JP5350048B2 - Clutch unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To sufficiently secure the effective gear length of a pinion gear arranged in a shaft part of an output shaft. <P>SOLUTION: This clutch unit is composed of a lever side clutch part on the input side for controlling the transmission or cutoff of rotational torque to the output side by lever operation, and a brake side clutch part on the output side for transmitting input torque from the lever side clutch part to the output side and cutting off inverse input torque from the output side. The brake side clutch part includes an output shaft 22 coaxially forming the pinion gear 41g in a shaft part 22c and outputting the torque from the pinion gear 41g. The pinion gear 41g is composed of a complete gear part 41g<SB>1</SB>formed on the tip side of the shaft part 22c and an incomplete gear part 41g<SB>2</SB>formed on the root side of the shaft part 22c. A shaft part root side end surface positioned between tooth parts of the incomplete gear part 41g<SB>2</SB>is constituted of an inclined face 22g<SB>2</SB>of the incomplete gear part 41g<SB>2</SB>diametrically contracting toward the tip side of the shaft part 22c and a parallel surface 22g<SB>1</SB>of the complete gear part 41g<SB>1</SB>parallel along the radial direction. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention includes a lever-side clutch portion that transmits rotational torque from the input side to the output side, a brake-side clutch portion that transmits rotational torque from the input side to the output side, and blocks reverse input torque from the output side, It is related with the clutch unit which has.

  In general, in a clutch unit using an engagement element such as a cylindrical roller or a ball, a clutch portion is disposed between an input side member and an output side member. The clutch portion is configured to control transmission / cutoff of input torque by engaging / disengaging an engagement element such as a cylindrical roller or a ball in a wedge clearance formed between the input side member and the output side member. It has become.

  The present applicant, for example, is incorporated in an automobile seat lifter that adjusts the seat seat up and down by lever operation, and transmits a rotational torque from the input side to the output side, and outputs a rotational torque from the input side. A clutch unit having a brake side clutch portion that transmits to the side and interrupts reverse input torque from the output side has been previously proposed (for example, see Patent Document 1).

  37 is a longitudinal sectional view showing the entire configuration of the conventional clutch unit disclosed in the above-mentioned Patent Document 1, FIG. 38 is a sectional view taken along the line DD in FIG. 37, and FIG. 39 is a line taken along the line EE in FIG. FIG.

  As shown in FIGS. 37 and 38, the lever-side clutch unit 111 includes a lever-side outer ring 114 as an input-side member to which torque is input by lever operation, and torque from the lever-side outer ring 114 as a brake-side clutch unit 112. And a cylindrical roller 116 as a plurality of engagement elements for controlling transmission / interruption of input torque from the lever-side outer ring 114 by engagement / disengagement between the lever-side outer ring 114 and the inner ring 115. A retainer 117 that holds each cylindrical roller 116 at a predetermined interval in the circumferential direction, a brake side outer ring 123 as a stationary side member whose rotation is restricted, and a cage 117 and a brake side outer ring 123. The elastic force is accumulated by the input torque from the lever side outer ring 114, and the cage 117 is moved by the accumulated elastic force by releasing the input torque. An inner centering spring 118 as a first elastic member to be returned to the state, provided between the lever side outer ring 114 and the brake side outer ring 123, accumulates an elastic force by an input torque from the lever side outer ring 114, and the input torque The main part is constituted by the outer centering spring 119 as a second elastic member that returns the lever-side outer ring 114 to the neutral state by the accumulated elastic force.

  In the figure, 113 is a lever side plate that is fixed to the lever side outer ring 114 by caulking and constitutes an input side member together with the lever side outer ring 114, and 131 is a washer attached to the output shaft 122 via a wave washer 130. .

  On the other hand, as shown in FIGS. 37 and 39, the brake side clutch portion 112 is a brake side outer ring 123 as a stationary side member whose rotation is restricted, and a connecting member to which torque from the lever side clutch portion 111 is input. The inner ring 115, the brake side outer ring 123 and the output shaft 122 are disposed in a wedge clearance. The engagement / disengagement between the brake side outer ring 123 and the output shaft 122 causes transmission of input torque from the inner ring 115 and output shaft 122. The main part is composed of a plurality of pairs of cylindrical rollers 127 that control the interruption of the reverse input torque.

  The bent tip of the enlarged diameter portion 115c that extends radially outward from the axial end of the inner ring 115 and functions in the axial direction functions as a cage that holds the cylindrical roller 127 at a predetermined interval in the circumferential direction. To do. In the figure, reference numerals 124 and 125 denote a cover and a brake side plate that form a stationary member together with the brake side outer ring 123. The brake side outer ring 123 and the cover 124 are integrally crimped and fixed by the brake side plate 125. Reference numeral 128 denotes a leaf spring having an N-shaped cross section, for example, disposed between each pair of cylindrical rollers 127, and 129 is a friction ring as a braking member attached to the brake side plate 125.

JP 2009-30634 A

  Incidentally, in the conventional clutch unit disclosed in Patent Document 1, the output shaft 122 has a large-diameter portion 122d that extends radially outward from the shaft portion 122c and is integrally formed at a substantially central portion in the axial direction. Yes. In addition, a pinion gear 141g for connecting to a seat lifter portion (not shown) of the automobile is coaxially formed at the tip of the shaft portion 122c (see FIGS. 40 and 41). The shaft base end surface on which the pinion gear 141g is formed is an inclined surface 122g whose cross-sectional shape along the axial direction is continuous along the radial direction, that is, an inclined surface 122g whose diameter decreases toward the tip end side of the shaft portion 122c. ing.

Pinion gear 141g provided on the output shaft 122, the inclined surface 122g from the fact that a continuous tapered as described above, a complete gear unit 141g ₁ formed on the tip side of the shaft portion 122c as shown in FIG. 42 , and a incomplete gear portion 141 g ₂ formed on a root side of the shaft portion 122c. The outer peripheral surface of the shaft portion 122c positioned between the incomplete gear portion 141g ₂ of the pinion gear 141g and the large diameter portion 122d, when mounting the brake-side side plate 125 (see FIG. 37) and a seat frame (not shown) It is the guide surface 122h.

In the conventional clutch unit, since there is an incomplete gear portion 141 g ₂ to the inclined surface 122g which is a continuous tapered as described above, becomes shorter the effective gear length G ₀ at full gear portion 141 g _1, guide The axial length I ₀ of the surface 122h is also relatively short. Thus, it is difficult to ensure the effective gear length G ₀ of the complete gear portion 141g ₁ and the axial length I ₀ of the guide surface 122h within the limited dimensions at the tip of the shaft portion 122c of the output shaft 122. That was the current situation.

  Accordingly, the present invention has been proposed in view of the above-mentioned problems, and an object of the present invention is to provide a clutch unit that can sufficiently secure the effective gear length of the pinion gear provided on the shaft portion of the output shaft. There is to do.

  The clutch unit according to the present invention is provided on the input side, and controls the transmission / cut-off of rotational torque to the output side by lever operation, and the input side torque from the lever side clutch unit provided on the output side. Is transmitted to the output side, and the brake side clutch portion for cutting off the reverse input torque from the output side is provided.

As a technical means for achieving the above-mentioned object, in the clutch unit of the present invention, the brake side clutch portion includes an output side member in which a pinion gear is coaxially formed in the shaft portion, and torque is output from the pinion gear, The pinion gear is composed of a complete gear portion formed on the distal end side of the shaft portion and an incomplete gear portion formed on the root side of the shaft portion, and is a shaft root end surface located between the teeth of the incomplete gear portion. The cross-sectional shape along the axial direction is a discontinuous shape along the radial direction, the inclined surface of the incomplete gear portion that is reduced in diameter toward the distal end side of the shaft portion, and the complete gear parallel to the radial direction The parallel surface of the part is formed by surface pressing toward the shaft base side .

In the present invention, the shaft root side end surface located between the teeth of the incomplete gear portion, discontinuous shapes sectional shape along the axial direction along the radial direction, i.e., toward the distal end side of the shaft portion condensation It is composed of the inclined surface of the incomplete gear portion that is radiated and the parallel surface of the complete gear portion that is parallel to the radial direction, and the parallel surface is formed by surface pressing toward the shaft base side. It is easy to secure the effective gear length of the portion, and the axial length of the entire clutch unit can be shortened, so that the size can be reduced.

  As for the parallel surface of the perfect gear part in this invention, it is desirable for the outline in the axial base end side surface to be formed along the shape of a tooth bottom part. This is effective in securing an effective gear length.

  Moreover, it is desirable that the parallel surfaces of the complete gear portion in the present invention are equally distributed in the circumferential direction in the same number as the tooth portions on the end surface on the shaft base side.

  Furthermore, the parallel surface of the complete gear portion in the present invention is 25 to 25 from the shaft tip end side of the incomplete gear portion overall length when only the inclined surface whose diameter is reduced toward the tip end side of the shaft portion. It is desirable that it is formed at a position of 50%. If it does in this way, it becomes easy to ensure sufficient effective gear length of a complete gear part.

  The lever side clutch portion in this clutch unit includes an input side member to which torque is input by lever operation, a connecting member that transmits torque from the input side member to the brake side clutch portion, and between the input side member and the connecting member. A plurality of engagement elements that control transmission / cutoff of input torque from the input side member by engagement / disengagement, a cage that holds the engagement elements at predetermined intervals in the circumferential direction, and a stationary side member that is restricted in rotation And an elastic force that is provided between the cage and the stationary member, accumulates an elastic force with an input torque from the input side member, and releases the input torque to return the cage to a neutral state with the accumulated elastic force. One elastic member, provided between the input side member and the stationary side member, accumulates the elastic force with the input torque from the input side member, and releases the input torque to cause the input side member to move with the accumulated elastic force. Neutral state Structure and a second elastic member for restoring are possible. In addition, it is desirable that the engaging member of the lever side clutch portion is a cylindrical roller.

  The brake side clutch portion in the clutch unit includes a connecting member to which torque from the lever side clutch portion is input, an output side member to which torque is output, a stationary side member in which rotation is constrained, and a stationary side member thereof. Plural pairs of engagement elements disposed in the wedge clearance between the output side members and controlling transmission of input torque from the connecting member and blocking of reverse input torque from the output side member by engagement / disengagement between the two members A configuration with The engaging member of the brake side clutch is preferably a cylindrical roller.

  The clutch unit according to the present invention is suitable for automobile use by incorporating the lever side clutch part and the brake side clutch part into the automobile seat lifter part. In this case, the input side member is coupled to the operation lever, and the output side member is connected to the link mechanism of the automobile seat lifter unit.

According to the present invention, the brake side clutch portion includes an output side member in which a pinion gear is coaxially formed on the shaft portion and torque is output from the pinion gear, and the pinion gear is a complete gear formed on the tip side of the shaft portion. And an incomplete gear portion formed on the base side of the shaft portion, and the shaft base end side end surface located between the tooth portions of the incomplete gear portion has a cross-sectional shape along the axial direction along the radial direction. Consists of a discontinuous shape, that is , an inclined surface of an incomplete gear portion that decreases in diameter toward the distal end side of the shaft portion, and a parallel surface of a complete gear portion that is parallel to the radial direction, and the parallel surface is an axis. By forming the surface by pressing the base, it is easy to secure the effective gear length of the complete gear part, and the axial length of the entire clutch unit can be shortened, resulting in a compact design. I can plan.

It is a longitudinal section showing the whole clutch unit composition in an embodiment of the present invention. It is a right view of FIG. It is a left view of FIG. It is sectional drawing which follows the AA line of FIG. It is sectional drawing which follows the BB line of FIG. (A) is sectional drawing which shows a lever side side board, (b) is a left view of (a). (A) is sectional drawing which shows an example of a lever side outer ring | wheel, (b) is a left view of (a), (c) is a right view of (a). (A) is a perspective view which shows an example of a lever side outer ring | wheel, (b) is a partial expansion perspective view which shows the nail | claw part of (a). (A) is a perspective view which shows the other example of a lever side outer ring | wheel, (b) is the elements on larger scale which show the nail | claw part of (a). (A) is a partial expansion perspective view which shows the modification of the nail | claw part of a lever side outer ring | wheel, (b) is the partial expansion perspective view which shows the other modification of the claw part of a lever side outer ring | wheel. (A) is a partial expansion perspective view which shows the state which attached the attachment to the nail | claw part of the lever side outer ring | wheel, (b) is a bottom view of (a). (A) is a partial expansion perspective view which shows the state which attached the other attachment to the nail | claw part of the lever side outer ring | wheel, (b) is a bottom view of (a). (A) is sectional drawing which shows an inner ring | wheel, (b) is a left view of (a). It is a perspective view which shows a holder | retainer. (A) is sectional drawing which shows a holder | retainer, (b) is a left view of (a), (c) is sectional drawing of (a). (A) is a front view which shows an inner side centering spring, (b) is a right view of (a). (A) is a side view showing an outer centering spring, (b) is a partially enlarged bottom view of (a). (A) is the perspective view which looked at the output shaft from one side, (b) is the perspective view which looked at the output shaft from the other side. (A) is sectional drawing which shows an output shaft, (b) is a left view of (a), (c) is a right view of (a). (A) and (b) are the principal part expanded sectional views of Fig.19 (a). It is an expansion perspective view which shows the leaf | plate spring of FIG. (A) and (b) are expansion perspective views which show two examples of a deformation | transformation of a leaf | plate spring. (A) is sectional drawing which shows a brake side outer ring | wheel, (b) is a left view of (a). (A) is sectional drawing which shows a cover, (b) is a left view of (a). (A) is sectional drawing which shows a brake side side board, (b) is a right view of (a). (A) is a front view showing a friction ring, (b) is a left side view of (a), and (c) is a right side view of (a). It is a principal part expanded sectional view which shows the leaf | plate spring and cylindrical roller of FIG. (A) is a perspective view which shows the state before attaching a brake side outer ring | wheel to a brake side side plate, (b) is a perspective view which shows the state after attaching a brake side outer ring | wheel to a brake side side plate. It is a perspective view which shows the state which assembled | attached the brake side outer ring | wheel and the cover to the brake side side plate. It is a perspective view which shows the state which integrated the brake side side board, the brake side outer ring | wheel, and the cover by crimping. (A) is a principal part expanded sectional view which shows an example of an inner ring | wheel and a cover, (b) is a principal part expanded sectional view which shows the other example of an inner ring | wheel and a cover. It is a principal part expanded sectional view which shows the state which interposed the sealing member between the inner ring | wheel and the cover. It is sectional drawing which follows the CC line of FIG. (A) is a perspective view showing a state before the cage is assembled to the brake side plate, the brake side outer ring, the cover and the inner centering spring, and (b) is the brake side plate, the brake side outer ring, the cover and the inner centering spring. It is a perspective view which shows the state after attaching a holder | retainer with respect to it. It is a conceptual diagram which shows the seat seat of a motor vehicle. (A) is a conceptual diagram which shows one structural example of a sheet lifter part, (b) is the principal part enlarged view. It is a longitudinal cross-sectional view which shows the whole structure of the conventional clutch unit. FIG. 38 is a transverse sectional view taken along the line DD of FIG. 37. It is a cross-sectional view which follows the EE line | wire of FIG. It is a perspective view which shows the output shaft of FIG. It is a longitudinal cross-sectional view which shows the output shaft of FIG. It is a principal part expanded sectional view of FIG.

  1 is a longitudinal sectional view showing an overall configuration of a clutch unit X according to an embodiment of the present invention, FIG. 2 is a right side view of the clutch unit X shown in FIG. 1, and FIG. 3 is a left side view of the clutch unit X shown in FIG. 4 is a cross-sectional view taken along line AA in FIG. 1, and FIG. 5 is a cross-sectional view taken along line BB in FIG. 6 to 26 are diagrams showing main components of the clutch unit X. FIG. 27 to 34 are views showing an assembled state of main components of the clutch unit X. FIG.

  The clutch unit X is incorporated in an automobile seat lifter (see FIGS. 35 and 36A and 36B) that adjusts the height of the seat by lever operation, for example. As shown in FIGS. 1 to 5, the clutch unit X is formed by unitizing a lever side clutch portion 11 provided on the input side and a brake side clutch portion 12 having a reverse input cutoff function provided on the output side. It has a configuration.

  As shown in FIGS. 1, 2 and 4, the lever side clutch portion 11 includes, for example, a lever side plate 13 and a lever side outer ring 14 as input side members to which an operation lever (not shown) is connected, and the lever. A wedge clearance 20 formed between an inner ring 15 as a connecting member that transmits torque from the side outer ring 14 to the brake-side clutch portion 12, and an outer peripheral surface 15 a of the inner ring 15 and an inner peripheral surface 14 a of the lever-side outer ring 14. For example, a plurality of cylindrical rollers 16 as engagement elements disposed on the holder, a retainer 17 that retains the cylindrical rollers 16 at equal intervals in the circumferential direction, and a first elasticity for returning the retainer 17 to a neutral state It has an inner centering spring 18 that is a member and an outer centering spring 19 that is a second elastic member for returning the lever-side outer ring 14 to a neutral state. A washer 31 is press-fitted into the end of the output shaft 22 described later via a wave washer 30 to prevent the component parts from coming off (see FIG. 1).

  The brake-side clutch portion 12 having a reverse input blocking function, which is called a lock type, has an inner ring as a connecting member to which torque from the lever-side clutch portion 11 is input as shown in FIGS. 15, an output shaft 22 as an output side member, a brake side outer ring 23, a cover 24 and a brake side plate 25 as stationary side members whose rotation is restricted, and a wedge clearance between the brake side outer ring 23 and the output shaft 22. Cylindrical rollers 27 as a plurality of pairs of engagement elements, which are arranged at 26 and control transmission of input torque from the inner ring 15 and interruption of reverse input torque from the output shaft 22 by engagement / disengagement between both members, The main part is composed of, for example, a leaf spring 28 having an N-shaped cross section as an elastic member that is inserted between each pair of cylindrical rollers 27 and biases a separation force between the cylindrical rollers 27. The output shaft 22 is provided with a protrusion 22f, and a hole 15d into which the protrusion 22f is inserted with a clearance is provided in the inner ring 15 (see FIG. 1).

  Next, main components of the lever side clutch part 11 and the brake side clutch part 12 in the clutch unit X will be described in detail.

  FIGS. 6A and 6B show the lever side plate 13 of the lever side clutch portion 11. The lever side plate 13 has a hole 13a through which the output shaft 22 and the inner ring 15 are inserted at a central portion thereof, and a plurality of (for example, five) claw portions 13b project from the outer peripheral edge. These claw portions 13b are bent in the axial direction to have a bifurcated tip, and are inserted into a notch recess 14e (see FIG. 7C) of the lever side outer ring 14 to be described later. By expanding outward, the lever side plate 13 is fixed by crimping to the lever side outer ring 14. In addition, the code | symbol 13c in a figure is the several (for example, four) hole for attaching the operation lever (not shown) for operating the height adjustment of a seat to the lever side side board 13. FIG.

  FIGS. 7A to 7C show the lever-side outer ring 14. The lever-side outer ring 14 is formed by pressing a single plate-shaped material into a cup shape, and a hole 14b through which the output shaft 22 and the inner ring 15 are inserted is formed in the center part 14c. A plurality of cam surfaces 14a are formed at equal intervals in the circumferential direction on the inner periphery of the cylindrical portion 14d extending in the axial direction (see FIG. 4).

  A plurality of (for example, three) claw portions 14f and 14g project from the outer peripheral edge portion of the lever-side outer ring 14 and are bent in the axial direction. Among these claw portions 14f and 14g, one claw portion 14f is inserted and disposed between two locking portions 19a (see FIG. 17A) of an outer centering spring 19 to be described later, and the remaining two claw portions 14f and 14g are locked. The claw portion 14g slides on the end surface of the brake-side outer ring 23 by the rotation of the lever-side outer ring 14 in contact with an end surface 23d (see FIGS. 23A and 23B) of a brake-side outer ring 23, which will be described later. It moves between a pair of locking portions 24e and 24f (see FIG. 24 (b)) as rotation stoppers provided on the outer periphery of the cover 24, and contacts each of the locking portions 24e and 24f at the moving end in the rotation direction. By making the contact possible, the operation angle of the operation lever is regulated.

  Here, depending on the specification of the automobile on which the clutch unit X is mounted, the rotation angle of the lever-side outer ring 14 by lever operation may be different between the clockwise direction and the counterclockwise direction. In order to comply with this specification, means for changing the rotation angle of the lever-side outer ring 14 between the clockwise direction and the counterclockwise direction is provided in the claw portion 14 g of the lever-side outer ring 14. As a result, when the lever-side outer ring 14 is rotated by lever operation, it is possible to quickly and easily cope with specifications that require different rotation angles of the lever-side outer ring 14 in the clockwise direction and the counterclockwise direction.

When the same is the rotation angle of the lever side outer ring 14 as in the conventional and clockwise T ₁ counterclockwise direction T _2, FIG. 8 (b) and the lever-side as shown by a broken line shown in FIG. 9 (b) shape and clockwise T ₁ and counterclockwise T ₂ the claw portions 14g of the outer ring 14 to the central axis L may be the same symmetrical shape. In contrast, in this embodiment, and FIG. 8 (a) (b) and FIG. 9 (a) counterclockwise _{T 2} the rotational angle and clockwise _{T 1} of the lever-side outer race 14 as shown in (b) corresponds to a case made different, the shape and clockwise T ₁ and counterclockwise T ₂ are different asymmetrical claws 14g of the lever-side outer race 14 with respect to the central axis L.

For example, the rotation angle of the lever side outer ring 14, in case of decreasing the rotation angle of the clockwise direction T ₁ than the rotation angle of the counterclockwise direction T ₂ are, the lever-side outer ring as shown in FIG. 8 (a) (b) providing the protrusion 14g ₁ clockwise ends of the claw portions 14g of 14. In other words, to increase the clockwise side width _{W 1} than the counterclockwise direction width _{W 2} relative to the center axis L of the claw portion 14 g _{(W 1> W} 2). Conversely, if smaller than the rotation angle of the counterclockwise direction T ₂ the rotation angle of the clockwise direction T ₁ is counterclockwise claws 14g of the lever-side outer race 14 as shown in FIG. 9 (a) (b) providing the convex portions 14 g ₂ in the direction end portion. That is, the counterclockwise direction width _{W 3} larger than the clockwise side width dimension _{W 4} with respect to the central axis L of the claw portion _{14g (W 3> W 4)} .

Note that the convex portions 14g ₁ and 14g ₂ are provided at portions that abut against locking portions 24e and 24f (see FIG. 24B) provided as rotation stoppers on the outer periphery of the cover 24, that is, at the tip portion of the claw portion 14g. What is necessary is just to form. Accordingly, the convex shape of the claw portion 14g is not limited to the illustrated shape, and for example, the width dimension increases toward the tip portion of the claw portion 14g as shown in FIGS. 10 (a) and 10 (b). The convex portions 14g ₁ ′ and 14g ₂ ′ having a tapered shape may be used. Although not shown, by providing a recess in a clockwise direction end portion or the counterclockwise direction end portion of the claw portion 14g, the clockwise T ₁ the claw portion 14g to the central axis L and counterclockwise T ₂ in An asymmetric shape having a different shape can also be used.

In the above has been described as being formed integrally with the projecting portion _14g 1, 14g ₂ on the claw portion 14g, but it is also possible to form the convex portions _14g 1, 14g ₂ in the claw portion 14g and separate. That is, the attachment 14h to the claw portions 14g of the lever-side outer race 14 and the clockwise direction T ₁ with respect to the central axis L and counterclockwise T ₂ and in different shapes asymmetrical shapes, also mounting the 14i to claw portion 14g Is possible.

For example, as shown in FIGS. 11 (a) and 11 (b), an attachment 14h having a U-shaped cross section is fitted into the counterclockwise end of the claw 14g by pressure bonding or adhesion. In the illustrated that although the case of smaller than the rotation angle of the counterclockwise direction T ₂ the rotation angle of the clockwise direction T _1, the rotation angle of the clockwise direction T ₁ from the rotational angle of the counterclockwise direction T ₂ In order to reduce the size, an attachment 14h having a U-shaped cross section may be fitted to the clockwise end of the claw portion 14g.

Also, as shown in FIGS. 12 (a) and 12 (b), an attachment 14i fitted so as to hold the claw portion 14g at both ends of the claw portion 14g in the clockwise direction and the counterclockwise direction is used. Is also possible. The attachment 14i includes a fitted portion 14i ₁ to the distal end portion of the counter-clockwise end of the claw portion 14 g, consist fitted portion 14i ₂ Metropolitan the intermediate portion of the clockwise end of the claw portion 14 g, The claw portion 14g has a shape in which a distal end portion at a clockwise end portion is opened. In this case as well, in the figure, the case where the rotation angle in the counterclockwise direction T ₂ is made smaller than the rotation angle in the clockwise direction T ₁ is illustrated, but the rotation angle in the clockwise direction T ₁ is set to the counterclockwise direction T _2. When the rotation angle is smaller than the rotation angle, a portion fitted to the tip portion of the claw portion 14g in the clockwise end portion and a portion fitted to the intermediate portion of the claw portion 14g in the counterclockwise end portion are used. Therefore, an attachment (not shown) having a shape in which the tip portion of the counterclockwise end of the claw portion 14g is opened may be used.

  On the outer periphery of the lever-side outer ring 14, a plurality of (five in the figure) notch recesses 14e into which the claw portions 13b of the lever-side side plate 13 (see FIGS. 6A and 6B) are inserted are formed. The lever side plate 13 and the lever side outer ring 14 are connected by crimping the claw portion 13b of the lever side plate 13 inserted into the notch recess 14e. The lever side outer ring 14 and the lever side plate 13 fixed by crimping to the lever side outer ring 14 constitute an input side member of the lever side clutch portion 11.

  FIGS. 13A and 13B show the inner ring 15. The inner ring 15 includes an outer peripheral surface 15a that forms a wedge clearance 20 (see FIG. 4) between the outer diameter of the cylindrical portion 15b through which the output shaft 22 is inserted and the cam surface 14a of the lever-side outer ring 14. . Further, an enlarged diameter portion 15c that extends radially outward from the end portion of the cylindrical portion 15b and is bent in the axial direction is integrally formed, and the brake side clutch portion 12 is formed at the bent distal end portion of the enlarged diameter portion 15c. In order to function as a cage, pockets 15e for accommodating the cylindrical rollers 27 and the leaf springs 28 are formed at equal intervals in the circumferential direction. Further, the bent portion 15f of the enlarged diameter portion 15c is provided with a relief 15g for preventing interference with a bent portion 24g of the cover 24 of the brake side clutch portion 12 described later (see FIG. 31A). The relief 15g is a tapered flat surface formed by pressing the bent portion 15f. In addition, the code | symbol 15d in a figure is a hole into which the protrusion 22f (refer FIG. 1) of the output shaft 22 is inserted with a clearance.

  14 and 15A to 15C show a resin-made cage 17. The cage 17 is a cylindrical member in which a plurality of pockets 17a for accommodating the cylindrical rollers 16 are formed at equal intervals in the circumferential direction. Two notch recesses 17b are formed at one end of the retainer 17, and the locking part 18a of the inner centering spring 18 is locked to two adjacent end surfaces 17c of each notch recess 17b. [See FIG. 15 (b)].

  FIGS. 16A and 16B show the inner centering spring 18. The inner centering spring 18 is formed of a C-shaped spring member having a circular cross section having a pair of engaging portions 18a bent radially inward, and is located on the inner diameter side of the outer centering spring 19 (see FIG. 33). The inner centering spring 18 is disposed between the cage 17 and a cover 24 which is a stationary side member of the brake side clutch portion 12, and both locking portions 18 a have two end faces 17 c of the cage 17 (see FIGS. 14 and 14). 15 (b)] and the claw portion 24b provided on the cover 24 (see FIGS. 24 (a) and (b)) (see FIGS. 34 (a) and (b)). .

  In the inner centering spring 18, when the input torque from the lever side outer ring 14 is applied, one locking portion 18 a is on one end surface 17 c of the cage 17, and the other locking portion 18 a is on the claw portion 24 b of the cover 24. As the lever-side outer ring 14 rotates, the inner centering spring 18 is pushed and expanded to accumulate elastic force. When the input torque from the lever-side outer ring 14 is released, the elastic restoring force causes the cage 17 to move. Is returned to the neutral state.

  17A and 17B show the outer centering spring 19. The outer centering spring 19 is a strip-shaped spring member having a C-shape and having a pair of locking portions 19a whose both ends are bent radially outward, and is located on the outer diameter side of the inner centering spring 18 ( (See FIG. 33). The outer centering spring 19 is disposed between the lever-side outer ring 14 of the lever-side clutch portion 11 and the cover 24 of the brake-side clutch portion 12, and both locking portions 19 a are claw portions 14 f provided on the lever-side outer ring 14. Locked to [see FIGS. 7 (a) to 7 (c)] and locked to a claw portion 24d (see FIGS. 24 (a) and (b)) provided on the cover 24 [FIG. 34 (a)]. (See (b)). The locking portion 19a is arranged with a circumferential phase (180 °) shifted from the locking portion 18a of the inner centering spring 18 (see FIG. 33).

  In the outer centering spring 19, when the lever side outer plate 14 is rotated by the lever operation by the lever operation and the lever side outer ring 14 rotates, one locking portion 19 a is engaged with the claw portion 14 f of the lever side outer ring 14 and the other engagement. Since the stop portions 19a are respectively engaged with the claw portions 24d of the cover 24, the outer centering spring 19 is pushed and expanded with the rotation of the lever side outer ring 14, and the elastic force is accumulated, and the input torque from the lever side outer ring 14 is increased. When opened, the lever-side outer ring 14 is returned to the neutral state by the elastic restoring force.

  FIGS. 18A and 18B and FIGS. 19A to 19C show the output shaft 22. The output shaft 22 has a large-diameter portion 22d that extends radially outward from the shaft portion 22c and is integrally formed at a substantially central portion in the axial direction. A pinion gear 41g for connecting to the seat lifter portion 41 is coaxially formed at the tip of the shaft portion 22c.

  A plurality of (for example, six) flat cam surfaces 22a are formed on the outer peripheral surface of the large-diameter portion 22d at equal intervals in the circumferential direction, and a wedge clearance 26 provided between the inner peripheral surface 23b of the brake-side outer ring 23 and the like. Two cylindrical rollers 27 and a leaf spring 28 are arranged on each (see FIG. 5). An annular recess 22b in which the friction ring 29 is accommodated is formed on one end face of the large diameter portion 22d. Reference numeral 22f in the figure is a protrusion formed on the other end face of the large-diameter portion 22d, and is inserted into the hole 15d of the inner ring 15 with a clearance (see FIGS. 1 and 13A and 13B).

Pinion gear 41g provided at the distal end of the shaft portion 22c of the output shaft 22, a complete gear unit 41g ₁ formed on the tip side of the shaft portion 22c, as shown in FIG. 19 (a), the base side of the shaft portion 22c The shaft base side end face that is formed between the formed incomplete gear portion 41g ₂ and is located between the tooth portions of the incomplete gear portion 41g ₂ has a shape in which the cross-sectional shape along the axial direction is discontinuous along the radial direction, in other words, the inclined surface 22 g ₂ of the incomplete gear portion 41 g ₂ whose diameter decreases toward the distal end side of the shaft portion 22c, is constituted by a parallel surface 22 g ₁ of the parallel full gear portion 41 g ₁ along the radial direction .

In the conventional clutch unit, as shown by the broken line in FIG. 20 (a), the shaft base end side end surface on which the pinion gear is formed has a shape in which the cross-sectional shape along the axial direction is continuous along the radial direction, that is, the shaft It was made into the inclined surface which diameter-reduces toward the front end side of a part. On the other hand, in this embodiment, the inclined surface 22g ₂ (solid line in the drawing) obtained by shifting the conventional inclined surface (broken line in the drawing) to the tip end side (left direction in the drawing) and the discontinuous parallel surface 22g ₁ Is forming. The parallel surfaces 22 g ₁ is formed by pressing a surface inclined plane (broken line in the figure below) the root side of the shaft section (rightward direction) in the conventional excess thickness incomplete gear portion 41g generated by the surface pressing inclined surfaces 22 g ₂ shifted to the front end side of the shaft portion is formed by moving the ₂ side.

Thus, complete gear portion 41 g ₁ of the effective gear length G, that is, longer than the axial length of the parallel surfaces 22 g ₁ to gear tip surface is conventional, the effective gear full gear portion 41 g ₁ length It becomes easy to secure G. In this way, the complete gear portion 41g with ₁ to ensure the effective gear length G becomes easy, compact can be achieved to be able to shorten the axial length of the entire clutch unit.

The outer peripheral surface of the shaft portion 22c located between the incomplete gear portion 41g ₂ and the large diameter portion 22d of the pinion gear 41g, when mounting the brake-side side plate 25 (see FIG. 1) and a seat frame (not shown) The guide surface 22h. Here, the inclined surfaces 22 g ₂ of the incomplete gear portion 41 g _2, since being formed by shifting the conventional inclined surface shown by a broken line shown in FIG. 20 (a) of the shaft portion to the distal end side, the guide of the above The axial length I of the surface 22h is also longer than in the conventional case, and it is easy to secure the axial length I of the guide surface 22h.

The complete gear portion 41g parallel surfaces 22 g _{1 1,} the contour of the axial portion root side end surface is formed along the shape of the tooth bottom. This is effective in securing the effective gear length G. Further, complete gear portion 41g parallel surfaces 22 g ₁ of ₁ is equally spaced circumferentially the same number and the tooth portion to the shaft proximal end face. Furthermore, parallel surfaces 22 g ₁ complete gear portion 41 g ₁ is 20 when the shaft portion base end face inclined surface whose diameter decreases toward the distal end side of the shaft portion 22c only as indicated by the dotted line in (b) The incomplete gear portion full length J is formed at a position of 25 to 50% from the shaft tip end side (a separation distance K from the shaft tip end side). This makes it easy to sufficiently ensure complete gear unit effective gear length G of 41 g _1. Incidentally, when less than 25% of the incomplete gear portion total length J, it is difficult to secure the effective gear length G of the complete gear portion 41 g _1, if greater than 50%, parallel surfaces 22 g ₁ is a broken line in FIG. from being formed by the flattened portion, the more the amount of the excess thickness caused by the surface pressing is moved to an incomplete gear portion 41 g ₂ side, there is a risk that protrudes on the outer diameter side of the pinion gear 41 g, brake-side It becomes difficult to assemble the side plate 25.

  FIG. 21 shows a leaf spring 28 having an N-shaped cross section that is inserted between two cylindrical rollers 27 of the brake side clutch portion 12. When a large load or a shocking load is input to the brake side clutch portion 12 during the operation of the brake side clutch portion 12, the cylindrical roller 27 starts from a wedge clearance 26 formed between the brake side outer ring 23 and the output shaft 22. There may be a popping phenomenon in which the popping out suddenly occurs. When this popping phenomenon occurs, there is a possibility that the leaf spring 28 pressed against the cylindrical roller 27 suddenly jumping out from the wedge clearance 26 may be suddenly contracted and fall between the cylindrical rollers 27. 28 is provided with a fall prevention means.

  As an example of the fall prevention means, the leaf spring 28 has a bent portion 28a in which both end portions are bent outward. As shown in FIG. 27, even if a large load or a shocking load is input to the brake side clutch portion 12 due to the provision of the bent portions 28a at both ends of the leaf spring 28, a popping phenomenon occurs. Further, since the bent portion 28a of the leaf spring 28 interferes with the cylindrical roller 27, the brake side outer ring 23, and the output shaft 22, the leaf spring 28 becomes difficult to fall, and the reliability at the time of operation of the brake side clutch portion 12 is improved. To do.

  Here, when the radius of the cylindrical roller 27 is r, the protruding length t of the bent portion 28a of the leaf spring 28 is larger than 0.1r and smaller than 0.5r (0.1r < t <0.5r) is preferred. By satisfying this range, the contact portion (engagement portion) between the cylindrical roller 27, the brake-side outer ring 23, and the output shaft 22 is secured while ensuring a sufficient protruding length for preventing the bent portion 28a from falling. On the other hand, the bent portion 28a does not interfere. If the protruding length t is 0.1r or less (t ≦ 0.1r), it is difficult to secure a sufficient protruding length to prevent the bent portion 28a from falling, and the protruding length If the length t is 0.5r or more (t ≧ 0.5r), the bent portion 28a may interfere with the contact portion between the cylindrical roller 27, the brake side outer ring 23, and the output shaft 22.

  In the above-described case, the bent portions 28a provided at both ends of the leaf spring 28 are used as the fall prevention means. However, as another fall prevention means, as shown in FIGS. 22 (a) and 22 (b), the cylindrical roller of the leaf spring 28 is used. You may make it form groove-shaped recessed part 28b, 28c along an axial direction in the contact part. The recess 28b shown in FIG. 22A has an R shape, and the recess 28c shown in FIG. 22B has a V shape. By forming the recesses 28b and 28c in the leaf spring 28 in this manner, even if a large load or an impact load is input to the brake side clutch portion 12 and a popping phenomenon occurs, the recesses 28b and 28c of the leaf spring 28 are generated. Since the cylindrical roller 27 is fitted into the plate spring 28, it is difficult for the leaf spring 28 to fall down, and the reliability when the brake side clutch portion 12 is operated is improved.

  Here, when the concave portion 28b of the leaf spring 28 has an R shape, the radius of curvature R is larger than 1.1r and smaller than 1.5r when the radius of the cylindrical roller 27 is r (1). .1r <R <1.5r) is preferred. By satisfying this range, the cylindrical roller 27 can be surely fitted in the recess 28b, and the leaf spring 28 can be prevented from falling over. When the radius of curvature R of the recess 28b is 1.1r or less (R ≦ 1.1r) or 1.5r or more (R ≧ 1.5r), the cylindrical roller 27 can be surely fitted into the recess 28b. It becomes difficult and the leaf spring 28 is likely to fall down.

  FIGS. 23A, 23B and 24A, 24B show the brake side outer ring 23 and its cover 24. FIG. FIGS. 25A and 25B show the brake side plate 25. The brake side outer ring 23 and the cover 24 are caulked and fixed integrally by the brake side plate 25. As shown in FIGS. 24 (a) and 24 (b), the cover 24 has a curved portion 24g extending outward in the radial direction in a state where the cover 24 is in contact with the enlarged diameter portion 15c of the inner ring 15 described above (FIGS. 1 and 31). (See (a)). In the figure, reference numeral 25b denotes a hole through which the output shaft 22 is inserted, and reference numeral 25c denotes a hole into which a projection 29a of a friction ring 29 described later is fitted.

  Here, the brake-side outer ring 23 is formed by forming the inner peripheral surface 23b and the outer peripheral surface 23c by simultaneous punching of a plate-like material and cutting the inner peripheral surface 23b formed by the simultaneous punching. For example, fine blanking (FB) processing is preferable as the simultaneous punching processing of the plate-like material for forming the inner peripheral surface 23b and the outer peripheral surface 23c. This fine blanking process is a hydraulic control device that can independently adjust the plate pressing pressure that fixes the plate material with V-shaped projections and the reverse pressure facing the shear pressure in order to generate hydrostatic pressure in addition to shear pressure And press working with a function of generating a processing speed of about 5 to 35 mm per second, high rigidity and accuracy.

  By using such fine blanking, the inner peripheral surface 23b and the outer peripheral surface 23c of the brake side outer ring 23 are formed by simultaneous punching, so that the inner peripheral surface 23b and the outer peripheral surface 23c of the brake side outer ring 23 are concentric. Since the degree depends only on the precision of the mold, it is easy to ensure the precision. The concentricity of the inner peripheral surface 23b and the outer peripheral surface 23c formed by simultaneous punching is set to φ0.05 or less. Thereby, the dimensional accuracy of the brake side outer ring 23 can be improved. When the concentricity is larger than φ0.05, it is difficult to improve the dimensional accuracy of the brake side outer ring 23.

Further, since the shearing surface length of the punched surface on the inner peripheral surface 23b and the outer peripheral surface 23c of the brake side outer ring 23 can be secured up to about the plate thickness, as shown in an enlarged manner in FIG. Since the shear surface length N of the outer peripheral surface 23c can be secured up to 80% or more of the plate thickness, the chuck accuracy at the time of cutting can be improved, and the machining allowance at the time of cutting can be reduced. If the shear surface length N of the outer peripheral surface 23c is smaller than 80%, it is difficult to ensure the chuck accuracy during cutting, and the machining allowance during cutting must be increased. The outer peripheral surface 23c showing an enlarged in FIG. 23 (b), consists of a shear surface 23c ₁ and fracture surface 23c _2.

  Further, by cutting the inner peripheral surface 23b formed by the simultaneous punching process, the inner peripheral surface 23b of the brake-side outer ring 23 can be prevented from being tapered with respect to the shaft core, and the degree of cylindricity can be reduced. Improvement can be achieved and a contact area with the cylindrical roller 27 can be secured, so that a reduction in brake force at the brake side clutch portion 12 is suppressed, and the meshing surface pressure of the cylindrical roller 27 between the brake side outer ring 23 and the output shaft 22 is also reduced. Since the releasing force of the cylindrical roller 27 can be reduced and the lever-side clutch portion 11 is operated, an abnormal noise is generated when the cylindrical roller 27 is released between the brake-side outer ring 23 and the output shaft 22. There is nothing.

  Further, even if a scratch in the punching direction due to a minute punching residue adhered to the press working tool occurs on the inner peripheral surface 23b of the brake side outer ring 23, the scratch can be removed by cutting, Deterioration of the circumferential surface roughness of the inner peripheral surface 23b of the brake side outer ring 23 can be prevented. In the brake side outer ring 23, the circumferential surface roughness of the inner peripheral surface is set to a range of Ra 0.05 to 0.3. As a result, it is possible to prevent a decrease in the braking force at the brake side clutch portion 12 and a slight vibration generated when the lever is operated at the lever side clutch portion 11. If the surface roughness is less than Ra0.05, the oil film on the inner peripheral surface 23b with which the cylindrical rollers 27 are in contact may be difficult to break, and the brake side clutch portion 12 may be easily slipped. If it is greater than 3, it will be difficult to prevent the brake force at the brake side clutch portion 12 from decreasing and the slight vibrations that occur when the lever side clutch portion 11 is operated.

  Further, since the radial burrs generated by the end face polishing after punching can be removed from the punched side end surface of the brake side outer ring 23 by cutting, the inner side of the brake side outer ring 23 is assembled when the brake side clutch portion 12 is assembled. When the cylindrical roller 27 is inserted and arranged on the peripheral surface 23b, it is not necessary to make a front / back discrimination for the end face of the brake-side outer ring 23, and no dedicated equipment for the front / back discrimination is required, thereby reducing the cost. Further, if the chamfer 23e is provided at the inner peripheral surface edge portion of the brake side outer ring 23, it is easy to insert the cylindrical roller 27 into the inner peripheral surface 23b of the brake side outer ring 23 when the brake side clutch portion 12 is assembled. Thus, workability can be improved. Furthermore, the improvement in dimensional accuracy eliminates the need for selective fitting to change the roller diameter of the cylindrical roller 27 in accordance with the inner diameter of the brake-side outer ring 23, thereby improving the assembly workability of the brake-side clutch portion 12 and reducing the cost. .

  The brake side outer ring 23 is burnished on an inner peripheral surface 23b formed by cutting. This burnishing process makes it easy to improve the dimensional accuracy of the inner diameter of the brake side outer ring 23. The aforementioned burnishing process generally means a process for improving surface accuracy by crushing and plastically deforming a metal surface layer by using a roller or a ball.

  A plurality (three) of cutout recesses 23a are formed on the outer periphery of the brake side outer ring 23, and a plurality (three) of cutout recesses 24a are also formed on the outer periphery of the cover 24 so as to correspond to the cutout recesses 23a. Is formed. 28A and 28B, the claw portion 25a of the brake side plate 25 is inserted into the notch recess 23a of the brake side outer ring 23, and the notch recess 24a of the cover 24 is inserted into the notch recess 24a of the cover 24 as shown in FIG. The claw portion 25a of the brake side plate 25 is inserted.

The brake-side outer ring 23 and the cover 24 are connected and integrated together with the brake-side side plate 25 by crimping the claw portions 25a of the brake-side side plate 25 inserted into the notches 23a and 24a. Crimp claw portion 25a of the brake-side side plate 25, by utilizing crimping jig (not shown), it is carried out by expanding the bifurcated distal end portion 25a ₁ of the claw portion 25a to the outside (See FIG. 30).

  The cover 24 integrated with the brake-side side plate 25 together with the brake-side outer ring 23 is in contact with the diameter-enlarged portion 15 c of the inner ring 15 via a seal member 32 described later. Therefore, as shown in FIG. 31 (a), the bent portion 15f of the enlarged diameter portion 15c of the inner ring 15 is provided with a relief 15g having a tapered flat surface (for example, an angle with respect to the axial direction of 30 °) by surface pressing. Thus, interference with the bent portion 24g of the cover 24 of the brake side clutch portion 12 is prevented. By avoiding interference between the bent portion 15f of the enlarged diameter portion 15c of the inner ring 15 and the bent portion 24g of the cover 24, when the lever side clutch portion 11 is rotated by the lever operation, the torque due to the lever operation increases. Therefore, the feeling of lever operation can be improved.

  In this case, the bent portion 24g of the cover 24 does not need to have a large diameter in order to avoid interference between the bent portion 24g of the cover 24 and the bent portion 15f of the enlarged diameter portion 15c of the inner ring 15. It does not interfere with the outer centering spring 19 arranged on the outer periphery of the 24 bent portions 24g (see FIG. 33). Since there is no possibility that the outer centering spring 19 comes into contact with the claw portion 25a of the brake side plate 25 positioned on the outer periphery thereof, it is not necessary to increase the outer diameters of the brake side plate 25 and the brake side outer ring 23. The whole unit can be easily downsized.

  In this case, in order to avoid interference between the bent portion 24g of the cover 24 and the bent portion 15f of the enlarged diameter portion 15c of the inner ring 15, a relief 15g is provided in the bent portion 15f of the enlarged diameter portion 15c of the inner ring 15. However, a relief 24h may be provided in the bent portion 24g of the cover 24 as shown in FIG. The relief 24h in this case is also a tapered flat surface (for example, an angle with respect to the axial direction is 45 °) formed by pressing the curved portion 24g.

  Thus, by providing the relief 24 h in the bent portion 24 g of the cover 24, interference with the bent portion 15 f of the enlarged diameter portion 15 c of the inner ring 15 can be avoided. Note that the flat surface angle (30 ° with respect to the axial direction) when the relief 15g is provided in the bent portion 15f of the enlarged diameter portion 15c of the inner ring 15 and the relief 24h in the bent portion 24g of the cover 24 are provided. The reason why the angle of the flat surface (45 ° with respect to the axial direction) is different is that the bending state is different between the bent portion 15 f of the inner ring 15 and the bent portion 24 g of the cover 24.

  Further, as shown in FIG. 32, an annular seal member 32 is interposed between the enlarged diameter portion 15c of the inner ring 15 and the cover 24 as a means for closing the openings formed in the cover 24 and the enlarged diameter portion 15c. ing. The opening 24i formed in the cover 24 and the enlarged diameter portion 15c is a hole 24i formed so as to penetrate the cover 24 in order to form the claw portion 24b for locking the inner centering spring 18 by raising the surface. [Refer to FIG. 24 (b) and FIG. 29] and an output formed on the enlarged diameter portion 15c of the inner ring 15 to transmit the rotational torque from the lever side clutch portion 11 to the output shaft 22 of the brake side clutch portion 12. It means a communicating portion with the hole 15d in which the protrusion 22f of the shaft 22 is inserted and arranged.

  As described above, the hole 15d formed in the enlarged diameter portion 15c of the inner ring 15 of the lever side clutch portion 11 and the hole 24i formed in the cover 24 of the brake side clutch portion 12 coincide with each other in the rotation direction due to the rotation of the inner ring 15. There is a case. Even if the hole 24i of the cover 24 and the hole 15d of the enlarged diameter portion 15c coincide with each other in the rotational direction so that the inside of the brake side clutch portion 12 communicates with the outside, the enlarged diameter portion of the cover 24 and the inner ring 15 is provided. Since the seal member 32 is interposed between the grease 15 and the cover 15, the grease sealed in the brake side clutch portion 12 leaks to the outside through the hole 15 d of the enlarged diameter portion 15 c and the hole 24 i of the cover 24. Can be prevented. Thus, since the grease leakage from the brake side clutch part 12 can be prevented, early wear and abnormal noise due to insufficient lubrication in the brake side clutch part 12 can be suppressed.

  Further, since the seal member 32 is interposed between the cover 24 and the enlarged diameter portion 15c of the inner ring 15, the cover 24 and the enlarged diameter portion 15c are not in direct contact with each other. It is possible to suppress the occurrence of metal powder due to wear of the enlarged diameter portion 15c, and to prevent the meshing failure of the cylindrical rollers 27 of the brake side clutch portion 12 and the deterioration of feeling.

  Further, since the contact force between the cover 24 and the seal member 32 and between the seal member 32 and the enlarged diameter portion 15c of the inner ring 15 can be reduced, the sliding resistance of the enlarged diameter portion 15c of the inner ring 15 with respect to the cover 24 is reduced. The lever operating force at the lever side clutch portion 11 can be reduced.

  The seal member 32 can be made of iron or resin. If a resin member is used as the seal member 32, the weight can be reduced as compared with the iron member. Further, when an iron member is used as the seal member 32, it is desirable that at least the contact surface with the enlarged diameter portion 15c is surface-treated. Examples of the surface treatment include a coating treatment of a material having a low coefficient of friction and wear resistance. If a material having a low friction coefficient is coated, sliding resistance can be reduced, and if a material having wear resistance is coated, durability can be improved. Further, when a resin member is used as the sealing member 32, if the sealing member 32 is formed of a material having a low friction coefficient and wear resistance, the sealing member itself can reduce sliding resistance and improve durability.

  A wedge clearance 26 is formed between the inner peripheral surface 23b of the brake-side outer ring 23 and the cam surface 22a of the output shaft 22 (see FIG. 5). The cover 24 is formed with a claw portion 24b protruding in the axial direction, and the claw portion 24b is disposed between the two locking portions 18a of the inner centering spring 18 of the lever side clutch portion 11 [FIG. 16 (b). And FIG. 34 (a) (b)]. The claw part 24b of the cover 24 is formed by raising the outer diameter side of the claw part forming position. A claw portion 24 d that protrudes in the axial direction is formed on the outer periphery of the cover 24. The claw portion 24d is disposed between the two locking portions 19a of the outer centering spring 19 of the lever side clutch portion 11 (see FIGS. 17A, 34A, and 34B).

  Two sets of locking portions 24e and 24f are formed on the outer periphery of the cover 24 by a stepped process (see FIGS. 34A and 34B). These locking portions 24e and 24f are in the direction of rotation with the claw portion 14g that slides on the end surface of the brake side outer ring 23 by the rotation of the lever side outer ring 14 with the cover 24 in contact with the end surface 23d of the brake side outer ring 23. By enabling the contact, it functions as a rotation stopper that regulates the operation angle of the operation lever. That is, when the lever side outer ring 14 is rotated by the operation of the operation lever, the claw portion 14g moves along the outer periphery of the cover 24 between the locking portions 24e and 24f of the cover 24.

Here, depending on the vehicle specifications the clutch unit X as described above is mounted, it is possible to vary the rotation angle of the lever side outer ring 14 by lever operation in a clockwise direction T ₁ and counterclockwise T ₂ [FIG. 8 (a) (b) and FIGS. 9 (a) and 9 (b)]. To address this specification, it is also possible to form the means for varying the rotational angle of the lever-side outer race 14 in the clockwise direction T ₁ and counterclockwise T ₂ the locking portion 24e of the cover 24, to 24f. Thus, it is possible to respond quickly and easily with respect to the lever upon rotation of the lever side outer ring 14 by the operation, the rotation angle of the lever side outer ring 14 required in the clockwise direction T ₁ and counterclockwise T ₂ are different specifications . In this case, the claw portions 14g of the lever-side outer race 14, a clockwise direction T ₁ with respect to the central axis L as in the prior art as shown by the broken line in FIGS. 8 (b) and 9 (b) shape counterclockwise direction T ₂ may be the same symmetrical shape.

The rotation angle of the lever-side outer race 14 as a means of differentiating between clockwise T ₁ counterclockwise direction T _2, a pair of engaging portions 24e, the structure in which the asymmetric position in the direction of rotation of the lever-side outer race 14 a 24f Is possible.

For example, the rotation angle of the lever side outer ring 14, in case of decreasing the rotation angle of the clockwise direction T ₁ than the rotation angle of the counterclockwise direction T ₂ are a pair of locking as shown by a broken line shown in FIG. 24 (b) parts 24e, with respect to the rotation direction central position M between 24f, than the counterclockwise direction spaced distance S ₂ in the clockwise side separation dimension S ₁ to one of the locking portion 24f 'is to the other engaging portion 24e The locking portion 24f ′ is arranged so as to be small (see FIGS. 29 and 33). That is, the clockwise movement end position may be changed from the locking portion 24f to the locking portion 24f ′.

Conversely, in the case of smaller than the rotation angle of the rotation angle clockwise T ₁ of the counter-clockwise direction T ₂ are a pair of locking portions 24e as shown by the broken line in FIG. 24 (b), the rotational direction between the 24f the central position M, one of the locking portion 24e so as to be smaller than the counter-clockwise side separation dimension S ₄ in the clockwise direction side separation dimension S ₃ until the locking portion 24e 'is to the other engaging portion 24f 'Is arranged (see FIG. 29 and FIG. 33). That is, the counterclockwise moving end position may be changed from the locking portion 24e to the locking portion 24e ′.

  On the outer periphery of the brake side plate 25, one flange portion 25e and two flange portions 25f are provided as clutch attachment portions to the seat lifter portion (see FIGS. 2 to 4). At the tips of these three flange portions 25e and 25f, holes 25g and 25h for attachment to the seat lifter portion are bored so that the cylindrical portions 25i and 25j are axially bent so as to surround the attachment holes 25g and 25h. Projected.

  FIGS. 26A to 26C show a resin friction ring 29. A plurality of circular protrusions 29a are provided on the end face of the friction ring 29 at equal intervals along the circumferential direction thereof, and the protrusions 29a are press-fitted into the holes 25c of the brake side plate 25 to be fitted to the brake side. It is fixed to the side plate 25 (see FIGS. 1 and 3).

  When the protrusion 29a is press-fitted, the fitting state with the hole 25c is obtained by elastic deformation of the protrusion 29a by the resin material. By adopting the press-fitting structure of the protrusions 29a and the holes 25c in this way, the friction ring 29 can be prevented from dropping off from the brake side plate 25 during handling and the like, and handling characteristics during assembly are improved. Can be made.

  The friction ring 29 is press-fitted into the inner peripheral surface 22e of the annular recess 22b formed in the large-diameter portion 22d of the output shaft 22 with a tightening margin (see FIGS. 18A and 19A and 19B). A rotational resistance is applied to the output shaft 22 by a frictional force generated between the outer peripheral surface 29 c of the friction ring 29 and the inner peripheral surface 22 e of the annular recess 22 b of the output shaft 22.

  On the outer peripheral surface 29c of the friction ring 29, a plurality of concave grooves 29b are formed at equal intervals in the circumferential direction (see FIG. 5). By providing the slit 29b in this manner, the friction ring 29 can be made elastic, so that the rate of change of the sliding torque with respect to the inner diameter tolerance of the output shaft 22 and the outer diameter tolerance of the friction ring 29 does not increase. .

  That is, the setting range of the rotational resistance provided by the frictional force generated between the outer peripheral surface 29c of the friction ring 29 and the inner peripheral surface 22e of the annular recess 22b of the output shaft 22 can be reduced, and the magnitude of the rotational resistance can be reduced. Can be set appropriately. Further, since the slit 29b becomes a grease reservoir, it is possible to suppress the outer peripheral surface 29c of the friction ring 29 from being worn by sliding with the inner peripheral surface 22e of the annular recess 22b of the output shaft 22.

  The operation of the lever side clutch portion 11 and the brake side clutch 12 in the clutch unit X having the above configuration will be described.

  In the lever side clutch portion 11, when an input torque acts on the lever side outer ring 14, the cylindrical roller 16 engages with a wedge clearance 20 between the lever side outer ring 14 and the inner ring 15, and the inner ring 15 is engaged via the cylindrical roller 16. Torque is transmitted and the inner ring 15 rotates. At this time, an elastic force is accumulated in the centering springs 18 and 19 as the lever-side outer ring 14 and the cage 17 rotate. When the input torque is lost, the lever-side outer ring 14 and the cage 17 are returned to the neutral state by the elastic force of the centering springs 18 and 19, while the inner ring 15 maintains the given rotational position. Therefore, the inner ring 15 rotates in a jog by repeating the rotation of the lever side outer ring 14, that is, by the pumping operation of the operation lever.

  In the brake-side clutch portion 12, when reverse input torque is input to the output shaft 22, the cylindrical roller 27 engages with the wedge clearance 26 between the output shaft 22 and the brake-side outer ring 23, and the output shaft 22 becomes the brake-side outer ring. 23 is locked. Accordingly, the reverse input torque from the output shaft 22 is locked by the brake side clutch portion 12 and the return of the reverse input torque to the lever side clutch portion 11 is interrupted.

  On the other hand, the input torque from the lever-side outer ring 14 is input to the inner ring 15 via the lever-side clutch portion 11, and the inner ring 15 comes into contact with the cylindrical roller 27 and presses against the elastic force of the leaf spring 28. The cylindrical roller 27 is removed from the wedge clearance 26, the locked state of the output shaft 22 is released, and the output shaft 22 becomes rotatable. When the inner ring 15 further rotates, the clearance between the hole 15d of the inner ring 15 and the protrusion 22f of the output shaft 22 is clogged, and the inner ring 15 comes into contact with the protrusion 22f of the output shaft 22 in the rotation direction, so that the input torque from the inner ring 15 is increased. The output shaft 22 is transmitted to the output shaft 22 through the protrusion 22f, and the output shaft 22 rotates.

  The clutch unit X having the structure described in detail above is used by being incorporated in, for example, an automobile seat lifter. FIG. 35 shows a seat seat 40 installed in a passenger compartment of an automobile. The seat 40 includes a seat 40a and a backrest 40b, and includes a seat lifter 41 that adjusts the height H of the seat 40a. The height H of the seating seat 40a is adjusted by the operation lever 41a of the seat lifter 41.

FIG. 36A conceptually shows one structural example of the sheet lifter unit 41. Seat slide adjuster 41b of the slide moving member 41b ₁ to the link member 41c, one end of 41d are respectively rotatably hinged. The other ends of the link members 41c and 41d are pivotally attached to the seating seat 40a. The other end of the link member 41c is pivotally attached to the sector gear 41f via the link member 41e. Sector gear 41f is pivotally rotatably sitting seat 40a, a swingable fulcrum 41f ₁ around. The other end of the link member 41d is pivotally attached to the seating seat 40a.

  The clutch unit X of the above-described embodiment is fixed to an appropriate part of the seating seat 40a. The clutch unit X is fixed to the seating seat 40a by plastically deforming the three flange portions 25e and 25f of the brake side plate 25 so that the distal end portions of the cylindrical portions 25i and 25j are expanded outward. It is fixed by caulking to a seat frame (not shown) of the seat 40a.

  On the other hand, an operation lever 41a made of resin, for example, is coupled to the lever side plate 13 of the lever side clutch portion 11, and a pinion gear 41g that meshes with a sector gear 41f that is a rotating member is provided on the output shaft 22 of the brake side clutch portion 12. Yes. The pinion gear 41g is integrally formed at the tip of the shaft portion 22c of the output shaft 22 as shown in FIGS. 1, 18A, 18B, and 19A, 19B.

  In FIG. 36B, 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 rotates counterclockwise. To do. Then, the sector gear 41f that meshes with the pinion gear 41g swings in the clockwise direction, and pulls the other end of the link member 41c through the link member 41e. As a result, both the link member 41c and the link member 41d stand up, and the seating surface of the seating seat 40a is raised.

  In this way, after adjusting the height H of the seating seat 40a, when the operation lever 41a is opened, the operation lever 41a is rotated clockwise by the elastic force of the two centering springs 18 and 19 to return to the original position ( Return to the neutral state. When the operation lever 41a is swung clockwise (downward), the seating surface of the seating seat 40a is lowered by the reverse operation. When the operation lever 41a is released after the height adjustment, the operation lever 41a rotates counterclockwise and returns to the original position (neutral state).

  The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the gist of the present invention. It includes the equivalent meanings recited in the claims and the equivalents recited in the claims, and all modifications within the scope.

11 Lever side clutch part 12 Brake side clutch part 13 Input side member (lever side side plate)
14 Input side member (lever side outer ring)
15 Connecting member (inner ring)
16 Engagement element (cylindrical roller)
17 Cage 18 First elastic member (inner centering spring)
19 Second elastic member (outer centering spring)
22 Output side member (output shaft)
22c Shaft 22g ₁ Shaft Root Side End Surface (Inclined Surface)
22 g ₂ shank root side end surface (parallel surfaces)
23 Static side member (brake side outer ring)
24 Static side member (cover)
25 Static side member (brake side plate)
26 Wedge clearance 27 Engagement element (cylindrical roller)
41g Pinion gear 41g ₁ Complete gear part 41g ₂ Incomplete gear part

Claims (9)

Provided on the input side, lever side clutch part that controls transmission / cutoff of rotational torque to the output side by lever operation, and provided on the output side, and transmits input torque from the lever side clutch part to the output side It consists of a brake side clutch that cuts off the reverse input torque from the output side,
The brake side clutch portion includes a pinion gear coaxially formed on a shaft portion, and includes an output side member that outputs torque from the pinion gear, and the pinion gear includes a complete gear portion formed on a distal end side of the shaft portion, and The shaft portion root side end surface located between the tooth portions of the incomplete gear portion has a cross-sectional shape along the axial direction along the radial direction. It is a discontinuous shape , and is composed of an inclined surface of an incomplete gear portion that is reduced in diameter toward the tip end side of the shaft portion, and a parallel surface of a complete gear portion that is parallel to the radial direction. A clutch unit formed by surface pressing toward the root side . The parallel surfaces of the complete gear unit, the clutch unit according to claim 1, the contour at the shaft portion root side end surface is formed along the shape of the tooth bottom. The parallel surfaces of the complete gear unit, the clutch unit according to claim 1 or 2 are equally spaced circumferentially the same number as teeth on the shaft portion the root side end surface. The parallel surface of the complete gear portion is located at a position of 25 to 50% from the front end side of the shaft portion of the entire length of the incomplete gear portion when the end surface on the base side of the shaft portion is only an inclined surface whose diameter is reduced toward the front end side of the shaft portion. The clutch unit according to any one of claims 1 to 3 , wherein the clutch unit is formed. The lever side clutch portion includes an input side member to which torque is input by lever operation, a connecting member that transmits torque from the input side member to the brake side clutch portion, and engagement between the input side member and the connecting member. A plurality of engagement elements that control transmission / cutoff of input torque from the input side member by detachment, a retainer that holds the engagement elements at predetermined intervals in the circumferential direction, and a stationary side member that is restricted in rotation, A first is provided between the cage and the stationary side member, accumulates an elastic force with an input torque from the input side member, and returns the cage to a neutral state with the accumulated elastic force by releasing the input torque. The elastic member is provided between the input side member and the stationary side member, and an elastic force is accumulated by an input torque from the input side member. By releasing the input torque, the input side member is moved by the accumulated elastic force. Return to neutral Clutch unit according to any one of claims 1 to 4, and a second elastic member. The brake side clutch portion includes a connecting member to which torque from the lever side clutch portion is input, an output side member to which torque is output, a stationary side member in which rotation is restricted, and the stationary side member and the output side member. A plurality of pairs of engagement elements that are disposed in a wedge clearance between the members and control transmission of input torque from the connecting member and blocking of reverse input torque from the output side member by engagement / disengagement between the two members. The clutch unit according to any one of claims 1 to 4 . The clutch unit according to claim 5 or 6 , wherein at least one of the engaging member of the lever side clutch portion or the engaging member of the brake side clutch portion is a cylindrical roller. The clutch unit according to any one of claims 1 to 7 , wherein the lever side clutch part and the brake side clutch part are incorporated in an automobile seat lifter part. The clutch unit according to claim 8 , wherein an input side member of the lever side clutch portion is coupled to an operation lever, and an output side member of the brake side clutch portion is connected to a link mechanism of an automobile seat lifter portion.

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