JP7327099B2 - Vibration suppression mechanism for vehicle seat - Google Patents

Description

The present invention relates to a vibration suppression mechanism for a vehicle seat.

A vibration suppression mechanism for a vehicle seat, which is arranged between a first member attached to a cushion frame and a second member attached to an upper rail of a slide rail installed on a floor of a vehicle. It is known to suppress the vibration applied to the seat. A vibration suppressing mechanism for a vehicle seat disclosed in Patent Document 1 includes a first tubular member attached to a first member, a second tubular member attached to a second member, a first tubular member, and a second tubular member. and an elastic member disposed between the member and connecting the two tubular members. Further, when a large load is applied to the vehicle seat due to a vehicle collision or the like, the elastic member is largely deformed to prevent the first member from being largely displaced with respect to the second member. A displacement amount limiting member is arranged between the first cylindrical member.

JP 2013-82304 A

In the vehicle seat vibration suppression mechanism described in Patent Document 1, the vehicle seat is supported in a state in which it can move vertically, forward, backward, and laterally with respect to the floor via four vibration suppression mechanisms. Vibration transmitted to the vehicle seat when vertical acceleration is applied is reduced. However, when a large load is applied to the vehicle seat in the vertical direction due to a vehicle collision, etc., the elastic material is deformed greatly and the vehicle seat is not displaced excessively with respect to the floor. It was necessary to dispose a displacement amount limiting member, which is a member.

In view of such problems, an object of the present invention is to provide a vehicle seat capable of reducing vibrations applied to the vehicle seat from the floor and suppressing movement of the vehicle seat when a large load is applied with a simple structure. is to provide a vibration suppressing mechanism.

A first aspect of the present invention is a vibration suppression mechanism for a vehicle seat disposed between a cushion frame forming the skeleton of the seat cushion and a vehicle floor, the vibration suppression mechanism comprising a large-diameter substantially cylindrical body. A first member and a substantially cylindrical second member having a small diameter are arranged coaxially with an elastic member interposed therebetween, and a part of the first member and/or the second member extends radially. and a narrow ring portion is formed to narrow the distance between the first member and the second member, and the first member is directly or indirectly connected to either the cushion frame or the vehicle floor. the second member is connected to the other of the cushion frame or the vehicle floor, and the narrow ring portion applies a large radial load to the vibration damping mechanism. is applied, the first member and the second member are prevented from coming closer than a predetermined value.

According to the first invention, the cushion frame and the vehicle floor are connected via the vibration suppression mechanism, and the vibration suppression mechanism includes the first member and the second member coaxially arranged via the elastic member. configured as follows. The first member is connected to either the cushion frame or the vehicle floor, and the second member is connected to the other of the cushion frame or the vehicle floor. As a result, the vibration applied from the vehicle floor to the vehicle seat due to the elastic deformation of the elastic member can be reduced, and the ride comfort can be improved. On the other hand, when a large load is applied to the vehicle seat from the vehicle floor due to a vehicle collision or the like, the first member and the second member come into contact with each other or come close to each other via the elastic member at the narrow ring portion to receive the load. Movement of the vehicle seat with respect to the vehicle floor can be suppressed. That is, the vibration suppressing mechanism can reduce the vibration applied to the vehicle seat from the floor and suppress the movement of the vehicle seat when a large load is applied, with a simple structure that does not require a separate member. .

According to a second aspect of the present invention, in the first aspect, the first member has a shorter length in the axial direction than the second member, and the narrow ring portions are provided at both ends in the axial direction of the first member. It is characterized by

According to the second aspect of the invention, when a large load is applied between the first member and the second member to approach them in the radial direction, the first member abuts or approaches the second member at both ends in the axial direction. As a result, an approach exceeding a predetermined value is suppressed. Thereby, when the first member approaches the second member, it is easy to keep the axial directions parallel to each other.

According to a third aspect of the present invention, in the first aspect, the first member has a shorter length in the axial direction than the second member, and the narrow ring portion is provided at the central portion in the axial direction of the first member. It is characterized by

According to the third aspect of the invention, when a large load is applied between the first member and the second member, the first member abuts or approaches the second member at the central portion in the axial direction. As a result, an approach exceeding a predetermined value is suppressed. As a result, when the first member approaches the second member, it is somewhat difficult to maintain parallelism in the axial direction. Since the molding material of the elastic member can be injected from both ends, the manufacturing is facilitated.

According to a fourth aspect of the present invention, in the second aspect or the third aspect, there is provided a regulation mechanism that regulates the axial movement distance of the first member with respect to the cushion frame or the vehicle floor to a predetermined value or less. It is characterized by being arranged directly or indirectly on the cushion frame or the vehicle floor.

According to the fourth invention, relative movement of the first member in the axial direction with respect to the second member can be suppressed.

1 is a perspective view of an automobile seat to which a vibration suppression mechanism according to a first embodiment of the invention is attached; FIG. It is a side view of the automobile seat of the embodiment. FIG. 3 is a cross-sectional view along the line III-III in FIG. 2; FIG. 3 is a cross-sectional view taken along the line IV-IV in FIG. 2; FIG. 4 is a cross-sectional view corresponding to FIG. 3 in a second embodiment of the present invention; FIG. 5 is a cross-sectional view corresponding to FIG. 4 in a third embodiment of the present invention; It is a sectional view corresponding to Drawing 4 in a 4th embodiment of the present invention.

1 to 4 show a first embodiment of the invention. This embodiment is an example in which the present invention is applied to an automobile seat 1 . In each figure, the arrows indicate the directions of the vehicle and the vehicle seat 1 when the vehicle seat 1 is attached to the floor F of the vehicle. In the following description, descriptions regarding directions are based on this direction. Here, the automobile seat 1 and the floor F respectively correspond to a "vehicle seat" and a "vehicle floor" in the claims.

As shown in FIG. 1, an automobile seat 1 is a right rear seat, and includes a seat cushion 2 that serves as a seating portion for a seated occupant, and a seat back 3 that serves as a backrest.

As shown in FIGS. 1 and 2, the seat cushion 2 includes a cushion frame 10 forming a framework, a cushion pad 2p serving as a cushion material, and a cushion cover 2c serving as an upholstery material. The cushion frame 10 includes a pair of left and right side frames 11, a cylindrical front frame 12 extending left and right connecting the side frames 11 at the front end side, and a cylindrical front frame 12 extending left and right connecting the side frames 11 at the rear end side. and a cylindrical rear frame 13 . Further, the cushion frame 10 has a pair of left and right lower arm members 14 attached to the upper portion of the rear end portion of each side frame 11 .

As shown in FIGS. 1 to 4, the side frame 11 is made of die-cast aluminum and has a substantially isosceles trapezoidal shape in which the upper base is longer than the lower base when viewed from the side. A through hole 11a is provided that functions as a lightening hole. The left and right side frames 11 are connected by a front frame 12 near the front upper end and connected by a rear frame 13 slightly below the rear upper end. A ladder-like wire frame 15 is arranged between the front frame 12 and the rear frame 13 as a bridge. The wire frame 15 has a function of supporting the cushion pad 2p from below. A substantially triangular plate-shaped lower arm member 14 having a base on the lower side in a side view is attached by bolting to the upper rear end portions of the left and right side frames 11 . A lower end portion of a back frame 30 is attached to the upper end portion side of each lower arm member 14 via a recliner 16 . This allows the back frame 30 to change the tilt angle in the front-rear direction with respect to the cushion frame 10 . Slightly above the front lower ends of the left and right side frames 11 are provided cylindrical shaft holes 11b penetrating in the left-right direction. A cylindrical front pipe hole 11c and a rear pipe hole 11d penetrating in the left-right direction are provided in the vicinity of the rear lower end portions of the left and right side frames 11 so as to be aligned in the front-rear direction. The front pipe hole 11c and the rear pipe hole 11d have the same diameter and are set slightly larger than the outer diameter of the cylindrical outer pipe member 51. As shown in FIG.

As shown in FIGS. 1 to 4, the front lower ends of the left and right side frames 11 are attached to the front end sides of the upper rails 4b of the slide rails 4 via the front brackets . The rear lower ends of the left and right side frames 11 are attached to the rear end sides of the upper rails 4 b of the slide rails 4 via the rear brackets 19 . The front bracket 18 is formed to have a substantially U-shape with a cross section opening toward the rear and extending in the vertical direction. A threaded hole 18a is provided in the upper portion of the front bracket 18 and penetrates in the left-right direction, and a threaded portion 20a of a front truss bolt 20 is inserted through the screw hole 18a. is provided with a screw hole 18b through which the . The front truss bolt 20 has a threaded portion 20a and a head portion 20b. The rear bracket 19 is formed to have a substantially U-shaped cross section that is open forward and extends in the vertical direction. A front threaded hole 19a and a rear threaded hole 19b are provided side by side in the upper portion of the rear bracket 19 so as to penetrate in the left-right direction and through which the threaded portion 21a of the rear truss bolt 21 is passed. The rear truss bolt 21 has a threaded portion 21a and a head portion 21b. The lower portion of the rear bracket 19 is provided with a threaded hole (not shown) that penetrates in the front-rear direction and through which a threaded portion of a bolt (not shown) is passed. The inner diameters of the front threaded hole 19a and the rear threaded hole 19b are slightly larger than the outer diameter of the threaded portion 21a of the rear truss bolt 21, and the threaded portion 21a of the rear truss bolt 21 passes through the front threaded hole 19a and the rear threaded hole 19b. It is set so that there is almost no gap in the radial direction. A pair of left and right slide rails 4 are arranged on the floor F to extend in the front-rear direction. Specifically, each slide rail 4 is composed of a lower rail 4a fixed to the floor F side and an upper rail 4b slidably assembled to the lower rail 4a in the longitudinal direction.

As shown in FIGS. 1 to 3, a front bracket 18 is provided at the front lower ends of the left and right side frames 11 with the shaft hole 11b aligned with the screw hole 18a, and the threaded portion 20a of the front truss bolt 20 is passed through the nut 22. is installed by tightening the The lower portion of the front bracket 18 is fixed to the upper rail 4b by threading the threaded portion of a bolt through the screw hole 18b and tightening the front end portion of the upper rail 4b. As a result, the left and right side frames 11 are rotatably attached to the upper rail 4b about the threaded portion 20a of the front truss bolt 20. As shown in FIG. At this time, the inner diameter of the shaft hole 11b and the inner diameter of the threaded hole 18a are only slightly larger than the outer diameter of the threaded portion 20a of the front truss bolt 20, so that the front ends of the left and right side frames 11 are positioned at the front ends of the left and right upper rails 4b. There is almost no movement in the front, back, up and down directions with respect to the side. Further, since each side frame 11 is sandwiched by each front bracket 18 without a gap and is fastened by the threaded portion 20a of the front truss bolt 20 and the nut 22, the left and right side frames 11 are horizontally mounted with respect to the left and right upper rails 4b. rarely move to

As shown in FIGS. 1, 2 and 4, vibration suppressing mechanisms 50 are inserted into the front pipe holes 11c and the rear pipe holes 11d at the rear lower end portions of the left and right side frames 11, respectively. The vibration suppression mechanism 50 has an outer pipe member 51 , an inner pipe member 52 , and a rubber member 53 arranged between the outer pipe member 51 and the inner pipe member 52 . The outer pipe member 51 has a cylindrical shape with an annular flange portion 51a at one end in the axial direction. Its outer diameter is slightly smaller than the inner diameter of the rear pipe hole 11d. It is formed slightly smaller than the interval between the left and right wall surfaces of 19 . The inner pipe material 52 is formed as a large diameter portion 52a having a large outer diameter at both ends in the axial direction and as a small diameter portion 52b having a small outer diameter at the central portion. The inner pipe material 52 is formed to have an inner diameter slightly larger than the outer diameter of the threaded portion 21 a of the rear truss bolt 21 . The axial length of the inner pipe member 52 is substantially equal to the interval between the left and right wall surfaces of the rear bracket 19, and the axial length of the small diameter portion is shorter than the axial length of the outer pipe member 51. . The rubber member 53 is made of an elastic material such as elastomer or hard rubber, and has a cylindrical shape whose axial length is substantially equal to the axial length of the small-diameter portion 52b. The outer diameter of the rubber member 53 is substantially equal to the inner diameter of the outer pipe member 51, and the inner diameter of the rubber member 53 is substantially equal to the outer diameter of the small diameter portion 52b. The vibration suppression mechanism 50 is configured by coaxially arranging an outer pipe member 51, a rubber member 53, and an inner pipe member 52 in this order. A specific manufacturing method is to inject the raw material of the rubber member 53 into the gap between the outer pipe member 51 and the inner pipe member 52 arranged coaxially, and to mold and harden the raw material. In the vibration suppression mechanism 50, the small diameter portion 52b of the inner pipe member 52 faces the inner diameter surface of the outer pipe member 51 via the rubber member 53, and the large diameter portion 52a of the inner pipe member 52 directly faces the outer pipe member 51. It faces the inner diameter surface. The radial distance between the outer diameter surface of the small diameter portion 52b and the inner diameter surface of the outer pipe member 51 is set larger than the radial distance between the outer diameter surface of the large diameter portion 52a and the inner diameter surface of the outer pipe member 51. It is Here, the outer pipe material 51, the inner pipe material 52, and the rubber member 53 respectively correspond to the "first member", the "second member", and the "elastic member" in the claims. A portion of the inner diameter surface of the outer pipe material 51 where the outer diameter surface of the large diameter portion 52a and the outer diameter surface of the large diameter portion 52a face each other corresponds to the "narrow ring portion" in the claims. Further, the radial distance between the outer diameter surface of the large diameter portion 52a and the inner diameter surface of the outer pipe material 51 corresponds to the "predetermined value" in the claims.

The central axis of the inner diameter portion of the inner pipe material 52 in the front side vibration suppressing mechanism 50 is aligned with the central axis of the front threaded hole 19a of the rear bracket 19, and the threaded portion 21a of the rear truss bolt 21 is passed through and the nut 22 is tightened. Also, the central axis of the inner diameter portion of the inner pipe material 52 in the rear side vibration suppressing mechanism 50 is aligned with the central axis of the rear threaded hole 19b of the rear bracket 19, and the threaded portion 21a of the rear truss bolt 21 is passed through and the nut 22 is tightened. tighten. By this tightening, the front and rear inner pipe members 52 are joined in a state of being abutted between the left and right upright plate portions of the rear bracket 19 respectively. As a result, the left and right side frames 11 are assembled to the rear bracket 19 via the front and rear vibration suppression mechanisms 50, respectively. As a result, due to deformation of the rubber member 53, the rear end sides of the left and right side frames 11 can slightly move in the front, rear, up and down directions with respect to the rear end sides of the upper rails 4b. However, the movement of the left and right side frames 11 in the front, rear, left, and right directions with respect to the upper rail 4b is restricted by the front truss bolt 20 and the nut 22 connected via the front bracket 18, as described above. Only small movements are allowed. As a result, vertical vibrations applied to the vehicle seat 1 from the floor F are absorbed by the deformation of the rubber member 53 when the left and right side frames 11 are rotated around the threaded portions 20a of the front truss bolts 20 . At this time, the left and right side frames 11 do not move in the front, rear, left, and right directions.

As shown in FIGS. 1 and 2, the seat back 3 has a back frame 30 forming a skeleton, a back pad 3p as a cushion material, and a back cover 3c as a skin material. The back frame 30 includes a pair of left and right side frames 31 extending in the vertical direction, an upper frame 32 extending in the horizontal direction connecting the side frames 31 at the upper end side, and a left and right frame connecting the side frames 31 at the center in the vertical direction. and a middle frame 33 extending in the direction. Further, the back frame 30 has a horizontally extending lower frame 34 connecting the side frames 31 at their lower ends, and a pair of left and right upper arm members 35 attached to the lower ends of the side frames 31 . The pair of left and right upper arm members 35 are attached to the pair of left and right lower arm members 14 of the cushion frame 10 via recliners 16 . A retractor 40 for retracting and storing a seat belt 41 is attached to a retractor bracket 33a attached to the center of the middle frame 33 in the left-right direction so as to extend upward. The seat belt 41 let out from the retractor 40 is supported in a folded manner on the upper surface portion 36a of the belt support portion 36 attached to the upper right end portion of the upper frame 32, and extends toward the front side of the seated occupant's body (not shown). placed. When a large tension force is applied to the seat belt 41 from the body of the seated occupant in the event of an automobile collision, etc., the upper surface portion 36a of the belt support portion 36 is subjected to a forward and downward tensile force. This tensile force causes the left and right side frames 11 to rotate about the threaded portions 20a of the front truss bolts 20 so that the rear ends thereof face upward, and the rubber members 53 of the front and rear vibration suppression mechanisms 50 are deformed. At this time, as shown in FIGS. 2 and 4, the left and right side frames 11 are at most the outer diameter surface of the large diameter portion 52a of the inner pipe member 52 and the outer pipe member 51 with respect to the threaded portion 21a of the rear truss bolt 21. It only rises by the distance in the radial direction from the inner diameter surface, and hardly moves in the front-rear direction. As a result, the forward movement distance of the upper surface portion 36a of the belt support portion 36 can be suppressed to be substantially only due to the forward bending of the back frame 30, and can be reduced.

The present embodiment configured as described above has the following effects. Rear lower ends of the left and right side frames 11 are attached to rear brackets 19 attached to the slide rails 4 via front and rear vibration suppression mechanisms 50 . As a result, the vibration applied from the floor F to the automobile seat 1 due to the elastic deformation of the rubber member 53 can be reduced, and the ride comfort can be improved. On the other hand, when a large load is applied from the seat belt 41 to the automobile seat 1 due to an automobile collision or the like, the outer diameter surface of the large-diameter portion 52a of the inner pipe member 52 in the vibration suppressing mechanism 50 becomes the inner diameter of the outer pipe member 51. It abuts against the surface to receive the load and prevent further elastic deformation of the rubber member 53 . As a result, the amount of movement of the automobile seat 1 with respect to the floor F can be suppressed. That is, the vibration suppression mechanism 50 has a simple structure that does not require separate members other than the outer pipe member 51, the inner pipe member 52, and the rubber member 53, and reduces the vibration applied to the automobile seat 1 from the floor F. It is possible to reduce the amount of movement of the automobile seat 1 when a large load is applied.

The outer pipe member 51 has a shorter axial length than the inner pipe member 52, and the inner diameter surfaces of both axial ends of the outer pipe member 51 face the outer diameter surfaces of the large diameter portions 52a of the inner pipe member 52, respectively. are doing. As a result, when a large load is applied to the outer pipe member 51 to approach the inner pipe member 52 in the radial direction, both ends of the outer pipe member 51 are prevented from approaching the inner pipe member 52 by a predetermined value or more. Therefore, the outer pipe member 51 and the inner pipe member 52 can be brought into contact with each other while being parallel to each other in the axial direction.

Furthermore, since the cushion frame 10 is supported on the front side by the upper rail 4b so as to be rotatable in the vertical direction with respect to the floor F around the threaded portion 20a of the front truss bolt 20, movement in the front-rear direction with respect to the floor F is restricted. ing. Also, the cushion frame 10 is connected to the rear bracket 19 via the vibration suppression mechanism 50 at the front pipe hole 11c and the rear pipe hole 11d. As a result, the vibration suppression mechanism 50 can absorb and suppress the vertical vibration of the cushion frame 10 caused by the vertical rotation about the threaded portion 20a of the front truss bolt 20 with respect to the upper rail 4b. That is, the automobile seat 1 eliminates movement in the front-rear direction with respect to the floor F to suppress the occurrence of discomfort, and reduces vertical vibrations among the vibrations applied to the automobile seat 1 from the floor F to provide a comfortable ride. can be improved.

FIG. 5 shows a second embodiment of the invention. The difference from the first embodiment is that the front lower ends of the left and right side frames 11 are attached to the front bracket 18 via the vibration suppression mechanism 50 . Other parts are the same as in the first embodiment. About the structure which overlaps with the said 1st Embodiment, the same code|symbol is attached|subjected to drawing and description is abbreviate|omitted. Slightly above the front lower ends of the left and right side frames 11 are provided cylindrical shaft holes 11e penetrating in the left-right direction. The inner diameter of the shaft hole 11e is the same as the inner diameter of the front pipe hole 11c and the inner diameter of the rear pipe hole 11d. With the vibration suppression mechanism 50 inserted into the shaft hole 11e, the left and right shaft holes 11b of the front bracket 18 are aligned with the inner diameter surface of the inner pipe member 52 of the vibration suppression mechanism 50, and the threaded portion 20a of the front truss bolt 20 is installed. It is attached by tightening the nut 22 through the .

The present embodiment configured as described above has the following effects. Since the front lower ends of the left and right side frames 11 are also attached to the front brackets 18 attached to the slide rails 4 via the vibration suppressing mechanism 50, the front lower ends of the left and right side frames 11 are also attached to the floor F. Therefore, the vibration applied to the automobile seat 1 can be reduced, and the ride comfort can be improved. When a large load is applied from the seat belt 41 to the automobile seat 1 due to an automobile collision or the like, the outer diameter surface of the large-diameter portion 52a of the inner pipe member 52 in the vibration suppressing mechanism 50 becomes the inner diameter of the outer pipe member 51. It abuts against the surface to receive the load and prevent further elastic deformation of the rubber member 53 . As a result, the amount of movement of the automobile seat 1 with respect to the floor F can be suppressed. In addition, unlike the first embodiment, movement in the front-rear direction with respect to the floor F cannot be eliminated.

FIG. 6 shows a third embodiment of the invention. The difference from the first embodiment is that the rear lower ends of the left and right side frames 11 are attached to the rear bracket 19 via the vibration suppression mechanism 60 . Other parts are the same as in the first embodiment. About the structure which overlaps with the said 1st Embodiment, the same code|symbol is attached|subjected to drawing and description is abbreviate|omitted. The vibration suppression mechanism 60 has an outer pipe member 61 , an inner pipe member 62 , and a rubber member 63 arranged between the outer pipe member 61 and the inner pipe member 62 . The outer pipe material 61 differs from the outer pipe material 51 only in that the length in the axial direction is slightly shorter. The outer pipe member 61 has a cylindrical shape with an annular flange portion 61a at one end in the axial direction. Its outer diameter is slightly smaller than the inner diameter of the rear pipe hole 11d. It is formed slightly smaller than the interval between the vertical walls 62a of the material 62. As shown in FIG. The other end portion 61b is the end portion of the outer pipe member 61 opposite to the flange portion 61a in the axial direction. The inner pipe material 62 has vertical walls 62a extending in the radial direction at both ends, and is formed in a curved shape that gradually bulges in the radial direction so that the outer diameter of the portion between the vertical walls 62a becomes larger at the center in the left-right direction. . A large-diameter portion 62b is formed at the central portion in the left-right direction where the outer diameter is the largest, and a small-diameter portion 62c is formed at the base of the standing wall 62a. This curve can be an arc. Further, the inner pipe member 62 has an inner diameter slightly larger than the outer diameter of the threaded portion 21 a of the rear truss bolt 21 . The length of the inner pipe material 62 in the axial direction is formed substantially equal to the interval between the left and right upright plate portions of the rear bracket 19 . The rubber member 63 is made of an elastic material such as elastomer or hard rubber, and its axial length is approximately equal to the axial length of the outer pipe member 61, and its thickness is reduced at the central portion in the left-right direction. It has a cylindrical shape. The outer diameter of the rubber member 63 is approximately equal to the inner diameter of the outer pipe member 61 , and the inner diameter surface of the rubber member 63 is in close contact with the outer diameter surface of the inner pipe member 62 . The vibration suppression mechanism 60 is configured by coaxially arranging an outer pipe member 61, a rubber member 63, and an inner pipe member 62 in this order. A specific manufacturing method is to inject the raw material of the rubber member 63 into the gap between the outer pipe material 61 and the inner pipe material 62 arranged coaxially, and to mold and harden the material. In the vibration suppressing mechanism 60, the large diameter portion 62b of the inner pipe member 62 faces the inner diameter surface of the outer pipe member 61 with the rubber member 63 interposed therebetween. The outer surface of the flange portion 61a of the outer pipe member 61 and the end surface of the other end portion 61b face the inner surface of the vertical wall 62a of the inner pipe member 62 with a slight gap therebetween. As a result, when the outer pipe member 61 attempts to move laterally relative to the inner pipe member 62, the upright wall 62a and the flange portion 61a or the upright wall 62a and the other end portion 61b come into contact with each other to suppress the amount of movement. ing. Here, the outer pipe member 61, the inner pipe member 62 and the rubber member 63 respectively correspond to the "first member", the "second member" and the "elastic member" in the claims. A portion of the inner diameter surface of the outer pipe member 61 where the outer diameter surface of the large diameter portion 62b faces the outer diameter surface of the large diameter portion 62b corresponds to the "narrow ring portion" in the claims. Furthermore, when a large load is applied and the rubber member 63 between the outer diameter surface of the large diameter portion 62b and the inner diameter surface of the outer pipe member 61 is crushed, the outer diameter surface of the large diameter portion 62b and the outer pipe member 61 are crushed. corresponds to the "predetermined value" in claims. In addition, the upright wall 62a and the flange portion 61a, and the upright wall 62a and the other end portion 61b correspond to the "restriction mechanism" in the claims.

The center axis of the inner diameter portion of the inner pipe material 62 in the front side vibration suppression mechanism 60 is aligned with the center axis of the front threaded hole 19a of the rear bracket 19, and the threaded portion 21a of the rear truss bolt 21 is passed through and the nut 22 is tightened. Also, the central axis of the inner diameter portion of the inner pipe material 62 in the rear side vibration suppressing mechanism 60 is aligned with the central axis of the rear threaded hole 19b of the rear bracket 19, and the threaded portion 21a of the rear truss bolt 21 is passed through and the nut 22 is tightened. tighten. By this tightening, the front and rear inner pipe members 62 are joined in a state of being abutted between the left and right upright plate portions of the rear bracket 19 respectively. As a result, the left and right side frames 11 are assembled to the rear bracket 19 via the front and rear vibration suppression mechanisms 60, respectively. As a result, the rear end sides of the left and right side frames 11 are made slightly movable in the longitudinal and vertical directions with respect to the rear end sides of the upper rails 4b due to the deformation of the rubber member 63 . However, the movement of the left and right side frames 11 in the front, rear, left, and right directions with respect to the upper rail 4b is restricted by the front truss bolt 20 and the nut 22 connected via the front bracket 18, as described above. Only small movements are allowed. As a result, the vertical vibration applied to the vehicle seat 1 from the floor F is absorbed by the deformation of the rubber member 63 when the left and right side frames 11 are rotated around the threaded portions 20a of the front truss bolts 20 . At this time, the left and right side frames 11 do not move in the front, rear, left, and right directions.

When a large tension force is applied to the seat belt 41 from the body of the seated occupant in the event of an automobile collision, etc., the upper surface portion 36a of the belt support portion 36 is subjected to a forward and downward tensile force. This tensile force causes the left and right side frames 11 to rotate about the threaded portions 20a of the front truss bolts 20 so that the rear ends thereof face upward, and the rubber members 63 of the front and rear vibration suppression mechanisms 60 are deformed. At this time, as shown in FIGS. 2 and 6, the left and right side frames 11 are applied with a large maximum load to the threaded portion 21a of the rear truss bolt 21, and the outer diameter surface of the large diameter portion 62b and the outer pipe member 61 are separated from each other. When the rubber member 63 between the inner diameter surface of the large-diameter portion 62b and the inner diameter surface of the outer pipe member 61 is crushed, it rises only by the radial distance between the outer diameter surface of the large diameter portion 62b and the inner diameter surface of the outer pipe member 61, and hardly moves in the front-rear direction. . As a result, the forward movement distance of the upper surface portion 36a of the belt support portion 36 can be suppressed to be substantially only due to the forward bending of the back frame 30, and can be reduced. At this time, it is conceivable that the deformation of the rubber member 63 is not uniform on the left and right sides in the axial direction, and the axial direction of the outer pipe member 61 is inclined with respect to the axial direction of the inner pipe member 62 . In such a case, the upright wall 62a and the flange portion 61a or the opposite end of the upright wall 62a and the flange portion 61a abut to suppress the amount of movement of the outer pipe member 61 in the left-right direction with respect to the inner pipe member 62. can be done.

The present embodiment configured as described above has the following effects. Rear lower ends of the left and right side frames 11 are attached to rear brackets 19 attached to the slide rails 4 via front and rear vibration suppression mechanisms 60 . As a result, the vibration applied from the floor F to the automobile seat 1 due to the elastic deformation of the rubber member 63 can be reduced, and the ride comfort can be improved. On the other hand, when a large load is applied from the seat belt 41 to the automobile seat 1 due to an automobile collision or the like, the outer diameter surface of the large-diameter portion 62b of the inner pipe member 62 in the vibration suppressing mechanism 60 becomes the inner diameter of the outer pipe member 61. The load is received by approaching via the rubber member 63 crushed to the surface, and further elastic deformation of the rubber member 63 is prevented. As a result, the amount of movement of the automobile seat 1 with respect to the floor F can be suppressed. That is, the vibration suppression mechanism 60 has a simple structure that does not require separate members other than the outer pipe member 61, the inner pipe member 62, and the rubber member 63, and reduces the vibration applied to the automobile seat 1 from the floor F. It is possible to reduce the amount of movement of the automobile seat 1 when a large load is applied. Furthermore, even if the deformation of the rubber member 63 is not uniform on the left and right sides in the axial direction, the standing wall 62a and the flange portion 61a or the standing wall 62a and the other end portion 61b come into contact with each other, so that the outer pipe member with respect to the inner pipe member 62 is deformed. The amount of movement of 61 in the horizontal direction can be suppressed.

FIG. 7 shows a fourth embodiment of the invention. The difference from the first embodiment is that the rear lower ends of the left and right side frames 11 are attached to the rear bracket 19 via the vibration suppression mechanism 70 . Other parts are the same as in the first embodiment. About the structure which overlaps with the said 1st Embodiment, the same code|symbol is attached|subjected to drawing and description is abbreviate|omitted. The vibration suppression mechanism 70 has an outer pipe member 71 , an inner pipe member 72 , and a rubber member 73 arranged between the outer pipe member 71 and the inner pipe member 72 . The outer pipe member 71 has a substantially cylindrical shape with an annular flange portion 71a at one end in the axial direction. Its outer diameter is slightly smaller than the inner diameter of the rear pipe hole 11d. It is formed slightly smaller than the interval between the standing walls 72a of the pipe material 72. As shown in FIG. The other end portion 71d is the end portion of the outer pipe member 61 opposite to the flange portion 71a in the axial direction. The inner diameter of the outer pipe material 71 is formed in a curved shape gradually recessed in the radial direction so that it is large at both ends in the axial direction and small at the central portion in the left-right direction. A small inner diameter portion 71b is formed at the central portion in the left-right direction where the outer diameter is the smallest, and both ends are formed as large inner diameter portions 71c. This curve can be an arc. The inner pipe material 72 has standing walls 72a extending in the radial direction at both ends, and the outer diameter of the portion between the standing walls 72a is formed to be constant. Also, the inner pipe material 72 is formed to have an inner diameter slightly larger than the outer diameter of the threaded portion 21 a of the rear truss bolt 21 . The axial length of the inner pipe material 72 is formed substantially equal to the interval between the left and right upright plate portions of the rear bracket 19 . The rubber member 73 is made of an elastic material such as elastomer or hard rubber, and its axial length is substantially equal to the axial length of the outer pipe member 71, and its thickness is reduced at the central portion in the left-right direction. It has a cylindrical shape. The outer diameter surface of the rubber member 73 is in close contact with the inner diameter surface of the outer pipe member 71 , and the inner diameter of the rubber member 73 is substantially equal to the outer diameter of the inner pipe member 72 . The vibration suppression mechanism 70 is configured by coaxially arranging an outer pipe member 71, a rubber member 73, and an inner pipe member 72 in this order. A specific manufacturing method is to inject the raw material of the rubber member 73 into the gap between the outer pipe material 71 and the inner pipe material 72 arranged coaxially, and to mold and harden the material. In the vibration suppression mechanism 70, the inner small diameter portion 71b of the outer pipe member 71 faces the outer diameter surface of the inner pipe member 72 with the rubber member 73 interposed therebetween. The outer surface of the flange portion 71a of the outer pipe member 71 and the end surface of the other end portion 71d of the flange portion 71a are opposed to the inner surface of the vertical wall 72a of the inner pipe member 72 with a slight gap therebetween. . As a result, when the outer pipe member 71 attempts to move in the lateral direction relative to the inner pipe member 72, the vertical wall 72a and the flange portion 71a or the vertical wall 72a and the other end portion 71d come into contact with each other to suppress the amount of movement. ing. Here, the outer pipe member 71, the inner pipe member 72 and the rubber member 73 respectively correspond to the "first member", the "second member" and the "elastic member" in the claims. Further, the portion of the outer diameter surface of the inner pipe material 72 where the inner diameter surface of the inner small diameter portion 71b and the inner diameter surface of the inner small diameter portion 71b face each other corresponds to the "narrow ring portion" in the claims. Furthermore, when a large load is applied and the rubber member 73 between the outer diameter surface of the inner small diameter portion 71b and the outer diameter surface of the inner pipe member 72 is crushed, the outer diameter surface of the inner small diameter portion 71b and the inner pipe member are crushed. The radial distance from the outer diameter surface of 72 corresponds to the "predetermined value" in the claims. In addition, the upright wall 72a and the flange portion 71a, and the upright wall 72a and the other end portion 71d correspond to the "restriction mechanism" in the claims.

The central axis of the inner diameter portion of the inner pipe material 72 in the front side vibration suppressing mechanism 70 is aligned with the central axis of the front threaded hole 19a of the rear bracket 19, and the threaded portion 21a of the rear truss bolt 21 is passed through and the nut 22 is tightened. Also, the central axis of the inner diameter portion of the inner pipe member 72 in the rear side vibration suppressing mechanism 70 is aligned with the central axis of the rear threaded hole 19b of the rear bracket 19, and the threaded portion 21a of the rear truss bolt 21 is passed through and the nut 22 is tightened. tighten. By this tightening, the front and rear inner pipe members 72 are joined in a state of being abutted between the left and right standing plate portions of the rear bracket 19 respectively. As a result, the left and right side frames 11 are assembled to the rear bracket 19 via the front and rear vibration suppression mechanisms 70, respectively. As a result, the rear end sides of the left and right side frames 11 are made slightly movable in the longitudinal and vertical directions with respect to the rear end sides of the upper rails 4b due to the deformation of the rubber member 73 . However, the movement of the left and right side frames 11 in the front, rear, left, and right directions with respect to the upper rail 4b is restricted by the front truss bolt 20 and the nut 22 connected via the front bracket 18, as described above. Only small movements are allowed. As a result, vertical vibrations applied to the vehicle seat 1 from the floor F are absorbed by the deformation of the rubber member 73 when the left and right side frames 11 are rotated around the threaded portions 20a of the front truss bolts 20 . At this time, the left and right side frames 11 do not move in the front, rear, left, and right directions.

When a large tension force is applied to the seat belt 41 from the body of the seated occupant in the event of an automobile collision, etc., the upper surface portion 36a of the belt support portion 36 is subjected to a forward and downward tensile force. This tensile force causes the left and right side frames 11 to rotate about the threaded portions 20a of the front truss bolts 20 so that the rear ends thereof face upward, and the rubber members 73 of the front and rear vibration suppression mechanisms 70 are deformed. At this time, as shown in FIGS. 2 and 7, the left and right side frames 11 are applied with a large maximum load to the threaded portion 21a of the rear truss bolt 21, and the outer diameter surface of the inner pipe member 72 and the outer pipe member 71 are separated from each other. When the rubber member 73 between the inner small diameter portion 71b of the inner pipe member 72 and the inner small diameter portion 71b of the outer pipe member 71 is crushed, the rubber member 73 rises only by the distance in the radial direction between the outer diameter surface of the inner pipe member 72 and the inner small diameter portion 71b of the outer pipe member 71. hardly move. As a result, the forward movement distance of the upper surface portion 36a of the belt support portion 36 can be suppressed to be substantially only due to the forward bending of the back frame 30, and can be reduced. At this time, it is conceivable that the deformation of the rubber member 73 is not uniform on the left and right sides in the axial direction, and the axial direction of the outer pipe member 71 is inclined with respect to the axial direction of the inner pipe member 72 . In such a case, the upright wall 72a and the flange portion 71a or the upright wall 72a and the other end portion 71d contact each other, so that the lateral movement of the outer pipe member 71 with respect to the inner pipe member 72 can be suppressed.

The present embodiment configured as described above has the following effects. Rear lower ends of the left and right side frames 11 are attached to rear brackets 19 attached to the slide rails 4 via front and rear vibration suppression mechanisms 70 . As a result, the vibration applied from the floor F to the automobile seat 1 due to the elastic deformation of the rubber member 73 can be reduced, and the ride comfort can be improved. On the other hand, when a large load is applied from the seat belt 41 to the automobile seat 1 due to an automobile collision or the like, the outer diameter surface of the inner small-diameter portion 71b of the outer pipe member 71 in the vibration suppressing mechanism 70 is pushed outside the inner pipe member 72. It approaches via the rubber member 73 crushed to the radial surface, receives the load, and prevents further elastic deformation of the rubber member 73 . As a result, the amount of movement of the automobile seat 1 with respect to the floor F can be suppressed. That is, the vibration suppression mechanism 70 has a simple structure that does not require separate members other than the outer pipe member 71, the inner pipe member 72, and the rubber member 73, and reduces the vibration applied to the automobile seat 1 from the floor F. It is possible to reduce the amount of movement of the automobile seat 1 when a large load is applied. Furthermore, even if the deformation of the rubber member 73 is not uniform on the left and right sides in the axial direction, the vertical wall 72a and the flange portion 71a or the vertical wall 72a and the other end portion 71d of the flange portion 71a come into contact with each other. It is possible to suppress the amount of lateral movement of the outer pipe member 71 relative to the .

Although specific embodiments have been described above, the present invention is not limited to those configurations, and various modifications, additions, and deletions are possible without changing the gist of the present invention. For example:

1. In the first embodiment and the second embodiment, in the vibration suppressing mechanism 50, there is a gap between the outer diameter surface of the large diameter portion 52a and the inner diameter surface of the outer pipe member 51 facing the outer diameter surface of the large diameter portion 52a. is configured so that the rubber member 53 is not arranged. However, the configuration is not limited to this, and the rubber member 53 is arranged between the outer diameter surface of the large diameter portion 52a and the inner diameter surface of the outer pipe member 51 facing the outer diameter surface of the large diameter portion 52a. good too.

2. In the third embodiment, the front lower ends of the left and right side frames 11 are rotatably attached to the upper rail 4b about the threaded portion 20a of the front truss bolt 20. As shown in FIG. However, the present invention is not limited to this, and the front lower ends of the left and right side frames 11 may be attached to the front bracket 18 via the vibration suppression mechanism 60 . Thereby, the same effects as those of the second embodiment can be obtained.

3. In the fourth embodiment, the front lower ends of the left and right side frames 11 are rotatably attached to the upper rail 4b about the threaded portion 20a of the front truss bolt 20. As shown in FIG. However, the present invention is not limited to this, and the front lower ends of the left and right side frames 11 may be attached to the front bracket 18 via the vibration suppression mechanism 70 . Thereby, the same effects as those of the second embodiment can be obtained.

4. In the above embodiment, the case where the present invention is applied to the automobile seat 1 has been described, but the present invention is not limited to this and may be applied to seats mounted on ships, trains, airplanes, etc. other than automobiles. .

1 Automotive seat (vehicle seat)
2 seat cushion 10 cushion frame 11 side frame 50 vibration suppression mechanism 51 outer pipe material (first member)
52 inner pipe material (second member)
52a large diameter portion 53 rubber member (elastic member)
60 Vibration suppression mechanism 61 Outer pipe material (first member)
61a flange portion (restriction mechanism)
61b other end (restriction mechanism)
62 inner pipe material (second member)
62a Standing wall (regulatory mechanism)
62b large diameter portion 63 rubber member (elastic member)
70 Vibration suppression mechanism 71 Outer pipe material (first member)
71a flange portion (restriction mechanism)
71d other end (restriction mechanism)
72 inner pipe material (second member)
72a Standing wall (regulating mechanism)
71b inner small diameter portion 73 rubber member (elastic member)
F floor (vehicle floor)

Claims (4)

A vibration suppressing mechanism for a vehicle seat disposed between a cushion frame forming a skeleton of a seat cushion and a vehicle floor,
The vibration suppression mechanism is formed by coaxially arranging a large-diameter substantially cylindrical first member and a small-diameter substantially cylindrical second member with an elastic member interposed therebetween,
A narrow ring portion is formed in which a part of the first member and/or the second member approaches in a radial direction to narrow the distance between the first member and the second member,
wherein the first member is directly or indirectly connected to either the cushion frame or the vehicle floor;
the second member is connected to the other of the cushion frame different from the one or the vehicle floor;
The narrow ring portion is a vibration suppression mechanism for a vehicle seat that suppresses approaching of the first member and the second member by a predetermined value or more when a large radial load is applied to the vibration suppression mechanism. 2. The vehicle seat vibration suppression mechanism according to claim 1, wherein the first member is shorter in axial length than the second member, and the narrow ring portions are provided at both ends of the first member in the axial direction. . 2. The vehicle seat vibration suppressing mechanism according to claim 1, wherein the first member is shorter in the axial direction than the second member, and the narrow ring portion is provided in the axial center portion of the first member. . 4. A regulating mechanism according to claim 2 or 3, wherein a regulating mechanism for regulating the axial movement distance of said first member with respect to said cushion frame or said vehicle floor to a predetermined value or less is directly attached to said cushion frame or said vehicle floor. Or a vibration suppression mechanism for a vehicle seat that is indirectly arranged.

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