JP2008185131A - Pulley unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a pulley unit capable of effectively preventing an accessary rotating speed from becoming excessive in engine high-speed rotation even when the diameter of an accessary pulley is reduced due to a situation such as reduction of an idling speed, and of contributing to reduction of weight or the like of a rotation element on the accessary side. <P>SOLUTION: This pulley unit is characterized in that, since centrifugal speed limiter mechanisms 30 are arranged in a one-way clutch mechanism incorporated in the pulley unit 100, when a drive-side engine comes into high-speed rotation above a certain value, the one-way clutch mechanism 3 is brought into an unlock state to block rotary torque transmission to an accessary rotary shaft 2 by the operation of the centrifugal speed limiter mechanisms 30. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a pulley unit.

JP 2001-4011 A

  When an auxiliary machine such as an alternator is driven to rotate from the crankshaft of an automobile engine via a belt or pulley unit, if a sudden rotational speed fluctuation occurs on the engine side, which is the driving side, the rotation of the driven side auxiliary machine will occur. It is difficult to follow this, and problems such as belt squealing and flapping are likely to occur. In addition, excessive rotational torque and tension may be generated in the pulleys, rotating shafts, belts, etc. of the auxiliary machine, which may cause a reduction in the life. Therefore, in order to prevent this, a one-way clutch mechanism for disconnecting the rotational connection with the auxiliary equipment when the rotational speed of the crankshaft decreases is interposed between the auxiliary equipment pulley and the auxiliary equipment rotating shaft. A technique is known (see Patent Document 1).

  In recent years, the idling of automobile engines has been promoted to reduce fuel consumption and environmental regulations. However, a decrease in the engine speed during idling leads to a decrease in the output of the driven alternator, so the auxiliary pulley is reduced in diameter in order to ensure sufficient alternator speed even during low idling. Has been done. However, when the diameter of the auxiliary pulley is reduced, the rotation speed of the alternator increases in proportion to the reduction ratio of the pulley diameter not only when idling but also when the engine rotates at high speed. The alternator not only saturates the power generation efficiency when the rotation speed increases beyond a certain level and is inefficient, but also increases the cost because the rotating elements such as the rotating shaft, pulleys, and bearings must be compatible with high-speed rotation. There is a problem that leads to

  It is an object of the present invention to effectively prevent an auxiliary machine rotation speed from becoming excessive at the time of engine high speed rotation even when the diameter of the auxiliary machine pulley is reduced due to low idling or the like. An object of the present invention is to provide a pulley unit that can contribute to weight reduction of elements.

Means for Solving the Problems and Effects of the Invention

In order to solve the above problems, the pulley unit of the present invention is:
In a pulley unit comprising a pulley, a rotating shaft, and a one-way clutch mechanism interposed between the pulley and the rotating shaft,
One-way clutch mechanism
An annular driving wheel fixed to the pulley and rotating integrally with the pulley;
A driven wheel that has a cam surface whose rotation radius changes along the circumferential direction so as to form a wedge-shaped space with the driving wheel, is fixed to the rotating shaft, and rotates integrally with the rotating shaft;
When the rotational speed of the driving wheel is lower than the rotational speed of the driven wheel, switching between the locked state that is arranged in the wedge-shaped space and is bitten in the wedge-shaped space and the unlocked state in which the biting is released, A wedge member in an unlocked state in which the bite is released in the wedge-shaped space;
When the wedge member is in a locked state and the driven wheel is rotating following the driving wheel, a transition is made from a normal rotation state where the rotation speed of the driving wheel is less than a predetermined level to a high speed rotation state exceeding the level. Accordingly, a centrifugal speed limiter mechanism that forcibly moves the wedge member from the lockable position to the non-lockable position by the rotational centrifugal force,
It is characterized by providing.

  According to the present invention, since the centrifugal speed limiter mechanism is provided in the one-way clutch mechanism incorporated in the pulley unit, for example, when the engine on the driving side rotates at a speed higher than a certain level, the operation of the centrifugal speed limiter mechanism As a result, the one-way clutch mechanism is brought into a non-lockable position (unlocked state), and transmission of rotational torque to the rotation shaft (auxiliary device rotation shaft or the like) can be interrupted. Thereby, it is possible to effectively prevent the auxiliary machine rotation speed from becoming excessive at the time of high-speed rotation of the engine, and thus it is possible to reduce the size and weight of the auxiliary element-side rotating element. This is particularly effective when the accessory pulley has a reduced diameter due to low idling or the like.

  In the pulley unit of the present invention, the centrifugal speed limiter mechanism can include a centrifugal lock return means for returning the wedge member from the non-lockable position to the lockable position when the high-speed rotation state shifts to the normal rotation state. Even if the one-way clutch mechanism is unlocked due to the operation of the centrifugal speed limiter mechanism, if the accessory rotation speed decreases, the one-way clutch mechanism is returned to the locked state again by the centrifugal lock return means, and the rotation speed The one-way clutch mechanism as the difference absorbing mechanism can be operated again without any problem.

  The one-way clutch mechanism has an elastic biasing member that biases the wedge member toward the lockable position side in the circumferential direction, and when the driving rotation speed of the driving wheel is lower than the inertia rotation speed of the driven wheel, The wedge member may transition from the locked state to the unlocked state while receiving the elastic force of the elastic biasing member. In this case, in the centrifugal speed limiter mechanism described above, the wedge member is forcibly moved to the non-lockable position when the component in the moving direction of the rotational centrifugal force to the non-lockable position overcomes the elastic biasing force of the elastic biasing member and increases. The elastic urging member can also be used as the centrifugal lock return means. Thus, by using the elastic member of the one-way clutch mechanism also for releasing the limiter, the number of parts can be reduced and the pulley unit can be configured at a lower cost.

  In the one-way clutch mechanism, a cylindrical surface that forms the raceway surface of the wedge member is formed on the outer peripheral surface of the inner ring, and the inner peripheral surface of the outer ring can be configured as a cam surface. Since the direction of the centrifugal force acting on the wedge member during high-speed rotation is outward in the radial direction, the clutch rolling element can be smoothly moved to the non-lockable position by forming a cam surface on the inner peripheral surface of the outer ring.

  Further, the driving wheel can be configured as an inner ring of a one-way clutch mechanism, and the driven wheel can be configured as an outer ring of a one-way clutch mechanism. Thereby, since the inner ring | wheel of a one-way clutch mechanism turns into a driving | running | working side, a limiter can be applied on the basis of the rotational speed of the auxiliary machine side. For example, when the auxiliary machine is an alternator, it is possible to effectively prevent an excessive rotation state in which power generation efficiency is saturated.

  In this case, an outer ring connecting portion for connecting the outer ring on the first end surface side in the axial direction so as to be integrally rotatable in the radial direction with respect to the auxiliary machine rotation shaft, and an outer ring axial position on the second end surface side of the outer ring. And the inner ring | wheel connection part which connects the 2nd end surface in the axial direction of an inner ring | wheel and a pulley so that integral rotation is possible in a radial direction can be provided. Usually, in the pulley unit on the auxiliary machine side, the correspondence between the inner ring and the outer ring of the one-way clutch mechanism inserted between the pulley and the auxiliary machine rotation shaft is such that the outer ring is the driving side and the inner ring is the driven side. However, by adopting the outer ring connecting portion and the inner ring connecting portion having the above-described configuration, the corresponding relationship can be reversed, and the inner ring can be compared with the positional relationship between the auxiliary machine rotation shaft and the pulley to be attached to the outside. Can be the driving side and the outer ring can be the driven side. As a result, the inner and outer rings, the pulley, and the auxiliary machine rotation shaft can be reasonably assembled in the above positional relationship while avoiding mutual interference.

  Specifically, in the axial direction, the side on which the one-way clutch mechanism of the auxiliary machine rotation shaft is attached is the front side, the outer ring connecting part is integrated with the rear end face of the outer ring, and the inner ring connecting part is integrated with the front end face of the outer ring. Can be configured. Thereby, both the inner ring | wheel with which the outer ring | wheel and the pulley were integrated can be easily assembled | attached from the front end side of an auxiliary machinery rotating shaft.

  Next, the cam surface formed on the inner peripheral surface of the outer ring is formed as a guide slope having a configuration in which the radial distance from the cam surface to the outer ring rotation axis continuously increases toward the downstream side in the circumferential direction. can do. In this case, the wedge-shaped space is located between the cylindrical surface of the inner ring and the guide inclined surface of the outer ring, and the lockable position in a form that is closer to the rotation leading side end in the circumferential direction than the outer diameter of the wedge member. Unlockable positions that are wider than the outer diameter on the downstream side of the lockable position can be formed. In this way, in the high-speed rotation state, the wedge member locks over the elastic urging force of the elastic urging member by the induced component of the centrifugal force acting on the wedge member along the guide slope to the downstream side. Can move to the impossible position. That is, by configuring the cam surface as a guide slope, the function of the centrifugal speed limiter mechanism can be realized very simply. The inner peripheral surface of the outer ring can be formed in a serrated shape in which a plurality of guide slopes are formed in the circumferential direction. By forming a plurality of guide slopes on the inner peripheral surface of the outer ring in a serrated shape, a centrifugal speed limiter function can be given to each wedge member, and a more reliable operation can be secured.

  Hereinafter, embodiments of the pulley unit of the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal sectional view showing an example of a pulley unit according to an embodiment of the present invention, FIG. 2 is a sectional view taken along line AA of a one-way clutch mechanism used in the pulley unit, FIG. 3 and FIG. B) is an enlarged view corresponding to the C section.

  As shown in FIG. 1, the pulley unit 100 is attached to auxiliary machines (not shown), such as an alternator, a compressor, and a wash pump. The rotational torque of the driving side rotation shaft on the rotation input side from an engine (not shown) is an auxiliary pulley (hereinafter simply referred to as a pulley) concentrically attached to an auxiliary rotation shaft (hereinafter also referred to as a rotation shaft) 2. ) 1 is transmitted by the belt B and is transmitted from the pulley 1 through the one-way clutch mechanism 3 to the rotating shaft 2 on the driven side.

  The pulley unit 100 is a transmission path from the pulley 1 to the rotary shaft 2 and is a roller-type one-way clutch disposed in an axial direction central portion of the annular space in the annular space formed between the two. Mechanism 3 and deep groove ball bearings (hereinafter also simply referred to as bearings) 4 and 4 (rolling bearings) respectively disposed on both sides in the axial direction of the one-way clutch mechanism 3. It has a function of mainly supporting a radial load acting on the one-way clutch mechanism 3.

  Each bearing 4 includes an inner ring 41, an outer ring 42, a plurality of balls 43 (rolling elements), and a corrugated cage 44. In the illustrated bearing 4, a seal 45 is attached only to the outer end side in the axial direction between the inner and outer rings 41, 42. The seal 45 is fitted into one seal mounting groove 42 a of the outer ring 42, and its lip is in contact with the inner ring 41. The cage 44 has a structure in which pockets 44a that are opened in one axial direction are provided at several circumferential positions of the annular portion, and the basic configuration is generally known. The cage 44 is formed of a pressed steel plate such as SPCC. Further, in order to conceal the seal 45 of the bearing 4 from the outside on the end face of the bearing 4 on the front side (left side in the figure), the side where the pulley 1 is attached to the rotary shaft 2 in the axial direction is the front side. 7 is attached. In addition, you may use a double row ball bearing for the bearings 4 and 4, respectively.

  Next, as shown in FIG. 2, the one-way clutch mechanism 3 is disposed concentrically with an inner ring 32 that is fixed to the pulley 1 and is an annular driving wheel that rotates integrally with the pulley 1, and the inner ring 32. An outer ring 31 which is a driven wheel fixed to the rotating shaft 2 and rotates integrally with the rotating shaft 2, and a radial clutch rolling element housing space (wedge-shaped space) K formed between the inner ring 32 and the outer ring 31. And a clutch rolling element (wedge member) 33. Further, in a state where the clutch rolling element 33 is in the lockable position LP (see FIG. 4A) and the outer ring 31 is rotating following the inner ring 32, the rotational speed of the inner ring 32 is less than a predetermined level. With the transition from the normal rotation state to the high-speed rotation state exceeding the level, the clutch rolling element 33 is forcibly moved from the lockable position LP to the lock impossible position ULP (see FIG. 4B) by the rotational centrifugal force. A centrifugal speed limiter mechanism 30 is provided.

  As shown in FIG. 3, in the lockable position LP (see FIG. 4A), the clutch rolling element 33 is engaged between the inner ring 32 and the outer ring 31 so as to engage with the clutch, thereby moving from the driving wheel to the driven wheel. It has a switching function between a locked state that allows rotational torque transmission to and an unlocked state (free state) that releases clutch engagement and prevents rotational torque transmission, and is arranged to be able to roll in the circumferential direction, When the driving rotational speed of the inner ring 32 falls below the inertial rotational speed of the outer ring 31, the locked state is shifted to the unlocked state.

  Specifically, the one-way clutch mechanism 3 elastically biases the clutch rolling element 33 in the circumferential direction toward the rotation leading direction (counterclockwise direction) indicated by an arrow in the drawing, that is, the side to be locked. It has the member 35 (it is comprised with the coil spring in this embodiment: Hereinafter, it is also called the coil spring 35). When the driving rotational speed of the inner ring 32 falls below the inertial rotational speed of the outer ring 31 (when the inner ring 32 apparently rotates in the clockwise direction), the clutch rolling element 33 that has been engaged is elastically biased 35. While receiving the elastic force, the biting is released in the opposite direction (clockwise) to the arrow in the figure, and the locked state is shifted to the unlocked state. The coil spring 35 is a centrifugal lock return means for returning the clutch rolling element 33 from the unlockable position ULP to the lockable position LP when the centrifugal speed limiter mechanism 30 shifts from the high speed rotation state to the normal rotation state. (See FIG. 4).

  Returning to FIG. 1, the pulley unit 100 includes a cylindrical outer ring support sleeve 22 that is coaxially disposed on the rotation shaft 2 and supports the outer ring 31, and the outer ring support sleeve 22 and the rotation shaft 2 are connected to each other. A plate-shaped outer ring connecting portion 21 integrated with the rear end surface of the support sleeve 22, a cylindrical inner ring support sleeve 12 that supports the inner ring 32 inside the outer ring support sleeve 22, the inner ring support sleeve 12 and the pulley 1. And a plate-like inner ring connecting portion 11 integrated with the front end surface of the inner ring supporting sleeve 12.

  Specifically, an outer ring coupling portion 21 is formed that couples the outer ring 31 to be a driven wheel on the first end surface (rear side end surface; right side in the drawing) 31b side in the axial direction so as to be integrally rotatable with the rotary shaft 2 in the radial direction. ing. Further, the pulley 1 is located on the second end surface (front end surface: left side in the drawing) 31c side of the outer ring 31 on the outer side in the axial direction of the outer ring 31 and on the second end surface 32c side in the axial direction of the inner ring 32 serving as a driving wheel. And an inner ring connecting portion 11 that is connected so as to be integrally rotatable in the radial direction. In the axial direction, the side on which the pulley 1 (one-way clutch mechanism 3) of the rotating shaft 2 is attached will be referred to as the front side, and the opposite side will be described as the rear side.

  The outer ring connecting portion 22 is integrated with the rear end surface of the cylindrical outer ring support sleeve 21 and is formed in a plate shape that closes the opening on the outside light end surface side. The outer ring 31 serving as a driven wheel is located in the outer ring support sleeve 21. It is relatively press-fitted coaxially. On the other hand, the inner ring connecting portion 11 is integrated with the front end surface of the inner ring support sleeve 12 and is formed in a plate shape that closes an annular opening formed between the pulley 1 and the inner ring support sleeve 12. A cylindrical inner ring support sleeve 12 is relatively press-fitted coaxially inside the inner ring 32. As a result, the outer ring connecting portion 21 is integrated at the rear side end surface of the outer ring 31 via the outer ring support sleeve 22, and the inner ring connecting portion 11 is integrated at the front side end surface of the inner ring 32 via the inner ring supporting sleeve 12. . In the one-way clutch mechanism 3, the inner ring 32 is configured as a driving wheel and the outer ring 31 is configured as a driven wheel by the outer ring connecting portion 21, the outer ring supporting sleeve 22, the inner ring connecting portion 11, and the inner ring supporting sleeve 12 as described above. It becomes.

  In the plate-like outer ring connecting portion 21, a shaft insertion hole 21a into which the tip end portion of the rotary shaft 2 is inserted in a protruding form from the rear side is formed in a portion located inside the inner ring supporting sleeve 12 in a penetrating manner. Has been. Then, the shaft 2 is fastened to the outer ring connecting portion 21 by the shaft fixing nut 2a being screwed into the female screw portion formed on the outer peripheral surface of the distal end portion of the rotating shaft 2 protruding from the shaft insertion hole 21a. . A bush 6 is interposed between the pulley 1 and the outer ring support sleeve 22.

  Next, as shown in FIG. 2, in the one-way clutch mechanism 3, a space formed between the cylindrical surface 32 a of the inner ring 32 and the guide slope 31 a of the outer ring 31 is a clutch rolling element accommodation space K. . The clutch rolling element housing space K has a lockable position LP at the end of the rotation leading side in the circumferential direction that is narrower than the outer diameter of the clutch rolling element 33 on the downstream side of the lockable position LP. A wedge-shaped space (hereinafter, the clutch rolling element housing space K is also referred to as a wedge-shaped space K) in which unlockable positions ULP each having a wider interval than the outer diameter are formed.

  As shown in FIG. 6, a cam surface 31 a whose rotational radius changes along the circumferential direction is formed on the inner peripheral surface of the outer ring 31. A cylindrical surface 32 a that forms a raceway surface of the clutch rolling element 33 is formed on the outer peripheral surface of the inner ring 32. The cam surface 31a on the outer ring 31 side is a guide slope having a configuration in which a radial distance L from the cam surface 31a to the outer ring rotation axis O continuously increases toward the downstream side in the circumferential direction (hereinafter referred to as “the guide slope”). The cam surface 31a is also referred to as a guide slope 31a).

  FIG. 5 is a perspective view of the outer ring 31 and the cage 34. As shown in the drawing, the inner peripheral surface of the outer ring 31 is formed in a serrated shape in which a plurality of guide inclined surfaces 31a are formed in the circumferential direction. An annular retainer 34 having the same outer peripheral surface shape as the inner peripheral surface shape of the outer ring 31 is fitted into the outer ring 31. The retainer 34 is provided with a plurality of window-like pocket portions P for accommodating the clutch rolling elements 33 in such a manner that the guide slopes 31a of the outer ring 31 face each other and penetrate in the radial direction. The clutch rolling element 33 is held by the pocket portion P against the serrated inner peripheral surface of the outer ring 31. Then, the inner edge on the rotation leading side in the circumferential direction of each pocket portion is fitted and arranged so as to engage with the stepped surfaces formed at the boundary positions of the guide slopes 31a adjacent to each other on the serrated inner peripheral surface. Has been. A spring in which a proximal end side of a coil spring 35 constituting an elastic urging member is mounted in an external fitting manner in each pocket portion P of the cage 34 so as to protrude in the circumferential direction from an inner edge on the downstream side in the circumferential direction. A mounting portion 36 is formed to protrude.

  The outline of the operation of the centrifugal speed limiter mechanism 30 is as follows. That is, as shown in FIG. 4 (A), in a state where the clutch rolling element 33 is in the lock position LP and the outer ring 31 follows and rotates with the rotation of the inner ring 32 (normal rotation state; locked state), A rotational centrifugal force F that presses itself against the guide slope 31a is acting on the moving body 33. Each guide slope 31a is different in inclination angle from each side of the virtual regular octagon 40 (see FIG. 6) obtained by connecting the radially outer vertex positions thereof. As a result, as the inner ring 32 rotates, a centrifugal component force (moving direction component force) f that guides the clutch rolling element 33 pressed onto the guide inclined surface 31a by the centrifugal force to the subsequent side of the rotation acts.

  With the transition from the normal rotation state to the high speed rotation state, as shown in FIG. 4B, the centrifugal component force f (rotational centrifugal force F) includes the frictional force in the locked state and the elastic biasing force of the coil spring 35. By overcoming and increasing (the force opposite to the centrifugal component force f), the clutch rolling element 33 is forcibly moved to the unlockable position ULP, and the rotational torque transmission is interrupted (unlocked state). The speed limiter is applied.

  If the clutch rolling element 33 moves to the unlockable position ULP, the outer ring 31 enters a free state and continues to rotate due to inertia. However, since the rotational torque is not transmitted from the inner ring 32, the rotational speed gradually decreases. As a result, the high-speed rotation state shifts to the normal rotation state again. Then, the rotational centrifugal force F decreases, and the elastic biasing force of the coil spring 35 overcomes the centrifugal component force f to return the clutch rolling element 33 to the lockable position LP (see FIG. 4A). As a result, the speed limiter is automatically canceled.

  Next, a modified example of the pulley unit of the present invention will be described with reference to FIG. 7 (note that there are many common points with the embodiment of FIG. 1, mainly the differences will be described, and overlapping parts will be described) The same reference numerals are given and detailed description is omitted). In the pulley unit 100A, an outer ring connecting portion that connects an outer ring 31 that is a driven wheel so as to be integrally rotatable in the radial direction with respect to the rotary shaft 2 on the second end face (front end face; left side in the figure) 31c side in the axial direction. 210 is formed. The pulley 1 is positioned on the outer side in the axial direction of the outer ring 31 on the first end surface (rear side end surface: right side in the drawing) 31b side of the outer ring 31 and on the first end surface 32b side in the axial direction of the inner ring 32 serving as a driving wheel. And an inner ring connecting portion 110 that is connected so as to be integrally rotatable in the radial direction.

  The outer ring coupling portion 220 is integrated with the front end surface of the cylindrical outer ring support sleeve 21 and is formed in a plate shape that closes the opening on the outer light end surface side, and the outer ring 31 serving as a driven wheel is placed in the outer ring support sleeve 21. The inner ring connecting portion 110 is relatively press-fitted coaxially, and is integrated with the rear end surface of the inner ring support sleeve 12, and an annular opening formed between the pulley 1 and the inner ring support sleeve 12. A cylindrical inner ring support sleeve 12 is relatively press-fitted coaxially inside an inner ring 32 serving as a driving wheel.

  Also in the above configuration, the one-way clutch mechanism 3A can be configured with the inner ring 32 as a driving wheel and the outer ring 31 as a driven wheel, as in the above embodiment, and the same centrifugal speed limiter mechanism as that of FIG. 1 can be enjoyed.

The longitudinal section showing an example of the pulley unit concerning the embodiment of the present invention. FIG. 2 is a cross-sectional view of the one-way clutch mechanism used in the pulley unit in FIG. The enlarged view corresponding to the C section of FIG. The enlarged view corresponding to the C section of FIG. The perspective view of an outer ring | wheel and a holder | retainer. The figure which shows an inner ring | wheel and an outer ring | wheel with a virtual regular octagon. The longitudinal cross-sectional view which shows an example of the pulley unit which concerns on another embodiment of this invention.

Explanation of symbols

1 Pulley (auxiliary pulley)
2 Rotating shaft (Auxiliary machinery rotating shaft)
3 One-way clutch mechanism 11, 110 Inner ring connecting portion 12 Inner ring supporting sleeve 21, 210 Outer ring connecting portion 22 Outer ring supporting sleeve 30 Centrifugal speed limiter mechanism 31 Outer ring (driven wheel)
31a Cam surface (guide slope)
32 Inner ring (motor wheel)
32a Cylindrical surface (track surface)
33 Roller (Wedge member; Clutch rolling element)
34 Cage 35 Compression coil spring (centrifugal lock return means; elastic biasing member)
36 Spring mounting part B Belt K Clutch rolling element accommodation space (wedge-shaped space)
P Pocket part 100, 100A Pulley unit

Claims (5)

In a pulley unit comprising a pulley, a rotating shaft, and a one-way clutch mechanism interposed between the pulley and the rotating shaft,
The one-way clutch mechanism is
An annular driving wheel fixed to the pulley and rotating integrally with the pulley;
A driven wheel that has a cam surface with a radius of rotation changing along the circumferential direction so as to form a wedge-shaped space between the driven wheel and is fixed to the rotating shaft and rotates integrally with the rotating shaft;
Switching between a locked state that is disposed in the wedge-shaped space and is engaged in the wedge-shaped space and an unlocked state in which the engagement is released, and the rotational speed of the driving wheel is lower than the rotational speed of the driven wheel. A wedge member that is in an unlocked state in which the biting is released in the wedge-shaped space,
In a state where the wedge member is in the locked state and the driven wheel is rotating following the driving wheel, the rotational speed of the driving wheel exceeds the level from a normal rotation state where the rotational speed is less than a predetermined level. A centrifugal speed limiter mechanism for forcibly moving the wedge member from a lockable position to a non-lockable position by the rotational centrifugal force as it shifts to a high-speed rotation state;
A pulley unit comprising:   The said centrifugal speed limiter mechanism is equipped with the centrifugal lock reset means which returns the said wedge member from the said lock impossible position to the said lockable position, when it transfers to the said normal rotation state from the said high speed rotation state. Pulley unit. The driving wheel is configured as an inner ring of the one-way clutch mechanism, and the driven wheel is configured as an outer ring of the one-way clutch mechanism;
An outer ring connecting portion for connecting the outer ring so as to be integrally rotatable in the radial direction with respect to the rotation shaft on the first end surface side in the axial direction;
An inner ring connecting portion that is positioned on the outer side in the axial direction of the outer ring on the second end surface side of the outer ring, and connects the second end surface in the axial direction of the inner ring and the pulley so as to be integrally rotatable in a radial direction;
The pulley unit according to claim 1, comprising:   In the axial direction, the outer ring connecting portion is integrated with the rear end surface of the outer ring, and the inner ring connecting portion is connected to the front end surface of the outer ring, with the side on which the one-way clutch mechanism of the rotating shaft is attached as the front side. The pulley unit according to claim 3, which is integrated. The cam surface formed on the inner peripheral surface of the outer ring is formed as a guide slope in a form in which the radial distance from the cam surface to the outer ring rotation axis continuously increases toward the downstream side in the circumferential direction. And
The wedge-shaped space between the cylindrical surface of the inner ring and the guide slope of the outer ring has the lockable position at a position closer to the rotation leading side end in the circumferential direction than the outer diameter of the wedge member. Each of the non-lockable positions that are wider than the outer diameter on the downstream side of the lock from the lockable position,
In the high-speed rotation state, the wedge member overcomes the elastic biasing force of the centrifugal lock return means by the induced component force of the centrifugal force acting on the wedge member along the guide slope to the downstream side of the rotation. The pulley unit according to claim 2, wherein the pulley unit moves to the non-lockable position.

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