JP2022089238A - Brake device - Google Patents

Abstract

To provide a brake device which is constructed to suppress its operation play without increasing its operational ability.SOLUTION: A turn transmission member 40 is provided which is turned with the turn of an input member 20 to depart a second roller 33 from a wedge-shaped space against energizing force by a second spring 34 and turn a second cam 32 connected to a pinion gear 35. The turn transmission member 40 is formed with a through-hole 42a through which a columnar part 35b of the pinion gear 35 passes. Between the through-hole 42a and the columnar part 35b, a bush 50 is provided for friction-contacting both the inner peripheral face of the through-hole 42a and the outer peripheral face of the columnar part 35b.SELECTED DRAWING: Figure 15

Description

The present invention relates to a braking device for a vehicle seat.

Conventionally, as a technique related to a brake device which is arranged on a vehicle seat and controls a torque transmitted from an input member to an output member in posture adjustment of the vehicle seat or the like, for example, a clutch device disclosed in Patent Document 1 below is known. Has been done. This clutch device transmits the input torque input from the lever member in response to the operation of the operating lever to the pinion gear via the rotation transmission member and outputs the clutch device, and when the input torque is exhausted, the clutch device regulates the rotation of the pinion gear. It is configured as. More specifically, the rotation of the pinion gear is caused by the roller pressed by the spring entering the wedge-shaped space formed between the cam surface of the output side cam assembled to the pinion gear and the inner peripheral surface of the housing. Be regulated. From such a restricted state, the rotation transmission member rotates against the urging of the spring in response to the operation of the operation lever, and the roller pressed by the pressing piece of the rotation transmission member opposes the spring. The restriction is released by separating from the wedge-shaped space, and the pinion gear rotates by rotating the output side cam pressed from the rotation transmission member in this restriction release state.

Japanese Unexamined Patent Publication No. 2011-153675 Japanese Unexamined Patent Publication No. 2018-141478

By the way, in the configuration as described above, as shown in FIG. 17, in order to secure strength and the like, in a neutral state where there is no input torque, a wedge shape is formed by the pressing piece 201 and the spring 202 of the rotation transmission member urged by the spring. A gap G is provided between the roller 203 and the roller 203 that are urged to enter the space. In FIG. 17, the cam surface of the output side cam is illustrated by reference numeral 204, and the inner peripheral surface of the housing is illustrated by reference numeral 205.

Such a gap causes play (hereinafter, also referred to as actuation play) from the start of rotation of the rotation transmission member to the contact with the roller by the pressing piece, and the operability is poor due to this actuation play. There is a problem of becoming.

As a technique for suppressing such operation play, for example, a clutch device disclosed in Patent Document 2 is known. In this clutch device, the resin plate engaged and fixed to the rotation transmission member is press-fitted and fixed to the inner peripheral surface of the housing. With such a configuration, even if the input torque disappears after the roller is separated from the wedge-shaped space by the pressing piece of the rotation transmission member that rotates according to the input torque, the frictional force between the resin plate and the housing is lost. This makes it difficult for the rotation transmission member to rotate. As a result, the contact state between the pressing piece and the roller at the time of pressing is maintained even after the input torque is lost, so that the operation play can be suppressed.

However, in the configuration that suppresses the operation play by utilizing the friction between the resin plate and the housing as described above, the frictional force always acts when the rotation transmission member is rotated, that is, when the operation lever is operated. There is a problem that the required operating force increases.

The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a configuration capable of suppressing operation play without increasing an operating force.

In order to achieve the above object, the invention of claim 1 described in the claims is
The input torque is transmitted from the input member (20) to the output member (30) via the rotation transmission member (40) and output, and when the torque input to the input member is exhausted, the output member is rotated. A brake device (10) for vehicle seats that regulates movement.
The output member is
Output shaft (35) and
A brake cam (32) coaxially connected to the output shaft to form a plurality of cam surfaces (32a) on the outer peripheral surface.
A ring (31) arranged so that a pair of wedge-shaped spaces are formed for each cam surface by the inner peripheral surface (31a) and the plurality of cam surfaces facing the inner peripheral surface.
A brake roller (33) for restricting the relative rotation between the ring and the brake cam by entering the wedge-shaped space, and
An urging member (34) that urges the brake roller toward the wedge-shaped space, and
Equipped with
By rotating the rotation transmission member in response to the rotation of the input member, the brake roller is separated from the wedge-shaped space against the urging force of the urging member, and the brake cam is moved. Formed to rotate,
A through hole (42a) through which the cylindrical portion (35b) of the output shaft penetrates is formed in the rotation transmission member.
A bush (50) is provided between the through hole and the columnar portion so as to be in frictional contact with both the inner peripheral surface of the through hole and the outer peripheral surface of the columnar portion.
The reference numerals in the parentheses indicate the correspondence with the specific means described in the embodiments described later.

In the invention of claim 1, by rotating according to the rotation of the input member, the brake roller is separated from the wedge-shaped space against the urging force by the urging member, and the brake cam is connected to the output shaft. A rotation transmission member for rotating the is provided. A through hole through which the cylindrical portion of the output shaft penetrates is formed in the rotation transmission member, and a bush that frictionally contacts the inner peripheral surface of the through hole and the outer peripheral surface of the cylindrical portion between the through hole and the cylindrical portion. Is provided.

As a result, even if the input torque disappears after the brake roller is separated from the wedge-shaped space by the rotation transmission member that rotates according to the input torque, the rotation transmission member frictionally contacts the bush through the through hole. Therefore, since the frictional force acts so as to maintain the contact state between the rotation transmission member and the brake roller, the operation play can be suppressed. When the rotation transmission member rotates while the brake roller is separated from the wedge-shaped space, the output shaft rotates integrally with the rotation transmission member, so that the output shaft and the rotation transmission member Since friction does not occur in the bushes interposed between them, the operating force does not increase. Therefore, it is possible to realize a configuration in which operation play can be suppressed without increasing the operating force.

It is a side view which shows the vehicle seat device to which the brake device which concerns on this invention is applied. It is a perspective view which looked at the brake device from the input side. It is a perspective view which looked at the brake device from the output side. It is a front view of the brake device. It is a side view which looked at the brake device from the input side. It is a side view which looked at the brake device from the output side. It is an exploded perspective view of a brake device. FIG. 5 is an enlarged cross-sectional view showing an enlarged cross section of X1-X1 shown in FIG. FIG. 5 is an enlarged cross-sectional view showing an enlarged cross section of X2-X2 shown in FIG. FIG. 3 is an enlarged cross-sectional view showing an enlarged cross section of X3-X3 shown in FIG. FIG. 5 is an enlarged cross-sectional view showing an enlarged cross section of X4-X4 shown in FIG. 12 (A) is a view of the second cam as viewed from the input side, and FIG. 12 (B) is a side view of FIG. 12 (A). 13 (A) is a view of the rotation transmission member as viewed from the input side, and FIG. 13 (B) is a side view of FIG. 13 (A). It is a perspective view which shows the bush enlarged. FIG. 15A is an explanatory diagram illustrating a state in which the contact state between the regulating portion of the rotation transmission member and the second roller is maintained, and FIG. 15B is the state shown in FIG. 15A. Is an explanatory diagram illustrating a state in which the contact state between the different second roller and the regulating portion is maintained. It is a graph which shows the change of the operation torque in the brake device which concerns on this embodiment, and the change of the operation torque in the conventional structure which has operation play with respect to the operation angle of the operation lever. It is explanatory drawing explaining the operation play in a conventional structure.

Hereinafter, an embodiment of a vehicle seat device to which the vehicle seat brake device according to the present invention is applied will be described with reference to the drawings.
As shown in FIG. 1, the vehicle seat device 100 mainly includes a seat rail 101 slidable back and forth with respect to the vehicle floor B, and a seat bracket (not shown) on the seat rail 101. It includes a seat cushion 102 to be attached and a seat back 103 that is tiltably supported with respect to the seat cushion 102. A brake device (clutch device) 10 for a vehicle seat according to the present invention is disposed on one side of the seat cushion 102, and an operation lever 104 is connected to the brake device 10.

The brake device 10 transmits the input torque by the operation lever 104 to the known height mechanism (output side mechanism) provided on the seat bracket via the input member, the output member, and the like, thereby increasing the height of the seat cushion 102. Plays the role of arbitrarily adjusting.

That is, the brake device 10 transmits and outputs the torque input from the input member to the output member in response to the operation of the operation lever 104, and the rotation of the output member is restricted when the torque input to the input member is exhausted. Only the input member is configured to return to the neutral position side. Therefore, in the brake device 10, the output member is non-rotatably fixed so as to maintain the height of the seat cushion 102 at the neutral position N where the operation lever 104 is horizontal.

Further, in the brake device 10, when the operation lever 104 is oscillated upward in order to raise the height of the seat cushion 102, the input torque corresponding to the oscillating operation is transmitted through the input member and the output member. Is transmitted to the height mechanism. As a result, the height of the seat cushion 102 increases. When the input torque disappears, the output member maintains its rotation angle, and the input member returns to the neutral position side together with the operation lever 104, so that the height of the raised seat cushion 102 is maintained.

On the other hand, in the brake device 10, when the operation lever 104 is oscillated downward D in order to lower the height of the seat cushion 102, the input torque corresponding to the oscillating operation is transmitted through the input member and the output member. Is transmitted to the height mechanism. As a result, the height of the seat cushion 102 is lowered. When the input torque disappears, the output member maintains its rotation angle, and the input member returns to the neutral position side together with the operation lever 104, so that the height of the lowered seat cushion 102 is maintained.

Next, the configuration of the brake device 10 will be described with reference to the drawings.
As shown in FIGS. 2 to 11, the brake device 10 includes a lever member 21, a cover 22, a wave washer 23, a first cam 24, six first rollers 25, three first springs 26, and two washers. An input member 20 having 27 and 28, an output member 30 having a ring 31, a second cam 32, 10 second rollers 33, 5 second springs 34, a pinion gear 35, and a friction spring 36, and rotation transmission. The member 40, the bush 50, and the bracket 60 are provided, and the input member 20 and the output member 30 are arranged coaxially via the rotation transmission member 40.

First, each component constituting the input member 20 will be described.
The lever member 21 is fastened to the operating lever 104 by using three tapping screws 110 that function as fastening members, and serves to transmit the input torque due to the swinging operation of the operating lever 104 to the first cam 24 and the like. Fulfill. In FIG. 8, for convenience, the operation lever 104 and the tapping screw 110 are shown by a two-dot chain line.

As shown in FIGS. 2, 5 and 7, the lever member 21 has a flat plate shape, and has an arcuate bottom edge 21b and one side edge 21c facing each other so as to be continuous with the bottom edge 21b and the other side. Three recesses 21a including the edges 21d are provided so as to be recessed inward with respect to the outer edge. The "flat plate shape" in the present embodiment is a shape obtained by processing a plate-shaped material having parallel front and back surfaces, and includes a shape in which unevenness is partially provided. The recesses 21a have the same shape and are arranged so as to be located at equal intervals in the circumferential direction. Further, an engaging hole 21e with which the first cam 24 is engaged is formed in the center of the lever member 21, and three through holes 21f for fixing the tapping screw 110 are formed around the engaging hole 21e. Has been done.

As shown in FIGS. 7 and 8, the cover 22 is an input-side cover formed in a substantially bottomed cylindrical shape so as to include a side wall portion 22a as a bottom portion and a cylindrical portion 22f, and is a center of the side wall portion 22a. Is formed with a through hole 22b through which the engaging protrusion 24b of the first cam 24, which will be described later, is inserted. The through hole 22b is formed so that the engaging protrusion 24b does not come into contact with the first cam 24 when the first cam 24 is rotated. Further, around the through hole 22b, three guide pieces 22c, three insertion holes 22d, and three regulation portions 22e are provided.

Each guide piece 22c controls the rotation range of the lever member 21, and is formed so as to cut off a part of the side wall portion 22a toward the input side at positions at equal intervals in the circumferential direction. .. The guide piece 22c abuts on one side edge 21c when the lever member 21 rotates to one end of the rotation range, and the other side edge 21d when the lever member 21 rotates to the other end of the rotation range. It is formed so as to abut on. In the present embodiment, as shown in FIG. 5, each recess 21a is arranged so as to face the guide piece 22c at the central portion of the bottom edge 21b in the neutral position. As a result, the rotation angle of the lever member 21 from the neutral position to one end of the rotation range and the rotation angle of the lever member 21 to the other end of the rotation range become the same angle.

Each insertion hole 22d has an elongated hole shape so as not to come into contact with the tapping screw 110 that moves with the rotation of the lever member 21, and is formed so as to be continuous with the cut-up portion of the guide piece 22c.

Each of the regulating portions 22e is equally spaced in the circumferential direction, and a part of the side wall portion 22a is cut up to the output side so as to be located between the first rollers 25 corresponding to the pair of cam surfaces 24a described later. (See FIG. 9).

The cylindrical portion 22f is formed in a cylindrical shape so that a slit is interposed between the plurality of extending portions. More specifically, in the cylindrical portion 22f, the six extension portions 22g and the six slits 22h are located at equal intervals, and the ring 31 is press-fitted into the inner peripheral surface side of each extension portion 22g. It is formed. Further, each slit 22h has the same shape and is formed so that the opening width becomes wider as the distance from the side wall portion 22a increases. In the present embodiment, in order to achieve both reduction of pressure input and securing of necessary welding strength, the circumferential length of each extending portion 22g at the welded portion is about twice the circumferential width of the slit 22h. It is set to be.

As shown in FIG. 8, the wave washer 23 is arranged so as to apply an axial urging force to both the side wall portion 22a of the cover 22 and the first cam 24. By arranging the wave washer 23 in this way, backlash in the axial direction is suppressed, so that the vertical position of the inner surface of the first cam 24 and the rotation transmission member 40 is stabilized and the operation of the second roller 33 is stabilized. Etc. can be planned.

As shown in FIGS. 7 and 9, the first cam 24 is provided with a pair of cam surfaces 24a at three locations at equal intervals on the outer peripheral surface thereof, and each cam surface 24a is rotated and transmitted, which will be described later. It is arranged so as to form six wedge-shaped spaces with the inner peripheral surface 41a of the member 40. At the center of the first cam 24, an engaging protrusion 24b that engages with the engaging hole 21e of the lever member 21 with the through hole 22b of the cover 22 inserted is provided so as to project toward the input side. Further, three groove portions 24c are provided on the outer peripheral surface of the first cam 24 at equal intervals, and each groove portion 24c is formed so that the tapping screw 110 fastened to the lever member 21 can be inserted therein. (See Fig. 9).

Each of the first rollers 25 is an input side roller formed in a substantially cylindrical shape, and the diameter thereof is a pair formed by the cam surface 24a of the first cam 24 and the inner peripheral surface 41a of the rotation transmission member 40. It is arranged so as to have a play for allowing forward and reverse rotation in the facing wedge-shaped space. Then, as shown in FIG. 9, the regulation portion 22e of the cover 22 is located between the first rollers 25 corresponding to the pair of cam surfaces 24a.

The first spring 26 is a coil spring-like urging member, and as shown in FIG. 9, the first roller 25 is urged toward the regulation portion 22e on one end side and different on the other end side. The rollers 25 are arranged so as to urge them toward different regulation portions 22e.

The washer 27 is arranged so as to be interposed between the first roller 25 and the first spring 26 and the side wall portion 22a of the cover 22 to prevent contact between the expandable and contractable first spring 26 and the side wall portion 22a. It functions to suppress the movement of the first roller 25 to the axial input side.

The washer 28 is arranged so as to be interposed between the first roller 25 and the first spring 26 and the side wall portion 42 of the rotation transmission member 40, and makes contact between the expandable and contracted first spring 26 and the side wall portion 42. It functions to prevent and suppress the movement of the first roller 25 to the axial output side.

Next, each component constituting the output member 30 will be described.
As shown in FIGS. 2 to 4, the ring 31 is an annular member that constitutes a part of the outer shell of the brake device 10 on its outer peripheral surface. As shown in FIG. 10, the ring 31 has a wedge-shaped space formed for each cam surface 32a by the inner peripheral surface 31a and the cam surface 32a of the second cam 32 facing the inner peripheral surface 31a. Have been placed. Further, the ring 31 is formed so as to be press-fitted on the inner peripheral surface side of each extending portion 22g of the cover 22 on the outer peripheral surface thereof.

As shown in FIGS. 12A and 12B, the second cam 32 is provided with a pair of cam surfaces 32a at five locations at equal intervals on the outer peripheral surface thereof, and each cam surface 32a is provided with a ring 31. It is arranged so as to form 10 wedge-shaped spaces with the inner peripheral surface 31a of the above (see FIG. 10). An engagement hole 32b for coaxially engaging the pinion gear 35 is formed in the center of the second cam 32. Further, on the end surface of the second cam 32 on the input side, five engaging convex portions 32c are arranged so as to be located at equal intervals in the circumferential direction. The second cam 32 can correspond to an example of a "brake cam".

Each second roller 33 is formed in a substantially cylindrical shape, and its diameter thereof is within a pair of opposed wedge-shaped spaces formed by the cam surface 32a of the second cam 32 and the inner peripheral surface 31a of the ring 31. It is arranged so as to have a play for allowing forward and reverse rotation. Then, as shown in FIG. 10, the regulation portion 42c of the rotation transmission member 40, which will be described later, is located between the second rollers 33 corresponding to the pair of cam surfaces 32a. The second roller 33 may correspond to an example of a "brake roller".

The second spring 34 is a coil spring-like urging member, and as shown in FIG. 10, the second roller 33 is urged toward the regulation portion 42c on one end side and different on the other end side. The rollers 33 are arranged so as to urge them toward different regulation portions 42c.

As shown in FIGS. 7 and 8, an engaging protrusion 35a that engages with the engaging hole 32b of the second cam 32 is formed on the input side of the pinion gear 35, and coaxially from the engaging protrusion 35a. The columnar portion 35b is formed so as to extend. The pinion gear 35 may correspond to an example of an "output shaft".

As shown in FIGS. 7 and 8, the friction spring 36 is arranged so as to engage the engaging projection 35a of the pinion gear 35 together with the engaging hole 32b of the second cam 32 at the engaging hole 36a. The friction spring 36 functions to apply an urging force in the reverse rotation direction to the pinion gear 35 by sliding contact with the inner peripheral surface 31a of the ring 31 when the pinion gear 35 rotates.

Next, the rotation transmission member 40 and the bush 50 for transmitting the torque input from the input member 20 to the output member 30 will be described.
As shown in FIGS. 13A and 13B, the rotation transmission member 40 includes a cylindrical portion 41 and a side wall portion 42, and is formed in a substantially bottomed cylindrical shape. The cylindrical portion 41 is arranged so as to form the wedge-shaped space by facing each cam surface 24a of the first cam 24 on its inner peripheral surface 41a (see FIG. 11).

In the side wall portion 42, a through hole 42a through which the cylindrical portion 35b of the pinion gear 35 is inserted is formed in the center thereof, and five engagement holes 42b are formed at equal intervals in the circumferential direction with the through hole 42a as a reference. There is. As shown in FIG. 11, each engaging hole 42b is formed so that the engaging convex portion 32c of the second cam 32 is inserted through a predetermined gap in the circumferential direction.

On the outer edge side of each engaging hole 42b, a regulating portion 42c extending to the output side is provided by utilizing the cut-up at the time of forming the engaging hole 42b. Each regulating portion 42c is formed so as to be located between the second rollers 33 corresponding to the pair of cam surfaces 24a of the second cam 32 at equal intervals in the circumferential direction (see FIG. 10). In FIG. 10, for convenience, the regulating portion 42c is shown so as not to come into contact with the second roller 33.

As shown in FIG. 14, the bush 50 is configured to include a substantially cylindrical bush main body portion 51 and a flange portion 52 in which a slit 53 is formed in the axial direction. The bush main body 51 is formed by bending a metal plate material having a resin coating on the plate surfaces constituting the outer peripheral surface 51a and the inner peripheral surface 51b into a cylindrical shape. The inner diameter of the inner peripheral surface 51b of the bush main body 51 is slightly smaller than the outer diameter of the cylindrical portion 35b of the pinion gear 35 when no external force is applied, and the bush main body 51 is assembled to the outer peripheral surface of the cylindrical portion 35b. The outer peripheral surface 51a is formed so as to be in frictional contact with the inner peripheral surface of the through hole 42a of the rotation transmission member 40.

The bush 50 configured in this way is the rotation transmission member 40 on the outer peripheral surface 51a of the bush main body 51 in a state of being assembled to the outer peripheral surface of the cylindrical portion 35b on the inner peripheral surface 51b of the bush main body 51. It is arranged so as to be in frictional contact with the inner peripheral surface of the through hole 42a. With the bush 50 arranged in this way, when the rotation transmission member 40 rotates relative to the pinion gear 35, a frictional force that suppresses the relative rotation of the rotation transmission member 40 is applied to the bush 50. Acts through.

The bracket 60 is a cover member that covers the ring 31, the second cam 32, and the like from the output side. A through hole 61 through which the pinion gear 35 penetrates is formed in the central portion, and a connecting hole 62 for connecting to the seat cushion 102 is provided. A total of three are formed on one end and the other end.

In the brake device 10 configured as described above, the cover 22 is welded and fixed to the outer peripheral surface of the ring 31 in a state where the ring 31 is press-fitted to the inner peripheral surface side of each extending portion 22 g. Specifically, at a position separated from the input side end surface of the ring 31 by a predetermined distance L (for example, 2 mm: see FIG. 4), the circumferential welding length at each extension portion 22 g is predetermined with reference to the rotation axis. It is welded and fixed so that it has an angle (for example, 30 °). As the welding method, for example, laser welding or TIG welding can be adopted. Further, in FIG. 4, the welded portion W is shown by a thick line.

Next, the operation of the input member 20, the output member 30, and the like in the brake device 10 configured as described above will be described with reference to FIGS. 15A and 15B.
When the operating lever 104 is not operated, the lever member 21 and the lever member 21 and the two first rollers 25 urged by different first springs 26 are pressed against one regulating portion 22e from different directions. The first cam 24 is located in the neutral position.

Then, when the operating lever 104 is swung from the neutral position N to the upward direction U or the downward direction D according to the operating force with respect to the operating lever 104, the lever member 21 and the first cam 24 respond to the swinging operation. Rotate in the same direction. At that time, in the pair of cam surfaces 24a, the first roller 25 corresponding to the cam surface 24a on the rotation direction side enters the clearance space formed by the cam surfaces 24a, so that the lock state is established and the clearance space is formed. The rotation transmission member 40 also rotates together with the first cam 24. On the other hand, the first roller 25 corresponding to the other cam surface 24a is maintained in a state of being pressed by the regulating portion 22e by the first spring 26.

When the second roller 33 pressed in the rotation direction by the restricting portion 42c of the rotation transmission member 40 that rotates as described above is separated from the wedge-shaped space, the relative rotation of the second cam 32 with respect to the ring 31 is performed. The regulation will be lifted. Therefore, when the rotation transmission member 40 rotates in response to the rotation of the input member 20, the restricting portion 42c separates the second roller 33 from the wedge-shaped space against the urging force of the second spring 34. It works to make you.

Then, the engagement convex portion 32c of the second cam 32 that has entered the engagement hole 42b of the rotation transmission member 40 is pressed against the outer edge of the engagement hole 42b, so that the second cam 32 is the rotation transmission member. Along with rotating with 40, the pinion gear 35 engaged with the second cam 32 rotates. Therefore, the engaging hole 42b functions to rotate the second cam 32 by pressing the engaging convex portion 32c in the rotation direction in a state where the second roller 33 is separated from the wedge-shaped space. ..

As a result, the input torque input from the input member 20 is transmitted to the height mechanism via the pinion gear 35 of the output member 30 and the like. In this way, when the pinion gear 35 rotates together with the rotation transmission member 40, the bush 50 interposed between the inner peripheral surface of the through hole 42a of the rotation transmission member 40 and the outer peripheral surface of the cylindrical portion 35b of the pinion gear 35 also Since it rotates as a unit, no frictional force is generated on the bush 50.

Then, when the input torque disappears due to the release of the operating force, the first roller 25 receiving the force from the cam surface 24a is pressed against the regulating portion 22e by the urging force of the first spring 26. Return to the original position. Therefore, as described above, the first roller 25 that tries to return to the original position exerts a force that tries to rotate the rotation transmission member 40 in the direction opposite to that at the time of operation. At this time, since the rotation transmission member 40 is in frictional contact with the outer peripheral surface 51a of the bush 50 through the through hole 42a, the rotation of the rotation transmission member 40 in the opposite direction as described above is suppressed. As a result, even after the input torque disappears, as shown in FIG. 15A, the contact state between the restricting portion 42c of the rotation transmission member 40 and the second roller 33 is maintained, so that the rotation transmission member It is possible to eliminate the operation play from when the 40 starts to rotate in the same direction as the previous time until the regulating portion 42c contacts the second roller 33.

When the operation lever 104 is operated in the opposite direction to the previous time, there is an operation play because the regulating portion 42c is not in contact with the second roller 33 in the rotation direction at the first operation, but the operation in the same rotation direction is continued. Occasionally, as shown in FIG. 15B, the regulating portion 42c is in contact with the second roller 33, which is different from the state shown in FIG. 15A, so that the operation play can be eliminated.

Next, the effect of the brake device 10 on reducing the operating force will be described with reference to FIG. In FIG. 16, regarding the operating angle of the operating lever 104, the change in the operating torque in the brake device 10 according to the present embodiment is shown as T1, and the change in the operating torque in the conventional configuration with operating play is shown as T2. ..

As shown in FIG. 16, in the conventional configuration with operation play, even if the operation angle starts to increase by starting to operate the operation lever 104, the pressing piece of the rotation transmission member (see reference numeral 201 in FIG. 17) is a roller (see reference numeral 201 in FIG. 17). Since it is not in contact with reference numeral 203 in FIG. 17, the rotation transmission member or the like does not rotate, so that the operation torque T2 required for the operation does not increase so much. After that, when the pressing piece comes into contact with the roller and the rotation transmission member or the like starts to rotate and the operating angle increases, the operating torque T2 rapidly increases and then stabilizes.

On the other hand, in the brake device 10 in which the operation play is suppressed, when the operation angle starts to increase by starting to operate the operation lever 104, the regulation portion 42c of the rotation transmission member 40 already has the second roller as described above. By being in contact with 33, the rotation transmission member 40 and the like immediately start to rotate, and the operation torque T1 required for operation increases. After that, when the pinion gear 35 reaches an operating angle that rotates integrally with the rotation transmission member 40, the frictional force of the bush 50 does not act, so that the operating torque T1 stabilizes at substantially the same value as the operating torque T2. ..

As described above, in the brake device 10 according to the present embodiment, by rotating according to the rotation of the input member 20, the second roller 33 is wedge-shaped space against the urging force of the second spring 34. A rotation transmission member 40 for rotating the second cam 32 connected to the pinion gear 35 is provided. The rotation transmission member 40 is formed with a through hole 42a through which the columnar portion 35b of the pinion gear 35 penetrates, and between the through hole 42a and the columnar portion 35b, the inner peripheral surface of the through hole 42a and the outer periphery of the columnar portion 35b are formed. A bush 50 that is in frictional contact with both surfaces is provided.

As a result, even if the input torque is lost after the second roller 33 is separated from the wedge-shaped space by the rotation transmission member 40 that rotates according to the input torque, the rotation transmission member 40 is formed in the through hole 42a. Since the bush 50 is in frictional contact, the frictional force acts so as to maintain the contact state between the rotation transmission member 40 and the second roller 33, so that the operation play can be suppressed. When the rotation transmission member 40 rotates while the second roller 33 is separated from the wedge-shaped space, the pinion gear 35 rotates integrally with the rotation transmission member 40, so that the rotation transmission member 35 rotates with the pinion gear 35. Since friction does not occur in the bush 50 interposed between the transmission member 40 and the bush 50, the operating force does not increase. Therefore, it is possible to realize a configuration in which operation play can be suppressed without increasing the operating force.

[Other embodiments]
The present invention is not limited to the above embodiment, and may be embodied as follows, for example.
(1) The bush 50 is not limited to being configured by bending a metal plate material having a resin coating on the plate surface into a cylindrical shape, but also has a frictional force with respect to the through hole 42a of the rotation transmission member 40. Any member may be used, and may be formed of, for example, a resin-made cylindrical member.

10 ... Brake device 20 ... Input member 30 ... Output member 31 ... Ring 31a ... Inner peripheral surface 32 ... Second cam (brake cam)
32a ... Cam surface 33 ... Second roller (brake roller)
34 ... 2nd spring (biasing member)
35 ... Pinion gear (output shaft)
35b ... Cylindrical part 40 ... Rotation transmission member 42a ... Through hole 50 ... Bush 51 ... Bush body 100 ... Vehicle seat device

Claims (1)

The input torque is transmitted from the input member to the output member via the rotation transmission member and output, and when the torque input to the input member is exhausted, the rotation of the output member is restricted. It ’s a device,
The output member is
Output axis and
A brake cam coaxially connected to the output shaft to form a plurality of cam surfaces on the outer peripheral surface,
A ring arranged so that a pair of wedge-shaped spaces are formed for each cam surface by the inner peripheral surface and the plurality of cam surfaces facing the inner peripheral surface.
A brake roller for restricting the relative rotation between the ring and the brake cam by entering the wedge-shaped space, and
An urging member that urges the brake roller toward the wedge-shaped space,
Equipped with
By rotating the rotation transmission member in response to the rotation of the input member, the brake roller is separated from the wedge-shaped space against the urging force of the urging member, and the brake cam is moved. Formed to rotate,
The rotation transmission member is formed with a through hole through which the cylindrical portion of the output shaft penetrates.
A brake device characterized in that a bush is provided between the through hole and the columnar portion so as to be in frictional contact with the inner peripheral surface of the through hole and the outer peripheral surface of the columnar portion.

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