JP2006336837A - Clutch unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact clutch unit which materializes the reduction in the surface pressure of a contact surface with a roller and the reduction in a parts count and assembling man-hour. <P>SOLUTION: A clutch unit comprises a lever side clutch part 11 equipped with an outer ring 13, an inner ring 14, a roller 15, a retainer 16, an outer ring 21 and center rings 17, 18, and with a brake side clutch part 12 which is equipped with an inner ring 14, an output shaft 22, an outer ring 21, a locking means 24, an unlocking means 14c and a torque transmission means 25 and in which the locking means 24 contains in the output shaft 22 an eccentric cam 22b having an outer diameter surface eccentric to its rotational center and in which a pair of engaging members 28a, 28b coming into surface contact with the outer diameter surface of the eccentric cam 22b and the inner diameter surface 21c of the outer ring 21 are engageably and separably interposed between the eccentric cam 22b and the outer ring 21 so as to mutually form a concave-convex circular arc shape. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention is incorporated in, for example, a seat lifter that adjusts a seat of an automobile, and transmits a rotational torque from the input side to the output side, and transmits a rotational torque from the input side to the output side and outputs the clutch. The present invention relates to a clutch unit having a clutch portion for blocking reverse input torque from the side.

  In general, in a clutch unit using an engagement element such as a roller or a ball, a clutch portion is disposed between an input side member and an output side member. This clutch portion is composed of the input side member and the output side member described above. The configuration is such that input torque transmission / interruption is controlled by engaging / disengaging rollers, balls, and other engaging elements between the wedge gaps formed therebetween (see, for example, Patent Document 1).

  This type of clutch unit may be used by being incorporated in, for example, an automobile seat lifter that moves a seat up and down by lever operation. In the seat lifter portion, the input side member of the clutch unit is connected to the operation lever, and the output side member is connected to a rotating member that moves the seat seat up and down, and the operation lever is operated to swing and rotate in the up and down direction. Thus, the seating surface can be adjusted by moving the seat seat up and down by transmitting the rotational torque to the output side member and rotating the rotating member. Also, when the passenger sits on the seat, even if rotational torque is applied to the output side member via the rotating member, the output side member is locked by the reverse input rotational torque so that the input side member does not rotate. It has become.

  As shown in FIG. 15, the above-described clutch unit includes a lever side clutch portion 101 provided on the input side and a brake side clutch portion 102 having a reverse input cutoff function provided on the output side.

  In the lever side clutch unit 101, the rotation torque from the outer ring 103 which is an input side member connected to the operation lever is applied to the inner ring which is the output side member via the roller 105 by the swinging rotation of the operation lever (not shown). 104 (see FIG. 11 to FIG. 13 of Patent Document 1), the brake-side clutch unit 102 receives the rotational torque from the inner ring 104 (retainer) serving as the input-side member as one inner ring 104 (retainer). It transmits to the output shaft 112 which is an output side member through the protrusion 106 provided in the part (refer FIG. 26 and FIG. 27 of patent document 1). Thereby, the seat is moved up and down by the swinging rotation of the operation lever.

On the other hand, when the occupant sits on the seat, even if rotational torque is applied to the output shaft 112, the roller 114 is engaged between the output shaft 112 and the outer ring 111, which is a stationary member, by the reverse rotational torque. Then, the output shaft 112 is locked (see FIG. 25 of Patent Document 1), and the outer ring 103 of the lever side clutch portion 101 is prevented from rotating by blocking the reverse input torque from the output side.
JP 2003-93187 A

  Incidentally, in the clutch unit disclosed in Patent Document 1 described above, when the output shaft 112 is locked by the reverse input torque from the output side in the brake side clutch portion 102, the outer ring 111 and the output shaft 112 are engaged. The roller 114 is in line contact with the inner peripheral surface of the outer ring 111 and the outer peripheral surface of the output shaft 112. Since the outer ring 111 and the output shaft 112 are in line contact with the roller 114 in this way, in order to improve reverse input torque resistance and durability, the contact pressure of the contact surface between the outer ring 111 and the output shaft 112 and the roller 114 is increased. To prevent buckling of the engaging surfaces of the two.

  For this purpose, it is necessary to increase the number of rollers 114 or to increase the size of the brake side clutch portion 102. However, since the clutch unit must be incorporated in a limited space in the automobile, The size of the clutch portion 102 is limited, and it is very difficult to increase the number of rollers 114 for the brake-side clutch portion 102 of the limited size. When the number of rollers 114 is increased, the number of parts and assembly man-hours are increased, which is not a preferable means.

  Accordingly, the present invention has been proposed in view of the above-described problems, and the object of the present invention is to provide a compact clutch unit that can reduce the surface pressure of the contact surface with the roller and reduce the number of parts and assembly man-hours. Is to provide.

  As technical means for achieving the above-mentioned object, the present invention is characterized by having a first clutch portion and a second clutch portion having the following configuration.

  The first clutch portion includes an input side member that receives torque, an output side member that outputs torque, and engagement / disengagement between the input side member and the output side member. Provided between the retainer and the stationary side member, a plurality of engaging elements for controlling transmission / interruption, a retainer for holding each engaging element at a predetermined interval in the circumferential direction, a stationary member whose rotation is restricted A first elastic member that accumulates an elastic force with an input torque from the input side member and returns the cage to a neutral state with the accumulated elastic force by releasing the input torque; and the input side member is stationary A second elastic member that is provided between the side members, accumulates elastic force with input torque from the input side member, and releases the input torque to return the input side member to a neutral state with the accumulated elastic force; Is provided.

  The second clutch portion is provided between an input side member to which torque is input, an output side member to which torque is output, a stationary side member in which rotation is constrained, and the stationary side member and the output side member. Lock means for locking the output side member and the stationary side member against reverse input torque from the side member, and a lock state provided by the lock means for the input torque from the input side member provided on the input side member Unlocking means for releasing the torque, and torque transmitting means provided between the input side member and the output side member, and transmitting input torque from the input side member to the output side member when releasing the locked state by the locking means; The locking means is provided with an eccentric cam whose outer diameter surface is eccentric with respect to the rotation center of the output side member, the outer diameter surface is eccentric with respect to the inner diameter center, and the outer diameter surface of the eccentric cam. And stationary side A pair of engagement members to surface contact so as to form the inner surface and each other irregularities arcuate timber, having an engaging removably interposed allowed structure between the stationary member and the eccentric cam.

  In the present invention, as the locking means of the second clutch portion constituting the clutch unit, the output side member is provided with an eccentric cam whose outer diameter surface is eccentric with respect to the rotation center, and the outer diameter surface is eccentric with respect to the inner diameter center. In addition, a pair of engaging members that are in surface contact with the outer diameter surface of the eccentric cam and the inner diameter surface of the stationary side member so as to form an uneven arc shape are engaged between the eccentric cam and the stationary side member. By adopting a structure that is detachably interposed, the surface pressure on the contact surface with the engaging member can be kept lower than in the case of the brake side clutch portion of the conventional clutch unit disclosed in Patent Document 1. it can.

  That is, by providing the output side member with an eccentric cam whose outer diameter surface is eccentric with respect to the rotation center, a wedge space is formed between the outer diameter surface of the eccentric cam and the inner diameter surface of the stationary side member, By interposing a pair of engagement members whose outer diameter surfaces are eccentric with respect to the center of the inner diameter in the wedge space, the engagement members are mutually connected to the outer diameter surface of the eccentric cam and the inner diameter surface of the stationary member. Since the surface contact is formed so as to form an uneven arc shape, the surface pressure on the contact surface with the engaging member can be suppressed lower than the conventional product in which the roller is in line contact in the locked state. Moreover, since the locking means of the second clutch portion is configured as described above, the number of parts and the number of assembly steps are not increased, and the clutch portion can be made compact.

It is desirable that the locking means of the second clutch portion is arranged between a pair of engaging members and has a structure provided with an elastic member that biases the separating force between the engaging members. When the separation force is urged between the engagement members by the elastic member, when a reverse input torque is applied from the output side member, in the wedge space between the eccentric cam and the stationary side member, Either one can be wedge-engaged, and the output side member can be locked with respect to the stationary side member in both forward and reverse rotation directions.
In addition, each of the pair of engaging members is preferably formed in a convex arc shape in which the outer diameter surface is formed with a single radius of curvature. In this way, since the engaging member having a simple shape can be used, the size and weight of the clutch can be reduced.

  According to the present invention, as the locking means of the second clutch portion, the output side member is provided with an eccentric cam whose outer diameter surface is eccentric with respect to the rotation center thereof, the outer diameter surface is eccentric with respect to the inner diameter center, and A pair of engaging members that are in surface contact with the outer diameter surface of the eccentric cam and the inner diameter surface of the stationary side member so as to form an uneven arc shape can be disengaged between the eccentric cam and the stationary side member. By adopting the intervening structure, the surface pressure at the contact surface with the engaging member can be kept low, the number of parts and assembly man-hours can be reduced, and a compact clutch unit can be provided. Reverse input torque resistance and durability can also be improved.

  FIG. 1 shows an overall configuration of a clutch unit X in an embodiment of the present invention. The clutch unit X is used, for example, by being incorporated in a seat lifter portion that adjusts a seat of an automobile, and a lever side clutch portion 11 that is a first clutch portion provided on the input side and a second side provided on the output side. It is comprised with the brake side clutch part 12 of the reverse input interruption | blocking function which is a clutch part.

  As shown in FIGS. 1 and 2, the lever side clutch portion 11 holds an outer ring 13 as an input side member, an inner ring 14 as an output side member, a plurality of rollers 15 as engaging elements, and a roller 15. A cage 16, a centering spring 17 that is a first elastic member for returning the cage 16 to a neutral state, and a centering spring 18 that is a second elastic member for returning the outer ring 13 to a neutral state. Have.

  On the inner periphery of the outer ring 13, a plurality of cam surfaces 13a are formed at equal intervals in the circumferential direction. The inner ring 14 includes an outer peripheral surface 14 a that forms a wedge clearance 20 between the outer ring 13 and the cam surface 13 a of the outer ring 13. The cage 16 has a plurality of pockets 19 for accommodating the rollers 15.

  As shown in FIG. 3, the centering springs 17 and 18 are both end ring-shaped plate springs formed by rolling a strip plate material, and one centering spring 17 is disposed on the inner diameter side of the other centering spring 18. Yes. The centering spring 17 positioned on the inner diameter side has a pair of locking portions 17a bent radially inward, and the centering spring 18 positioned on the outer diameter side is paired with a pair of locking portions bent radially outward. 18a.

  The centering spring 17 is disposed between the cage 16 and the outer ring 21 which is a stationary side member of the brake side clutch portion 12, and one locking portion 17a is locked to the cage 16 and the other engagement. The stop portion 17 a is locked to a claw portion 21 a provided on the outer ring 21.

  In the centering spring 17, when the input torque from the outer ring 13 is applied, one locking portion 17 a engages with a part of the retainer 16 and the other locking portion 17 a engages with the claw portion 21 a of the outer ring 21. As the outer ring 13 rotates, the centering spring 17 is expanded and elastic force is accumulated, and when the input torque from the outer ring 13 is released, the retainer 16 is returned to the neutral state by the elastic restoring force.

  The centering spring 18 is disposed between the outer ring 13 and the outer ring 21 of the brake side clutch portion 12, and both locking portions 18 a are locked to the claw portions 13 b provided on the outer ring 13, and It is locked to the provided claw portion 21b. The locking portion 18 a is arranged with a circumferential phase shifted from the locking portion 17 a of the centering spring 17.

  In the centering spring 18, when the outer ring 13 rotates due to input torque from the outer ring 13, one locking part 18 a is on the claw part 13 b of the outer ring 13, and the other locking part 18 a is on the claw part 21 b of the outer ring 21. Since the centering spring 18 is pushed and expanded with the rotation of the outer ring 13 and the elastic force is accumulated. When the input torque from the outer ring 13 is released, the outer ring 13 is returned to the neutral state by the elastic restoring force. Let

  On the other hand, as shown in FIGS. 1 and 4, the brake-side clutch portion 12 having a reverse input cutoff function includes an inner ring 14 of the lever-side clutch portion 11 that is an input-side member to which torque is input, and an output side from which torque is output. An output shaft 22 that is a member, an outer ring 21 that is a stationary member whose rotation is constrained, and an output shaft 22 that is provided between the outer ring 21 and the output shaft 22 with respect to the reverse input torque from the output shaft 22. A lock means 24 for locking the outer ring 21, a lock release means 14 c provided on the inner ring 14, for releasing the locked state by the lock means 24 against the input torque from the inner ring 14, and the inner ring 14 and the output shaft 22. The torque transmission means 25 is provided between the inner ring 14 and the torque transmission means 25 that is provided between the inner ring 14 and the locking means 24 when the lock means 24 releases the locked state. In addition, the brake side clutch part 12 shown in FIG. 1 is shown in the cross section which follows the COC line | wire of FIG.

  The inner ring 14 has a shape in which a flange portion 14b extending in the radial direction is formed at one end of the cylindrical portion 14a, and a claw portion 14c extending in the axial direction is formed in a part of the flange portion 14b. The claw portion 14c constitutes the above-described unlocking means. On the other hand, the output shaft 22 has a shape in which a flange portion 22b is formed at a substantially central portion of the shaft-like portion 22a. By inserting one of the shaft-like portions 22a of the output shaft 22 into the center hole of the inner ring 14, the output shaft 22 and the inner ring 14 are arranged coaxially. A through hole 22 c is formed in the flange portion 22 b of the output shaft 22, and a pin 25 is projected in the axial direction at the end of the cylindrical portion 14 a of the inner ring 14 and disposed in the above-described through hole 22 c. The inner diameter of the through hole 22 c of the output shaft 22 is slightly larger than the outer diameter of the pin 25. Thus, by providing a gap between the inner diameter of the through hole 22c and the outer diameter of the pin 25, the lock release by the claw portion 14c of the inner ring 14 is allowed. After the lock is released, the pin 25 is engaged with the inner diameter of the through hole 22c to connect the inner ring 14 and the output shaft 22, whereby the pin 25 serves as a torque transmission means.

  The outer ring 21 is arranged on the outer periphery of the inner ring 14 described above, and the position of one end side of the outer ring 21 in the axial direction is restricted with respect to the inner ring 14 by the retaining ring 26, and the fixed side plate 27 is screwed to the other end side in the axial direction. The position of the flange 22b of the output shaft 22 is restricted while being sandwiched between the flange 14b of the inner ring 14.

  A pair of engaging members 28 a and 28 b and an elastic member 29 are accommodated in an annular space surrounded by the outer ring 21, the flange portion 22 b of the output shaft 22, the flange portion 14 b of the inner ring 14 and the fixed side plate 27. The locking means 24 is configured by interposing the pair of engaging members 28 a and 28 b and the elastic member 29 between the flange portion 22 b of the output shaft 22 and the outer ring 21.

As shown in FIGS. 4 and 5, the flange portion 22b of the output shaft 22 has an eccentric cam having a center O ₁ whose outer diameter surface 22b ₁ is eccentric by e _{1 with} respect to the rotation center O of the shaft-like portion 22a. Hereinafter, the eccentric cam is denoted by reference numeral 22b). The eccentric cam 22b of the outer diameter surface 22b ₁ and the pair of engaging members 28a which is engaged removably arranged between the inner surface 21c of the outer ring 21, each of 28b, the outer diameter surface as shown in FIG. 6 28a ₁ , 28b ₁ and inner diameter surfaces 28a ₂ , 28b ₂ are formed in an arc shape, and the outer diameter surfaces 28a ₁ , 28b ₁ have a center O ₂ that is eccentric by e _{2 with} respect to the inner diameter center O.

For example, a compression coil spring can be used as the elastic member 29. The elastic member 29 is disposed between the pair of engagement members 28a and 28b in the annular space described above, and biases a separation force between the engagement members 28a and 28b. To do. The pair of engaging members 28 a and 28 b are brought into contact with the outer diameter surface 22 b ₁ of the eccentric cam 22 b of the output shaft 22 and the inner diameter surface 21 c of the outer ring 21 even when no torque is applied by the elastic force of the elastic member 29. is doing.

As shown in FIGS. 4 and 6, the inner diameter surface 21 c of the outer ring 21 has a concave arc shape having a center coincident with the rotation center O of the shaft-like portion 22 a of the output shaft 22, and contacts the inner diameter surface 21 c of the outer ring 21. The outer diameter surfaces 28a ₁ , 28b ₁ of both engaging members 28a, 28b are convex arcs with respect to the concave arc shape of the inner diameter surface 21c of the outer ring 21, and the radius of curvature R ₂ is the inner diameter surface of the outer ring 21. It is set slightly smaller than the radius of curvature R _{3 of} 21c. In this way, the contact surfaces of the engaging members 28a and 28b, that is, the outer diameter surfaces 28a ₁ and 28b _{1 of} the engaging members 28a and 28b and the inner diameter surface 21c of the outer ring 21 form a concave and convex arc shape with each other. Thus, the surface pressure on the contact surfaces of the engaging members 28a and 28b can be lowered when locked by reverse input torque.

The outer diameter surface 22b ₁ of the eccentric cam 22b has a convex arc shape having a center O ₁ that is eccentric by e _{1 with} respect to the rotation center O of the shaft-like portion 22a of the output shaft 22 as shown in FIGS. , two engaging members 28a, the inner diameter surface 28a _2, 28b ₂ of 28b in contact with the outer surface 22b ₁ of the eccentric cam 22b is concave arcuate relative to the outer diametric surface 22b ₁ of the convex arc-shaped eccentric cam 22b The curvature radius R ₄ is set to be slightly larger than the curvature radius R ₁ of the outer diameter surface 22b ₁ of the eccentric cam 22b. As described above, the contact surfaces of the engagement members 28a and 28b, that is, the inner diameter surfaces 28a ₂ and 28b _{2 of} the engagement members 28a and 28b and the outer diameter surface 22b ₁ of the eccentric cam 22b form a concave and convex arc shape. By doing so, the surface pressure on the contact surface of the engaging members 28a and 28b can be lowered when locked by reverse input torque.

  With respect to the clutch unit configured as described above, an operation when a reverse input torque is applied to the output shaft 22 will be described.

In the state shown in FIG. 7, for example, when reverse input torque is applied to the output shaft 22, the brake side clutch portion 12 is formed with a wedge space formed by the outer diameter surface 22 b ₁ of the eccentric cam 22 b and the inner diameter surface 21 c of the outer ring 21. ₁ , of the pair of engaging members 28 a and 28 b that are in contact with the outer diameter surface 22 b ₁ of the eccentric cam 22 b and the inner diameter surface 21 c of the outer ring 21 by the elastic force of the elastic member 29, if members (if the rotational direction is the clockwise direction engaging member 28a, if the rotational direction is the counterclockwise direction engaging member 28b) is wedge between the inner diameter surface 21c of the outer diameter surface 22b ₁ and the outer ring 21 of the eccentric cam 22b The output shaft 22 is locked with respect to the outer ring 21.

In this way, the reverse input torque from the output shaft 22 is locked in both the forward and reverse rotational directions by the engaging members 28a and 28b. At the time of locking by the reverse input torque, as described above, the contact surfaces of the engagement members 28a and 28b, that is, the outer diameter surfaces 28a ₁ and 28b _{1 of} the engagement members 28a and 28b and the inner diameter surface 21c of the outer ring 21 are mutually. The concave and convex arc shape is formed, and the inner diameter surfaces 28a ₂ and 28b _{2 of} the engaging members 28a and 28b and the outer diameter surface 22b ₁ of the eccentric cam 22b form a concave and convex arc shape. The surface pressure at the contact surfaces of the engaging members 28a and 28b can be reduced.

In particular, in the conventional clutch unit, as shown in FIG. 15, when the output shaft 112 is locked by reverse input torque in the brake side clutch portion 102, the roller 114 engaged between the outer ring 111 and the output shaft 112 is Since the surface and the outer peripheral surface of the output shaft 112 are in line contact, the surface pressure of the contact surface between the outer ring 111 and the output shaft 112 and the roller 114 is high (see FIG. 25 of Patent Document 1). On the other hand, in this embodiment, the inner diameter surfaces 28a ₂ and 28b ₂ of the engaging members 28a and 28b are concave arc shapes, and the outer diameter surface 22b ₁ of the eccentric cam 22b is convex arc shape, Since the outer diameter surfaces 28a ₁ and 28b _{1 of} the engaging members 28a and 28b have a convex arc shape and the inner diameter surface 22c of the outer ring 21 has a concave arc shape, the engaging members 28a and 28b are brought into contact with each other by surface contact. The surface pressure at the contact surface 28b can be made lower than before.

As described above, the engaging members 28a and 28b in the embodiment are in surface contact with the inner diameter surface 21c of the outer ring 21 and the outer diameter surface 22b ₁ of the eccentric cam 22b so as to form a concavo-convex arc shape. Thus, even if each member of the eccentric cam 22b, the engaging members 28a and 28b, and the outer ring 21 is made thin, the surface pressure on the contact surface can be afforded. Etc., a sheared surface can be obtained on the contact surface, and plastic processing can be easily applied.

  Each member of the eccentric cam 22b, the engaging members 28a and 28b, and the outer ring 21 may be made of ferrous metal, a self-lubricating sintered material or resin, or a combination thereof. Good. For applications with a large torque capacity, an appropriate surface treatment (heat treatment) such as simmering a metal material, carburizing, carbonitriding, or plating may be performed.

  The operation at the time of unlocking and torque transmission in the clutch unit of this embodiment is as follows. The operation of the lever side clutch portion 11 will be described with reference to FIGS. 10 to 12, the centering springs 17 and 18 and the outer ring 21 of the brake side clutch portion 12 are schematically illustrated and conceptually illustrated. The operation of the brake side clutch unit 12 will be described with reference to FIGS.

  In the above-described lever-side clutch portion 11, when no input torque is applied to the outer ring 13 as shown in FIG. 10, the roller 15 is positioned at the circumferential center of the cam surface 13 a of the outer ring 13 and the outer ring 13. The inner ring 14 is held in a non-engaged state. When input torque acts on the outer ring 13, the outer ring 13 rotates in the direction of the arrow in the figure as shown in FIG. 11, so that the roller 15 moves to one end side (right side in the figure) of the wedge clearance 20. The state is pushed and engaged between the cam surface 13 a of the outer ring 13 and the outer peripheral surface 14 a of the inner ring 14. Since the retainer 16 tries to stand still together with the outer ring 21 by the centering spring 17, the relative movement of the outer ring 13 becomes possible.

  Thereby, since the outer ring 13 and the inner ring 14 are locked, the input torque from the outer ring 13 is transmitted to the inner ring 14 via the roller 15, and the outer ring 13, the roller 15, the retainer 16 and the inner ring 14 are rotated together. Move. As the outer ring 13 and the cage 16 rotate, the centering springs 17 and 18 are bent, and elastic forces corresponding to the amount of the bending are accumulated in each.

  On the other hand, when the input torque from the outer ring 13 is released, the cage 16 is returned to the neutral state by the elastic restoring force accumulated in the centering spring 17 as shown in FIG. The return torque in the direction of the arrow in the figure by the centering spring 17 at that time is transmitted to the outer ring 13 via the cage 16 and the roller 15, and the outer ring 13 returns to the neutral state. While the cage 16 and the outer ring 13 return to the neutral state, the inner ring 14 maintains the given rotation position as it is. Therefore, the rotation amount of the outer ring 13 is repeatedly accumulated in the inner ring 14 due to repeated rotation.

On the other hand, in the brake-side clutch portion 12, when the input torque is applied from the inner ring 14 as shown in FIG. 8 from the state of FIG. 7, the pawl portion 14c that is the unlocking means is located on the rear side in the rotational direction. The engaging member engages with the engaging member 28a if the rotation direction is clockwise (in the case of illustration), and engages with the engaging member 28b if the rotation direction is counterclockwise. The elastic member 29 is pressed forward in the rotational direction against the elastic force of the elastic member 29. Thus, outer surface 22b ₁ and the engaging member 28a which has been engaged wedge between the radially inner surface 21c of the outer ring 21 (28b) is disengaged from the wedge spaces, the locked state is released the output shaft 22 of the eccentric cam 22b Is done. At this time, the engaging member 28 b (28 a) positioned forward in the rotational direction does not wedge engage between the outer diameter surface 22 b ₁ of the eccentric cam 22 b and the inner diameter surface 21 c of the outer ring 21 in the wedge space. As a result, the output shaft 22 can rotate.

  Further, when the inner ring 14 is rotated from the state of FIG. 8 as shown in FIG. 9, a pin 25 having a gap allowing the engagement member 28a (28b) to be unlocked is formed between the inner ring 14 and the through hole 22c of the output shaft 22. By engaging the inner diameter surface of the through hole 22c, the inner ring 14 is connected to the output shaft 22 via the pin 25. After the lock of the engaging member 28a (28b) is released, the inner ring 14 is connected via the pin 25. Thus, torque is transmitted and the output shaft 22 rotates.

  The clutch unit X having the structure described in detail above is used by being incorporated in, for example, an automobile seat lifter. FIG. 13 shows a seat seat 40 installed in a passenger compartment of an automobile. The seat 40 includes a seat 40a and a backrest 40b, and includes a seat lifter 41 that adjusts the height H of the seat 40a. The height H of the seating seat 40a is adjusted by the operation lever 41a of the seat lifter 41.

FIG. 14A conceptually shows one structural example of the sheet lifter unit 41. Seat slide adjuster 41b of the slide moving member 41b ₁ to the link member 41c, one end of 41d are respectively rotatably hinged. The other ends of the link members 41c and 41d are pivotally attached to the seating seat 40a. The other end of the link member 41c is pivotally attached to the sector gear 41f via the link member 41e. Sector gear 41f is pivotally rotatably sitting seat 40a, a swingable fulcrum 41f ₁ around. The other end of the link member 41d is pivotally attached to the seating seat 40a.

  The clutch unit X of the above-described embodiment is fixed to an appropriate part of the seating seat 40a, and an operation lever 41a made of resin, for example, is coupled to the outer ring 13 of the lever side clutch portion 11, and the output shaft 22 of the brake side clutch portion 12 is connected. Is provided with a pinion gear 41g which meshes with a sector gear 41f which is a rotating member. The pinion gear 41g is formed integrally with the shaft end of the output shaft 22 as shown in FIGS.

  For example, in FIG. 14B, when the operation lever 41a is swung counterclockwise (upward), the input torque in that direction is transmitted to the pinion gear 41g via the clutch unit X, and the pinion gear 41g is counterclockwise. Rotate. Then, the sector gear 41f that meshes with the pinion gear 41g swings in the clockwise direction, and pulls the other end of the link member 41c through the link member 41e. As a result, both the link member 41c and the link member 41d stand up, and the seating surface of the seating seat 40a is raised.

  In this way, after adjusting the height H of the seating seat 40a, when the operation lever 41a is opened, the operation lever 41a is rotated clockwise by the elastic force of the centering springs 17 and 18 to return to the original position (neutral state). Return to). When the operation lever 41a is swung clockwise (downward), the seating surface of the seating seat 40a is lowered by the reverse operation. When the operation lever 41a is released after the height adjustment, the operation lever 41a rotates counterclockwise and returns to the original position (neutral state).

In embodiment of this invention, it is sectional drawing which shows the whole structure of a clutch unit. It is sectional drawing which follows the AA line of FIG. It is sectional drawing in alignment with the BB line of FIG. 1, and shows two centering springs, a holder | retainer, and a part of outer ring | wheel. It is a left view in the state where the fixed side plate of FIG. 1 was removed. It is a side view which shows the eccentric cam of FIG. It is a side view which shows a pair of engaging member of FIG. FIG. 8 is a side view for explaining the operation of the brake side clutch portion of FIG. 1 and showing a locked state of the output shaft. FIG. 8 is a side view for explaining the operation of the brake side clutch portion of FIG. 1 and showing the unlocked state of the output shaft. FIG. 8 is a side view for explaining the operation of the brake side clutch portion of FIG. 1 and showing the rotation state of the output shaft. FIG. 3 is an enlarged cross-sectional view of a main part illustrating a state where a roller is in a neutral position, for explaining an operation of the lever side clutch part of FIG. 2. FIG. 3 is an enlarged cross-sectional view of a main part illustrating the operation of the lever side clutch portion of FIG. 2 and showing a state in which a roller is caught in a wedge clearance. FIG. 3 is an enlarged cross-sectional view of a main part illustrating a state in which a roller returns to a neutral position, for explaining the operation of the lever side clutch portion of FIG. 2. It is a conceptual diagram which shows the seat seat of a motor vehicle. (A) is a conceptual diagram which shows one structural example of a sheet lifter part, (b) is the principal part enlarged view. It is sectional drawing which shows the structural example of the conventional clutch unit.

Explanation of symbols

11 First clutch (lever side clutch)
12 Second clutch part (brake side clutch part)
13 Input side member (outer ring)
14 Input / output side member (inner ring)
14c Unlocking means 15 Engagement element (roller)
16 Cage 17 First elastic member (centering spring)
18 Second elastic member (centering spring)
21 Static side member (outer ring)
21c Inner diameter surface of stationary side member 22 Output side member (output shaft)
22b Eccentric cam 22b ₁ Eccentric cam outer diameter surface 24 Locking means 25 Torque transmitting means (pin)
28a, 28b engaging member 28a _1, 28b ₁ engagement member of the outer diameter surface 28a _2, 28b ₂ engaging member inner surface 29 the elastic member 41 seat lifter section 41a operating lever 41f rotating member (sector gear)

Claims (5)

An input side member to which torque is input, an output side member to which torque is output, and engagement / disengagement between the input side member and the output side member are used to control transmission / cutoff of input torque from the input side member. A plurality of engagement elements, a retainer that holds each engagement element at a predetermined interval in the circumferential direction, a stationary side member that is constrained to rotate, and provided between the retainer and the stationary side member. A first elastic member that accumulates an elastic force with the input torque of the input and releases the input torque to return the cage to a neutral state with the accumulated elastic force; and is provided between the input side member and the stationary side member. A first clutch comprising: a second elastic member that accumulates an elastic force with an input torque from the input side member and returns the input side member to a neutral state with the accumulated elastic force by releasing the input torque And
An input side member to which torque is input, an output side member to which torque is output, a stationary side member whose rotation is restricted, and a reverse input from the output side member provided between the stationary side member and the output side member Lock means for locking the output side member and the stationary side member with respect to torque, and a lock release means provided on the input side member for releasing the locked state by the lock means with respect to input torque from the input side member And a torque transmission means that is provided between the input side member and the output side member, and transmits the input torque from the input side member to the output side member when the locked state is released by the locking means, and the locking means The output side member is provided with an eccentric cam whose outer diameter surface is eccentric with respect to the center of rotation, the outer diameter surface is eccentric with respect to the inner diameter center, and the outer diameter surface of the eccentric cam and the inner diameter of the stationary side member are Face and mutual A pair of engagement members to surface contact so as to form an uneven arc shape, and said eccentric cam and a second clutch portion which engages removably interposed between the stationary member,
A clutch unit comprising:   The clutch unit according to claim 1, further comprising an elastic member that is disposed between the pair of engagement members and biases a separation force between the engagement members.   The clutch unit according to claim 1 or 2, wherein each of the pair of engaging members has a convex arc shape in which an outer diameter surface is formed with a single radius of curvature.   The clutch unit according to any one of claims 1 to 3, wherein the first clutch part and the second clutch part are incorporated in an automobile seat lifter part.   The clutch unit according to claim 4, wherein an input side member of the first clutch portion is coupled to an operation lever, and an output side member of the second clutch portion is coupled to a rotating member of a vehicle seat lifter portion.