JP2003097605A - Clutch unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clutch unit capable of surely returning an input side member to the neutral position by improving an elasticity member of a clutch unit. SOLUTION: While an input torque input to an outer ring 1 is transmitted to the output side member 2 through the medium of a clutch 8, a retainer 4 is rotated by the input torque so as to accumulate the elastic force in an elastic member 5 engaged with the retainer 4. The elasticity member 5 is composed by overlapping ended annular plate springs 5A and 5B. The outer ring 1 returns to the neutral position by the elastic force accumulated in the elastic member 5 when the input torque is opened.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch unit that transmits and cuts torque between an input side member and another member.

[0002]

2. Description of the Related Art Generally, in a mechanical clutch using an engaging member such as a roller or a ball, a clutch portion is arranged between an input side member and an output side member. Engage the engaging element in the wedge gap formed on the
It is configured to control transmission / interruption of the input torque by disengagement.

That is, when the engaging element engages with the wedge gap, the input side member and the output side member are locked via the engaging element, and the input torque is transmitted between both members via the engaging element. , By disengaging the engaging element from the wedge gap,
The input side member and the output side member are relatively rotatable, and the input torque is cut off between the both members.

[0004]

As an actual mechanism of the clutch portion, by repeatedly swinging the operating lever, the input side member is intermittently rotated to transmit the input torque to the output side member and output the output torque. There is one in which the amount of rotation for each operation is accumulated in a superimposed manner on the side member. In this case, each time the operating lever is operated once, it is necessary to return the operating lever to the neutral position by appropriate returning means while restricting the follow-up rotation of the output side member.

As the return means, each time the operation lever is operated, both ends of the torsion coil spring are twisted in opposite directions to accumulate elastic force, and when the operation lever is opened, the accumulated elastic force causes the operation lever to return force. A structure that gives

However, since the torsion coil spring has a length in the axial direction, when a torsional force in the opposite circumferential direction is applied to both ends, the elastic force becomes a moment force and a member (for example, an engaging member) that supports the elastic force. It acts on the cage that holds the mat. Therefore, the member is eccentric or tilted to cause friction with other surrounding members, and the friction loss at this time may lead to a shortage of the twisting torque and hinder the return operation of the operating lever.

The present invention has been made in view of the above circumstances, and its main object is to make it possible to reliably return the input side member to the neutral position by improving the elastic member of the clutch unit.

[0008]

In order to achieve the above technical object, a first means according to the present invention is an input side member to which torque is input, an output side member to which torque is output, and an input side member. Member provided between the output member and the output member, elastic force is accumulated by the input torque input to the input member, and the input member is neutralized by the accumulated elastic force as the input torque is released. The elastic member that is returned to (the position before the input torque is input) is characterized in that the elastic member is formed by a leaf spring having an end ring shape.

Here, the "input side member" is a member that has a cam surface that constitutes the clutch portion, and input torque is input through the operating member, and the "output side member" constitutes the clutch portion. For example, through the engagement / disengagement action of the engaging element,
It is a member having a function of rotating integrally with the input side member and a function of rotating relative to the input side member.

With such a structure, even if a torsion torque is applied to the elastic member as the input side member rotates, the point of action of the elastic force is displaced in the axial direction like a torsion coil spring. There is no. Therefore, moment force does not act on other members that support elastic force, and eccentricity and inclination of the member can be suppressed to minimize torque cross due to friction with other members. The member can be reliably returned to the neutral position.

In the first means, the clutch portion is provided in the torque transmission path between the input side member and the output side member, and an engaging element for transmitting the input torque from the input side member to the output side member. It is preferable to have a cage that has a pocket for holding the engaging element and that has a retainer that applies a restoring force to the input side member via the engaging element by the elastic force of the elastic member when the input torque is released.

This clutch portion forms a wedge gap between the input side member and the output side member, and when the input torque acts, an engaging element is engaged in the wedge gap to shift the input side member to the output side member. Transmit torque to. On the other hand, when the input torque is released, the accumulated elastic force acts on the retainer in the return direction, and the engaging element is pushed by the retainer to press the input side member in the return direction. Then, since the input side member is opened, the engaging element, the retainer, and the input side member rotate with respect to the output side member, and return to the neutral position. At this time, since the rotation position of the output side member is maintained as it is, the rotation amount for each operation can be accumulated in the output side member in a superimposed manner by repeating the above operation.

In the above-mentioned structure, it is desirable to form engaging portions which can engage with the retainer and the stationary member at both ends of the elastic member. In this case, by providing the engaging portion at one end and the engaging portion at the other end at circumferentially opposed positions, it is possible to prevent generation of a moment force due to release of the elastic force. Therefore, it is possible to prevent the eccentricity / inclination of the member that supports the elastic force, for example, the cage, and reduce the loss of the torsion torque due to the friction loss.

In this case, it is desirable that the retainer is formed with an opening which is engageable with the engaging portion of the elastic member and whose periphery is closed. If the opening that engages with the retainer has a closed peripheral shape (window type), compared to the case where a part of the opening is open to the retainer end face (notched type), The rigidity can be increased.

By providing stress adjusting portions near both ends of the elastic member, the stress distribution inside the elastic member after elastic deformation can be made uniform, and fatigue life reduction due to imbalance of the stress distribution can be avoided. be able to.

If two or more leaf springs are piled up as the elastic member, an arbitrary elastic force can be obtained by changing the number of leaf springs, and the elasticity suitable for the use conditions and applications can be obtained. Power can be secured easily. in this case,
If both ends of the leaf spring on the inner diameter side are bent at an acute angle to form a locking portion, and both ends of the leaf spring on the outer diameter side are locked by this locking portion,
It is possible to reliably prevent the phase shift and the falling of the outer diameter side leaf spring due to the action of the external force.

The input-side member is formed by connecting a first thin-walled member having a cam surface forming a clutch portion and a second thin-walled member to which an operating member for inputting torque is attached so as not to rotate relative to each other. Is desirable.

According to this structure, the input member is
Since the first thin-walled member and the second thin-walled member are separated and processed, the processing is facilitated and manufactured as compared with the case where they are integrally molded by cold forging or the like. The cost is cheap. In addition, the first thin member and the second thin member only need to ensure a minimum wall thickness according to their respective roles, and there is a useless wall portion as in the case of being integrally molded by cold forging or the like. Therefore, it is possible to reduce the weight of the input side member and thus the clutch unit. Moreover, since the first thin-walled member has the cam surface which is a component of the clutch portion, the second thin-walled member has the mounting portion for the operation member, so that the required rigidity or strength is required. The characteristics such as are different in both members. Therefore, the material, the processing conditions, or the processing conditions can be made different between the first thin-walled member and the second thin-walled member, and it is possible to perform processing, heat treatment, etc. while responding to the required characteristics of both members without waste. Becomes The “thin-walled member” here means a member that is thinner than the wall thickness when the input-side member is integrally molded.

In this case, the first thin-walled member and the second thin-walled member are joined by connecting the inner periphery of the end of the second thin-walled member (the end that regulates the axial movement of the cage) to the end of the first thin-walled member. It is desirable to perform this in a state of being arranged on the outer peripheral side. As a result, the axial dimension of the clutch unit can be made compact by the thickness of the second thin member, or the axial length of the engaging element can be extended by the thickness while suppressing an increase in the axial width of the unit. As a result, the torque rigidity of the clutch portion can be improved.

By the way, in the neutral clutch portion, in order to secure the function as a clutch, it is necessary to provide an initial clearance in the circumferential direction between the wedge clearance and the engagement element. The input side member is inevitable in the circumferential direction. On the other hand, if the input side member is preloaded in the axial direction, the displacement of the input side member is restrained, so that it is possible to reduce rattling.

On the other hand, the second means according to the present invention includes an input side member to which torque is input, an output side member to which torque is output, and a torque transmission path between the input side member and the output side member. An intervening control member, a stationary side member whose rotation is restricted, a first clutch portion provided between the input side member and the control member, and a first clutch portion provided between the stationary side member and the output side member. An input side includes two clutch portions and an elastic member that stores an elastic force by the input torque input to the input side member and returns the input side member to the neutral position by the stored elastic force when the input torque is released. The input torque of the member is transmitted to the output side member via the first clutch portion and the control member, and the reverse input torque from the output side member is locked between the stationary side member via the second clutch portion. The end of the elastic member Characterized by formed by a plate spring.

According to this structure, the rotational position of the output side member can be adjusted by the input torque from the input side member, and the reverse input torque from the output side member can be adjusted by the second clutch portion. Since it is locked, the position of the output side member after adjustment can be held. Moreover, by the action of the elastic member, it is possible to return the input side member to the neutral position after the position adjustment of the output side member, and even in that case, the operation at the time of return is smooth and noise such as ratchet mechanism is generated. There is no problem. By forming the elastic member with a leaf spring in the shape of an end ring, the same effects as the corresponding items of the first means can be obtained.

Also in the second means, a) The first clutch portion is interposed in the torque transmission path between the input side member and the output side member to transmit the input torque from the input side member to the control member. An engaging member and a pocket that holds the engaging member are provided, and a retainer that applies a restoring force to the input side member via the engaging member by the elastic force of the elastic member when the input torque is released is provided: b) At both ends of the elastic member , Forming an engaging portion engageable with the retainer and the stationary member: c) providing an engaging portion at one end and an engaging portion at the other end at circumferentially opposed positions: d) in the retainer, To form an opening that is engageable with the engaging portion of the elastic member and has a closed periphery: e) Providing stress adjusting portions near both ends of the elastic member. f) As the elastic member, a stack of two or more leaf springs is used: g) Both ends of the leaf spring on the inner diameter side are bent at an acute angle to form a locking portion, and the locking portion forms a plate on the outer diameter side. Locking both ends of the spring: h) The input side member is relatively non-rotatable between a first thin member having a cam surface that constitutes a clutch portion and a second thin member to which an operating member for inputting torque is attached. And i) arranging the inner circumference of the end of the second thin member on the outer peripheral side of the end of the first thin member: j) applying an axial preload to the input member: etc. Can be appropriately selected and combined, and with such a configuration, the same operational effects as the corresponding items of the first means can be obtained.

[0024]

BEST MODE FOR CARRYING OUT THE INVENTION A first embodiment of a clutch unit according to the present invention will be described below with reference to the drawings.

As shown in FIG. 1, the clutch unit of the first embodiment has an outer ring 1 as an input side member, an inner ring 2 as an output side member, a plurality of rollers 3 as engaging elements, and rollers. The retainer 4 for holding 3 and the elastic member 5 attached to the retainer 4 are main elements.

The outer ring 1 is a first thin member 1A shown in FIG.
And a second thin-walled member 1B shown in FIG. 3, and both thin-walled members 1A and 1B are manufactured by pressing a steel plate. If necessary, for example,
The second thin member 1B may be made of a molded product such as resin.

The second thin member 1A has a drum portion 1Ab in which a plurality of cam surfaces 1Aa are formed on the inner periphery at equal intervals in the circumferential direction.
And an inner diameter flange portion 1Ac extending from one end of the drum portion 1Ab to the inner diameter side, and an outer diameter flange portion 1Ad extending to the outer diameter side from the other end of the drum portion 1Ab.

Each cam surface 1Aa is deep in the central portion in the circumferential direction, and is shallower in an inclined shape from the central portion toward both sides in the circumferential direction. The inner diameter flange portion 1Ac serves to prevent the retainer 4 from slipping out in one axial direction and to maintain the coaxiality of the outer ring 1 with respect to the inner ring 2.

The outer diameter flange portion 1Ad is formed with a plurality of (six in the illustrated example) fitting grooves 1Ae used for coupling with the second thin member 1B, and extends from the outer diameter end in the axial direction. A plurality of (three in the illustrated example) stopper claws 1Af are formed on the opposite side of the drum portion 1Ab. These stopper claws 1Af are provided on one side of the first thin member 1A (see FIG. 1).
Rotation of the outer ring 1 by engaging with a stopper protrusion (not shown) of the stationary member 7 (see FIG. 8A) which is disposed on the right side of (a) and whose rotation is restricted, in the rotation direction. Is regulated within a predetermined range.

All of the first thin member 1A or the cam surface 1Aa
For example, heat treatment (surface hardening treatment) such as carburizing and tempering, carbonitriding and quenching tempering, induction hardening and soaking quenching and tempering is performed.

As shown in FIG. 3, the second thin-walled member 1B has a plurality of (six in the illustrated example) fitting claws extending axially from the outer diameter end toward the first thin-walled member 1A. 1Ba are formed, and the fitting claws 1Ba are fitted and press-fitted into the fitting grooves 1Ae of the first thin member 1A as shown in FIG. Directional relative movement is restricted. Then, under this state, the fitting claw 1Ba engages with the uneven portion of the operation lever 6 as an operation member mounted on the outer periphery thereof in the rotation direction,
The relative rotation of the operating lever 6 with respect to the outer ring 1 is restricted. In the illustrated example, two short claws 1B
Although the b is formed, these claws 1Bb are not used for joining with the first thin member 1A (they serve only to regulate the rotation direction).

A plurality (two in the illustrated example) of burring portions 1Bc extending in the axial direction toward the first thin member 1A are formed at the outer diameter side end of the second thin member 1B. ,
Bolt insertion holes (or screw holes) 1Bd are formed in the burring portions 1Bc, respectively.
By screwing the operation lever 6 through the through hole, the axial relative movement of the operation lever 6 with respect to the outer ring 1 is restricted.

Therefore, by rotating the operating lever 6, the first thin member 1A and the second thin member 1B are integrally rotated, whereby the input torque from the operating lever 6 is input to the outer ring 1. The inner ring 2 is provided with a circumferential surface 2a forming a wedge gap with the cam surface 1Aa of the outer ring 1 (first thin member 1A), and is connected to an output member (not shown).

According to this structure, the outer ring 1 as the input side member is manufactured by pressing two members, the first thin member 1A and the second thin member 1B. Therefore, as compared with the case where the outer ring 1 is integrally molded by cold forging or the like, the processing is facilitated and the manufacturing cost is low, and the outer ring 1 and thus the clutch unit can be reduced in weight. .

Further, the first thin member 1A has a cam surface 1Aa which is a constituent element of the clutch portion, whereas the second thin member 1B has a fitting claw 1Ba which is a connecting portion with the operating lever 6. Although both members 1A and 1B have different required rigidity or hardness, surface hardening treatment (heat treatment) is applied only to the first thin-walled member 1A, so that the respective required characteristics can be satisfied. You can deal with it without waste.

The cage 4 has a cylindrical shape, and as shown in FIG. 5, a plurality of (for example, 10) window-shaped pockets 4a for accommodating the rollers 3 and a pair of openings 4b circumferentially separated from each other.
Equipped with. Both openings 4b are window-shaped with their peripheries closed, and both openings 4b have engaging portions 5a1 and 5a of the elastic member 5 described later.
a2 is inserted respectively. (See FIG. 8A).

The material of the cage 4 is not particularly limited, but in this embodiment, the cage 4 is an injection molded product of a synthetic resin material, for example, a synthetic resin material in which 30% by weight of glass fiber is mixed with polyamide 66 (PA66). There is.

The clutch portion 8 according to the first embodiment
Mainly includes a cam surface 1Aa of the first thin member 1A of the outer ring 1, a circumferential surface 2a of the inner ring 2, a cage 4 interposed between the cam surface 1Aa and the circumferential surface 2a, and an elastic member 5. It is configured as an element. Further, the cam surface 1Aa, the circumferential surface 2a, and the roller 3 constitute a locking means, and the retainer 4 and the elastic member 5 constitute a returning means.

As shown in FIG. 6, the elastic member 5 is formed by rolling a metal strip plate material such as stainless steel into end plate-shaped leaf springs 5A and 5B, and stacking the two leaf springs 5A and 5B. Composed by combining. Leaf spring 5 on the inner diameter side
Among the both end portions of A, the engaging portions 5a1 and 5a2 are formed on one axial side by bending the respective tip portions toward the inner diameter side. Both engaging portions 5a1 and 5a2 are opposed to each other at a predetermined interval in the circumferential direction and are inserted into the opening 4b of the retainer 4, respectively. Further, locking portions 5b1 are formed on both ends of the inner diameter side leaf spring 5A on the other side in the axial direction by bending the tip end portions to the outer diameter side. The locking portion 5b1 has a role of locking both ends of the outer-diameter side leaf spring 5B, and restricting the leaf spring 5B from falling off and phase shift in the circumferential direction. As shown in FIG. 7, if both locking portions 5b1 are further bent in directions away from each other and the inclination angle θ is made an acute angle, such a regulating function can be further strengthened.

When assembling the elastic member 5, FIG.
(A) {In FIGS. 8 (a) and 8 (b), the leaf spring 5B on the outer diameter side is not shown for simplification of the drawing} ()
As shown in FIG. 4, the engaging portions 5a1 and 5a2 are inserted into the openings 4b of the retainer 4 in a state where the distance between the pair of engaging portions 5a1 and 5a2 is widened in the circumferential direction.
1, 5a2 to the circumferential side surfaces 4b1 and 4b of the opening 4b.
2 respectively. Locking portions 7a provided on the stationary side member 7 are arranged on the outer diameter sides of both side surfaces 4b1 and 4b2, and the elastic member 5 is engaged at the neutral position of the cage 4 shown in FIG. Both the parts 5a1 and 5a2 are the locking parts 7a.
Is also locked by. By the above assembling, the cage 4
Is rotatably connected to the stationary member 7 via the elastic member 5.

From this state, as shown in FIG.
For example, when the cage 4 is rotated relative to the stationary member in the clockwise direction, the engaging portion 5a of the engaging portions 5a1 and 5a2 of the elastic member 5 which is located in the clockwise direction (forward in the rotating direction).
1 is pushed by the side surface 4b1 of the cage 4 and elastically displaced clockwise. At this point, the engaging portion 5a2 of the elastic member 5 located in the counterclockwise direction (rearward in the rotational direction) is locked by the locking portion 7a of the stationary member 7. As a result, the elastic member 5 elastically bends in the direction in which the gap between the engaging portions 5a1 and 5a2 is widened, and the elastic force corresponding to the amount of bending is accumulated in the elastic member 5. After that, when the rotational force acting on the cage 4 is released, the elastic force of the elastic member 5 causes the cage 4 to return to the neutral position shown in FIG.

When the cage 4 is relatively rotated counterclockwise from the state shown in FIG. 7A, the counterclockwise engaging portion 5a2 of the elastic member 5 is pushed against the side surface 4b2 of the cage 4. The elastic member 5 is elastically displaced counterclockwise, and the elastic force is accumulated in the elastic member 5 by the operation opposite to the above.

By the way, when the cage 4 is rotated as shown in FIG. 8B, the stress distribution becomes non-uniform over the entire circumference of the elastic member 5, and the elastic member 4 flexes irregularly, which is not preferable. May be affected. In order to prevent this, as shown in FIGS. 9 (a) and 9 (b), it is desirable to form stress adjusting portions 5c near both ends of the leaf springs 5A and 5B.
The stress adjusting portion 5c partially weakens the spring rigidity,
For example, it can be configured by forming a hole in the leaf spring 5A as shown in FIG. 7A or by cutting off both axial side portions of the leaf spring 5B as shown in FIG. Whichever stress adjustment section 5c is used, the axial cross-sectional area of the leaf spring is reduced toward the end closer to the leaf springs 5A and 5B.

In FIGS. 9A and 9B, a hole is formed in the leaf spring 5A on the inner diameter side and a cut portion is formed in the leaf spring 5B on the outer diameter side as the stress adjusting portion 5c. A cutout portion may be formed in the leaf spring 5A on the inner diameter side, and a hole may be formed in the leaf spring 5B on the outer diameter side [see FIGS. 10 (a) and 10 (b)]. In this case, the same type of stress adjusting portions 5c may be formed in both the leaf springs 5A and 5B (holes may be formed in both, or cut portions may be formed in both). However, when both the stress adjusting portions 5c are holes, the inner diameter side and the outer diameter side of the elastic member 5 are in communication with each other through the holes, and the sealing property (for example, foreign matter is caught in the inner diameter side of the elastic member 5). Therefore, the stress adjusting portion 5 of at least one of the leaf springs (more desirably, the outer diameter side) is caused.
It is desirable to adopt a cut portion as c. The stress adjusting portion 5c may be provided on both of the leaf springs 5A and 5B as described above, or may be provided on only one of the leaf springs.

Next, the operation of the clutch unit of this embodiment will be described with reference to FIGS. 11 to 13. 11 to 13, the elastic member 5 and the stationary member 7 are schematically illustrated and are conceptually shown. The operation lever 6 is also omitted.

FIG. 11 shows the neutral position of the clutch unit (the state shown in FIG. 8A). In the neutral position, the roller 3 is located at the center of the cam surface 1Aa, and separates from the wedge gaps formed between the cam surface 1Aa and the circumferential surface 2a in both the forward and reverse directions. The diameter of the roller 3 is set to be slightly smaller than the radial distance between the central portion of the cam surface 1Aa and the circumferential surface 2a.
There is a radial gap between the central portion of the and the circumferential surface 2a. Further, in this embodiment, the reverse input torque input to the inner ring 2 from the output side is locked in both forward and reverse directions. Therefore, the inner ring 2 rotates only for the input torque input from the operation lever 6 (outer ring 1),
Even if reverse input torque is input from the output side, it does not rotate and maintains its position.

In FIG. 12, the operation lever 6 is rotated to
The state when input torque is input to the outer ring 1 is shown.
For example, in the figure, when a counterclockwise input torque is input to the outer ring 1, the cam surface 1Aa is rotated along with the rotation of the outer ring 1.
Moves counterclockwise with respect to the roller 3, and the roller 3 engages (engages) in the wedge gap. As a result, the input torque from the outer ring 1 is transmitted to the inner ring 2 via the roller 3, and the outer ring 1, the roller 3, the cage 4, and the inner ring 2 integrally rotate counterclockwise. The maximum amount of this rotation is restricted by the stopper protrusion of the stationary member 7 and the stopper claw 1Af of the outer ring 1. Then, the elastic member 5 bends with the rotation of the cage 4, and the elastic force f corresponding to the amount of bending is accumulated.

FIG. 13 shows a state in which the operation lever 6 (outer ring 1) is opened. By the elastic force f accumulated in the elastic member 5, a clockwise turning force acts on the cage 4,
The roller 3 is pushed by the retainer 4 and pushes the cam surface 1Aa. Then, since the outer ring 1 is opened, the roller 3, the cage 4, and the outer ring 1 rotate clockwise with respect to the inner ring 2 to return to the neutral position shown in FIG. Further, the inner ring 2 maintains the turning position given by the turning operation of FIG. 12 as it is. Therefore, when the turning operation of FIG. 12 is repeated, the turning amount for each turning operation is accumulated in the inner ring 2 in a superimposed manner.

11 to 13, when the clockwise input torque is input to the outer ring 1, the same operation as described above is performed (the operation direction is opposite). Alternatively, the input torque may be input from the inner ring side, in which case the cam surface is provided on the outer circumference of the inner ring and the circumferential surface is provided on the inner circumference of the outer ring.

FIG. 14 shows a comparative example of the present invention. In this clutch unit, a centering spring composed of a torsion coil spring is used as the elastic member 5 '. As shown in FIGS. 15 (a) and 15 (b), the centering spring 5'has engaging portions 5a1 'and 5a2' that are bent toward the inner diameter side at both ends of a plurality of winding portions.
1'and 5a2 'are at positions displaced in the axial direction.

The centering spring 5 is mounted on the outer circumference of the cage 4 '. The retainer 4 ′ is shown in FIGS.
As shown in FIG. 3, in addition to the plurality of pockets 4a ′, there are provided axially notched engaged portions 4b ′ having different depths at two positions in the circumferential direction of one end surface. Both of the engaging portions 5a1 'and 5a2' of the centering spring 5'are respectively locked to the engaged portion 4b ', and are close to the mating engaged portion on the peripheral surface of the engaged portion 4b'. Engage with the circumferential side surfaces 4b1 ', 4b2'. Then, as shown in FIG. 15D, the cage 4 '
The centering spring 5'bends due to the relative rotation of and the elastic force corresponding to the amount of the bending is accumulated in the centering spring 5 '.

When the torsion coil spring 5'is used as the elastic member as described above, since the engaging portions 5a1 ', 5a2' have a positional deviation in the axial direction, the action point P of the load received by the cage 4'from the spring is applied. , Q are also displaced in the axial direction, from which a moment M (see FIG. 16 (a)) acts on the cage 4 '. This moment load increases the friction between the cage 4'and the member (the output side member 2 in FIG. 1) fitted to the inner circumference of the cage 4 ', so that the return torque of the input side member 1 due to the elastic force is reduced. However, the return to the neutral position may be hindered. Further, since the engaged portions 4b 'have different depths, stress becomes excessive near the point Q, which is thinner than the point P, and the cage 4'may be damaged.

On the other hand, the elastic member 5 shown in FIGS.
If the end-shaped ring-shaped leaf springs 5A and 5B shown in FIG. 0 are used, the positions of the engaging portions 5a1 and 5a2 can be aligned in the axial direction. Therefore, the moment load does not act on the cage 4, and therefore, the return torque after the turning operation is increased, and the outer ring 1 and the operation lever 6 can be reliably returned to the neutral position.

In order to confirm the above effects, regarding the clutch unit (invention product) shown in FIG. 1 and the clutch unit (comparative product) shown in FIG. 14, the torque generated by a single elastic member and the operation lever 6 are respectively. Measure the return force,
When the friction loss was calculated, in the comparative product, the generated torque was 170 [N · cm] and the restoring force was 60 [N · cm],
The friction loss became 110 [N · cm], but in the product of the present invention, the generated torque was 110 [N · cm] and the restoring force was 80.
At [N · cm], the friction loss amount was 20 [N · cm], and it was confirmed that the friction loss of the return torque could be significantly reduced.

When the end-ring-shaped leaf springs 5A and 5B are used as the elastic member 5, the openings 4b formed in the cage 4 can have the same size, and therefore the openings 4 can be formed.
There is no extremely thin part around b, therefore
The strength of the cage 4 can be improved.

The number of leaf springs used as the elastic member 5 can be determined according to the required return torque. Therefore, in addition to using two as described above, only one,
Alternatively, three or more sheets can be stacked and used. In this way, the return torque can be easily adjusted by increasing or decreasing the number of leaf springs used.

Next, a second embodiment of the clutch unit according to the present invention will be described.

As shown in FIG. 17, the clutch unit of the second embodiment has an outer ring 1 as an input side member,
The output shaft 12 as the output side member, the inner ring 13 as the control member, the outer ring 14 as the stationary side member, the first clutch portion 15 provided between the outer ring 1 and the inner ring 13, the outer ring 14 and the output The second clutch portion 1 provided between the shaft 12 and
6 and 6 as main elements.

The outer ring 1 as the input side member is composed of the first thin member 1A and the second thin member 1B, as in the first embodiment. In the first embodiment, both members 1A and 1B
The inner diameter side end portion of the second thin wall member 1 </ b> A is closely attached in the axial direction as is clear from FIGS. 1 to 4. Perimeter of
More specifically, it is arranged on the outer periphery of the inner diameter flange portion 1Ac, and the end surfaces 1Ag, 1Bg of both members 1A, 1B are arranged on the same plane in the radial direction. In addition, in this second embodiment,
By interposing an elastic body 29 made of a corrugated spring or a disc spring between the washer 28 and the end surface of the first thin member 1A, a configuration for applying an axial preload to the outer ring 1 is added.

Since the structure of the outer ring 1 other than this is the same as that shown in FIGS. 2 to 4, the illustration and description of the individual parts thereof will be omitted, and the description of the clutch unit will be given below. 2 to 4 and the reference numerals attached to them are used. Further, the cage 4 and the elastic member 5 have the same configurations as those shown in FIG. 5 to FIG. In describing the units, FIGS. 5 to 10 and the reference numerals attached to them will be used.

FIG. 18 shows an output shaft 12 as an output side member.
Is shown. The output shaft 12 has a journal portion 1 on one end side.
2a, a large diameter portion 12b on the center side, and a connecting portion 12c on the other end side. The journal portion 12a has an inner ring (1
3: (see FIG. 19) is inserted into the radial bearing surface (13a1). A plurality (eg, eight) is provided on the outer circumference of the large-diameter portion 12b.
Cam surfaces 12b1 are formed at equal intervals in the circumferential direction. Each cam surface 12b1 is formed in a flat surface shape forming a chord with respect to a circle centered on the axis of the output shaft 12. Also, the large diameter portion 1
A plurality of (e.g., eight) pin holes 12b3 in the axial direction are formed at predetermined intervals on the one end side portion of 2b. The pin (13b1) of the inner ring (13) is inserted into these pin holes 12b3. An annular recess 12b4 is formed at the other end of the large diameter portion 12b. A friction member (19: see FIG. 22) described later is press-fitted into the annular recess 12b4, and
The inner peripheral wall 12b5 of the annular recess 12b4 has a radial bearing surface (17e2) of a fixed side plate (17: see FIG. 21) described later.
Becomes the journal surface to be inserted into. In the connecting portion 12c,
A tooth mold 12c1 for connecting another rotating member is formed.

The output shaft 12 is formed by forging from a steel material such as case-hardened steel, carbon steel for machine structure, bearing steel, etc., and is subjected to carburizing and quenching tempering, carbonitriding and quenching tempering, induction hardening and soaking quenching and tempering. Appropriate heat treatment is performed. In this embodiment, case hardening steel (for example, chrome molybdenum steel SCM42) is used as the steel material forming the output shaft 12.
0) is used and is subjected to carburizing quenching and tempering as a heat treatment to adjust the surface hardness of the surface layer portion to 57 to 62 HRC. The output shaft 12 may be a machined steel product.

FIG. 19 shows the inner ring 13 as a control member. The inner ring 13 includes a tubular portion 13a and a tubular portion 13a.
Mainly includes a flange portion 13b extending from one end to the outer diameter side and a plurality of (for example, eight) column portions 13c extending from the outer diameter end of the flange portion 13b to one side in the axial direction. The tubular portion 13 a is externally inserted into the journal portion 12 a of the output shaft 12 and also inside the outer ring 1. Tubular part 13a
The journal portion 1 of the output shaft 12 is provided on the inner periphery of the other end side portion of the
Radial bearing surface 13a1 for supporting 2a in the radial direction
The outer peripheral surface of the other end portion of the tubular portion 13a is formed with a circumferential surface 13a2 that forms a wedge gap between the cam surface 1Aa of the outer ring 1 in both forward and reverse rotation directions. Flange part 13
A plurality of (e.g., eight) pins 13b1 protruding in one axial direction are formed in b at predetermined intervals in the circumferential direction. These pins 13b1 are inserted into the pin holes 12b3 of the output shaft 12, respectively. Also, the column portions 13c adjacent to each other in the circumferential direction
In between, there is a pocket 13 opening toward one side in the axial direction.
c1 is formed, and the roller (30) and the leaf spring (31) of the second clutch portion (16: see FIG. 24) described later are housed in these pockets 13c1. Since the roller (30) and the leaf spring (31) can be incorporated into the pocket 13c1 from the axial opening of the pocket 13c1, the assembling work is easy.

The inner ring 13 is formed by forging from a steel material such as case-hardened steel, carbon steel for machine structure, bearing steel, etc. Is heat treated. In this embodiment, case hardening steel (for example, chrome molybdenum steel SCM420) is used as the steel material forming the inner ring 13.
Is used as the heat treatment, and the surface hardness of the surface layer portion is adjusted to 57 to 62 HRC. The inner ring 13 may be a machined steel product or a press-formed product of a steel plate (for example, cold rolled steel plate).

FIG. 20 shows the outer ring 14 as a stationary member. The outer ring 14 includes a flange portion 14a extending in the radial direction, a tubular portion 14c extending axially in one direction from the outer diameter end of the flange portion 14a, and a flange portion protruding from one end of the tubular portion 14c to the outer diameter side. 14d and mainly. On the flange portion 14a, a plurality of (for example, two) stopper portions 14a1 protruding in the other axial direction are arrayed at predetermined intervals in the circumferential direction. These stopper portions 14a1 engage with the stopper claws 1Af of the outer ring 1 in the rotation direction to regulate the rotation range of the outer ring 1. Further, the flange portion 14a is formed with a pair of locking portions 14a2 protruding in the other axial direction and a plurality of (for example, two) mounting portions 14a3, and the circumferential outer surface of the pair of locking portions 14a2. The engaging portions 5a1 and 5a2 of the elastic member 5 of the first clutch portion (15) are locked to the respective portions (see FIG. 8). Further, the elastic member 5 is mounted on the outer periphery of the mounting portion 14a3.

On the inner circumference of the cylindrical portion 14c, there is formed a circumferential surface 14c1 which forms a wedge gap between the cam surface 12b1 of the output shaft 12 in both forward and reverse rotation directions. A plurality of (for example, six) notches 14d1 are formed in the flange 14d at predetermined intervals in the circumferential direction. The notch portion 14d1 fits with a caulking portion (17c: see FIG. 21) of the fixed side plate (17) described later.

The outer ring 14 is formed by forging from a steel material such as case-hardened steel, carbon steel for machine structure, bearing steel, etc. Is heat treated. In this embodiment, case hardening steel (for example, chrome molybdenum steel SCM420) is used as the steel material forming the outer ring 14.
Is used as the heat treatment, and the surface hardness of the surface layer portion is adjusted to 57 to 62 HRC. The outer ring 14 may be a machined steel product or a press-formed product of a steel plate (for example, cold rolled steel plate).

FIG. 21 shows a fixed side plate 17 fixed to the outer ring 14. The fixed side plate 17 includes a flange portion 17a extending in the radial direction and a plurality of (for example, four) bracket portions 17 protruding outward from the outer diameter end of the flange portion 17a.
b, a plurality (for example, 6) of caulking portions 17c that project in one axial direction from the outer diameter end of the flange portion 17a, and a plurality of (for example, 8) engagement holes 17 that are formed in the flange portion 17a.
The main components are a1 and a boss portion 17e projecting from the inner diameter end of the flange portion 17a in one axial direction. The four bracket portions 17b are formed at predetermined intervals in the circumferential direction, and hollow pin-shaped caulking portions 17b1 are integrally (or separately) formed in each of them. The six caulking portions 17c are formed at predetermined intervals in the circumferential direction, and each of the six caulking portions 17c includes a pair of bifurcated claw portions 17c1. This caulking portion 17c is attached to the notch portion 14d1 of the outer ring 14, and the pair of claw portions 17c
By caulking 1 in the opposite directions in the circumferential direction and bringing it into contact with the flange portion 14d, it is possible to prevent relative movement of the outer ring 14 with respect to the fixed side plate 17 in the axial direction and in the rotational direction. The caulking portion 17b1 is caulked and fixed in the mounting hole of the mating member.

A radial bearing surface 17e2 is formed on the inner circumference of the boss portion 17e. The boss 17e is inserted into the annular recess 12b4 of the output shaft 12, and a friction member (1) described later is provided between the outer periphery of the boss 17e and the outer peripheral wall of the annular recess 12b4.
9: see FIG. 22). The engaging hole 17a1 engages with the convex portion (19a) of the friction member (19) in the rotational direction,
The relative rotation of the friction member (19) with respect to the fixed side plate 17 is prevented. The radial bearing surface 17e2 of the boss portion 17e is externally inserted into the journal surface 12b5 of the annular recess 12b4 to support the journal surface 12b5 in the radial direction.

The fixed side plate 17 is formed by pressing a steel plate material such as cold rolled steel plate, for example. In this embodiment, cold-rolled steel plate (for example, SPCE) is used as the steel plate material forming the fixed side plate 17. Further, in consideration of workability when caulking the caulking portions 17c and 17b1, heat treatment is not performed. In addition, carburizing and tempering (or carbonitriding and quenching and tempering) may be performed by performing carburizing prevention (or carburizing and denitrifying treatment) on the portion to be crimped such as the crimped portions 17c and 17b1.

FIG. 22 shows a friction member 19 as a braking means.
Is shown. In this embodiment, the friction member 19 has a ring shape, and a plurality of friction members (for example, 8
Convex portions 19a are formed at predetermined intervals in the circumferential direction.
The convex portion 19a engages with the engaging hole 17a1 of the fixed side plate 17 in the rotation direction, and prevents the friction member 19 from rotating relative to the fixed side plate 17.

The friction member 19 is made of an elastic material such as rubber or synthetic resin, and is, for example, the annular recess 12b4 of the output shaft 12.
It is press-fitted to the outer peripheral wall with a tight margin. The frictional force generated between the outer periphery of the friction member 19 and the outer peripheral wall of the annular recess 12b4 causes the output shaft 12 to have a braking force in the rotational direction (friction braking force).
Is given. The magnitude of this braking force (braking torque) is
It may be appropriately set in consideration of the magnitude of the reverse input torque input to the output shaft 12, but from the viewpoint of effectively preventing the reverse input torque recirculation phenomenon, the magnitude is approximately the same as the assumed reverse input torque. It is preferable to set the height. In the case of the seat height adjusting device, the reverse input torque that acts on the output shaft 12 when the seated person is seated on the seat (for example, 1
0-60 kgf. It is better to set the size to cm.
When the friction member 19 is used as the braking means as in this embodiment, there is an advantage that the braking force can be set or changed by adjusting the interference of the friction member 19.

The material of the friction member 19 is not particularly limited, but in this embodiment, the friction member 19 is an injection molded product of a synthetic resin material, for example, a synthetic resin material in which 30% by weight of glass fiber is mixed with polyacetal (POM). .

FIG. 23 (cross section BB in FIG. 17) shows the first clutch portion 15. The first clutch portion 15 includes a plurality of (for example, 10) cam surfaces 1Aa provided on the outer ring 1.
And the circumferential surface 13a2 provided on the inner ring 13 and the cam surface 1
A plurality of (for example, nine) rollers 20 as engaging elements interposed between Aa and the circumferential surface 13a2, a retainer 4 that holds the rollers 20 (see FIG. 5), and the retainer 4 to the outer ring (14).
And an elastic member 5 (see FIG. 6) that is connected in the direction of rotation as a main element. Cam surface 1Aa, circumferential surface 13a
2, the roller 20 constitutes a locking means, and the retainer 4 and the elastic member 5 constitute a returning means. In this embodiment, the cam surface 1Aa is the circumferential surface 13
A wedge gap is formed between a2 and the a2 in both forward and reverse rotation directions. Further, an operation lever 23 is coupled to the outer wheel 1, and a forward or reverse input torque is input from the operation lever 23 to the outer wheel 1. In addition, the inner circumference of the outer ring 1 and the inner ring 13 (the tubular portion 13
Grease is filled in the space between the outer circumference of a), especially between the cam surface 1Aa and the circumferential surface 13a2.

The structure of the first clutch portion 15 is different from that of the clutch portion 8 of the above-described first embodiment in that the inner ring 13 is
Is a control member arranged on the outer peripheral side of the output shaft 12 as the output side member, and the other configurations are the same. Therefore, the operation of the first clutch portion 15 is substantially the same as the description based on the above-mentioned FIGS. 11 to 13, and therefore the reference numerals of the corresponding constituent elements in each of these drawings are given in parentheses. The description is omitted.

FIG. 24 (section AA in FIG. 17) shows the second clutch portion 16. The second clutch portion 16 includes a circumferential surface 14c1 provided on the outer ring 14, a plurality (for example, eight) cam surfaces 12b1 provided on the output shaft 12, and a gap between each cam surface 12b1 and the circumferential surface 14c1. A pair of rollers 30 (for example, a total of 8 pairs) as an intervening member, an elastic member interposed between the pair of rollers 30, such as a leaf spring 31 having an N-shaped cross section, a column portion 13c of the inner ring 13, and an inner ring 13. The pin 13b1 and the pin hole 12b3 of the output shaft 12 are configured as main elements. Cam surface 12b1, circumferential surface 1
4c1, the pair of rollers 30, and the leaf spring 31 constitute a locking means, and the pillar portions 13c of the inner ring 13 located on both sides in the circumferential direction of the pair of rollers 30 constitute a lock releasing means, and the pin 13b1 of the inner ring 13 and The pin hole 12b3 of the output shaft 12 constitutes torque transmitting means. In this embodiment, the leaf spring 31 is made of stainless steel (for example, SUS301CPS-H),
Tempering is applied as heat treatment. Also, the outer ring 1
Grease is filled in the space between the inner circumference of the shaft No. 4 and the outer circumference of the output shaft 12 (large diameter portion 12b), particularly between the cam surface 12b1 and the circumferential surface 14c1.

As shown in an enlarged view in FIG. 25, in the neutral position, the pair of rollers 30 are formed by the leaf springs 31 in the normal and reverse rotational directions formed between the cam surface 12b1 and the circumferential surface 14c1, respectively. It is pressed in the direction of the wedge gap. At this time, there is a rotational gap δ1 between each column portion 13c of the inner ring 13 and each roller 30. Also, the inner ring 13
A rotational gap δ2 exists between the pin 13b1 and the pin hole 12b3 of the output shaft 12 in both the forward and reverse rotational directions. The rotational gap δ1 and the rotational gap δ2 are δ1 <
It has a relationship of δ2. The size of the rotational gap δ1 is, for example, about 0 to 0.4 mm (0 to 1.5 ° about the axis of the second clutch portion 16), and the size of the rotational gap δ2 is, for example, 0.4 to. It is about 0.8 mm (1.8 to 3.7 ° about the axis of the second clutch portion 16).

In the state shown in the figure, for example, when a counterclockwise input torque is input to the output shaft 12, the roller 30 in the counterclockwise direction (rearward in the rotational direction) is wedge-engaged with the wedge gap in that direction. The output shaft 12 is locked in the clockwise direction with respect to the outer ring 14. When a counterclockwise reverse input torque is input to the output shaft 12, the roller 30 rotates clockwise (rotationally rearward).
Engages with the wedge gap in that direction, and the output shaft 12 becomes the outer ring 1
It is locked counterclockwise with respect to 4. Therefore, the reverse input torque from the output shaft 12 is locked by the second clutch portion 16 in both forward and reverse rotation directions.

In FIG. 26, the input torque (clockwise in the figure) from the outer wheel 1 is input to the inner ring 13 via the first clutch portion 15, and the inner ring 13 starts to rotate clockwise in the figure. It shows the state. Since the clearance in the rotation direction is set to δ1 <δ2, first, the counterclockwise (rearward in the rotation direction) column portion 13c of the inner ring 13 engages with the roller 30 in that direction (rearward in the rotation direction), and The leaf spring 31 is pressed in the clockwise direction (forward in the rotation direction) against the elastic force. This allows
The roller 30 in the counterclockwise direction (rearward in the rotation direction) separates from the wedge gap in that direction, and the locked state of the output shaft 12 is released. Therefore, the output shaft 12 can be rotated clockwise.

When the inner ring 13 is further rotated clockwise,
As shown in FIG. 27, the pin 13b1 of the inner ring 13 engages with the pin hole 12b3 of the output shaft 12 in the clockwise direction. As a result, the clockwise input torque from the inner ring 13 is applied to the pin 13b.
1 is transmitted to the output shaft 12 via the pin hole 12b3, and the output shaft 12 rotates clockwise. When the counterclockwise input torque is input to the outer ring 1, the output shaft 12 rotates counterclockwise by the operation opposite to the above. Therefore, the input torque from the outer ring 1 in both the forward and reverse rotation directions is transmitted to the output shaft 12 through the first clutch portion 15, the inner ring 13, and the pin 13b1 and the pin hole 12b3 as the torque transmitting means, and the output shaft 12 Rotates in both forward and reverse rotation directions. When the input torque from the inner ring 13 disappears, the leaf spring 3
The elastic restoring force of 1 returns to the neutral position shown in FIG.

The above-mentioned outer ring 1, output shaft 12, inner ring 13,
The outer ring 14, the first clutch portion 15, the second clutch portion 16,
When the fixed side plate 17 and the friction member 19 are assembled in the manner shown in FIG. 17, the clutch unit of this embodiment is completed. The outer ring 1 has, for example, a resin operating lever 23.
Are coupled, and the output shaft 12 is coupled to a rotating member of an output side mechanism (not shown). Further, the fixed side plate 17 is caulked and fixed by a caulking portion 17b1 to a fixing member such as a casing (not shown). The outer ring 1 includes a washer (or nut) 28 mounted on the outer side of the second thin plate member 1B and the outer ring 1.
With respect to the flange portion 14a of No. 4, it is prevented from coming off on both sides in the axial direction.

In the first clutch portion 15, the elastic member 5
Is housed in the inner periphery of the stopper claw 1Af of the outer ring 1 (first thin member 1A), and is prevented from slipping out on both axial sides between one end surface of the outer ring 1 and the flange portion 14a of the outer ring 14. Further, the cage 4 and the roller 20 are prevented from slipping out on both axial sides between the inner diameter flange portion 1Ac of the outer ring 1 and the flange portion 14a of the outer ring 14. The retainer 4, the roller 20, and the elastic member 5 of the first clutch portion 15 are housed inside the outer ring 1, and there is no protruding portion on the input side portion. In addition, the cage 4 is externally inserted into the circumferential surface 13a2 of the inner ring 13, and the rotation of the cage 4 causes the circumferential surface 13a2 of the inner ring 13 to rotate.
Since it is guided by, there is no inclination of the retainer 4 during rotation, and smooth clutch operation is possible.

The second clutch portion 16 is compactly housed in the radial direction and the axial direction in the space surrounded by the outer ring 14 and the fixed side plate 17. Further, the pillar portion 13c as the unlocking means and the pin 13b1 as the torque transmitting means.
Is integrally formed with the inner ring 13, the number of parts is small and the structure is simple. Further, since the pocket 13c1 between the pillar portions 13c has a shape that is open to one side in the axial direction (on the side of the fixed side plate 17), after the output shaft 12, the inner ring 13, the outer ring 14 and the like are assembled, the roller 30 and the leaf spring 31 are separated. From the axial opening of the pocket 13c1 to the pocket 13c
It can be incorporated into one and the assembling work is easy.

Further, the output shaft 12 is fixed to the radial bearing surface 13a1 of the inner ring 13 and the radial bearing surface 17e of the fixed side plate 17.
Since the structure is supported in a two-sided manner by 2, the rotational movement of the output shaft 12 is stable, and an unbalanced load is less likely to act on the first clutch portion 15 and the second clutch portion 16, and smooth clutch operation is possible. Is.

Moreover, since the outer ring 1 as the input side member is manufactured by pressing the two members of the first thin member 1A and the second thin member 1B, This simplifies the manufacturing cost and makes it possible to reduce the weight of the outer ring 1 and thus the clutch unit.

Further, the first thin member 1A and the second thin member 1
Although the required rigidity or hardness is different from that of B, the required characteristics can be met without waste by performing surface hardening treatment (heat treatment) only on the first thin member 1A.

FIG. 28 shows a seat 40 installed in a passenger compartment of an automobile. The seat 40 includes a seat 40a and a backrest 40b, and a seat height adjusting device 4 for adjusting the height H of the seat 40a.
1, a seat inclination adjusting device 42 for adjusting the inclination θ of the backrest seat 40b, and the front-back position L of the seat 40a
The seat slide adjusting device (not shown) for adjusting The height H of the seat 40a is adjusted by the operating lever 41a of the seat height adjusting device 41, and the inclination θ of the backrest seat 40b is adjusted by the seat inclination adjusting device 4.
2 operation lever 42a, seat seat 40a
The front-rear position L of the vehicle is adjusted by an operation lever (not shown) of the seat slide adjusting device. The clutch unit of the above-described embodiment is incorporated in the seat height adjusting device 41, for example.

FIG. 29A shows a seat height adjusting device 41.
1 conceptually shows one structural example. One ends of link members 41c and 41d are rotatably and pivotally attached to the slide movable member 41b1 of the seat slide adjuster 41b. The other ends of the link members 41c and 41d are pivotally attached to the seat 40a, respectively. Link member 41c
The other end of the sector gear 41f via the link member 41e.
Is rotatably pivoted to. The sector gear 41f is pivotally attached to the seat 40a so as to be rotatable, and can swing around a fulcrum 41f1. The other end of the link member 41d is rotatably pivotally attached to the seat 40a. The clutch unit X of the above-described embodiment is fixed to an appropriate portion of the seat 40a via the fixed side plate 17, and the outer ring 1 thereof has, for example, a resin operation lever 41a (operation lever 2 in FIG. 23).
(Corresponding to 3), and the sector gear 41 is connected to the output shaft 12.
A pinion gear 41g that meshes with f is connected.

For example, in FIG. 29 (b), when the operating 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 turned counterclockwise. Rotate clockwise. Then, the sector gear 41f meshing with the pinion gear 41g swings clockwise and pulls the other end of the link member 41c via the link member 41e.
As a result, the link member 41c and the link member 41d both stand up, and the seating surface of the seat 40a becomes higher. When the operating lever 41a is opened after adjusting the height H of the seat 40a in this manner, the operating lever 41a moves to the first position.
The clutch 15 is rotated clockwise by the elastic force (elastic restoring force) of the elastic member 5 to return to the original position (neutral position). When the operation lever 41a is rocked in the clockwise direction (downward), the seat surface of the seat 41a is lowered by the reverse operation. When the operation lever 41a is opened after the height adjustment, the operation lever 41a rotates counterclockwise and returns to the original position (neutral position).

According to the seat height adjusting device 41 having the above structure, the seat 40 can be seated only by swinging the operating lever 41a.
The height H of the seat a can be adjusted, and the height position of the seat 40a after the height adjustment can be automatically maintained. Further, when the operation lever 41a is opened after the height adjustment, the operation lever 41a can be automatically returned to the neutral position, and even in that case, the operation at the time of return is smooth and the noise generation problem of the ratchet mechanism does not occur. further,
Since the braking force in the rotational direction is applied to the output shaft 12 by the friction member 19, there is no (or little) reflux phenomenon of the reverse input torque when the operation lever 41a is operated, and stable adjustment operation is possible.

[0091]

As described above, according to the clutch unit of the present invention, since the leaf spring having an end ring shape is used as the elastic member, the points of action of the elastic force are arranged at the circumferentially opposed positions. can do. Therefore, during the rotation of the input side member, the moment load does not act on the member that supports the elastic force of the clutch portion. Therefore, the loss of the return torque due to the friction between the member and other members can be reduced. Therefore, the input side member can be reliably returned to the neutral position.

Further, in the input side member composed of the first and second thin-walled members, the inner circumference of the end portion of the second thin-walled member is arranged on the outer peripheral side of the end portion of the first thin-walled member, so that a required axial space Can be reduced. Therefore, the clutch unit can be made compact. Further, since the length of the engaging element can be extended, the torque rigidity of the clutch portion can be improved and the operation stability can be improved.

Furthermore, by applying a preload to the input side member in the axial direction, it is possible to eliminate rattling of the input side member due to the initial clearance of the clutch portion, etc., and to improve the operational feeling. it can.

[Brief description of drawings]

FIG. 1 is a vertical sectional side view showing an overall configuration of a clutch unit according to a first embodiment {FIG. 1 (a)}, B in FIG. 1 (a).
It is a -B sectional view {Fig. 1 (b)}.

FIG. 2 is a perspective view showing a first thin member of the input side member of the clutch unit according to the first embodiment {FIG. 2 (a)}, a longitudinal side view {FIG. 2 (b)}, a front view {FIG. 2]. (C)}.

FIG. 3 is a perspective view showing a second thin member of the input side member of the clutch unit according to the first embodiment {FIG. 3 (a)}, a longitudinal side view {FIG. 3 (b)}, a front view {FIG. (C)}.

FIG. 4 is a single perspective view showing an input side member of the clutch unit according to the first embodiment.

FIG. 5 is a perspective view showing a retainer of the clutch unit according to the first embodiment.

FIG. 6 is a perspective view showing an elastic member of the clutch unit according to the first embodiment.

7 is a perspective view showing a leaf spring on the inner diameter side of the elastic member shown in FIG.

FIG. 8 is a front view showing the action of the elastic member of the clutch unit according to the first embodiment, and FIG. 8 (a) shows a neutral state,
The figure (b) shows the state where the input torque is input.

9A and 9B are perspective views showing another example of the elastic member of the clutch unit according to the first embodiment. FIG. 9A shows a leaf spring on the inner diameter side, and FIG. 9B shows a leaf spring on the outer diameter side. .

10A and 10B are perspective views showing another example of the elastic member of the clutch unit according to the first embodiment, wherein FIG. 10A shows a leaf spring on the inner diameter side, and FIG. 10B shows a leaf spring on the outer diameter side. .

FIG. 11 is a schematic diagram conceptually explaining the operation of the clutch unit according to the first embodiment and the second embodiment.

FIG. 12 is a schematic diagram conceptually explaining the operation of the clutch unit according to the first embodiment and the second embodiment.

FIG. 13 is a schematic diagram conceptually explaining the operation of the clutch unit according to the first embodiment and the second embodiment.

FIG. 14 is a vertical cross-sectional view showing a comparative example using a torsion coil spring as an elastic member.

FIG. 15 is a side view showing a torsion coil spring of a comparative example {FIG.
5 (a)}, a front view {FIG. 15 (b)}, and a front view {FIG. 15 (c), (d)} showing its action.

FIG. 16 is a perspective view showing a cage of a comparative example {FIG. 16
FIG. 17A is a perspective view seen from the arrow b direction in FIG. 16A.

FIG. 17 is a vertical sectional side view showing the overall configuration of a clutch unit according to a second embodiment.

FIG. 18 is a front view of the output shaft of the clutch unit according to the second embodiment {FIG. 18 (a)}, B of FIG. 18 (a).
It is a -B line sectional view {FIG. 18 (b)}.

FIG. 19 is a front view showing an inner ring (control member) of the clutch unit according to the second embodiment {FIG. 19 (a)}, FIG.
It is a BB line sectional view of (a) {FIG.19 (b)}, and the principal part enlarged view {FIG.19 (c)}.

20 is a front view showing the outer ring (stationary member) of the clutch unit according to the second embodiment {(FIG. 20 (a)}, and a cross-sectional view taken along line BB of FIG. 20 (a) {FIG. 13 (b). )}.

21 is a front view showing a stationary side plate of the clutch unit according to the second embodiment {FIG. 21 (a)}, and a sectional view taken along line BB of FIG. 21 (a) {FIG. 21 (b)}.

FIG. 22 is a front view {FIG. 22 (a)} showing a friction member (braking means) of the clutch unit according to the second embodiment, and a longitudinal side view {FIG. 22 (b)}.

FIG. 23 is a sectional view taken along line BB of FIG. 17, showing a first clutch portion of the clutch unit according to the second embodiment.

FIG. 24 is a sectional view taken along the line AA of FIG. 17, showing a second clutch portion of the clutch unit according to the second embodiment.

FIG. 25 is a partially enlarged front view showing the action of the second clutch portion (neutral position).

FIG. 26 is a partially enlarged front view showing the action of the second clutch portion (when unlocked).

FIG. 27 is a partially enlarged front view showing the action of the second clutch portion (during torque transmission).

FIG. 28 is a conceptual diagram showing a seat of an automobile.

FIG. 29 (a) is a conceptual diagram showing an example of the structure of the seat height adjusting device, and FIG. 29 (b) is an enlarged view of a main part thereof.

[Explanation of symbols]

1 Outer ring (input side member) 1A 1st thin member 1Aa cam surface 1Ae Fitting groove (groove part) 1B Second thin member 1Ba mating claw 2 Inner ring (output side member) 2a Circumferential surface 3 roller (engager) 4 cage 4a pocket 4b opening 5 Elastic member 5A leaf spring 5B leaf spring 5a1 engaging part 5a2 engaging part 5b1 locking part 6 Operation lever (operation member) 8 Clutch 12 Output shaft (output side member) 13 Inner ring (control member) 14 Outer ring (stationary member) 15 First clutch part 16 Second clutch part 23 Operation lever (operation member)

Claims (22)

[Claims] 1. An input side member to which a torque is input, an output side member to which a torque is output, a clutch portion provided between the input side member and the output side member, and an input side member. An elastic member that stores an elastic force by an input torque, and that returns the input side member to the neutral position by the accumulated elastic force when the input torque is released.
A clutch unit formed by a leaf spring having an end ring shape. 2. A clutch portion is interposed in a torque transmission path between an input side member and an output side member and holds an engagement element for transmitting an input torque from the input side member to the output side member and the engagement element. The clutch unit according to claim 1, further comprising: a retainer that has a pocket and that applies a restoring force to the input side member via the engaging element by the elastic force of the elastic member when the input torque is released. 3. The clutch unit according to claim 2, wherein engaging portions capable of engaging with the retainer and the stationary member are formed at both ends of the elastic member. 4. The clutch unit according to claim 3, wherein the engaging portion at one end and the engaging portion at the other end of the elastic member are provided at circumferentially opposed positions. 5. The clutch unit according to claim 3, wherein the retainer has an opening which is engageable with the engaging portion of the elastic member and whose periphery is closed. 6. The clutch unit according to claim 3, wherein stress adjusting portions are provided near both ends of the elastic member. 7. The clutch unit according to claim 1, wherein the elastic member is a stack of two or more leaf springs. 8. The clutch unit according to claim 7, wherein both ends of the leaf spring on the inner diameter side are bent at acute angles to form locking portions, and both ends of the leaf spring on the outer diameter side are locked by the locking portions. 9. The input-side member is configured by connecting a first thin-walled member having a cam surface forming a clutch portion and a second thin-walled member to which an operating member for inputting torque is attached so as not to rotate relative to each other. The clutch unit according to any one of claims 1 to 8. 10. The clutch unit according to claim 9, wherein the inner periphery of the end of the second thin member is arranged on the outer peripheral side of the end of the first thin member. 11. The clutch unit according to claim 1, wherein an axial preload is applied to the input side member. 12. An input side member for inputting torque, an output side member for outputting torque, a control member interposed in a torque transmission path between the input side member and the output side member, and rotation restrained. A stationary side member, a first clutch part provided between the input side member and the control member, a second clutch part provided between the stationary side member and the output side member, and an input to the input side member. An elastic member for accumulating the elastic force by the input torque thus generated, and returning the input side member to the neutral position by the accumulated elastic force when the input torque is released. In the configuration in which the reverse input torque from the output side member is transmitted to the output side member via the control member and is locked to the stationary side member via the second clutch portion, the elastic member is A special feature is that it is made of a ring-shaped leaf spring. Clutch unit to collect. 13. A first clutch portion is interposed in a torque transmission path between an input side member and an output side member and holds an engagement element for transmitting an input torque from the input side member to a control member and the engagement element. 13. The clutch unit according to claim 12, further comprising: a pocket that holds the input torque, and a retainer that applies a restoring force to the input side member via the engaging element by the elastic force of the elastic member when the input torque is released. 14. The clutch unit according to claim 13, wherein engaging portions capable of engaging with the retainer and the stationary member are formed at both ends of the elastic member. 15. The clutch unit according to claim 14, wherein the engaging portion at one end and the engaging portion at the other end of the elastic member are provided at circumferentially opposed positions. 16. The clutch unit according to claim 14, wherein the retainer is formed with an opening portion which is engageable with the engaging portion of the elastic member and whose periphery is closed. 17. The clutch unit according to claim 14, wherein stress adjusting portions are provided near both ends of the elastic member. 18. The clutch unit according to claim 12, wherein the elastic member is a stack of two or more leaf springs. 19. The clutch unit according to claim 18, wherein both ends of the leaf spring on the inner diameter side are bent at acute angles to form locking portions, and both ends of the leaf spring on the outer diameter side are locked by the locking portions. 20. The input-side member is configured by connecting a first thin-walled member having a cam surface forming a clutch portion and a second thin-walled member to which an operating member for inputting torque is attached so as not to rotate relative to each other. 20. The clutch unit according to claim 12. 21. The clutch unit according to claim 20, wherein the inner periphery of the end portion of the second thin member is arranged on the outer peripheral side of the end portion of the first thin member. 22. The clutch unit according to claim 12, wherein a friction body is interposed between the input side member and the control member.