JP7549209B2 - Brake system - Google Patents

Description

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

Conventionally, as a technology related to a brake device that is arranged on a vehicle seat and controls the torque transmitted from an input member to an output member when adjusting the position of the vehicle seat, for example, a clutch device disclosed in the following Patent Document 1 is known. This clutch device is configured such that, in response to the operation of an operating lever, the lever member, connecting shaft, reverse plate, retainer, and input side cam that constitute the input side member each rotate, causing the rotation transmission member and washer to rotate so as to be pressed by the input side roller, and the rotation of the rotation transmission member causes the output side roller to leave the wedge-shaped space, causing the output side members such as the output side cam and pinion gear to rotate together with the rotation transmission member.

JP 2010-127418 A

However, in a configuration in which torque from an input member is controllably transmitted to an output member by combining multiple members as described above, there is a problem in that the greater the number of parts, the more difficult it becomes to reduce costs, and it also becomes difficult to reduce the size and weight.

The present invention was made to solve the above-mentioned problems, and its purpose is to provide a configuration that can reduce the number of parts by giving multiple functions to a rotation transmission member that transmits input torque from an input member to an output member.

In order to achieve the above object, the invention of claim 1 described in the claims is as follows:
A brake device (10) for a vehicle seat that transmits and outputs an input torque from an input member (20) to an output member (30) via a rotation transmission member (40) and restricts rotation of the output member when the torque input to the input member is eliminated, comprising:
The output member is
An output shaft (35);
a brake cam (32) coaxially connected to the output shaft, having a plurality of cam surfaces (32a) formed on its outer circumferential surface and a plurality of engaging protrusions (32c) formed on its input side surface;
a ring (31) arranged such that a pair of wedge-shaped spaces are formed for each cam surface by an inner circumferential surface (31a) and the plurality of cam surfaces facing the inner circumferential surface;
a brake roller (33) for restricting relative rotation between the ring and the brake cam by entering the wedge-shaped space;
a biasing member (34) that biases the brake roller toward the wedge-shaped space;
Equipped with
The rotation transmission member is formed with a plurality of engagement holes (42b) through which the plurality of engagement protrusions can be inserted with a predetermined gap therebetween in the circumferential direction, and a restriction portion (42c) is formed by utilizing the cut-and-raised portions formed when the engagement holes are formed,
the regulating portion is formed to disengage the brake roller from the wedge-shaped space against the biasing force of the biasing member when the rotation transmission member rotates in response to the rotation of the input member,
The engagement hole is formed so as to rotate the brake cam by pressing the engagement protrusion in a rotational direction when the brake roller is removed from the wedge-shaped space.
The symbols in parentheses above indicate the corresponding relationship with the specific means described in the embodiments described later.

In the invention of claim 1, the rotation transmission member that transmits the input torque from the input member to the output member is formed with a plurality of engagement holes through which the plurality of engagement protrusions of the brake cam can be inserted with a predetermined gap in the circumferential direction, and a regulating portion is formed by utilizing the cut-outs made when forming the engagement holes. The regulating portion is formed so as to disengage the brake roller from the wedge-shaped space against the biasing force of the biasing member when the rotation transmission member rotates in response to the rotation of the input member, and the engagement hole is formed so as to rotate the brake cam by pressing the engagement protrusions in the rotation direction when the brake roller is disengaged from the wedge-shaped space.

This allows the rotation transmission member to be configured to have the function of disengaging the brake roller from the wedge-shaped space by the restricting portion, and the function of rotating the brake cam in the disengaged state by the engagement hole. In this way, the number of parts can be reduced by giving multiple functions to the rotation transmission member that transmits the input torque from the input member to the output member. In particular, because the restricting portion is formed by utilizing the cut and raised portion formed when the engagement hole is formed, the number of manufacturing steps can be reduced compared to a configuration in which the restricting portion and the engagement hole are each formed separately.

1 is a side view showing a vehicle seat device to which a brake device according to the present invention is applied; FIG. 2 is a perspective view of the brake device as viewed from the input side. FIG. 2 is a perspective view of the brake device as seen from the output side. FIG. FIG. 2 is a side view of the brake device as viewed from the input side. FIG. 2 is a side view of the brake device as viewed from the output side. FIG. 6 is an enlarged cross-sectional view showing the X1-X1 cross section shown in FIG. 5. 5 is an enlarged cross-sectional view showing the X2-X2 cross section shown in FIG. 4. 5 is an enlarged cross-sectional view showing a cross section taken along the line X3-X3 in FIG. 4. 5 is an enlarged cross-sectional view showing the X4-X4 cross section shown in FIG. 4. FIG. 12A is a view of the second cam as seen from the input side, and FIG. 12B is a side view of FIG. 12A. 13A is a diagram of the rotation transmission member as viewed from the input side, and FIG. 13B is a side view of FIG. 13A. FIG. 4 is an enlarged perspective view of a bush. 13 is an explanatory view illustrating a state in which an engaging protrusion of a second cam is pressed by an outer edge of an engaging hole of a rotating rotation transmission member; FIG. Figure 16 (A) is an explanatory diagram illustrating a state in which a contact state between the regulating portion of the rotation transmission member and the second roller is maintained, and Figure 16 (B) is an explanatory diagram illustrating a state in which a contact state between the second roller and the regulating portion that is different from the state in Figure 16 (A) is maintained.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment of a vehicle seat device to which a brake device for a vehicle seat according to the present invention is applied will be described with reference to the drawings.
1, the vehicle seat device 100 mainly includes a seat rail 101 that is slidable back and forth relative to a vehicle floor B, a seat cushion 102 that is attached to the seat rail 101 via a seat bracket (not shown) or the like, and a seat back 103 that is supported so as to be tiltable relative to the seat cushion 102. A vehicle seat brake device (clutch device) 10 according to the present invention is disposed on one side of the seat cushion 102, and an operating lever 104 is connected to the brake device 10.

This brake device 10 serves to adjust the height of the seat cushion 102 as desired by transmitting the input torque from the operating lever 104 to a known height mechanism (output mechanism) provided on the seat bracket via an input member, an output member, etc.

In other words, the brake device 10 transmits the torque input from the input member to the output member in response to the operation of the operating lever 104, and is configured so that when the torque input to the input member disappears, the rotation of the output member is restricted and only the input member returns to the neutral position. Therefore, in the brake device 10, when the operating lever 104 is in the horizontal neutral position N, the output member is fixed so as not to rotate so as to maintain the height of the seat cushion 102.

When the operating lever 104 of the brake device 10 is swung in the upward direction U to raise the height of the seat cushion 102, an input torque corresponding to this swinging operation is transmitted to the height mechanism via the input member and the output member. This raises the height of the seat cushion 102. Then, when the input torque is eliminated, the output member maintains its rotation angle, and the input member returns to the neutral position together with the operating lever 104, so that the raised height of the seat cushion 102 is maintained.

On the other hand, when the operating lever 104 of the brake device 10 is swung in the downward direction D to lower the height of the seat cushion 102, an input torque corresponding to this swinging operation is transmitted to the height mechanism via the input member and the output member. This lowers the height of the seat cushion 102. Then, when the input torque is eliminated, the output member maintains its rotation angle, and the input member returns to the neutral position together with the operating lever 104, so that the lowered height of the seat cushion 102 is maintained.

Next, the configuration of the brake device 10 will be described with reference to the drawings.
As shown in Figures 2 to 11, the brake device 10 includes an input member 20 having 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 27, 28, an output member 30 having a ring 31, a second cam 32, ten second rollers 33, five second springs 34, a pinion gear 35, and a friction spring 36, a rotation transmission member 40, a bush 50, and a bracket 60, and the input member 20 and the output member 30 are arranged coaxially via the rotation transmission member 40.

First, each part 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 plays a role in transmitting input torque generated by the swing operation of the operating lever 104 to the first cam 24, etc. In addition, in Fig. 8, for the sake of convenience, the operating lever 104 and the tapping screws 110 are illustrated by two-dot chain lines.

As shown in Figs. 2, 5 and 7, the lever member 21 is flat and has three recesses 21a, each of which is made up of an arc-shaped bottom edge 21b and one side edge 21c and the other side edge 21d that are connected to the bottom edge 21b, and is recessed inward relative to the outer edge. In this embodiment, the term "flat" refers to a shape obtained by processing a plate-shaped material with parallel front and back surfaces, and includes a shape in which some unevenness is provided. The recesses 21a are the same shape and are arranged at equal intervals in the circumferential direction. In addition, an engagement hole 21e with which the first cam 24 engages is formed in the center of the lever member 21, and three through holes 21f for fixing the tapping screws 110 are formed around the engagement hole 21e.

As shown in Figures 7 and 8, the cover 22 is an input side cover formed in a generally bottomed cylindrical shape with a side wall portion 22a that serves as the bottom and a cylindrical portion 22f, and a through hole 22b is formed in the center of the side wall portion 22a, through which an engaging protrusion 24b of the first cam 24 described below is inserted. This through hole 22b is formed so that the engaging protrusion 24b does not come into contact when the first cam 24 rotates. In addition, three guide pieces 22c, three insertion holes 22d, and three restriction portions 22e are provided around the through hole 22b.

Each guide piece 22c controls the rotation range of the lever member 21, and is formed by cutting out a part of the side wall portion 22a toward the input side at positions that are equally spaced in the circumferential direction. The guide piece 22c is formed so that it abuts against one side edge 21c when the lever member 21 rotates to one end of the rotation range, and abuts against the other side edge 21d when the lever member 21 rotates to the other end of the rotation range. In this embodiment, as shown in FIG. 5, each recess 21a is arranged so that it faces the guide piece 22c at the center of the bottom edge 21b in the neutral position. This makes the rotation angle of the lever member 21 from the neutral position to one end of the rotation range the same as the rotation angle of the lever member 21 to the other end of the rotation range.

Each insertion hole 22d is elongated 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 connect to the cut-out portion of the guide piece 22c.

Each regulating portion 22e is equally spaced in the circumferential direction and is formed by cutting out a portion of the side wall portion 22a toward the output side so that it is positioned between the first rollers 25 that correspond to a pair of cam surfaces 24a described below (see Figure 9).

The cylindrical portion 22f is formed in a cylindrical shape such that slits are interposed between the multiple extensions. More specifically, the cylindrical portion 22f is formed such that six extensions 22g and six slits 22h are positioned at equal intervals, and a ring 31 is pressed into the inner peripheral surface side of each extension 22g. In addition, each slit 22h has the same shape and is formed so that the opening width becomes wider as it is farther away from the side wall portion 22a. In this embodiment, in order to achieve both a reduction in the press-in force and ensuring the necessary welding strength, the circumferential length of each extension 22g at the welded portion is set to be about twice the circumferential width of the slit 22h.

As shown in FIG. 8, the wave washer 23 is positioned to apply an axial biasing force to both the side wall portion 22a of the cover 22 and the first cam 24. By positioning the wave washer 23 in this manner, axial play is suppressed, which makes it possible to stabilize the vertical position of the inner surface of the first cam 24 and the rotation transmission member 40, stabilize the operation of the second roller 33, etc.

7 and 9, the first cam 24 has three pairs of cam surfaces 24a at equal intervals on its outer circumferential surface, and each cam surface 24a is arranged to form six wedge-shaped spaces between the inner circumferential surface 41a of the rotation transmission member 40 described later. At the center of the first cam 24, an engagement protrusion 24b is provided so as to protrude toward the input side and engages with the engagement hole 21e of the lever member 21 when inserted through the through hole 22b of the cover 22. In addition, three grooves 24c are provided at equal intervals on the outer circumferential surface of the first cam 24, and each groove 24c is formed so that a tapping screw 110 fastened to the lever member 21 can be inserted into it (see FIG. 9).

Each first roller 25 is an input roller formed in a substantially cylindrical shape, and is arranged so that its diameter has a play to allow forward and reverse rotation within a pair of opposing wedge-shaped spaces formed by the cam surface 24a of the first cam 24 and the inner peripheral surface 41a of the rotation transmission member 40. As shown in FIG. 9, the restricting portion 22e of the cover 22 is located between the first rollers 25 that correspond to the pair of cam surfaces 24a.

The first spring 26 is a coil spring-shaped biasing member, and as shown in FIG. 9, is arranged so that one end biases the first roller 25 toward the regulating portion 22e, and the other end biases a different first roller 25 toward a different regulating portion 22e.

The washer 27 is positioned between the first roller 25 and the first spring 26 and the side wall portion 22a of the cover 22, and functions to prevent contact between the expanding and contracting first spring 26 and the side wall portion 22a, and to suppress movement of the first roller 25 toward the axial input side.

The washer 28 is disposed between the first roller 25 and the first spring 26 and the side wall portion 42 of the rotation transmission member 40, and functions to prevent contact between the expanding and contracting first spring 26 and the side wall portion 42, and to suppress movement of the first roller 25 toward the axial output side.

Next, each part constituting the output member 30 will be described.
2 to 4, the ring 31 is an annular member whose outer circumferential surface constitutes part of the outer shell of the brake device 10. As shown in Fig. 10, the ring 31 is disposed such that a wedge-shaped space is formed for each cam surface 32a by its inner circumferential surface 31a and the cam surface 32a of the second cam 32 facing the inner circumferential surface 31a. The ring 31 is also formed such that its outer circumferential surface is press-fitted into the inner circumferential surface side of each extension portion 22g of the cover 22.

12(A) and 12(B), the second cam 32 has five pairs of cam surfaces 32a at equal intervals on its outer circumferential surface, and each cam surface 32a is arranged to form ten wedge-shaped spaces between the inner circumferential surface 31a of the ring 31 (see FIG. 10). An engagement hole 32b for coaxially engaging with the pinion gear 35 is formed in the center of the second cam 32. In addition, five engagement protrusions 32c are arranged at equal intervals in the circumferential direction on the input side end surface of the second cam 32. As shown in FIG. 7 and FIG. 12, the engagement protrusions 32c are formed so that the inner surface with respect to the rotation center is formed in an arc shape based on the rotation center, and the circumferential side surface is curved so as to be convex outward. The second cam 32 can be an example of a "brake cam".

Each second roller 33 is formed in a generally cylindrical shape, and is arranged so that its diameter has a play to allow forward and reverse rotation within a pair of opposing wedge-shaped spaces formed by the cam surface 32a of the second cam 32 and the inner peripheral surface 31a of the ring 31. As shown in FIG. 10, a regulating portion 42c of the rotation transmission member 40 (described later) is located between the second rollers 33 that correspond to the pair of cam surfaces 32a. The second rollers 33 may be an example of a "brake roller."

The second spring 34 is a coil spring-shaped biasing member, and as shown in FIG. 10, is arranged so that one end biases the second roller 33 toward the regulating portion 42c, and the other end biases a different second roller 33 toward a different regulating portion 42c.

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

As shown in Figures 7 and 8, the friction spring 36 is arranged so that the engagement hole 36a engages with the engagement protrusion 35a of the pinion gear 35 together with the engagement hole 32b of the second cam 32. This friction spring 36 slides against the inner peripheral surface 31a of the ring 31 when the pinion gear 35 rotates, thereby applying a biasing force to the pinion gear 35 in the reverse rotation direction.

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.
13A and 13B, the rotation transmission member 40 is formed in a generally cylindrical shape with a bottom, and includes a cylindrical portion 41 and a side wall portion 42. The cylindrical portion 41 is disposed so that its inner peripheral surface 41a faces each cam surface 24a of the first cam 24 to form the wedge-shaped space (see FIG. 11).

The side wall portion 42 has a through hole 42a in its center through which the cylindrical portion 35b of the pinion gear 35 is inserted, and five engagement holes 42b are formed at equal intervals in the circumferential direction based on the through hole 42a. As shown in FIG. 11, each engagement hole 42b is formed so that the engagement protrusion 32c of the second cam 32 can be inserted through a predetermined gap in the circumferential direction. Specifically, the engagement hole 42b is formed so that its inner arc-shaped edge faces the inner surface of the engagement protrusion 32c of the second cam 32, and the distance between the circumferential edges is longer than the circumferential length of the engagement protrusion 32c of the second cam 32 by the predetermined gap.

A restricting portion 42c extending toward the output side is provided on the outer edge of each engagement hole 42b by utilizing the cut-and-raised portions formed when the engagement hole 42b is formed. Each restricting portion 42c is formed to be equidistantly spaced in the circumferential direction and positioned between the second rollers 33 corresponding to the pair of cam surfaces 24a of the second cam 32 (see FIG. 10). For convenience, FIG. 10 illustrates the restricting portion 42c as not contacting the second rollers 33.

As shown in FIG. 14, the bush 50 is configured to include a substantially cylindrical bush main body 51 with axially formed slits 53, and a flange portion 52. The bush main body 51 is formed by bending a metal plate material with a resin coating applied to the plate surfaces constituting the outer peripheral surface 51a and the inner peripheral surface 51b into a cylindrical shape. When no external force is applied, 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, and when assembled to the outer peripheral surface of the cylindrical portion 35b, the outer peripheral surface 51a is 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 manner is arranged so that the outer peripheral surface 51a of the bush main body 51 is in frictional contact with the inner peripheral surface of the through hole 42a of the rotation transmission member 40 when the inner peripheral surface 51b of the bush main body 51 is assembled to the outer peripheral surface of the cylindrical portion 35b. With the bush 50 arranged in this manner, when the rotation transmission member 40 rotates relative to the pinion gear 35, a frictional force that suppresses the relative rotation acts on the rotation transmission member 40 via the bush 50.

The bracket 60 is a cover member that covers the ring 31, the second cam 32, etc. from the output side, and has a through hole 61 formed in the center through which the pinion gear 35 passes, and a total of three connection holes 62 formed at one end and the other end for connecting to the seat cushion 102.

In the brake device 10 configured in this manner, the cover 22 is welded and fixed to the outer circumferential surface of the ring 31 with the ring 31 pressed into the inner circumferential surface of each extension 22g. Specifically, the cover 22 is welded and fixed at a position a predetermined distance L (e.g., 2 mm: see FIG. 4) away from the input end face of the ring 31 so that the circumferential weld length of each extension 22g is a predetermined angle (e.g., 30°) based on the rotation axis. For example, laser welding or TIG welding can be used as the welding method. 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, etc. in the brake device 10 configured as above will be described with reference to FIGS.
When the operating lever 104 is not operated, the lever member 21 and the first cam 24 are positioned in the neutral position with the two first rollers 25, each biased by a different first spring 26, being pressed from different directions against one regulating portion 22e.

When the operating lever 104 is swung from the neutral position N in the upward direction U or downward direction D in response to the operating force applied to the operating lever 104, the lever member 21 and the first cam 24 rotate in a direction corresponding to the swinging operation. At that time, the first roller 25 corresponding to the cam surface 24a on the rotating direction side of the pair of cam surfaces 24a enters the gap space formed by the cam surface 24a, thereby entering a locked state, and the rotation transmission member 40 forming the gap space also rotates together with the first cam 24. Meanwhile, the first roller 25 corresponding to the other cam surface 24a is maintained in a state of being pressed against the restricting portion 22e by the first spring 26.

As described above, the second roller 33, which is pressed in the rotation direction by the restricting portion 42c of the rotating rotation transmission member 40, leaves the wedge-shaped space (see arrow F1 in FIG. 15), and the restriction on the relative rotation of the second cam 32 with respect to the ring 31 is released. Therefore, when the rotation transmission member 40 rotates in response to the rotation of the input member 20, the restricting portion 42c functions to cause the second roller 33 to leave the wedge-shaped space against the biasing force of the second spring 34.

As described above, when the second roller 33 is released from the wedge-shaped space, the engaging protrusion 32c of the second cam 32 that is inserted into the engaging hole 42b of the rotation transmission member 40 is pressed against the outer edge of the engaging hole 42b (see arrow F2 in FIG. 15), so that the second cam 32 rotates together with the rotation transmission member 40, and the pinion gear 35 that engages with the second cam 32 rotates. Therefore, when the second roller 33 is released from the wedge-shaped space, the engaging hole 42b functions to rotate the second cam 32 by pressing the engaging protrusion 32c in the rotation direction.

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. In this way, when the pinion gear 35 rotates together with the rotation transmission member 40, the bush 50 interposed between the inner circumferential surface of the through hole 42a of the rotation transmission member 40 and the outer circumferential surface of the cylindrical portion 35b of the pinion gear 35 also rotates together, so no frictional force is generated in the bush 50.

When the input torque is eliminated by releasing the operating force, the first roller 25, which has been receiving a force from the cam surface 24a, returns to its original position so as to be pressed against the restricting portion 22e by the biasing force of the first spring 26. Therefore, the first roller 25, which is trying to return to its original position as described above, exerts a force on the rotation transmission member 40 to rotate it in the opposite direction to that during operation. At this time, since the rotation transmission member 40 is in frictional contact with the outer peripheral surface 51a of the bush 50 at the through hole 42a, the rotation transmission member 40 is prevented from rotating in the opposite direction as described above. As a result, even after the input torque is eliminated, the contact state between the restricting portion 42c of the rotation transmission member 40 and the second roller 33 is maintained as shown in FIG. 16(A), so that the operating play from when the rotation transmission member 40 starts to rotate in the same direction as the previous time until it comes into contact with the second roller 33 at the restricting portion 42c can be eliminated.

When the operating lever 104 is operated in the opposite direction to the previous operation, the regulating part 42c is not in contact with the second roller 33 in the rotation direction during the first operation, so there is some operating play. However, during subsequent operations in the same rotation direction, as shown in FIG. 16(B), the regulating part 42c is in contact with a different second roller 33 than in the state shown in FIG. 16(A), so the operating play can be eliminated.

As described above, in the brake device 10 according to this embodiment, the rotation transmission member 40 that transmits the input torque from the input member 20 to the output member 30 has a plurality of engagement holes 42b through which the plurality of engagement protrusions 32c of the second cam 32 can be inserted with a predetermined gap in the circumferential direction, and the regulating portion 42c is formed by using the cut-outs made when the engagement holes 42b are formed. The regulating portion 42c is formed so as to disengage the second roller 33 from the wedge-shaped space against the biasing force of the second spring 34 when the rotation transmission member 40 rotates in response to the rotation of the input member 20, and the engagement hole 42b is formed so as to rotate the second cam 32 by pressing the engagement protrusions 32c in the rotation direction when the second roller 33 is disengaged from the wedge-shaped space.

This allows the rotation transmission member 40 to be configured to have the function of disengaging the second roller 33 from the wedge-shaped space by the restricting portion 42c, and the function of rotating the second cam 32 in the disengaged state by the engaging hole 42b. In this way, the number of parts can be reduced by giving multiple functions to the rotation transmission member 40 that transmits the input torque from the input member 20 to the output member 30. In particular, since the restricting portion 42c is formed by utilizing the cut and raised portion formed when the engaging hole 42b is formed, the number of manufacturing steps can be reduced compared to a configuration in which the restricting portion 42c and the engaging hole 42b are each formed separately.

[Other embodiments]
The present invention is not limited to the above-described embodiment, and may be embodied as follows, for example.
(1) The number of engagement holes 42b provided in the side wall portion 42 of the rotation transmission member 40 is not limited to five, and may be two to four or six or more, equally spaced in the circumferential direction, or multiple holes may be provided unequally spaced, depending on the usage environment, etc. In such a configuration, the same number of restriction portions 42c and the engagement protrusions 32c of the second cam 32, etc., can be provided at corresponding positions.

(2) The engaging protrusions 32c of the second cam 32 are not limited to being formed so that the inner surface is arc-shaped with respect to the center of rotation and the circumferential side surface is curved outwardly as described above, but may be formed, for example, in a substantially cylindrical or prismatic shape. Even with this configuration, the engaging holes 42b are formed so that the engaging protrusions 32c can be inserted through the above-mentioned predetermined gaps in the circumferential direction, thereby allowing the rotation of the rotation transmission member 40 to be appropriately transmitted to the second cam 32.

REFERENCE SIGNS LIST 10 Brake device 20 Input member 30 Output member 31 Ring 31a Inner peripheral surface 32 Second cam (brake cam)
32a: cam surface; 32c: engagement protrusion; 33: second roller (brake roller)
34...Second spring (biasing member)
35...Pinion gear (output shaft)
40: rotation transmission member 41: cylindrical portion 42: side wall portion 42b: engagement hole 42c: restriction portion 100: vehicle seat device

Claims (1)

1. A brake device for a vehicle seat that transmits an input torque from an input member through a rotation transmission member to an output member and outputs the torque, and restricts rotation of the output member when the torque input to the input member is eliminated, comprising:
The output member is
An output shaft;
a brake cam that is coaxially connected to the output shaft and has a plurality of cam surfaces formed on an outer circumferential surface thereof and a plurality of engagement protrusions formed on an input side surface thereof;
a ring disposed such that a pair of wedge-shaped spaces are formed for each cam surface by an inner circumferential surface and the plurality of cam surfaces facing the inner circumferential surface;
a brake roller for restricting relative rotation between the ring and the brake cam by entering the wedge-shaped space;
a biasing member that biases the brake roller toward the wedge-shaped space;
Equipped with
a plurality of engagement holes are formed in the rotation transmission member, into which the plurality of engagement protrusions can be inserted with a predetermined gap therebetween in the circumferential direction, and a restriction portion is formed by utilizing the cut-and-raised portions formed when the engagement holes are formed;
the regulating portion is formed to disengage the brake roller from the wedge-shaped space against the biasing force of the biasing member when the rotation transmission member rotates in response to the rotation of the input member,
A braking device characterized in that the engagement hole is formed so as to rotate the brake cam by pressing the engagement protrusion in a rotational direction when the brake roller is removed from the wedge-shaped space.

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