JP4684181B2 - Seat damper - Google Patents

Description

  The present invention relates to a seat damper attached to a vehicle seat, and more particularly to a seat damper capable of suppressing auditory discomfort due to a hitting sound.

  In vehicles such as automobiles, various dynamic dampers are used in order to reduce harmful vibrations generated from an engine or a differential. In recent years, the vibration of the seat itself due to diversification of seats mounted on vehicles and lack of rigidity has become a problem, and dynamic dampers (seat dampers) are being used for seats as well (patent documents). 1).

This seat damper is mainly composed of a bracket member attached to a seat back, a mass member as a mass body, and a vibration-proof base that connects the bracket member and the mass member and is made of a rubber-like elastic material. By configuring beforehand the mass of the mass member and the spring constant of the vibration isolating base so that the resonance frequency (natural frequency) of the vibration system matches the peak frequency of the harmful vibration in question, Harmful vibration is reduced by resonance.
JP 2004-245314 A

  By the way, the above-described conventional seat damper is formed so that the bracket member surrounds the mass member and the bracket member regulates the relative displacement amount of the mass member.

  Thus, for example, when a large vibration is input when the vehicle passes through a step on the road surface, and the mass member is greatly displaced, the bracket member receives and regulates the displacement of the mass member, so that Each member is prevented from being damaged due to interference with the other member, and the amount of distortion of the vibration-proof substrate is suppressed to a predetermined amount or less, thereby improving its durability.

  However, in the above-described conventional seat damper, when the mass member is largely displaced with the input of large vibration, the displacement is received and regulated by the bracket member, but when the mass member abuts on the bracket member, There has been a problem in that an audible discomfort is given to the occupant due to the hitting sound generated between these two members.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a seat damper capable of suppressing auditory discomfort due to a hitting sound.

  In order to achieve this object, a seat damper according to claim 1 is attached to a vehicle seat, and includes a mass member functioning as a mass body, and a bracket member attached to the seat. The bracket member and the mass member are connected to each other and provided with a vibration-proof base composed of a rubber-like elastic material, and the bracket member includes a pair of attachment plate portions attached to the sheet, A pair of upright plate portions, each of which rises from the pair of mounting plate portions and faces each other in parallel with a predetermined interval, and to which the mass member is connected via the vibration isolation base, and the pair of upright plate portions And a counter plate portion facing the upper surface of the mass member in parallel with a predetermined distance therebetween, the mass member comprising the upper surface, a bottom surface facing the upper surface, and the upper surface thereof The four side surfaces connecting the bottom surface and the bottom surface are formed in a rectangular parallelepiped shape, and two of the four side surfaces facing each other parallel to each other are provided with a pair of upright bracket members via the vibration isolation base. Each of the bracket members is connected to a plate portion, and the bracket member includes an opening formed by opening the counter plate portion in the plate thickness direction.

  The seat damper according to claim 2 is the seat damper according to claim 1, wherein the seat damper projects from the upper surface of the mass member toward the lower surface of the counter plate portion and is orthogonal to the direction connecting the pair of upright plate portions. And a ridge-shaped ridge rubber portion made of a rubber-like elastic material.

  According to a third aspect of the present invention, in the seat damper according to the second aspect, the opening is formed at two locations on the counter plate portion.

  According to a fourth aspect of the present invention, there is provided the seat damper according to the second or third aspect, wherein the seat damper is configured integrally with the vibration-proof base from a rubber-like elastic material, and includes a covering rubber portion that covers the mass member. The strip rubber part is formed integrally with the covering rubber part.

  The seat damper according to claim 5 is the seat damper according to claim 4, wherein the covering rubber portion exposes the four corner portions where the four side surfaces of the mass member are connected to each other and removes the remaining portions excluding the four corner portions. It is something to cover.

  According to a sixth aspect of the present invention, in the seat damper according to the third aspect, the openings formed at the two positions of the opposing plate portion are arranged along a direction connecting the pair of standing plate portions. The protruding rubber part is disposed at a position overlapping at least the region on the side of the standing plate part with respect to the central part of the opening in the top view of the mass member.

  The seat damper according to claim 7 is the seat damper according to claim 6, wherein the protruding rubber portion is configured such that at least a part of the protruding rubber portion is at an edge portion of the opening in a top view of the mass member. It is arranged at a position to be divided.

  The sheet damper according to claim 8 is the sheet damper according to any one of claims 2 to 7, wherein the protrusion rubber portion is positioned on an upper surface of the mass member toward the both ends in the extending direction of the protrusion rubber portion. The projecting height from the center is reduced, and the projecting height is maximized at the center in the extending direction.

  The sheet damper according to claim 9 is the sheet damper according to any one of claims 2 to 8, and is made of an elastic material, and is adhered to either the upper surface of the mass member or the lower surface of the counter plate portion. The buffer member is affixed to the upper surface of the mass member or the lower surface of the counter plate portion, and is attached to an edge portion on the end side in the extending direction of the protrusion rubber portion.

  The sheet damper according to claim 10 is the sheet damper according to any one of claims 1 to 9, wherein the vibration isolation base is a thickness between an upper surface and a bottom surface of the mass member in a side view of the mass member. The mass members are connected to the two side surfaces of the mass member in a state of being displaced from the center in the direction toward the upper surface side or the bottom surface side.

  The seat damper according to claim 11 is the seat damper according to claim 10, wherein the vibration isolation base is one side surface of two side surfaces of the mass member and one of the pair of standing plate portions. A first connection base and a second connection base for connecting the upright plate portions; the other side surface of the two side surfaces of the mass member; and the other upright plate portion of the pair of upright plate portions; A third connecting base and a fourth connecting base for connecting the mass member, and supporting the mass member by connecting the mass member to the upright plate at four positions, one end on one side and the other end on the other side. Is.

  The seat damper according to claim 12 is the seat damper according to claim 11, wherein the anti-vibration base is located between the first connection base and the second connection base and is separated from the one standing plate portion. The first stopper portion projecting toward the side surface of the first connecting portion, and located between the third connection base and the fourth connection base and projecting from the other standing plate portion toward the other side surface. And a second stopper portion.

  According to the seat damper of claim 1, the mass system is configured by connecting the mass member via the anti-vibration base between the pair of upright plate portions of the bracket member, and vibration is generated in the seat. The vibration is input to the vibration system, and the mass member as the mass body is displaced along with the deformation of the vibration-proof base.

  Here, when the frequency of the input vibration coincides with the resonance frequency of the vibration system, the vibration system is resonated, and the resonance action (the mass member is displaced in the opposite phase to the vibration of the sheet, so that the mass is The vibration of the sheet is reduced by acting as a canceling force on the sheet.

  Further, for example, when the mass member is greatly displaced toward the opposing plate portion of the bracket member due to the input of large vibration when the vehicle passes through the step on the road surface, the upper surface of the mass member becomes the opposing plate portion of the bracket member. Abutting (collision), the displacement of the mass member is regulated.

  In this case, in the conventional seat damper, there is a problem that the hitting sound when the upper surface of the mass member collides with the opposing plate portion of the bracket member gives an audible discomfort to the occupant. According to the above, since the opening is formed in the opposing plate portion of the bracket member, there is an effect that the timbre of the hitting sound can be changed to suppress the occupant's auditory discomfort. .

  Here, the inventor of the present application does not connect the rising ends of the pair of standing plate portions of the bracket member with the counter plate portion, but connects one end of the counter plate portion to only one of the pair of standing plate portions. The present inventors have conceived that the timbre of the hitting sound can be changed even when the other end of the plate portion is a free end. However, in this case, since it becomes difficult to ensure the bending strength and torsional strength of the opposing plate portion (and the standing plate portion), it is necessary to configure the plate thickness to be thick, and the part cost is correspondingly reduced. As it rises, there is a problem that the weight of the product increases.

  Further, even when the rising ends of the pair of upright plate portions of the bracket member are connected by the opposing plate portion and the notch is provided in the edge portion of the opposing plate portion, the tone color of the hitting sound can be changed. However, when the edge portion of the opposing plate portion is notched, it is difficult to secure the rigidity and strength particularly in the direction of twisting the plate surface of the opposing plate portion, and similarly to the case described above, there is a problem that the component cost and weight increase. Invite.

  On the other hand, according to the seat damper of the present invention, the rising ends of the pair of standing plate portions of the bracket member are connected by the opposing plate portion, and the opening portion is provided in the opposing plate portion. A plate surface can be present at a position where both sides are sandwiched (both edges of the opposing plate portion). Thereby, while ensuring the opening amount necessary to change the hitting sound, it is possible to effectively ensure the bending strength and torsional strength of the opposing plate portion, so the thickness of the bracket member is reduced, Accordingly, there is an effect that the part cost can be reduced and the weight can be reduced.

  According to the seat damper of claim 2, in addition to the effect produced by the seat damper of claim 1, since it includes a protruding rubber portion that is formed of a rubber-like elastic material and protrudes from the upper surface of the mass member, When the upper surface of the mass member collides with the opposing plate portion of the bracket member, the protruding rubber portion is deformed to provide a buffering action, so that the impact can be absorbed and the volume of the hitting sound can be reduced. As a result, there is an effect that an occupant's hearing discomfort can be reduced.

  In addition, since the ridge rubber portion is formed in a ridge shape extending in a direction perpendicular to the direction connecting the pair of standing plate portions, the width of the ridge rubber portion is reduced to reduce the protrusion. While making it easy to deform the strip rubber portion, it is possible to secure a contact area that is in contact with the opposing plate portion, and therefore, there is an effect that the function as the buffer portion can be more effectively exhibited.

  That is, by making the ridge rubber part narrow, its deformability can be ensured and the buffering action for absorbing the impact can be sufficiently exerted, so the volume of the hitting sound can be surely reduced. Can do. And it is input into the opposing board part of a bracket member by ensuring the contact area of the protrusion rubber part contact | abutted to an opposing board part along the direction orthogonal to the direction which ties a pair of standing board part. The impact load is effectively dispersed, and the hitting sound generated by the collision can be changed to a tone with less discomfort.

  According to the seat damper of the third aspect, in addition to the effect produced by the seat damper according to the second aspect, the opening is formed at two positions of the counter plate portion. The plate surface can be present not only between the two edges of the part but also between the two openings.

  As a result, even when the opening area is the same, it is possible to change the hitting sound to a timbre with less discomfort compared to the case where only one opening is formed, and the bending of the opposing plate portion. There is an effect that strength and torsional strength can be effectively secured. As a result, it is possible to reduce occupant hearing discomfort and to reduce the component cost and weight by reducing the thickness of the bracket member.

  According to the seat damper of the fourth aspect, in addition to the effect produced by the seat damper according to the second or third aspect, a covering rubber portion is integrally formed from the rubber-like elastic material and covers the mass member. Therefore, compared to the case where the entire outer surface of the mass member is exposed, there is an effect that vibration of the mass member itself when the mass member collides with the opposing plate portion can be suppressed. As a result, the vibration of the mass member itself after the collision can be converged at an early stage, so that the mass member (and the anti-vibration base) can be appropriately displaced to stably function as a dynamic damper that reduces harmful vibrations. Can be made.

  Further, since the ridge rubber portion is configured integrally with the covering rubber portion, the vibration isolating base (and the covering rubber portion, There is an effect that the mold structure for vulcanizing and molding the ridge rubber portion) can be simplified, and the manufacturing cost can be reduced and the yield can be improved.

  Furthermore, the ridge rubber portion is formed integrally with the covering rubber portion, that is, by providing the ridge rubber portion on the upper surface side of the mass member, the ridge rubber portion is provided on the lower surface of the counter plate portion. Thus, there is an effect that the hitting sound can be changed to a tone with less discomfort.

  That is, even when the protruding rubber part is configured to have the same protruding height, when the protruding rubber part is configured integrally with the covering rubber part, the rubber volume at the base of the protruding rubber part is covered with the covering rubber. While ensuring that it is integrated with the part, the tip of the ridge rubber part can be tapered to reduce the rubber volume, effectively exerting a buffering effect and reducing the volume of the hitting sound. The timbre can be changed.

  According to the seat damper of the fifth aspect, in addition to the effect produced by the seat damper of the fourth aspect, the covering rubber portion exposes the four corner portions where the four side surfaces of the mass member are connected to each other and the four corner portions. When the vulcanization molding of the vibration-proof base (and the covering rubber part and the protruding rubber part) is obtained while sufficiently obtaining the above-described effect by covering the outer surface of the mass member. Since the four corners of the mass member can be fixed (positioned) in the vulcanization mold, the relative position of the mass member with respect to the bracket member and the vibration isolating base can be set with higher accuracy. As a result, it is possible to stably exhibit the role as a dynamic damper that reduces harmful vibrations by suppressing variations in the resonance frequency of each product, and it is possible to suppress variations in sound volume and timbre. There is an effect.

  According to the seat damper of the sixth aspect, in addition to the effect produced by the seat damper of the third aspect, the openings formed at two positions of the opposing plate portion are along the direction connecting the pair of standing plate portions. The protrusion rubber part is arranged at a position overlapping at least the region on the side of the standing plate part with respect to the center part of the opening part in a top view of the mass member, that is, more than the opening part. Since the protruding rubber part collides with the opposing plate part on the outer side (standing plate part side), there is an effect that the hitting sound can be changed to a timbre with less discomfort.

  According to the seat damper of claim 7, in addition to the effect produced by the seat damper of claim 6, at least a part of the projecting rubber part is the opening of the projecting rubber part in the top view of the mass member. Since it is disposed at a position divided by the edge of the portion, there is an effect that the sound volume of the hitting sound can be reduced while ensuring the life of the protruding rubber portion.

  That is, in order to effectively exhibit the buffering effect at the time of collision, it is not appropriate that the contact area of the protruding rubber part that is in contact with the counter plate part is too large. However, the ridge rubber portion needs to be formed as a ridge continuous in the extending direction due to the mold structure of the vulcanization mold, and cannot be formed in a shape in which the intermediate portion in the extending direction is omitted. Further, the protrusion rubber portion needs to exhibit a buffering effect even when the mass member is displaced in the rotation direction and collides with the opposing plate portion, and therefore needs to be extended to the edge of the upper surface of the mass member. There is. On the other hand, if the width of the ridge rubber portion is reduced in order to reduce the contact area, the load (distortion amount) of the ridge rubber portion at the time of a collision becomes excessive, leading to a decrease in durability.

  On the other hand, according to the seat damper of the present invention, as described above, in the top view of the mass member, since it is configured such that at least a part of the protruding rubber portion is divided into the edge portion of the opening, the division is performed. Accordingly, the contact area of the protruding rubber portion that is in contact with the opposing plate portion can be reduced. As a result, by increasing the width of the ridge rubber part and ensuring its durability, avoiding an excessive contact area and properly exhibiting a buffering effect, the volume of the hitting sound Can be reduced. In addition, by making the contact area appropriate, it is possible to effectively disperse the impact load input to the opposing plate portion of the bracket member, and to change the hitting sound generated by the collision into a tone with less discomfort. . Further, since the end portion in the extending direction of the ridge rubber portion is not divided, the buffering effect when the mass member is displaced in the rotation direction and collides with the opposing plate portion is not hindered by the division. .

  In addition, the division | segmentation of the protrusion rubber | gum part by an opening part here is only when a protrusion rubber | gum part is completely divided | segmented by an opening part in the intermediate part of the extending direction (all the width direction overlaps with an opening part). It is the meaning including not only the part of the width direction of a ridge rubber part but an opening part.

  According to the seat damper of the eighth aspect, in addition to the effect exhibited by the seat damper according to any one of the second to seventh aspects, the ridge rubber portion is closer to both ends in the extending direction of the ridge rubber portion. Since the protruding height from the upper surface of the mass member is reduced and the protruding height is maximized at the center in the extending direction, the upper surface of the mass member collides with the opposing plate portion of the bracket member. In this case, the protruding rubber part can be easily deformed, and the buffering action can be effectively exhibited. As a result, the impact can be reliably absorbed and the volume of the hitting sound can be further reduced, so that there is an effect that the passenger's hearing discomfort can be further reduced.

  According to the seat damper of claim 9, in addition to the effect produced by the seat damper of any of claims 2 to 8, the seat damper is made of an elastic material, and either the upper surface of the mass member or the lower surface of the counter plate portion The buffer member is attached to the edge of the upper surface of the mass member or the lower surface of the opposing plate portion, which is the end in the extending direction of the ridge rubber portion. Therefore, there is an effect that the life of the ridge rubber portion can be improved.

  In other words, since the protruding rubber part is configured to extend in a direction perpendicular to the direction connecting the pair of standing plates, when the mass member is displaced in the rotational direction, the displacement in the rotational direction is projected. Since it is received only at the extended end of the strip rubber part, the buffering effect cannot be fully exhibited, the volume of the hitting sound increases, and the burden on the protruding rubber part increases, and the damage The life is shortened by such reasons.

  On the other hand, according to the seat damper of the present invention, the buffer member is attached to the upper surface of the mass member or the lower surface of the opposing plate portion, and is attached to the edge on the end side in the extending direction of the protruding rubber portion. Even when the mass member is displaced in the rotational direction, the displacement in the rotational direction can be received not only by the end portion in the extending direction of the ridge rubber portion but also by the buffer member, so that the buffer effect is sufficiently exhibited, It is possible to reduce the volume of the hitting sound, reduce the burden on the protruding rubber part, and suppress the breakage or the like.

  Moreover, since it is the structure which attaches a buffer member by sticking, and the attachment position (sticking position) is the edge part which becomes the extension direction edge part side of a protrusion rubber part, attachment work of a buffer member is easy. It can be carried out. As a result, the assembly cost can be reduced, and the product cost of the entire seat damper can be reduced.

  According to the seat damper of the tenth aspect, in addition to the effect produced by the seat damper according to any one of the first to ninth aspects, there is an effect that the resonance action can be obtained in a wide frequency range.

  Here, the resonance action of the seat damper has a characteristic of rapidly decreasing when the frequency of the vibration system slightly deviates from the resonance frequency, and a sufficient effect can be obtained only in a very narrow frequency region. Therefore, it is necessary to accurately match the resonance frequency of the vibration system with the peak frequency of harmful vibration.

  However, the peak frequency of harmful vibrations that occur in the seat usually varies from vehicle to vehicle due to, for example, dimensional variations in the members constituting the seat. Therefore, in the conventional seat damper described above, it is difficult to accurately match the resonance frequency of the vibration system with the peak frequency of the harmful vibration in question, and the harmful vibration cannot be sufficiently reduced. there were.

  On the other hand, according to the seat damper of the present invention, the vibration isolating base is displaced from the center in the thickness direction between the top surface and the bottom surface of the mass member to the upper surface side or the bottom surface side in a side view of the mass member. Therefore, since it is connected to each of the two side surfaces of the mass member (the anti-vibration base supports the position offset from the center of gravity position of the mass member), harmful vibration occurs in the seat, and along with the harmful vibration, When the mass member as the mass body is displaced, the mass member can be vibrated in two vibration modes (for example, two vibration modes in the vehicle longitudinal direction and the rotation direction).

  Thereby, since the resonance peak of each of the two vibration modes can be obtained, there is an effect that the resonance action can be obtained in a wider frequency region by superimposing these vibration modes. As a result, even if the peak frequency of harmful vibrations that occur in the seat does not match the preset frequency value due to dimensional variations in the components, the resonance action of the seat damper is exhibited. Thus, the harmful vibration of the seat can be reduced.

  According to the seat damper of the eleventh aspect, in addition to the effect produced by the seat damper according to the tenth aspect, the mass member is provided on the upright plate portion at four locations, one end on one side and the other end on the other side. Since the mass member is connected, the mass member can be easily vibrated in two vibration modes (for example, two vibration modes in the vehicle front-rear direction and the rotational direction), and the resonance frequency of these two vibration modes. Can be set to an appropriate frequency value.

  That is, if the mass member is configured to be connected to the standing plate portion at a total of two places, for example, one side surface and the other side surface, the resonance frequencies of the two vibration modes have different frequency values. Although it is difficult to obtain the effect of overlapping the vibration modes, as described above, the two vibration modes can be expressed in a well-balanced manner by connecting the end portions of each side face at a total of four locations.

  According to the seat damper of the twelfth aspect, in addition to the effect achieved by the seat damper of the eleventh aspect, the seat damper is located between the first connection base and the second connection base and protrudes from one of the standing plates. Since the first stopper portion and the second stopper portion located between the third connecting base and the fourth connecting base and projecting from the other upright plate portion are provided, the mass member is connected to each connecting base. In the case of displacement in the compression direction, the first stopper portion or the second stopper portion exerts a stopper action that regulates the displacement of the mass member, so that the deformation amount (compression strain and tensile strain) of each connection base is excessive. As a result, there is an effect that the life of each connection base can be improved.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described with reference to the accompanying drawings. FIG. 1A is a top view of the seat damper 100 according to the first embodiment of the present invention, FIG. 1B is a side view of the seat damper 100, and FIG. 2 is a bottom view of the seat damper 100. FIG.

  3A is a top view in which the seat damper 100 is partially sectioned, and FIG. 3B is a cross-sectional view of the seat damper 100 taken along the line IIIb-IIIb in FIG. 4A is a cross-sectional view of the seat damper 100 taken along the line IVa-IVa in FIG. 1, and FIG. 4B is a partially enlarged cross-sectional view of the seat damper 100 in the IVb portion in FIG. 3B. It is.

  3A, in order to clarify the positional relationship between the opening portions 26 and 27 and the protruding rubber portions 51 and 52, the counter plate portion 25 is partially omitted, and the opening portion 26 is not illustrated. , 27 are virtually illustrated by a two-dot chain line.

  The seat damper 100 is a dynamic damper that is attached to a vehicle seat and suppresses vibration of the seat. Here, with reference to FIG. 18, the attachment state of the sheet damper 100 to the sheets S1 and S2 in the present embodiment will be described.

  18A and 18B are a side view and a front view of the sheets S1 and S2, respectively. Note that arrows FB, LR, and UD in the figure correspond to the vehicle longitudinal direction, the vehicle lateral direction, and the vehicle vertical direction, respectively.

  The seats S1 and S2 in the present embodiment are configured as a rear row seat of an automobile (for example, a second row seat of a vehicle having three rows of seats), and a seat S1 for two seats and a seat for one seat The sheet S2 is configured to be splittable into S2, and the sheet S2 is configured to be foldable.

  As shown in FIG. 18, the seat damper 100 is attached to the seat backs B1 and B2 of the sheets S1 and S2, and is mainly driven by a resonance action of a vibration system including a mass member 10 and a vibration isolating base 30 described later. Further, vibrations of the seats S1 and S2 in the vehicle front-rear direction (arrow FB direction in FIG. 18A) and the vehicle left-right direction (arrow LR direction in FIG. 18B) are reduced.

  Returning to FIG. 1 to FIG. The seat damper 100 includes a mass member 10 that functions as a mass body, a bracket member 20 that is attached to the seats S1 and S2 (seat backs B1 and B2, see FIG. 18), the bracket member 20 and the mass member 10. A vibration-proof base 30 that is connected and made of a rubber-like elastic material is mainly provided.

  The mass member 10 is made of a metal material such as cast iron, and as shown in FIGS. 1 to 4, the upper surface 11 is formed in a rectangular shape in front view, and faces the upper surface 11 in parallel and has the same size as the upper surface 11. The bottom surface 12 is formed in a rectangular shape and the four side surfaces 13 to 16 connecting the top surface 11 and the bottom surface 12 are formed in a rectangular parallelepiped shape.

  As shown in FIGS. 1 to 4, the four side surfaces 13 to 16 have the side surface 13 facing the side surface 14 and the side surface 15 facing the side surface 16 in parallel. Further, a vibration isolating base 30 is connected to the side surfaces 13 and 14, and the mass member 10 is elastically supported between the pair of standing plate portions 22 of the bracket member 20 via the vibration isolating base 30. .

  In the seat damper 100 according to the present embodiment, the upper surface 11 and the bottom surface 12 of the mass member 11 are in the vehicle front-rear direction (arrow FB direction) and the side surfaces 13, 14 when attached to the sheets S1, S2. Is perpendicular to the vehicle vertical direction (arrow UD direction) and the side surfaces 15 and 16 are perpendicular to the vehicle left-right direction (arrow LR direction) (see FIG. 18).

  The bracket member 20 is a plate-like body configured by bending a metal material, and as shown in FIGS. 1 to 4, a pair of attachment plate portions 21 and 22 attached to the sheets S1 and S2. And a pair of upright plate portions 23 and 24 facing each other in parallel with a predetermined spacing from the pair of attachment plate portions 21 and 22, and the rising ends of the pair of upright plate portions 23 and 24 And an opposing plate portion 25 for connecting the two.

  As shown in FIG. 1 or FIG. 3, attachment holes 21a and 22a are formed in the attachment plate portions 21 and 22, and bolts (not shown) inserted through the attachment holes 21a and 22a. Then, the bracket member 20 is fastened and fixed to the seats S1 and S2 (seat backs B1 and B2) (see FIG. 18).

  As shown in FIGS. 1 to 3, the upright plate portions 23 and 24 rise in a direction perpendicular to the attachment plate portions 21 and 22 and face the side surfaces 13 and 14 of the mass member 10 in parallel. . An anti-vibration base 30 is connected to the upright plate portions 23 and 24, and the mass member 10 is elastically supported between the upright plate portions 23 and 24 through the anti-vibration base 30.

  The counter plate portion 25 is a member that connects the rising ends (FIG. 1 (a) on the front side of FIG. 1B, upper side of FIG. 1 (b)) of the pair of upright plate portions 23 and 24, as shown in FIGS. Thus, it is formed in a rectangular shape when viewed from the front, and is disposed to face the upper surface 11 of the mass member 10 in parallel with a predetermined distance therebetween.

  As shown in FIG. 1 or FIG. 3, the bracket member 20 is formed with an opening by drilling the opposing plate portion 25 in the thickness direction (FIG. 1 (a) perpendicular to the paper surface, FIG. 1 (b) vertical direction). The openings 26 and 27 are provided. When the displacement of the mass member 10 is restricted by the bracket member 20 and a hitting sound is generated, the timbre of the hitting sound is generated by the openings 26 and 27 being formed in the opposing plate part 25, so that It is possible to change to a timbre that can reduce hearing discomfort.

  Here, as a method of changing the tone of the hitting sound, for example, one end of the opposing plate portion 25 (for example, the right side in FIG. 1A) is connected to the standing plate portion 23, while A method is also conceivable in which the end is not connected to the standing plate portion 24 and the other end of the counter plate portion 25 is configured as a free end.

  However, in this case, since it becomes difficult to ensure the bending strength and torsional strength of the opposing plate portion 25 (and the standing plate portions 23 and 24), it is necessary to configure the plate thickness to be thick. There is a problem that the cost of parts increases and the weight of the product increases.

  Moreover, although the rising edge of a pair of standing board parts 23 and 24 is connected with the opposing board part 25, even if it is the structure which notches the edge part of the opposing board part 25 (provides a notch), it is sounding Can change the tone. However, if the edge portion of the counter plate portion 25 is notched in this way, it becomes difficult to secure rigidity in the direction of twisting the plate surface of the counter plate portion 25 in particular. Incurs the problem of increased weight.

  On the other hand, according to the seat damper 100 in the present embodiment, the rising ends of the pair of upright plate portions 23 and 24 are connected by the counter plate portion 25 and the width direction of the counter plate portion 25 (FIG. 1 ( a) Up and down direction) Since the opening portions 26 and 27 are provided in the center, the plate surface is located at the positions sandwiching the opening portions 26 and 27 (both edges of the opposing plate portion 25, upper and lower sides in FIG. 1A). Can exist.

  Thereby, while ensuring the opening area required for changing the hitting sound in the opposing plate portion 25, the bending strength and the torsional strength of the opposing plate portion 25 are effectively ensured by the plate surfaces existing at both edges. Therefore, it is possible to reduce the thickness of the bracket member 20 and reduce the component cost and the weight accordingly.

  Furthermore, the seat damper 100 according to the present embodiment has a configuration in which the openings 26 and 27 are formed at two locations on the opposing plate portion 25, so that the positions sandwiching the opening 25 (both edges of the opposing plate portion, FIG. 1 (a) upper side and lower side), as well as between the openings 26 and 27 (FIG. 1 (a) left and right central portion), the plate surface can be present.

  Thereby, even if the opening area is the same, the hitting sound can be changed to a timbre with less discomfort compared to the case where only one opening is formed. Bending strength and torsional strength can be effectively ensured. As a result, the occupant's hearing discomfort can be reduced, and the thickness of the bracket member 20 can be reduced to reduce the component cost and weight.

  In the present embodiment, as shown in FIG. 1 or FIG. 3, the openings 26 and 27 are each configured to be circular with the same diameter, and the longitudinal direction of the bracket member 20 (left and right in FIG. 1 (a)). Direction).

  That is, the centers of the openings 26 and 27 are located in the center in the width direction (the vertical direction in FIG. 1 (a)) of the opposing plate 25, and a pair of imaginary lines passing through the centers of the openings 26 and 27 are provided. The center of the mounting holes 21a and 22b is positioned on the imaginary line as viewed from the top surface shown in FIG.

  The anti-vibration base 30 is a member for elastically connecting and supporting the mass member 10 to the bracket member 20 and is made of a rubber-like elastic material. As shown in FIGS. 10 is vulcanized and bonded between the side surfaces 13 and 14 and the upright plate portions 23 and 24 of the bracket member 20.

  As shown in FIGS. 1 to 4, the vibration isolating base 30 includes four connecting portions from the first connecting base 31 to the fourth connecting base 34, and two first stopper portions 35 and second stopper portions 36. A stopper portion is provided, and four portions that are both end portions of the side surfaces 13 and 14 of the mass member 10 are connected to and supported by the connecting plate portions 623 and 624 of the bracket member 20.

  As shown in FIGS. 1 to 4, the first connection base 31 and the second connection base 32 are portions that connect the side surface 13 of the mass member 10 and the upright plate portion 23 of the bracket member 20. The third connection base 33 and the fourth connection base 34 are portions for connecting the side surface 14 of the mass member 10 and the standing plate portion 24 of the bracket member 20.

  As shown in FIGS. 1 to 3, the first connection base 31 to the fourth connection base 34 are configured in the same shape, and are formed by cross sections (arrows LR and FB). The cross section is a rectangular parallelepiped shape, and the first connection base 31 is the third connection base 33 and the second connection base 32 is the fourth connection in the direction of the arrow UD in the figure. It is arranged at a position overlapping with the base 34.

  As shown in FIGS. 1 to 4, the first stopper portion 35 is located between the first connection base 31 and the second connection base 32 and extends from the standing plate portion 23 of the bracket member 20 to the side surface of the mass member 10. 13, while the second stopper portion 36 is located between the third connection base 33 and the fourth connection base 34 and extends from the standing plate portion 24 of the bracket member 20 to the mass. It is a part protruding toward the side surface 14 of the member 10.

  As shown in FIG. 2, the first stopper portion 35 and the second stopper portion 36 are configured integrally with the first connecting base 31 and the like, and as shown in FIG. 1B or FIG. 3B. Furthermore, it extends from the lower end to the upper end of the standing plate portions 23 and 24 along the rising direction of the standing plate portions 23 and 24 (the vertical direction in FIG. 1B).

  Thus, according to the seat damper 100 in the present embodiment, the first stopper 35 is provided between the first connection base 31 and the second connection base 32, and the third connection base 33 and the fourth connection base are provided. 34, the second stopper portion 36 is provided between the first stopper portion 35 and the mass member 610 when the mass member 610 is displaced in the direction in which each of the connection bases 31 to 34 is compressed (the left-right direction in FIG. 2). The second stopper portion 36 exerts a stopper action that restricts the displacement of the mass member 10. Thereby, it can suppress that the deformation amount (compression distortion and tensile strain) of each connection base | substrate 31-34 becomes excessive, As a result, the improvement of the lifetime of each connection base | substrate 31-34 can be aimed at.

  As described above, in a state where the mass member 10 is connected and supported to the bracket member 20 via the vibration isolation base 30, as shown in FIGS. 1 to 4, the upper surface 11 of the mass member 10 and the bracket member 20 face each other. The plate portion 25 faces in parallel with a predetermined interval.

  Similarly, in this state, as shown in FIGS. 1 to 3, the side surfaces 13 and 14 of the mass member 10 and the standing plate portions 23 and 24 of the bracket member 20 face each other in parallel with a predetermined distance therebetween. . Note that the facing distance between the side surface 13 and the standing plate portion 23 is equal to the facing distance between the side surface 14 and the standing plate portion 24.

  Here, as shown in FIGS. 1 to 4, the seat damper 100 includes a covering rubber portion 40, ridge rubber portions 51 and 52, and buffer members 61 and 62. The covering rubber portion 40 is a member for covering the outer surface of the mass member 10, is made of a rubber-like elastic material, and is integrally formed with the vibration-proof base 30.

  Thereby, compared with the case where the whole outer surface of the mass member 10 is exposed, when the mass member 10 collides with the opposing plate part 25 (when the displacement of the mass member 10 is regulated by the opposing plate part 25). The vibration of the mass member 10 itself can be suppressed. As a result, since the vibration of the mass member 10 itself after the collision can be converged at an early stage, the mass member 10 (and the vibration isolation base 30) can be appropriately displaced to serve as a dynamic damper that reduces harmful vibrations. Can be exhibited stably.

  As shown in FIGS. 1 to 3, the covering rubber part 40 exposes the four corners where the side surfaces 13 to 16 of the mass member 10 are connected to each other, and the remaining part excluding the exposed parts (four corners). Is covered with a certain thickness.

  Thus, when the vibration-proof base 30 (and the covering rubber portion 40 and the protruding rubber portions 51 and 52) is vulcanized and molded while ensuring the above-described effects by covering the outer surface of the mass member 10 sufficiently. Since the four corners of the mass member 10 can be fixed (positioned at four locations) in the vulcanization mold, the relative position of the mass member 10 with respect to the bracket member 20 and the vibration isolation base 30 can be set with higher accuracy. it can.

  As a result, it is possible to stably exhibit the role as a dynamic damper that reduces harmful vibrations by suppressing variations in the resonance frequency of each product, and it is possible to suppress variations in sound volume and timbre. .

  The protruding rubber portions 51 and 52 are members for suppressing an impact when the displacement of the mass member 10 is regulated by the bracket member 20 (when the mass member 10 collides with the bracket member 20), and is elastic like rubber. As shown in FIG. 1 to FIG. 4, the material is formed in a ridge shape, and is formed integrally with the covering rubber portion 40.

  That is, as shown in FIG. 3A, the protruding rubber portions 51 and 52 are orthogonal to the direction connecting the standing plate portions 23 and 24 of the bracket member 20 on the upper surface 11 of the mass member 10 (FIG. 3A). As shown in FIG. 4 (b), it is configured as a tapering protrusion having a tapered cross section that protrudes from the upper surface 11 of the mass member 10 toward the opposing plate portion 25 of the bracket member 20. Has been.

  Thus, as shown in FIGS. 1 to 4, the seat damper 100 includes the protruding rubber portions 51 and 52 on the upper surface of the mass member 10, so that the upper surface 11 side of the mass member 10 faces the bracket member 20. When colliding with the plate portion 25, the protruding rubber portions 51 and 52 are deformed to provide a buffering action, so that the impact can be absorbed and the volume of the hitting sound can be reduced. As a result, occupant hearing discomfort can be reduced.

  Further, as shown in FIG. 3A, the protrusion rubber portions 51 and 52 are configured as protrusions extending in a direction perpendicular to the direction connecting the standing plates 23 and 24. The width of the strip rubber portions 51 and 52 (the dimension in the left-right direction in FIG. 3 (a)) is reduced to make the projection rubber portions 51 and 52 easy to deform, but contact with the opposing plate portion 25. Since the contact area can be ensured, the function as the buffer portion can be more effectively exhibited.

  That is, by making the protrusion rubber portions 51 and 52 narrow, the deformability can be secured and the buffering action for absorbing the impact can be sufficiently exerted, so that the volume of the hitting sound can be ensured. Can be reduced. Then, the contact area of the protruding rubber portions 51 and 52 that are in contact with the opposing plate portion 25 is along a direction orthogonal to the direction connecting the standing plate portions 23 and 24 (the vertical direction in FIG. 3A). By ensuring, the impact load input to the opposing plate portion 25 of the bracket member 20 can be efficiently dispersed, and the hitting sound generated by the collision can be changed to a tone with less discomfort.

  Here, as shown in FIG. 3A, the protruding rubber portions 51 and 52 have openings 26 and 27 in a front view (a top view of the mass member 10) when the upper surface 11 of the mass member 10 is viewed from the front. The protrusion rubber part 51 is not overlapped, and the protrusion rubber part 51 is in the area between the opening part 26 and the standing plate part 23, and the protrusion rubber part 52 is in the area between the opening part 27 and the standing plate part 24, Each is arranged.

  Thereby, when the displacement of the mass member 10 is regulated by the counter plate portion 25 (when the mass member 10 collides with the counter plate portion 25), it is outside the opening portions 26 and 27 (the standing plate portions 23 and 24). Since the protruding rubber portions 51 and 52 can collide with the opposing plate portion 25 at the position of the side), the hitting sound can be changed to a tone with less discomfort.

  Since the protruding rubber portions 51 and 52 are formed integrally with the covering rubber portion 40, the protruding rubber portions 51 and 52 are formed on the lower surface of the counter plate portion 25 (the lower side surface in FIG. 1B). Compared with the case where it is provided, the mold structure for vulcanizing and molding the vibration-proof base 30 (and the covering rubber portion 40 and the protruding rubber portions 51 and 52) is simplified, thereby reducing the manufacturing cost and improving the yield. Can be achieved.

  Furthermore, the ridge rubber portions 51 and 52 are configured integrally with the covering rubber portion 40, that is, the ridge rubber portions 51 and 52 are provided on the upper surface 11 side of the mass member 10, thereby the ridge rubber portions 51 and 52. Can be changed to a tone color with less discomfort than in the case where is provided on the lower surface of the opposing plate portion 25.

  That is, comparing the case in which the ridge rubber portions 51 and 52 are provided on the mass member 10 and the case in which the ridge rubber portions 51 and 52 are provided on the counter plate portion 25, the former and the latter are provided with the ridge rubber portions 51 and 52. Even if the protruding heights of the protrusions are the same, if the protruding rubber parts 51 and 52 are formed integrally with the covering rubber part 40 (that is, provided on the mass member 10), the protruding rubber parts The rubber volumes of the base portions 51 and 52 are secured by being integrated with the covering rubber portion 40, while the tip portions of the protruding rubber portions 51 and 52 are tapered to reduce the rubber volume. The effect can be exhibited effectively, and the volume of the hit sound can be reduced and the timbre can be changed.

  The buffer members 61 and 62 are members for suppressing an impact when the displacement of the mass member 10 is regulated by the bracket member 20 (when the upper surface 11 side of the mass member 10 collides with the opposing plate portion 25), and is elastic. The material is formed into a sheet shape, and is attached to a covering rubber portion 40 that covers the upper surface 11 of the mass member 10 as shown in FIGS. 1 to 4.

  In the present embodiment, the buffer members 61 and 62 are made of a urethane sheet material, and an adhesive sheet layer is laminated on the back surface of the sheet material. The buffer members 61 and 62 are attached to the covering rubber part 40.

  As shown in FIG. 3A, the buffer members 61 and 62 are configured in a horizontally long belt shape, and are disposed between the opposing ridge rubber portions 51 and 52, and the ridge rubber portions 51 and 52. It is arrange | positioned in the state which put the long side along the edge of the upper surface 11 used as the extension direction edge part side (FIG. 3 (a) upper side and lower side).

  As described above, the sheet damper 100 is configured by sticking the buffer members 61 and 62 to the edge portion on the upper surface 11 of the mass member 10 and on the end side in the extending direction of the protrusion rubber portions 51 and 52. Therefore, the life of the ridge rubber portions 51 and 52 can be improved while suppressing the occurrence of the hitting sound and changing the timbre.

  That is, as shown in FIG. 3 (a) or FIG. 4 (a), the protruding rubber portions 51 and 52 are perpendicular to the direction connecting the standing plate portions 23 and 24 (the vertical direction in FIG. 3 (a)). When the mass member 10 is displaced in the rotation direction (for example, in FIG. 4A, the side surface 15 side approaches the counter plate portion 25, while the side surface 16 side moves away from the counter plate portion 25. In the case where the mass member 10 is displaced in the direction), the displacement in the rotational direction is received only by the extended end portions (FIG. 4 (a) left and right end portions) of the protrusion rubber portions 51 and 52.

  For this reason, the pressure receiving area is reduced, and the buffering effect cannot be sufficiently exerted, so that the volume of the hitting sound is increased, the burden on the protruding rubber portions 51 and 52 is increased, and the end portion is damaged. As a result, the service life is reduced.

  On the other hand, according to the sheet damper 100 in the present embodiment, the cushioning members 61 and 62 are adhered to the edge of the upper surface 11 that is the end in the extending direction of the protruding rubber portions 51 and 52. Even when the member 10 is displaced in the rotational direction as described above, the displacement in the rotational direction can be received not only by the end portions of the protruding rubber portions 51 and 52 but also by the buffer members 61 and 62. And the buffering effect can be sufficiently exerted, so that the volume of the hitting sound can be reduced and the burden on the ridge rubber portions 51 and 52 can be reduced to suppress the breakage thereof. Can do.

  Moreover, since it is the structure which attaches a buffer member by sticking, and the attachment position (sticking position) is the edge part which becomes the extension direction edge part side of a protrusion rubber part, attachment work of a buffer member is easy. It can be carried out. As a result, the assembly cost can be reduced, and the product cost of the entire seat damper can be reduced.

  In addition, the thickness dimension (FIG.3 (b) vertical direction dimension) of the buffer members 61 and 62 is the height dimension (FIG. 3 (b) or FIG. 3 (b) (dimension in the vertical direction), and the spacing between the cushioning members 61, 62 and the opposing plate portion 25 is between the protruding rubber portions 51, 52 and the opposing plate portion 25. It is comprised so that it may become larger than an opposing space | interval.

  Therefore, when the mass member 10 is displaced in the rotational direction as described above, after the protrusion rubber portions 51 and 52 first receive the displacement in the rotational direction, the buffer members 61 and 62 then receive the displacement. Therefore, such displacement can be received more smoothly. As a result, the buffering effect can be exhibited more effectively, the volume of the hitting sound can be reduced, and the timbre can be changed to a timbre with less discomfort.

  Next, a second embodiment will be described with reference to FIGS. FIG. 5 is a top view of the seat damper 200 according to the second embodiment, and FIG. 6 is a cross-sectional view of the seat damper 200 taken along line VI-VI in FIG.

  In FIG. 5, for easy understanding, a part of the protruding rubber portions 251 and 252 and the buffer members 61 and 62 are shown by broken lines. 6A shows a state before the displacement of the mass member 10 is regulated by the counter plate portion 25, and FIG. 6B shows a state where the displacement of the mass member 10 is regulated by the counter plate portion 25. , Respectively.

  In the first embodiment, the case where the protruding rubber portions 51 and 52 are arranged at positions that do not overlap with the openings 26 and 27 in the top view has been described (see FIG. 3), but in the second embodiment, When viewed from the top, the protruding rubber portions 251 and 252 are disposed at positions where they overlap the openings 26 and 27. In addition, the same code | symbol is attached | subjected to the part same as above-described 1st Embodiment, and the description is abbreviate | omitted.

  As shown in FIG. 5, the protruding rubber portions 251 and 252 in the second embodiment have a portion in the middle in the extending direction (up and down direction in FIG. 5) in the plan view of the mass member 10. 27 is arranged at a position divided by the edge portion. Thereby, the sound volume of the hitting sound can be reduced while ensuring the life of the protruding rubber portions 251 and 252 as a whole.

  That is, in order to effectively exhibit the buffering effect at the time of collision, it is not appropriate that the contact area of the protruding rubber portions 252 and 252 that are in contact with the opposing plate portion 25 is too large. However, the protrusion rubber portions 251 and 252 need to be formed as protrusions continuous in the extending direction (the vertical direction in FIG. 5) due to the mold structure of the vulcanization mold, and the intermediate portion in the extending direction (FIG. 5). The protruding rubber portions 251 and 252 cannot be formed in a shape in which the vertical center portion is omitted.

  Further, since the protruding rubber portions 251 and 252 need to exhibit a buffering effect even when the mass member 10 is displaced in the rotational direction and collides with the opposing plate portion 25 as described above, the upper surface of the mass member 10 It is necessary to extend up to 11 edges. On the other hand, if the width dimension of the ridge rubber portions 251 and 252 is reduced in order to reduce the contact area, the burden (distortion amount) of the ridge rubber portions 251 and 252 at the time of the collision becomes excessive, and the durability thereof. Cause a decline.

  On the other hand, according to the seat damper 200 in the present embodiment, as shown in FIG. 5, when the mass member 10 is viewed from above, part of the protruding rubber portions 251 and 252 is the edge of the openings 26 and 27. Therefore, the contact area of the protruding rubber portions 251 and 252 that are in contact with the opposing plate portion 25 can be reduced by that amount.

  As a result, the width dimension of the protruding rubber portions 251 and 252 can be increased to ensure the durability, while avoiding an excessive contact area and properly exhibiting a buffering effect. The volume of the hitting sound can be reduced. In addition, by making the contact area appropriate, it is possible to effectively disperse the impact load input to the opposing plate portion 25 and change the hitting sound generated by the collision to a tone with less discomfort. Furthermore, since the extending direction end portions (upper side and lower side in FIG. 5) of the protruding rubber portions 251 and 252 are not divided, the mass member 10 is displaced in the rotation direction and collides with the opposing plate portion 25. The buffering effect is not inhibited.

  Next, a third embodiment will be described with reference to FIG. FIG. 7 is a top view of the seat damper 300 according to the third embodiment. In FIG. 7, for easy understanding, a part of the protruding rubber portions 351 and 352 and the buffer members 61 and 62 are shown by broken lines.

  In the first embodiment, the case where the protruding rubber portions 51 and 52 are arranged at positions that do not overlap with the openings 26 and 27 in the top view is described (see FIG. 3), but in the third embodiment, In the top view, the protruding rubber portions 351 and 352 are arranged at positions where they overlap with the openings 26 and 27. In addition, the same code | symbol is attached | subjected to the part same as above-described 1st Embodiment, and the description is abbreviate | omitted.

  As shown in FIG. 7, the protruding rubber portions 351, 352 in the third embodiment have a portion in the middle in the extending direction (vertical direction in FIG. 5) of the mass member 10 as the opening 26, 27 is arranged at a position divided by the edge portion.

  In the second embodiment, the portion to be divided by the openings 26 and 27 is up to the center in the width direction (left and right direction in FIGS. 5 and 6) of the protruding rubber portions 251 and 252 (see FIG. 5 and FIG. 6), in the third embodiment, as shown in FIG. 7, the edges of the openings 26 and 27 extend to the position where they extend beyond the protruding rubber portions 351 and 352 in the width direction (left and right direction in FIG. 7). At the same time, the extending direction intermediate portions (the center in the vertical direction in FIG. 7) of the protruding rubber portions 351 and 352 are completely divided by the openings 26 and 27.

  Similarly to the case of the second embodiment described above, the seat damper 300 according to the third embodiment also reduces the volume of the hitting sound while ensuring the life of the protruding rubber portions 251 and 252 as a whole. Can do.

  Next, a fourth embodiment will be described with reference to FIGS. FIG. 8 is a top view of the seat damper 400 according to the fourth embodiment. 9A is a cross-sectional view of the seat damper 400 taken along the line IXa-IXa in FIG. 8, and FIG. 9B is a cross-sectional view of the sheet damper 400 taken along the line IXb-IXb in FIG.

  In FIG. 8, for easy understanding, the protruding rubber portions 51 and 52, the protruding rubber portion 453, and a part of the buffer members 461a to 462b are shown by broken lines.

  In the first embodiment, the case where the pair of protruding rubber portions 51 and 52 are provided on the upper surface 11 of the mass member 10 has been described (see FIG. 3), but in the fourth embodiment, the pair of protruding rubber portions 51. , 52 and the protruding rubber part 453 are arranged on the upper surface 11 of the mass member 10. In addition, the same code | symbol is attached | subjected to the part same as above-described 1st Embodiment, and the description is abbreviate | omitted.

  As shown in FIG. 8, the seat damper 400 according to the fourth embodiment has a protruding rubber part 453 disposed between the opening 26 and the opening 27 and a position sandwiching the protruding rubber part 453. And buffer members 461a to 462b. The buffer members 461a to 462b are configured by dividing the buffer members 61 and 62 described above, and exhibit the same operational effects as the buffer members 61 and 62, and thus description thereof is omitted.

  The ridge rubber portion 453 is a member for working together with the ridge rubber portions 51, 52 to reduce the hitting sound and change the timbre, and is extended in parallel with the ridge rubber portions 51, 52. The protrusion protruding from the upper surface 11 of the mass member 10 is made of a rubber-like elastic material.

  As shown in FIG. 8, the protruding rubber part 453 is configured such that its width dimension w2 is narrower than the width dimension w1 of the protruding rubber parts 51 and 52 (w2 <w1), and FIG. ), The top portion (upper side in FIG. 9) is configured to be inclined downward in a straight line from the center to the end in the extending direction (left and right direction in FIG. 9B).

  That is, as shown in FIG. 9B, the protruding rubber portion 453 has the highest protruding height from the upper surface 11 of the mass member 10 at the center in the extending direction (the center in the left-right direction in FIG. 9B). At the same time, the protruding height from the upper surface 11 of the mass member 10 is the lowest at the ends in the extending direction (left side and right side in FIG. 9B).

  9A and 9B, the ridge rubber portion 453 has a maximum height dimension h2 set to a value larger than the height dimension h1 of the ridge rubber portions 51 and 52. (H1 <h2), the minimum height dimension h3 is set to a value smaller than the height dimension h1 of the protrusion rubber portions 51 and 52 (h3 <h1).

  As a result, in the cross-sectional view shown in FIG. 9, the tops of the projecting rubber portions 51 and 52 are higher than the tops of the projecting rubber portions 453 at and near the end in the extending direction of the projecting rubber portion 453 (FIG. 9. (B) It is located on the upper side and is close to the opposing plate part 25. Similarly, the upper surfaces of the buffer members 461a to 462b are also located above the top of the protruding rubber portion 453.

  According to the seat damper 400 in the fourth embodiment, when the mass member 10 is displaced in the vehicle front-rear direction (arrow FB direction) and the displacement is restricted by the opposing plate portion 25, first, The central part of the protruding rubber part 453 in the extending direction (the center in the left-right direction in FIG. 9B) is brought into contact with the opposing plate part 25, and then the entire protruding rubber part 51, 52 contacts the opposing plate part 25. By being in contact with each other, it is possible to gradually deform the protruding rubber portions 453, 51, 52 and smoothly receive the displacement of the mass member 10.

  As a result, the cushioning effect by the protruding rubber portions 453, 51, 52 can be exhibited more effectively, the volume of the hitting sound can be reduced, and the timbre can be changed to a timbre with less discomfort. . In particular, according to the seat damper 400 of the present embodiment, the width dimension w2 of the ridge rubber portion 453 is configured to be narrower than the width dimension w1 of the ridge rubber portions 51 and 52, so The function can be exhibited more effectively.

  On the other hand, when the mass member 10 is displaced in the rotational direction (for example, in FIG. 9B, the side surface 15 side is displaced in a direction approaching the opposing plate portion 25, and the side surface 16 side is displaced in a direction away from the opposing plate portion 25. ) However, the displacement in the rotational direction is received not only by the end portions of the ridge rubber portions 51 and 52 but also by the buffer members 61 and 62, and then also by the ridge rubber portions 453. It can be exhibited effectively, can reduce the volume of the hitting sound and change the timbre, and can reduce the burden on the ridge rubber portions 51 and 52 and suppress the breakage thereof. .

  Furthermore, in the seat damper 400 according to the present embodiment, as shown in FIG. 9B, since the protruding rubber portion 453 is inclined downward along the extending direction, the mass member 10 rotates as described above. When displaced in the direction, the mass of the mass member 10 can be received by contacting the opposing plate portion 25 in the entire area of the top portion (upper side of FIG. 9B) of the protruding rubber portion 453. Also with this configuration, since the buffering effect can be more effectively exhibited, it is possible to reduce the volume of the hitting sound and to change the tone color, and to reduce the burden on the protruding rubber portions 51 and 52. The damage can be suppressed.

  Next, a fifth embodiment will be described with reference to FIG. FIG. 10 is a top view of the seat damper 500 according to the fifth embodiment. In addition, in FIG. 10, in order to make an understanding easy, the protruding rubber | gum rubber parts 51 and 52 and some buffer members 61 and 62 are illustrated by the broken line.

  In the first embodiment, the case where the openings 26 and 27 are configured in a circular shape has been described (see FIG. 1), but in the fifth embodiment, the openings 526 and 527 are configured in a rectangular shape. In addition, the same code | symbol is attached | subjected to the part same as above-described 1st Embodiment, and the description is abbreviate | omitted.

  As shown in FIG. 10, the seat damper 400 according to the fifth embodiment has openings 526 and 527 formed in a rectangular shape, and the openings 526 and 527 formed in a rectangular shape in a top view of FIG. 10. Is overlapped with the center in the width direction (left and right direction in FIG. 10) of the protruding rubber portions 51 and 52.

  Next, a sixth embodiment will be described with reference to FIGS. FIG. 11A is a top view of the seat damper 600 according to the sixth embodiment, FIG. 11B is a side view of the seat damper 600, and FIG. 12 is a bottom view of the seat damper 600. .

  FIG. 13A is a top view in which the seat damper 600 is partially viewed in cross section, and FIG. 13B is a cross-sectional view of the seat damper 600 taken along line XIIIb-XIIIb in FIG. FIG. 14 is a cross-sectional view of the seat damper 600 taken along the line XIVa-XIVa of FIG.

  FIG. 15A is a side view of the seat damper 600, and FIG. 15B is a graph showing the frequency response of the seat damper 600. FIG. 16A is a side view of the seat damper in which the connection position of the vibration isolation base 630 is changed with respect to the seat damper 600, and FIG. 16B is a frequency of the seat damper in which the connection position is changed. It is a graph which shows a response.

  In FIG. 13A, in order to clarify the positional relationship between the opening 626 and the protruding rubber portions 651 and 652, the illustration of the counter plate portion 625 is partially omitted, and the opening 626 has two openings 626. This is virtually illustrated by the dotted line. FIG. 15 (a) is a side view corresponding to FIG. 11 (b). For ease of understanding, FIG. 15 (a) is simplified and illustrated by omitting the illustration of the protrusion rubber portions 651 and 652. ing.

  In the first embodiment, the case where the vibration-proof base 30 is connected to the center in the thickness direction of the mass member 10 in the side view has been described. However, in the sixth embodiment, the mass member 610 is offset from the center in the thickness direction. The vibration isolating base 630 is connected to the position. In addition, the same code | symbol is attached | subjected to the part same as above-described 1st Embodiment, and the description is abbreviate | omitted.

  The seat damper 600 in the sixth embodiment is a dynamic damper that is attached to a vehicle seat and suppresses vibration of the seat, like the seat damper 100 in the first embodiment. Here, with reference to FIG. 18, the attachment state of the sheet damper 600 to the sheets S1 and S2 in the present embodiment will be described.

  As shown in FIG. 18, the seat damper 600 is attached to the seat back B1 of the seat S1 together with the seat damper 100 in the first embodiment described above, and includes a mass member 610, a vibration isolation base 630, and the like which will be described later. Mainly, the vibration of the seat S1 in the vehicle longitudinal direction (FIG. 18A, arrow FB direction) and the vehicle lateral direction (FIG. 18B, arrow LR direction) is reduced. .

  As shown in FIG. 18B, since the sheet S1 is configured wider than the sheet S2, the width direction end (on the right side of FIG. 18B) is the same as that in the first embodiment. The seat damper 100 is attached, and the seat damper 600 according to the sixth embodiment is attached to the center portion in the width direction (the center in the left-right direction in FIG. 19B).

  Returning to FIG. 11 to FIG. The seat damper 600 connects the mass member 610 functioning as a mass body, the bracket member 620 attached to the seat S1 (seat back B1, see FIG. 18), the bracket member 620 and the mass member 610, and rubber. And a vibration-proof base 630 made of an elastic material.

  The mass member 610 is made of a metal material such as cast iron, and as shown in FIGS. 11 to 14, the upper surface 611 formed in a rectangular shape when viewed from the front, and is opposed to the upper surface 611 in parallel and has the same size as the upper surface 611. The bottom surface 612 formed in a rectangular shape and four side surfaces 613 to 616 connecting the top surface 611 and the bottom surface 612 are formed in a rectangular parallelepiped shape.

  As shown in FIGS. 11 to 14, the four side surfaces 613 to 616 have the side surface 613 facing the side surface 614 and the side surface 615 facing the side surface 616 in parallel. Further, a vibration isolating base 630 is connected to the side surfaces 613 and 614, and the mass member 610 is elastically supported between the pair of standing plate portions 622 of the bracket member 620 via the vibration isolating base 630. .

  Note that in the state where the seat damper 600 according to the present embodiment is attached to the seat S1, the upper surface 611 and the bottom surface 612 of the mass member 611 are the vehicle front-rear direction (arrow FB direction), and the side surfaces 613, 614 are the vehicle. The vertical direction (arrow UD direction) and the side surfaces 615 and 616 are orthogonal to the vehicle horizontal direction (arrow LR direction), respectively (see FIG. 18).

  The bracket member 620 is a plate-like body configured by bending a metal material. As shown in FIGS. 11 to 14, the pair of attachment plate portions 621 and 622 attached to the sheet S1, The pair of upright plate portions 623 and 624 that are opposed to each other in parallel with a predetermined interval from the pair of mounting plate portions 621 and 622, and the rising ends of the pair of upright plate portions 623 and 624 are connected to each other. And an opposing plate portion 625.

  As shown in FIG. 11 or FIG. 13, the mounting plate portions 621 and 622 are provided with mounting holes 21a and 22a, and bolts (not shown) inserted through the mounting holes 21a and 22a. Then, the bracket member 620 is fastened and fixed to the seat S1 (seat back B1) (see FIG. 18).

  As shown in FIGS. 11 to 13, the standing plate portions 623 and 624 rise in a direction perpendicular to the mounting plate portions 621 and 622 and face the side surfaces 613 and 614 of the mass member 610 in parallel. . An anti-vibration base 630 is connected to the upright plate portions 623 and 624, and the mass member 610 is elastically supported between the upright plate portions 623 and 624 through the anti-vibration base 630.

  The counter plate portion 525 is a member that connects the rising ends (FIG. 11 (a) on the front side of FIG. 11B, upper side of FIG. 11 (b)) of the pair of upright plate portions 623 and 624, and is shown in FIGS. Thus, it is formed in a rectangular shape when viewed from the front, and is disposed in parallel with the upper surface 611 of the mass member 610 with a predetermined distance therebetween.

  As shown in FIG. 11 or FIG. 13, the bracket member 620 is formed with an opening by drilling the opposing plate portion 525 in the thickness direction (FIG. 11 (a) perpendicular to the paper surface, FIG. 11 (b) vertical direction). The circular opening 626 is provided. When the displacement of the mass member 610 is restricted by the bracket member 620 and a hitting sound is generated, the tone of the hitting sound is determined by the opening 626 being formed in the counter plate 525 so that the passenger can hear it. The tone can be changed to reduce the discomfort.

  Here, as a method of changing the tone color of the hitting sound, for example, one end (for example, the right side of FIG. 11A) of the opposing plate portion 525 is connected to the standing plate portion 23, while other than the opposing plate portion 525. A method is also conceivable in which the end is not connected to the standing plate portion 24 and the other end of the counter plate portion 525 is configured as a free end.

  However, in this case, since it becomes difficult to ensure the bending strength and torsional strength of the opposing plate portion 525 (and the standing plate portions 623 and 624), it is necessary to configure the plate thickness to be thick. There is a problem that the cost of parts increases and the weight of the product increases.

  Further, the rising ends of the pair of upright plate portions 623 and 624 are connected by the counter plate portion 525, but even if the edge portion of the counter plate portion 525 is notched (notch is provided) Can change the tone. However, when the edge portion of the counter plate portion 525 is notched in this way, it becomes difficult to ensure the rigidity and strength in the direction of twisting the plate surface of the counter plate portion 525 in particular. Incurs the problem of increased weight.

  On the other hand, according to the seat damper 600 in the present embodiment, the rising ends of the pair of upright plate portions 623 and 624 are connected by the counter plate portion 525 and the width direction of the counter plate portion 525 (FIG. 11 ( a) Up and down direction) Since the opening 626 is provided in the center, the plate surface should be present at positions sandwiching the opening 626 (both edges of the opposing plate 525, FIG. 11A upper side and lower side). Can do.

  As a result, while the opening area necessary for changing the hitting sound is secured in the facing plate portion 525, the bending strength and the twisting strength of the facing plate portion 525 are effectively secured by the plate surfaces existing at both edges. Therefore, it is possible to reduce the thickness of the bracket member 620 and reduce the component cost and the weight accordingly.

  Note that the opening 626 is formed in a circular shape, the center of which is located at the center of the opposing plate 525 in the width direction (the vertical direction in FIG. 11A), and a pair of virtual lines passing through the center of the opening 626. The center of the attachment holes 21a and 22b is located on the imaginary line in the top view shown in FIG. 11 (a).

  The anti-vibration base 630 is a member for elastically connecting and supporting the mass member 610 with respect to the bracket member 620, and is composed of a rubber-like elastic material. As shown in FIGS. The side surfaces 613 and 614 of the 610 and the standing plate portions 623 and 624 of the bracket member 620 are vulcanized and bonded.

  As shown in FIGS. 11 to 14, the vibration isolating base 630 includes four connecting portions from the first connecting base 31 to the fourth connecting base 34, and two first stopper portions 35 and second stopper portions 36. A stopper portion is provided, and four portions that are both end portions of the side surfaces 613 and 614 of the mass member 610 are connected to and supported by the connecting plate portions 623 and 624 of the bracket member 620.

  As shown in FIGS. 11 to 14, the first connection base 631 and the second connection base 632 are portions that connect the side surface 613 of the mass member 610 and the upright plate portion 23 of the bracket member 620, The third connection base 633 and the fourth connection base 634 are portions that connect the side surface 614 of the mass member 610 and the standing plate portion 624 of the bracket member 620.

  These first connection base 631 to fourth connection base 634 are configured in the same shape as shown in FIGS. 11 to 13 and are formed by cross sections (arrows LR and FB). The cross section is a rectangular parallelepiped shape, and the first connection base 631 is the third connection base 633 and the second connection base 632 is the fourth connection in the direction of the arrow UD in the figure. The base 634 is disposed so as to overlap with the base 634.

  As shown in FIGS. 11 to 14, the first stopper portion 635 is located between the first connection base 631 and the second connection base 632, and extends from the standing plate portion 623 of the bracket member 620 to the side surface of the mass member 610. On the other hand, the second stopper portion 636 is located between the third connection base 633 and the fourth connection base 634 and is connected to the mass from the standing plate portion 624 of the bracket member 620. This is a portion that protrudes toward the side surface 614 of the member 610.

  As shown in FIG. 12, the first stopper portion 635 and the second stopper portion 636 are integrated with the first connecting base 631 and the like, and as shown in FIG. 11B or FIG. 13B. In addition, it extends from the lower end to the upper end of the standing plate portions 623 and 624 along the rising direction of the standing plate portions 623 and 624 (the vertical direction in FIG. 11B).

  In this manner, in a state where the mass member 610 is connected and supported to the bracket member 620 via the vibration isolation base 630, as shown in FIGS. 11 to 14, the upper surface 611 of the mass member 610 and the bracket member 620 are opposed to each other. The plate portion 525 is opposed in parallel with a predetermined interval.

  Similarly, in this state, as shown in FIGS. 11 to 13, the side surfaces 613 and 614 of the mass member 610 and the standing plate portions 623 and 624 of the bracket member 620 face each other in parallel with a predetermined distance therebetween. . Note that the facing distance between the side surface 613 and the standing plate portion 623 is equal to the facing distance between the side surface 614 and the standing plate portion 624.

  Here, as shown in FIGS. 11 to 14, the seat damper 600 includes a covering rubber portion 40, ridge rubber portions 651 and 652, and buffer members 661 and 662. The covering rubber portion 640 is a member for covering the outer surface of the mass member 610 and is formed of a rubber-like elastic material and is integrally formed with the vibration isolation base 630.

  Thereby, compared with the case where the whole outer surface of the mass member 610 is exposed, when the mass member 610 collides with the opposing plate portion 525 (when the displacement of the mass member 610 is restricted by the opposing plate portion 525). The vibration of the mass member 610 itself can be suppressed. As a result, since the vibration of the mass member 610 itself after the collision can be converged at an early stage, the mass member 610 (and the vibration isolation base 630) can be appropriately displaced to serve as a dynamic damper that reduces harmful vibrations. Can be exhibited stably.

  As shown in FIGS. 11 to 13, the covering rubber part 640 exposes the four corners where the side surfaces 613 to 616 of the mass member 610 are connected to each other, and the remaining part excluding the exposed parts (four corners). Is covered with a certain thickness.

  Thereby, when the above-mentioned effect by covering the outer surface of the mass member 610 is sufficiently secured, the anti-vibration base 630 (and the covering rubber portion 640 and the protruding rubber portions 651 and 652) is vulcanized. Since the four corners of the mass member 610 can be fixed in the vulcanization mold (positioning four positions), the relative position of the mass member 610 with respect to the bracket member 620 and the vibration isolation base 630 can be set with higher accuracy. it can.

  As a result, it is possible to stably exhibit the role as a dynamic damper that reduces harmful vibrations by suppressing variations in the resonance frequency of each product, and it is possible to suppress variations in sound volume and timbre. .

  The protruding rubber portions 651 and 652 are members for suppressing an impact when the displacement of the mass member 610 is restricted by the bracket member 620 (when the mass member 610 collides with the bracket member 620), and is elastic like rubber. As shown in FIG. 11 to FIG. 14, the material is formed in a ridge shape, and is formed integrally with the covering rubber portion 640.

  That is, as shown in FIG. 13A, the protruding rubber portions 651 and 652 are perpendicular to the direction connecting the standing plate portions 623 and 624 of the bracket member 620 on the upper surface 611 of the mass member 610 (FIG. 13). (A) It is comprised as a protrusion with a tapered cross section that extends in the vertical direction and protrudes from the upper surface 611 of the mass member 610 toward the opposing plate portion 525 of the bracket member 620 (see FIG. 4B). ).

  Thus, as shown in FIGS. 11 to 14, the seat damper 600 includes the protruding rubber portions 651 and 652 on the upper surface of the mass member 610, so that the upper surface 611 side of the mass member 610 faces the bracket member 620. When colliding with the plate portion 525, the protruding rubber portions 651 and 652 are deformed to provide a buffering action, so that the impact can be absorbed and the volume of the hitting sound can be reduced. As a result, occupant hearing discomfort can be reduced.

  Further, as shown in FIG. 13A, the protrusion rubber portions 651 and 652 are configured as protrusions extending in a direction perpendicular to the direction connecting the standing plate portions 623 and 624. The width of the strip rubber portions 651 and 652 (the dimension in the left-right direction in FIG. 13 (a)) is reduced to make the projection rubber portions 651 and 652 easy to deform, but the abutting against the opposing plate portion 525. Since the contact area can be ensured, the function as the buffer portion can be more effectively exhibited.

  That is, by making the protrusion rubber portions 651 and 652 narrow, the deformability can be secured and the buffering action for absorbing the impact can be sufficiently exerted, so that the volume of the hitting sound can be ensured. Can be reduced. Then, the contact areas of the protruding rubber portions 651 and 652 that are in contact with the opposing plate portion 525 are along a direction perpendicular to the direction connecting the standing plate portions 623 and 624 (the vertical direction in FIG. 13A). By ensuring, the impact load input to the opposing plate portion 525 of the bracket member 620 can be efficiently dispersed, and the hitting sound generated by the collision can be changed to a tone with less discomfort.

  Here, as shown in FIG. 13A, the protruding rubber portions 651 and 652 are overlapped with the opening 626 in a front view when the upper surface 611 of the mass member 610 is viewed from the front (upper surface view of the mass member 610). In addition, the protruding rubber part 51 is arranged in the region between the opening 26 and the standing plate part 623, and the protruding rubber part 52 is arranged in the region between the opening 27 and the standing plate part 624, respectively. It is installed.

  Thereby, when the displacement of the mass member 610 is regulated by the counter plate portion 525 (when the mass member 610 collides with the counter plate portion 525), the outer side than the opening 626 (the standing plate portions 623 and 624 side). Since the protruding rubber portions 651 and 652 can be caused to collide with the opposing plate portion 525 at the position, the hitting sound can be changed to a tone with less discomfort.

  Since the protruding rubber portions 651 and 652 are integrally formed with the covering rubber portion 640, the protruding rubber portions 651 and 652 are provided on the lower surface of the counter plate portion 525 (the lower surface in FIG. 11B). Compared with the case where it is provided, the mold structure for vulcanizing and molding the anti-vibration base 630 (and the covering rubber part 640, the protruding rubber part 651, 652) is simplified, and the manufacturing cost is reduced and the yield is improved. Can be achieved.

  Further, the ridge rubber portions 651 and 652 are integrally formed with the covering rubber portion 640, that is, the ridge rubber portions 651 and 652 are provided on the upper surface 611 side of the mass member 610, whereby the ridge rubber portions 651 and 652 are provided. Can be changed to a timbre with less discomfort compared to the case where is provided on the lower surface of the opposing plate portion 525.

  That is, comparing the case where the rib rubber portions 651 and 652 are provided on the mass member 610 with the case where the rib rubber portions 651 and 652 are provided on the counter plate portion 525, the rib rubber portions 651 and 652 are the former and the latter. If the protruding rubber portions 651 and 652 are formed integrally with the covering rubber portion 640 (that is, provided on the mass member 610), the protruding rubber portions are the same. The rubber volume of the base part of 651, 652 is secured by being integrated with the covering rubber part 640, while the tip end part of the protruding rubber part 651, 652 is tapered to reduce the rubber volume. The effect can be exhibited effectively, and the volume of the hit sound can be reduced and the timbre can be changed.

  The buffer members 661 and 662 are members for suppressing the impact when the displacement of the mass member 610 is restricted by the bracket member 620 (when the upper surface 611 side of the mass member 610 collides with the opposing plate portion 525), and is elastic. The material is formed into a sheet shape, and is attached to a covering rubber portion 640 that covers the upper surface 611 of the mass member 610 as shown in FIGS. 11 to 14.

  In the present embodiment, the buffer members 661 and 662 are made of urethane sheet material, and an adhesive sheet layer is laminated on the back surface of the sheet material, and through the adhesive sheet layer, The buffer members 661 and 662 are attached to the covering rubber portion 640.

  As shown in FIG. 13A, the buffer members 661 and 662 are configured in a horizontally long belt shape, and are disposed between the facing rubber portions 651 and 652, and the protruding rubber portions 651 and 652. It is arrange | positioned in the state which put the long side along the edge of the upper surface 611 used as the extension direction edge part side (FIG. 13 (a) upper side and lower side).

  As described above, the seat damper 600 is configured by sticking the buffer members 661 and 662 to the edge on the upper surface 611 of the mass member 610 and on the end side in the extending direction of the protruding rubber portions 651 and 652. Therefore, it is possible to improve the life of the protrusion rubber portions 651 and 652 while suppressing the occurrence of hitting sound and changing the tone color.

  That is, as shown in FIG. 13A or FIG. 14A, the protruding rubber portions 651 and 652 are perpendicular to the direction connecting the standing plate portions 623 and 624 (the vertical direction in FIG. 13A). When the mass member 610 is displaced in the rotational direction (for example, in FIG. 14A, the side surface 15 side approaches the counter plate portion 525, while the side surface 16 side moves away from the counter plate portion 525. In the case where the mass member 610 is displaced in the direction), the displacement in the rotational direction is received only by the extended end portions (FIG. 14 (a) left and right end portions) of the protrusion rubber portions 651 and 652.

  For this reason, the pressure receiving area is reduced and the buffering effect cannot be sufficiently exerted, so that the volume of the hitting sound is increased and the burden on the protruding rubber portions 651 and 652 is increased, and the end portion is damaged. As a result, the service life is reduced.

  On the other hand, according to the seat damper 600 in the present embodiment, the buffer members 661 and 662 are attached to the edge of the upper surface 611 on the extending direction end side of the protruding rubber portions 651 and 652, so Even when the member 610 is displaced in the rotational direction as described above, the displacement in the rotational direction can be received not only by the end portions of the protruding rubber portions 651 and 652, but also by the buffer members 661 and 662, so that the pressure receiving area And the buffering effect can be sufficiently exerted, so that the volume of the hitting sound can be reduced and the burden on the ridge rubber portions 651 and 652 can be reduced to suppress the breakage thereof. Can do.

  Moreover, since it is the structure which attaches a buffer member by sticking, and the attachment position (sticking position) is the edge part which becomes the extension direction edge part side of a protrusion rubber part, attachment work of a buffer member is easy. It can be carried out. As a result, the assembly cost can be reduced, and the product cost of the entire seat damper can be reduced.

  In addition, the thickness dimension (FIG. 13 (b) vertical direction dimension) of the buffer members 661 and 662 is the height dimension (FIG. 13 (b) or FIG. 14 (a)) of the protrusion rubber portions 651 and 652. 13 (b) vertical dimension), the facing distance between the buffer members 661, 662 and the opposing plate portion 525 is between the protruding rubber portions 651, 652 and the opposing plate portion 525. It is comprised so that it may become larger than an opposing space | interval.

  Therefore, when the mass member 610 is displaced in the rotational direction as described above, first, the protrusion rubber portions 651 and 652 receive the displacement in the rotational direction, and then the buffer members 661 and 662 receive. Therefore, such displacement can be received more smoothly. As a result, the buffering effect can be exhibited more effectively, the volume of the hitting sound can be reduced, and the timbre can be changed to a timbre with less discomfort.

  Here, as shown in FIG. 15A, the seat damper 600 according to the present embodiment is more than the center in the thickness direction of the mass member 610 (an intermediate portion between the top surface 611 and the bottom surface 612) in the side view. The vibration isolating base 630 (first to fourth connecting bases 631 to 634) is connected to the side surfaces 613 and 614 of the mass member 610 in a state where the position is shifted by the distance s to the upper surface 611 side.

  In FIG. 15A, the imaginary line L1 is an imaginary line passing through the center of the mass member 610 in the thickness direction, and the imaginary line L2 is the anti-vibration base 630 (first to fourth connecting bases 631 to 634). Is a virtual line passing through the center of the thickness direction (vertical direction in FIG. The distance s between the virtual lines L1 and L2 is the amount of positional deviation of the vibration isolation base 630.

  As described above, according to the seat damper 600 in the present embodiment, since the vibration isolating base 630 is connected to the mass member 610 in a position-shifted state, the resonance action for suppressing the harmful vibration of the sheet S1 is achieved. It can be obtained in a wide frequency range.

  That is, for example, as shown in FIG. 16B, the resonance action of the seat damper has a characteristic that it rapidly decreases when the frequency of the vibration system slightly deviates from the resonance frequency, and is sufficient only in a very narrow frequency region. The effect cannot be obtained. Therefore, it is necessary to accurately match the resonance frequency of the vibration system with the peak frequency of harmful vibration.

  However, the peak frequency of harmful vibrations occurring in the seat S1 usually varies from vehicle to vehicle due to, for example, dimensional variations and weight variations of the members constituting the seat S1. For this reason, in the conventional seat damper, it is difficult to accurately match the resonance frequency of the vibration system with the peak frequency of the harmful vibration in question, and the harmful vibration cannot be sufficiently reduced.

  On the other hand, according to the sheet damper 600 in the present embodiment, as described above, the vibration isolating base 630 is farther from the center in the thickness direction between the upper surface 611 and the bottom surface 612 of the mass member 610 to the upper surface 611 side. The vibration isolating base 630 supports a position connected to the mass member 610 in a state shifted by s (ie, offset from the center of gravity of the mass member 610 in the thickness direction (vertical direction in FIG. 16A)). ).

  Therefore, when harmful vibration occurs in the seat S1 and the mass member 610 as a mass body is displaced along with the harmful vibration, the mass member 610 is moved in two vibration modes (for example, the vehicle longitudinal direction (arrow It is possible to vibrate in two directions (the FB direction) and the rotation direction, or two vibration modes in the vehicle left-right direction (arrow LR direction) and the rotation direction).

  As a result, as shown in FIG. 15B, the resonance peaks of each of the two vibration modes can be obtained, and the connection position of the vibration-proof base 630 is not offset by superimposing these vibration modes. Compared with the case (see FIG. 16A and FIG. 16B), the resonance action can be obtained in a wider frequency range.

  As a result, even if the peak frequency of harmful vibration generated in the sheet S1 does not match the preset frequency value due to dimensional variation or weight variation of the component parts, By exerting the resonance effect, harmful vibrations of the sheet S1 can be sufficiently reduced.

  Further, in the sheet damper 600 according to the present embodiment, the mass member 610 is raised by the vibration isolating base 630 (first to fourth connecting bases 631 to 634) at four locations, both ends of the side 613 and both ends of the side 614. Since the structure is connected to the plate portions 623 and 624 (see FIG. 12), the mass member 610 can be easily vibrated in two vibration modes, and the resonance frequencies of these two vibration modes can be appropriately set. Can be set to a frequency value.

  That is, when the mass member 610 is configured to be connected to the standing plate portions 623 and 624 by the vibration isolation base at only two places in total, for example, the side surface 613 and the side surface 614, the resonance frequencies of the two vibration modes are respectively Although the frequency values are greatly different and it is difficult to obtain the effect of superimposing the two vibration modes, as shown above, the both ends of each of the side surfaces 613 and 614 are connected at a total of four locations as shown in FIG. Thus, the two vibration modes can be expressed with a good balance.

  Here, the facing distance between the first connection base 631 and the second connection base 632 (the distance in the vertical direction in FIG. 2 at the center of the width direction (the vertical direction in FIG. 12) of each connection base 631, 632) is the mass member 610. It is preferable that the width is set to 40% or more and 80% or less of the width dimension (the dimension between the side surfaces 15 and 16). This is because when the width dimension exceeds the above range, the difference between the resonance frequencies of the two resonance modes tends to be excessive, and it is difficult to obtain the effect of the above-described superposition.

  In the present embodiment, the facing distance between the first connection base 631 and the second connection base 32 described above is set to 50% of the width of the mass member 10. Since the distance between the third connection base 33 and the fourth connection base 34 is also set to the same dimension value, the description thereof is omitted.

  Next, a seventh embodiment will be described with reference to FIG. FIG. 17 is a top view of the seat damper 700 according to the seventh embodiment. In FIG. 17, for easy understanding, the protruding rubber portions 651 and 652 and part of the protruding rubber portions 751 and 752 are shown by broken lines.

  In the first embodiment, the case where the pair of protruding rubber portions 51 and 52 are provided on the upper surface 11 of the mass member 10 has been described (see FIG. 3), but in the seventh embodiment, the pair of protruding rubber portions 651. A pair of protruding rubber portions 751 and 752 are further disposed on the outer side of 652, and a total of four are disposed on the upper surface 611 of the mass member 610. In addition, the same code | symbol is attached | subjected to the part same as each above-mentioned embodiment, and the description is abbreviate | omitted.

  As shown in FIG. 17, the seat damper 700 according to the seventh embodiment is provided with a pair of protruding rubber portions 751 and 752 outside the protruding rubber portions 651 and 652 (on the standing plate portions 623 and 624 side). Configured. As shown in FIG. 17, the protruding rubber portions 751 and 752 are configured by omitting end portions in the extending direction (vertical direction in FIG. 17) and shorter than the protruding rubber portions 651 and 652.

  The present invention has been described above based on the embodiments. However, the present invention is not limited to the above embodiments, and various improvements and modifications can be made without departing from the spirit of the present invention. It can be easily guessed.

  For example, the numerical values given in the above embodiments are merely examples, and other numerical values can naturally be adopted.

  In each of the above embodiments, the case where the buffer members 61, 62, 661a to 662b are attached to the mass members 10, 610 (covering rubber portions 40, 640) has been described. However, the present invention is not necessarily limited thereto. Of course, it is possible to adhere to the opposing plate portions 25 and 625. Or you may affix on both the mass members 10 and 610 and the opposing board parts 25 and 625. FIG.

  In each of the above embodiments, the automobile is described as an example of the vehicle having the seats S1 and S2 to which the seat dampers 100 to 600 of the present invention are applied. However, the invention is not necessarily limited to the automobile, and other vehicles are adopted. Of course it is possible to do. For example, a train etc. are illustrated as another vehicle.

  It is naturally possible to apply the technical idea of each of the above embodiments to other embodiments or to combine the above embodiments. For example, as described in the second and third embodiments, the technical idea of configuring the openings 26 and 27 and the protruding rubber portions 251 to 352 to overlap in a top view is the sixth or the sixth. You may apply to 7 embodiment.

  Further, for example, as described in the fourth embodiment, the technical idea in which the protrusion rubber portion 453 is further provided between the pair of protrusion rubber portions 51 and 52 is configured from the first to third embodiments. Alternatively, the present invention may be applied to the fifth to seventh embodiments.

  Further, for example, as described in the fourth embodiment, the technical idea of changing the protruding height of the protrusion rubber portion 453 in the extending direction is the first to third embodiments or the fifth to seventh. You may apply to one or all the protrusion rubber | gum parts 51 grade | etc., In embodiment.

  Further, for example, as described in the sixth embodiment, the technical idea of configuring the connection position of the vibration isolation base 630 with respect to the mass member 610 by offsetting the first to fifth embodiments or the seventh embodiment. You may apply to.

  Further, for example, as described in the seventh embodiment, the technical idea of providing a pair of protruding rubber portions 751 and 752 outside the pair of protruding rubber portions 651 and 652, and the protruding rubber portion The technical idea of omitting the formation of the extending direction end portions 751 and 752 may be applied to the first to sixth embodiments.

  In the first to fourth embodiments, the case where the openings 26 and 27 are configured to be circular with the same diameter has been described. However, it is not always necessary to have the same diameter, and different diameters are naturally possible. is there. By configuring the openings 26 and 27 with different diameters, different natural frequencies can be provided, so that the timbre of the hitting sound can be changed to a timbre with less discomfort.

  In the fourth embodiment, a case has been described in which the top of the protrusion rubber portion 453 is inclined downward in a straight line from the center toward the end (see FIG. 9B), but is not necessarily limited to a straight line. Of course, other shapes are possible.

  For example, as another shape, the structure which curves in the convex curve shape toward the opposing board part 25 is illustrated. Thereby, when the mass member is displaced in the rotation direction, the top portion of the protruding rubber portion 453 can be gradually brought into contact with the opposing plate portion 25, and the function as a buffer member can be more effectively exhibited. Can do.

  In the sixth embodiment, the case where the direction of displacement of the vibration isolation base 630 with respect to the mass member 610 is given in the thickness direction of the mass member 610 (the vertical direction in FIG. 15A) is described. It is not limited, and it is naturally possible to apply in other directions. For example, it may be applied in the width direction of the mass member 610 (FIG. 15A, the direction perpendicular to the paper surface). Further, the positional deviation direction does not need to coincide with the vehicle front-rear direction, and may correspond to another direction (for example, the vehicle left-right direction).

(A) is a top view of the seat damper in 1st Embodiment of this invention, (b) is a side view of a seat damper. It is a bottom view of a sheet damper. (A) is a partial cross-sectional top view of a seat damper, and (b) is a cross-sectional view of the seat damper taken along line IIIb-IIIb in FIG. (A) is sectional drawing of the sheet damper in the IVa-IVa line of FIG. 1, (b) is the elements on larger scale of the IVb part of FIG.3 (b). It is a top view of the sheet damper in a 2nd embodiment. It is a partial expanded sectional view of a sheet damper. It is a top view of the sheet damper in a 3rd embodiment. It is a top view of the sheet damper in a 4th embodiment. (A) is sectional drawing of the sheet damper in the IXa-IXa line of FIG. 8, (b) is sectional drawing of the sheet damper in the IXb-IXb line of FIG. It is a top view of the sheet damper in a 5th embodiment. (A) is a top view of the seat damper in 6th Embodiment, (b) is a side view of a seat damper. It is a bottom view of a sheet damper. FIG. 13A is a partial cross-sectional top view of the seat damper, and FIG. 13B is a cross-sectional view of the seat damper taken along line XIIIb-XIIIb in FIG. 12. It is sectional drawing of the sheet | seat damper in the XIVa-XIVa line | wire of FIG. (A) is a side view of a seat damper, (b) is a graph which shows the frequency response of a seat damper. (A) is a side view of a seat damper that does not have an offset of the connection position of the vibration-proof substrate, and (b) is a graph showing the frequency response of the seat damper. It is a top view of the sheet damper in a 7th embodiment. (A) is a side view of a sheet | seat, (b) is a front view of a sheet | seat.

Explanation of symbols

100, 200, 300, 400, 500, 600, 700 Sheet damper 10, 610 Mass member 11, 611 Top surface 12, 612 Bottom surface 13, 14, 613, 614 Side surface (side surface to which vibration-proof substrate is connected)
20,620 Bracket members 21, 22, 621, 622 Mounting plate portions 23, 24, 623, 624 Standing plate portions 25, 625 Opposing plate portions 26, 27, 526, 527, 626 Opening portions 30, 630 31, 631 First connection base 32, 632 Second connection base 33, 633 Third connection base 34, 634 Fourth connection base 35, 635 First stopper portion 36, 636 Second stopper portion 40, 640 Covering rubber portion 51 , 251, 351, 451, 651, 751 ridge rubber part 52, 252, 352, 452, 652, 752 ridge rubber part 453 ridge rubber part 61, 461 a, 461 b, 661 buffer member 62, 462 a, 462 b, 662 Buffer member S1, S2 sheet

Claims (12)

A seat damper attached to a vehicle seat, a mass member functioning as a mass body, a bracket member attached to the seat, and connecting the bracket member and the mass member together with a rubber-like elastic material In a seat damper comprising an anti-vibration base composed of
The bracket member includes a pair of attachment plate portions to be attached to the sheet, and rises from the pair of attachment plate portions to face each other in parallel with a predetermined interval therebetween, and is connected to the mass via the vibration isolation base. A pair of upright plate portions to which the members are connected, and opposed plate portions that connect the rising ends of the pair of upright plate portions and face each other in parallel with the upper surface of the mass member at a predetermined interval;
The mass member is formed in a rectangular parallelepiped shape from the top surface, a bottom surface facing the top surface, and four side surfaces connecting the top surface and the bottom surface, and two of the four side surfaces facing each other in parallel. Side surfaces are respectively connected to a pair of upright plate portions of the bracket member via the vibration isolation base,
The bracket member includes an opening formed by opening the counter plate in the thickness direction.   A ridge shape that is provided from the upper surface of the mass member toward the lower surface of the opposing plate portion and that extends in a direction orthogonal to the direction connecting the pair of standing plate portions and is made of a rubber-like elastic material. The seat damper according to claim 1, further comprising a protruding rubber portion.   The seat damper according to claim 2, wherein the opening is formed at two locations of the counter plate portion. The rubber-like elastic material is integrally formed with the vibration-proof base, and includes a covering rubber portion that covers the mass member,
The seat damper according to claim 2 or 3, wherein the protruding rubber portion is configured integrally with the covering rubber portion.   The seat damper according to claim 4, wherein the covering rubber portion exposes the four corner portions where the four side surfaces of the mass member are connected to each other and covers the remaining portions except for the four corner portions. Openings formed at two locations of the opposing plate portion are disposed along a direction connecting the pair of standing plate portions,
4. The protruding rubber portion is disposed at a position overlapping at least a region on the side of the standing plate portion with respect to the central portion of the opening in a top view of the mass member. The described seat damper.   The said protruding rubber part is arrange | positioned in the position by which at least one part of the said protruding rubber part is parted by the edge of the said opening part in the top view of the said mass member. The described seat damper.   The protruding rubber part has a lower protruding height from the upper surface of the mass member toward the both ends of the protruding rubber part in the extending direction, and the protruding height is maximum in the extending direction central part. The seat damper according to any one of claims 2 to 7, wherein the seat damper is configured as follows. It is composed of an elastic material, and includes a buffer member that is attached to either the upper surface of the mass member or the lower surface of the counter plate part,
The said buffer member is an upper surface of the mass member or a lower surface of the counter plate portion, and is attached to an edge portion on the end side in the extending direction of the protruding rubber portion. The seat damper according to any one of 2 to 8.   The side surface of the mass member is shifted to the upper surface side or the bottom surface side from the center in the thickness direction between the upper surface and the bottom surface of the mass member in a side view of the mass member. The seat damper according to claim 1, wherein the seat damper is connected to each other.   The vibration-proof base includes a first connection base and a second connection base that connect one side surface of the two side surfaces of the mass member and one of the pair of upright plate portions. A third connection base and a fourth connection base for connecting the other side surface of the two side surfaces of the mass member and the other vertical plate portion of the pair of vertical plate portions; The seat damper according to claim 10, wherein the member is connected to and supported by the upright plate portion at four locations of both end portions of the one side surface and both end portions of the other side surface.   The anti-vibration base is located between the first connection base and the second connection base, the first stopper portion protruding from the one standing plate portion toward the one side surface, and the third 12. A second stopper portion located between the connecting base and the fourth connecting base and projecting from the other standing plate portion toward the other side surface is provided. Seat damper.

Images