  In addition, as shown in FIG. 3, the roller 7 is held on the inner peripheral side from the outer peripheral edge of the pocket 9 when not rotating. Further, as shown in FIG. 4, the contact point between the roller 7 and the weight body 8 is located on the inner diameter side from the center of the roller 7.

(Second embodiment)
Next, a second embodiment of the present invention will be described. FIG. 6 is a front view of the one-way clutch 30 showing the second embodiment, and FIG. 7 is a schematic view of the pocket portion viewed from the outer diameter side of the second embodiment.

  In the first embodiment, a pocket for accommodating a roller, a weight body, an accordion spring and the like constituting the one-way clutch portion is formed in the inner ring, but in the second embodiment, most of these elements are stored in the cage 32. It accommodates in the provided window part 43 (refer FIG.7 and FIG.9).

  The substantially annular retainer 32 disposed between the outer ring 3 and the inner ring 2 is a retainer body, and a substantially annular support plate 34 is provided on an end surface in the axial direction of the retainer 32. The support plate 34 is fixed to the cage 32 by the cage coupling portion 33.

  An accordion spring 35 that urges the roller 37 from the outer ring 3 side, a roller 37 that transmits torque between the outer ring 3 and the inner ring 2, and a roller 37 A weight 38 that acts on the roller 37 to press the roller 37 in the meshing direction is disposed. When the weight body 38 is not acting, a part of the weight body 38 is fitted in the recess 31 provided on the outer peripheral surface of the inner ring 2.

  The retainer 32 is provided with a concave portion 36 having a substantially U-shaped radial cross section, and the end of the accordion spring 35 opposite to the end that applies a biasing force to the roller 37 is fitted in the concave portion 36 (see FIG. 9). Are held together.

  As can be seen from FIG. 7, the window portion 43 of the cage 32 is formed through the cage 32 in the radial direction, leaving a wall portion on the axial side portion. The open end in the axial direction of the window portion 43 is closed by the support plate 34 described above. Accordingly, the accordion spring 35, the roller 37, and the weight body 38 accommodated in the window 43 are held in the axial direction by the wall of the cage 32 and the support plate 34, and are held in the radial direction by the outer ring 3 and the inner ring 2. And does not deviate from the window 43.

  FIG. 8 is an axial sectional view of the one-way clutch 30. It can be seen that the support plate 34 is fixed to the cage 32 by the cage coupling portion 33. It can also be seen that the roller 37 has a small clearance between the wall of the cage 32 and the support plate 34 and is supported in the axial direction.

  Next, the operation of the one-way clutch 30 of the second embodiment will be described with reference to FIGS. FIG. 9 is a diagram illustrating the state of the roller and the weight body during non-rotation to low-speed rotation in the second embodiment, and FIG. 10 illustrates that the roller is located inside the outer peripheral edge of the pocket during non-rotation in the second embodiment. FIG. 11 is a view showing a state where the roller and the weight body are at a predetermined rotation speed or more at which the one-way clutch function of the second embodiment is exhibited.

  Here, the configuration of the second embodiment will be described in more detail with reference to FIG. The cage 32 includes a plurality of convex portions 44 that fit into a plurality of concave grooves 45 provided on the outer circumferential surface of the inner ring 2 equally in the circumferential direction. Since the convex portion 44 is fitted in the concave groove 45, the cage 32 and the inner ring 2 are configured not to rotate relative to each other.

  A weight operating surface 40 is formed on one side surface of the window portion 43 of the cage 32, and when the weight body 38 receives centrifugal force, the weight body 38 moves to the outer diameter side along this surface and is pressed against the roller 37. The roller 37 is moved to the meshing position. A weight locking portion 41 that restricts the operating range of the weight body 38 is provided on the outer diameter side of the weight operating surface 40 so that the weight body 38 cannot move further to the outer diameter side. Further, on the outer diameter side, a roller locking portion 42 (rolling body locking portion) for limiting the operating range of the roller 37 in the direction of the weight body 38 is provided. The weight operating surface 40, the weight locking portion 41, and the roller locking portion 42 are continuously provided in the embodiment, but are not necessarily formed continuously.

  A concave portion 31 into which a part of the weight body 38 is fitted is formed on the outer peripheral surface of the inner ring 2 facing the portion provided with the weight operating surface 40, the weight locking portion 41, and the roller locking portion 42 of the cage 32. A cam surface 47 that is a torque transmission surface of the roller 37 is formed adjacent to the recess 31, and is further on the outer diameter side of the cam surface 47, on the opposite side of the cam surface 47 from the recess 31. A non-wedge action surface 46 that is inclined more greatly than the cam surface is formed. The recess 31, the cam surface 47, and the non-wedge acting surface 46 are continuously provided in the embodiment, but are not necessarily formed continuously.

  The recess 31 can accommodate a part of the weight body 38, but the reason why only the part is accommodated is to make the operating range of the weight body 38 as small as possible.

  As shown in FIG. 9, during non-rotation to low-speed rotation (range), the weight body 38 is positioned on the inner diameter side of the recess 31 and is in contact with the roller 37, and the roller 37 is pushed against the roller locking portion 42 by the accordion spring 35. It is in a hit state. Thereafter, when the inner ring 2 rotates and the rotation starts at a high speed equal to or higher than a predetermined number of rotations, the weight body 38 receiving the centrifugal force moves to the outer diameter side as shown in FIG. The cam surface 47 is moved to the meshing position. In this state, when the inner ring 2 rotates in the counterclockwise direction in the figure with respect to the outer ring 3, torque is transmitted. The state at the time of this operation is shown in FIG.

  Furthermore, when the roller 37 receives excessive torque, the roller 37 moves to the non-wedge acting surface 46 so that the torque can be released. That is, the contact point between the roller 37 and the weight body 38 is always located on the inner diameter side from the center of the roller 37 as the center reference of the inner ring 2 or the outer ring 3.

  As shown in FIG. 10, the roller 37 is held on the inner peripheral side from the outer peripheral edge of the pocket 39 when not rotating. That is, a gap d <b> 2 is formed between the outer peripheral edge 39 of the cage 44 and the roller 37. Moreover, even if a slight misalignment occurs between the outer ring and the outer ring due to vibrations such as engine rotation, it is possible to prevent a malfunction that the roller is dragged by the inner ring surface of the outer ring and bites into the cam surface. The operation of the weight body and the rolling element becomes smooth. Also, drag torque during idling can be reduced. Further, the weight body 8 is located almost at the innermost part of the pocket 9.

As shown in FIG. 9, a window 43 is formed in the cage 44, and a pocket is constituted by the outer peripheral surface of the inner ring and the window portion 43. The weight operation surface 40 is provided on one of the surfaces of the window 43 that extend in the radial direction. The space 20 formed by the roller 37, the weight body 38, and the weight operation surface 40 is formed smaller than the weight body. Further, as shown in FIG. 11, the contact point between the roller 37 and the weight body 38 is located on the inner diameter side from the center of the roller 37. That is, the circle C1 passing through the center of the roller 37 is located on the outer diameter side of the circle C2 passing through the contact point between the roller 37 and the weight body 38.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIGS. In the third embodiment, the positional relationship and operation of the weight body 38, the roller 37, and the accordion spring 35 are substantially the same as those of the second embodiment described above. In the third embodiment, the form of the cage is greatly different from those of the first and second embodiments.

  As shown in detail in FIGS. 12, 13, and 17, the cage 50 used in the present embodiment includes a first plate 60 and a second plate 70, and is made by punching a plate-shaped steel plate. The holder 50 is formed by joining two plates. The roller 37, the weight body 38, etc. are accommodated between both plates.

  Next, details of the one-way clutch 80 of the third embodiment will be described with reference to FIGS. FIG. 12 is a front view of the one-way clutch 80 showing the third embodiment, and FIG. 13 is an axial sectional view of the one-way clutch 80 showing the third embodiment. FIG. 14 is a view showing the state of the roller and the weight body during non-rotation to low-speed rotation in the third embodiment, and FIG. 15 is a predetermined rotation speed at which the one-way clutch function of the third embodiment is exhibited. FIG. 16 is a view showing the state of the roller and the weight body as described above, and FIG. 16 is a view showing a state where the roller is held on the inner peripheral side from the outer peripheral edge of the pocket when not rotating in the third embodiment. is there.

  In FIG. 12, the cam surface 47 and the non-wedge acting surface 46 (FIGS. 14-16) provided on the outer peripheral surface of the inner ring 2 are substantially the same as those in the first and second embodiments described above. The difference between the third embodiment and the first and second embodiments is that the working surface of the weight body 38 is formed on a convex portion provided on the first or second plate constituting the cage 50. Is a point.

  The retainer 50 is formed by the coupling portion 53 by fitting the claws 71 for caulking of the second plate 70 into the caulking holes 64 of the first plate 60 and caulking. The convex portion of the second plate 70 is bent and fitted to the inner periphery of the outer ring 3 to form a weight operating surface 52 having a predetermined inclination with respect to the radial direction.

  FIG. 13 is a cross-sectional view in the axial direction of FIG. 12, and it can be seen that the retainer 50 is composed of a first plate 60 and a second plate 70 located on both sides in the axial direction.

  Next, the operation of the rotary operation type one-way clutch 80 of the third embodiment will be described with reference to FIGS. The basic operation is the same as in the first and second embodiments. As shown in FIG. 14, during non-rotation to low-speed rotation (range), the weight body 38 is positioned on the inner diameter side of the recess 31 and is in contact with the roller 37, and the roller 37 is pressed in the non-engagement direction by the accordion spring 35. Has been.

  Thereafter, when the inner ring 2 rotates and the rotation starts at a high speed equal to or higher than a predetermined number of rotations, the weight body 38 that has received the centrifugal force moves toward the outer diameter side along the weight operation surface 52 as shown in FIG. It moves so that the roller 37 is moved to the meshing position of the cam surface 47, and when the inner ring 2 rotates in the counterclockwise direction in the drawing with respect to the outer ring 3, torque is transmitted.

  Furthermore, when the roller 37 receives excessive torque, the roller 37 moves to the non-wedge acting surface 46 so that the torque can be released.

  Here, the relationship between the cage 50 and the accordion spring 35 is as follows. FIG. 17 is a schematic view of the pocket portion viewed from the outer diameter side of the third embodiment. FIG. 18 is a front view of an accordion spring mounting portion in the third embodiment.

  As shown in FIGS. 17 and 18, the accordion spring 35 has a joining portion 58 that presses the roller 37 at the tip portion, and a mounting portion 57 at the root portion. The accordion spring 35 is fixed to the cage 50 by sandwiching the first column portion 51 by the attachment portion 57. Further, by engaging the tongue piece 56 formed by cutting out the attachment portion with the hole 62, the accordion spring 35 is more firmly fixed and can be prevented from falling off.

  A tongue piece 56 at the tip of the attachment portion 57 is fitted in the hole 62 of the first plate 60 of the cage. According to the third embodiment, the inner ring 2 is made of steel, whereas the cage 50 can be made of synthetic resin, aluminum, copper, or the like, so that the one-way clutch can be reduced in weight. In addition, the processing cost can be reduced.

  As shown in FIG. 16, when not rotating, the roller 37 is held on the inner peripheral side from the outer peripheral edge of the pocket. That is, a gap d <b> 3 is formed between the outer peripheral edge 59 of the cage 50 and the roller 37. Moreover, even if a slight misalignment occurs between the outer ring and the outer ring due to vibrations such as engine rotation, it is possible to prevent a malfunction that the roller is dragged by the inner ring surface of the outer ring and bites into the cam surface. The operation of the weight body and the rolling element becomes smooth. Also, drag torque during idling can be reduced. Further, the weight body 8 is located almost at the innermost part of the pocket 9. The space 20 formed by the roller 37, the weight body 38, and the weight operation surface 52 is formed smaller than the weight body 38. Further, when not rotating, the roller 37 is held on the inner peripheral side from the outer peripheral edge of the pocket. Further, the contact point between the roller 37 and the weight body 38 is located on the inner diameter side from the center of the roller 37. That is, the circle C1 passing through the center of the roller 37 is located on the outer diameter side of the circle C2 passing through the contact point between the roller 37 and the weight body 38.

  The weight may be formed from a material such as steel, copper, steel alloy, aluminum, or synthetic resin. However, if a material with a large specific gravity such as steel is used, the centrifugal force received per unit volume increases. Thus, it is possible to obtain a state in which the size of the device is small and can be engaged even at low speed rotation, and the diameter of the weight body 8 can be reduced.

  In each of the embodiments described above, a cylindrical roller as a rolling element disposed in a pocket is shown, but this may be a sphere. Also, the weight may be a sphere instead of a cylindrical roller. Further, regarding the combination of the rolling element and the weight, both may be rollers, both may be spheres, one of them may be a roller, and the other may be a sphere.

  Moreover, in each Example, although the pocket is provided in multiple places in the circumferential direction, this number can be arbitrarily changed according to a required torque capacity etc., and may be other than eight places, for example, four places or six places. But it ’s okay. However, it is preferable to provide the pockets with equal distribution in the circumferential direction regardless of the number.

  The present invention can also be used for vehicles other than motorcycles and snowmobiles, that is, four-wheeled vehicles.

1 is a front view of a rotary actuated one-way clutch showing a first embodiment of the present invention. It is an axial sectional view along the AA line of FIG. FIG. 2 is a front view showing a main part of FIG. 1, showing a state before the rollers are engaged (when not engaged). FIG. 2 is a front view showing a main part of FIG. 1, showing a state when the rollers are engaged (engaged). It is a figure which shows the detail of the accordion spring used for this invention. It is a front view of the rotation actuated one-way clutch showing a second embodiment of the present invention. It is the schematic of the pocket part seen from the outer diameter side of 2nd Example of this invention. It is an axial sectional view of a rotary actuated one-way clutch showing a second embodiment of the present invention. It is the figure which showed the state of the roller and weight body at the time of non-rotation-low speed rotation in 2nd Example of this invention. In 2nd Example, it is a figure which shows the state by which the roller is hold | maintained from the outer periphery of the pocket to the inner peripheral side at the time of non-rotation. It is the figure which showed the state of the roller and weight which are rotating more than the predetermined rotation speed of 2nd Example of this invention. It is a front view of the rotation actuated one-way clutch showing a third embodiment of the present invention. It is an axial sectional view of a rotary actuated one-way clutch showing a third embodiment of the present invention. It is the figure which showed the state of the roller and weight body at the time of non-rotation-low speed rotation in 3rd Example of this invention. It is the figure which showed the state of the roller and weight which are rotating more than the predetermined rotation speed of 3rd Example of this invention. In 3rd Example, it is a figure which shows the state by which the roller is hold | maintained from the outer periphery of the pocket to the inner peripheral side at the time of non-rotation. It is the schematic of the pocket part seen from the outer diameter side of 3rd Example of this invention. It is a front view of the accordion spring attachment part in 3rd Example of this invention.

Explanation of symbols

1, 30, 80 Rotation actuated one-way clutch 2 Inner ring 3 Outer ring 5, 35 Accordion spring 7, 37 Rolling element (roller)
8,38 Weight 9 Pocket 11,47 Cam surface

Claims (1)

An outer ring having an inner peripheral cylindrical surface, an inner ring formed with a cam surface, a rolling element that transmits torque between the outer and inner rings, a biasing spring that biases the rolling element, and a biasing force that receives centrifugal force In the rotary operation type one-way clutch provided with a weight body that presses the rolling element in the engaging direction while resisting the urging force of the spring, and a weight operation surface that guides the operation of the weight body,
A rotationally actuated one-way clutch characterized in that the contact point between the rolling element and the weight body is always located on the inner diameter side from the center of the rolling element from the non-engaged state to the engaged state of the rolling element .

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