JP5817385B2 - Vehicle body structure - Google Patents

Vehicle body structure Download PDF

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JP5817385B2
JP5817385B2 JP2011208376A JP2011208376A JP5817385B2 JP 5817385 B2 JP5817385 B2 JP 5817385B2 JP 2011208376 A JP2011208376 A JP 2011208376A JP 2011208376 A JP2011208376 A JP 2011208376A JP 5817385 B2 JP5817385 B2 JP 5817385B2
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section
reinforcing
bulkhead
vibration damping
cross
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JP2013067308A (en
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治 黒木
治 黒木
杉原　毅
毅 杉原
興也 中川
興也 中川
長尾　邦昭
邦昭 長尾
栄 寺田
栄 寺田
三穂 蔵田
三穂 蔵田
小畑　聡
聡 小畑
章 伊吉
章 伊吉
重昭 渡邊
重昭 渡邊
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Mazda Motor Corp
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Mazda Motor Corp
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Description

この発明は、１または２以上の車両部材により形成される閉断面部または開断面部における車両の車体構造に関し、詳しくは、乗り心地を向上させ、また、騒音の発生を防止するために車両用部材に伝達される振動を低減するような車両の車体構造に関する。   The present invention relates to a vehicle body structure in a closed cross section or an open cross section formed by one or two or more vehicle members, and more particularly, for a vehicle for improving riding comfort and preventing noise generation. The present invention relates to a vehicle body structure that reduces vibration transmitted to a member.

従来より自動車等の車両における乗り心地を向上させ、また、騒音の発生を防止するために、車両用部材に伝達される振動を低減するように構成した諸種の技術が知られている。   2. Description of the Related Art Conventionally, various techniques are known that are configured to reduce vibration transmitted to a vehicle member in order to improve riding comfort in a vehicle such as an automobile and to prevent generation of noise.

例えば、特許文献１には、断面ハット形状のフレーム部材（骨格部材）とパネル部材（副材）とから成る閉断面部を設け、この閉断面部の内部にビードを一体形成した隔壁部材（いわゆるバルクヘッド）を設けると共に、該隔壁部材に一体に折曲げ形成したフランジ部を、断面ハット形状のフレーム部材の内壁と結合して、フレーム部材の強度、剛性を高めたものが開示されている。   For example, Patent Document 1 discloses a partition wall member (so-called partition wall member) in which a closed cross-section portion including a frame member (frame member) having a cross-sectional hat shape and a panel member (secondary material) is provided, and a bead is integrally formed in the closed cross-section portion. (Bulk head) is provided, and a flange portion formed integrally with the partition wall member is combined with the inner wall of the frame member having a hat-shaped cross section to increase the strength and rigidity of the frame member.

この特許文献１に開示された従来構造においては、上述の隔壁部材により閉断面部の断面崩れを抑えて、フレーム部材の強度、剛性を高め、この剛性を高めることにより、ある程度振動を低減することができるが、まだ充分ではなく、振動を効果的に抑制することができない、という問題点があった。   In the conventional structure disclosed in Patent Document 1, the above-described partition wall member suppresses the collapse of the cross section of the closed cross section, increases the strength and rigidity of the frame member, and reduces the vibration to some extent by increasing the rigidity. However, there is a problem that it is not sufficient yet and vibrations cannot be effectively suppressed.

特開２００６−１３１１２５号公報JP 2006-131125 A

そこで、この発明は、閉断面部または開断面部の剛性を確保し、閉断面部または開断面部の断面崩れによる揺動変形を抑制すると共に、振動減衰部材により効果的に振動減衰を行なうことができて、乗り心地を向上させ、また騒音の低減を図ることができる車両の車体構造の提供を目的とする。   Therefore, the present invention secures the rigidity of the closed cross section or the open cross section, suppresses the swing deformation due to the collapse of the cross section of the closed cross section or the open cross section, and effectively attenuates the vibration by the vibration damping member. It is an object of the present invention to provide a vehicle body structure that can improve the ride comfort and reduce noise.

この発明による車両の車体構造は、１または２以上の車両部材により形成される閉断面部または開断面部における車両の車体構造であって、上記閉断面部または上記開断面部の内部に結合される補強体を備え、該補強体は第１補強部と第２補強部とからなり、上記第１補強部と上記第２補強部とは重ね合せ部を有し、上記第１補強部は上記閉断面部または上記開断面部の内壁と結合され、上記第２補強部は上記閉断面部または上記開断面部の内壁と結合されており、上記第１補強部と上記第２補強部とが上記重ね合せ部の少なくとも一部において振動減衰部材を介して結合され、上記重ね合せ部の１箇所または２箇所以上において、上記第１補強部と上記第２補強部とが剛結合されたものである。
上述の閉断面部は、断面ハット形状のフレーム部材とパネル部材とで形成してもよく、また、上述の開断面部は、断面ハット形状のフレーム部材で形成してもよい。
さらに、上述の補強体の結合は、溶接結合、接着結合、締結結合の何れでもよく、また、上述の振動減衰部材としては粘弾性部材、特に、損失係数（２０℃、３０ＨＺ）が０．２以上の粘弾性部材が好ましい。 A vehicle body structure according to the present invention is a vehicle body structure in a closed section or an open section formed by one or more vehicle members, and is coupled to the inside of the closed section or the open section. The reinforcing body comprises a first reinforcing portion and a second reinforcing portion, and the first reinforcing portion and the second reinforcing portion have an overlapping portion, and the first reinforcing portion is The closed cross section or the inner wall of the open cross section is coupled, and the second reinforcing section is coupled to the closed cross section or the inner wall of the open cross section, and the first reinforcing section and the second reinforcing section are At least a part of the overlapping portion is coupled via a vibration damping member , and the first reinforcing portion and the second reinforcing portion are rigidly coupled at one or two or more locations of the overlapping portion. is there.
The closed cross section described above may be formed by a frame member having a cross section hat shape and a panel member, and the open cross section described above may be formed by a frame member having a cross section hat shape.
Further, the above-mentioned reinforcing body may be bonded by any of welded, adhesive, and fastening connections, and the above-described vibration damping member may be a viscoelastic member, particularly having a loss factor (20 ° C., 30 H Z ) of 0. Two or more viscoelastic members are preferred.

上記構成によれば、補強体を第１補強部と第２補強部との２つに分割し、これらの各補強部を閉断面部または開断面部の内壁と結合したので、補強体により閉断面部または開断面部の断面崩れによる揺動変形を抑制することができる。
しかも、第１補強部と第２補強部とが重ね合せ部の少なくとも一部において振動減衰部材を介して結合されているので、この振動減衰部材により効果的に振動減衰を行なうことができる。
要するに、補強体により閉断面部または開断面部の剛性を確保しつつ、振動減衰部材により振動を効果的に抑制することができ、乗り心地を向上させ、また騒音の低減を図ることができる効果がある。
さらに上記構成によれば、重ね合せ部において第１補強部と第２補強部とを剛結合したので、これら第１補強部と第２補強部との位置ずれが生じにくくなり、補強体の閉断面部または開断面部に対する組付け性の向上を図ることができる。 According to the above configuration, the reinforcing body is divided into two parts, the first reinforcing part and the second reinforcing part, and these reinforcing parts are connected to the closed cross-section part or the inner wall of the open cross-sectional part. Oscillating deformation due to the collapse of the cross section of the cross section or open cross section can be suppressed.
In addition, since the first reinforcing portion and the second reinforcing portion are coupled via the vibration damping member in at least a part of the overlapped portion, the vibration damping member can effectively perform vibration damping.
In short, the vibration damping member can effectively suppress vibrations while ensuring the rigidity of the closed cross section or the open cross section by the reinforcing body, and can improve riding comfort and reduce noise. There is.
Further, according to the above configuration, since the first reinforcing portion and the second reinforcing portion are rigidly connected in the overlapping portion, the positional displacement between the first reinforcing portion and the second reinforcing portion is less likely to occur, and the reinforcing body is closed. The assembling property with respect to the cross section or the open cross section can be improved.

この発明の一実施態様においては、上記第１補強部と上記閉断面部または上記開断面部の内壁との結合部と、上記第２補強部と上記閉断面部または上記開断面部の内壁との結合部とが、略対向する内壁面に設けられたものである。
上記構成によれば、第１補強部の上記結合部と、第２補強部の上記結合部とが略対向する内壁面に設けられ、これらの各結合部がそれぞれ対向する面に剛結合されるので、第１補強部と第２補強部との重ね合せ部は相対的な変位が生じやすく、該重ね合せ部に介設した振動減衰部材にてより一層高い振動減衰効果が得られる。
因みに、相対的な変位が全くない場合には振動減衰部材で振動減衰を行なうことはできないので、この実施形態では、第１補強部と第２補強部との重ね合せ部、つまり各部の自由端側に相対的な変位が生じやすいように構成したものである。 In one embodiment of the present invention, a connecting portion between the first reinforcing portion and the closed cross-section portion or the inner wall of the open cross-section portion, the second reinforcing portion and the closed cross-section portion or the inner wall of the open cross-section portion, Are provided on substantially opposite inner wall surfaces.
According to the said structure, the said coupling | bond part of a 1st reinforcement part and the said coupling | bond part of a 2nd reinforcement part are provided in the inner wall surface which substantially opposes, and these each coupling | bond part are each rigidly coupled to the surface which each opposes. Therefore, the overlapping portion of the first reinforcing portion and the second reinforcing portion is likely to be relatively displaced, and a higher vibration damping effect can be obtained by the vibration damping member interposed in the overlapping portion.
Incidentally, if there is no relative displacement at all, vibration damping cannot be performed by the vibration damping member. Therefore, in this embodiment, the overlapping portion of the first reinforcing portion and the second reinforcing portion, that is, the free end of each portion. It is configured so that relative displacement is likely to occur on the side.

この発明の一実施態様においては、上記重ね合せ部が、上記補強体の縁上の一点と他点とを結んでなる最長の直線となるように設けられたものである。
上述の最長の直線は、補強体が略四角形の場合には対角線となる。
上記構成によれば、重ね合せ部に介設する振動減衰部材の設定面積を、可能な限り大きくすることができ、これにより振動減衰能力の向上を図ることができる。 In one embodiment of the present invention, the overlapping portion is provided so as to be the longest straight line connecting one point on the edge of the reinforcing body and another point.
The longest straight line described above is a diagonal line when the reinforcing body is substantially square.
According to the said structure, the setting area of the vibration damping member interposed in the overlapping part can be enlarged as much as possible, and the improvement of a vibration damping capability can be aimed at by this .

この発明の一実施態様においては、上記第１補強部と上記第２補強部とが重ね合せ部の２箇所以上で剛結合されたものにおいて、該剛結合部位が上記重ね合せ部の長手方向の端部を避けるように設けられたものである。
上記構成によれば、振動減衰部材による振動減衰能力を損なうことなく、補強体の閉断面部または開断面部に対する組付け性の向上を図ることができる。
因みに、剛結合部位が重ね合せ部の長手方向の両端部に設けられた場合には、第１補強部と第２補強部との相対的な変位が抑制されて、振動減衰効果が僅小となるので、相対的な変位が得られるように重ね合せ部の長手方向の端部を避けて剛結合部位を設けるものである。 In one embodiment of this invention, in which the a first reinforcing portion and the second reinforcing portion is rigidly connected at two or more mating portions overlapping longitudinal mating portion rigid binding sites the overlapped It is provided so as to avoid the end of the.
According to the said structure, the improvement of the assembly | attachment property with respect to the closed cross-section part or open cross-section part of a reinforcement body can be aimed at, without impairing the vibration damping capability by a vibration damping member.
Incidentally, when the rigid coupling portions are provided at both ends in the longitudinal direction of the overlapping portion, the relative displacement between the first reinforcing portion and the second reinforcing portion is suppressed, and the vibration damping effect is small. Therefore, the rigid coupling portion is provided so as to avoid the end portion in the longitudinal direction of the overlapping portion so as to obtain a relative displacement.

この発明によれば、閉断面部または開断面部の剛性を確保し、閉断面部または開断面部の断面崩れによる揺動変形を抑制すると共に、振動減衰部材により効果的に振動減衰を行なうことができて、騒音の低減を図ることができる効果がある。   According to the present invention, the rigidity of the closed cross-section or open cross-section is ensured, the swing deformation due to the cross-sectional collapse of the closed cross-section or open cross-section is suppressed, and vibration damping is effectively performed by the vibration damping member. This is effective in reducing noise.

本発明の車両の車体構造を示す分解斜視図1 is an exploded perspective view showing a vehicle body structure of a vehicle according to the present invention. 補強体の斜視図Perspective view of reinforcement 車両の車体構造を示す正面図Front view showing the vehicle body structure 車両の車体構造の他の実施例を示す斜視図The perspective view which shows the other Example of the vehicle body structure of a vehicle 補強体の斜視図Perspective view of reinforcement 車両の車体構造を示す正面図Front view showing the vehicle body structure シミュレーション解析方法を示す加振点と応答点の説明図Illustration of excitation point and response points showing the simulation analysis method （ａ）は溶接箇所を１箇所と成した補強体の斜視図、（ｂ）は図８（ａ）の補強体を備えた本実施例品と比較例品との解析データを比較して示す特性図(A) is a perspective view of a reinforcing body having a single welded portion, and (b) is a comparison of analytical data of the product of this example and the comparative example product provided with the reinforcing body of FIG. 8 (a). Characteristics chart （ａ）は溶接箇所を２箇所と成した補強体の斜視図、（ｂ）は図９（ａ）の補強体を備えた本実施例品と比較例品との解析データを比較して示す特性図(A) is a perspective view of a reinforcing body having two welds, and (b) shows a comparison of analysis data of the product of this example and the comparative product provided with the reinforcing body of FIG. 9 (a). Characteristics chart （ａ）は溶接箇所を３箇所と成した補強体の斜視図、（ｂ）は図１０（ａ）の補強体を備えた本実施例品と比較例品との解析データを比較して示す特性図(A) is a perspective view of a reinforcing body having three welds, and (b) shows a comparison of analysis data of the product of this example and the comparative product provided with the reinforcing body of FIG. 10 (a). Characteristics chart スポット溶接部のピッチと振動低減量との関係を示す特性図Characteristic diagram showing the relationship between the pitch of spot welds and the amount of vibration reduction （ａ）は車両の車体構造の他の実施例を示す正面図、（ｂ）は車両の車体構造のさらに他の実施例を示す正面図、（ｃ）は車両の車体構造のさらに他の実施例を示す正面図(A) is a front view showing another embodiment of the vehicle body structure of the vehicle, (b) is a front view showing still another embodiment of the vehicle body structure of the vehicle, and (c) is still another embodiment of the vehicle body structure of the vehicle. Front view showing an example （ａ）は車両の車体構造の参考例を示す斜視図、（ｂ）は図１３（ａ）のＢ‐Ｂ線矢視断面図(A) is a perspective view which shows the reference example of the vehicle body structure of a vehicle, (b) is a BB sectional view taken on the line in FIG. 13 (a).

閉断面部または開断面部の剛性を確保し、閉断面部または開断面部の断面崩れによる揺動変形を抑制すると共に、振動減衰部材により効果的に振動減衰を行なうことができて、乗り心地を向上させ、また騒音の低減を図るという目的を、１または２以上の車両部材により形成される閉断面部または開断面部における車両の車体構造において、上記閉断面部または上記開断面部の内部に結合される補強体を備え、該補強体は第１補強部と第２補強部とからなり、上記第１補強部と上記第２補強部とは重ね合せ部を有し、上記第１補強部は上記閉断面部または上記開断面部の内壁と結合され、上記第２補強部は上記閉断面部または上記開断面部の内壁と結合されており、上記第１補強部と上記第２補強部とが上記重ね合せ部の少なくとも一部において振動減衰部材を介して結合されるという構成にて実現した。   The rigidity of the closed cross section or open cross section can be ensured, and the vibration deformation caused by the collapse of the cross section of the closed cross section or open cross section can be suppressed. In the vehicle body structure of a vehicle in a closed cross section or an open cross section formed by one or two or more vehicle members, the interior of the closed cross section or the open cross section is provided. The reinforcing body is composed of a first reinforcing portion and a second reinforcing portion, and the first reinforcing portion and the second reinforcing portion have an overlapping portion, and the first reinforcing portion And the second reinforcing portion is connected to the inner wall of the closed cross-section portion or the open cross-section portion, and the first reinforcing portion and the second reinforcing portion are connected to the inner wall of the closed cross-section portion or the open cross-section portion. At least part of the overlapped part It was realized by configurations that are coupled via the vibration damping member Te.

この発明の一実施例を以下図面に基づいて詳述する。
まず、図１〜図３を参照して車両の車体構造を閉断面部に適用した実施例について説明する。
図１は車両の車体構造を示す分解斜視図、図２は補強体の斜視図、図３は図１の正面図であって、図１〜図３において、２つの車両部材として断面ハット形状のフレーム部材１０（骨格部材）とパネル部材２０とで閉断面部３０（図３参照）を形成している。
上述のフレーム部材１０は、基壁１１と、この基壁１１に連続する一対の側壁１２，１３と、これら側壁１２，１３の端部から外方に延びるフランジ部１４，１５とを一体形成した車両部材である。
また、上述のパネル部材２０としては偏平な部材を例示したが、これはフレーム部材１０と同様に断面ハット形状の部材であってもよい。 An embodiment of the present invention will be described in detail with reference to the drawings.
First, an embodiment in which the vehicle body structure of a vehicle is applied to a closed cross section will be described with reference to FIGS.
1 is an exploded perspective view showing a vehicle body structure of a vehicle, FIG. 2 is a perspective view of a reinforcing body, and FIG. 3 is a front view of FIG. 1, and in FIGS. The frame member 10 (frame member) and the panel member 20 form a closed section 30 (see FIG. 3).
The frame member 10 described above is integrally formed with a base wall 11, a pair of side walls 12 and 13 continuing to the base wall 11, and flange portions 14 and 15 extending outward from the end portions of the side walls 12 and 13. It is a vehicle member.
Moreover, although the flat member was illustrated as the above-mentioned panel member 20, this may be a member of a cross-sectional hat shape similarly to the frame member 10.

図３に示すように、上述の閉断面部３０の内部に結合される補強体としての略四角形状のバルクヘッド４０を設けるが、この実施例では、該バルクヘッド４０を、図３の左側かつ上側に位置する第１バルクヘッド４１と、図３の右側かつ下側に位置する第２バルクヘッド４２とに２分割している。   As shown in FIG. 3, a substantially square bulkhead 40 is provided as a reinforcing body coupled to the inside of the above-described closed section 30. In this embodiment, the bulkhead 40 is connected to the left side of FIG. The first bulkhead 41 located on the upper side and the second bulkhead 42 located on the right side and lower side in FIG. 3 are divided into two.

図２，図３に示すように、第１バルクヘッド４１は略直角三角形状に形成され、その直角部が閉断面部３０内の図示左上コーナ部に位置するように配設されるもので、この第１バルクヘッド４１の左辺および上辺にはフランジ部４１ａ，４１ｂが一体的に折曲げ形成されている。   As shown in FIGS. 2 and 3, the first bulkhead 41 is formed in a substantially right triangle shape, and the right angle portion is disposed so as to be positioned at the upper left corner in the closed cross section 30. Flange portions 41 a and 41 b are integrally bent at the left side and the upper side of the first bulkhead 41.

図２，図３に示すように、第２バルクヘッド４２も略直角三角形状に形成され、その直角部が閉断面部３０内の図示右下コーナ部に位置するように配設されるもので、この第２バルクヘッド４２の右辺および下辺にはフランジ部４２ａ，４２ｂが一体的に折曲げ形成されている。   As shown in FIGS. 2 and 3, the second bulkhead 42 is also formed in a substantially right triangle shape, and is disposed so that the right angle portion is positioned at the lower right corner portion shown in the closed section 30. The right and lower sides of the second bulkhead 42 are integrally formed with flange portions 42a and 42b.

ここで、上述の各フランジ部４１ａ，４１ｂ，４２ａ，４２ｂの折曲げ角度は、閉断面部３０の内壁と対応するように設定すればよく、また上述の各フランジ部４１ａ，４１ｂ，４２ａ，４２ｂの折曲げ方向は、図８の（ａ）、図９の（ａ）、図１０の（ａ）に示すよう、図２の実施例と逆方向であってもよい。さらに、図示しないが、フランジ部４１ａの折曲げ方向と、フランジ部４２ａの折曲げ方向とを逆方向に設定すると共に、フランジ部４１ｂの折曲げ方向と、フランジ部４２ｂの折曲げ方向とを逆方向に設定してもよい。   Here, the bending angle of each of the flange portions 41a, 41b, 42a, 42b may be set so as to correspond to the inner wall of the closed cross-section portion 30, and each of the flange portions 41a, 41b, 42a, 42b described above. The bending direction may be the reverse direction of the embodiment of FIG. 2, as shown in FIG. 8 (a), FIG. 9 (a), and FIG. 10 (a). Further, although not shown, the bending direction of the flange portion 41a and the bending direction of the flange portion 42a are set in opposite directions, and the bending direction of the flange portion 41b and the bending direction of the flange portion 42b are reversed. The direction may be set.

補強体としてのバルクヘッド４０を閉断面部３０内に配置した時、第１バルクヘッド４１の下部と第２バルクヘッド４２の上部との間に、これら各バルクヘッド４１，４２の自由端側（直角三角形の斜辺に相当する側）が重ね合わされるオーバラップ部４３を有するものである。
上述のオーバラップ部４３は、バルクヘッド４０の縁上の一点と他点とを結んでなる最長の直線となるように設けられている。すなわち、図３に示すように、オーバラップ部４３はバルクヘッド４０の左下コーナ部と右上コーナ部とを結んで閉断面部３０内において対角線状に延びるように形成されている。
また、第１バルクヘッド４１および第２バルクヘッド４２は閉断面部３０の内壁と結合されるが、この実施例では、直角三角形の底辺に相当する第１バルクヘッド４１のフランジ部４１ａが、フレーム部材１０の側壁１２と結合されて、結合部４４が形成されており、直角三角形の底辺に相当する第２バルクヘッド４２のフランジ部４２ａは、上記側壁１２と略対向する側壁１３に結合されて、結合部４５が形成されている。 When the bulkhead 40 as a reinforcing body is disposed in the closed cross-section portion 30, a free end side of each of the bulkheads 41, 42 between the lower part of the first bulkhead 41 and the upper part of the second bulkhead 42 ( It has an overlap portion 43 on which the side corresponding to the hypotenuse of a right triangle is overlapped.
The above-described overlap portion 43 is provided to be the longest straight line connecting one point on the edge of the bulkhead 40 and another point. That is, as shown in FIG. 3, the overlap portion 43 is formed to extend diagonally in the closed cross-section portion 30 by connecting the lower left corner portion and the upper right corner portion of the bulkhead 40.
In addition, the first bulkhead 41 and the second bulkhead 42 are coupled to the inner wall of the closed cross section 30. In this embodiment, the flange portion 41a of the first bulkhead 41 corresponding to the bottom of the right triangle is a frame. A coupling portion 44 is formed by being coupled to the side wall 12 of the member 10, and a flange portion 42 a of the second bulkhead 42 corresponding to the bottom of a right triangle is coupled to the side wall 13 substantially opposite to the side wall 12. The coupling part 45 is formed.

同様に、直角三角形の対辺に相当する第１バルクヘッド４１のフランジ部４１ｂが、パネル部材２０と結合されて、結合部４６が形成されており、直角三角形の対辺に相当する第２バルクヘッド４２のフランジ部４２ｂは、上記パネル部材２０と略対向するフレーム部材１０の基壁１１に結合されて、結合部４７が形成されている。
つまり、第１バルクヘッド４１と閉断面部３０の内壁との結合部４４，４６と、第２バルクヘッド４２と閉断面部３０の内壁との結合部４５，４７とが、略対向する内壁面に設けられたものである。
しかも、図３に示すように、第１バルクヘッド４１と第２バルクヘッド４２とが重ね合せ部としてのオーバラップ部４３において振動減衰部材５０を介して結合されたものである。 Similarly, the flange portion 41b of the first bulkhead 41 corresponding to the opposite side of the right triangle is coupled to the panel member 20 to form a coupling portion 46, and the second bulkhead 42 corresponding to the opposite side of the right triangle. The flange portion 42b is coupled to the base wall 11 of the frame member 10 substantially facing the panel member 20 to form a coupling portion 47.
That is, the inner wall surfaces at which the coupling portions 44 and 46 between the first bulkhead 41 and the inner wall of the closed section 30 and the coupling portions 45 and 47 between the second bulkhead 42 and the inner wall of the closed section 30 are substantially opposed. Is provided.
In addition, as shown in FIG. 3, the first bulkhead 41 and the second bulkhead 42 are coupled to each other via a vibration damping member 50 in an overlap portion 43 as an overlapping portion.

この実施例においては、図２，図３に示すように上述のオーバラップ部４３の長手方向の中間部で、かつ長手方向に離間する２箇所において第１バルクヘッド４１と第２バルクヘッド４２とをスポット溶接により剛結合しているので、この２箇所のスポット溶接部６０，６０を除くオーバラップ部４３の全領域に上述の振動減衰部材５０を介設している。なお、図示の便宜上、振動減衰部材５０の介設領域を、図３においてハッチングを施して示す。
上述の振動減衰部材５０としては、損失係数（２０℃、３０ＨＺ）が０．２以上の粘弾性部材を用い、この粘弾性部材は上述のオーバラップ部４３に接着により取付けられて、第１バルクヘッド４１と第２バルクヘッド４２とのオーバラップ部４３にサンドイッチ状に介設されたものである。 In this embodiment, as shown in FIG. 2 and FIG. 3, the first bulkhead 41 and the second bulkhead 42 are located at the intermediate portion in the longitudinal direction of the above-described overlap portion 43 and at two locations separated in the longitudinal direction. Are firmly coupled by spot welding, so that the above-described vibration damping member 50 is interposed in the entire region of the overlap portion 43 except for the two spot welds 60 and 60. For convenience of illustration, the intervening region of the vibration damping member 50 is shown hatched in FIG.
As the above-described vibration damping member 50, a viscoelastic member having a loss coefficient (20 ° C., 30H Z ) of 0.2 or more is used, and this viscoelastic member is attached to the above-described overlap portion 43 by bonding, and the first It is sandwiched between overlap portions 43 of the bulkhead 41 and the second bulkhead 42.

図３に示すように、第１バルクヘッド４１と第２バルクヘッド４２とがオーバラップ部４３の２箇所で剛結合された場合、これら剛結合部位、すなわち、スポット溶接部６０，６０の位置は、オーバラップ部４３の端部を避けるように設けられている。   As shown in FIG. 3, when the first bulkhead 41 and the second bulkhead 42 are rigidly coupled at two locations of the overlap portion 43, these rigid coupling portions, that is, the positions of the spot welds 60 and 60 are as follows. The end portion of the overlap portion 43 is provided so as to be avoided.

このように、図１〜図３で示した実施例の車両の車体構造は、２つの車両部材（フレーム部材１０とパネル部材２０）により形成される閉断面部３０における車両の車体構造であって、上記閉断面部３０の内部に結合される補強体としてのバルクヘッド４０を備え、該補強体（バルクヘッド４０）は第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）とからなり、上記第１補強部（第１バルクヘッド４１）と上記第２補強部（第２バルクヘッド４２）とは重ね合せ部（オーバラップ部４３）を有し、上記第１補強部（第１バルクヘッド４１）は上記閉断面部３０の内壁と結合され、上記第２補強部（第２バルクヘッド４２）は上記閉断面部３０の内壁と結合されており、上記第１補強部（第１バルクヘッド４１）と上記第２補強部（第２バルクヘッド４２）とが上記重ね合せ部（オーバラップ部４３）の少なくとも一部（この実施例では略全域）において振動減衰部材５０を介して結合されたものである（図３参照）。   As described above, the vehicle body structure of the vehicle according to the embodiment shown in FIGS. 1 to 3 is a vehicle body structure of the vehicle in the closed cross section 30 formed by two vehicle members (the frame member 10 and the panel member 20). And a bulkhead 40 as a reinforcing body coupled to the inside of the closed cross section 30, and the reinforcing body (bulkhead 40) includes a first reinforcing portion (first bulkhead 41) and a second reinforcing portion (second The first reinforcing portion (first bulkhead 41) and the second reinforcing portion (second bulkhead 42) have an overlapping portion (overlap portion 43), and One reinforcing portion (first bulkhead 41) is coupled to the inner wall of the closed cross section 30 and the second reinforcing portion (second bulkhead 42) is coupled to the inner wall of the closed cross section 30; 1 reinforcing part (first bulkhead 41) and The second reinforcing portion (second bulkhead 42) is coupled via a vibration damping member 50 in at least a part (substantially the entire area in this embodiment) of the overlapping portion (overlap portion 43). (See FIG. 3).

この構成によれば、補強体（バルクヘッド４０）を第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）との２つに分割し、これらの各補強部（各バルクヘッド４１，４２）を閉断面部３０の内壁と結合したので、補強体（バルクヘッド４０）により閉断面部３０の断面崩れによる揺動変形を抑制することができる。
しかも、第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）とが重ね合せ部（オーバラップ部４３）の少なくとも一部において振動減衰部材５０を介して結合されているので、この振動減衰部材５０により効果的に振動減衰を行なうことができる。
要するに、補強体（バルクヘッド４０）により閉断面部３０の剛性を確保しつつ、振動減衰部材５０により振動を効果的に抑制することができ、乗り心地を向上させ、また騒音の低減を図ることができる効果がある。
また、上記第１補強部（第１バルクヘッド４１）と上記閉断面部３０の内壁との結合部４４，４６と、上記第２補強部（第２バルクヘッド４２）と上記閉断面部３０の内壁との結合部４５，４７とが、略対向する内壁面に設けられたものである（図３参照）。 According to this configuration, the reinforcing body (bulk head 40) is divided into two parts, a first reinforcing part (first bulk head 41) and a second reinforcing part (second bulk head 42), and each of these reinforcing parts. Since (each bulkhead 41, 42) is coupled to the inner wall of the closed cross section 30, the reinforcing member (bulk head 40) can suppress the rocking deformation due to the collapse of the cross section of the closed cross section 30.
In addition, the first reinforcing portion (first bulkhead 41) and the second reinforcing portion (second bulkhead 42) are coupled via the vibration damping member 50 at least at a part of the overlapping portion (overlap portion 43). Therefore, the vibration damping member 50 can effectively perform vibration damping.
In short, while the rigidity of the closed section 30 is secured by the reinforcing body (bulk head 40), vibration can be effectively suppressed by the vibration damping member 50, and riding comfort is improved and noise is reduced. There is an effect that can.
Further, the connecting portions 44 and 46 of the first reinforcing portion (first bulkhead 41) and the inner wall of the closed cross section 30; the second reinforcing portion (second bulkhead 42) and the closed cross section 30; The connecting portions 45 and 47 with the inner wall are provided on the substantially opposing inner wall surfaces (see FIG. 3).

この構成によれば、第１補強部（第１バルクヘッド４１）の上記結合部４４，４６と、第２補強部（第２バルクヘッド４２）の上記結合部４５，４７とが略対向する内壁面に設けられ、これらの各結合部４４〜４７がそれぞれ対向する面に剛結合されるので、第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）との重ね合せ部（オーバラップ部４３）は相対的な変位が生じやすく、該重ね合せ部（オーバラップ部４３）に介設した振動減衰部材５０にてより一層高い振動減衰効果が得られる。
因みに、相対的な変位が全くない場合には振動減衰部材で振動減衰を行なうことはできないので、この実施形態では、第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）との重ね合せ部（オーバラップ部）、つまり各部４１，４２の自由端側に相対的な変位が生じやすいように構成したものである。
さらに、上記重ね合せ部（オーバラップ部４３）が、上記補強体（バルクヘッド４０）の縁上の一点と他点とを結んでなる最長の直線（図３の対角線参照）となるように設けられたものである（図３参照）。 According to this configuration, the coupling portions 44 and 46 of the first reinforcement portion (first bulkhead 41) and the coupling portions 45 and 47 of the second reinforcement portion (second bulkhead 42) are substantially opposed to each other. Since these coupling portions 44 to 47 are provided on the wall surface and are rigidly coupled to the opposing surfaces, the first reinforcing portion (first bulkhead 41) and the second reinforcing portion (second bulkhead 42) The overlapping portion (overlap portion 43) is likely to be relatively displaced, and a higher vibration damping effect can be obtained by the vibration damping member 50 interposed in the overlapping portion (overlap portion 43).
Incidentally, if there is no relative displacement at all, vibration damping cannot be performed by the vibration damping member. Therefore, in this embodiment, the first reinforcing portion (first bulkhead 41) and the second reinforcing portion (second bulk). It is configured such that relative displacement is likely to occur on the overlapping portion (overlap portion) with the head 42), that is, on the free end side of each portion 41, 42.
Further, the overlapping portion (overlap portion 43) is provided so as to be the longest straight line (see the diagonal line in FIG. 3) connecting one point on the edge of the reinforcing body (bulk head 40) and the other point. (See FIG. 3).

この構成によれば、重ね合せ部（オーバラップ部４３）に介設する振動減衰部材５０の設定面積を、可能な限り大きくすることができ、これにより振動減衰能力の向上を図ることができる。
加えて、上記重ね合せ部（オーバラップ部４３）の１箇所または２箇所以上（この実施例では２箇所）において、上記第１補強部（第１バルクヘッド４１）と上記第２補強部（第２バルクヘッド４２）とが剛結合されたものである（図３参照）。 According to this configuration, the set area of the vibration damping member 50 interposed in the overlapping portion (overlap portion 43) can be increased as much as possible, thereby improving the vibration damping capability.
In addition, at one or more (two in this embodiment) of the overlapping portion (overlap portion 43), the first reinforcing portion (first bulkhead 41) and the second reinforcing portion (first 2 bulkhead 42) (see FIG. 3).

この構成によれば、重ね合せ部（オーバラップ部４３）において第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）とを剛結合したので、これら第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）との位置ずれが生じにくくなり、補強体（バルクヘッド４０）の閉断面部３０に対する組付け性の向上を図ることができる。
また、上記第１補強部（第１バルクヘッド４１）と上記第２補強部（第２バルクヘッド４２）とが重ね合せ部（オーバラップ部４３）の２箇所以上（この実施例では２箇所）で剛結合されたものにおいて、該剛結合部位（スポット溶接部６０の位置）が上記重ね合せ部（オーバラップ部４３）の端部を避けるように設けられたものである（図３参照）。 According to this configuration, since the first reinforcing portion (first bulkhead 41) and the second reinforcing portion (second bulkhead 42) are rigidly connected in the overlapping portion (overlap portion 43), these first reinforcing portions The position (first bulkhead 41) and the second reinforcing portion (second bulkhead 42) are less likely to be displaced, and the assembling property of the reinforcing body (bulkhead 40) to the closed cross-section portion 30 is improved. Can do.
In addition, the first reinforcing portion (first bulkhead 41) and the second reinforcing portion (second bulkhead 42) are at two or more places (two places in this embodiment) of the overlapping portion (overlap portion 43). In this case, the rigid coupling portion (the position of the spot welded portion 60) is provided so as to avoid the end portion of the overlapping portion (overlap portion 43) (see FIG. 3).

この構成によれば、振動減衰部材５０による振動減衰能力を損なうことなく、補強体（バルクヘッド４０）の閉断面部３０に対する組付け性の向上を図ることができる。
因みに、剛結合部位が重ね合せ部の両端部に設けられた場合には、第１補強部と第２補強部との相対的な変位が抑制されて、振動減衰効果が僅小となるので、相対的な変位が得られるように重ね合せ部（オーバラップ部４３）の端部を避けて剛結合部位を設けるものである。 According to this configuration, it is possible to improve the assembling property of the reinforcing body (bulkhead 40) with respect to the closed cross section 30 without impairing the vibration damping capability of the vibration damping member 50.
Incidentally, when the rigid coupling sites are provided at both ends of the overlapped portion, the relative displacement between the first reinforcing portion and the second reinforcing portion is suppressed, and the vibration damping effect becomes small. In order to obtain a relative displacement, a rigid coupling portion is provided avoiding the end of the overlapping portion (overlap portion 43).

次に、図４〜図６を参照して車両の車体構造を開断面部に適用した実施例について説明する。
図４は車両の車体構造を示す分解斜視図、図５は補強体の斜視図、図６は図４の正面図であって、図４〜図６において、１つの車両部材として断面ハット形状のフレーム部材１０（骨格部材）で開断面部３１（図６参照）を形成している。
上述のフレーム部材１０は、基壁１１と、この基壁１１に連続する一対の側壁１２，１３と、これら側壁１２，１３の端部から外方に延びるフランジ部１４，１５とを一体形成した車両部材である。 Next, an embodiment in which the vehicle body structure of the vehicle is applied to the open cross section will be described with reference to FIGS.
4 is an exploded perspective view showing the vehicle body structure of the vehicle, FIG. 5 is a perspective view of the reinforcing body, and FIG. 6 is a front view of FIG. 4. In FIGS. An open section 31 (see FIG. 6) is formed by the frame member 10 (frame member).
The frame member 10 described above is integrally formed with a base wall 11, a pair of side walls 12 and 13 continuing to the base wall 11, and flange portions 14 and 15 extending outward from the end portions of the side walls 12 and 13. It is a vehicle member.

図６に示すように、上述の開断面部３１の内部に結合される補強体としての略四角形状のバルクヘッド４０を設けるが、この実施例では、該バルクヘッド４０を、図６の左側かつ上側に位置する第１バルクヘッド４１と、図６の右側かつ下側に位置する第２バルクヘッド４２とに２分割している。   As shown in FIG. 6, a substantially square bulkhead 40 is provided as a reinforcing body coupled to the inside of the above-described open section 31. In this embodiment, the bulkhead 40 is connected to the left side of FIG. The first bulkhead 41 located on the upper side and the second bulkhead 42 located on the right side and lower side in FIG. 6 are divided into two.

図５，図６に示すように、第１バルクヘッド４１は略直角三角形状に形成され、その直角部が開断面部３１内の図示左上コーナ部に位置するように配設されるもので、この第１バルクヘッド４１の左辺にはフランジ部４１ａが一体的に折曲げ形成されている。   As shown in FIG. 5 and FIG. 6, the first bulkhead 41 is formed in a substantially right triangle shape, and the right angle portion is disposed so as to be located in the illustrated upper left corner portion in the open section 31. A flange portion 41 a is integrally formed on the left side of the first bulkhead 41 by bending.

図５，図６に示すように、第２バルクヘッド４２も略直角三角形状に形成され、その直角部が開断面部３１内の図示右下コーナ部に位置するように配設されるもので、この第２バルクヘッド４２の右辺および下辺にはフランジ部４２ａ，４２ｂが一体的に折曲げ形成されている。   As shown in FIGS. 5 and 6, the second bulkhead 42 is also formed in a substantially right triangle shape, and is arranged so that the right angle portion is positioned at the lower right corner portion shown in the open section 31. The right and lower sides of the second bulkhead 42 are integrally formed with flange portions 42a and 42b.

ここで、上述の各フランジ部４１ａ，４２ａ，４２ｂの折曲げ角度は、開断面部３１の内壁と対応するように設定すればよく、また上述の各フランジ部４１ａ，４２ａ，４２ｂの折曲げ方向は、図８の（ａ）、図９の（ａ）、図１０の（ａ）に示すよう、図５の実施例と逆方向であってもよい。さらに、図示はしないが、フランジ部４１ａの折曲げ方向に対して、フランジ部４２ａの折曲げ方向を逆方向と成してもよい。   Here, the bending angle of each of the flange portions 41a, 42a, and 42b may be set so as to correspond to the inner wall of the open section 31, and the bending direction of each of the flange portions 41a, 42a, and 42b described above. As shown in FIGS. 8A, 9A, and 10A, the direction may be opposite to that of the embodiment of FIG. Furthermore, although not illustrated, the bending direction of the flange portion 42a may be opposite to the bending direction of the flange portion 41a.

補強体としてのバルクヘッド４０を開断面部３１内に配置した時、第１バルクヘッド４１の下部と第２バルクヘッド４２の上部との間に、これら各バルクヘッド４１，４２の自由端側（直角三角形の斜辺に相当する側）が重ね合わされるオーバラップ部４３を有するものである。
上述のオーバラップ部４３は、バルクヘッド４０の縁上の一点と他点とを結んでなる最長の直線となるように設けられている。すなわち、図６に示すように、オーバラップ部４３はバルクヘッド４０の左下コーナ部と右上コーナ部とを結んで開断面部３１内において対角線状に延びるように形成されている。
また、第１バルクヘッド４１および第２バルクヘッド４２は開断面部３１の内壁と結合されるが、この実施例では、直角三角形の底辺に相当する第１バルクヘッド４１のフランジ部４１ａが、フレーム部材１０の側壁１２と結合されて、結合部４４が形成されており、直角三角形の底辺に相当する第２バルクヘッド４２のフランジ部４２ａは、上記側壁１２と略対向する側壁１３に結合されて、結合部４５が形成されている。
さらに、直角三角形の対辺に相当する第２バルクヘッド４２のフランジ部４２ｂは、フレーム部材１０の基壁１１に結合されて、結合部４７が形成されている。
つまり、第１バルクヘッド４１と開断面部３１の内壁との結合部４４と、第２バルクヘッド４２と開断面部３１の内壁との結合部４５とが、略対向する内壁面に設けられたものである。
しかも、図６に示すように、第１バルクヘッド４１と第２バルクヘッド４２とが重ね合せ部としてのオーバラップ部４３において振動減衰部材５０を介して結合されたものである。 When the bulkhead 40 as a reinforcing body is disposed in the open section 31, between the lower part of the first bulkhead 41 and the upper part of the second bulkhead 42, the free end side of each of these bulkheads 41, 42 ( It has an overlap portion 43 on which the side corresponding to the hypotenuse of a right triangle is overlapped.
The above-described overlap portion 43 is provided to be the longest straight line connecting one point on the edge of the bulkhead 40 and another point. That is, as shown in FIG. 6, the overlap portion 43 is formed so as to extend diagonally in the open section 31 by connecting the lower left corner portion and the upper right corner portion of the bulkhead 40.
In addition, the first bulkhead 41 and the second bulkhead 42 are coupled to the inner wall of the open section 31. In this embodiment, the flange portion 41a of the first bulkhead 41 corresponding to the bottom of the right triangle is a frame. A coupling portion 44 is formed by being coupled to the side wall 12 of the member 10, and a flange portion 42 a of the second bulkhead 42 corresponding to the bottom of a right triangle is coupled to the side wall 13 substantially opposite to the side wall 12. The coupling part 45 is formed.
Further, the flange portion 42 b of the second bulkhead 42 corresponding to the opposite side of the right triangle is coupled to the base wall 11 of the frame member 10 to form a coupling portion 47.
In other words, the connecting portion 44 between the first bulkhead 41 and the inner wall of the open section 31 and the connecting portion 45 between the second bulkhead 42 and the inner wall of the open section 31 are provided on substantially opposing inner wall surfaces. Is.
In addition, as shown in FIG. 6, the first bulkhead 41 and the second bulkhead 42 are coupled to each other via a vibration damping member 50 in an overlap portion 43 as an overlapping portion.

この実施例においては、図５，図６に示すように上述のオーバラップ部４３の長手方向の中間部で、かつ長手方向に離間する２箇所において第１バルクヘッド４１と第２バルクヘッド４２とをスポット溶接により剛結合しているので、この２箇所のスポット溶接部６０，６０を除くオーバラップ部４３の全領域に上述の振動減衰部材５０を介設している。なお、図示の便宜上、振動減衰部材５０の介設領域を、図６においてもハッチングを施して示している。
上述の振動減衰部材５０としては、損失係数（２０℃、３０ＨＺ）が０．２以上の粘弾性部材を用い、この粘弾性部材は上述のオーバラップ部４３に接着により取付けられて、第１バルクヘッド４１と第２バルクヘッド４２とのオーバラップ部４３にサンドイッチ状に介設されたものである。 In this embodiment, as shown in FIGS. 5 and 6, the first bulkhead 41 and the second bulkhead 42 are located at the intermediate portion in the longitudinal direction of the above-described overlap portion 43 and at two locations separated in the longitudinal direction. Are firmly coupled by spot welding, so that the above-described vibration damping member 50 is interposed in the entire region of the overlap portion 43 except for the two spot welds 60 and 60. For convenience of illustration, the intervening region of the vibration damping member 50 is also hatched in FIG.
As the above-described vibration damping member 50, a viscoelastic member having a loss coefficient (20 ° C., 30H Z ) of 0.2 or more is used, and this viscoelastic member is attached to the above-described overlap portion 43 by bonding, and the first It is sandwiched between overlap portions 43 of the bulkhead 41 and the second bulkhead 42.

図６に示すように、第１バルクヘッド４１と第２バルクヘッド４２とがオーバラップ部４３の２箇所で剛結合された場合、これら剛結合部位、すなわち、スポット溶接部６０，６０の位置は、オーバラップ部４３の端部を避けるように設けられている。   As shown in FIG. 6, when the first bulkhead 41 and the second bulkhead 42 are rigidly coupled at two locations of the overlap portion 43, these rigid coupling portions, that is, the positions of the spot welds 60 and 60 are as follows. The end portion of the overlap portion 43 is provided so as to be avoided.

このように、図４〜図６で示した実施例の車両の車体構造は、１つの車両部材（フレーム部材１０参照）により形成される開断面部３１における車両の車体構造であって、上記開断面部３１の内部に結合される補強体（バルクヘッド４０）を備え、該補強体（バルクヘッド４０）は第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）とからなり、上記第１補強部（第１バルクヘッド４１）と上記第２補強部（第２バルクヘッド４２）とは重ね合せ部（オーバラップ部４３）を有し、上記第１補強部（第１バルクヘッド４１）は上記開断面部３１の内壁と結合され、上記第２補強部（第２バルクヘッド４２）は上記開断面部３１の内壁と結合されており、上記第１補強部（第１バルクヘッド４１）と上記第２補強部（第２バルクヘッド４２）とが上記重ね合せ部（オーバラップ部４３）の少なくとも一部（この実施例では略全域）において振動減衰部材５０を介して結合されたものである（図６参照）。   As described above, the vehicle body structure of the vehicle shown in FIGS. 4 to 6 is the vehicle body structure of the vehicle in the open section 31 formed by one vehicle member (see the frame member 10). A reinforcing body (bulk head 40) coupled to the inside of the cross section 31 is provided, and the reinforcing body (bulk head 40) includes a first reinforcing part (first bulk head 41) and a second reinforcing part (second bulk head 42). The first reinforcing part (first bulkhead 41) and the second reinforcing part (second bulkhead 42) have an overlapping part (overlap part 43), and the first reinforcing part The (first bulkhead 41) is coupled to the inner wall of the open section 31 and the second reinforcing section (second bulkhead 42) is coupled to the inner wall of the open section 31 and the first reinforcing section. (First bulkhead 41) and the second reinforcing portion ( 2 bulkhead 42) and is the overlap portion (overlapping portion 43) of the at least a portion (in this embodiment is one that is bound via the vibration damping member 50 in substantially the entire region) (see FIG. 6).

この構成によれば、補強体（バルクヘッド４０）を第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）との２つに分割し、これらの各補強部（各バルクヘッド４１，４２）を開断面部３１の内壁と結合したので、補強体（バルクヘッド４０）により開断面部３１の断面崩れによる揺動変形を抑制することができる。
しかも、第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）とが重ね合せ部（オーバラップ部４３）の少なくとも一部において振動減衰部材５０を介して結合されているので、この振動減衰部材５０により効果的に振動減衰を行なうことができる。
要するに、補強体（バルクヘッド４０）により開断面部３１の剛性を確保しつつ、振動減衰部材５０により振動を効果的に抑制することができ、騒音の低減を図ることができる効果がある。
また、上記第１補強部（第１バルクヘッド４１）と上記開断面部３１の内壁との結合部４４と、上記第２補強部（第２バルクヘッド４２）と上記開断面部３１の内壁との結合部４５とが、略対向する内壁面に設けられたものである（図６参照）。 According to this configuration, the reinforcing body (bulk head 40) is divided into two parts, a first reinforcing part (first bulk head 41) and a second reinforcing part (second bulk head 42), and each of these reinforcing parts. Since (each bulkhead 41, 42) is coupled to the inner wall of the open cross section 31, the reinforcing member (bulk head 40) can suppress swing deformation due to the cross section of the open cross section 31.
In addition, the first reinforcing portion (first bulkhead 41) and the second reinforcing portion (second bulkhead 42) are coupled via the vibration damping member 50 at least at a part of the overlapping portion (overlap portion 43). Therefore, the vibration damping member 50 can effectively perform vibration damping.
In short, while the rigidity of the open section 31 is secured by the reinforcing body (bulk head 40), vibration can be effectively suppressed by the vibration damping member 50, and noise can be reduced.
Further, a connecting portion 44 between the first reinforcing portion (first bulkhead 41) and the inner wall of the open cross-section portion 31, the second reinforcing portion (second bulkhead 42) and the inner wall of the open cross-section portion 31 The connecting portion 45 is provided on the substantially opposite inner wall surfaces (see FIG. 6).

この構成によれば、第１補強部（第１バルクヘッド４１）の上記結合部４４と、第２補強部（第２バルクヘッド４２）の上記結合部４５とが略対向する内壁面に設けられ、これらの各結合部４４，４５がそれぞれ対向する面に剛結合されるので、第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）との重ね合せ部（オーバラップ部４３）は相対的な変位が生じやすく、該重ね合せ部（オーバラップ部４３）に介設した振動減衰部材５０にてより一層高い振動減衰効果が得られる。
因みに、相対的な変位が全くない場合には振動減衰部材で振動減衰を行なうことはできないので、この実施形態では、第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）との重ね合せ部（オーバラップ部４３）、つまり各部４１，４２の自由端側に相対的な変位が生じやすいように構成したものである。
さらに、上記重ね合せ部（オーバラップ部４３）が、上記補強体（バルクヘッド４０）の縁上の一点と他点とを結んでなる最長の直線（図６の対角線参照）となるように設けられたものである（図６参照）。 According to this configuration, the connecting portion 44 of the first reinforcing portion (first bulkhead 41) and the connecting portion 45 of the second reinforcing portion (second bulkhead 42) are provided on the inner wall surfaces that are substantially opposed to each other. Since these coupling portions 44 and 45 are rigidly coupled to the opposing surfaces, the overlapping portion (the first reinforcing portion (first bulkhead 41) and the second reinforcing portion (second bulkhead 42) are overlapped ( The overlap portion 43) is likely to be relatively displaced, and a higher vibration damping effect can be obtained by the vibration damping member 50 interposed in the overlapping portion (overlap portion 43).
Incidentally, if there is no relative displacement at all, vibration damping cannot be performed by the vibration damping member. Therefore, in this embodiment, the first reinforcing portion (first bulkhead 41) and the second reinforcing portion (second bulk). It is configured such that relative displacement is likely to occur on the overlapping portion (overlap portion 43) with the head 42), that is, on the free end side of each portion 41, 42.
Further, the overlapping portion (overlap portion 43) is provided so as to be the longest straight line (see the diagonal line in FIG. 6) connecting one point on the edge of the reinforcing body (bulk head 40) and the other point. (See FIG. 6).

この構成によれば、重ね合せ部（オーバラップ部４３）に介設する振動減衰部材５０の設定面積を、可能な限り大きくすることができ、これにより振動減衰能力の向上を図ることができる。
加えて、上記重ね合せ部（オーバラップ部４３）の１箇所または２箇所以上（この実施例では２箇所）において、上記第１補強部（第１バルクヘッド４１）と上記第２補強部（第２バルクヘッド４２）とが剛結合されたものである（図６参照）。 According to this configuration, the set area of the vibration damping member 50 interposed in the overlapping portion (overlap portion 43) can be increased as much as possible, thereby improving the vibration damping capability.
In addition, at one or more (two in this embodiment) of the overlapping portion (overlap portion 43), the first reinforcing portion (first bulkhead 41) and the second reinforcing portion (first 2 bulkhead 42) is rigidly coupled (see FIG. 6).

この構成によれば、重ね合せ部（オーバラップ部４３）において第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）とを剛結合したので、これら第１補強部（第１バルクヘッド４１）と第２補強部（第２バルクヘッド４２）との位置ずれが生じにくくなり、補強体（バルクヘッド４０）の開断面部３１に対する組付け性の向上を図ることができる。
また、上記第１補強部（第１バルクヘッド４１）と上記第２補強部（第２バルクヘッド４２）とが重ね合せ部（オーバラップ部４３）の２箇所以上（この実施例では２箇所）で剛結合されたものにおいて、該剛結合部位（スポット溶接部６０の位置）が上記重ね合せ部（オーバラップ部４３）の端部を避けるように設けられたものである（図６参照）。 According to this configuration, since the first reinforcing portion (first bulkhead 41) and the second reinforcing portion (second bulkhead 42) are rigidly connected in the overlapping portion (overlap portion 43), these first reinforcing portions The position (first bulkhead 41) and the second reinforcing portion (second bulkhead 42) are less likely to be displaced, and the assembling property of the reinforcing body (bulkhead 40) with respect to the open section 31 is improved. Can do.
In addition, the first reinforcing portion (first bulkhead 41) and the second reinforcing portion (second bulkhead 42) are at two or more places (two places in this embodiment) of the overlapping portion (overlap portion 43). The rigid coupling portion (position of the spot welded portion 60) is provided so as to avoid the end portion of the overlapping portion (overlap portion 43) (see FIG. 6).

この構成によれば、振動減衰部材５０による振動減衰能力を損なうことなく、補強体（バルクヘッド４０）の開断面部３１に対する組付け性の向上を図ることができる。
因みに、剛結合部位が重ね合せ部の両端部に設けられた場合には、第１補強部と第２補強部との相対的な変位が抑制されて、振動減衰効果が僅小となるので、相対的な変位が得られるように重ね合せ部（オーバラップ部４３）の端部を避けて剛結合部位（スポット溶接部６０の位置参照）を設けるものである。 According to this configuration, it is possible to improve the assembling property of the reinforcing body (bulk head 40) with respect to the open section 31 without impairing the vibration damping capability of the vibration damping member 50.
Incidentally, when the rigid coupling sites are provided at both ends of the overlapped portion, the relative displacement between the first reinforcing portion and the second reinforcing portion is suppressed, and the vibration damping effect becomes small. In order to obtain a relative displacement, an end portion of the overlapping portion (overlap portion 43) is avoided and a rigid coupling portion (refer to the position of the spot weld portion 60) is provided.

図８，図９，図１０は、スポット溶接箇所を１箇所、２箇所、３箇所にそれぞれ設定し、図７に示すシミュレーション解析方法にてイナータンス（単位加振力当りの加速度振幅の大きさ）を測定した結果を示すものである。 8, 9 and 10, the spot welding portion to one point, two points, respectively set to three positions, the magnitude of the acceleration amplitude of the inertance (per unit excitation force at simulation analysis method shown in FIG. 7 This shows the result of measuring (S).

図７は図１〜図３で示した車体構造とほぼ同一構造（但し、フレーム部材１０とパネル部材２０の上下位置関係を逆にすると共に、フランジ部４１ａ，４１ｂ，４２ａ，４２ｂの折曲げ方向も逆方向としている）の閉断面構造体を設け、この閉断面構造体の長手方向の一端における閉断面部３０の所定の角部を加振点Ｘとし、閉断面構造体の長手方向の他端における閉断面部３０の上記角部と対角上に位置する角部を応答点Ｙとし、加振点Ｘを加振して、応答点Ｙにおけるイナータンスを測定するものである。   7 is substantially the same as the vehicle body structure shown in FIGS. 1 to 3 (however, the vertical positional relationship between the frame member 10 and the panel member 20 is reversed, and the bending direction of the flange portions 41a, 41b, 42a, 42b is also shown. Are provided in the opposite direction), and a predetermined corner of the closed section 30 at one end in the longitudinal direction of the closed section structure is defined as an excitation point X. The corner located diagonally above the corner of the closed section 30 at the end is set as the response point Y, the excitation point X is vibrated, and the inertance at the response point Y is measured.

この測定に際しては、本実施例品と比較例品との特性を比較する目的で、オーバラップ部４３において第１バルクヘッド４１と第２バルクヘッド４２とを単にスポット溶接し、振動減衰部材５０を全く用いない比較例品と、オーバラップ部４３において第１バルクヘッド４１と第２バルクヘッド４２とをスポット溶接すると共に、これら両バルクヘッド４１，４２間に振動減衰部材５０を介設した本実施例品とに対して、同一条件にて解析を行なった。
また、本実施例品における振動減衰部材５０としては、損失係数が０．４、貯蔵弾性率が２００ＭＰａ（２０℃、３０ＨＺ）の粘弾性部材を用いた。 In this measurement, the first bulkhead 41 and the second bulkhead 42 are simply spot-welded at the overlap portion 43 for the purpose of comparing the characteristics of the present embodiment product and the comparative product, and the vibration damping member 50 is attached. In this embodiment, the comparative example product not used at all and the first bulkhead 41 and the second bulkhead 42 are spot-welded in the overlap portion 43, and a vibration damping member 50 is interposed between the bulkheads 41 and 42. The analysis was performed under the same conditions for the example products.
Moreover, as the vibration damping member 50 in the product of this example, a viscoelastic member having a loss coefficient of 0.4 and a storage elastic modulus of 200 MPa (20 ° C., 30 H Z ) was used.

図８の（ａ）は溶接箇所を１箇所と成したバルクヘッド４０を示し、同図の（ｂ）は振動減衰部材５０をオーバラップ部４３のスポット溶接部６０の両側に介設した本実施例品と、振動減衰部材を有さない比較例品との特性を比較して示すものであり、図８の（ｂ）において横軸は周波数であり、縦軸はイナータンスである。   FIG. 8A shows the bulkhead 40 having a single welded portion, and FIG. 8B shows the embodiment in which the vibration damping member 50 is interposed on both sides of the spot welded portion 60 of the overlap portion 43. The characteristic of an example product and the comparative example product which does not have a vibration damping member is shown in comparison. In FIG. 8B, the horizontal axis represents frequency and the vertical axis represents inertance.

図８の（ｂ）に実線で示す本実施例品は、同図に仮想線で示す比較例品に対してイナータンスの低減量が約３．５ｄＢであることが認められ、振動レベルが充分に低下していることが明らかとなった。   In this example product shown by the solid line in FIG. 8B, the reduction in inertance is recognized to be about 3.5 dB compared to the comparative product shown by the phantom line in FIG. It became clear that it was decreasing.

図９の（ａ）は溶接箇所を２箇所と成したバルクヘッド４０を示し、同図の（ｂ）は２箇所のスポット溶接部６０を除く、オーバラップ部４３の略全域に振動減衰部材５０を介設した本実施例品と、振動減衰部材を有さない比較例品との特性を比較して示すものであり、図９の（ｂ）において横軸は周波数であり、縦軸はイナータンスである。   9A shows the bulkhead 40 having two welds, and FIG. 9B shows the vibration damping member 50 over substantially the entire overlap part 43 excluding the two spot welds 60. FIG. 9B shows a comparison between the characteristics of the product of the present example with the intervening member and the comparative product without the vibration damping member. In FIG. 9B, the horizontal axis represents the frequency, and the vertical axis represents the inertance. It is.

図９の（ｂ）に実線で示す本実施例品は、同図に仮想線で示す比較例品に対してイナータンスの低減量が約２．６ｄＢであることが認められ、振動レベルが低下していることが明らかとなった。   In this example product indicated by the solid line in FIG. 9B, the reduction in inertance is recognized to be about 2.6 dB compared to the comparative example product indicated by the phantom line in FIG. It became clear that.

図１０の（ａ）は溶接箇所を３箇所と成したバルクヘッド４０を示し、同図の（ｂ）は３箇所のスポット溶接部６０，６０間において、オーバラップ部４３に振動減衰部材５０，５０を介設した本実施例品と、振動減衰部材を有さない比較例品との特性を比較して示すものであり、図１０の（ｂ）において横軸は周波数であり、縦軸はイナータンスである。   10A shows the bulkhead 40 having three welds, and FIG. 10B shows the vibration damping member 50, which is placed on the overlap part 43 between the three spot welds 60, 60. 50 shows a comparison between the characteristics of the product of the present example having a 50 and a comparative product having no vibration damping member. In FIG. 10B, the horizontal axis represents frequency, and the vertical axis represents Inertance.

図１０の（ｂ）に実線で示す本実施例品は、同図に仮想線で示す比較例品に対してイナータンスの低減量が約０．２５ｄＢであることが認められ、僅かではあるが振動レベルが低下していることが明らかとなった。   In this example product indicated by a solid line in FIG. 10B, the reduction in inertance is recognized to be about 0.25 dB compared to the comparative example product indicated by a virtual line in FIG. It became clear that the level was falling.

図１１は溶接箇所を２箇所とした場合（図９の（ａ）参照）のスポット溶接部６０，６０間のピッチＰを可変設定し、ピッチＰの変更に対する振動低減量を実測した結果を示すものであり、この場合、オーバラップ部４３に介設した振動減衰部材５０，５０間の長手方向一端と長手方向他端との間の距離Ｌ（図９の（ａ）参照）を１００ｍｍに設定した。   FIG. 11 shows the result of actually measuring the amount of vibration reduction with respect to the change of the pitch P by variably setting the pitch P between the spot welds 60 and 60 when the number of welding locations is two (see FIG. 9A). In this case, the distance L (see FIG. 9A) between one end in the longitudinal direction and the other end in the longitudinal direction between the vibration damping members 50 and 50 interposed in the overlap portion 43 is set to 100 mm. did.

図１１の特性から明らかなように、スポット溶接部６０，６０間のピッチＰが小さい方が、振動低減量が大きくなり、スポット溶接部６０，６０間のピッチＰが大きい方が、振動低減量が小さくなることが認められた。
図１１の特性図を表にまとめると、次の［表１］のようになる。 As is clear from the characteristics of FIG. 11, the vibration reduction amount increases when the pitch P between the spot welds 60, 60 is small, and the vibration reduction amount increases when the pitch P between the spot welds 60, 60 is large. Was found to be smaller.
The characteristics shown in FIG. 11 are summarized in a table as shown in [Table 1] below.

Figure 0005817385
つまり、２点スポット溶接部６０，６０間のピッチＰが小さい場合には、第１バルクヘッド４１と第２バルクヘッド４２との振動（相対変位）が許容され、この振動を振動減衰部材５０で減衰するので、大きい振動低減量が得られ、２点スポット溶接部６０，６０間のピッチＰが大きくなる程、第１バルクヘッド４１と第２バルクヘッド４２との振動（相対変位）が抑制されて小さくなり、この振動を振動減衰部材５０で減衰した場合の振動低減量も小さくなることが明らかとなった。このため、オーバラップ部４３の２箇所以上で剛結合されたバルクヘッド４０においては、剛結合部位がオーバラップ部４３の端部を避けるように設けることが望ましい。
Figure 0005817385
 That is, when the pitch P between the two-point spot welds 60, 60 is small, vibration (relative displacement) between the first bulkhead 41 and the second bulkhead 42 is allowed, and this vibration is absorbed by the vibration damping member 50. Since it attenuates, a large vibration reduction amount is obtained, and the vibration (relative displacement) between the first bulkhead 41 and the second bulkhead 42 is suppressed as the pitch P between the two-point spot welds 60, 60 increases. It has become clear that the amount of vibration reduction when the vibration is attenuated by the vibration damping member 50 is also small. For this reason, in the bulkhead 40 that is rigidly coupled at two or more locations of the overlap portion 43, it is desirable that the rigid coupling portion is provided so as to avoid the end portion of the overlap portion 43.

図１２の（ａ）、（ｂ）、（ｃ）は車両の車体構造の他の実施例を示す正面図である。なお、図１２において、図３と同一の部分には同一符号を付している。
図１２の（ａ）に示す実施例は、閉断面部３０の内部に結合されるバルクヘッド７０を設け、このバルクヘッド７０を図示左側の第１バルクヘッド７１と、図示右側の第２バルクヘッド７２とに２分割し、これら各バルクヘッド７１，７２に一体形成したそれぞれのフランジ部７１ａ，７１ｂ，７１ｃ，７２ａ，７２ｂ，７２ｃを閉断面部３０の対応する内壁にそれぞれ結合して結合部７３を形成すると共に、第１バルクヘッド７１と第２バルクヘッド７２とを重ね合せて図示上下方向（縦方向）に延びるオーバラップ部４３を形成し、さらに、該オーバラップ部４３の上下方向中間をスポット溶接部６０で剛結合し、このスポット溶接部６０の上下におけるオーバラップ部４３の略全域に振動減衰部材５０，５０を介設したものである。
図１２の（ａ）においては、図示の便宜上、振動減衰部材５０の介設領域を、ハッチングを施して示している。
図１２の（ａ）で示した実施例においても、バルクヘッド７０により閉断面部３０の剛性を確保しつつ、オーバラップ部４３に介設した振動減衰部材５０により振動を効果的に抑制することができ、乗り心地を向上させ、また騒音の低減を図ることができる。 12A, 12B, and 12C are front views showing another embodiment of a vehicle body structure. In FIG. 12, the same parts as those in FIG.
The embodiment shown in FIG. 12A is provided with a bulkhead 70 to be coupled to the inside of the closed section 30, and this bulkhead 70 includes a first bulkhead 71 on the left side in the drawing and a second bulkhead on the right side in the drawing. 72, and the flanges 71a, 71b, 71c, 72a, 72b, 72c formed integrally with each of the bulkheads 71, 72 are respectively coupled to the corresponding inner walls of the closed cross-section 30 to be coupled 73 And the first bulkhead 71 and the second bulkhead 72 are overlapped to form an overlap portion 43 extending in the vertical direction (longitudinal direction) in the figure, and an intermediate portion in the vertical direction of the overlap portion 43 is formed. The spot welded portion 60 is rigidly connected, and vibration damping members 50 and 50 are interposed substantially over the entire overlap portion 43 above and below the spot welded portion 60.
In FIG. 12A, for convenience of illustration, the intervening region of the vibration damping member 50 is shown hatched.
Also in the embodiment shown in FIG. 12A, vibration is effectively suppressed by the vibration damping member 50 interposed in the overlap portion 43 while ensuring the rigidity of the closed section 30 by the bulkhead 70. It is possible to improve ride comfort and reduce noise.

図１２の（ｂ）に示す実施例は、閉断面部３０の内部に結合されるバルクヘッド８０を設け、このバルクヘッド８０を図示上側の第１バルクヘッド８１と、図示下側の第２バルクヘッド８２とに２分割し、これら各バルクヘッド８１，８２に一体形成したそれぞれのフランジ部８１ａ，８１ｂ，８１ｃ，８２ａ，８２ｂ，８２ｃを閉断面部３０の対応する内壁にそれぞれ結合して結合部８３を形成すると共に、第１バルクヘッド８１と第２バルクヘッド８２とを重ね合せて図示左右方向（横方向）に延びるオーバラップ部４３を形成し、さらに、該オーバラップ部４３の中間において互いに離間した２箇所をスポット溶接部６０，６０で剛結合し、オーバラップ部４３においてスポット溶接部６０，６０を除く略全域に振動減衰部材５０…を介設したものである。
図１２の（ｂ）においても、図示の便宜上、振動減衰部材５０の介設領域を、ハッチングを施して示している。
図１２の（ｂ）で示した実施例においても、バルクヘッド８０により閉断面部３０の剛性を確保しつつ、オーバラップ部４３に介設した振動減衰部材５０により振動を効果的に抑制することができ、乗り心地を向上させ、また騒音の低減を図ることができる。 The embodiment shown in FIG. 12B is provided with a bulkhead 80 coupled to the inside of the closed cross section 30, and the bulkhead 80 is divided into a first bulkhead 81 on the upper side and a second bulkhead on the lower side in the figure. The flanges 81a, 81b, 81c, 82a, 82b, and 82c that are divided into the head 82 and are integrally formed with the bulk heads 81 and 82 are respectively coupled to the corresponding inner walls of the closed cross-sectional portion 30 to be coupled portions. 83, and the first bulkhead 81 and the second bulkhead 82 are overlapped to form an overlap portion 43 extending in the left-right direction (lateral direction) in the figure, and in the middle of the overlap portion 43, each other The two separated locations are rigidly connected with the spot welds 60, 60, and the vibration damping member 50. It is obtained by set.
Also in FIG. 12B, for convenience of illustration, the intervening region of the vibration damping member 50 is shown hatched.
Also in the embodiment shown in FIG. 12B, vibration is effectively suppressed by the vibration damping member 50 interposed in the overlap portion 43 while the rigidity of the closed cross-section portion 30 is secured by the bulkhead 80. It is possible to improve ride comfort and reduce noise.

図１２の（ｃ）に示す実施例は、閉断面部３０の内部に結合されるバルクヘッド９０を設け、このバルクヘッド９０を図示上側の第１バルクヘッド９１と図示下側の第２バルクヘッド９２とに２分割し、これら各バルクヘッド９１，９２に一体形成したそれぞれのフランジ部９１ａ，９１ｂ，９１ｃ，９２ａ，９２ｂ，９２ｃを閉断面部３０の対応する内壁にそれぞれ結合して結合部９３を形成すると共に、第１バルクヘッド９１下部の円弧凹部と、第２バルクヘッド９２上部の円弧凸部とを重ね合せて略左右方向に円弧状に延びるオーバラップ部４３を形成し、さらに、該オーバラップ部４３の中間において互いに離間した２箇所をスポット溶接部６０，６０で剛結合し、オーバラップ部４３においてスポット溶接部６０，６０を除く略全域に振動減衰部材５０…を介設したものである。
図１２の（ｃ）においても、図示の便宜上、振動減衰部材５０の介設領域を、ハッチングを施して示している。
図１２の（ｃ）で示した実施例においても、バルクヘッド９０により閉断面部３０の剛性を確保しつつ、オーバラップ部４３に介設した振動減衰部材５０により振動を効果的に抑制することができ、乗り心地を向上させ、また騒音の低減を図ることができる。 The embodiment shown in FIG. 12C is provided with a bulkhead 90 coupled to the inside of the closed cross section 30, and the bulkhead 90 is divided into a first bulkhead 91 on the upper side in the drawing and a second bulkhead on the lower side in the drawing. The flange portions 91 a, 91 b, 91 c, 92 a, 92 b, and 92 c that are integrally formed with the bulkheads 91 and 92 are respectively coupled to the corresponding inner walls of the closed cross-section portion 30. And an overlap portion 43 extending in a substantially arc shape in the left-right direction is formed by superimposing the arc concave portion at the bottom of the first bulkhead 91 and the arc convex portion at the top of the second bulkhead 92, Two locations that are spaced apart from each other in the middle of the overlap portion 43 are rigidly connected by spot welds 60 and 60, and substantially all of the overlap portion 43 except for the spot weld portions 60 and 60 is used. In which a vibration damping member 50 ... is interposed.
Also in FIG. 12C, the intervening region of the vibration damping member 50 is shown hatched for convenience of illustration.
Also in the embodiment shown in FIG. 12C, vibration is effectively suppressed by the vibration damping member 50 interposed in the overlap portion 43 while ensuring the rigidity of the closed section 30 by the bulkhead 90. It is possible to improve ride comfort and reduce noise.

図１３はバルクヘッド（補強体）の参考例を示し、図１３の（ａ）はバルクヘッドの斜視図、図１３の（ｂ）は図１３の（ａ）のＢ‐Ｂ線矢視断面図である。
図１３の（ａ）、（ｂ）に示すように、補強体としてのバルクヘッド１００は、両端にフランジ部１０１ａ，１０１ｂを有する第１バルクヘッド１０１と、両端にフランジ部１０２ａ，１０２ｂを有する第２バルクヘッド１０２とから成り、対称構造に形成されたこれら両バルクヘッド１０１，１０２間の略全領域に振動減衰部材５０を介設したものである。
また、上述の各フランジ部１０１ａ，１０１ｂ，１０２ａ，１０２ｂは、１または２以上の車両部材により形成される閉断面部または開断面部の内壁とスポット溶接手段等により結合されるものである。
図１３に示すこの参考例では、フランジ部１０１ａ，１０１ｂ，１０２ａ，１０２ｂ以外の各バルクヘッド１０１，１０２の全領域を面状のオーバラップ部と成すことができるので、振動減衰部材５０の設定面積を最大限に大きくすることができ、この結果、振動減衰能力を大幅に向上させることができる。 FIG. 13 shows a reference example of a bulkhead (reinforcing body), FIG. 13A is a perspective view of the bulkhead, FIG. 13B is a cross-sectional view taken along line BB in FIG. It is.
As shown in FIGS. 13A and 13B, a bulkhead 100 as a reinforcing body includes a first bulkhead 101 having flange portions 101a and 101b at both ends, and a first bulkhead 101 having flange portions 102a and 102b at both ends. The vibration damping member 50 is interposed in substantially the entire region between the two bulkheads 101 and 102 formed of a symmetric structure.
Each of the flange portions 101a, 101b, 102a, and 102b described above is connected to a closed cross-section portion or an inner wall of an open cross-section portion formed by one or more vehicle members and spot welding means or the like.
In this reference example shown in FIG. 13, the entire area of each of the bulkheads 101, 102 other than the flange portions 101a, 101b, 102a, 102b can be formed as a planar overlap portion. Can be maximized, and as a result, the vibration damping ability can be greatly improved.

この発明の構成と、上述の実施例との対応において、
この発明の車両部材は、実施例のフレーム部材１０、パネル部材２０に対応し、
以下同様に、
補強体は、バルクヘッド４０，７０，８０，９０に対応し、
第１補強部は、第１バルクヘッド４１，７１，８１，９１に対応し、
第２補強部は、第２バルクヘッド４２，７２，８２，９２に対応し、
重ね合せ部は、オーバラップ部４３に対応するも、
この発明は、上述の実施例の構成のみに限定されるものではない。
例えば、上記オーバラップ部４３は実施例で示した直線状、円弧状、面状のオーバラップ部以外に凹凸状、波状、鋸歯形状のオーバラップ部であってもよい。
また、本発明の車両の車体構造は、フロントサイドフレーム、リヤサイドフレーム、フロアクロスメンバ、トンネルメンバ、サイドシル、フロントピラー、センタピラー、リヤピラー、クオータピラー、ヒンジピラー、ルーフサイドレール、フロアフレームなどの車両の各部位に適用することができる。 In the correspondence between the configuration of the present invention and the above-described embodiment,
The vehicle member of the present invention corresponds to the frame member 10 and the panel member 20 of the embodiment,
Similarly,
Reinforcement corresponds to bulkhead 40,70,80,9 0,
The first reinforcing part corresponds to the first bulkhead 41,71,81,9 1,
Second reinforcing section corresponds to the second bulkhead 42,72,82,9 2,
The overlapping portion corresponds to the overlap portion 43,
The present invention is not limited to the configuration of the above-described embodiment.
For example, the overlap portion 43 may be an uneven portion, a wavy shape, or a sawtooth shape overlap portion in addition to the linear, arcuate, and planar overlap portions shown in the embodiments.
The vehicle body structure of the vehicle according to the present invention includes a front side frame, a rear side frame, a floor cross member, a tunnel member, a side sill, a front pillar, a center pillar, a rear pillar, a quarter pillar, a hinge pillar, a roof side rail, and a floor frame. It can be applied to each site.

以上説明したように、本発明は、１または２以上の車両部材により形成される閉断面部または開断面部における車両の車体構造について有用である。   As described above, the present invention is useful for a vehicle body structure of a vehicle in a closed section or an open section formed by one or more vehicle members.

１０…フレーム部材（車両部材）
２０…パネル部材（車両部材）
３０…閉断面部
３１…開断面部
４０，７０，８０，９０…バルクヘッド（補強体）
４１，７１，８１，９１…第１バルクヘッド（第１補強部）
４２，７２，８２，９２…第２バルクヘッド（第２補強部）
４３…オーバラップ部（重ね合せ部）
４４〜４７，７３，８３，９３…結合部
５０…振動減衰部材 10: Frame member (vehicle member)
20 ... Panel member (vehicle member)
30 ... Closed section 31 ... Open section 40, 70, 80, 90 ... Bulkhead (reinforcing body)
41, 71, 81, 91 1 ... 1st bulkhead (1st reinforcement part)
42, 72, 82, 92 2 ... 2nd bulkhead (2nd reinforcement part)
43 ... Overlap part (overlapping part)
44-47, 73, 83, 93 ... coupling | bond part 50 ... vibration damping member

Claims (4)

１または２以上の車両部材により形成される閉断面部または開断面部における車両の車体構造であって、
上記閉断面部または上記開断面部の内部に結合される補強体を備え、
該補強体は第１補強部と第２補強部とからなり、
上記第１補強部と上記第２補強部とは重ね合せ部を有し、
上記第１補強部は上記閉断面部または上記開断面部の内壁と結合され、
上記第２補強部は上記閉断面部または上記開断面部の内壁と結合されており、
上記第１補強部と上記第２補強部とが上記重ね合せ部の少なくとも一部において振動減衰部材を介して結合され、
上記重ね合せ部の１箇所または２箇所以上において、上記第１補強部と上記第２補強部とが剛結合された
車両の車体構造。 A vehicle body structure of a vehicle in a closed section or an open section formed by one or more vehicle members,
A reinforcing body coupled to the inside of the closed cross section or the open cross section;
The reinforcing body includes a first reinforcing portion and a second reinforcing portion,
The first reinforcing part and the second reinforcing part have an overlapping part,
The first reinforcing portion is coupled to the inner wall of the closed cross section or the open cross section,
The second reinforcing portion is coupled to the inner wall of the closed cross-section portion or the open cross-section portion,
The first reinforcing portion and the second reinforcing portion are coupled via a vibration damping member in at least a part of the overlapping portion ,
The vehicle body structure of a vehicle, wherein the first reinforcing portion and the second reinforcing portion are rigidly connected to each other at one or two or more locations of the overlapping portion . 上記第１補強部と上記閉断面部または上記開断面部の内壁との結合部と、
上記第２補強部と上記閉断面部または上記開断面部の内壁との結合部とが、
略対向する内壁面に設けられた
請求項１記載の車両の車体構造。 A coupling portion between the first reinforcing portion and the inner wall of the closed cross-section portion or the open cross-section portion;
A coupling portion between the second reinforcing portion and the closed cross-section portion or the inner wall of the open cross-section portion,
The vehicle body structure according to claim 1, wherein the vehicle body structure is provided on substantially opposite inner wall surfaces. 上記重ね合せ部が、上記補強体の縁上の一点と他点とを結んでなる最長の直線となるように設けられた
請求項１または２記載の車両の車体構造。 The vehicle body structure of a vehicle according to claim 1, wherein the overlapping portion is provided so as to be a longest straight line connecting one point on the edge of the reinforcing body and another point . 上記第１補強部と上記第２補強部とが重ね合せ部の２箇所以上で剛結合されたものにおいて、
該剛結合部位が上記重ね合せ部の長手方向の端部を避けるように設けられた
請求項１〜３の何れか１項に記載の車両の車体構造。 In those upper Symbol the first reinforcing portion and the second reinforcing portion is rigidly connected at two or more mating portions overlapping,
The rigid coupling portion is provided so as to avoid the longitudinal end of the overlapping portion.
The vehicle body structure according to any one of claims 1 to 3 .
JP2011208376A 2011-09-26 2011-09-26 Vehicle body structure Active JP5817385B2 (en)

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