JP5207778B2 - Clutch unit - Google Patents

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.

  This type of clutch unit is incorporated in, for example, an automobile seat lifter that adjusts a seat up and down by lever operation, and transmits a rotational torque from the input side to the output side, and a rotational torque from the input side. Is transmitted to the output side, and a brake side clutch portion that interrupts the reverse input torque from the output side is provided (see, for example, Patent Document 1).

  30 is a longitudinal sectional view showing the entire configuration of the conventional clutch unit disclosed in Patent Document 1, FIG. 31 is a sectional view taken along the line DD in FIG. 30, and FIG. 32 is a line taken along the line EE in FIG. FIG.

  As shown in FIGS. 30 and 31, 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 130 is a washer attached to the output shaft 122 via a wave washer 131. .

  On the other hand, as shown in FIGS. 30 and 32, 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 clearance. The engagement / disengagement between the brake-side outer ring 123 and the output shaft 122 causes the transmission of input torque from the inner ring 115 and the output shaft 122. The main part is constituted by a plurality of pairs of cylindrical rollers 127 that control the interruption of the reverse input torque.

In addition, the large diameter part 115c which expanded the axial direction edge part of the inner ring | wheel 115 functions as a holder | retainer which hold | maintains the cylindrical roller 127 at a predetermined interval in the circumferential direction. In the figure, 125 is a brake side plate that is fixed to the brake side outer ring 123 by caulking and constitutes a stationary side member together with the brake side outer ring 123, and 128 is a leaf spring having an N-shaped cross section, for example, disposed between each pair of cylindrical rollers 127. Reference numeral 129 denotes a friction ring as a braking member attached to the brake side plate 125.
JP 2003-166555 A

  By the way, the lever side clutch part 111 in the conventional clutch unit disclosed in Patent Document 1 transmits the torque from the lever side outer ring 114 to which torque is inputted by lever operation and the lever side outer ring 114 to the brake side clutch part 112. A plurality of cylindrical rollers 116 for controlling transmission / cutoff of input torque from the lever-side outer ring 114 by engagement / disengagement with the inner ring 115 to be held at predetermined intervals in the circumferential direction; The elastic force is accumulated with the input torque from the lever side outer ring 114, and the cage 117 is returned to the neutral state with the accumulated elastic force by releasing the input torque. And an inner centering spring 118 (see FIG. 30) (see FIG. 2 and FIG. 3 of Patent Document 1).

  The inner centering spring 118 disclosed in Patent Document 1 is a C-shaped spring member having a band plate shape. However, in order to reduce the axial dimension of the clutch unit and to make it compact, the inner centering spring 118 is provided. It is preferable that the cross-sectional shape is circular. The retainer 117 in the case where the inner centering spring 118 has a circular cross-sectional shape is illustrated in FIGS. 33 and 34A to 34D.

  The cage 117 is a cylindrical member in which a plurality of pockets 117a for accommodating the cylindrical rollers 116 are formed at equal intervals in the circumferential direction, and the inner centering spring 118 has a pair of locking portions bent inward in the radial direction. This is a C-shaped spring member having a circular section having 118a [see FIG. 34 (b)]. Two notch recesses 117b are formed at one end of the retainer 117, and the locking part 118a of the inner centering spring 118 is locked to two adjacent end surfaces 117c of each notch recess 117b. .

  When the input torque from the lever-side outer ring 114 is applied, the inner centering spring 118 has one locking portion 118 a on one end surface 117 c of the retainer 117 and the other locking portion 118 a on the claw portion of the brake-side outer ring 123. (Not shown), the inner centering spring 118 is pushed and expanded as the lever-side outer ring 114 rotates, and an elastic force is accumulated. When the input torque from the lever-side outer ring 114 is released, the elasticity is increased. The cage 117 is returned to the neutral state by the restoring force.

  Here, in the cage 117 disclosed in Patent Document 1, the end surface 117c to which the locking portion 118a of the inner centering spring 118 is locked has a straight shape along the axial direction. In consideration of the property, it is preferable to form a chamfered portion 117d at the tip of the end surface 117c as shown in FIGS. 33 and 34 (a) and 34 (b). If the chamfered portion 117d is formed at the tip of the end surface 117c of the retainer 117 in this way, the engaging portion 118a of the inner centering spring 118 is inserted from the axial direction into the notch recess 117b of the retainer 117 and comes into contact with the end surface 117c. Assembling work to be facilitated.

  However, the inner centering spring 118 is assembled between the retainer 117 and the brake outer ring 123 as described above, but due to the assembly tolerance, the retainer 117 moves in the axial direction so as to be separated from the brake outer ring 123. In this case, the inner centering spring 118 tries to sink into the gap between the retainer 117 and the brake outer ring 123. As a result, the tip edge portion of the end surface 117c of the retainer 117 is worn, and the locking portion 118a of the inner centering spring 118 is easily pulled out from the end surface 117c of the retainer 117.

  This phenomenon remarkably occurs in a structure in which a chamfered portion 117d is formed at the tip of the end surface 117c of the retainer 117 as indicated by an arrow in FIG. When the locking portion 118a of the inner centering spring 118 is removed from the end surface 117c of the retainer 117, the inner centering spring 118 sinks into the gap between the retainer 117 and the brake outer ring 123, and the function of the inner centering spring 118 is increased. It may be difficult to demonstrate.

  Therefore, the present invention has been proposed in order to improve the above-mentioned points, and the object of the present invention is to prevent the inner centering spring from coming off from the cage, and to ensure the function of the inner centering spring. The object is to provide a clutch unit that can be exerted.

  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 that cuts off the reverse input torque from the output side. The lever side clutch portion includes the input side member to which torque is input by lever operation and the torque from the input side member. A retainer for holding a plurality of engagement elements in the circumferential direction at predetermined intervals by controlling engagement / disengagement of input torque from the input side member by engagement / disengagement with the connecting member that transmits the brake to the brake side clutch portion And an engaging portion that is engaged with the end face of the cage, accumulates an elastic force by the input torque from the input side member, and keeps the accumulated elastic force by releasing the input torque. Comprising a configuration in which an elastic member for returning to the neutral state vessel.

As a technical means for achieving the above-mentioned object, the clutch unit of the present invention is a C-shaped spring member having a circular cross section having a pair of engaging portions bent radially inward. The end surface of the cage that comes into contact with the locking portion has an R-shaped cross section , and a hook portion that holds the locking portion projects from the end surface of the cage where the locking portion is locked.

  In the present invention, the hook portion for holding the latching portion of the elastic member is provided on the end surface of the cage to which the latching portion of the elastic member is latched, so that the latching portion of the elastic member becomes the end surface of the cage. Even if it is going to be pulled out from the hook, it is possible to prevent the hooking portion from being pulled out. As a result, it becomes easy to maintain the state in which the locking portion of the elastic member is locked to the end surface of the cage, and the function of the elastic member can be reliably exhibited.

This elastic member is a C-shaped spring member having a circular cross section having a pair of locking portions bent radially inward, and the end surface of the cage that comes into contact with the locking portions has an R-shaped cross section . Thus, by making the end surface of the cage into a cross-sectional R shape that matches the outer shape of the locking portion of the elastic member, the contact state in which the locking portion of the elastic member contacts the end surface of the cage is stabilized. And it is much easier to maintain that state.

  Further, it is desirable that the protruding dimension of the hook portion protruding from the end face of the cage is 1/6 to 1/3 of the outer diameter of the elastic member (the outer diameter when the elastic member is circular in cross section). . In this way, it is possible to reliably prevent the locking portion of the elastic member from being pulled out from the end face of the cage, and to move over the catch portion when the elastic member is assembled to the cage. It becomes easy to insert the locking portion into the end face of the cage from the axial direction.

  In addition, when the protrusion dimension of the hook part is smaller than 1/6 of the outer dimension of the elastic member, the engaging part of the elastic member is easily pulled out from the end face of the cage, and conversely, when it is larger than 1/3. When the elastic member is assembled to the cage, it is difficult to insert the latching portion of the elastic member into the end surface of the cage from the axial direction by getting over the hook portion.

  Furthermore, it is desirable to form a chamfered portion at the protruding end of the hook portion protruding from the end surface of the cage. In this way, the hooking portion can be easily climbed over when the elastic member is assembled to the cage, so that it is much easier to insert the locking portion of the elastic member into the end surface of the cage from the axial direction. Become.

  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 hook portion for holding the locking portion of the elastic member is provided on the end surface of the cage to which the locking portion of the elastic member is locked, so that the locking portion of the elastic member is held by the cage. Even if it is going to be pulled out from the end face, the hooking portion can be prevented from being pulled out. As a result, it becomes easy to maintain the state in which the locking portion of the elastic member is locked to the end surface of the cage, and the function of the elastic member can be surely exhibited. Can be provided.

  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 19 are diagrams showing main components of the clutch unit X. FIG. 20 to 25 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 section (see FIGS. 26 and 27A and 27B) 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. 7 (c)) of the lever-side outer ring 14 to be described later. The lever-side side plate 13 is caulked and fixed 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. Of these claw portions 14f and 14g, one claw portion 14f is inserted and disposed between two locking portions 19a (see FIG. 12A) of an outer centering spring 19 to be described later, and the remaining two 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 the end surface of a brake side outer ring 23 (see FIG. 16B), which will be described later. The operation angle of the operation lever is regulated by allowing contact with two locking portions 24e and 24f [see FIG. 17 (b)] provided as a rotation stopper in the rotation direction.

  Further, a plurality of (five in the drawing) notch recesses 14e into which the claw portions 13b of the lever side plate 13 (see FIGS. 6A and 6B) are inserted are formed on the outer periphery of the lever side outer ring 14. Yes. 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. 8A and 8B show the inner ring 15. The inner ring 15 has an outer peripheral surface 15a that forms a wedge clearance 20 (see FIG. 4) between the outer diameter of the bottomed cylindrical portion 15b through which the output shaft 22 is inserted and the cam surface 14a of the lever side outer ring 14. I have. Further, an enlarged diameter portion 15c is integrally formed at the end of the cylindrical portion 15b, and the enlarged diameter portion 15c accommodates the cylindrical roller 27 and the leaf spring 28 in order to function as a cage for the brake side clutch portion 12. Pockets 15e to be formed are formed at equal intervals in the circumferential direction. 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.

By punching the bottom portion of the cylindrical portion 15b with a press, a hole 15f into which the output shaft 22 (lever-side shaft portion 22c ₁ described later) is rotatably inserted is formed in the bottom portion. The inner diameter surface of the hole 15f serves as a guide surface for the rotatable output shaft 22. The inner diameter dimension of the cylindrical portion 15 b is set to be larger than the outer diameter dimension of the output shaft 22, whereby a gap m is formed between the inner diameter of the cylindrical portion 15 b and the outer diameter of the output shaft 22. As described above, the inner ring 15 is formed by punching the bottom of the cylindrical portion 15b with a press to form a hole 15f through which the output shaft 22 is rotatably inserted. To reduce the cost of manufacturing

  As shown in FIGS. 20A and 20B, the inner ring 15 is assembled by inserting the output shaft 22 into the hole 15f at the bottom of the cylindrical portion 15b from the enlarged diameter portion 15c side. At this time, chamfer 15g is given to the inner peripheral edge of the hole 15f so that the output shaft 22 can be easily inserted into the hole 15f of the cylindrical part 15b. The chamfer 15g serves as a guide surface when the output shaft 22 is inserted. Further, by forming the inner diameter dimension of the cylindrical portion 15 b larger than the outer diameter dimension of the output shaft 22, a gap m is formed between the inner diameter of the cylindrical portion 15 b and the outer diameter of the output shaft 22. Even if there is a protrusion such as a scratch on the outer diameter surface of the 22, it is possible to insert the output shaft 22 into the cylindrical portion 15 b, thereby improving the assemblability.

  9 and 10 (a) to 10 (e) show a cage 17 made of resin. 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. 10 (b)].

  11A and 11B show the inner centering spring 18. The inner centering spring 18 is composed of a C-shaped spring member having a circular section and having a pair of locking portions 18a bent radially inward, and is located on the inner diameter side of the outer centering spring 19 (see FIG. 1). The inner centering spring 18 is disposed between the retainer 17 and a cover 24 that is a stationary side member of the brake side clutch portion 12 (see FIGS. 21A and 21B), and is held by both locking portions 18a. Locked to the two end faces 17c (see FIG. 9 and FIG. 10 (b)) of the container 17 and locked to the claw portion 24b (see FIGS. 17 (a) and (b)) provided on the cover 24. .

  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.

  As shown in FIG. 9 and FIG. 10B and FIG. 10D, a hook for holding the locking portion 18a of the inner centering spring 18 on the end surface 17c of the retainer 17 to which the locking portion 18a of the inner centering spring 18 is locked. A portion 17d is provided projecting in the circumferential direction. As described above, the inner centering spring 18 is assembled between the retainer 17 and the cover 24, but due to the assembly tolerance, the retainer 17 may move in the axial direction so as to be separated from the cover 24. In that case, the inner centering spring 18 tries to dive into the gap between the retainer 17 and the cover 24, but since the hooking portion 17d is projected, the locking portion 18a of the inner centering spring 18 is Even if it is going to be pulled out from the end surface 17c of the cage 17 in the axial direction, the catching portion 17d can prevent the locking portion 18a from being pulled out. As a result, it is easy to maintain the state in which the locking portion 18a of the inner centering spring 18 is locked to the end surface 17c of the retainer 17, and the function of the inner centering spring 18 can be reliably exhibited.

  Since the inner centering spring 18 has a circular cross section, the end surface 17c of the retainer 17 that contacts the locking portion 18a of the inner centering spring 18 has an R shape in cross section. Thus, by making the end surface 17c of the retainer 17 into a cross-sectional R shape that matches the outer diameter shape of the retaining portion 18a of the inner centering spring 18, the retaining portion 18a of the inner centering spring 18 becomes the end surface of the retainer 17. The contact state in contact with 17c can be stabilized.

  Further, the projecting dimension t of the hooking portion 17 d provided on the end surface 17 c of the cage 17 is 1/6 to 1/3 of the outer diameter of the inner centering spring 18. By defining the dimensions in this manner, it is possible to reliably prevent the locking portion 18a of the inner centering spring 18 from being pulled out from the end surface 17c of the retainer 17 in the axial direction, and the inner centering spring 18 to the retainer 17. When assembling, it is easy to get over the hook portion 17d and insert the locking portion 18a of the inner centering spring 18 into the end surface 17c of the retainer 17 from the axial direction.

  If the protrusion dimension t of the hook portion 17d is smaller than 1/6 of the outer diameter of the inner centering spring 18, the locking portion 18a of the inner centering spring 18 can be easily pulled out from the end surface 17c of the cage 17 in the axial direction. On the other hand, when the inner centering spring 18 is larger than 1/3, when the inner centering spring 18 is assembled to the retainer 17, the catching portion 17d is moved over and the locking portion 18a of the inner centering spring 18 is pivoted to the end surface 17c of the retainer 17. It becomes difficult to insert from the direction.

  The front end surface 17e of the hook portion 17d projecting from the end surface 17c of the cage 17 is formed parallel to the axial direction of the cage 17, and extends forward from the end surface 17c at an angle of, for example, about 45 °. It is also possible to use a tapered inclined surface. Further, as shown in FIG. 10 (e), if the chamfered portion 17f is formed at the protruding end of the tip end surface 17e of the hooking portion 17d, the hooking portion 17d can be easily overcome when the inner centering spring 18 is assembled to the cage 17. Therefore, it becomes much easier to insert the locking portion 18a of the inner centering spring 18 into the end surface 17c of the retainer 17 from the axial direction.

  12A and 12B 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. 1). Further, as will be described later, the outer centering spring 19 is disposed between the cover 24 and the lever-side outer ring 14 in a state where the radial position is regulated by a rising portion 24g (see FIG. 1) provided on the input-side end surface of the cover 24. It is arranged in a space formed between them.

  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 19a are provided on the lever-side outer ring 14 as shown in FIG. It is locked to the claw portion 14f provided and locked to the claw portion 24d provided to the cover 24 (see FIGS. 7A to 7C and FIGS. 17A and 17B). The locking portion 19 a is arranged with a circumferential phase (180 °) shifted from the locking portion 18 a of the inner centering spring 18.

  In the outer centering spring 19, when the lever-side outer ring 14 rotates due to the input torque from the lever-side outer ring 14, one locking portion 19 a is connected to the claw portion 14 f of the lever-side outer ring 14 and the other locking portion 19 a. Are 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. When the input torque from the lever side outer ring 14 is released, The lever side outer ring 14 is returned to the neutral state by the elastic restoring force.

  When the outer centering spring 19 is pushed and expanded in the circumferential direction, a radially outward force acts on the locking portion 19a, and the outer centering spring 19 tends to be displaced in the radial direction. However, since the position of the outer centering spring 19 is regulated in the radial direction by the rising portion 24g of the cover 24 (see FIGS. 17 (a), (b) and FIG. 23), displacement in the radial direction is prevented in advance. Thus, the outer centering spring 19 can be reliably and stably operated.

13 and FIGS. 14A to 14C show the output shaft 22. The output shaft 22 includes a lever side shaft portion 22c ₁ located on the lever side clutch portion 11 side, a brake side shaft portion 22c ₂ located on the brake side clutch portion 12 side, and the lever side shaft portion 22c ₁ it is arranged between the brake-side shaft portion 22c _2, a forged part which is integrally formed a large diameter portion 22d which is enlarged radially extends outward. This tip of the brake-side shaft portion 22c _2, the pinion gear 41g for connecting the seat lifter section 41 is formed integrally.

  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 8A and 8B).

When manufacturing the output shaft 22 including the lever side shaft portion 22c ₁ , the large diameter portion 22d and the brake side shaft portion 22c ₂ by forging, first, the lever side shaft portion 22c ₁ is fixed as shown in FIG. thereby molding the brake-side shaft portion 22c ₂ in the movable side of the mold 50b with molding in the side of the mold 50a. At this time, the portion to be the large-diameter portion 22d is formed in a flange shape, then, to the fixed side of the mold 50c for supporting the lever-side shaft portion 22c _1, as shown in FIG. 22 (b), the brake-side shaft the part 22c ₂ for forming the large diameter portion 22d at the movable side of the mold 50d for supporting. In that case, there is a possibility that the coaxial deviation occurs between the lever-side shaft portion 22c ₁ and the brake-side shaft portion 22c _2, lathing as post-processing the brake-side shaft portion 22c ₂ after its forging.

By performing turning as post-processing after forging the brake-side shaft portion 22c _2, to ensure the coaxiality of the lever-side shaft portion 22c ₁ and the brake-side shaft portion 22c _2. If securing coaxiality of such a lever-side shaft portion 22c ₁ and the brake-side shaft portion 22c ₂ in the pore 25b [Figure 18 of the brake-side side plate 25 of the brake-side shaft portion 22c ₂ is inserted (a) ( The positioning accuracy with respect to b) is improved. That is, to avoid that by ensuring coaxiality between the lever-side shaft portion 22c ₁ and the brake-side shaft portion 22c _2, brake-side shaft portion 22c ₂ with respect to the rotation of the lever-side shaft portion 22c ₁ eccentrically rotates it can. As a result, the brake-side shaft portion 22c ₂ that is inserted into the hole 25b of the brake-side side plate 25 is able to reduce the resistance due to contact with the brake-side side plate 25, increases the lever operating torque at the lever side clutch section 11 Can be suppressed.

Further, as described above, the output shaft 22 includes a plurality (for example, six) of flat cam surfaces 22a on the outer peripheral surface, and a plurality (for example, six) of protrusions 22f on the end surface on the lever side shaft portion 22c ₁ side. Have In the output shaft 22 is manufactured by forging simultaneously with a fixed side mold 50c for molding the lever-side shaft portion 22c ₁ and a plurality of cam surfaces 22a projecting 22f as shown in FIG. 22 (b) molding To do. That is, the die 50c of the stationary side has a peripheral wall portion 50c ₁ for molding a cam surface 22a of the large diameter portion 22 d, and a recess 50c ₂ for molding the projection 22f.

By co-molded with the peripheral wall portion 50c ₁ and the recess 50c ₂ having such a plurality of cam surfaces 22a and the projection 22f of one of the mold 50c, displacement occurs in the relative positional relationship between the projection 22f and the cam surface 22a Hateful. That is, when the torque is transmitted from the lever side clutch portion 11 to the brake side clutch portion 12, the cylindrical roller 27 engaged on the cam surface 22a is released from the wedge clearance 26, so that the output shaft 22 is unlocked. Thus, the relative position between the cam surface 22a and the protrusion 22f is such that 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 contacts the protrusion 22f of the output shaft 22 in the rotational direction. Relationship is set. Therefore, if the relative positional relationship between the cam surface 22a and the protrusion 22f is less likely to shift, the hole 15d of the inner ring 15 and the protrusion 22f of the output shaft 22 can be reliably contacted after the locked state of the output shaft 22 is released. It is possible to make contact and smooth torque transmission is possible.

  15A to 15D show a leaf spring 28 having an N-shaped cross section. As shown in FIGS. 15 (a) to 15 (c), the leaf spring 28 has an R shape having a different size between one bent portion 28a and the other bent portion 28b. 15A to 15C illustrate, for example, a case where one bent portion 28a has a small R shape and the other bent portion 28b has a large R shape.

  As shown in FIG. 15 (d), when the bent portion 28 a and the other bent portion 28 b are formed in an R shape having different sizes, the leaf spring 28 can be handled during transportation. When the plurality of leaf springs 28 are vertically stacked, if the plurality of leaf springs 28 are overlapped so that one bent portion 28a and the other bent portion 28b are alternately positioned in the vertical direction, Since the R-shaped size of the one bent portion 28a and the other bent portion 28b are different from each other, the bent portions 28a and 28b are not fitted into each other, and the brake side clutch portion of the leaf spring 28 is fitted. The work to be separated at the time of assembling to 12 becomes easy.

  The plate spring 28 has chamfers 28c at both ends in the plate width direction of the end portion on the side where the one bent portion 28a is located. When the leaf spring 28 is transported, the leaf spring 28 is placed on the conveyance path in a state where the end portion on the side where the one bent portion 28a is located [state of FIGS. 15 (a) to 15 (c)], When moving in the direction of the arrow in FIG. 15 (a), the end on the side where one bent portion 28a is located is in sliding contact with the conveying path, but the one bent portion 28a is located. By forming the chamfer 28c at the end on the side, the leaf spring 28 can be smoothly transferred on the conveyance path without being caught on the conveyance path.

  In the case described above, the chamfers 28c are formed at both ends in the plate width direction of the end portion on the side where one bent portion 28a is located, but the plate width of the end portion on the side where the other bent portion 28b is located. Chamfering may be formed at both ends in the direction. In this case, the leaf spring 28 can be smoothly moved regardless of the vertical direction of the leaf spring 28.

  16 (a) to 16 (c) and FIGS. 17 (a) to 17 (c) show the brake side outer ring 23 and its cover 24. FIG. The brake-side outer ring 23 is a thick plate-like member obtained by punching one material with a press, and the cover 24 is formed by pressing another material with a press. 18A and 18B show the brake side plate 25. FIG. The brake outer ring 23 and the cover 24 are caulked and fixed integrally by the brake side plate 25. 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.

  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. The claw portions 25a of the brake side plate 25 are inserted into the cutout recesses 23a and 24a (see FIGS. 21A and 21B and FIG. 24A). By tightening the claw portions 25a of the brake side plate 25 inserted into the notches 23a and 24a, the brake outer ring 23 and the cover 24 are connected and integrated with the brake side plate 25 (see FIG. 24B). . The crimping of the claw portion 25a of the brake side plate 25 is performed by expanding the bifurcated tip end portion of the claw portion 25a outward as shown in FIGS.

As shown in FIGS. 16 (a) to 16 (c) and FIGS. 17 (a) to (c), the notch recess 23a of the brake-side outer ring 23 and the notch recess 24a of the cover 24 are opposed to the opposite side end surfaces 23a ₁ , has a tapered to form a predetermined angle θ with respect to 24a ₁ are radially. That is, both side end surfaces 23a ₁ of the notch recess 23a and both end surfaces 24a ₁ of the notch recess 24a are tapered so as to be inclined toward the radially outer side, and the widths of the side end surfaces 23a ₁ and 24a ₁ . The dimensions are gradually reduced toward the outside in the radial direction.

Thus, by the both end faces 24a ₁ of the cutout recess 24a of the both end surfaces 23a ₁ and the cover 24 of the cutout recess 23a of the brake-side outer race 23 has a tapered shape, their notched recess 23a, which is inserted into 24a The amount by which the claw portion 25a of the brake side plate 25 moves radially outward can be reduced, and the claw portion 25a of the brake side plate 25 is prevented from coming out of the notches 23a and 24a.

Further, the notch recess 23a of the brake side outer ring 23 and the notch recess 24a of the cover 24 are provided with trapezoidal receiving portions 23a ₂ and 24a ₂ on the bottom surfaces thereof. By providing such trapezoidal receiving portions 23a ₂ and 24a ₂ , the movement of the claw portions 25a of the brake side plate 25 inserted into the notch recesses 23a and 24a inward in the radial direction can be restricted. . It is preferable to form the chamfer 23a ₃ the edge of the brake-side side plate 25 side at the bottom surface of the cutout recess 23a of the brake-side outer ring 23 [see FIG. 16 (a)]. Since the chamfer 23a ₃ serves as a relief of the bent base portion of the claw portion 25a of the brake side plate 25, the claw portion 25a of the brake side plate 25 can be reliably brought into contact with the receiving portions 23a ₂ and 24a _2. Therefore, the movement inward in the radial direction can be reliably controlled.

  As described above, the brake-side outer ring 23 and the brake-side side plate 25 that are integrated with the cover 24 need to be assembled in close contact with each other without a gap. On the other hand, since the brake-side outer ring 23 is a thick plate-like member obtained by punching a single material with a press, burrs may exist at the inner and outer diameter edge portions.

  Therefore, as shown in FIGS. 18A and 18B, annular concave grooves 25m and 25n for escaping burrs existing on the brake side outer ring 23 are formed on the surface of the brake side side plate 25 facing the brake side outer ring 23, as shown in FIGS. ing. The inner concave groove 25m positioned on the radially inner side is provided at a position corresponding to the inner diameter edge portion of the brake side outer ring 23, and the outer concave groove 25n positioned on the outer side in the radial direction is formed on the outer diameter edge portion of the brake side outer ring 23. It is provided at the corresponding position.

  As described above, by forming the inner concave groove 25m and the outer concave groove 25n on the surface facing the brake side outer ring 23 of the brake side side plate 25, even if burrs exist on the inner and outer diameter edge portions of the brake side outer ring 23, The burrs can be accommodated in the inner concave grooves 25m and the outer concave grooves 25n, so that no burrs are sandwiched, and the brake-side outer ring 23 and the brake-side side plate 25 can be assembled without any gaps. 25 (a) and (b)]. As a result, the conventional deburring process for the brake side outer ring 23 is not required, the cost for manufacturing the brake side outer ring 23 can be reduced, and the assembly of the brake side side plate 25 and the brake side outer ring 23 is improved. To do.

  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 projecting 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. And see FIG.

  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. 12A and 23). On the inner periphery of the cover 24, a rising portion 24g is formed concentrically with the punching hole 24c, and the radial position of the outer centering spring 19 is regulated by the rising portion 24g.

  Two sets of locking portions 24e and 24f are formed on the outer periphery of the cover 24 by a stepped process (see FIGS. 21A and 21B). These locking portions 24e and 24f are in contact with the claw portion 14g that slides on the end surface of the brake side outer ring 23 by the rotation of the lever outer ring 14 with the cover 24 in contact with the end surface of the brake side outer ring 23 in the rotation direction. By making it possible, it functions as a rotation stopper that regulates the operation angle of the operation lever. That is, if the lever 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.

  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. 19A to 19C 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 margin (see FIGS. 14A and 14B). 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. By applying this rotational resistance, stick-slip noise caused by a sudden slip occurring between the brake side plate 25 that is a stationary side member and the output shaft 22 is prevented in advance. The magnitude of this rotational resistance may be set as appropriate in consideration of the magnitude of the reverse input torque input to 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 the wedge clearance 20 between the lever outer ring 14 and the inner ring 15, and torque is applied to the inner ring 15 via the cylindrical roller 16. 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. 26 shows a seat 40 installed in a passenger compartment of a car. 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. 27A 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. The seat frame 40c (see FIG. 28) is fixed by caulking.

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 brake-side shaft portion 22c ₂ of FIG. 1 and FIG. 14 (a) (b) are shown as the output shaft 22.

The seat frame 40c described above, as shown in FIG. 28, the hole 40c ₁ of the tip shaft portion 22c ₃ of the output shaft 22 is inserted is formed, the elastic portion 40c ₂ is formed on the periphery of the hole 40c ₁ ing. The elastic portion 40c ₂ is a peripheral portion of the hole 40c ₁ of the seat frame 40c is bent toward the axially outer side, further, it forms a U-shape by molding to wrap toward the axially inner side. In other words, the elastic portion 40c ₂ is composed of an outer cylindrical portion _{40c 21} it provided continuously been an inner cylindrical portion _{40c 22.}

By providing such an elastic portion 40c _2, when the output shaft 22 is rotated about the lever-side shaft portion 22c _1, also as a brake-side shaft portion 22c ₂ is eccentrically rotated, the elastic deformation of the elastic portion 40c ₂ Thus, the eccentric amount of the brake side shaft portion 22c ₂ can be absorbed, and the resistance caused by the contact between the elastic portion 40c ₂ of the seat frame 40c and the front end shaft portion 22c ₃ of the output shaft 22 can be reduced. An increase in the lever operation torque can be suppressed.

The elastic portion 40c ₂ described above, it is effective to be thinner than other portions of the seat frame 40c. If the elastic portion 40c ₂ and thin, it is possible to elastic deformation thereof is facilitated, the resistance due to contact between the elastic portion 40c ₂ of the seat frame 40c and the tip end shaft portion 22c ₃ of the output shaft 22 to further reduce. Further, the gap amount s between the outer cylindrical portion _{40c 21} and the inner cylindrical portion _{40c 22} of the elastic portion 40c ₂ may be set equal to the eccentricity expected amount of the tip end shaft portion 22c ₃ of the output shaft 22.

In the above-mentioned seat frame 40c, it has been described as being integrally formed resilient portion 40c _2, as shown in FIG. 29, it is also possible to provide an elastic portion 40c ₃ and the seat frame 40c separately. The elastic portion 40c _3, as the outer cylindrical portion _{40c 31} and the inner cylindrical portion _{40c 32} provided continuously to wrap one end on the inside, to bend the other end of the outer cylindrical portion _{40c 31} outwardly It consists of the flange part 40c ₃₃ provided continuously, and is comprised with the iron-type member which has flexibility.

The elastic portion 40c ₃ is attached by press-fitting the outer cylindrical portion 40c ₃₁ into the hole 40c ₄ of the seat frame 40c, or the flange portion 40c ₃₃ is welded to the peripheral portion of the hole 40c ₄ of the seat frame 40c. Can be attached. Incidentally, operation and effect of the elastic portion 40c ₃ are the same as the elastic portion 40c ₂ of FIG. 28, description will not be repeated.

  In FIG. 27B, when the operation lever 41a is swung counterclockwise (upward), the input torque in that direction is transmitted to the pinion gear 41g via the clutch unit X, and the pinion gear 41g 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.

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 a lever side outer ring | wheel, (b) is a left part side view of (a), (c) is a right 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 a sectional view showing a cage, (b) is a left side view of (a), (c) is a sectional view of (a), and (d) is an enlarged arrow view from a hollow arrow in (b). FIG. 4E is an enlarged view showing a modified example of FIG. (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) is a perspective view showing a leaf spring of a brake side clutch portion, (b) is a front view of (a), (c) is a left side view of (a), and (d) is a leaf spring of (b). It is a front view which shows the state piled up. (A) is sectional drawing which shows a brake side outer ring | wheel, (b) is a left view of (a), (c) is the elements on larger scale which show the notch recessed part of (b). (A) is sectional drawing which shows a cover, (b) is a left view of (a), (c) is the elements on larger scale which show the notch recessed part of (b). (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). (A) is sectional drawing which shows the state before attaching an inner ring | wheel to an output shaft, (b) is sectional drawing which shows the state after attaching an inner ring | wheel to an output shaft. (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. (A) is sectional drawing which shows the metal mold | die which shape | molds the large diameter part of an output shaft, (b) is sectional drawing which shows the metal mold | die which shape | molds the cam surface and protrusion of an output shaft. It is sectional drawing which follows the CC line of FIG. It is a caulking structure of a brake side outer ring and a cover and a brake side side plate, (a) is an essential part enlarged plan view showing a state before caulking, and (b) is an essential part enlarged plan view showing a state after caulking. is there. (A) is a perspective view showing a state before the brake side outer ring is assembled to the brake side plate, and (b) is a perspective view showing a state after the brake side outer ring is assembled to the brake side side plate. 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 state which assembled | attached the clutch unit (refer FIG. 1) to the seat frame of a seat lifter part. It is a longitudinal cross-sectional view which shows the modification of the seat frame of a seat lifter part. It is a longitudinal cross-sectional view which shows the whole structure of the conventional clutch unit. It is a cross-sectional view which follows the DD line | wire of FIG. It is a cross-sectional view which follows the EE line | wire of FIG. It is a perspective view which shows the holder | retainer in the conventional clutch unit. (A) is a cross-sectional view of the cage of FIG. 33, (b) is a left side view of (a), (c) is a cross-sectional view of (a), and (d) is from the white arrow in (b). It is an enlarged arrow view.

Explanation of symbols

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 17c End face 17d Hook part 17f Chamfer 18 First elastic member (inner centering spring)
18a Locking portion 19 Second elastic member (outer centering spring)
22 Output side member (output shaft)
23 Static side member (brake side outer ring)
24 Static side member (cover)
25 Static side member (brake side plate)
27 Engaging element (cylindrical roller)

Claims (8)

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 lever side clutch portion is separated from the input side member by engagement / disengagement between an input side member to which torque is input by lever operation and a connecting member that transmits torque from the input side member to the brake side clutch portion. A retainer that holds a plurality of engagement elements that control transmission / interruption of the input torque at a predetermined interval in the circumferential direction, and a locking portion that is locked to an end surface of the retainer. An elastic member that accumulates an elastic force with an input torque, and returns the cage to a neutral state with the accumulated elastic force by releasing the input torque; and
The elastic member is a C-shaped spring member having a circular cross section having a pair of locking portions bent radially inward, and an end surface of a cage that contacts the locking portion has a cross-sectional R shape, the end surface of the retainer part is engaged, the clutch unit, characterized in that projecting from the catching portion saddled the locking portion. 2. The clutch unit according to claim 1 , wherein a protruding dimension of a hook portion protruding from an end face of the cage is 1/6 to 1/3 of an outer diameter of the elastic member. The clutch unit according to claim 1 or 2 , wherein a chamfered portion is formed at a protruding end of a hook portion protruding from an end surface of the cage. 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 3, 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 3 . The clutch unit according to any one of claims 1 to 5 , 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 6 , 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 7 , 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.

Images