JP2002122159A - Clutch unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clutch unit capable of performing the sufficient miniaturization and improving the design versatility while avoiding any interference of a centering spring equipped on a clutch part with a peripheral part thereof. SOLUTION: The centering spring 12 comprises a plurality of torsional coil springs, and each winding center in a natural condition is displaced in the direction opposite to the transferring direction of each winding center associated with the increase in the working quantity (the relative rotational angle) of a holder 11 in an assembled condition. Each winding center of the centering spring 12 is located concentrically when the holder 11 in the assembled condition is not in operation.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch unit having a clutch portion in the middle of a torque transmission path between an input member and an output member. For example, input torque from the input side is transmitted to the output side. On the other hand, the present invention relates to a clutch unit that has a function of locking the reverse input torque from the output side and not returning it to the input side, and is used for, for example, a seat adjustment device of an automobile.

[0002]

2. Description of the Related Art For example, in an apparatus for transmitting an input torque by a rotation operation of an operation member to an output side mechanism to adjust a position of a required portion, the output side mechanism is held at a fixed position when the operation member is not operated. Functions may be required. As a specific example, in a seat height adjusting device for a seat in an automobile, a brake unit for supporting a load (a seat's own weight and a weight of a seated person) from the seat is provided on an output side mechanism. The height of the seat is adjusted by inputting a forward or reverse input torque from the operating member to the input shaft, and the position of the seat with the operating member opened is held by the brake unit. Has been implemented.

[0003] This type of device is limited in mounting space,
In consideration of operability, commercial value, and the like, it is preferable to reduce the size. In view of the above, the applicant of the present application has disclosed in the earlier patent application (Japanese Patent Application No. 2000-240213) that a first clutch portion is provided between a control member and an input-side member interposed in a torque transmission path between input and output, A clutch unit has been proposed in which a second clutch portion is provided between a stationary-side member and an output-side member in which is restricted, and the two clutch portions are integrally unitized. According to this clutch unit, it is expected that the above-described required operation can be ensured and the size can be reduced.

[0004]

By the way, the first clutch portion of the clutch unit engages with the engaging member interposed between the input side member and the control member, and engages with the engaging member through relative rotation with respect to the stationary side member. It has a retainer for controlling the detachment, and a centering spring for connecting the stationary side member and the retainer in the rotation direction.

As the centering spring, as shown in FIG. 22, a rewind type torsion coil spring Xa wound a plurality of times is used as an example. Engagement portions Xa1 and Xa2 are formed at both ends of the centering spring Xa, and in the natural state shown in the figure, the centers of the plurality of windings are concentrically located.

When the centering spring Xa is assembled to the first clutch portion, as shown in FIG.
In a state where the pair of engagement portions Xa1 and Xa2 are expanded in the rewinding direction, the engagement portions Xa1 and Xa2 are locked to the locking portion Xb of the retainer and the locking portion Xc of the stationary member, respectively. Under this condition,
The centers of the respective windings of the centering spring Xa are sequentially displaced due to the above-mentioned spreading.

From this state, as shown in FIG. 1D, the retainer (locking portion Xb) is moved from the stationary side member (locking portion X).
In the case of relative rotation with respect to c), the amount of deviation of the center of each winding of the centering spring Xa increases, and accordingly, for example, the vicinity of the engaging portion Xa1 bulges to the outer diameter side, and There is a fear that the member Xd may come into contact with the outer ring on the operation member side.

In order to avoid this problem, it is necessary to expand the space for accommodating the centering spring Xa.
It is presumed that this will lead to an increase in the size of the clutch portion, and there is a concern that this may hinder the downsizing of the clutch unit. In addition, there is a concern that the design range of the present clutch unit, which is characterized in that the first clutch unit and the second clutch unit are unitized, is narrowed.

It has been attempted to use a centering spring Ya of a winding type as shown in FIG. However, when the centering spring Ya is assembled to the first clutch portion, as shown in FIG. 2B, the pair of engagement portions Ya1 and Ya2 are spread in the winding direction, Locking part Y of cage
Since the centering spring Ya is reduced in diameter because the centering spring Ya is locked to the locking portion Yc of the stationary side member, each winding center is sequentially displaced due to the above-mentioned spreading.

If the retainer rotates relatively from such a state, the centering spring Ya may be further reduced in diameter, and at the same time, the amount of deviation of the center of each winding may increase, and the centering spring Ya may tighten the retainer. As a result, the expected clutch function may not be obtained. To avoid this problem, as in the above case, the first clutch portion must be expanded, and there is a concern that the clutch unit will not be compact and the design range will be narrowed.

The present invention has been made in view of the above circumstances, and by improving the structure of the centering spring in the clutch portion, it is possible to sufficiently reduce the size of the centering spring while avoiding interference between the centering spring and its peripheral portion. Another object of the present invention is to provide a clutch unit that can improve the degree of freedom in design.

[0012]

In order to achieve the above technical object, the present invention provides an input member to which a torque is input,
Controlling engagement / disengagement of an output-side member from which torque is output, a clutch portion provided in the middle of a torque transmission path between the input-side member and the output-side member, and an engaging element provided in the clutch portion. In a clutch unit including a retainer and a centering spring for centering the retainer, the centering spring is constituted by a plurality of torsion coil springs, and each winding center in a natural state operates the retainer in an assembled state. It is characterized by being displaced in the direction opposite to the direction of transition of each winding center with an increase in the amount.

According to such a configuration, when the retainer is operated (relatively rotated) in a state in which the centering spring formed of a plurality of winding torsion coil springs is assembled to the clutch portion, the amount of operation (relative rotation). As the relative rotation angle increases, the center of each winding of the centering spring shifts in a predetermined direction.
In this case, since the center of each winding in the natural state is displaced in a direction opposite to the predetermined direction, the amount of deviation of each winding center during the operation of the retainer corresponds to the deviation. Becomes smaller. As a result, it is possible to reduce the diameter of the accommodation space for the centering spring in the clutch portion, thereby achieving a compact clutch unit and increasing the degree of freedom in design.

[0014] In the above configuration, the clutch portion is provided between the control member and the input side member interposed in the torque transmission path between the input side member and the output side member, and the rotation is restricted. A second clutch portion provided between the stationary side member and the output side member to transmit input torque from the input side member to the output side member via the first clutch portion and the control member. A reverse input torque from the member is locked between the stationary member and the stationary member via a second clutch portion, and an engaging member, a retainer, and a centering spring are disposed in the first clutch portion. Is interposed between the input side member and the control member, the retainer controls engagement / disengagement of the engaging element through a relative rotation operation with respect to the stationary side member, and the centering spring connects the stationary side member and the retainer. Connected in the direction of rotation It can be applied to the latch unit. By doing so, the space for accommodating the centering spring in the first clutch portion can be reduced, which leads to a reduction in the size of the entire clutch unit and also contributes to an increase in the design flexibility.

It is preferable that each winding center of the centering spring is located concentrically when the retainer is not operated in the assembled state. In this way, regardless of whether the operating direction (relative rotation direction) of the cage is forward or reverse, each winding center of the centering spring is uniformly displaced with respect to both directions, and the amount of deviation is small. The quantification is performed efficiently.

It is preferable to use a rewinding type spring as the centering spring. In this way, the centering spring does not contract in diameter, so even if a small-diameter centering spring is provided on the outer diameter side of the retainer, the centering spring tightens the retainer and hinders the clutch function. Therefore, the diameter of the centering spring can be reduced.

Further, the cross-sectional shape of the centering spring is preferably non-round. In other words, even if the inner and outer diameters are the same, a non-round shape that can obtain a greater spring rigidity than a round shape can hold, for example, the operation lever attached to the input-side member in a horizontal position with sufficient strength.
In particular, by setting the cross-sectional shape of the centering spring to be rectangular, it is possible to change the torsional torque only by changing the outer diameter, even if the inner diameter and width are the same. And flexible response is possible.

Further, the centering spring is preferably a so-called pitch-wound spring wound with a gap provided between the wires. That is, when a so-called close contact spring having no gap between the wires is used, the required torsional force and return force cannot be obtained due to the friction loss generated between the wires.
By using a pitch-wound spring, such a problem can be avoided.

The clutch unit of the present invention is suitable for a seat adjustment device of an automobile. In this case, an operation lever is connected to an input member, and an output member is connected to a rotation member of the seat adjustment device. Here, the seat adjustment device includes a seat height adjustment device for adjusting the height of the seat.
Seat tilt adjustment device that adjusts the tilt of the backrest seat,
A seat slide adjusting device for adjusting the front-back position of the seat is included. Among them, the clutch unit of the present invention is particularly suitable for a seat height adjusting device for a seat. According to this configuration, the height of the seat can be adjusted by swinging the operation lever, so that the convenience in operation is increased as compared with the conventional apparatus, and at the same time, the design freedom of the vehicle body and the seat is improved. The height can be increased, and it is particularly useful for a seat height adjusting device of a small car or a popular car.

[0020]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 shows the overall structure of a clutch unit according to an embodiment of the present invention. The clutch unit of this embodiment includes an outer ring 1 as an input member, an output shaft 2 as an output member, and an inner ring 3 as a control member.
An outer ring 4 as a stationary side member, a first clutch part 5 provided between the outer ring 1 and the inner ring 3, and a second clutch part 6 provided between the outer ring 4 and the output shaft 2 mainly include: Configured as an element.

FIG. 2 shows the outer race 1 as an input-side member. On the outer periphery of the outer ring 1, a plurality (for example, three) ribs 1 a protruding toward the outer diameter side and a plurality (for example, four) ribs 1
b, a plurality of (for example, two) ribs 1e, and one or more ribs 1f are formed at predetermined intervals in a circumferential direction. Rib 1
The one end portion in the axial direction of a protrudes in the axial direction from one end of the outer race 1 to form a protruding portion 1a2. Also, three ribs 1a
One, for example, the rib 1 located on the upper side in FIG.
An identification mark 1a1 used for identifying the direction when the clutch unit is attached to a mating member is provided on the outer periphery of the member a. In this embodiment, the identification mark 1a1 is in the form of an axial groove. These ribs 1a, 1b, 1
e and 1f are rotationally engaged with operation levers (13: see FIGS. 8 and 9) mounted on the outer periphery of the outer race 1 to prevent the operation lever (13) from rotating relative to the outer race 1.

An axial screw hole 1b1 is formed in the rib 1b. The relative movement of the operation lever (13) in the axial direction with respect to the outer ring 1 is performed by moving the operation lever (1) into the screw hole 1b1 of the rib 1b.
This is prevented by screwing 3). As shown in FIG. 9, in this embodiment, the clutch unit and the operation lever (13) are arranged on either the left or right side of the seat according to the design of the right-hand drive vehicle, the left-hand drive vehicle, the vehicle body and the seat. In order to enable this, the outer ring 1 is made symmetrical with respect to the Y axis in FIG.
3) can be mounted in either direction. In this case, since the operating torque of the operating lever (13) mainly acts on the screw connection portion of the two ribs 1b located at 180 ° opposite positions, a screw hole 1b1 is formed only in these two ribs 1b, In the two ribs 1b, a pilot hole (through hole) for processing the screw hole 1b1 may be left as it is. Thereby, the processing cost of the screw hole processing can be reduced. For example, when the operation lever (13) is mounted rightward in the figure (solid line), a screw hole 1b1 is formed in two ribs 1b located on an inclined line inclined rightward with respect to the Y axis in the figure. The two ribs 1b located on the inclined line inclined to the left are formed as pilot holes 1b1 '. When the operation lever (13) is mounted to the right in the same figure (two-dot chain line), the operation is reversed. Of course, the screw holes 1b1 may be formed in all four ribs 1b.

A centering spring (12: see FIG. 11) of a first clutch portion (5), which will be described later, is housed in the inner periphery of the protruding portion 1a2. The rotation range of the outer ring 1 is restricted by the protrusion 1a2 engaging with a stopper (4a1) of an outer ring (4: see FIG. 5) described later in the rotational direction.

On the inner circumference of the other end of the outer race 1, a flange 1c extending toward the inner diameter side is formed. This flange portion 1c is formed by a first
Cage (5) retainer (11: see FIGS. 1 and 10)
In one direction in the axial direction, and has a role of maintaining coaxiality of the outer ring 1 with the inner ring 3. A plurality of (for example, ten) cam surfaces 1d are formed on the inner periphery of the outer race 1 at equal intervals in the circumferential direction. Each cam surface 1d is deep at the center in the circumferential direction, and becomes shallower in an inclined manner from both sides in the circumferential direction.

The outer ring 1 is formed by forging from a steel material such as case hardening steel, carbon steel for machine structure, and bearing steel.
Appropriate heat treatment such as carburizing and quenching and tempering, carbonitriding and quenching and tempering, induction hardening and tempering, and soot quenching and tempering are performed. In this embodiment, case hardening steel (for example, chromium molybdenum steel SCM420) is used as a steel material forming the outer ring 1, and carburizing, quenching and tempering are performed as a heat treatment on the case hardening steel to reduce the surface hardness of at least the surface layer portion on the cam surface 1d to 57. ~
It is adjusted to 62HRC. Here, HRC represents the C scale of Rockwell hardness. The outer ring 1 is
It is also possible to use a cut product of a steel material or a press-formed product of a steel plate (for example, a cold-rolled steel plate).

FIG. 3 shows the output shaft 2 as an output-side member. The output shaft 2 includes a journal 2a at one end, a large diameter portion 2b at the center, and a connecting portion 2c at the other end.
The journal 2a is inserted into a radial bearing surface (3a1) of an inner ring (3: see FIG. 4) described later. A plurality (for example, eight) of cam surfaces 2b1 are formed at equal intervals in the circumferential direction on the outer periphery of the large diameter portion 2b. Each cam surface 2b1 is connected to the output shaft 2
Is formed in a flat surface shape that forms a chord with respect to a circle centered on the axis of the. In addition, a plurality of (for example, eight) pin holes 2b3 in the axial direction are formed at predetermined circumferential intervals at one end portion of the large diameter portion 2b. A pin (3b1) of an inner ring (3: see FIG. 4) described later is inserted into these pin holes 2b3. Further, an annular concave portion 2b4 is formed in the other end portion of the large diameter portion 2b. A friction member (9: see FIG. 7), which will be described later, is attached to the annular concave portion 2b4.
Is a journal surface to be inserted into a radial bearing surface (7e2) of a fixed side plate (7: see FIG. 6) described later. A tooth mold 2c1 for connecting another rotating member is formed in the connecting portion 2c.

The output shaft 2 is formed by forging from a steel material such as case hardening steel, carbon steel for machine structure, bearing steel, etc., and is formed by carburizing and quenching and tempering, carbonitriding and quenching and tempering, induction hardening and tempering, soot quenching and tempering, and the like. An appropriate heat treatment is performed. In this embodiment, case hardening steel (for example, chrome molybdenum steel SCM420) is used as the steel material forming the output shaft 2.
The surface hardness of the surface layer is adjusted to 57 to 62 HRC by carburizing, quenching and tempering as a heat treatment. In addition, the output shaft 2 may be a machined steel product.

FIG. 4 shows the inner race 3 as a control member. The inner ring 3 includes a cylindrical portion 3a, a flange portion 3b extending from one end of the cylindrical portion 3a to the outer diameter side, and a plurality (for example, eight) extending from the outer diameter end of the flange portion 3b in one axial direction. It is mainly composed of the column 3c. The cylindrical portion 3 a is inserted outside the journal portion 2 a of the output shaft 2 and is inserted inside the outer ring 1. On the inner circumference of the other end side portion of the cylindrical portion 3a,
A radial bearing surface 3a1 for supporting the journal portion 2a of the output shaft 2 in the radial direction is formed. The outer periphery of the other end portion of the cylindrical portion 3a is provided between the cam surface 1d of the outer ring 1 in the forward and reverse directions. Is formed with a circumferential surface 3a2 forming a wedge gap.
A plurality of (for example, eight) pins 3b1 protruding in one direction in the axial direction are formed on the flange portion 3b at predetermined intervals in the circumferential direction. These pins 3b1 are inserted into pin holes 2b3 of the output shaft 2, respectively. Moreover, the pillar part 3 adjacent in the circumferential direction
Between pockets c, pockets 3 opening toward one side in the axial direction
c1 are formed, and second pockets 3c1 described later are formed in these pockets 3c1.
The roller (20) and the leaf spring (21) of the clutch section (6: see FIG. 15) are housed. Roller (20) and leaf spring (2)
Since 1) can be incorporated into the pocket 3c1 from the axial opening of the pocket 3c1, the assembling work is easy.

The inner ring 3 is formed by forging from a steel material such as case hardening steel, carbon steel for machine structure, and bearing steel.
Appropriate heat treatment such as carburizing and quenching and tempering, carbonitriding and quenching and tempering, induction hardening and tempering, and soot quenching and tempering are performed. In this embodiment, case hardening steel (for example, chromium molybdenum steel SCM420) is used as a steel material forming the inner ring 3, and carburizing, quenching and tempering are performed as heat treatment to adjust the surface hardness of the surface layer portion to 57 to 62 HRC. ing. In addition, the inner ring 3 may be a cut product of a steel material or a press-formed product of a steel plate (for example, a cold-rolled steel plate).

FIG. 5 shows the outer race 4 as a stationary member. The outer ring 4 has a flange portion 4a extending in a radial direction.
And a cylindrical portion 4c extending in one axial direction from the outer diameter end of the flange portion 4a, and a flange portion 4d protruding from one end of the cylindrical portion 4c to the outer diameter side. A plurality (for example, three) of stopper portions 4a1 projecting to the other side in the axial direction are arranged and formed at predetermined intervals in the circumferential direction on the flange portion 4a.
The stoppers 4a1 are engaged with the protruding portions 1a2 of the outer race 1 in the rotation direction to regulate the rotation range of the outer race 1. The flange portion 4a has a pair of locking portions 4a2 protruding toward the other side in the axial direction, and a plurality of (for example, two) mounting portions 4a3.
Are formed. Engaging portions (12a1, 12a) of a centering spring (12: see FIG. 11) of a first clutch portion (5) to be described later are provided on outer circumferential surfaces of the pair of locking portions 4a2.
2) are respectively locked. A winding part (12a) of a centering spring (12) is mounted on the outer periphery of the mounting part 4a3.

On the inner periphery of the cylindrical portion 4c, there is formed a circumferential surface 4c1 which forms a wedge gap in both forward and reverse rotation directions with the cam surface 2b1 of the output shaft 2. A plurality of (for example, 6
) Notches 4d1 are formed at predetermined intervals in the circumferential direction. The notch 4d1 is compatible with a crimping portion (7c: see FIG. 6) of the fixed side plate (7) described later.

The outer race 4 is formed by forging from a steel material such as case hardening steel, carbon steel for machine structure, and bearing steel.
Appropriate heat treatment such as carburizing and quenching and tempering, carbonitriding and quenching and tempering, induction hardening and tempering, and soot quenching and tempering are performed. In this embodiment, case hardening steel (for example, chromium molybdenum steel SCM420) is used as a steel material forming the outer ring 4, and carburizing, quenching and tempering are performed on the case hardening steel to adjust the surface hardness of the surface layer to 57 to 62 HRC. ing. In addition, the outer ring 4 can also be a cut product of a steel material or a press-formed product of a steel plate (for example, a cold-rolled steel plate).

FIG. 6 shows a fixed side plate 7 fixed to the outer race 4. The fixed side plate 7 includes a flange portion 7a extending in a radial direction, a plurality of (for example, four) bracket portions 7b protruding from the outer diameter end of the flange portion 7a to the outer diameter side, and a shaft from the outer diameter end of the flange portion 7a. A plurality of (for example, six) caulking portions 7c protruding in one of the directions, and a plurality (for example, four) locking portions 7a1 protruding in one of the axial directions from the flange portion 7a;
A boss 7e protruding in one axial direction from the inner diameter end of the flange 7a is mainly configured. The four bracket portions 7b are formed at predetermined intervals in the circumferential direction, and each of the four bracket portions 7b is integrally (or separately) formed with a hollow pin-shaped caulking portion 7b1. The six caulking portions 7c are formed at predetermined intervals in the circumferential direction, and each has a pair of claw portions 7c1 branched in a forked shape. The fixed side plate 7 of the outer ring 4 is attached by attaching the caulked portion 7c to the notch portion 4d2 of the outer ring 4 and caulking the pair of claw portions 7c1 in opposite directions in the circumferential direction to abut against the flange portion 4d. , Relative movement in the axial direction and relative movement in the rotation direction can be prevented. The caulking portion 7b1 is caulked and fixed to a mounting hole of the mating member.

A radial bearing surface 7 is provided on the inner periphery of the boss 7e.
e2 is formed. The boss 7 e is provided in the annular recess 2 of the output shaft 2.
The friction member (9: see FIG. 7), which will be described later, is mounted between the outer periphery of the boss 7e and the outer peripheral wall of the annular concave portion 2b4. The locking portion 7a1 is provided in the concave portion (9) of the friction member (9).
a) in the rotational direction to prevent relative rotation of the friction member (9) with respect to the fixed side plate 7. The radial bearing surface 7e2 of the boss 7e is connected to the journal surface 2b5 of the annular recess 2b4.
To support the journal surface 2b5 in the radial direction.

The fixed side plate 7 is formed by pressing a steel plate material such as a cold-rolled steel plate. In this embodiment, a cold-rolled steel sheet (for example, SPCE) is used as a steel sheet material forming the fixed side plate 7. In addition, caulking part 7
In consideration of the workability when caulking c and 7b1,
No heat treatment was applied. In addition, the parts to be caulked, such as the caulked parts 7c and 7b1, are subjected to carbon-proof treatment (or carbon-proof and nitric-proof treatment).
To perform carburizing and quenching and tempering (or carbonitriding and quenching and tempering).

FIG. 7 shows a friction member 9 as a braking means. In this embodiment, the friction member 9 has a ring shape, and a plurality of (for example, four) concave portions 9a are formed on one end surface thereof at predetermined intervals in a circumferential direction. Recess 9a
Is engaged with the locking portion 7a1 of the fixed side plate 7 in the rotational direction,
The relative rotation of the friction member 9 with respect to the fixed side plate 7 is prevented.

The friction member 9 is formed of an elastic material such as rubber or synthetic resin, and is press-fit into the outer peripheral wall of the annular concave portion 2b4 of the output shaft 2 with an interference. The frictional force generated between the outer periphery of the friction member 9 and the outer peripheral wall of the annular recess 2b4 applies a braking force (friction braking force) to the output shaft 2 in the rotational direction. The magnitude of the braking force (braking torque) may be appropriately set in consideration of the magnitude of the reverse input torque input to the output shaft 2, but from the viewpoint of effectively preventing the reverse input torque reflux phenomenon. It is preferable to set the same magnitude as the assumed reverse input torque. In the case of the seat height adjusting device, it is preferable to set the same magnitude as the reverse input torque acting on the output shaft 2 when the occupant is seated on the seat. As in this embodiment, the friction member 9 is used as the braking means.
Is advantageous in that the braking force can be set and changed by adjusting the interference of the friction member 9.

Although the material of the friction member 9 is not particularly limited, in this embodiment, the friction member 9 is made of a synthetic resin material, for example, polyacetal (POM) containing 30% by weight of glass fiber.
It is an injection molded product of the compounded synthetic resin material.

FIG. 8 (cross section taken along the line BB in FIG. 1) shows the first clutch unit 5. The first clutch unit 5 includes a plurality of (for example, ten) cam surfaces 1 d provided on the outer ring 1 and the inner ring 3.
, A cam surface 1d and a circumferential surface 3a
Plural (for example, 9) as engaging elements interposed between 2 and
Roller 10, a retainer 11 for holding the roller 10,
An elastic member that connects the retainer 11 to the outer ring (4) in the rotational direction, for example, a centering spring (12: see FIG. 11) is configured as a main element. Cam surface 1d, circumferential surface 3a
2, and the roller 10 constitute a lock means, and the retainer 11 and the centering spring (12) constitute a return means. In this embodiment, the cam surface 1d
Forms a wedge gap with the circumferential surface 3a2 in both forward and reverse rotation directions. An operation lever 13 is coupled to the outer wheel 1, and a forward or reverse input torque is input from the operation lever 13 to the outer wheel 1. Grease is sealed in a space between the inner circumference of the outer race 1 and the outer circumference of the inner race 3 (cylindrical portion 3a), in particular, between the cam surface 1d and the circumferential surface 3a2.

FIG. 10 shows the retainer 11. A plurality of retainers 11 (for example, ten) accommodating the rollers 10
And a locking portion 11b protruding from one end face to one side in the axial direction. Locking part 11b
Is formed, for example, in an arc shape, and is inserted into the inner peripheral side of the locking portion 4a2 of the outer ring 4. In addition, centering springs (12: 12) are provided on both circumferential side surfaces 11b1 and 11b2 of the locking portion 11b.
The engaging portions (12a1, 12a2) of FIG. 11 are respectively locked.

Although the material of the cage 11 is not particularly limited, in this embodiment, the cage 11 is formed by injection molding of a synthetic resin material, for example, a synthetic resin material in which glass fiber is blended with polyamide 66 (PA66) at 30% by weight. I have.

In this embodiment, the axial dimension of the pocket 11a 'which is close to one of the circumferential side surfaces 11b1 and 11b2 of the locking portion 11b is set to the other pocket 11a.
It is smaller than a.

FIG. 11 shows the centering spring 12. The centering spring 12 is a torsion coil spring having a plurality of turns (approximately three turns in the illustrated example).
Engaging portions 12a bent toward the inner diameter side at both ends of 2a
1 and 12a2 are formed.
12a2 are opposed at predetermined intervals in the circumferential direction. The centering spring 12 is formed of a non-circular, for example, rectangular wire having a cross-sectional shape. In this embodiment, a piano wire (SWPB) is used as the wire. further,
The centering spring 12 is a rewind type spring that is used by rewinding from a natural state, and is shown in FIG.
Is a so-called pitch-wound spring wound with a gap S provided between the lines of the winding part 12a. Thus, the winding part 1
By providing the gap S between the lines 2a, friction loss due to contact between the lines is avoided.

As shown in FIG. 4B, when the centering spring 12 is in a natural state, the centers of the plurality of windings are displaced in a direction opposite to the direction of transition of the centers of the windings due to the unwinding deformation. ing. In other words, the centering spring 12
The winding centers of the winding portions 12a are displaced in a direction opposite to the direction in which the winding centers shift when the relative rotation angle of the retainer 11 with respect to the outer ring 4 increases in an assembled state described later. When assembling the centering spring 12 to the first clutch portion 5, as shown in FIG. 3C, the centering spring 12 is extended in the circumferential direction with the interval between the pair of engagement portions 12a1 and 12a2. (At this time, the centering spring 12 is unwound and slightly expanded in diameter.) The pair of engaging portions 12a1, 12a
2 is a locking portion 11b of the retainer 11 and a locking portion 4 of the outer ring 4.
a2. Thereby, the retainer 11 is connected to the outer ring 4 via the centering spring 12 in the rotational direction.
At this time, each winding center of the centering spring 12 is located concentrically.

From this state, when the retainer 11 is rotated clockwise relative to the outer ring 4, for example, as shown in FIG. 4D, the centering spring 12 is rotated clockwise (forward in the rotational direction). The engaging portion 12a1 is pushed by the locking portion 11b of the retainer 11 and elastically displaces clockwise. At this time, the engaging portion 12a2 of the centering spring 12 in the counterclockwise direction (rearward in the rotation direction) is locked by the locking portion 4a2 of the outer race 4. Thereby, the centering spring 12
Is bent in a direction in which the interval between the pair of engagement portions 12a1 and 12a2 is expanded (diameter expanding direction), and an elastic force corresponding to the amount of bending is accumulated. In this case, the center of each winding of the centering spring 12 shifts with an increase in the relative rotation angle of the cage 11, but when the cage 11 is not rotated relative to each other, the centers of the windings are concentrically positioned. The deviation amount of each winding center when the container 11 is relatively rotated by a predetermined angle is a small amount. Thereafter, when the rotational force acting on the retainer 11 is released, the retainer 11 (the locking portion 11b) is centered at the neutral position shown in FIG. Is done. When the retainer 11 is relatively rotated counterclockwise from the state shown in FIG. 4C, the counterclockwise engaging portion 1 of the centering spring 12 is rotated.
2a2 is pushed by the locking portion 11b of the retainer 11 and elastically displaces in the counterclockwise direction, and an elastic force is accumulated in the centering spring 12 by the reverse operation.

As described above, since the amount of deviation of the center of each winding of the centering spring 12 during the relative rotation of the retainer 11 is reduced, interference with the projection 1a2 of the outer ring 1 as the input side member does not occur. . As a result, the degree of freedom in designing the clutch unit in which the first clutch portion 5 having the centering spring 12 is built in increases, and the clutch unit can be made more compact.

The above-described structure of the centering spring 12 can be applied to a spring of a tightening type. That is, the center of each winding of the wind-tightening centering spring Ya in the natural state shown in FIG. 23 (a) is set to the direction of transition of each winding center due to an increase in the relative rotation angle of the retainer in the assembled state. Displace in the opposite direction. Then, the retainer (locking portion Yb) in the assembled state shown in FIG.
During the non-relative rotation of, each winding center of the centering spring Ya is concentrically positioned. In this case, it is necessary to set the inner diameter of the centering spring Ya to a size that does not cause interference with the retainer due to the reduced diameter.

The centering spring 12 (Y
The structure of a) is similar to that of the first embodiment except that the first clutch 5
The present invention is not limited to the clutch unit having the two clutch portions, namely, the first clutch portion and the second clutch portion 6, but can be similarly applied to a clutch unit having a single clutch portion.

Next, the operation of the first clutch unit 5 will be described with reference to FIGS. FIG.
14, the centering spring 12 and the outer ring 4
Is schematically and conceptually shown. The description of the operation lever 13 is also omitted.

FIG. 12 shows the neutral position of the first clutch section 5 (the state shown in FIG. 8). In the neutral position, the roller 10 is located at the center of the cam surface 1d, and separates from the wedge gaps formed between the cam surface 1d and the circumferential surface 3a2 in both the forward and reverse rotation directions. The diameter of the roller 10 is set slightly smaller than the radial distance between the central portion of the cam surface 1d and the circumferential surface 3a2.
There is a radial gap between the center portion and the circumferential surface 3a2. As will be described later, the reverse input torque input from the output shaft 2 is locked by the second clutch unit 6 in both forward and reverse rotation directions. Therefore, the inner wheel 3 rotates only for the input torque input from the operation lever 13 (the outer wheel 1), and does not rotate even if the reverse input torque is input from the output shaft 2, and maintains its position. I do.

FIG. 13 shows a state in which an input torque is input to the outer wheel 1 by swinging the operation lever 13. For example, in FIG. 1, when an input torque in a counterclockwise direction is input to the outer race 1, the cam surface 1 is rotated as the outer race 1 rotates.
d moves counterclockwise relative to the roller 10, and the roller 10 is wedge-engaged in the wedge gap in that direction. Thus, the input torque from the outer ring 1 is transmitted to the inner ring 3 via the roller 10, and the outer ring 1, the roller 10, the retainer 11, and the inner ring 3 rotate counterclockwise as a unit. Then, the centering spring 12 bends with the rotation of the retainer 11, and the elastic force f corresponding to the amount of the bending is accumulated. The maximum range of the amount of rotation of the outer ring 1 is determined by the protrusion 1 a
It is regulated by the engagement of the outer ring 4 with the stopper 4a1 of the outer race 4.

FIG. 14 shows a state where the operating lever 13 (outer ring 1) is released from the state shown in FIG. Due to the elastic force f accumulated in the centering spring 12, a clockwise turning force acts on the retainer 11, and the roller 10 is pressed by the retainer 11 to press the cam surface 1d. Then,
Since the outer ring 1 is open, the roller 10, the cage 1
1 and the outer ring 1 idles clockwise with respect to the inner ring 3 to return to the neutral position shown in FIG. At that time, inner ring 3
Maintains the rotation position given by the rotation operation of FIG. Therefore, when the rotation operation in FIG. 13 is repeatedly performed, the rotation amount for each rotation operation is accumulated in the inner race 3 in a superimposed manner. In FIG. 12, when a clockwise input torque is input to the outer ring 1, the operation reverse to the above is performed.

FIG. 15 (section AA in FIG. 1) shows the second clutch unit 6. The second clutch portion 6 includes a circumferential surface 4c1 provided on the outer race 4, a plurality of (for example, eight) cam surfaces 2b1 provided on the output shaft 2, and a portion between each of the cam surfaces 2b1 and the circumferential surface 4c1. (For example, eight pairs in total), an elastic member interposed between the pair of rollers 20, for example, a leaf spring 21 having an N-shaped cross section, a column portion 3c of the inner ring 3, and an inner ring 3 Pin 3b1 and output shaft 2
And the pin hole 2b3 as a main element. Locking means is constituted by the cam surface 2b1, the circumferential surface 4c1, the pair of rollers 20, and the leaf spring 21, and the lock releasing means is constituted by the column portions 3c of the inner ring 3 located on both circumferential sides of the pair of rollers 20. The pin 3b1 of the inner ring 3 and the pin hole 2b3 of the output shaft 2 constitute a torque transmitting means. In this embodiment, the leaf spring 21 is formed of stainless steel (for example, SUS301CPS-H), and is subjected to a tempering process as a heat treatment. Grease is sealed in a space between the inner circumference of the outer race 4 and the outer circumference of the output shaft 2 (large-diameter portion 2b), in particular, between the cam surface 2b1 and the circumferential surface 4c1.

As shown in FIG. 16 in an enlarged manner, at the neutral position, the pair of rollers 20 are respectively formed by the leaf spring 21 in the forward and reverse rotation directions formed between the cam surface 2b1 and the circumferential surface 4c1. It is pressed in the direction of the wedge gap. At this time,
A rotation direction gap δ1 exists between each pillar 3c of the inner ring 3 and each roller 20. Also, the pin 3b of the inner ring 3
1 and the pin hole 2b3 of the output shaft 2, there are rotational gaps δ2 in both forward and reverse rotational directions. The rotation direction gap δ1 and the rotation direction gap δ2 have a relationship of δ1 <δ2. The size of the rotation direction gap δ1 is, for example, 0 to 0.4 m.
m (0 to 1.5 around the axis of the second clutch unit 6)
°), the size of the rotational gap δ2 is, for example, 0.4
About 0.8 mm (1.8 to 3.7 degrees around the axis of the second clutch unit 6).

In the state shown in the figure, for example, when a clockwise reverse input torque is input to the output shaft 2, the roller 20 in the counterclockwise direction (rearward in the rotational direction) engages with the wedge gap in that direction. Thus, the output shaft 2 is locked clockwise with respect to the outer ring 4. When a counterclockwise reverse input torque is input to the output shaft 2, the roller 20 in the clockwise direction (rearward in the rotational direction) engages with the wedge gap in that direction, and the output shaft 2 Locked clockwise. Therefore, the reverse input torque from the output shaft 2 is locked in the forward and reverse rotation directions by the second clutch unit 6.

FIG. 17 shows an initial state in which the input torque from the outer wheel 1 (clockwise in FIG. 17) is input to the inner wheel 3 via the first clutch portion 5, and the inner wheel 3 starts to rotate clockwise in FIG. The state is shown. Since the rotation direction gap is set to δ1 <δ2, first, the inner ring 3 is rotated counterclockwise (rearward in the rotation direction).
Is engaged with the roller 20 in that direction (rearward in the rotational direction), and presses this in the clockwise direction (forward in the rotational direction) against the elastic force of the leaf spring 21. As a result, the roller 20 in the counterclockwise direction (rearward in the rotation direction) is separated from the wedge gap in that direction, and the locked state of the output shaft 2 is released. Therefore, the output shaft 2 can rotate clockwise.

When the inner ring 3 is further rotated clockwise, the pin 3b1 of the inner ring 3 is engaged with the pin hole 2b3 of the output shaft 2 clockwise as shown in FIG. Thereby, the inner ring 3
Is transmitted to the output shaft 2 via the pin 3b1 and the pin hole 2b3, and the output shaft 2 rotates clockwise. When the input torque in the counterclockwise direction is input to the outer ring 1, the output shaft 2 rotates counterclockwise by the reverse operation. Therefore, the input torque in the forward and reverse rotation directions from the outer ring 1 is transmitted to the output shaft 2 via the first clutch portion 5, the inner ring 3, and the pin 3b1 and the pin hole 2b3 as the torque transmitting means, and the output shaft 2 Rotate in both forward and reverse rotation directions. Note that when the input torque from the inner ring 3 is lost, the plate spring 21 returns to the neutral position shown in FIG.

The outer ring 1, the output shaft 2, the inner ring 3, the outer ring 4, the first clutch part 5, the second clutch part 6, and the fixed side plate 7 described above.
When the friction member 9 is assembled in the manner shown in FIG. 1, the clutch unit of this embodiment is completed. An operation lever (13) made of, for example, resin is coupled to the outer ring 1,
The output shaft 2 is connected to a rotating member of an output-side mechanism (not shown). The fixed side plate 7 is fixedly fixed to a fixing member such as a casing (not shown) by a fixing portion 7b1. The outer ring 1 is prevented from falling off on both sides in the axial direction between a washer (or nut) 18 mounted on the outside of the flange 1c and the flange 4a of the outer ring 4.

In the first clutch portion 5, the centering spring 12 is accommodated in the inner periphery of the protruding portion 1a2 of the outer ring 1, and is disengaged on both axial sides between one end surface of the outer ring 1 and the flange portion 4a of the outer ring 4. Stop regulation. Further, the retainer 11 and the roller 10 are prevented from coming off on both sides in the axial direction between the flange 1c of the outer ring 1 and the flange 4a of the outer ring 4.
The retainer 11, the roller 10, and the centering spring 12 of the first clutch unit 5 are housed inside the outer race 1,
There is no protruding part on the input side. In addition, since the retainer 11 is externally inserted into the circumferential surface 3a2 of the inner race 3, and the rotation of the retainer 11 is guided by the circumferential surface 3a2 of the inner race 3, there is no inclination of the retainer 11 during the rotation. Smooth clutch operation is possible.

The second clutch section 6 includes the outer ring 4 and the fixed side plate 7.
It is compactly accommodated in the radial and axial directions in the space surrounded by. Further, since the pillar 3c as the unlocking means and the pin 3b1 as the torque transmitting means are provided integrally with the inner ring 3, the number of parts is small and the structure is simple. In addition, since the pocket 3c1 between the column portions 3c has a shape that is opened on one side (side plate 7 side) in the axial direction, after the output shaft 2, the inner ring 3, the outer ring 4, and the like are assembled, the roller 20 and the leaf spring 21 are removed. The pocket 3c1 can be incorporated into the pocket 3c1 from the opening in the axial direction, and the assembling work is easy.

Further, since the output shaft 2 is supported bilaterally by the radial bearing surface 3a1 of the inner race 3 and the radial bearing surface 7e2 of the fixed side plate 7, the rotation of the output shaft 2 is stabilized, and An unbalanced load hardly acts on the first clutch portion 5 and the second clutch portion 6, and a smooth clutch operation is possible.

FIG. 19 shows a seat 30 provided in a passenger compartment of an automobile. The seat 30 comprises a seat 30a and a backrest 30b, and a seat height adjusting device 3 for adjusting the height H of the seat 30a.
1. The seat tilt adjusting device 32 for adjusting the tilt θ of the backrest seat 30b, and the front-back position L of the seating seat 30a
Is provided with a seat slide adjusting device (not shown) for adjusting the position of the seat. The height H of the seat 30a is adjusted by the operation lever 31a of the seat height adjustment device 31, and the inclination θ of the backrest seat 30b is adjusted by the seat inclination adjustment device 3.
2 by the operation lever 32a, and the seat 30a
Is adjusted by an operation lever (not shown) of the seat slide adjustment device. The clutch unit according to the above-described embodiment is incorporated in, for example, the seat height adjusting device 31.

FIG. 20A shows a seat height adjusting device 31.
1 schematically shows an example of the structure of FIG. One ends of link members 31c and 31d are rotatably connected to the slide movable member 31b1 of the seat slide adjuster 31b. The other end of the link member 31c is pivotally connected to the sector gear 31f via a link member 31e. The sector gear 31f is pivotally attached to the seat 30a so as to be freely rotatable, and can swing around a fulcrum 31f1. Link member 3
The other end of 1d is pivotally connected to the seat 30a so as to be freely rotatable. The clutch unit X according to the above-described embodiment is fixed to an appropriate portion of the seat 30a via the fixed side plate 7 and has, for example, a resin operation lever 31a (corresponding to the operation lever 13 in FIGS. 8 and 9) attached to the outer ring 1 thereof. ) Are combined,
A pinion gear 31g meshing with the sector gear 31f is connected to the output shaft 2.

For example, in FIG. 20 (b), when the operation lever 31a is pivoted counterclockwise (upward), the input torque in that direction is transmitted to the pinion gear 31g via the clutch unit X, and the pinion gear 31g is rotated counterclockwise. Rotate clockwise. Then, the sector gear 31f meshing with the pinion gear 31g swings clockwise to pull the other end of the link member 31c via the link member 31e.
As a result, both the link member 31c and the link member 31d stand upright, and the seat surface of the seat 30a is raised. After adjusting the height H of the seat 30a in this manner, when the operation lever 31a is opened, the operation lever 31a is moved to the first position.
The clutch unit 5 rotates clockwise by the elastic force (elastic restoring force) of the centering spring 12 of the clutch unit 5 and returns to the original position (neutral position). When the operation lever 31a is swung clockwise (downward), the seating surface of the seat 31a is lowered by the reverse operation. When the operation lever 31a is released after the height adjustment, the operation lever 31 is released.
a rotates counterclockwise and returns to the original position (neutral position).

According to the seat height adjusting device 31 having the above-described structure, the seating seat 30 can be operated only by swinging the operation lever 31a.
The height H of the seat a can be adjusted, and the height position of the seating seat 30a after the height adjustment can be automatically held. Further, when the operation lever 31a is released after the height adjustment, the operation lever 31a can be automatically returned to the neutral position. Even in this case, the operation at the time of return is smooth, and there is no problem of noise generation such as a ratchet mechanism. further,
Since the frictional member 9 applies a braking force in the rotation direction to the output shaft 2, there is no (or little) reverse input torque return phenomenon when the operation lever 31a is operated, and a stable adjustment operation is possible.

Note that an inner ring 3 'shown in FIG. 21 may be used instead of the inner ring 3 in the clutch unit of the above-described embodiment. The inner ring 3 'shown in FIG.
The other part (the part composed of the flange portion 3b, the pillar portion 3c, and the pin 3b1) has a separate structure, and both portions are fixed by appropriate fixing means such as brazing. There is an advantage that it can be manufactured at relatively low cost and with high accuracy compared to the inner ring 3 having an integral structure.

[0068]

As described above, according to the present invention, the center of each winding in the natural state of the centering spring constituted by a plurality of winding torsion coil springs is increased when the operation amount of the retainer increases in the assembled state. Since the winding center is displaced in the direction opposite to the direction in which the winding is shifted, the amount of deviation of each winding center when the retainer is operated is reduced by an amount corresponding to the amount of deviation in the natural state, and the centering spring is displaced. And interference with the surrounding area hardly occurs. As a result, the diameter of the clutch unit is reduced, and the size of the clutch unit is reduced, and the degree of freedom in designing the clutch unit is improved.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a clutch unit according to an embodiment of the present invention.

FIG. 2A is a longitudinal sectional view of an outer ring (input side member).
FIG. 2B is a rear view thereof.

FIG. 3A is a longitudinal sectional view of an output shaft (output member).
FIG. 3B is a front view thereof.

FIG. 4A is a front view of an inner ring (control member), and FIG.
4B is a longitudinal sectional view, and FIG. 4C is an enlarged view of a main part thereof.

5 (a) is a front view of an outer race (stationary member), and FIG. 5 (b) is a longitudinal sectional view thereof.

6 (a) is a longitudinal sectional view of a fixed side plate, and FIG. 6 (b)
Is a front view thereof.

7A is a longitudinal sectional view of a friction member (braking means), and FIG. 7B is a front view thereof.

FIG. 8 is a sectional view taken along the line BB of FIG. 1 showing the first clutch unit.

FIG. 9 is a front view showing an operation lever.

10 (a) is a vertical sectional front view showing the retainer, FIG. 10 (b) is a vertical sectional side view thereof, and FIG. 10 (c) is a rear view thereof.

11A is a side view showing the natural state of the centering spring, FIG. 11B is a front view showing the natural state, and FIG. 11C is a front view showing the assembled state. 1
1 (d) is a front view showing the operation, and FIG. 11 (e) is an enlarged side view of the main part.

FIG. 12 is a conceptual diagram illustrating an operation of a first clutch unit (neutral position).

FIG. 13 is a conceptual diagram illustrating an operation of a first clutch unit (during torque transmission).

FIG. 14 is a conceptual diagram showing the operation of the first clutch unit (at the time of return).

FIG. 15 is a sectional view taken along the line AA of FIG. 1 showing a second clutch unit.

FIG. 16 is a partially enlarged front view showing an operation of a second clutch unit (neutral position).

FIG. 17 is a partially enlarged front view showing an operation of a second clutch unit (at the time of unlocking).

FIG. 18 is a partially enlarged front view illustrating an operation of a second clutch unit (when torque is transmitted).

FIG. 19 is a conceptual diagram showing an automobile seat.

20 (a) is a conceptual diagram showing an example of the structure of a seat height adjusting device, and FIG. 20 (b) is an enlarged view of a main part thereof.

FIG. 21 (a) is a rear view showing another example of the inner ring (control member), and FIG. 21 (b) is a longitudinal sectional view thereof.

22 (a) is a side view showing a natural state of a conventional centering spring, FIG. 22 (b) is a front view showing the natural state, and FIG. 22 (c) is a front view showing the assembled state. FIG. 22D is a front view showing the operation.

FIG. 23A is a front view showing a natural state of a conventional centering spring, and FIG. 23B is a front view showing an assembled state thereof.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Outer ring (input side member) 2 Output shaft (output side member) 3 Inner ring (control member) 4 Outer ring (stationary side member) 5 1st clutch part 6 2nd clutch part 7 Fixed side plate 11 Cage 12 Centering spring

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[Procedure amendment]

[Submission date] October 9, 2001 (2001.10.
9)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Claims

[Correction method] Change

[Correction contents]

[Claims]

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0019

[Correction method] Deleted

Claims (10)

[Claims] An input member to which a torque is input, an output member to which a torque is output, and a clutch portion provided in a torque transmission path between the input member and the output member. A clutch unit comprising: a retainer for controlling engagement and disengagement of an engagement element provided in the clutch portion; and a centering spring for centering the retainer, wherein the centering spring is constituted by a multi-turn torsion coil spring. The clutch unit is characterized in that each winding center in a natural state is displaced in a direction opposite to a direction in which each winding center shifts with an increase in the operation amount of the retainer in an assembled state. A first clutch provided between the input member and a control member interposed in a torque transmission path between the input member and the output member; A second clutch portion provided between the stationary side member to be restrained and the output side member, wherein the output side member receives the input torque from the input side member via the first clutch portion and the control member. Communicate to
The reverse input torque from the output side member is configured to be locked with the stationary side member via the second clutch portion, and the first clutch portion includes the engagement element, the retainer, and the A centering spring is disposed, the engaging element is interposed between the input-side member and the control member, and the retainer engages and disengages the engaging element through a relative rotation operation with respect to the stationary-side member. The clutch unit according to claim 1, wherein the centering spring controls the stationary side member and the retainer in a rotational direction. 3. The center of each winding of the centering spring,
The clutch unit according to claim 1, wherein the clutch unit is concentrically located when the retainer is not operated in an assembled state. 4. The clutch unit according to claim 1, wherein the centering spring is of a rewind type. 5. The clutch unit according to claim 1, wherein a cross-sectional shape of the centering spring is non-round. 6. The clutch unit according to claim 5, wherein a cross-sectional shape of the centering spring is rectangular. 7. The clutch unit according to claim 1, wherein the centering spring is wound with a gap between wires. 8. The clutch unit according to claim 1, wherein the clutch unit is used in a seat adjustment device for an automobile. 9. The clutch unit according to claim 8, wherein the input member is connected to an operation lever, and the output member is connected to a rotating member of the seat adjustment device. 10. The clutch unit according to claim 8, wherein the seat adjustment device is a seat height adjustment device for a seat.