JP2017166508A - Clutch device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a structure capable of suppressing bulkiness in an output shaft direction in a clutch device.SOLUTION: Between a third gear part 33d of a pinion gear 33 and an inner peripheral surface 20h of a first housing 20, a friction spring 40 is provided. Also, the friction spring 40 engages to the pinion gear 33 so as to elastically energize the third gear part 33d of the pinion gear 33 from a radial direction, contacts the inner peripheral surface 20h of the first housing 20 so as to elastically energize the inner peripheral surface and slides to the inner peripheral surface 20h of the first housing 20 according to turning of the pinion gear 33.SELECTED DRAWING: Figure 8

Description

  The present invention relates to a clutch device.

  2. Description of the Related Art Conventionally, there is known a clutch device that is disposed in a vehicle seat device or the like and transmits input torque from an input side member to an output side member for output. For example, Patent Document 1 discloses a clutch device disposed in a vehicle seat device. This clutch device is incorporated in an automobile seat lifter or the like that adjusts the seat seat up and down by lever operation, and rotational torque is input to the input side member by lever operation, and the rotational torque from the input side member is transmitted to the output side. The clutch mechanism is configured to cut off the rotational torque from the output side when the input side member returns after the lever operation. Also, a configuration in which a plate-like friction spring is provided between the pinion gear and the housing in the direction orthogonal to the output shaft in order to suppress sudden movement of the output side member and generation of abnormal noise due to contact with other members. It has become. The friction spring is arranged so that the plate surface is orthogonal to the output shaft direction, and when the output side member rotates as the output side member rotates, the frictional spring is slidably contacted with the housing or the like to rotate the output side member. Resistance is generated.

JP 2011-153675 A

  In the clutch device as disclosed in Patent Document 1, a shaft portion extending in the output shaft direction of the pinion gear is inserted through the opening formed in the center of the friction spring so that the friction spring does not move in the output shaft direction. In order to fix, it is necessary to hold by pinching with other members in the output shaft direction. In Patent Document 1, the friction spring is supported from the torque output side by abutting against the flange portion of the pinion gear located on the torque output side, and is formed of a disk-shaped output side cam located on the torque input side. It is configured to be supported from the torque input side by contacting the plate surface. As described above, in the configuration in which the friction spring is held in the housing by being sandwiched between the other members in the output shaft direction, the space in the output shaft direction with respect to the friction spring in the housing is used by the other member. Therefore, the bulkiness of the member in the output shaft direction is unavoidable, leading to an increase in the size of the clutch device.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a configuration that can suppress bulkiness in the output shaft direction in a clutch device.

In order to achieve the above-mentioned object, the invention according to claim 1 described in the claims transmits the input torque from the input member (21) to the output member (33) and outputs it, and also inputs it to the input member. A clutch device (10) for restricting the rotation of the output member when the torque to be output is eliminated, wherein the output member is rotatably accommodated around an output shaft, and the outer peripheral surface of the output member around the output shaft Between the housing (20, 30) in which an inner peripheral surface (20h) opposite to the outer surface is formed, the outer peripheral surface of the output member and the inner peripheral surface of the housing, and centering on the output shaft The output member is engaged with the output member so as to elastically urge the outer peripheral surface of the output member from the radial direction, and abuts against the inner peripheral surface of the housing, and according to the rotation of the output member On the inner peripheral surface of the housing Characterized in that it comprises a and a biasing member (40) that slides in.
In addition, the code | symbol in each said parenthesis shows the correspondence with the specific means as described in embodiment mentioned later.

According to the first aspect of the present invention, the urging member is provided between the outer peripheral surface of the output member and the inner peripheral surface of the housing. The urging member engages with the output member so as to elastically urge the outer peripheral surface of the output member from the radial direction, contacts the inner peripheral surface of the housing, and responds to the rotation of the output member. Sliding against the inner peripheral surface of the housing.
Thus, by providing the biasing member that engages with the output member and slides relative to the housing, resistance is generated in the rotation direction when the output member rotates, and Relative rotation is prevented. Accordingly, the torque transmitted from the input member to the output member can be reduced according to the resistance generated in the rotation direction of the output member, and the sudden movement of the output member or contact with other members during torque transmission It is possible to suppress the generation of abnormal noise. In addition, since the biasing member elastically biases the outer peripheral surface of the output member from the radial direction in the engaged state with the output member, the biasing member is more firmly held in the radial direction. Become. Therefore, movement in the output shaft direction can be restricted without providing a structure for supporting the biasing member from the output shaft direction. Thus, since it is not necessary to provide the support structure of the urging member in the output shaft direction with respect to the urging member, the bulk of the member in the output shaft direction can be suppressed.

In the invention of claim 2, the urging member is configured to abut against the inner peripheral surface of the housing so as to elastically urge.
As a result, the biasing member is further biased toward the outer peripheral surface of the output member with respect to the configuration in which the biasing member elastically biases the outer peripheral surface of the output member from the radial direction. Is more firmly held in the radial direction.

In the invention of claim 3, the urging member outputs from the opposite side to the first engaging portion engaged so as to elastically urge the outer peripheral surface of the output member from one side in the radial direction. And a second engagement portion that engages so as to elastically urge the outer peripheral surface of the member. Further, the urging member is configured such that the urging member is engaged with the output member by sandwiching the output member between the first engaging portion and the second engaging portion.
Accordingly, the output member is elastically moved by a simple assembly process in which the output member is inserted between the first engaging portion and the second engaging portion that are elastically deformed in the direction away from each other and the deformed state is returned. A configuration in which the biasing member is engaged with the output member so as to be biased can be easily realized.

In the invention of claim 4, the housing is configured to pivotally support the output member from the output side of the output shaft. Further, the output member is formed with a flange portion that extends in the radial direction and is supported by the housing from the output side of the output shaft, and the biasing member elastically biases the flange portion from the radial direction. ing.
Thereby, in the output member, a portion (a portion facing the output shaft direction of the flange portion) different from the engagement portion is used while utilizing the portion facing the radial direction of the flange portion as the engagement portion of the biasing member. It can be used as a support portion by a housing. Therefore, compared with the structure which forms the collar part supported from a housing separately from the engaging part of a biasing member, the bulkiness of an output-axis direction can be suppressed further.

In the fifth aspect of the present invention, the urging member is formed with a fitting portion that fits into a fitted portion that is formed to be recessed in the radial direction at the flange portion of the output member.
As a result, the fitting portion and the fitted portion are fitted to each other, so that it is difficult for a backlash to occur in the turning direction between the biasing member and the output member when the output member is turned. Accordingly, the output member can be smoothly rotated.

1 is a side view showing a vehicle seat device to which a clutch device according to the present invention is applied. It is the perspective view which looked at the clutch apparatus from the output side. It is the perspective view which looked at the clutch apparatus from the input side. It is a disassembled perspective view of a clutch apparatus. It is a front view of the friction spring of FIG. It is a partially exploded perspective view of a clutch device. It is a front view of the clutch apparatus of the state which removed the 2nd housing. It is an expanded sectional view which expands and shows the cut surface equivalent to the AA line shown in FIG.

  Hereinafter, an embodiment of a vehicle seat device to which a clutch device according to the present invention is applied will be described with reference to the drawings. FIG. 1 is a side view showing a vehicle seat device to which a clutch device according to the present invention is applied. FIG. 2 is a perspective view of the front side of the clutch device as viewed obliquely from above. FIG. 3 is a perspective view of the rear side of the clutch device as viewed obliquely from above.

  As shown in FIG. 1, a vehicle seat device 100 mainly includes a seat rail 101 that can slide back and forth with respect to a vehicle floor B, and a seat bracket (not shown) on the seat rail 101. A seat cushion 102 to be attached and a seat back 103 supported to be tiltable with respect to the seat cushion 102 are provided. A clutch device 10 (see FIGS. 2 and 3) according to the present invention is disposed on one side of the seat cushion 102, and an operation lever 104 is coupled to the clutch device 10.

  The clutch device 10 transmits a torque input by the operation lever 104 to a known height mechanism (output-side mechanism) provided on the seat bracket via the input-side member 11 and the output-side member 12 and the like. It plays the role of adjusting the height of 102 arbitrarily.

  That is, the clutch device 10 is configured to transmit the rotation of the input side member 11 by the input torque to the output side member 12 and to return only the input side member 11 to the neutral position when the input torque disappears. Therefore, in the clutch device 10, the output side member 12 is fixed so as not to be rotatable so that the height of the seat cushion 102 is maintained at the neutral position N where the operation lever 104 is horizontal.

  In addition, when the operation lever 104 is swung in the upward direction U in order to raise the height of the seat cushion 102, the clutch device 10 causes the input torque corresponding to the swing operation to be applied to the input side member 11 and the output side. It is transmitted to the height mechanism via the member 12. As a result, the height of the seat cushion 102 increases. When the input torque disappears, the output side member 12 maintains its rotation angle, and the input side member 11 returns to the neutral position together with the operation lever 104, so that the height of the raised seat cushion 102 is maintained.

  On the other hand, when the operating lever 104 is swung downward D in order to lower the height of the seat cushion 102, the clutch device 10 causes the input torque corresponding to this swinging operation to be applied to the input side member 11 and the output side. It is transmitted to the height mechanism via the member 12. Thereby, the height of the seat cushion 102 is lowered. When the input torque disappears, the output side member 12 maintains its rotation angle, and the input side member 11 returns to the neutral position together with the operation lever 104, so that the height of the lowered seat cushion 102 is maintained.

  Next, the configuration of the clutch device 10 will be described with reference to the drawings. FIG. 4 is an exploded perspective view of the clutch device. FIG. 5 is a front view of the friction spring of FIG.

  As shown in FIGS. 2 to 4, the clutch device 10 includes a first housing 20, a lever member 21, a first spring 22, a second spring 23, a washer 24, a connection plate 25, a first cam 26, a resin plate 27, An input side member 11 having eight first rollers 28 and a retainer 29; an output side member 12 having a second housing 30, 14 second rollers 31, a second cam 32, a pinion gear 33, and a friction spring 40; , And the input side member 11 and the output side member 12 are arranged coaxially via the rotation transmission member 50.

First, each part which comprises the input side member 11 is demonstrated.
The first housing 20 is integrally formed with a bottomed cylindrical main body portion 20a and a flange portion 20b that extends annularly from the open end of the main body portion 20a in the outer circumferential direction. A through hole 20c is formed at the center of the bottom of the main body 20a, and a first opening 20d, a pair of second openings 20e, and a third opening 20f are formed around the through hole 20c. . A pair of protruding pieces 20g are formed on the outer peripheral side of the opening edge of the first opening 20d so as to protrude to one side in the axial direction (left side in FIG. 4).

  The lever member 21 is connected to the operation lever 104 and plays a role of transmitting input torque generated by a swing operation of the operation lever 104 to the first cam 26 and the like. The lever member 21 is formed so that the central portion of the substantially circular plate protrudes to the other side in the axial direction (the right side in FIG. 4). Three engagement holes 21 a that engage with the first cam 26 are formed in the central portion. Further, a part of the outer edge of the lever member is formed with a protruding piece 21b that extends outward and contacts the protruding piece 20g of the first housing 20 and the first spring 22, and the outer edge of the protruding piece 21b is , Bent toward the other side of the axis. The lever member 21 corresponds to an example of the “input member” in the present invention.

  The first spring 22 is formed by bending a flat plate-like elastic member and functions to bias the lever member 21 to the neutral position with respect to the first housing 20. The first spring 22 includes a substantially C-shaped spring body 22a, hook portions 22b that are bent outward from both ends of the spring body 22a, and protrusions that protrude from the vicinity of both hook portions 22b to one side in the axial direction. Part 22c. The protrusion 22 c is in contact with a guide surface 21 c that is a part of the outer edge of the lever member 21.

  The second spring 23 is formed by bending a flat plate-like elastic member, and functions to urge the connecting plate 25 and the retainer 29 to the neutral position with respect to the first housing 20. The second spring 23 includes a substantially C-shaped spring body 23a and hook portions 23b that are bent inward from both ends of the spring body 23a.

  In the washer 24, a through hole 24a is formed at the center through which one end 33a of the pinion gear 33 in the axial direction is inserted, and in the vicinity of the through hole 24a, three engagement holes 24b to be engaged with the first cam 26 are formed. Has been.

  The connecting plate 25 includes an engaging portion 25a that protrudes in a U shape in the radial direction, two extending pieces 25b that extend from the vicinity of the engaging portion 25a to one side in the axial direction, and an engaging portion 25a. On the opposite side, an engaging portion 25c is formed that protrudes in a U shape in the radial direction. The engaging portion 25a and the engaging portion 25c are engaged with the retainer 29, and the extending piece 25b is engaged with both the hook portions 23b of the second spring 23 so as to be pressed from both sides. It functions to transmit the urging force from the two springs 23 to the retainer 29.

  The first cam 26 is formed in a substantially disk shape with a large plate thickness, and an engagement hole 26a that can be coaxially engaged with the first gear portion 33b of the pinion gear 33 is formed at the center thereof. . Further, in the vicinity of the engagement hole 26a, a protruding portion 26b that protrudes to one side in the axial direction and engages with the engagement hole 21a of the lever member 21 and the engagement hole 24b of the washer 24 is formed. Further, the outer peripheral surface of the first cam 26 constitutes a cam surface 26c, and this cam surface 26c has a pair of opposing wedge-shaped spaces with the inner peripheral surface of the cylindrical portion 50a of the rotation transmitting member 50. It is formed so that eight places are provided.

  The resin plate 27 is formed in a substantially annular shape, and is press-fitted and fixed to the bottom of the main body 20 a of the first housing 20. Further, an engaging portion 27 a for engaging and fixing the rotation transmitting member 50 is formed on the inner peripheral edge of the resin plate 27.

  Each first roller 28 is formed in a cylindrical shape, and the diameter thereof is within a pair of opposing wedge-shaped spaces formed by the cam surface 26 c and the inner peripheral surface of the cylindrical portion 50 a of the rotation transmitting member 50. Thus, it is arranged to have play for enabling forward and reverse rotation.

  The retainer 29 is formed in a substantially disc shape, and an opening hole 29a is provided at the center thereof. Further, the retainer 29 is formed with a protruding portion 29b that protrudes to one side in the axial direction, and this protruding portion 29b engages with the engaging portion 25a and the engaging portion 25c of the connecting plate 25. Further, eight openings 29c are formed in the retainer 29, and the openings 29c are formed so that the first roller 28 can be pressed by the opening side surface.

Next, each part which comprises the output side member 12 is demonstrated.
Each of the second rollers 31 is formed in a cylindrical shape, and the diameter thereof is a pair of opposing wedges formed by the cam surface 32d of the second cam 32 and the inner peripheral surface of the main body portion 20a of the first housing 20. It arrange | positions so that it may have a play for enabling forward / reverse rotation in the shape space. As shown in FIG. 8, each second roller 31 is disposed so as to be in frictional contact with a portion of the inner peripheral surface 20h of the main body portion 20a that is close to the flange portion 20b.

  The second cam 32 has a bottomed cylindrical main body portion 32a, an engagement hole 32b for engaging with the second gear portion 33c of the pinion gear 33 at the center of the bottom surface of the main body portion 32a, An engagement hole 32c for coaxially engaging with the rotation transmitting member 50 is formed in the periphery of the joint hole 32b. The outer peripheral surface of the second cam 32 constitutes a cam surface 32d, and the cam surface 32d is provided with a pair of opposing wedge-shaped spaces between the inner peripheral surface of the main body portion 20a of the first housing 20 and 14 locations. It is formed to be.

  The pinion gear 33 is formed such that its one axial end 33a can be inserted through the through hole 24a of the washer 24 and the like. Further, the pinion gear 33 has a first gear portion 33b that can be engaged with the engagement hole 26a of the first cam 26 and a second engagement hole 32b of the second cam 32 at an intermediate portion in the axial direction. A second gear portion 33c and a third gear portion 33d that can be engaged with the opening 41a of the friction spring 40 are formed. The third gear portion 33d corresponds to an example of the “ridge portion” of the present invention, extends in the radial direction, and is supported by the first housing 20 from the torque output side in the output axis L direction. Further, the other axial end 33e is formed so as to be able to mesh with an input shaft (not shown) of the height mechanism.

  The friction spring 40 corresponds to an example of the “biasing member” of the present invention, and engages with the pinion gear 33 and slides with respect to the first housing 20 to rotate the pinion gear 33 when the pinion gear 33 rotates. Function to cause resistance. The friction spring 40 is formed by, for example, punching a steel material, and as shown in FIGS. 6 and 7, a substantially annular central portion 41 that engages with the third gear portion 33d of the pinion gear 33, The four support portions 42 are in contact with the inner peripheral surface 20 h of the first housing 20. Each support portion 42 has a shape extending along a predetermined position on the outer edge of the central portion 41 and a position facing the predetermined position along the outer edge.

  The central portion 41 includes a first engagement portion 43 that engages with the third gear portion 33d from one side in the radial direction (hereinafter, also simply referred to as radial direction) centered on the output axis L, and the other radial side. And a second engaging portion 44 that engages with the third gear portion 33d. The first engaging portion 43 includes a protruding portion 45 protruding in a substantially U shape radially outward, a pair of connecting portions 46 extending from both ends of the protruding portion 45, and a protruding portion 45 in the connecting portion 46. And a pair of connecting portions 47 connected to the second engaging portion 44 at the end opposite to the connecting portion. The connecting portion 46 is formed in a curved shape, and projecting pieces 46 a and 46 b projecting toward the center of the central portion 41 are formed in the vicinity of both end portions. The protruding piece 46a is formed in a substantially trapezoidal plate shape, and the protruding piece 46b is formed in a rounded protruding shape. Further, the connecting portion 47 has a curved shape so as to protrude outward from the connecting portion 46.

  Each support portion 42 extends along the circumferential direction centering on the output axis L from the connection portion between the first engagement portion 43 and the second engagement portion 44 in order to mitigate and absorb the impact transmitted from the first housing 20. The shape extends about a quarter of a circle, and the distance from the central portion 41 to the portion of the first housing 20 that contacts the inner peripheral surface 20h of the main body portion 20a is increased. Further, each support portion 42 is formed so as to avoid a portion of the inner peripheral surface 20 h of the main body portion 20 a in the first housing 20 where the second rollers 31 make frictional contact. A through hole 42 a is formed at the tip of each support portion 42.

  Similar to the first engaging portion 43, the second engaging portion 44 includes a protruding portion 45, a pair of connecting portions 46, and a pair of connecting portions 47. As a result, the friction spring 40 has a symmetric shape with respect to a straight line passing through the connecting portions of the first engaging portion 43 and the second engaging portion 44.

  The rotation transmitting member 50 includes a cylindrical portion 50a, seven pressing pieces 50b, and seven engaging protrusions 50c. The inner peripheral surface of the cylindrical portion 50 a faces the cam surface 26 c of the first cam 26. Each pressing piece 50b is a cylinder that can press the corresponding second roller 31 with a side surface in a pair of opposing wedge-shaped spaces formed by the cam surface 3dd and the inner peripheral surface of the main body portion 20a of the first housing 20. Each is formed so as to protrude from the other end of the portion 50a to the other side in the axial direction. Further, the engagement protrusion 50 c is coaxially engaged with the engagement hole 32 c of the second cam 32.

  The second housing 30 is configured by a plate portion 30a having an outer shape similar to the outer shape of the flange portion 20b of the first housing 20, and closes the opening portion of the main body portion 20a of the first housing 20 from the other side in the axial direction. The first housing 20 is assembled by fastening with bolts or the like. A through hole 30b is formed in the center of the plate portion 30a, and the other end 33e in the axial direction of the pinion gear 33 accommodated in the first housing 20 is coaxial with the first housing 20 from the through hole 30b. It is designed to protrude. The first housing 20 and the second housing 30 correspond to an example of the “housing” of the present invention, and accommodate the output member so as to be rotatable around the output shaft.

Next, the assembly process of the friction spring 40 to the pinion gear 33 and the first housing 20 will be specifically described. FIG. 7 is a front view of the clutch device 10 with the second housing 30 removed.
The friction spring 40 inserts the pinion gear 33 between the first engagement portion 43 and the second engagement portion 44 (opening portion 41a) in a state of being elastically deformed in a direction away from each other, and returns the deformation state of these portions. Thus, the pinion gear 33 can be engaged. As a result, the friction spring 40 is engaged with the pinion gear 33 so as to sandwich the third gear portion 33d by the first engagement portion 43 and the second engagement portion 44, as shown in FIG. Specifically, the first engaging portion 43 abuts on the third gear portion 33d so as to elastically bias the third gear portion 33d from one radial side (left side in FIG. 7), and the second The engaging portion 44 comes into contact with the third gear portion 33d so as to elastically bias the third gear portion 33d from the side opposite to the one side in the radial direction (the right side in FIG. 7). Further, the protruding pieces 46a and 46b are fitted into fitted portions 33f (inter-tooth portions of the third gear portion 33d) that are recessed in the radial direction of the pinion gear 33, respectively. The protruding pieces 46a and 46b correspond to an example of the “fitting portion” in the present invention. Further, the friction spring 40 is positioned in a space surrounded by the inner peripheral surface 20h of the first housing 20 in a state where each support portion 42 is elastically deformed in a direction toward the output axis L (a direction toward the center of the opening 41a). Then, it can be assembled to the first housing 20 by returning the deformation state of each support portion 42. As a result, the friction spring 40 abuts against the inner peripheral surface 20h of the first housing 20 so as to elastically urge it, as shown in FIGS.

  The step of engaging the central portion 41 of the friction spring 40 with the pinion gear 33 and the step of bringing each support portion 42 into contact with the first housing 20 can be performed simultaneously. First, in a state where the input side member 11, the rotation transmission member 50, each second roller 31, the second cam 32, and the pinion gear 33 are assembled to the first housing 20, the first engaging portion 43 and the second engaging portion 44. Are elastically deformed in directions away from each other, and each support portion 42 is elastically deformed in a direction toward the output axis L (direction toward the center of the opening 41a). Specifically, a force is applied toward the outside at the U-shaped inner portion of each of the protrusions 46a and 46b, and a force is applied toward the other support portion 42 adjacent in the through hole 42a of each support portion 42. Thus, the friction spring 40 is elastically deformed. Next, while the pinion gear 33 is inserted between the first engagement portion 43 and the second engagement portion 44 (opening 41a), the space surrounded by the inner peripheral surface 20h of the first housing 20 (more specifically, The friction spring 40 is positioned at a position overlapping the third gear portion 33d in the output axis L direction. Next, by returning the deformation state of the first engaging portion 43, the second engaging portion 44, and each support portion 42, the friction spring 40 is engaged with the pinion gear 33 as shown in FIGS. Can be assembled in the first housing 20. Thus, the friction spring 40 can be engaged with the pinion gear 33 in one step, and workability can be improved.

  As described above, the friction spring 40 is configured to elastically urge the third gear portion 33d of the pinion gear 33 from the radial direction in an engaged state with the pinion gear 33, and thus is further attached to the first housing 20. By assembling so as to urge, it is held more firmly in the radial direction. Therefore, the movement in the output axis L direction can be restricted without providing a structure for supporting the friction spring 40 from the output axis L direction. In other words, the friction spring 40 needs to be supported from the torque input side by the second cam 32, or to be supported from the torque output side by the flange portion (for example, the third gear portion 33d) provided on the pinion gear 33. There is no.

  As in the prior art, in a configuration in which a support structure for the friction spring 40 from the direction of the output axis L (for example, a structure that is supported by being sandwiched between the second cam 32 and the second housing 30) is provided, the first housing 20 of the pinion gear 33 is provided. The second cam 32 is pressed through the friction spring 40 when assembled to the head. Then, a member such as the second cam 32 may be pressed to cause deformation or the like, causing a problem that rattling occurs between the pinion gear 33 and the second cam 32. However, as in the first embodiment, the friction spring 40 is engaged with the pinion gear 33 so as to elastically bias the pinion gear 33 from the radial direction, so that the pinion gear is pressed against the friction spring 40. 33 does not need to be assembled, and such a problem does not occur.

Next, the operation of the input side member 11 and the output side member 12 in the clutch device 10 configured as described above will be described below.
When the operation lever 104 is swung upward from the neutral position N in the upward direction U, the lever member 21 rotates clockwise as viewed from the input side. In response to this rotation, the first cam 26 rotates clockwise. Further, the connecting plate 25 swings in accordance with the rotation of the lever member 21, so that the retainer 29 engaged with the connecting plate 25 rotates.

  Due to the rotation of the retainer 29 as described above, the side surface of the opening 29 c causes the first roller 28 to form the cam surface 26 c forming a wedge-shaped space on the counterclockwise direction and the inner peripheral surface of the main body portion 32 a of the second cam 32. Since the first cam 26 is pressed, the first cam 26 rotates integrally with the rotation transmitting member 50 via the first rollers 28. Therefore, the input torque is transmitted to the output side member 12 through the lever member 21, the first cam 26, the first rollers 28, and the rotation transmission member 50.

  By the rotation of the rotation transmitting member 50 as described above, the second roller 31 is pressed in the rotation direction by a part of the pressing pieces 50b and is detached from the wedge-shaped space. Thereby, the restriction | limiting of the relative rotation of the 2nd cam 32 with respect to the 1st housing 20 is cancelled | released.

  Then, the second cam 32 is rotated by being pressed by the remaining pressing piece 50b, and the pinion gear 33 engaged with the second cam 32 is rotated. Thereby, the input torque input from the input side member 11 is transmitted to the height mechanism via the pinion gear 33 of the output side member 12 or the like. At this time, since the friction spring 40 slides with respect to the inner peripheral surface 20h of the first housing 20 in accordance with the rotation of the pinion gear 33, resistance occurs in the rotation direction when the pinion gear 33 rotates. Thus, the relative rotation of the pinion gear 33 with respect to the first housing 20 is prevented. Further, since the protruding pieces 46a and 46b of the friction spring 40 are fitted in the fitted portion 33f of the pinion gear 33 (inter-tooth portion of the third gear portion 33d), the friction spring 40 and the pinion gear are rotated when the pinion gear 33 is rotated. It is difficult for rattling to occur in the direction of rotation with 33.

  When the input torque is lost, the lever member 21 and the connecting plate 25 are urged by the first spring 22 and the second spring 23, respectively, so that the lever member 21 and the first cam 26 rotate counterclockwise. Then, the connecting plate 25 swings in the neutral direction and the retainer 29 rotates to return to the neutral position. When the first cam 26 and the retainer 29 rotate in this way, each first roller 28 is not pressed into the wedge-shaped space, so that the rotation of the first cam 26 is not transmitted to the rotation transmitting member 50. . Even when the lever member 21 rotates counterclockwise according to the input torque, the input torque is similarly transmitted to the output side member 12.

  As described above, in the clutch device 10 according to the first embodiment, friction is generated between the outer peripheral surface of the pinion gear 33 (more specifically, the third gear portion 33d) and the inner peripheral surface 20h of the first housing 20. A spring 40 is provided. The friction spring 40 engages with the pinion gear 33 so as to elastically urge the outer peripheral surface of the pinion gear 33 from the radial direction, and abuts against the inner peripheral surface 20 h of the first housing 20. It slides with respect to the inner peripheral surface 20h of the first housing 20 according to the rotation.

  As described above, by providing the friction spring 40 that engages with the pinion gear 33 and slides with respect to the first housing 20, resistance is generated in the rotation direction when the pinion gear 33 rotates. The relative rotation of the pinion gear 33 with respect to the housing 20 is prevented. Thereby, the torque transmitted from the input side member 11 to the pinion gear 33 can be reduced according to the resistance generated in the rotation direction of the pinion gear 33, and the sudden operation of the pinion gear 33 at the time of torque transmission and other members can be reduced. It is possible to suppress the generation of abnormal noise due to contact. In addition, since the friction spring 40 elastically biases the third gear portion 33d from the radial direction in the engaged state with the pinion gear 33, the friction spring 40 is held more firmly in the radial direction. Become. Therefore, the movement in the output axis L direction can be restricted without providing a structure for supporting the friction spring 40 from the output axis L direction. Thus, since it is not necessary to provide a support structure for the friction spring 40 in the direction of the output axis L with respect to the friction spring 40, the bulk of the member in the direction of the output axis L can be suppressed.

Further, the friction spring 40 is configured to abut against the inner peripheral surface 20 h of the housing 20 so as to elastically urge it.
As a result, the friction spring 40 is biased to the third gear portion 33d of the pinion gear 33 in contrast to the configuration in which the friction spring 40 elastically biases the third gear portion 33d of the pinion gear 33 from the radial direction. Therefore, the friction spring 40 is held more firmly in the radial direction.

Further, the friction spring 40 includes a first engagement portion 43 that abuts so as to elastically urge the third gear portion 33d of the pinion gear 33 from one side in the radial direction, and a third gear from the opposite side to the one side. A second engagement portion 44 that abuts the portion 33d so as to elastically bias the portion 33d. Further, the friction spring 40 is configured such that the friction spring 40 engages with the pinion gear 33 by sandwiching the pinion gear 33 between the first engagement portion 43 and the second engagement portion 44.
As a result, the pinion gear 33 is elastically moved by a simple assembly process in which the pinion gear 33 is inserted between the first engaging portion 43 and the second engaging portion 44 that are elastically deformed in the direction away from each other and the deformed state is returned. Therefore, it is possible to easily realize a configuration in which the friction spring 40 is engaged with the pinion gear 33 so as to be biased.

The first housing 20 is configured to pivotally support the pinion gear 33 from the output side of the output axis L. The pinion gear 33 is formed with a third gear portion 33d that extends in the radial direction and is supported by the first housing 20 from the output side of the output axis L. The friction spring 40 has a third gear portion 33d from the radial direction. Is urged elastically.
Thus, in the pinion gear 33, the portion facing the radial direction of the third gear portion 33d is used as the engaging portion of the friction spring 40, and a portion different from the engaging portion (the output axis L of the third gear portion 33d). The portion facing the direction) can be used as a support portion by the housing. Therefore, the bulk in the direction of the output axis L can be further suppressed as compared with a configuration in which a hook-shaped portion supported from the first housing 20 is formed separately from the engaging portion of the friction spring 40.

  Further, the friction spring 40 is formed with projecting pieces 46a and 46b that fit into the fitted portion 33f of the pinion gear 33 (inter-tooth portion of the third gear portion 33d). As a result, the protrusions 46a and 46b of the friction spring 40 are fitted into the fitted portion 33f of the pinion gear 33, so that when the pinion gear 33 is rotated, there is a backlash in the rotation direction between the friction spring 40 and the pinion gear 33. Therefore, the pinion gear 33 can be smoothly rotated according to the rotation of the pinion gear 33.

In addition, this invention is not limited to the said 1st Embodiment, You may actualize as follows, and even in that case, the effect | action and effect equivalent to the said 1st Embodiment are acquired.
(1) The friction spring 40 is not limited to a configuration in which the friction spring 40 is elastically urged against the inner peripheral surface 20h of the housing 20, but is configured to be in contact with the inner peripheral surface 20h of the housing 20. May be.
(2) The friction spring 40 is not limited to a configuration that engages with the pinion gear 33, and may be a configuration that engages with the second cam 32. For example, a gear portion having the same configuration as that of the third gear portion 33d is formed on the torque output side of the second cam 32, and the friction spring 40 is engaged with the gear portion so as to elastically bias the gear portion from the radial direction. It may be.
(3) The configuration is not limited to the configuration in which the pinion gear 33 and the second cam 32 are separate members, and the pinion gear 33 and the second cam 32 may be integrally formed.
(4) Each support portion 42 of the friction spring 40 is not limited to a configuration extending from the central portion 41, and may be formed integrally in a ring shape and elastically deformable inward.
(5) Each first roller 28 is not limited to being formed in a cylindrical shape, and may be formed in a shape capable of frictional contact with the wedge-shaped space. Further, the shape of each second roller 31 can be similarly changed.
(6) The number of the first rollers 28 is not limited to eight, and nine or more may be provided, or seven or less may be provided. In this case, the cam surface 26c of the first cam 26, the inner peripheral surface of the cylindrical portion 50a of the rotation transmitting member 50, and the like are formed according to the number of the changed first rollers 28. Further, the number of the second rollers 31 can be similarly changed.
(7) The first housing 20 is not limited to being configured by integrally forming the main body 20a and the flange 20b, but is provided with another member that extends annularly from the outer peripheral surface to the outer peripheral direction with respect to the main body 20a. It may be configured to be fixed as a flange portion.
(8) The clutch device 10 according to the present invention is not limited to the vehicle seat device 100 described above, but is applied to a seat position adjusting device for adjusting the position including the height of other seats. May be.

DESCRIPTION OF SYMBOLS 10 ... Clutch apparatus 11 ... Input side member 12 ... Output side member 20 ... 1st housing (housing)
20h ... inner peripheral surface 21 ... lever member (input member)
30 ... Second housing (housing)
33 ... Pinion gear (output member)
33d ... 3rd gear part (buttock part)
33f ... mated portion 40 ... friction spring (biasing member)
43 ... 1st engaging part 44 ... 2nd engaging part 46a, 46b ... Projection piece (fitting part)
100 ... Vehicle seat device

Claims (5)

A clutch device that transmits an input torque from an input member to an output member and outputs the torque, and restricts the rotation of the output member when there is no torque input to the input member,
A housing in which the output member is rotatably accommodated around an output shaft, and an inner peripheral surface facing the outer peripheral surface of the output member around the output shaft is formed;
The output is provided between the outer peripheral surface of the output member and the inner peripheral surface of the housing, and elastically biases the outer peripheral surface of the output member from a radial direction around the output shaft. A biasing member that engages with a member, abuts against the inner peripheral surface of the housing, and slides against the inner peripheral surface of the housing in response to rotation of the output member;
A clutch device comprising:   The clutch device according to claim 1, wherein the urging member abuts on the inner peripheral surface of the housing so as to elastically urge the urging member. The biasing member is
A first engagement portion engaged so as to elastically bias the outer peripheral surface of the output member from one side in the radial direction;
A second engaging portion engaged so as to elastically urge the outer peripheral surface of the output member from a side opposite to the one side;
With
3. The clutch according to claim 1, wherein the urging member is engaged with the output member by sandwiching the output member between the first engaging portion and the second engaging portion. 4. apparatus. The housing is configured to pivotally support the output member from the output side of the output shaft,
The output member is formed with a flange extending in the radial direction and supported by the housing from the output side of the output shaft,
4. The clutch according to claim 1, wherein the urging member is engaged with the output member so as to elastically urge the flange portion from the radial direction. 5. apparatus.   The fitting portion that fits into the fitting portion that is formed to be recessed in the radial direction in the flange portion of the output member is formed in the biasing member. The clutch device as described.

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