JP5718004B2 - Clutch unit - Google Patents

Description

  The present invention relates to a clutch unit, and more particularly to a clutch unit capable of switching between a forward rotation lock state and a reverse rotation lock state.

  For example, in FIGS. 1 to 4 of Patent Document 1, torque transmission is performed by locking an engagement element, an input portion, and an output portion with a wedge engagement via a cam surface and locking in a forward rotation lock state or a reverse rotation lock state. The clutch unit to perform is shown. The “forward rotation locked state” means a state in which the input torque in the forward rotation direction from the input unit can be transmitted to the output unit (that is, the reverse input torque in the reverse rotation direction from the output unit can be transmitted to the input unit. State). On the other hand, the “reverse rotation locked state” means a state in which the input torque in the reverse rotation direction from the input unit can be transmitted to the output unit (that is, the reverse input torque in the normal rotation direction from the output unit can be transmitted to the input unit. (The same applies to the following description).

  Such a clutch unit is applied to, for example, a regenerative power generation system for a battery-assisted bicycle. Specifically, during normal driving of the bicycle, the input torque in the forward rotation direction from the motor is transmitted to the wheel rotation shaft via the clutch unit in the forward rotation lock state, so that when the driver depresses the pedal, Reduce the load. On the other hand, when the bicycle is decelerated, the reverse input torque in the forward rotation direction from the rotating shaft of the wheel is transmitted to the motor through the clutch unit in the reverse rotation lock state, and the motor is rotated, so that the generated electric power is transferred to the battery. It is charged.

  In the clutch unit as described above, if the forward rotation locked state is suddenly switched to the reverse rotation locked state, an impact at the time of switching the locked state is transmitted to the motor, and the motor may be damaged. In order to avoid such a situation, FIGS. 7 to 9 of Patent Document 1 show a torque limiter mechanism that slides the engagement element and the input portion to release the engagement state when a large torque is applied in the reverse rotation locked state. A clutch unit with is shown.

JP 2004-270877 A

  However, when the torque limiter mechanism as described above is provided, the following problems occur. First, since slip occurs between the engaging element and the cam surface, there is a concern that the cam surface and the engaging element may be deteriorated or damaged due to shearing or heat generation. Second, in order to provide the torque limiter mechanism, it is necessary to provide a stopper portion on the cam surface that increases the cam angle (the tangent intersection angle at the contact point between the engagement element and the input portion and the output portion). Is complicated and expensive to manufacture. Thirdly, the set torque (torque value that causes slippage) of the torque limiter mechanism is set according to the shape of the cam surface and the outer diameter of the engagement element. Man-hours increase.

  The problem to be solved by the present invention is to provide a clutch unit that can alleviate an impact when the locked state is suddenly switched without providing a torque limiter mechanism as described above.

In order to solve the above problems, the present invention is disposed between an input unit to which a torque in a positive rotation direction is input from a motor , an output unit to which the torque is output, and the input unit and the output unit. A plurality of engagement elements, a cage that holds the plurality of engagement elements at a predetermined interval, and the input unit and the output unit are wedge-engaged with the plurality of engagement units, and the input unit to the output unit. the normal rotation locked state to transmit the forward rotation direction of the torque or, a plurality of cam surfaces to lock the reverse rotation lock state of transmitting forward rotational direction of the torque to the input unit from the output unit, the output A regenerative power generation system that generates power by rotating the motor by transmitting the rotation of the output unit to the input unit by locking the input unit and the output unit in a reverse rotation locked state with the unit rotated. Contact to the clutch unit of use Te, wherein the input unit, and having a damper, and a plurality of members connected to transmit the torque through the damper.

  In this way, by providing a damper in the input part or the output part and connecting a plurality of members via this damper so as to be able to transmit torque, even when the locked state is suddenly switched, the damper can absorb the impact. Therefore, the impact applied to the rotational drive source such as a motor can be reduced.

For example, when a damper is provided between the circumferential directions of a plurality of members, the damper receives a compressive force or a tensile force due to relative rotation of the plurality of members during torque transmission. On the other hand, when both axial ends of the damper are fixed to the plurality of members, the damper receives a shearing force in the circumferential direction due to relative rotation of the plurality of members during torque transmission. In general, the amount of deformation of a damper increases when it receives a shearing force rather than a compressive or tensile force. Therefore, by applying a shearing force to the damper as in the latter case, a higher shock absorbing capacity can be obtained. It is done.

  In this case, if the concave portion is provided in the middle portion in the axial direction of the damper, the thickness of the damper is locally reduced, so that the damper is easily deformed by the shearing force, and the shock absorbing ability is further enhanced.

  In the fixing part between the plurality of members and the damper, by providing a protruding part protruding in the axial direction on one side and providing a fitting hole in which the protruding part fits on the other side, both can be engaged in the rotational direction. . In this case, the shape of the member in which the protruding portion or the fitting hole is formed is complicated, but if this member is molded with resin including the protruding portion or the fitting hole, the manufacturing can be facilitated.

  A damper can be provided in an input part, for example. In this case, the input unit includes an outer ring having an inner peripheral surface that comes into contact with the engagement element, a fixed portion fixed to the outer peripheral surface of the outer ring, a fixing member having a flange extending from the fixed portion to the outer diameter, And a rotation transmission member facing the axial direction, and a damper may be provided between the flange portion of the fixing member and the rotation transmission member in the axial direction.

  At this time, if the collar part is deformed in the axial direction due to the deformation of the damper, the input part (the collar part or the damper) and the cage may interfere with each other. Therefore, it is preferable that the flange portion and the cage are opposed to each other via an axial gap, and the axial gap is set so that the cage and the input portion do not interfere with each other due to the deformation of the damper during torque transmission.

  The damper is preferably made of a material having a large allowable width for elastic deformation, and can be made of rubber, for example.

  Switching from the forward rotation lock state to the reverse rotation lock state can be performed, for example, by braking the rotation of the cage.

  The clutch unit as described above can be suitably incorporated in a regenerative power generation system having a motor connected to the input unit and a load side connected to the output unit.

  As described above, according to the clutch unit of the present invention, the shock when the forward rotation locked state and the reverse rotation locked state are suddenly switched can be absorbed by the damper, so that a torque limiter mechanism is not provided. The possibility of damaging the motor can be avoided.

It is sectional drawing of the axial direction of the clutch unit which concerns on one Embodiment of this invention. It is a disassembled perspective view of the input part of the said clutch unit, a damper, and an input gear. It is sectional drawing of the said clutch unit of a normal rotation locked state of the orthogonal axis direction. FIG. 3 is a cross-sectional view in the direction perpendicular to the axis of the clutch unit in a reverse rotation locked state. It is a figure which shows the structural example of the drive part of the battery-assisted bicycle incorporating the said clutch unit, (a) A figure is the side view, (b) A figure is the top view.

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

  As shown in FIG. 1, a clutch unit 1 according to an embodiment of the present invention includes an input unit A that receives a torque in a positive rotation direction from a rotational drive source (not shown), and an output unit B that outputs the torque. And a plurality of cylindrical rollers 4 as engagement elements disposed between the input part A and the output part B, and a cage 5 that equally distributes the rollers 4 at a plurality of locations in the circumferential direction. . At least one of the input part A and the output part B is provided with a damper. In the present embodiment, the input part A is provided with a damper 9.

  As shown in FIG. 2, the input part A includes an outer ring 2, a fixing member 3, a damper 9, and an input gear 7 as a rotation transmission member. As shown in FIG. 1, the output unit B includes an inner ring 8 and an output shaft 11.

  The outer ring 2 is formed of a metal, for example, and forms a ring body having a cylindrical inner peripheral surface 2a (see FIG. 2). An inner peripheral surface 2 a of the outer ring 2 is in contact with the roller 4, and a male spline 2 b is formed on the outer peripheral surface of the outer ring 2.

  The fixing member 3 is, for example, a metal press-molded product, and a cylindrical fixing portion 3a fixed to the outer peripheral surface of the outer ring 2 and a flange portion 3b extending from one end in the axial direction of the fixing portion 3a to the outer diameter are integrated. The cross section is L-shaped (see FIG. 1). As shown in FIG. 2, a female spline 3a1 that fits with the male spline 2b on the outer periphery of the outer ring 2 is formed on the inner periphery of the fixed portion 3a. The flange 3b has a hollow disk shape, and a plurality of fitting holes 3b1 are formed at equal intervals in the circumferential direction. The fitting hole 3b1 penetrates the flange 3b.

  The input gear 7 includes a cylindrical portion 7a disposed on the outer periphery of the outer ring 2 and the fixing member 3, and an extending portion 7b extending from the cylindrical portion 7a to the inner diameter (see FIG. 1). A tooth surface 7a1 is formed on the outer periphery of the cylindrical portion 7a as shown in FIG. 2 (only a part of the tooth surface 7a1 is shown in FIG. 2). A plurality of fitting holes 7b1 are provided at equal intervals in the circumferential direction on the surface of the extending portion 7b that faces the flange portion 3b of the fixing member 3 in the axial direction. The input gear 7 is integrally molded with resin including the fitting hole 7b1.

  The damper 9 is made of a material having a large allowable width for elastic deformation, and is made of rubber in this embodiment. The damper 9 forms a ring body as shown in FIG. 2, and a plurality of projecting portions 9a and 9b projecting in the axial direction are provided at equal intervals in the circumferential direction on both end surfaces in the axial direction. A recess is formed in the axially intermediate portion of the damper 9, and in the illustrated example, annular grooves 9c and 9d extending in the circumferential direction are formed in the axially intermediate portion of the outer peripheral surface and inner peripheral surface of the damper 9 over the entire periphery.

  A plurality of members constituting the input part A are connected via the damper 9 so that torque can be transmitted. In the present embodiment, the fixing member 3 and the input gear 7 are connected via the damper 9, and the relative displacement of each other is allowed by the deformation of the damper 9. The fixed member 3 and the input gear 7 are connected only via the damper 9. The damper 9 is provided between the flange portion 3 b of the fixing member 3 and the input gear 7 in the axial direction. Specifically, the protruding portions 9a and 9b of the damper 9 are fitted into the fitting holes 3b1 and 7b1 formed in the flange portion 3b of the fixing member 3 and the extending portion 7b of the input gear 7 (see FIG. 1). Thereby, the fitting holes 3b1 and 7b1 and the projecting portions 9a and 9b are engaged in both forward and reverse rotational directions, and the fixing member 3 and the input gear 7 are connected via the damper 9 so that torque can be transmitted.

  The inner ring 8 is formed of a metal, for example, and forms a ring body arranged on the inner periphery of the outer ring 2. An output shaft 11 is press-fitted and fixed to the inner peripheral surface 8a of the inner ring 8 (see FIG. 1). As shown in FIG. 3, a plurality of cam surfaces 12 that come into contact with the roller 4 are formed on the outer peripheral surface 8 b of the inner ring 8. In the illustrated example, the outer peripheral surface 8b of the inner ring 8 is formed in a regular polygonal cross section (regular dodecagonal cross section), and each plane constituting the outer peripheral surface 8b of the regular polygonal section functions as the cam surface 12. One roller 4 is arranged on each cam surface 12. Between the cam surface 12 and the cylindrical inner peripheral surface 2a of the outer ring 2, a wedge gap 13 is formed in which the radial width is reduced in both the forward and reverse rotational directions.

  The radial width at the central portion in the circumferential direction of the wedge gap 13 is set slightly larger than the diameter of the roller 4. As a result, the roller 4 disposed at the center in the circumferential direction of the wedge gap 13 can rotate. As shown in FIG. 3, the outer ring 2 is moved in a state where the roller 4 moves in the forward rotation direction (clockwise direction in the drawing) with respect to the inner ring 8 and is pushed into the narrow portion of the wedge gap 13 on the forward rotation direction side. When the input torque in the forward rotation direction is input to the roller 4, the roller 4 is wedge-engaged with the outer peripheral surface 8b (cam surface 12) of the inner ring 8 and the cylindrical inner peripheral surface 2a of the outer ring 2, and the outer ring 2 and the inner ring 8 are engaged with each other. Locked (forward rotation lock state). On the other hand, as shown in FIG. 4, the roller 4 moves in the reverse rotation direction (counterclockwise direction in the drawing) with respect to the inner ring 8 and is pushed into the narrow portion on the reverse rotation direction side of the wedge gap 13. When a reverse input torque in the forward rotation direction is input to the inner ring 8, the rollers are wedge-engaged with the outer peripheral surface 8b (cam surface 12) of the inner ring 8 and the cylindrical inner peripheral surface 2a of the outer ring 2, and the outer ring 2 and the inner ring 8 are engaged. 8 is locked (reverse rotation lock state).

  The output shaft 11 is rotatably supported by bearings (for example, ball bearings 10a and 10b) arranged on both sides in the axial direction with the roller 4 interposed therebetween. A spline 11a is formed at the shaft end of the output shaft 11 to be coupled to an output side transmission element, for example, a sprocket so as to be able to transmit torque. In addition, the inner ring | wheel 8 and the output shaft 11 can also be integrated as needed.

  As shown in FIG. 1, the retainer 5 includes a pocket 5 a for accommodating the roller 4, and a sliding surface 5 b that slides with a shoe 14 described later. The cage 5 in the illustrated example is integrally provided with a cylindrical holding portion 51 extending in the axial direction and a flange portion 52 extending in the outer diameter direction from one axial end of the holding portion 51. Pockets 5a are formed in the holding portion 51 at equidistant positions in the circumferential direction (see FIG. 1). A sliding surface 5b is formed on the outer peripheral surface of the flange portion 52 (see FIG. 1). The gap between the pocket 5a and the outer peripheral surface of the roller 4 is set to a negative gap or a positive gap that is 1/20 or less of the roller diameter. In the case of the regular gap, it is desirable to provide a protrusion protruding in the circumferential direction on the inner surface of the pocket of the holding portion 51 to prevent the roller 4 from falling off.

  The cage 5 is rotatably supported by a slide bearing 15 with respect to the output shaft 11 so that the coaxiality with respect to the outer ring 2 and the inner ring 8 is ensured even when the sliding surface 5b and the shoe 14 are in contact with each other. The sliding bearing 15 is, for example, a ring body fitted to the outer peripheral surface of the output shaft 11, and the inner peripheral surface 5 c of the cage 5 is slidably supported by the outer peripheral surface. A retaining ring 16 is attached to the annular groove 11 b formed on the outer peripheral surface of the output shaft 11. The retaining ring 16 and the inner ring 8 sandwich the sliding bearing 15 from both sides in the axial direction, whereby the sliding bearing 15 is positioned in the axial direction with respect to the output shaft 11.

  The shoe 14 is for braking the rotation of the cage 5 and is disposed so as to oppose the sliding surface 5b of the cage 5 in the radial direction as illustrated. The shoe 14 is provided so as to be movable in the radial direction, and is normally separated from the sliding surface 5b of the cage 5 (see FIG. 1), and slides on the sliding surface 5b by moving toward the inner diameter from this state. (Not shown).

  The clutch unit 1 is provided with an elastic member 6 that urges the cage 5 in the forward rotation direction with respect to the outer ring 2. The elastic member 6 is constituted by, for example, a ring spring. The elastic member 6 is interposed between the inner ring 8 and the cage 5 by fixing one end thereof to the holding portion 51 of the cage 5 and fixing the other end to the inner ring 8. Due to the elastic force of the elastic member 6, the cage 5 is urged in the forward rotation direction with respect to the inner ring 8, and the roller 4 pushed by the cage 5 is urged toward the forward rotation direction side of the wedge gap 13. (See FIG. 3).

  Hereinafter, the function of the clutch unit having the above configuration will be described with reference to FIGS. 3 and 4.

  When both the input part A and the output part B are stationary, the cage 5 and the roller 4 are displaced in the forward rotation direction of the wedge gap 13 by the elastic force of the elastic member 6 (see FIG. 3). In this state, when the outer ring 2 is rotated by applying an input torque in the positive rotation direction (clockwise direction in FIG. 3) from the rotation driving source, the roller 4 is engaged with the outer ring 2 and the inner ring 8 and locked ( Forward rotation lock state). Thereby, the input torque in the forward rotation direction is transmitted from the outer ring 2 (input unit A) to the inner ring 8 (output unit B), and the output shaft 11 rotates in the forward rotation direction. Note that the forward rotation lock state shown in FIG. 3 can be transmitted to the outer ring 2 by applying a reverse input torque in the reverse rotation direction (counterclockwise direction) to the inner ring 8 in terms of mechanism. On the other hand, when an input torque or a reverse input torque in a direction other than this is applied, the wedge engagement between the roller 4 and the outer ring 2 and the inner ring 8 in the wedge gap is released, so that torque transmission is not performed.

  When the input of torque is stopped and the rotation of the outer ring 2 is restricted, the inner ring 8 idles due to the inertial rotational force in the forward rotation direction, and the wedge engagement between the roller 4 and the outer ring 2 and the inner ring 8 is released. When the shoe 14 is pressed against the sliding surface 5b of the retainer 5 to apply a braking force in the idling state of the inner ring 8, a rotation delay occurs in the retainer 5, and the retainer 5 rotates in reverse with respect to the inner ring 8. Rotate relative to direction. As a result, the roller 4 is released from the wedge-engaged state on the forward rotation direction side of the wedge gap 13 and is engaged in the reverse rotation direction side as shown in FIG. 4 to engage with the outer ring 2 and the inner ring 8. Locked (reverse rotation lock state). Thereby, the reverse input torque in the forward rotation direction is transmitted from the inner ring 8 to the outer ring 2, and the input portion A including the outer ring 2 rotates in the forward rotation direction. Note that the reverse rotation lock state shown in FIG. 4 can mechanically transmit the input torque in the reverse rotation direction from the outer ring 2 to the inner ring 8. On the other hand, for the input torque and the reverse input torque in other directions, the wedge engagement state is released, so that torque transmission is not performed.

  In the clutch unit 1 described above, when the forward rotation locked state and the reverse rotation locked state are suddenly switched, a large impact load may be applied to the rotational drive source connected to the input unit A. In the present invention, since the damper 9 is provided in the clutch unit 1 as described above, an impact when the locked state is switched can be absorbed by deformation of the damper 9, and damage to the rotational drive source can be prevented. In particular, by providing a damper 9 between the flange 3b of the fixing member 3 and the axial direction of the input gear 7, the damper 9 is shear-deformed in the rotational direction by relative rotation of the fixing member 3 and the input gear 7 during torque transmission. Can be made. Thereby, since the damper 9 can be deform | transformed more compared with compression and tension | tensile_strength, shock absorption capability can be improved. Furthermore, by providing a concave portion (annular grooves 9c, 9d) in the axially intermediate portion of the damper 9, the deformation of the damper 9 is promoted and the shock absorbing capacity is further enhanced. At this time, the deformation amount of the damper 9 can be adjusted by changing the depth, width, or position of the recess formed in the damper 9.

  If the damper 9 is deformed during torque transmission, the input portion A (the damper 9 or the flange 3b of the fixing member 3) facing the cage 5 in the axial direction may be displaced in the axial direction and interfere with the cage 5. . In the present embodiment, the cage 5 and the input portion A do not interfere with each other due to the deformation of the damper 9 during torque transmission in the axial gap S (see FIG. 1) formed between the cage 5 and the input portion A. It is set as follows. For this reason, the situation where the cage 5 and the input unit A interfere with each other and the relative rotation is inhibited is avoided, and the locked state can be switched smoothly.

  By arranging the clutch unit 1 described above in the torque transmission path between the motor and the load side, a regenerative power generation system can be constructed.

  That is, when the input torque from the motor is input to the input gear 7 and the output shaft 11 is connected to the load side, the motor is driven in the forward rotation locked state shown in FIG. Torque can be transmitted to drive the driven object. Then, after the motor is stopped, if the shoe 14 is pressed against the sliding surface 5b, the reverse rotation locked state shown in FIG. 4 is obtained. Therefore, by inputting the load side reverse input torque due to inertia to the inner ring 8, This reverse input torque can be input to the motor through the roller 4 and further through the input unit A so that the motor can function as a generator. During this regenerative power generation, a braking force is applied by internal friction of the motor, so that it can be used as a load-side brake mechanism.

  As a specific application of the regenerative power generation system, for example, a battery-assisted bicycle shown in FIG. 5 can be cited.

  This battery-assisted bicycle is provided with a human power drive system that transmits a pedaling force applied to the pedal 100 to the rear wheel axle 106 and a motor drive system that transmits the output of the motor 114 to the rear wheel axle 106.

  More specifically, in the human power drive system, the pedal force acting on the pedal 100 is converted into the rotational motion of the crankshaft 101 by the crank 117, and the torque is transmitted to the axle 106 of the rear wheel via the first transmission means 115a. The The first transmission means 115a includes a front sprocket 102 attached to the crankshaft 101, a rear sprocket 104a attached to the rear wheel axle 106, and a chain 103a spanned between the two sprockets 102, 104a. The The rear sprocket 104a and the axle 106 are freely connected via a known one-way clutch 119 so as to transmit torque from the rear sprocket 104a to the axle 106, but not to transmit reverse input torque from the axle 106 to the rear sprocket 104a. Has been.

  In the motor drive system, the output of the motor 114 is input to the clutch unit 1, and the output of the clutch unit 1 is further transmitted to the axle 106 of the rear wheel via the second transmission means 115b. The second transmission means 115b includes a middle sprocket 118 attached to the output shaft 11 of the clutch unit 1, a rear sprocket 104b attached to the axle 106 of the rear wheel, and a chain 103b spanned between both sprockets 118 and 104b. It consists of. The rear sprocket 104b and the axle 106 are rigidly connected so that bidirectional torque transmission is possible between them.

  In the figure, reference numeral 120 denotes a tensioner disposed on the human-powered drive chain 103a for absorbing slack. The shoe 14 shown in FIG. 1 is mechanically connected to a brake lever of a bicycle via a wire or the like, and also converts an operation state of the brake lever into an electrical signal, for example, and excites a solenoid based on this signal. It can also be linked with the brake operation by electrical means.

  The crankshaft 101 is provided with torque detecting means for detecting the shaft torque. When the torque detected by the torque detection means exceeds a set value, the motor 114 is activated and generates a torque corresponding to the shortage as auxiliary power. During traveling by the motor assist, the clutch unit 1 is in the forward rotation locked state shown in FIG. Therefore, the input torque in the forward rotation direction from the motor 114 is transmitted to the rear sprocket 104b through the path of the input gear 7, the damper 9, the fixing member 3, the outer ring 2, the roller 4, the inner ring 8, and the output shaft 11. Since this motor torque is combined with the pedal effort torque from the human drive system and the axle 106, the bicycle can be run lightly.

  When the occupant performs a brake operation, the shoe 14 is pressed against the sliding surface 5b in conjunction with this, and the lock direction of the clutch unit 1 is switched to enter the reverse rotation lock state shown in FIG. In this state, the rotational torque of the rear wheels is transmitted to the output shaft 11 of the clutch unit 1 via the rear sprocket 104b and the chain 103b that are rigidly coupled to the axle 106. With respect to this reverse input torque, the roller 4 engages in the wedge clearance in the reverse rotation direction, so the reverse input torque is output shaft 11 → inner ring 8 → roller 4 → outer ring 2 → fixing member 3 → damper 9 → input gear. 7 is input to the motor 114 via a route 7. With this torque, the motor 114 can be driven to generate regenerative power, and the regenerative current can be stored in the battery. At the same time, the power for driving the motor 114 becomes a braking force, and an assist function for brake operation is obtained (brake assist).

  By the way, generally, when the chains 103a and 103b are rotated, uneven rotation of the chains is unavoidable. In particular, when uneven rotation occurs in the chain 103b of the motor drive system, the roller 4 (FIG. 3) in the forward rotation locked state suddenly shifts to the reverse rotation locked state (FIG. 4) and changes from the motor assist state to the brake assist state. There is a risk that it may interfere with stable driving. Even in such a case, the shock caused by the switching of the lock state can be absorbed by the damper 9, so that a stable running state can be maintained.

  The present invention is not limited to the above embodiment. Hereinafter, although other embodiment of this invention is described, the same code | symbol is attached | subjected to the location which has the function similar to said embodiment, and description is abbreviate | omitted.

  In the above-described embodiment, a configuration in which the damper 9 is provided in the input unit A is shown. However, the present invention is not limited thereto, and a damper may be provided in the output unit B (not shown). Or you may provide a damper in both the input part A and the output part B (illustration omitted).

  Further, the damper 9 can transmit torque between a plurality of members (in the above embodiment, the fixing member 3 and the input gear 7) connected via the damper 9, and can provide an impact when the lock state is switched. If it is the structure which can be absorbed, it will not be restricted to said shape. For example, in the above embodiment, the damper 9 forms a ring body, but the present invention is not limited to this, and the damper 9 may be divided into a plurality of parts in the circumferential direction. The recesses (annular grooves 9c, 9d) provided in the damper 9 are not limited in shape and location as long as the damper 9 can be easily deformed. For example, the recesses are provided in a plurality of locations separated in the circumferential direction. May be. Alternatively, if a recess is not particularly necessary, this may be omitted.

  Moreover, in the said embodiment, while providing the protrusion parts 9a and 9b in the damper 9, and providing the fitting hole in the fixing member 3 and the input gear 7, conversely, the damper 9 is provided with the fitting hole. Alternatively, the fixing member 3 and the input gear 7 may be provided with protrusions, and these may be fitted.

DESCRIPTION OF SYMBOLS 1 Clutch unit 2 Outer ring 3 Fixing member 3a Fixing part 3b Eaves part 3b1 Fitting hole 4 Roller 5 Cage 6 Elastic member 7 Input gear 7b1 Fitting hole 8 Inner ring 9 Damper 9a, 9b Projection part 9c, 9d Annular groove (recess)
11 Output shaft 12 Cam surface 13 Wedge gap 14 Shoe 15 Sliding bearing A Input part B Output part

Claims (9)

An input unit that receives torque in the positive rotation direction from the motor, an output unit that outputs the torque, a plurality of engagement elements disposed between the input unit and the output unit, and the plurality of engagement elements And a forward rotation lock for transmitting torque in the forward rotation direction from the input unit to the output unit by wedge-engaging the input unit and the output unit with the plurality of engagement elements. Or a plurality of cam surfaces that are locked in a reverse rotation lock state that transmits torque in the forward rotation direction from the output unit to the input unit, and in a state where the output unit is rotated, the input unit and In the clutch unit for a regenerative power generation system that generates power by rotating the motor by transmitting the rotation of the output unit to the input unit by locking the output unit in a reverse rotation lock state,
Wherein the input unit is, it possesses a damper, and a plurality of members connected to transmit the torque through the damper,
One end of the damper in the axial direction is fixed to one member of the plurality of members, and the other end of the damper in the axial direction is fixed to another member of the plurality of members to transmit torque. A clutch unit in which a circumferential shear force is applied to the damper by relative rotation of the one member and the other member . Clutch unit according to claim 1, wherein providing the recess in the axially intermediate portion of the damper. 3. The clutch according to claim 1, wherein a fixing portion between the plurality of members and the damper is provided with a protruding portion protruding in an axial direction on one side and a fitting hole into which the protruding portion is fitted on the other side. unit. The clutch unit according to claim 3, wherein a member in which the protruding portion or the fitting hole is formed is molded with resin. An outer ring having an inner peripheral surface in contact with the engagement element; an anchoring portion fixed to the outer peripheral surface of the outer ring; and a fixing member having a flange extending from the fixing portion to an outer diameter; The clutch unit according to claim 4 , further comprising: a rotation transmission member facing the flange portion in the axial direction, wherein the damper is provided between the flange portion of the fixing member and the rotation transmission member in the axial direction. And said retainer and said flange portion are opposed via the axial clearance, claims and said input portion and said retainer by the deformation of the damper during torque transmission and setting the axial clearance so as not to interfere 5 The clutch unit described. Clutch unit according to any one of claims 1 to 6, the damper is formed of rubber. The clutch unit according to any one of claims 1 to 7 , wherein switching from the forward rotation lock state to the reverse rotation lock state is performed by braking the rotation of the cage. A regenerative power generation system comprising the clutch unit according to any one of claims 1 to 8 , a motor connected to the input unit, and a load side connected to the output unit.

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