JP2012026503A - Clutch unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent the buckling of a leaf spring caused by the flick-out of cylindrical rollers at the release of the lock state of an output shaft, and to suppress the generation of noise caused by vibration at the moment of the flick-out of the cylindrical rollers.SOLUTION: A clutch unit includes a lever-side clutch which is arranged at an input side and controls the transmission and blocking of rotation torque to an output side by a lever operation, and a brake-side clutch 12 which is arranged at an output side, transmits input torque from the lever-side clutch to the output side and blocks reverse input torque from the output side. The brake-side clutch 12 includes an output shaft 22 to which torque is output, a brake-side outer ring 23 whose rotation is constrained, and the cylindrical rollers 27 which are arranged at a wedge clearance 26 between the brake-side outer ring 23a and the output shaft 22, and controls the transmission of the input torque and the block of the reverse input torque by engagement and release between the brake-side outer ring 23 and the output shaft 22. An elastomer member 28 which urges force of separation to the cylinder rollers 27 is interposed between a pair of the cylindrical rollers 27.

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).

  29 is a longitudinal sectional view showing the entire configuration of the conventional clutch unit disclosed in Patent Document 1, FIG. 30 is a sectional view taken along line DD in FIG. 29, and FIG. 31 is taken along line EE in FIG. FIG.

  As shown in FIGS. 29 and 30, 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. 29 and 31, 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 enlarged diameter portion 115c that extends radially outward from the axial end portion of the inner ring 115 and bends in the axial direction functions as a cage that holds the cylindrical rollers 127 at predetermined intervals in the circumferential direction. 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 2009-210114 A

  Incidentally, in the conventional clutch unit disclosed in Patent Document 1, when reverse input torque is input to the output shaft 122 in the brake-side clutch portion 112, the leaf spring 128 applies a separation force to each pair of cylindrical rollers 127. By energizing, the cylindrical roller 127 engages with the wedge clearance 126 between the output shaft 122 and the brake side outer ring 123, and the output shaft 122 is locked to the brake side outer ring 123. On the other hand, the input torque from the lever-side outer ring 114 is input to the inner ring 115 via the lever-side clutch portion 111, and the inner ring 115 comes into contact with the cylindrical roller 127 and presses against the elastic force of the leaf spring 128. The cylindrical roller 127 is detached from the wedge clearance 126, the locked state of the output shaft 122 is released, and the output shaft 122 can be rotated.

  Thus, the output shaft 122 is locked by the elastic force of the leaf spring 128 and the locked state of the output shaft 122 is released against the elastic force of the leaf spring 128. The spring load of the plate spring 128 is limited in the load applied to the cylindrical roller 127 due to its shape, plate thickness, and the like. Therefore, in order to increase the load applied to the cylindrical roller 127, it is necessary to take measures other than the leaf spring 128.

  When the load applied to the cylindrical roller 127 is small and the load applied to the output shaft 122 is large, the cylindrical roller 127 is detached from the wedge clearance 126 and the locked state of the output shaft 122 is released as shown in FIG. As described above, the cylindrical roller in the engaged state (the cylindrical roller 127 on the left side in the figure) pressed against the enlarged diameter portion 115c of the inner ring 115 functioning as a cage moves toward the other cylindrical roller (the cylindrical roller 127 on the right side in the figure). There is a possibility that the leaf spring 128 will buckle due to being blown off. When such a buckling of the leaf spring 128 occurs, the cylindrical roller 127 cannot be returned to the initial position after unlocking. Moreover, there is a concern that the vibration at the moment when the cylindrical roller 127 is blown off is generated as an abnormal noise.

  Therefore, the present invention has been proposed in view of the above-described improvements, and the object of the present invention is to prevent the cylindrical roller from being blown and the leaf spring to buckle when the output shaft is unlocked. An object of the present invention is to provide a clutch unit that can prevent the generation of noise due to vibration at the moment when the cylindrical roller is bounced off.

  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.

  The brake-side clutch portion in the present invention is disposed in an output-side member that outputs torque, a stationary-side member that is restricted in rotation, and a wedge clearance between the stationary-side member and the output-side member. The structure includes a plurality of pairs of engagement elements that control the transmission of input torque and the interruption of the reverse input torque by engaging and disengaging each other, and an elastomer member that biases the separation force between the engagement elements is provided between each pair of engagement elements. It is characterized by having been inserted into. The engaging member of the brake side clutch is preferably a cylindrical roller.

  In the present invention, since the load applied to the engagement element can be easily increased with an elastomer member that is inserted between each pair of engagement elements and biases the separation force between the engagement elements. Even when the applied load is large, when the output side member is released from the locked state, it is possible to prevent the engagement member from being flipped off by the elastomer member, and to prevent the generation of abnormal noise.

  It is desirable that the elastomer member in the present invention has an outer dimension larger than the gap between the pair of engaging elements, and is inserted between the engaging elements in an elastically deformed state. If it does in this way, the elastic restoring force of an elastomer member turns into a separation force to engagement elements, and it becomes easy to urge the separation force to engagement elements.

  The elastomer member according to the present invention preferably has a cylindrical shape or a quadrangular prism shape, and the axial dimension thereof is preferably equal to or smaller than the axial dimension of the engagement element. In this way, the function of the elastomer member can be exhibited with a simple shape, and if the axial dimension of the elastomer member is less than or equal to the axial dimension of the engagement element, the function of the elastomer member is reliably exhibited. It is effective in that it can.

  The elastomer member in the present invention is preferably composed of either a thermosetting elastomer or an elastically deformable resin material. Thus, selecting either a thermosetting elastomer or an elastically deformable resin material is effective in that the elastomer member can be easily manufactured.

  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 Configuration 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 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 load applied to the engagement element can be easily increased with an elastomer member that is inserted between each pair of engagement elements and biases the separation force between the engagement elements. Even when the load applied to the member is large, when the output side member is released from the locked state, it is possible to prevent the engagement member from being flipped off by the elastomer member and to prevent the generation of abnormal noise. As a result, a highly reliable clutch unit can be provided. When this clutch unit is incorporated in an automobile seat lifter, the lever operation for adjusting the seat seat up and down is good, and a comfortable lever operation can be realized.

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 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). It is a perspective view which shows an inner side centering spring. It is a perspective view which shows an outer side centering spring. (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 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). (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. 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 principal part enlarged view of FIG. 5, and is sectional drawing which shows embodiment which applied the cylindrical-shaped elastomer member. FIG. 25 is a cross-sectional view showing a state in which the inner ring presses the cylindrical roller from the state of FIG. 24 and the cylindrical roller is detached from the wedge clearance. It is sectional drawing which shows other embodiment to which the square pillar-shaped elastomer member is applied. 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. 30 is a transverse sectional view taken along the line DD of FIG. 29. FIG. 30 is a transverse sectional view taken along line EE in FIG. 29. FIG. 32 is an enlarged view of the main part of FIG. 31, and is a cross-sectional view showing a state in which the cylindrical roller is bounced off and the leaf spring is buckled when the output shaft is unlocked.

  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 18 are diagrams showing main components of the clutch unit X. FIG. 19 to 23 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. 27 and 28A and 28B) 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).

  As shown in FIGS. 1, 3 and 5, the brake side clutch portion 12 having a reverse input blocking function as a lock type is used as a connecting member to which torque from the lever side clutch portion 11 is input. Inner ring 15, output shaft 22 as an output side member, brake side outer ring 23, cover 24 and brake side side plate 25 as stationary side members restricted in rotation, and wedge between the brake side outer ring 23 and output shaft 22 A plurality of pairs of engagement elements disposed in the clearance 26 and controlling transmission of input torque from the inner ring 15 and interruption of reverse input torque from the output shaft 22 by engagement / disengagement between the brake side outer ring 23 and the output shaft 22. The cylindrical roller 27 and an elastomer member 28 inserted between each pair of cylindrical rollers 27 and energizing the separating force between the cylindrical rollers 27 constitute a main part. 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).

  The elastomer member 28 has an outer diameter larger than the gap between the pair of cylindrical rollers 27, and is inserted between the cylindrical rollers 27 in an elastically deformed state (see FIG. 24). That is, as shown in FIG. 24, the portion of the elastomer member 28 that comes into contact with the cylindrical roller 27 is in a state of being dented by being elastically deformed by the pressing force from the cylindrical roller 27. By doing so, the elastic restoring force of the elastomer member 28 becomes a separating force between the cylindrical rollers 27, and it becomes easy to bias the separating force toward the cylindrical rollers 27.

  The elastomer member 28 has a columnar shape and has an axial dimension that is equal to or smaller than the axial dimension of the cylindrical roller 27. With a simple shape such as this columnar shape, the function of the elastomer member 28, that is, the function of urging the separating force between the cylindrical rollers 27 can be exhibited. Further, if the axial dimension of the elastomer member 28 is set to be equal to or smaller than the axial dimension of the cylindrical roller 27, the elastomer member 28 has a function of biasing the separating force between the cylindrical rollers 27 without interfering with other components. It can be demonstrated reliably.

  The elastomer member 28 is made of either a thermosetting elastomer or an elastically deformable resin material. Thus, the elastomer member 28 can be easily manufactured by selecting either a thermosetting elastomer or an elastically deformable resin material. Further, as shown in FIG. 26, the elastomer member 28 'may have a quadrangular prism shape, and its cross-sectional shape is arbitrary.

  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. Of these claw portions 14f and 14g, one claw portion 14f is inserted and disposed between two locking portions 19a (see FIG. 12) of an outer centering spring 19 to be described later, and the remaining two claw portions 14g. Is a pair of engagements as rotation stoppers provided on the outer periphery of the cover 24 by sliding 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 the brake side outer ring 23 described later. The operation angle of the operation lever is regulated by moving between the stop portions 24e and 24f (see FIG. 16B) and making contact with each of the locking portions 24e and 24f at the moving ends in the rotation direction. I am doing so.

  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. 8A and 8B 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 extending radially outward from the end of the cylindrical portion 15b and bent in the axial direction is integrally formed, and the enlarged diameter portion 15c functions as a cage for the brake side clutch portion 12. Therefore, pockets 15e for accommodating the cylindrical rollers 27 and the elastomer member 28 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.

  9 and 10 (a) to 10 (c) 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. 22).

  FIG. 11 shows the inner centering spring 18. The inner centering spring 18 is composed 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. 22). The inner centering spring 18 is disposed between the cage 17 and a cover 24 that is a stationary side member of the brake side clutch portion 12, and both locking portions 18 a are two end surfaces 17 c of the cage 17 (see FIG. 9 and FIG. 9). 10 (see FIG. 10 (b)) and is latched on the claw portion 24 b (see FIGS. 16 (a) and (b)) provided on the cover 24 (see FIGS. 22 and 23 (a) and (b)). )reference〕.

  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.

  FIG. 12 shows 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. 22). 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. [FIGS. 7A to 7C] and is locked to a claw portion 24d [see FIGS. 16A and 16B] provided on the cover 24 [FIG. 23A]. (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. 22).

  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. 13A and 13B and FIGS. 14A to 14C 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 41 [see FIGS. 27 and 28 (a) and 28 (b)] is coaxially formed at the tip of the shaft 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 an elastomer member 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).

  FIGS. 15A and 15B and FIGS. 16A and 16B show the brake-side outer ring 23 and its cover 24. 17A and 17B show the brake side plate 25. FIG. The brake side outer ring 23 and the cover 24 are caulked and fixed integrally by the brake side plate 25. 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. Reference numerals 24c and 25b in the figure are holes through which the output shaft 22 is inserted, and reference numeral 25c is 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. 19 (a) and 19 (b), 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.

By tightening the claw portions 25a of the brake side plate 25 inserted into the notches 23a and 24a, the brake side outer ring 23 and the cover 24 are connected and integrated with the brake side plate 25 to constitute a stationary member. 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. 21).

  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 [FIGS. 11 and 23]. (See (a) and (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 engaging portions 19a of the outer centering spring 19 of the lever side clutch portion 11 (see FIGS. 12 and 23 (a) and 23 (b)).

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

  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.

  18A to 18C 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 with an allowance to an inner peripheral surface 22e of an annular recess 22b formed in the large-diameter portion 22d of the output shaft 22 (see FIGS. 13A, 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.

  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 portion 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 elastomer member 28 urges the pair of cylindrical rollers 27 so that the cylindrical rollers 27 are braked with the output shaft 22. The output shaft 22 is locked to the brake side outer ring 23 by engaging with the wedge clearance 26 between the side outer rings 23. 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 elastomer member 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.

  As described above, the output shaft 22 is locked by the elastic force of the elastomer member 28 and the locked state of the output shaft 22 is released against the elastic force of the elastomer member 28. In this embodiment, a leaf spring 128 (used in a conventional clutch unit) is provided with an elastomer member 28 inserted between each pair of cylindrical rollers 27 and having a function of biasing the separating force between the cylindrical rollers 27. The load applied to the cylindrical roller 27 can be easily increased as compared with FIG.

  As a result, even when the load applied to the output shaft 22 is large, when the cylindrical roller 27 is detached from the wedge clearance 26 and the locked state of the output shaft 22 is released, as shown in FIG. 128 (see FIG. 32), the cylindrical roller in the engaged state (cylindrical roller 27 on the left side in the figure) pressed against the inner ring 15 by the elastomer member 28 that does not buckle, and the other cylindrical roller (on the right side in the figure). It is possible to reliably return the cylindrical roller 27 to the initial position after unlocking without being blown off to the cylindrical roller 27) side, and to prevent generation of abnormal noise due to vibration at the moment when the cylindrical roller 27 is blown off. it can.

  The clutch unit X having the structure described in detail above is used by being incorporated in, for example, an automobile seat lifter. FIG. 27 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. 28A 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, 13A, 13B, and 14A, 14B.

  In FIG. 28B, 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.

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)
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)
28 Elastomer parts

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 is disposed in an output side member that outputs torque, a stationary side member that is constrained to rotate, and a wedge clearance between the stationary side member and the output side member. A plurality of pairs of engagement elements that control transmission of input torque and interruption of reverse input torque by engagement / disengagement, and an elastomer member that urges a separation force between the engagement elements is interposed between each pair of engagement elements. A clutch unit characterized by that.   2. The clutch unit according to claim 1, wherein the elastomer member has an outer dimension larger than a gap between a pair of engaging elements, and is inserted between the engaging elements in an elastically deformed state.   3. The clutch unit according to claim 1, wherein the elastomer member has a cylindrical shape and an axial dimension thereof is equal to or less than an axial dimension of the engagement element.   The clutch unit according to claim 1 or 2, wherein the elastomer member has a quadrangular prism shape and an axial dimension thereof is equal to or less than an axial dimension of the engagement element.   The clutch unit according to any one of claims 1 to 4, wherein the elastomer member is made of either a thermosetting elastomer or an elastically deformable resin material.   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 5 and a second elastic member.   The clutch unit according to claim 1 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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