JP5692205B2 - Headrest support structure - Google Patents

Description

  The present invention relates to a headrest support structure that elastically supports a headrest on a seat back.

  For the purpose of reducing the fuel consumption of the vehicle, the engine rotational speed is decreasing at the time of idling of the engine. As a result, the frequency range of engine vibration during idling includes the resonance frequency of the vehicle seat, which leads to a decrease in drivability. Therefore, in recent years, the development of a seat that attenuates vibration in the front-rear direction of the seat by swinging the headrest relative to the seat back in the front-rear direction when an excitation force is transmitted to the seat has been advanced. ing.

  Patent Document 1 discloses an example of a headrest support structure that elastically supports a headrest on a seat back. The support structure includes a cylindrical bracket provided on the seat back and a support member that supports a tip portion of the headrest stay that protrudes from the headrest, and the support member tilts in the front-rear direction in the accommodation chamber of the bracket. Is housed in a possible state. In addition, springs are respectively provided at two different positions in the prescribed direction in which the headrest stay extends between the outer surface of the support member and the inner surface of the bracket. When the excitation force is transmitted to the seat, the headrest swings relative to the seat back around the fulcrum set between the springs in the specified direction, and the seat vibration is attenuated. It is like that.

JP 2011-207335 A JP 2011-201526 A

  In the above support structure, the position of the fulcrum serving as the swing center of the headrest in the specified direction can be displaced due to individual differences in the characteristics of the pair of springs, attachment errors of the springs, and the like. Therefore, variations tend to occur in the vibration damping characteristics of the sheet.

  As a method for solving such a problem, for example, as described in Patent Document 2, a support shaft that protrudes in the vehicle width direction is provided on the support member, and a support portion that rotatably supports the support shaft is provided on the bracket. Is mentioned. In this case, by attaching the support member to the bracket so that the support shaft is supported by the support portion, the headrest swings in the front-rear direction with the support shaft as a fulcrum. As a result, variations in the position of the fulcrum in the prescribed direction can be suppressed, and variations in the vibration damping characteristics of the seat can be suppressed. However, the provision of the support shaft and the support portion causes a new problem that the configuration of the support member and the bracket is complicated.

  An object of the present invention is to provide a headrest support structure that can suppress variations in damping characteristics of vibrations generated in a seat with a simple configuration.

Hereinafter, means for solving the above-described problems and the effects thereof will be described.
The headrest support structure includes a support member that supports a protruding member that protrudes from the headrest, and a bracket that is provided on the seat back and includes a storage chamber in which the support member is accommodated so as to be tiltable in the front-rear direction. The accommodation chamber is provided with a spring that expands and contracts according to the tilt of the support member in the front-rear direction with respect to the bracket, and one of the outer surface of the support member and the inner side surface of the bracket that faces each other protrudes in the front-rear direction. The portion is provided at a position different from the spring in the specified direction orthogonal to both the front-rear direction and the width direction of the headrest.

  The support member that supports the headrest via the projecting member tilts in the front-rear direction with the convex portion serving as a fulcrum, regardless of individual differences in springs or spring mounting errors. For this reason, it is difficult for the headrest to be displaced from the center of swing when the headrest swings in the front-rear direction relative to the seat back. For this reason, it is possible to suppress variations in the attenuation characteristics of vibration generated in the seat with a simple configuration.

  The convex portion may be provided at a position farther from the headrest in the specified direction than the spring, but is preferably provided at a position closer to the headrest in the specified direction than the spring. By adopting this configuration, as compared with the configuration in which the convex portion is located farther from the headrest in the specified direction than the spring, the convex portion which is the swing center of the headrest is closer to the headrest, so that the headrest is moved in the front-rear direction. The amount of displacement of the support member in the front-rear direction increases with respect to the rocking motion. As a result, the headrest can be swung in the front-rear direction even when the allowable amount of displacement of the support member in the front-rear direction is smaller than the configuration in which the protrusion is provided at a position farther from the headrest than the spring. It becomes difficult to narrow. As a result, it is possible to suppress a reduction in vibration damping characteristics.

  By the way, in the above-described headrest support structure, a spring may be disposed on one side in the front-rear direction of the projecting member, and a convex portion may be disposed on the other side in the front-rear direction of the projecting member. Then, a gap is filled between the outer surface of the support member and the inner surface of the bracket facing each other on one side in the front-rear direction of the protruding member, and on the opposite side of the spring sandwiching the convex portion in the specified direction. It is preferable to provide a filling. As a result, the expansion and contraction of the spring when the support member tilts to one side in the front-rear direction around the convex portion is smaller than that in the case where the gap member is positioned between the convex portion and the spring in the specified direction. As a result, the swing range of the headrest is increased. For this reason, the damping efficiency of the vibration of the sheet due to the transmitted excitation force can be increased.

  Furthermore, the gap between the outer side surface of the support member and the inner side surface of the bracket facing each other on the other side in the front-rear direction of the projecting member and filling the gap at a position closer to the spring than the convex portion in the specified direction It is preferable to provide a gap filling body. Thereby, the support rigidity of the headrest can be increased with respect to an impact from the other side in the front-rear direction to the headrest.

  Here, in order to set the resonance frequency of the seat low, it is preferable not only to lower the support rigidity of the headrest but also to increase the weight of the headrest that can be displaced with respect to the seat back that can be regarded as a rigid body. Therefore, in order to increase the weight of the headrest, a headrest in which a weight that is harder than the cushion material is embedded in the cushion material may be employed. Thus, the resonance frequency of the seat can be further lowered by increasing the weight of the headrest while lowering the support rigidity of the headrest.

  In the headrest support structure described above, it is preferable to arrange the spring so that the headrest can be urged rearward. According to this configuration, even if the head of the occupant seated on the seat collides with the headrest from the front, the spring does not contract, so that the swaying of the occupant's head in the front-rear direction can be suppressed.

The disassembled perspective view which shows the disassembled perspective structure about one Embodiment of a headrest support structure. Sectional drawing which shows the side cross-section of a headrest support and a support bracket. Sectional drawing which shows the same headrest support when a headrest displaces ahead, and the side part sectional structure of the periphery. The graph which shows the relationship between the displacement of a headrest, and the load which the displacement requires. (A) is a side view schematically showing a side structure of a vehicle seat, and (b) is a schematic diagram showing a spring-mass model for vibration in the front-rear direction of the seat. The schematic diagram which shows the headrest support structure of a 1st comparative example. The schematic diagram which shows the headrest support structure of one Embodiment. Sectional drawing which shows the side cross-section of a headrest support and a support bracket in the headrest support structure of another embodiment. Sectional drawing which shows the side cross-section of a headrest support and a support bracket in the headrest support structure of another embodiment. The disassembled perspective view which shows the disassembled perspective structure about the headrest support structure of another embodiment. The disassembled perspective view which shows the disassembled perspective structure about the headrest support structure of another embodiment.

  Hereinafter, an embodiment embodied in a headrest support structure for a seat mounted on a vehicle will be described with reference to FIGS. In the present embodiment, the side on which the head of the person seated on the seat is positioned with respect to the headrest is “front”, and the opposite direction is “rear”. Further, the specified direction perpendicular to both the vehicle width direction and the front-rear direction, which is also the width direction of the seat, is referred to as “vertical direction”.

  As shown in FIG. 1, a seat back 12 serving as a backrest of the seat 11 elastically supports a headrest 13 in a state where the seat back 12 can swing in the front-rear direction. The headrest 13 includes a shock absorbing cushion material 14, and a weight 15 formed of a material harder than the cushion material 14 (for example, a metal such as iron) is embedded in the cushion material 14. The headrest 13 is provided with a pair of headrest stays 16 as an example of a protruding member. The front end portions 161 of the headrest stays 16 are juxtaposed along the vehicle width direction and protrude from the headrest 13 toward the seat back 12.

  A seat back frame 17 that forms a skeleton of the seat back 12 is provided in the seat back 12, and two support brackets 18 are provided at an upper portion of the seat back frame 17 at intervals in the vehicle width direction. Each of these support brackets 18 is formed of a metal in a square cylinder shape, and is fixed to the seat back frame 17 by welding or the like.

  As shown in FIGS. 1 and 2, the internal space of the support bracket 18 is a storage chamber 181 that opens on the side facing the headrest 13 and on the opposite side (that is, both the upper and lower sides). A headrest support 19 as a support member made of synthetic resin is inserted from the upper opening. Then, the headrest 13 is elastically supported by the seat back frame 17 by inserting the tip portion 161 of the headrest stay 16 into the headrest support 19.

  The lower end portion of the headrest support 19 is formed to be tapered. The headrest support 19 is formed with a stay hole 191 penetrating in the vertical direction, and the tip portion 161 of the headrest stay 16 is inserted into the stay hole 191 from the upper opening thereof. In this embodiment, the tip portion 161 of the headrest stay 16 passes through the stay hole 191.

  A chevron-shaped convex portion 193 projecting forward is provided on the outer front surface 192 of the headrest support 19 so as to extend in the vehicle width direction. That is, the convex portion 193 protrudes from the outer peripheral surface 192 of the headrest support 19 facing each other toward the inner peripheral surface 182 of the support bracket 18. The tip of the convex portion 193 is in contact with the inner peripheral surface 182 of the support bracket 18.

  Further, a first bead 21 as another gap filling member is provided in front of the lower portion of the headrest support 19 to fill a gap between the outer peripheral surface 192 of the headrest support 19 and the inner peripheral surface 182 of the support bracket 18 facing each other. It has been. The first bead 21 is made of the same synthetic resin as the headrest support 19 and has substantially the same height as the convex portion 193 (that is, the length in the front-rear direction). The first bead 21 may be formed integrally with the headrest support 19 or may be formed separately and later fixed to the headrest support 19 by bonding or the like.

  Further, at a position behind the headrest stay 16 and above the convex portion 193, a gap that fills a gap between the outer peripheral surface 192 of the headrest support 19 and the inner peripheral surface 182 of the support bracket 18 facing each other. A second bead 22 as a body is provided. Similar to the first bead 21, the second bead 22 is made of the same synthetic resin as the headrest support 19. The second bead 22 may be integrally formed with the headrest support 19 or may be formed separately and later fixed to the headrest support 19 by bonding or the like.

  Further, a metal leaf spring 23 supported by the headrest support 19 is provided at the lower rear of the headrest stay 16. That is, the leaf spring 23 is disposed on the opposite side of the second bead 22 with the convex portion 193 interposed therebetween in the vertical direction and at the same position as the first bead 21. The plate spring 23 is a cantilever spring having a lower end as a fixed end and an upper end as a free end. The leaf spring 23 applies an urging force to the headrest support 19 so that the headrest 13 tilts backward. Thereby, the tip of the convex portion 193 is pressed against the inner peripheral surface 182 of the support bracket 18.

  As shown in FIGS. 2 and 3, the headrest support 19 can tilt in the front-rear direction with respect to the support bracket 18 with the tip of the convex portion 193 as a fulcrum S. When the headrest support 19 is tilted in the counterclockwise direction in FIG. 3, a reaction force due to the bending of the leaf spring 23 is generated. The tilting range of the headrest support 19 is such that the plate on the outer peripheral surface 192 on the rear side of the headrest support 19 from the position at which the first bead 21 provided at the lower front portion contacts the inner peripheral surface 182 in front of the support bracket 18. The stopper portion 194 in the lower part of the spring 23 is set to a position where it comes into contact with the inner peripheral surface 182 behind the support bracket 18.

Next, with reference to FIG.4 and FIG.5, the effect | action of the headrest support structure of this embodiment is demonstrated.
When the headrest 13 is displaced forward, the headrest support 19 into which the tip portion 161 of the headrest stay 16 is inserted tilts counterclockwise in FIG. 3 with the tip of the projection 193 as a fulcrum S with respect to the support bracket 18. To do. During this tilting, the leaf spring 23 is deflected by being pressed against the inner peripheral surface 182 behind the support bracket 18, thereby generating a drag force against the displacement of the headrest 13.

  When the amount of forward displacement of the headrest 13 reaches a certain level, the stopper portion 194 comes into contact with the inner peripheral surface 182 on the rear side of the support bracket 18 and further tilting of the headrest support 19 is locked. Therefore, further forward displacement of the headrest 13 is performed by elastic deformation of the headrest stay 16 and the like.

  Here, a support structure of a first comparative example in which the second bead 22 is disposed at a position between the convex portion 193 and the leaf spring 23 in the vertical direction will be described. In the first comparative example, when the headrest support 19 tilts as the headrest 13 is displaced forward, the tilt is limited by the second bead 22. As a result, the tilting range of the headrest support 19 is narrowed, and further tilting of the headrest support 19 is restricted before the stopper portion 194 on the lower rear side of the headrest support 19 abuts against the inner peripheral surface 182 of the support bracket 18.

  In contrast, in the present embodiment, since the second bead 22 is disposed above the convex portion 193, the headrest support 19 is not limited to the second bead 22, and the headrest support 19 is counterclockwise in FIG. Tilt to. In other words, the headrest support 19 is allowed to tilt until the stopper portion 194 contacts the inner peripheral surface 182 of the support bracket 18. Therefore, the swing range of the headrest 13 is expanded by changing the arrangement position of the second bead 22 as compared with the case of the first comparative example.

  On the other hand, when the headrest 13 is displaced rearward, the tilting of the headrest support 19 with respect to the support bracket 18 is restricted from the beginning by the contact of the first bead 21 with the inner peripheral surface 182 of the front of the support bracket 18. ing. Therefore, the rearward displacement of the headrest 13 is performed from the beginning by elastic deformation of the headrest stay 16 and the like.

  Therefore, the relationship between the amount of displacement of the headrest 13 in the front-rear direction and the load necessary for the displacement is as shown in FIG. That is, an area where the support rigidity of the headrest 13 is small is set from the initial position where the displacement amount is “0 (zero)”, that is, from the initial position of the headrest 13 when no external force is received. However, the support rigidity of the headrest 13 is increased with respect to a forward displacement exceeding a certain amount and a backward displacement from the initial position. That is, in the seat 11 of the present embodiment, minute swinging (vibration) of the headrest 13 with respect to the seat back frame 17 is allowed. Therefore, when the vibration force is transmitted from the vehicle body to the seat 11 and the vibration in the front-rear direction caused by the vibration force is generated in the seat 11, the headrest 13 uses the tip of the convex portion 193 as a fulcrum S as a seat back. By swinging back and forth with respect to 12, the vibration of the seat 11 is attenuated.

However, since the rearward displacement of the headrest 13 shows high support rigidity, the headrest 13 can reliably receive the occupant's head when the vehicle receives a rear-end collision.
Here, the vibration in the front-rear direction of the seat 11 shown in FIG. 5A will be described using a spring-mass model having two degrees of freedom shown in FIG. In FIG. 5, “m1” indicates the equivalent mass of the seat skeleton including the rail and the seat back frame 17, and “m2” indicates the equivalent mass of the headrest 13. “K1” indicates the equivalent stiffness of the seat skeleton, and “k2” indicates the equivalent stiffness of the headrest support structure.

  If the support rigidity of the headrest 13 with respect to the seat skeleton is sufficiently small, the headrest 13 functions as a mass system of the dynamic damper of the seat 11 and the resonance frequency of the seat 11 is lowered. The effect of lowering the resonance frequency at this time increases as the equivalent mass m2 of the headrest 13 is increased or the equivalent rigidity k2 of the headrest support structure is reduced.

  In this regard, a weight 15 is built in the headrest 13 of the present embodiment. Thereby, the weight of the headrest 13 becomes large and the equivalent mass m2 of the headrest 13 can be increased. As a result, the resonance frequency of the sheet 11 is lowered.

  Further, in the support structure of the second comparative example in which the leaf spring 23 is disposed at the upper portion and the convex portion 193 is disposed at the lower portion, the convex portion 193 is disposed at a position away from the headrest 13. In this case, if the swing range in the front-rear direction of the headrest 13 with the tip of the convex portion 193 as the fulcrum S is constant, the allowable width of the displacement in the front-rear direction of the stopper portion 194 provided at the lower rear of the headrest support 19 is Narrow. In other words, in this embodiment, the allowable width of the displacement of the stopper portion 194 in the front-rear direction is wider than in the case of the second comparative example.

  Next, with reference to FIG.6 and FIG.7, the effect | action at the time of attaching the headrest 13 to the seat back 12 is demonstrated. FIG. 6 is a schematic diagram of the support structure of the third comparative example, and FIG. 7 is a schematic diagram of the support structure of the present embodiment.

  As shown in FIG. 6, the support structure of the third comparative example has a configuration in which a first spring 51 is provided in place of the convex portion 193 and a second spring 52 is provided in place of the leaf spring 23. In this case, the headrest support 19 tilts about the fulcrum S1 set between the springs 51 and 52 in the vertical direction.

  Here, it is assumed that the headrest support structure allows the headrest 13 to be positioned forward from the reference position indicated by the solid line in FIGS. 6 and 7 by an allowable displacement amount ΔM. In this case, the design swing width of the headrest 13 in the front-rear direction is a displacement allowance ΔM. However, the actual swinging width of the headrest 13 in the front-rear direction is narrower than the allowable displacement amount ΔM due to the tolerance of each component. In order to suppress a decrease in vibration damping performance due to the headrest support structure, it is preferable to make the swing width of the headrest 13 as wide as possible.

  In the third comparative example, the distance along the vertical direction from the fulcrum S1 to the upper end of the headrest 13 is the first distance L11, and the distance along the vertical direction from the fulcrum S1 to the lower end of the headrest support 19 is the second distance. Distance L12. In this case, when the headrest 13 is displaced forward from the reference position by an allowable displacement amount ΔM, a first displacement amount ΔM11 that is a backward displacement amount from the reference position indicated by a solid line in FIG. The relational expression shown in (1) is shown.

ΔM11 = ΔM × (L12 / L11) (Formula 1)
On the other hand, as shown in FIG. 7, in the present embodiment, the distance along the vertical direction from the fulcrum S to the upper end of the headrest 13 is the first distance L21 shorter than the first distance L11. A distance along the vertical direction to the lower end of the headrest support 19 is a second distance L22 that is longer than the second distance L12. In this case, when the headrest 13 is displaced forward from the reference position by an allowable displacement amount ΔM, a second displacement amount ΔM12 that is a backward displacement amount from the reference position indicated by a solid line in FIG. It is shown by the relational expression shown in (Formula 2).

ΔM12 = ΔM × (L22 / L21) (Formula 2)
There is a manufacturing tolerance in the headrest support 19 and the support bracket 18 constituting the headrest support structure. Therefore, if the outer diameter of the headrest support 19 is larger than the design value, or the inner diameter of the support bracket 18 is smaller than the design value, the space between the outer peripheral surface 192 of the headrest support 19 and the inner peripheral surface 182 of the support bracket 18 is reduced. The gap becomes narrower. In this case, the rearward displacement of the lower end of the headrest support 19 is limited by the tolerance of the headrest support 19 and the support bracket 18.

  For example, it is assumed that the rearward displacement of the lower end of the headrest support 19 is limited by a specified amount ΔM3 (<ΔM11, ΔM12). In this case, in the third comparative example, the actual first displacement amount to the rear of the lower end of the headrest support 19 is obtained by subtracting the specified amount ΔM3 from the first displacement amount ΔM11 calculated using the relational expression (Formula 1). Value. In the present embodiment, the actual second displacement amount to the rear of the lower end of the headrest support 19 is a value obtained by subtracting the specified amount ΔM3 from the second displacement amount ΔM12 calculated using the relational expression (Formula 2). The value is larger than the actual first displacement amount.

  As a result, in the support structure of the present embodiment, the position in the front-rear direction of the headrest 13 in the steady state is positioned rearward as compared with the support structure of the third comparative example. That is, the actual swinging width of the headrest 13 in the front-rear direction is wider than that of the support structure of the third comparative example. Therefore, in the support structure of the present embodiment, the actual oscillation width is less likely to be narrower than the support structure of the third comparative example, and hence the vibration damping efficiency is difficult to decrease.

  The same can be said for the comparison between the second comparative example and the present embodiment. That is, by disposing the convex portion 193 at a position close to the headrest 13, the actual swinging width of the headrest 13 in the front-rear direction is widened, and the vibration damping efficiency is increased.

As described above, in the present embodiment, the following effects can be obtained.
(1) The headrest support 19 that supports the headrest 13 via the headrest stay 16 tilts in the front-rear direction with the tip of the convex portion 193 as a fulcrum S regardless of individual differences in springs or spring mounting errors. Therefore, it is difficult for the headrest 13 to be displaced in the up-down direction when the headrest 13 swings relative to the seat back 12 in the front-rear direction. For this reason, it is possible to suppress variations in the attenuation characteristics of vibrations generated in the seat 11 with a simple configuration.

  (2) Further, by swinging the headrest 13 in the front-rear direction with the tip of the convex portion 193 as the fulcrum S, the distance from the center of the swing to the lower end of the headrest support 19 is set to the third comparative example or the second It can be made longer than in the case of the support structure of the comparative example. As a result, compared to the third comparative example and the second comparative example, the actual swinging width of the headrest 13 in the front-rear direction is less likely to be narrowed, and the vibration damping efficiency can be increased.

  Further, the tolerances of the headrest support 19 and the support bracket 18 required for securing the swing width in the front-rear direction of the headrest 13 to a certain level or more are compared with those of the second comparative example and the third comparative example. You can make it bigger. Therefore, the headrest support 19 and the support bracket 18 can be easily manufactured.

  (3) By arranging the second bead 22 on the opposite side of the leaf spring 23 with the convex portion 193 sandwiched in the vertical direction, the headrest support 19 is compared with the support structure of the first comparative example. However, the expansion and contraction of the leaf spring 23 when tilting forward with the tip of the projection 193 as the fulcrum S is less likely to be restricted by the second bead 22. As a result, the swing range of the headrest 13 in the front-rear direction can be expanded. Therefore, when the excitation force is transmitted to the sheet 11, the damping efficiency of the vibration of the sheet 11 caused by the excitation force can be increased.

  (4) In addition, the first bead 21 is provided in front of the lower portion of the storage chamber 181, and the second bead 22 is disposed above the convex portion 193, thereby restricting the rearward displacement of the headrest 13. . Therefore, when the vehicle on which the seat 11 of this embodiment is mounted receives a rear-end collision, the head of the occupant can be reliably received by the headrest 13.

  (5) By incorporating the weight 15 in the headrest 13, the headrest 13 can be made heavy. Thereby, the resonant frequency of the sheet | seat 11 can be made low and the vibration damping effect of the sheet | seat 11 can be improved.

  (6) Moreover, in this embodiment, the leaf | plate spring 23 is urging | biasing the headrest 13 back. Therefore, when an impact is applied to the headrest 13 from the front, the leaf spring 23 does not contract, so that the rearward displacement of the headrest 13 is restricted. Therefore, when the vehicle on which the seat 11 of this embodiment is mounted receives a rear-end collision, the head of the occupant can be reliably received by the headrest 13.

  Furthermore, when an impact is applied to the headrest 13 from behind, the headrest 13 is displaced forward against the urging force from the leaf spring 23, so that the impact can be reduced. .

The above embodiment may be changed to another embodiment as described below.
The weight 15 does not have to be embedded in the cushion material 14 of the headrest 13.
-You may provide the 1st bead 21 below the leaf | plate spring 23 in an up-down direction. Further, the first bead 21 may be provided above the plate spring 23 as long as it is closer to the plate spring 23 than the convex portion 193 in the vertical direction.

-You may make the height of the 1st bead 21 lower than the height of the convex part 193. FIG. In this case, the swing range of the headrest 13 can be expanded as compared with the above embodiment.
On the other hand, the height of the first bead 21 may be made higher than the height of the convex portion 193.

The first bead 21 may be formed of a material different from the material forming the headrest support 19 as long as the first bead 21 is a material having higher rigidity than the plate spring 23.
-If the 2nd bead 22 is arrange | positioned above the convex part 193, you may abbreviate | omit the 1st bead 21. FIG. Even in this configuration, the rearward displacement of the headrest 13 can be restricted by the second bead 22.

  Further, the leaf spring 23 may be disposed in front of the lower portion of the headrest stay 16, and the first bead 21 may be disposed in the lower rear of the headrest stay 16. In this case, it is preferable that the convex portion 193 is disposed on the upper rear side of the headrest stay 16 and the second bead 22 is disposed on the upper front side.

  As shown in FIG. 8, the leaf spring 23 may be disposed in front of the upper portion of the headrest stay 16, and the convex portion 193 may be disposed in the lower rear of the headrest stay 16. In this case, it is preferable that the first bead 21 is disposed on the upper rear side of the headrest stay 16 and the second bead 22 is disposed on the lower front side of the headrest stay 16. In this case, it is more preferable that the second bead 22 is disposed below the convex portion 193 in the vertical direction.

The second bead 22 may be provided at the same position as the convex part 193 in the vertical direction, or may be provided between the convex part 193 and the leaf spring 23 in the vertical direction.
The second bead 22 may be formed of a material different from the material forming the headrest support 19 as long as the second bead 22 is a material having higher rigidity than the leaf spring 23.

  If the first bead 21 is provided, the second bead 22 may be omitted. Even in this configuration, the backward displacement of the headrest 13 can be restricted by the first bead 21.

  As shown in FIG. 9, the convex portion 193 is configured to protrude from the inner peripheral surface 182 toward the outer peripheral surface 192 of the outer peripheral surface 192 of the headrest support 19 and the inner peripheral surface 182 of the support bracket 18 facing each other. May be. Even in this case, the headrest support 19 tilts in the front-rear direction with the tip of the convex portion 193 as the fulcrum S.

As shown in FIG. 9, the spring may be an arch-shaped spring 23 </ b> A configured by bending a part of the headrest support 19 outward.
The spring may be a coil spring. Further, the spring may be supported not on the headrest support 19 but on the support bracket 18.

  When adopting a tension spring as the spring, the spring and the convex part 193 may be arranged on the front side of the headrest stay 16, or the spring and the convex part 193 may be arranged on the rear side of the headrest stay 16.

  As shown in FIG. 10, the headrest support 19A may have a rectangular parallelepiped shape. In this case, stay holes 191 into which the tip portions 161 of the headrest stay 16 are inserted are formed on both sides of the headrest support 19A in the vehicle width direction. That is, the two headrest stays 16 are supported by one headrest support 19A. In this case, the headrest support 19A corresponds to a “support member”.

  Further, in the support structure that employs such a headrest support 19A, it is preferable to employ one support bracket 18A having a large accommodating chamber 181A that can accommodate the headrest support 19A.

  As shown in FIG. 11, the protruding member protruding from the headrest 13 may be a single plate member 16 </ b> A protruding toward the seat back 12. In this case, it is preferable that the headrest support 19B is provided with an insertion hole 60 having an opening extending in the vehicle width direction, and the plate material 16A is inserted into the insertion hole 60 from the upper opening. In this case, the headrest support 19B corresponds to a “support member”.

  By adopting such a configuration, it is possible to suppress fluctuations in the effect of reducing the resonance frequency in the support structure due to manufacturing errors of the pair of headrest stays 16 as compared with the case of the above embodiment.

  DESCRIPTION OF SYMBOLS 12 ... Seat back, 13 ... Headrest, 14 ... Cushion material, 15 ... Weight, 16 ... Headrest stay as an example of a protruding member, 16A ... Plate material as an example of a protruding member, 18, 18A ... Support bracket, 181, 181A ... Storage chamber, 182 ... inner peripheral surface, 19, 19A, 19B ... headrest support as support member, 192 ... outer peripheral surface, 193 ... convex portion, 21 ... first bead as another gap member, 22 ... gap filling Second bead as body, 23 ... leaf spring, 23A ... spring.

Claims (5)

A support member for supporting a protruding member protruding from the headrest;
A bracket having a storage chamber that is provided in a seat back and in which the support member is stored so as to be tiltable in the front-rear direction;
The storage chamber is provided with a spring that expands and contracts according to the tilting of the support member in the front-rear direction with respect to the bracket,
On one of the outer side surface of the support member and the inner side surface of the bracket facing each other, a convex portion protruding in the front-rear direction is located at a position different from the spring in a specified direction orthogonal to both the front-rear direction and the width direction of the headrest. with kicked set in,
The convex portion is provided at a position closer to the headrest in the prescribed direction than the spring.
Headrest support structure. The spring is disposed on one side in the front-rear direction of the protruding member, and the convex portion is disposed on the other side in the front-rear direction,
On the opposite side of the spring between the outer surface of the support member and the inner surface of the bracket facing each other on one side in the front-rear direction of the projecting member and sandwiching the convex portion in the prescribed direction, The headrest support structure according to claim 1, further comprising a gap filling member that fills the gap. In a position between the outer surface of the support member and the inner surface of the bracket that face each other on the other side in the front-rear direction of the projecting member, and closer to the spring than the convex portion in the prescribed direction, The headrest support structure according to claim 2 , further comprising another gap filling member that fills the gap. The headrest support structure according to any one of claims 1 to 3 , wherein a weight that is harder than the cushion material is embedded in the cushion material of the headrest. The headrest supporting structure according to any one of claims 1 to 4 , wherein the spring biases the headrest rearward.