WO2004072504A1

WO2004072504A1 - Rotation activated one-way clutch

Info

Publication number: WO2004072504A1
Application number: PCT/JP2004/001418
Authority: WO
Inventors: Kazuhiko Muramatsu; Masanori Tateishi; Nobuhiro Horiuchi
Original assignee: Nsk-Warner K.K.
Priority date: 2003-02-13
Filing date: 2004-02-10
Publication date: 2004-08-26

Abstract

A rotation activated one-way clutch has an outer ring with a circular cylindrical peripheral surface, an inner ring with cam faces, rolling bodies for transmitting torque between the outer and inner rings, urging springs for urging the rolling bodies, and weight bodies for pressing the rolling bodies, upon receiving centrifugal force, to an engagement direction against urging force of the urging springs. Weight operation faces for guiding the operation of the weight bodies are provided in the one-way clutch.

Description

Description Rotary-acting one-way clutch Technical field

The present invention relates to a rotation-actuated one-way clutch that is used for motorcycles, snowmobiles, and the like, and that functions as a one-way clutch when the number of rotations exceeds a predetermined value. , Background technology

In general, a one-way clutch has an outer ring and an inner ring that rotate relative to each other, and a sprag or roller that transmits torque between the outer ring and the inner ring engages with a cam surface provided on the raceway surface of the outer ring or the inner ring. , Transmitting rotation torque in only one direction. In the opposite direction, the vehicle is idle.

In such a one-way clutch, a roller is arranged in a pocket (recess) provided in the inner ring or the outer ring, and is rotated by a wedge action in which the roller is engaged with a wedge portion of the bucket according to the rotation direction. There is a known configuration that locks the lock. '

For example, Japanese Patent Publication No. Sho 53-81019 discloses that a roller is disposed in a recess provided in an outer race (outer race), and when the outer race rotates clockwise, the roller is locked in the recess by the action of a wedge. A configuration for locking the rotation of the outer ring with respect to the inner ring is disclosed.

Japanese Patent Application Laid-Open No. 52-100045 discloses that 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 number, the centrifugal force is increased. The auxiliary roller presses the roller. This pressing force allows the roller to be licked by a wedge action when rotated in a predetermined direction, and discloses a configuration in which the function of a one-way clutch is exhibited. The one disclosed in Japanese Patent Publication No. 53-81919 is a general one-way clutch using rollers, and is not configured to lock according to the number of rotations. .

Japanese Patent Application Laid-Open No. 52-100045 discloses a configuration in which locking is performed according to the number of rotations. However, since parts such as plates and holding pieces for pressing the mouthpiece are required, the number of parts is large, and the installation space for springs is required.

Furthermore, although a coil spring is provided for the spring that urges the roller, it is difficult to set a small spring constant in a limited space with a coil spring, and it is more cost-effective than an accordion spring or the like. May also be expensive. Disclosure of the invention

Therefore, an object of the present invention is to provide a rotary-operated one-way clutch having a structure capable of reducing the number of parts, being inexpensive, setting a small spring constant, and designing even in a space-saving manner.

Still another object of the present invention is to provide a rotary operation type one-way clutch in which the weight and the rolling element are smoothly operated.

It is another object of the present invention to reduce the drag torque without increasing the size of the rotation-operating one-way clutch.

In order to achieve the above object, a rotation-operating one-way clutch according to the present invention includes: an outer ring having an inner peripheral cylindrical surface; an inner ring having a cam surface; a rolling element that transmits torque between the outer and inner rings; An urging spring for urging the rolling element in the engaging direction while resisting the urging force of the urging spring under centrifugal force. A rotary operation type one-way clutch having a weight to press, characterized in that a weight operating surface for guiding the operation of the weight is provided.

In addition, the rotation operation type one-way clutch of the present invention

An outer ring having an inner peripheral cylindrical surface; an inner ring having a cam surface formed thereon; a rolling element for transmitting torque between the outer and inner rings; an urging spring for urging the rolling element; In a rotary operation type one-way clutch including a weight that presses the rolling element in an engagement direction while resisting the urging force of a spring, the urging spring is an accordion spring.

Furthermore, the rotation-operating one-way clutch of the present invention

An outer ring having an inner peripheral cylindrical surface; an inner ring having a cam surface formed thereon; a rolling element for transmitting torque between the outer and inner rings; an urging spring for urging the rolling element; In a rotary operation type one-way clutch including a weight that presses the rolling element in an engagement direction while resisting the urging force of a spring, a non-wedge action surface that is continuous at a shallow portion of the cam surface is formed. Features. In addition, the rotation operation type one-way clutch of the present invention

An outer ring having an inner peripheral cylindrical surface; an inner ring having a cam surface formed thereon; a rolling element for transmitting torque between the outer and inner rings; an urging spring for urging the rolling element; A rotary-acting one-way clutch including a weight that presses the rolling element in the engaging direction while piled on the urging force of a spring, wherein a retainer that holds the urging spring is provided. .

Furthermore, the rotation-operating one-way clutch of the present invention

An outer ring having an inner peripheral cylindrical surface; an inner ring having a cam surface formed thereon; a rolling element for transmitting torque between the outer and inner rings; an urging spring for urging the rolling element; In a rotary actuated one-way clutch including a weight that presses the rolling element in the engaging direction while resisting the urging force of a spring, a bearing mechanism that supports between the outer ring and the inner ring is provided. And Furthermore, the rotation-operating one-way clutch of the present invention

An outer ring having an inner peripheral cylindrical surface; an inner ring having a cam surface formed thereon; a rolling element for transmitting torque between the outer and inner rings; an urging spring for urging the rolling element; In a rotary operation type one-way clutch including a weight that presses the rolling element in an engagement direction while resisting the urging force of a spring, a locking portion that limits an operation range of the weight is provided. And

An outer ring having an inner peripheral cylindrical surface; an inner ring having a cam surface formed thereon; a rolling element for transmitting torque between the outer and inner rings; an urging spring for urging the rolling element; In a rotation type one-way clutch including a weight that presses the rolling element in an engaging direction while resisting the urging force of a spring, a retainer that holds at least one of the rolling element, the weight, and the urging spring The bearing is provided with a bearing portion for supporting between the outer and inner races.

An outer ring having an inner peripheral cylindrical surface; an inner ring having a cam surface formed thereon; a rolling element for transmitting torque between the outer and inner rings; an urging spring for urging the rolling element; In a rotation type one-way clutch including a weight that presses the rolling element in an engaging direction while resisting the urging force of a spring, a retainer that holds at least one of the rolling element, the weight, and the urging spring And a detent mechanism for preventing relative rotation between the retainer and the inner ring is provided.

An outer ring having an inner peripheral cylindrical surface; an inner ring having a cam surface formed thereon; a rolling element for transmitting torque between the outer and inner rings; a biasing spring for biasing the rolling element; The rolling element in the engaging direction while staking against the biasing force of the biasing spring A rotation-operating one-way clutch having a weight to be pressed, characterized in that a resin-made retainer for holding at least one of the rolling element, the weight, and the biasing spring is provided.

An outer ring having a cylindrical surface on the inner periphery and an inner ring having a cam surface formed on the outer periphery are coaxially arranged, and a rolling element for transmitting torque between the outer and inner rings; and an engagement direction of the rolling element by receiving centrifugal force. And a biasing spring for biasing the rolling element in a non-engagement direction, and a weight operating surface for guiding the operation of the weight body. In the clutch, the retainer or one of the members constituting the retainer is provided with a pillar that forms the weight operating surface, and a tip of the pillar is provided for caulking with a mating member. It is characterized by having a claw provided.

An outer ring having an inner peripheral cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, an urging spring for urging the rolling element; A weight that presses the te moving body in the engaging direction while resisting the urging force of the urging spring; and a rotary operation type one-way clutch including a weight operating surface that determines an operation direction of the weight. The feature is that the outer diameter side portion of the surface is more greatly inclined with respect to the radial direction than the inner diameter side portion.

An outer ring having an inner peripheral cylindrical surface; an inner ring having a cam surface; a rolling element for transmitting torque between the outer and inner rings; an urging spring for urging the rolling element; A weight that presses the rolling element in the engaging direction while resisting the urging force of the urging spring; and a weight operating surface that accommodates the rolling element, the weight, and the urging spring and determines the operating direction of the weight. In the rotary actuation type one-way clutch provided with a retainer, when the weight body is not operated, the rolling element moves around the outer periphery of the retainer. It is characterized in that it is held on the inner diameter side of the edge portion.

An outer ring having an inner peripheral cylindrical surface; an inner ring having a cam surface formed thereon; a rolling element for transmitting torque between the outer and inner rings; an urging spring for urging the rolling element; In a rotation type one-way clutch including a weight that presses the rolling element in an engaging direction while being piled by an urging force of a spring, the urging spring directly urges the rolling element. I have.

In the present specification, the term "rotationally actuated" means that the one-way clutch function reliably operates when rotating in a range exceeding the above-mentioned predetermined number of rotations. It may function as a one-way clutch even with rotations less than the rotation speed of. The “predetermined number of rotations” is arbitrarily determined by the weight of the weight, the distance of the weight from the center of the inner ring, and the inclination angle of the weight working surface.

In addition, in this specification, the “weight operating surface” is a surface on which a weight body that has been subjected to centrifugal force is guided by rolling or sliding along the surface toward the outer diameter side. However, it is provided to move the rollers to the mating position. It is preferable that the “weight operating surface” be slanted so that the circumferential width of the pocket gradually decreases in the outer diameter direction. BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a front view of a rotary actuated one-way clutch showing a first embodiment of the present invention.

FIG. 2 is an axial cross-sectional view taken along the line FIG. 2—FIG. 2 of FIG.

FIG. 3 is a front view showing a main part of FIG. 1, showing a state before the rollers are engaged (when they are not engaged).

FIG. 4 is a schematic diagram showing the position of the roller when not operating in the first embodiment of the present invention. FIG.

FIG. 5 is a front view showing a main part of FIG. 1, and shows a state where the rollers are engaged (engaged).

FIG. 6 is a diagram showing details of the accordion spring used in the first embodiment of the present invention.

FIG. 7 is a front view of a rotation actuated one-way clutch showing a second embodiment of the present invention.

FIG. 8 is a schematic view of a pocket portion of the second embodiment of the present invention as viewed from the outer diameter side. FIG. 9 is an axial cross-sectional view of a rotary actuated one-way clutch showing a second embodiment of the present invention.

FIG. 10 is a diagram showing the state of the rollers and the weight during non-rotation to low-speed rotation in the second embodiment of the present invention.

FIG. 11 is a diagram showing a state of the rollers and the weight body during operation (at the time of engagement) according to the second embodiment of the present invention.

FIG. 12 is a diagram showing the state of the rollers and the weight body when the eccentricity (when receiving over-torque) according to the second embodiment of the present invention.

FIG. 13 is a view showing a state in which the roller is held on the inner peripheral side of the outer peripheral edge of the pocket when not rotating in the second embodiment.

FIG. 14 is a front view of a rotary actuated one-way clutch showing a third embodiment of the present invention.

FIG. 15 is an axial sectional view of a rotary actuated one-way clutch according to a third embodiment of the present invention.

FIG. 16 is a view showing the condition of the rollers and the weight at the time of non-rotation to low-speed rotation in the third embodiment of the present invention.

FIG. 17 is a schematic view showing the position of the roller when it is not operated in the third embodiment of the present invention. FIG. 18 is a diagram showing a state of the roller and the weight body during operation (at the time of engagement) according to the third embodiment of the present invention.

FIG. 19 is a diagram showing the state of the mouth and the weight at the time of eccentricity (when over torque is applied) according to the third embodiment of the present invention.

FIG. 20 is a developed view of the cage (first plate) according to the third embodiment of the present invention. FIG. 21 is a developed view of the cage (second plate) according to the third embodiment of the present invention. FIG. 22 is a schematic view of the pocket portion of the third embodiment of the present invention viewed from the outer diameter side. FIG. 23 is a front view of an accordion spring mounting portion according to a third embodiment of the present invention.

FIG. 24 is a front view of a rotation actuated one-way clutch according to a fourth embodiment of the present invention.

FIG. 25 is an axial cross-sectional view of a rotation-actuated one-way clutch according to a fourth embodiment of the present invention.

FIG. 26 is a view showing the state of the rollers and the weight at the time of non-rotation to low-speed rotation in the fourth embodiment of the present invention.

FIG. 27 is a diagram showing the state of the roller and the weight rotating at a predetermined rotation speed or more in the fourth embodiment.

FIG. 28 is a diagram showing a state in which the roller is held on the inner peripheral side of the outer peripheral edge of the pocket when not rotating in the fourth embodiment. FIG. 29 is a development view of the cage (first plate) according to the fourth embodiment of the present invention. FIG. 30 is a developed view of a retainer (second plate) according to a fourth embodiment of the present invention. FIG. 31 is a schematic view of the pocket portion viewed from the inner diameter side in the fourth embodiment of the present invention.

FIG. 32 is a front view of an accordion spring mounting portion according to a fourth embodiment of the present invention.

FIG. 33 is a front view of a rotary operation type one-way clutch according to a fifth embodiment of the present invention. is there.

FIG. 34 is a cross-sectional view of FIG. 33 taken along the line FIG. 34—FIG. 34.

FIG. 35 is an enlarged view showing the operation of the weight and the roller during non-rotation.

FIG. 36 is an enlarged view showing the operation of the weight and the roller during rotation.

FIG. 37 is a top view showing the urging spring and the state of attachment thereof.

FIG. 38 is a front view showing a biasing spring and a state of attachment thereof.

Figure 39 is a side view of the weight. ,

FIG. 40 is a top view of the weight. BEST MODE FOR CARRYING OUT THE INVENTION

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. Each embodiment is described only for the purpose of illustrating the present invention by way of example, and it is needless to say that the present invention is not limited thereto.

(First embodiment)

FIG. 1 is a front view of a rotation-actuated one-way clutch showing an embodiment of the present invention, and FIG. 2 is an axial cross-sectional view taken along a line 2-2 in FIG. The rotary operation type one-way clutch 1 has an inner ring 2 having a hollow shaft fitted with a drive shaft (not shown) having a spline 2a engraved on an inner periphery thereof, coaxially on a radially outer side of the inner ring 2, and It comprises an inner ring 2 and an outer ring 3 arranged to be relatively rotatable. As shown in both FIGS. 1 and 2, an engagement tongue 26 extending in the axial direction is provided on the inner periphery of the retainer 4, and a concave groove 25 provided on the inner periphery of the inner ring 2 is provided. Mated and fixed to inner ring 2. The engagement between the engaging tongue 26 and the concave groove 25 can prevent the cage from being displaced, and the clearance between the outer and inner rings is properly maintained, thereby being affected by vibration and the like. Even in such a case, the joint operation can be performed reliably. In FIG. 3, a plurality of pockets 9 opened to the inner peripheral surface 3a of the outer ring 3 are provided on the outer peripheral portion of the inner ring 2 at equal intervals in the circumferential direction. 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. The bearing portion 13 has the same function as a slide bearing as a bearing mechanism for supporting between the outer ring 3 and the inner ring 2.

Each pocket 9 has a cam surface 11 (see FIGS. 3 and 5) formed on a part of its inner peripheral surface, and is a rolling element that transmits torque. The weight 8 of the shape is arrange | positioned. In the pocket 9, the roller 7 does not engage with the roller 7 in the direction of the depth of the cam surface 11, that is, between the cam surface 11 and the cylindrical inner peripheral surface of the outer ring 3, and the one-way A biasing spring 5 for biasing the clutch 1 in the non-engagement direction in which the clutch 1 idles is provided.

An accordion spring is used as the biasing spring 5, and as shown in detail in FIG. 6, the return portion 14 of the retainer pillar 10 is sandwiched between the mounting portions 15 of the biasing spring 5. Thus, the biasing spring 5 is attached to the retainer pillar 10 of the retainer 4. One end of the biasing spring 5 on the side opposite to the mounting portion 15 is a pressing portion 16 for pressing the mouthpiece 7. A coil spring or the like can be used as the biasing spring 5, but it is difficult to set a small spring constant in a limited space with a coil spring, and it is more expensive than an accordion spring or the like. Therefore, it is preferable to use an accordion spring.

FIG. 2 is an axial sectional view showing a relationship between the inner ring 2, the outer ring 3, and the biasing spring 5, and shows that the biasing spring 5 is held by the retainer 4.

Next, the operation of the rotation-actuated one-way latch 1 of this embodiment will be described with reference to FIGS. 3, 4, and 5. FIG. FIG. 3 is a front view showing a main part of FIG. 1 and shows a state before the rollers are engaged (when they are not engaged). FIG. 4 shows a position of the rollers when the rollers are not operated in the first embodiment. Fig. 5 is a front view showing the main part of Fig. 1. It is a figure and shows the state at the time of the engagement (at the time of engagement) of a roller.

In the rotation operation type one-way clutch 1 having the above-described configuration, the roller 7 does not transmit torque in any of the relative rotation directions of the inner and outer wheels from the non-rotation period to the low-speed rotation region. FIG. 3 shows this state, and there is a slight gap d between the inner peripheral surface 3 a of the outer ring 3 and the roller 7. At this time, the weight 8 is located almost at the innermost part of the pocket 9. Further, the roller 7 is urged and supported by an urging spring 5 in a state of contacting both the weight operating surface 12 and the cam surface 11 provided on a part of the surface defining the pocket 9, and the weight 8 is It is located in a space surrounded by the weight operating surface 12 and the cam surface 11 that define the roller 7 and the pocket 9. The pocket 9 can accommodate at least one of the roller 7, the weight 8, and the biasing spring 5.

FIG. 4 shows this state, in which a slight gap d 2 exists between the outer peripheral surface 2 a of the inner ring 2 and the mouthpiece 7. Further, the weight body 8 is located almost at the innermost part of the pocket 9. When the weight 8 is not operated, the roller 7 is held on the outer peripheral edge portion of the pocket 9, that is, on the inner diameter side of the outer peripheral surface 2 a of the inner ring 2.

When the rotation speed rises from the disengaged state in FIG. 3, the weight 8 is subjected to centrifugal force, and the circumferential width of the pocket formed gradually on the outer side of the pocket 9 is gradually increased in the radial direction. The roller 7 moves to the outer diameter side along the circumferential end surface inclined so as to be narrow, that is, the weight operating surface 12, and the centrifugal force (Fc) received by the weight 8 in addition to the centrifugal force received by the roller 7 itself is applied to the roller 7. In addition, a force (Fw) that presses the roller 7 in the circumferential direction to a position where the roller 7 can engage with the cam surface 11 acts. FIG. 5 shows such an engaged state, in which the roller 7 is fitted between the inner peripheral surface 3 a of the outer ring 3 and the cam surface 11.

Further, when the number of rotations exceeds a predetermined value, a sufficient pressing force is applied to the roller 7, and a state in which the function of the rotation actuated one-way clutch 1 can be exhibited, that is, a state in which lockup is possible. That is, in this state, assuming that the inner ring 2 is in a fixed state in FIG. 5, when the outer ring 3 rotates leftward in the figure, the idle state (non-engagement state) occurs. When rotating to the right in the figure, the engagement state (engagement state) is established, and torque is transmitted between the inner and outer wheels.

In FIG. 5, a circle C1 passing through the center of the roller 7 is located on the outer diameter side of a circle C2 passing through a contact point between the roller 7 and the weight body 8. Further, a weight operating surface 12 is provided on one of the radially extending surfaces constituting the pocket 9. The cavity formed by the roller 7 as the rolling element, the weight 8, and the weight operating surface 12 is formed smaller than the weight 8. That is, the contact point between the roller 7 and the weight 8 is always located on the inner diameter side with respect to the center of the inner ring 2 or the outer ring 3 from the center of the roller 7.

By the way, a predetermined wedge angle 0 is set on the weight operating surface 12 in order to prevent the weight 8 from being caught between the roller 7 and the weight operating surface 12. The wedge angle 0 is the angle between the tangent line at the contact point between the weight 8 and the roller 7 and the weight operating surface 12, and the set angle differs depending on the ratio between the diameters of the weight 8 and the roller 7. On the outer diameter side of the cam surface 11 and on the opposite side of the weight body 8, a non-wedge action surface 21 that is inclined more greatly than the cam surface 11 is formed. The non-wedge action surface 21 is shallower than the cam surface 11, that is, the inclination is set to be larger than the cam surface 11. When an excessive torque is applied to the roller 7, the roller 7 moves to the non-wedge action surface 21 and releases the excessive torque at the non-wedge action surface 21 to prevent the device from being damaged. ing.

In the one-way clutch 1 having the above-described configuration, the torque is not transmitted from the mouth roller 7 in either direction of the relative rotation of the inner and outer wheels from the non-rotation period to the low-speed rotation region. In addition, there is a slight gap between the inner peripheral surface 3 a of the outer ring 3 and the roller 7, and when the weight 8 is not operated, the roller 7 is positioned at the outer peripheral portion of the pocket, that is, the inner peripheral surface of the outer ring 3. It is held on the inner diameter side than 3a.

Further, the roller 7 and the weight body 8 can be formed in a cylindrical shape.

According to the first embodiment, the biasing spring causes the rolling element to move in the non-engagement direction with the cam surface. The pockets are provided with a weight that receives the centrifugal force and presses the rolling element in the direction of engagement with the cam surface while resisting the urging force of the urging spring. It is possible to provide a rotation-operating one-way clutch having a structure that can be designed at low cost, with a small spring constant, and that can be designed with a small amount of space. Further, according to the first embodiment, the operation of the weight can be made smooth, and furthermore, the device can be prevented from being damaged when an excessive torque is applied to the rolling elements. Further, the loadable torque can be set large. In addition, the shape is simple and processing is easy. Also, a weight having a simple shape and easy processing can be obtained, and the processing is easier and less expensive than the case where the biasing spring is directly attached to the inner ring or the like.

(Second embodiment)

Next, a second embodiment of the present invention will be described. FIG. 7 is a front view of a rotary operation type one-way clutch 130 showing the second embodiment, and FIG. 8 is a schematic diagram of a pocket portion of the second embodiment viewed from the outside diameter side. The rotation-actuated one-way clutch 130 has a spline 110a formed on the inner periphery thereof, and a radius of the inner ring 102, which is a hollow shaft fitted to a drive shaft (not shown), and a radius of the inner ring 102. An inner ring 102 and an outer ring 103 arranged coaxially on the outer side in the direction and rotatably relative to each other.

In the second embodiment, a pocket for accommodating a roller, a weight, an accordion spring and the like constituting a one-way clutch portion is formed by the outer peripheral surface of the inner ring 102 and the window portion 134 provided in the retainer 132. Constitute.

A substantially annular retainer 13 2 disposed between the outer ring 103 and the inner ring 102 is a retainer body, and a substantially annular support plate 13 is provided on an axial end surface of the retainer 13 2. 4 are provided. The support plate 134 is fixed to the retainer 132 by the retainer coupling part 133.

As shown in FIG. 7, FIG. 8 and FIG. 10, on the outer ring 103 side of the retainer 13 2, the inner circumferential surface 103 a of the outer ring 103 (FIGS. 14, FIG. 15 and FIG. 1 8) can be rubbed A simple bearing section 120 is provided. The bearing portion 120 has a function of supporting the inner ring 102 and the outer ring 103 concentrically. Further, bearing portions 120 having a predetermined length in the circumferential direction are provided between the window portions 144 at equal intervals in the circumferential direction.

An accordion spring 1 3 5, an outer ring 10 3, and an inner ring 13, which urge the roller 13 7 from almost the tangential direction, are provided in the window 1 3 4 A roller 1337 that transmits torque between the roller 130 and the roller 132, and a weight body 1338 that acts on the roller 1337 and presses the roller 1337 in the combining direction are arranged. When the weight 1 38 is not acting, a part of the weight 1 38 is housed in the concave portion 13 1 provided on the outer peripheral surface of the inner ring 102. The inner peripheral edge of the support plate 13 4 is located on the outer diameter side of the concave portion 13 1, and a communication portion 106 is formed so that a part of the weight 13 8 can be seen. With this communication part 106, after assembling the device (rotationally actuated one-way clutch), the presence or absence of the weight body 138 can be easily confirmed visually, and the missing item can be easily confirmed.

The retainer 1332 is provided with a concave portion 1336 having a substantially U-shaped cross section in the 铎 direction, and the end opposite to the end that applies a biasing force to the roller 1337 of the cordion spring 1335 is formed. It is fitted into and held by this recess 13 (see FIG. 10).

As can be seen from FIG. 8, the window portion 144 of the retainer 132 is formed by hollowing out the retainer 132 in the axial direction and leaving the wall portion. The axially open end of the window portion 144 is closed by the support plate 134 described above. Therefore, the accordion springs 135, rollers 135, and weights 135 accommodated in the windows 134 are axially formed by the walls of the retainers 132 and the support plates 134. It is held in the radial direction by the outer ring 103 and the inner ring 102, and does not deviate from the window portion 144.

FIG. 9 is an axial sectional view of the rotation operation type one-way clutch 130. It can be seen that the support plate 13 4 is fixed to the retainer 13 2 by the retainer connecting portion 13 3. The rollers 13 7 support the wall of the cage 1 32 It can also be seen that there is a very small clearance between the plate 13 and the plate 13 and it is supported in the axial direction.

Next, the operation of the rotation actuated one-way clutch 130 of the second embodiment will be described with reference to FIGS. FIG. 10 is a diagram showing the state of the roller and the weight at the time of non-rotation and low-speed rotation in the second embodiment. FIG. 11 shows the state of the roller and the roller during operation (at the time of engagement) of the second embodiment. FIG. 12 is a diagram showing a state of the weight, and FIG. 12 is a diagram showing a state of the roller and the weight at the time of eccentricity (when receiving over one torque) of the second embodiment.

Here, the configuration of the second embodiment will be described in more detail with reference to FIG. The retainer 1332 has a plurality of convex portions 144 fitted to a plurality of concave grooves 144 provided on the outer peripheral surface of the inner ring 102 at equal circumferential intervals. Since the convex portion 144 fits in the concave groove 144, the retainer 132 and the inner ring 102 do not rotate relative to each other. That is, the concave groove 144 and the convex part 144 constitute a rotation preventing mechanism for preventing the relative rotation between the retainer 132 and the inner ring 102.

A weight working surface 140 is formed on one side of the window 1 43 of the cage 1 32, and when the weight 1 38 receives centrifugal force, it moves to the outer diameter side along this surface. Then, the roller 1337 is brought into contact with the roller 1337, and the roller 1337 is moved to the mating position. At this time, the centrifugal force received by the weight 1338 is applied to the roller 1337 in addition to the centrifugal force received by the roller 1337 itself. On the outer diameter side of the weight working surface 140, there is provided a weight locking portion 141 that limits the operation range of the weight body 1 38, and the weight body 1 38 is further moved to the outer diameter side. You cannot move. The weight locking portion 141 is formed by narrowing the space between the retainer 132 and the outer peripheral surface of the inner ring 102. Further, a roller engaging portion 142 (rolling member engaging portion) for limiting an operation range of the roller 1337 in the direction of the weight 1338 is provided on the outer diameter side. The weight operating surface 140, the weight locking portion 141, and the roller locking portion 142 are provided continuously in the embodiment, but need not necessarily be formed continuously. On the outer peripheral surface of the inner ring 102, there is a weight 1 A concave portion 13 1 into which a part of 3 8 fits is provided, and a cam surface 1 47 which is a torque transmitting surface of the roller 13 7 is formed adjacent to the concave portion 13 1, and a cam surface 14 Further on the outer diameter side of 7, and on the opposite side of the concave portion 13 1 of the cam surface 147, a non-wedge action surface 146 inclined more greatly than the cam surface is formed. The concave portion 131, the cam surface 147, and the non-wedge action surface 146 are provided continuously in the embodiment, but need not necessarily be formed continuously.

As shown in Fig. 10, during non-rotation to low-speed rotation (region), the weight 1338 is located on the inner diameter side of the recess 131, contacts the roller 1337, and the roller 1337 accords. It is in a state of being pressed against the roller locking portion 142 by the spring 135. Thereafter, the inner ring 102 rotates, and when the inner ring rotates at a high speed equal to or higher than a predetermined number of revolutions, the weight 13 8 subjected to centrifugal force moves to the outer diameter side, and the roller 13 7 To the cam surface 1 4 7 mating position. In this state, when the inner wheel 102 rotates ahead of the outer wheel 3 in the counterclockwise direction in the drawing, torque transmission is performed. The state during this operation is shown in FIG. As shown in FIG. 11, the contact point between the roller 1337 and the weight body 138 is located on the outer diameter side from the center of the roller 1337. That is, the circle C 1 passing through the center of the roller 13 37 is located on the outer diameter side of the circle C 2 passing through the contact point between the roller 13 7 and the weight 13 8.

In addition, when the roller 1337 receives an excessive torque, as shown in FIG. 12, the roller 1337 moves to the non-wedge action surface 1446 so that the torque can be released. . At this time, the weight body 138 is restricted from moving toward the cam surface 147 by the weight locking portion 141. Therefore, the roller 1337 moves to the accordion spring 135 side, and the contact with the weight body 1338 whose movement is restricted by the weight locking portion 141 is cut off.

The retainer 13 of the second embodiment is mainly made of resin, and the roller. As a result, the coefficient of friction between the cage 13 and the roller 13 7 is lower than when the cage 13 2 is made of metal, and the operation of the roller 13 7 becomes smoother. . In addition, the weight can be reduced. The retainer 13 2 can also be made of a material such as animal or aluminum.

Note that the roller 1337 does not transmit torque in either direction of the relative rotation of the inner and outer wheels from the non-rotation period to the low-speed rotation range. As shown in FIG. 13, during non-rotation, the roller 1337 is held on the inner peripheral side of the outer peripheral edge of the pocket 1339. That is, a gap d3 is formed between the outer peripheral edge 139 of the retainer 144 and the roller 1337. As a result, even if there is a slight misalignment between the outer ring and inner ring due to vibrations such as engine rotation, etc., it is possible to prevent a malfunction in which the rollers are dragged by the inner ring surface of the outer ring and get into the cam surface. And the operation of the weight body and the rolling element becomes smooth. Also, drag torque during idling can be reduced.

(Third embodiment)

Next, a third embodiment of the present invention will be described with reference to FIGS. The third embodiment is substantially the same as the second embodiment described above in terms of the positional relationship and operation of the weight body 1338, the roller 1337, and the accordion spring 135. In the third embodiment, the form of the cage is significantly different from that of the second embodiment.

The retainer used in the present embodiment will be described with reference to FIGS. FIG. 20 is an exploded view of the first plate 160 of the cage 150 of the third embodiment, and FIG. 21 is a second plate 17 of the cage 150 of the third embodiment. It is a development view of 0. In this embodiment, the cage 150 is formed as a first and a second plate by punching a plate-shaped steel plate. FIG. 20 is an exploded view of the first plate 160. The first plate 160 is composed of a substantially annular main body 166 and a plurality of convex portions extending in the outer diameter direction. You. The protruding portion is composed of a first column portion 15 1 and a hole 16 2 for attaching an accordion spring 13 5. The main body 166 is further provided with a caulking hole 64 for coupling to a second plate 170 described later. Further, two engaging tongues 165 are provided in the inner diameter direction of the main body 166 to fix the retainer 150 to the inner ring 102. It is preferable that the above-described caulking holes 164 and the engaging tongue portions 1665 are equally arranged in the circumferential direction. The engaging tongue 165 is fitted in the concave groove 154 of the inner ring 102 and fixed to the entire inner ring 102 of the cage. That is, the concave groove 154 and the engaging tongue portion 165 constitute a detent mechanism for preventing the relative rotation between the retainer 150 and the inner ring 102.

FIG. 21 is an exploded view of the first plate 10, and the second plate 170 is composed of a substantially annular body 175, a plurality of convex portions extending in the outer diameter direction. You. The convex portion is composed of a second columnar portion 172 and a crimping projection 171, and a weight operating surface 152 described later is provided between the second columnar portion 172 and the projection 71. Is formed.

Two engaging tongues 174 are provided in the inner diameter direction of the main body 175 to fix the retainer 150 to the inner ring 102. It is preferable that the above-mentioned convex portion and engaging tongue portion 165 are respectively arranged equally in the circumferential direction. After bending the first plate 160 and the second plate 170 described above to obtain a predetermined shape, the retainer 150 of this embodiment is connected by connecting both plates (see FIG. 14 and Fig. 15).

Next, the details of the rotation actuated one-way latch 180 of the third embodiment will be described with reference to FIGS. FIG. 14 is a front view of a rotation-operated one-way clutch 180 showing the third embodiment, and FIG. 15 is an axial view of a rotation-operating one-way clutch 180 showing the third embodiment ′. It is sectional drawing. FIG. 16 is a diagram showing the state of the roller and the weight at the time of non-rotation to low-speed rotation in the third embodiment. FIG. 17 is a diagram showing the roller at the time of non-operation in the third embodiment of the present invention. FIG. 18 is a diagram showing the state of the roller and the weight when the third embodiment is in operation (at the time of engagement), and FIG. 19 is a diagram showing the third embodiment. When eccentric FIG. 4 is a diagram illustrating a state of a roller and a weight body.

In FIG. 14, the cam surface 14 7 and the non-wedge working surface 1 46 (FIGS. 16, 18 and 19) provided on the outer peripheral surface of the inner ring 102 are the same as those of the first embodiment. It is almost the same as The difference between the third embodiment and the second embodiment is that the working surface of the weight body 138 is formed on the convex portion provided on the first or second plate constituting the retainer 150. That is the point.

The crimping projections 17 1 of the second plate 170 are fitted into the crimping holes 16 4 of the first plate 160 and crimped, so that the retainer is 150 is formed. The convex portion of the second plate 170 is bent to be positioned on the inner periphery of the outer ring 103, and has a weight operating surface 15 2 having a predetermined inclination with respect to a radial direction, and a weight locking portion 1. 5 and 5 are formed. The weight locking portion 150 is formed by narrowing the space between the retainer 150 and the outer peripheral surface of the inner ring 2.

FIG. 15 is an axial sectional view of FIG. 14, and it can be seen that the retainer 150 is composed of the first plate 160 and the second plate 170.

Next, with reference to FIGS. 16 to 19, the operation of the rotation actuated one-way latch 180 of the third embodiment will be described. The basic operation is the same as in the second embodiment. As shown in Fig. 16, during non-rotation to low-speed rotation (region), the weight 1 38 is located on the inner diameter side of the recess 13 1, and the opening 13 7 is an accordion spring 13 # 5 in the non-engagement direction by # 5.

FIG. 17 shows this state, and a slight gap d4 exists between the outer peripheral edge of the second plate 170 and the roller 1337. When the weight body 1 38 is not operated, the opening 1.37 is held at the outer peripheral edge portion of the pocket, that is, at the inner diameter side portion of the outer peripheral edge of the retainer 150. .

Thereafter, the inner ring 102 rotates, and when the rotation starts rotating at a high speed equal to or higher than a predetermined number of revolutions, the weight body 1 38 subjected to the centrifugal force moves to the outer diameter side along the weight operation surface 152. Move the rollers 1 3 7 to the mating position of the cam surface 1 4 7 The mechanism is such that torque is transmitted when O2 rotates ahead of the outer ring 103 in the counterclockwise direction in the figure. Figure 18 shows the state during this operation. Further, when the roller 1337 receives an excessive torque, as shown in FIG. 19, the roller 1337 moves to the non-wedge action surface 1446 so that the torque can be released. . At this time, the weight body 1338 is blocked by the weight locking portion 1555, and the movement to the cam surface 147 side is restricted. Therefore, the roller 1337 moves to the accordion spring 135 side, and the contact with the weight 1338 whose movement is restricted by the weight locking portion 1555 is cut off. Note that the inner peripheral surface 103a of the outer ring 103 is displaced to the position 103b when there is no eccentricity.

Here, the relationship between the retainer 150 and the accordion spring 135 is as follows. FIG. 22 is a schematic diagram of the pocket portion of the second embodiment viewed from the outer diameter side. FIG. 23 is a front view of an accordion spring mounting portion in the third embodiment.

As shown in Fig. 22, the accordion spring 1 3 5 has a joint 1 5 8 at the tip which presses the mouth 1 3 7, and an attachment 1 5 7 at the base. . By holding the first pillar portion 151 with the mounting portion 157, the accordion spring 135 is fixed to the retainer 150. Further, by engaging the tongue piece 156 formed by notching the mounting portion with the hole 162, the accordion spring 135 is more firmly fixed and can be prevented from falling off.

The mounting state of the mounting part 1 57 of the accordion spring 1 3 5 is shown in FIG. 23, and the tongue at the tip of the mounting part 1 57 is inserted into the hole 16 2 of the first plate 160 of the cage. It can be seen that the pieces 1 56 are fitted. According to the third embodiment, the cage 150 can be made of steel, synthetic resin, aluminum or the like. Further, since the entire cage can be formed thinner than the cage of the first embodiment, the weight of the one-way clutch can be reduced. Along with this, the processing cost can be reduced. In addition, from the time of non-rotation to the low-speed rotation range, the rollers 1337 do not transmit torque in either direction of the relative rotation direction of the inner and outer wheels. There is a slight gap between the outer periphery of the second plate 170 and the roller 1337, and when the weight body 138 is not operated, the roller 1337 is positioned at the outer periphery of the pocket, that is, the cage 1 It is held on the inner diameter side of the outer peripheral edge of 50.

According to the second and third embodiments described above, it is possible to prevent a malfunction in which the weight body jumps out to the force surface side immediately after receiving the excessive torque and does not return to the weight operation surface side.

In addition, the positioning of the cage and the positional deviation in the circumferential direction can be prevented, and the operation becomes smooth because the frictional resistance with the weight body is relatively small. In addition, the effect that the entire device can be reduced is obtained.

(Fourth embodiment)

FIG. 24 is a front view of a rotation actuated one-way clutch 220 of the fourth embodiment of the present invention, and FIG. 25 is an axial sectional view thereof. The rotation-operating one-way clutch 220 has a spline 202a formed on the inner periphery thereof, and the inner ring 2 is a hollow shaft fitted to a drive shaft (not shown). The outer ring 203 is arranged coaxially on the outside, and is disposed so as to be rotatable relative to the inner ring 202. For convenience of description, in the present specification, the “rotationally actuated one-way latch” may be simply referred to as “one-way clutch”.

In FIG. 24, a plurality of pockets 209 that are open to the inner peripheral surface 203 a of the outer ring 203 are provided on the outer peripheral portion of the inner ring 202 at equal circumferential intervals. Each pocket 209 has a cam surface 206 formed on a part of the inner peripheral surface thereof, and a substantially cylindrical roller 7 and a substantially cylindrical weight 8 are arranged. In the pocket 209, the roller 207 is further provided with a roller 207 in the direction of the depth of the cam surface 206, that is, between the cam surface 206 and the cylindrical inner peripheral surface of the outer ring 203. 7 does not inject, the one-way clutch 2 20 runs idle, and a biasing spring that biases in the non-engagement direction 205 is provided. The weight body 208 is accommodated in a concave part 211 provided on the outer peripheral surface of the inner ring 202.

FIG. 25 is an axial cross-sectional view showing the relationship between the inner ring 202, the outer ring 203, and the cage 204, and the cage 204 is composed of the first plate 230 and the second plate It can be seen that it is composed of 40 and. FIG. 26 is a diagram illustrating the operation of the one-way clutch 220 during non-rotation to low-speed rotation (range). During non-rotation to low-speed rotation (region), the weight 208 is located on the inner diameter side of the concave portion 211 and is in contact with the roller 207, and the roller 207 is disengaged in the non-engagement direction by the accordion spring 5. Is pressed.

Thereafter, when the inner ring 202 rotates and rotates at a high speed equal to or higher than a predetermined number of revolutions, the weight body 208 subjected to the centrifugal force rolls to the outer diameter side along the weight operating surface 222. Or, while sliding, move the roller 207 to the position where the cam surface 206 engages, and when the outer ring 203 rotates ahead of the inner ring 202 in the clockwise direction in the figure, the torsion occurs. It is designed to transmit luck. Figure 27 shows the state at this time. The contact point between the roller 207 and the weight body 208 is located on the inner diameter side from the center of the roller 207. That is, the circle C1 passing through the center of the roller 207 is located on the outer diameter side of the circle C2 passing through the contact point between the roller 207 and the weight 208.

Further, as shown in FIG. 28, the roller 207 is held on the inner peripheral side of the outer peripheral edge 209 of the pocket when not rotating. That is, a gap d5 is formed between the outer peripheral edge portion 209 of the retainer 204 and the roller 207. As a result, even if a slight misalignment occurs between the outer ring and the outer ring due to vibrations of the engine or the like, it is possible to prevent a malfunction in which the rollers are dragged by the inner peripheral surface of the outer ring and fall into the cam surface. The operation of the weight and the rolling elements becomes smooth. In addition, the drag torque during idling can be reduced.

Next, the cage 204 used in the present embodiment will be described with reference to FIGS. FIG. 29 shows the expansion of the first plate 230 of the cage 204 of the present invention. FIG. 30 is an exploded view of the second plate 240 of the retainer 24. FIG. In the present embodiment, the retainer 204 is formed as a first and a second plate by punching a bent plate-shaped steel plate. As shown in FIG. 27, the first plate 230 is composed of a substantially annular main body 236 and a plurality of convex portions extending in the outer diameter direction. The protruding portion is composed of a first pillar portion 232 and a hole 231 for mounting an accordion spring 205.

The main body 2 36 is further provided with a caulking hole 34 for coupling with a second plate 240 described later. Further, two engaging tongues 2 35 are provided in the inner diameter direction of the main body 2 36 to fix the retainer 204 to the inner ring 202. The above-mentioned projections, caulking holes 2 3 4 and engaging tongues 2 3 5 are equally divided in the circumferential direction to disperse the stress applied to the cage and suppress the stress concentrated locally. It is preferable to arrange them. The engaging tongues 2 35 are fitted into the concave grooves 2 15 of the inner ring 202 (see FIG. 24) to fix the entire retainer to the inner ring 202.

As shown in FIG. 30, the second plate 240 is composed of a substantially annular main body 246 and a plurality of convex portions extending in the outer diameter direction. The protruding portion is composed of the second column portion 242 and a crimping protrusion, that is, a claw 241. The second column portion 242 has a claw 241 and a weight operating surface 221. Have been.

As described above, the retainer 204 composed of the first plate 230 and the second plate 240 is assembled as follows. Formed on the second column 2 4 2 of the second plate 2 40 having the weight operating surface 2 2 1, the claw 2 4 1 provided at the tip is provided with a caulking hole 2 3 provided on the first plate 2 3 0 Both plates are joined by fitting and crimping to 4. The cage 204 after coupling is shown in FIGS. 24 and 25.

The pawl 2 41 is provided at the position where the weight operating surface 2 21 is formed or at the outer diameter side when gripping the front of the one-way clutch 220 (FIG. 24). By adopting such a configuration, it is possible to fix the vicinity of a portion which receives direct force from the weight 208. The bending moment received from the weight operating surface 2 2 1 is reduced. FIGS. 31 and 32 show the relationship between the retainer 204 and the accordion spring 205. FIG. 31 is a schematic view of the pocket portion viewed from the inner diameter side in the present invention. FIG. 2 is a front view of an accordion spring mounting portion in the present invention.

As shown in FIG. 31, the accordion spring 205 has a joining portion 216 that presses the roller 207 at a tip portion, and a mounting portion 217 at a root portion. By holding the first column 2 32 between the mounting portions 2 17, the accordion spring 205 is fixed to the retainer 240. Further, by engaging the tongue piece 218 formed by notching the mounting portion 217 with the hole 231, the accordion spring 205 is more firmly fixed and can be prevented from falling off. The front view of the mounting part 2 17 of the accordion spring 205 is shown in FIG. 32, and the mounting part 2 1 7 is provided in the hole 31 of the first plate 230 of the cage 204. It can be seen that the tongue piece 2 18 at the tip of the is fitted. Also, since the inner ring 202 is made of steel, the retainer 204 can be made of synthetic resin, aluminum, or the like, so that the weight of the one-way clutch can be reduced. In addition to this, the processing cost can be reduced.

Furthermore, when a one-way clutch is used for a motorcycle, it is used under a high-speed rotation of about 1000 rpm, but in such a situation, the centrifugal force applied to the weight body becomes a problem. The weight working surface formed by bending the cage may be turned up. With the configuration as in the present embodiment, this can be prevented.

According to the fourth embodiment, the strength that can withstand use under high-speed rotation can be ensured, the number of parts can be reduced, the cost is low, the spring constant can be set small, dimensional accuracy can be easily obtained, and the weight can be reduced. It is possible to provide a rotation-operating one-way clutch having a structure that can be designed even in a space-saving manner without the possibility of getting stuck. (Fifth embodiment)

FIG. 33 is a front view of a rotary actuation one-way clutch showing a fifth embodiment of the present invention, and FIG. 34 is an axial sectional view taken along the line FIG. 34—FIG. 34 in FIG. It is. The rotation-actuated one-way clutch 501 has a spline 5002a engraved on the inner periphery thereof. The inner ring 5002 is a hollow shaft fitted to a drive shaft (not shown). The outer ring 503 is arranged coaxially on the outside in the radial direction, and is disposed so as to be relatively rotatable relative to the inner ring 502.

A substantially cylindrical rolling element, that is, a roller 507 and a substantially cylindrical weight 508 are disposed between the outer ring 503 and the inner ring 502. Further, the urging spring 505 is provided so as to press the roller 507. In addition, the gap between the cam surface 5 1 2 (FIG. 3 5) and the cylindrical inner peripheral surface 5 0 3a of the outer ring 5 0 3 is increased, that is, the one-way clutch 5 1 A biasing spring 505 for directly biasing the mouth 507 in the direction is provided.

A side plate 504 is provided between the outer ring 503 and the inner ring 502 to hold the urging spring 505, the roller 507, and the weight 508 so as not to drop off in the axial direction. Have been. As shown in FIG. 34, the side plate 504 includes a first portion 504 a substantially covering the biasing spring 505, the roller 507, and the weight 508 in the radial direction, and one end in the axial direction. The first portion 504a and the second portion 504b are joined together by caulking or the like to form an integral second portion 504b. This caulking has a configuration in which the end of the column portion 513 that is bent and raised in the axial direction from one side plate is bent, and the opposite side plate is sandwiched with other portions of the column portion. The side plate 504 has an engaging tongue piece 510 on the radially inner diameter side, and this engaging tongue piece 510 fits into a concave portion 511 provided on the inner periphery of the inner ring 502. This keeps the inner ring in a fixed state. The outer ring 503 is attached with a predetermined clearance.

As shown in Fig. 33, the first portion 504a of the side plate 504 A plurality of long holes 506 are provided at equal intervals in the circumferential direction, and a weight 508 is disposed in the long holes 506 (see FIGS. 35 and 36). The outer peripheral surface of the first cylindrical portion 52 1 of the weight body 508 (supported portion 52 3 <see FIG. 40>) is supported by the inner periphery of the long hole 506, and the length of the long hole 506 is long. It is mounted so that it can move within the length range in the direction. The long hole 506 is also provided in the second portion of the side plate 504 at a position corresponding to the first portion.

In this specification, the term "side plate" means a structure that can support the rolling element and the weight only from the axial side and cannot prevent the falling off unless assembled to the outer ring.

Next, the operation of the rotation-operated one-way clutch 501 of the present invention will be described with reference to FIGS. 35 and 36. As is evident from Fig. 33, a biasing spring 505 is attached to the column part 5 13, and the roller 507 is directed in the deep direction (non-engagement direction) of the cam surface 5 12. Is energizing.

FIG. 35 shows a state where the inner ring 502 is not rotating or rotating at a low speed. At this time, since the roller 507 is pressed by the biasing spring 505 and is at a deep position on the cam surface 512, a gap between the roller 507 and the outer ring 503 is indicated by D. Exists. Therefore, the outer wheel 503 is in a state where it can idle in both directions with respect to the inner wheel 502.

On the other hand, Fig. 36 shows the state during normal rotation. At this time, centrifugal force acts on the weight 508, and the weight 508 causes the roller 507 to move to the shallow position (engagement position) of the cam surface 512, that is, in the direction of the non-wedge action surface 516. Press toward. Then, there is no gap in the portion indicated by E between the roller 507 and the outer ring 503, and the urging spring 505 is in a state of being compressed by the centrifugal force of the weight 508. . Accordingly, at this time, the function as the rotation-operating one-way clutch 501 is exhibited, and when the outer ring 503 tries to rotate to the right relative to the inner ring 502 in the figure, the outer inner ring The gap is locked by the transmission of torque from the mouth 507, conversely turning to the left It spins when you try. In either of the states shown in FIGS. 35 and 36, the urging spring 505 directly applies the urging force to the roller 507.

An accordion spring is used for the biasing spring 505. As shown in detail in FIG. 37, the column portion 513 of the side plate 504 is attached to the mounting portion 5 of the biasing spring 505. The biasing spring 505 is attached to the side plate 504 by being sandwiched between the side plates 504. One end of the biasing spring 505 opposite to the mounting portion 515 is a pressing portion 517 for pressing the roller 507. Although a coil spring or the like can be used as the biasing spring 505, it is difficult to set a small spring constant in a limited space with a coil spring. However, it is preferable to use an accordion spring because the price may be relatively high.

FIG. 38 is a front view showing the biasing spring 505 (accordion spring) attached to the side plate 504. The accordion spring 505 is more firmly fixed by engaging the locking piece 515 formed by cutting out the mounting portion 514 with the hole 518.

Next, details of the weight body 508 used in the fifth embodiment of the present invention are shown in FIGS.

This will be described using 40. Figure 39 is a side view of the weight 508, and Figure 40 is the weight.

508 is a top view of FIG. The weight 508 is composed of two substantially cylindrical portions. It is composed of a small-diameter first cylindrical portion 522 and a large-diameter second cylindrical portion 522 provided integrally.

The first cylindrical portion 5221 is shorter than the second cylindrical portion 5222, and the supported portion 523 having a predetermined length is formed on both sides of the second cylindrical portion 5222 in the axial direction. The supported portion 523 is supported by long holes 506 provided on both axial sides of the side plate 504. That is, as the supported portion 23 moves in the elongated hole 506, the weight 508 moves. The outer peripheral surface of the large-diameter second cylindrical portion 522 contacts the roller 507 and presses the roller 507. In addition, the first cylindrical portion 5221 is a solid member, but may be a hollow member.

According to the fifth embodiment, since the urging spring is configured to directly urge the rolling element, the number of parts is reduced, the cost is low, the spring constant can be set small, and the structure can be designed in a small space. A rotation-operated one-way clutch can be provided.

In each of the embodiments described above, the weight may be formed from a material such as steel, copper, a steel alloy, aluminum, or a synthetic resin, but if a material having a large specific gravity such as steel is used, the weight per unit volume may be increased. Since the received centrifugal force increases, a state in which the size of the device is small and compatible even at low speed rotation is obtained, and the diameter of the weight can be reduced.

Although a cylindrical roller is shown as a rolling element disposed in a pocket, it may be a spherical roller. Also, the weight may be a sphere instead of a cylindrical mouthpiece. Further, as for the combination of the rolling element and the weight, both may be rollers and both may be spheres, either one may be a roller and the other may be a sphere.

In each embodiment, a plurality of pockets are provided in the circumferential direction. However, the number of pockets can be arbitrarily changed according to a required torque capacity and the like, and may be other than eight, for example, four or six. It may be a place. However, regardless of the number of pockets, it is preferable to arrange the pockets equally in the circumferential direction. By doing so, the reaction force received by the inner ring from the mouth during torque transmission can be dispersed, so that the durability of the inner ring is improved, and excessive force is applied to the bearing (not shown) that supports the outer and inner rings. It can be prevented from being added.

In some embodiments, the diameter of the roller and the weight is approximately the same size, but it is not necessary to make them the same size. (Range of numbers).

The rotation-actuated one-way clutch of the present invention can be applied not only to motorcycles, snowmobiles and the like, but also to four-wheeled vehicles and the like.

Claims

The scope of the claims

1. An outer ring having an inner peripheral cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, an urging spring for urging the rolling element, and a centrifugal force for receiving the centrifugal force. A rotation-operating one-way clutch including a weight that presses the rolling element in an engagement direction while resisting the urging force of an urging spring, wherein a weight operating surface that guides the operation of the weight is provided. Features a rotating one-way clutch.

2. The rolling element is biased and supported by the biasing spring in a state in which the rolling element is in contact with both the weight operating surface and the cam surface when the rotation operation type one-way clutch is not rotating. 2. The rotation actuated one-way clutch according to 1.

3. An outer ring having an inner peripheral cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, an urging spring for urging the rolling element, and a centrifugal force for receiving the centrifugal force. A rotation-operating one-way clutch including a weight that presses the rolling element in an engagement direction while resisting the urging force of the urging spring, wherein the urging spring is an accordion spring. One-way clutch. .

4. An outer ring having an inner peripheral cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, an urging spring for urging the rolling element, and receiving a centrifugal force. In a rotation type one-way clutch including a weight that presses the rolling element in an engagement direction while resisting the urging force of the urging spring, a continuous non-wedge action surface is formed in a shallow portion of the cam surface. A rotary actuated one-way clutch.

5. An outer ring having an inner cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, an urging spring for urging the rolling element, A rotation-operating one-way clutch including a weight that presses the rolling element in the engagement direction while resisting the urging force of the urging spring under centrifugal force, wherein a retainer that holds the urging spring is provided. A rotary actuated one-way clutch.

6. An inner groove of the inner ring is provided with a groove extending in the axial direction, while an engaging tongue extending in the axial direction is formed at a position corresponding to the groove on the inner periphery of the retainer. The rotation-actuated one-way clutch according to claim 5, wherein the retainer is attached to the inner ring by fitting the engaging tongue into the recess.

7. An outer ring having an inner peripheral cylindrical surface, an inner ring having a cam surface formed thereon, a rolling element for transmitting torque between the outer and inner rings, an urging spring for urging the rolling element, and a centrifugal force for receiving the centrifugal force. In a rotary actuated one-way clutch including a weight that presses the rolling element in an engagement direction while resisting the urging force of an urging spring, a bearing mechanism that supports between the outer ring and the inner ring is provided. A rotation-operated one-way clutch characterized by the following features:

8. The rotation-operated one-way clutch according to claim 7, wherein the bearing mechanism is provided on an outer peripheral surface of an inner race.

9. A retainer for holding the biasing spring is provided, and a concave groove extending in the axial direction is provided on the inner periphery of the inner ring, while a position corresponding to the concave groove on the retainer inner periphery. An engaging tongue extending in the axial direction is formed on the inner ring, and the retainer is attached to the inner ring by fitting the engaging tongue into the recess. And the rotation-operated one-way clutch according to any one of 6 to 8.

10. An outer ring having an inner cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, an urging spring for urging the rolling element, and a centrifugal force. The rolling element while receiving the urging force of the urging spring A rotary operation type one-way clutch provided with a weight body for pressing the weight in the engagement direction, wherein a locking portion for limiting an operation range of the weight body is provided.

11. An outer ring having an inner peripheral cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, an urging spring for urging the rolling element, and a centrifugal force. A rotary actuated one-way clutch having a weight that receives and pushes the rolling element in an engaging direction while staking the urging force of the urging spring; at least one of the rolling element, the weight, and the urging spring; A rotation-operating one-way clutch, characterized in that a retainer is provided for holding the bearing, and a bearing portion for supporting between the outer and inner rings is provided in the retainer.

12. The retainer is formed with a plurality of windows for positioning at least one of the rolling element, the weight, and the urging spring, and the window is provided between each of the windows. The rotation-operated one-way clutch according to claim 11, further comprising a bearing portion.

13. An outer ring having an inner peripheral cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, an urging spring for urging the rolling element, and a centrifugal force. A rotation-operating one-way clutch having a weight for receiving the urging force of the urging spring and pressing the rolling element in the engaging direction while resisting the urging force of the urging spring; at least one of the rolling element, the weight and the urging spring; A rotation-actuated one-way clutch, comprising: a retainer for holding the motor; and a detent mechanism for preventing relative rotation between the retainer and the inner ring.

14. An outer ring having an inner peripheral cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, an urging spring for urging the rolling element, and a centrifugal force. A rotary actuated one-way clutch comprising a weight that presses the rolling element in the engaging direction while receiving the urging force of the urging spring, and at least one of the rolling element, the weight, and the urging spring; Holding resin Rotation-operated one-way clutch provided with a cage made of steel.

15. A groove extending in the axial direction is provided on the outer periphery of the inner ring, while a convex portion is formed at a position corresponding to the concave groove on the inner periphery of the retainer, and the convex portion is formed on the concave portion. 14. The rotation-operated one-way clutch according to claim 13, wherein the retainer is attached to the inner race by fitting a portion.

16. The rotation actuated one-way clutch according to claim 12 or 15, wherein a communication portion is provided so that the weight body can be visually recognized from the outside when not rotating.

17. A rolling element that coaxially arranges an outer ring having a cylindrical surface on the inner circumference and an inner ring having a cam surface on the outer circumference to transmit torque between the outer and inner rings, and the rolling element that receives centrifugal force. And a biasing spring for biasing the rolling element in a non-engaging direction, and a retainer having a weight operating surface for guiding the operation of the weight. In the rotary actuation type one-way clutch, the retainer or one of the members constituting the retainer is provided with a column portion forming the weight operating surface, and a tip of the column portion is provided with a mating member. A rotation-actuated one-way clutch, which is provided with a claw for caulking.

18. The rotary actuated one-way clutch according to claim 17, wherein the pawl is provided at the same position as the weight operating surface or on an outer diameter side of the weight operating surface.

1 9. An outer ring having an inner peripheral cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, a biasing spring for biasing the rolling element, and a centrifugal force. The weight that presses the rolling element in the engagement direction while staking the urging force of the urging spring in response thereto, and the weight operating surface that determines the operating direction of the weight With a rotation-operated one-way clutch equipped with

A rotary operation type one-way clutch, wherein an outer diameter side portion of the weight operating surface is more greatly inclined with respect to a radial direction than an inner diameter side portion.

20. The rotary operation type one-way clutch according to claim 19, wherein the weight body operating surface includes two linear portions having different inclination angles and one arc portion connecting these linear portions.

2 1. An outer ring having an inner cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, a biasing spring for biasing the rolling element, and a centrifugal force. And a weight body that presses the rolling element in the engaging direction while being piled with the urging force of the urging spring, and accommodates the rolling element, the weight body, and the urging spring to determine the operating direction of the weight body. In a rotary operation type one-way clutch including a cage having a weight operation surface,

The rotation-operating one-way clutch, wherein the rolling element is held on an inner diameter side of an outer peripheral edge portion of the retainer when the weight body is not operated.

22. An outer ring having an inner peripheral cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, a biasing spring for biasing the rolling element, and a centrifugal force. In a rotation-operating one-way clutch provided with a weight that presses the rolling element in the engaging direction while receiving the urging force of the urging spring, the urging spring directly urges the rolling element. A rotation-operating one-way clutch characterized by:

23. An outer ring having an inner peripheral cylindrical surface, an inner ring having a cam surface, a rolling element for transmitting torque between the outer and inner rings, an urging spring for urging the rolling element, and a centrifugal force. A rotation-operating one-way clutch including a weight that presses the rolling element in the engaging direction while receiving the urging force of the urging spring and restricting the axial movement of the rolling element and the weight. Side plate is provided, 23. The rotation-operated one-way clutch according to claim 22, wherein the side plate is provided with an elongated hole for guiding the operation of the weight body.