JPH09277960A - Double cushioning member, and chassis frame and body construction using it - Google Patents
Double cushioning member, and chassis frame and body construction using itInfo
- Publication number
- JPH09277960A JPH09277960A JP9438296A JP9438296A JPH09277960A JP H09277960 A JPH09277960 A JP H09277960A JP 9438296 A JP9438296 A JP 9438296A JP 9438296 A JP9438296 A JP 9438296A JP H09277960 A JPH09277960 A JP H09277960A
- Authority
- JP
- Japan
- Prior art keywords
- strength member
- double
- deformation
- double cushioning
- load
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Body Structure For Vehicles (AREA)
- Vibration Dampers (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は二重緩衝部材及び
それを用いた車体構造に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double cushioning member and a vehicle body structure using the same.
【０００２】[0002]
【従来の技術】従来より車体を構成するフロントサイド
メンバやリヤサイドメンバ等の強度部材には、加わった
荷重のエネルギーを有効に吸収するための工夫がなされ
ている。例えば、強度部材に各種のビードを形成し、荷
重を受けた際における強度部材の蛇腹変形を促進させる
ことで、該強度部材のエネルギー吸収特性を高めている
（類似技術として、特開平４−１２６６７７号公報参
照）。2. Description of the Related Art Conventionally, strength members such as front side members and rear side members constituting a vehicle body have been devised so as to effectively absorb energy of applied load. For example, by forming various beads on the strength member and promoting bellows deformation of the strength member when a load is applied, the energy absorption characteristic of the strength member is enhanced (as a similar technique, JP-A-4-126677). (See the official gazette).
【０００３】[0003]
【発明が解決しようとする課題】しかしながら、このよ
うなビードに頼った構造の強度部材では、ビード間の
「腹」に相当する部分がビード部分と比較してエネルギ
ーの吸収効果が低く、また荷重を受けた側から部分的に
蛇腹変形するためＦ−Ｓ特性（変形ストロークＳに対す
る反力Ｆの特性）にかなりの変動（波）が見られ、更に
斜めから加わる偏荷重を受けた場合に折れやすい等の課
題がある。従って、それらの点を是正して、理想的なエ
ネルギー吸収特定を得ようとするには、結局、更なる補
強材の追加が必要となり、強度部材周辺の車体構造が複
雑にならざるを得ない。However, in such a strength member having a structure that relies on beads, the portion corresponding to the "belly" between the beads has a lower energy absorption effect than the bead portion, and the load is reduced. Since the bellows is partially deformed from the receiving side, a considerable fluctuation (wave) is observed in the F-S characteristic (the characteristic of the reaction force F with respect to the deformation stroke S), and the F-S characteristic is bent when an unbalanced load is applied. There are issues such as being easy. Therefore, in order to correct those points and obtain the ideal energy absorption identification, it is necessary to add a further reinforcing material in the end, and the vehicle body structure around the strength member must be complicated. .
【０００４】この発明はこのような従来の技術に着目し
てなされたものであり、比較的簡単な構造で理想的なエ
ネルギー吸収特性が得られる二重緩衝部材及びそれを用
いた車体構造を提供するものである。The present invention has been made by paying attention to such a conventional technique, and provides a double cushioning member which can obtain ideal energy absorption characteristics with a relatively simple structure and a vehicle body structure using the double cushioning member. To do.
【０００５】[0005]
【課題を解決するための手段】請求項１記載の発明は、
一端側から荷重を受け得る閉断面形状の外側強度部材内
に、閉断面形状の内側強度部材を設け、且つ前記外側強
度部材の他端に内側強度部材の他端を受容して該他端の
押し出し変形の態様を特定する案内部材を設けたもので
ある。According to the first aspect of the present invention,
An inner strength member having a closed cross section is provided in an outer strength member having a closed cross section capable of receiving a load from one end side, and the other end of the inner strength member is received at the other end of the outer strength member and The guide member is provided to specify the mode of the push-out deformation.
【０００６】請求項１記載の発明によれば、外側強度部
材の内部に内側強度部材を設け且つその内側強度部材の
他端を案内部材により押し出し変形させることができる
ため、エネルギー吸収効率が高まると共に、理想的なＦ
−Ｓ特性が得られ、更に偏荷重を受けても折れにくくな
る。According to the first aspect of the invention, since the inner strength member can be provided inside the outer strength member and the other end of the inner strength member can be pushed out and deformed by the guide member, the energy absorption efficiency is improved and , Ideal F
-S characteristics are obtained, and even if an unbalanced load is applied, it is less likely to break.
【０００７】請求項２記載の発明は、押し出し変形の態
様を特定する案内部材に代えて、押し込み変形の態様を
特定する案内部材を設けたものである。According to a second aspect of the present invention, instead of the guide member for specifying the mode of push-out deformation, a guide member for specifying the mode of push-in deformation is provided.
【０００８】請求項２記載の発明によれば、内側強度部
材の他端を押し込み変形させても前記同様の効果が得ら
れる。According to the second aspect of the invention, the same effect as described above can be obtained even when the other end of the inner strength member is pushed and deformed.
【０００９】請求項３記載の発明は、内側強度部材の他
端に、変形を促進させるための初期たわみ部が形成され
ている。According to a third aspect of the present invention, an initial bending portion for promoting deformation is formed at the other end of the inner strength member.
【００１０】請求項３記載の発明によれば、内側強度部
材の他端に初期たわみ部が形成されているため、押し出
し変形又は押し込み変形が促進されて、より理想的なＦ
−Ｓ特性が得られる。According to the third aspect of the invention, since the initial bending portion is formed at the other end of the inner strength member, pushing deformation or pushing deformation is promoted, and a more ideal F
-S characteristics are obtained.
【００１１】請求項４記載の発明は、内側強度部材の他
端と案内部材との間に所定の隙間が設けられている。According to a fourth aspect of the invention, a predetermined gap is provided between the other end of the inner strength member and the guide member.
【００１２】請求項４記載の発明によれば、内側強度部
材の他端と案内部材との間に所定の隙間が設けられてい
るため、外側強度部材の蛇腹変形を先に誘発させると共
に、内側強度部材の他端が案内部材に当たる際の衝撃に
より、該他端の押し出し変形又は押し込み変形が促進さ
れて、より理想的なＦ−Ｓ特性が得られる。According to the fourth aspect of the present invention, since the predetermined gap is provided between the other end of the inner strength member and the guide member, the bellows deformation of the outer strength member is induced first, and the inner strength member is also induced. The impact when the other end of the strength member hits the guide member promotes the push-out deformation or the push-in deformation of the other end, thereby obtaining a more ideal F-S characteristic.
【００１３】請求項５記載の発明は、外側強度部材に横
ビードが形成され、内側強度部材に縦ビードが形成され
ている。According to a fifth aspect of the present invention, a lateral bead is formed on the outer strength member and a vertical bead is formed on the inner strength member.
【００１４】請求項５記載の発明によれば、外側強度部
材に横ビードが形成され、内側強度部材に縦ビードが形
成されているため、外側強度部材の蛇腹変形が促進さ
れ、内側強度部材の折れが抑制される。According to the fifth aspect of the present invention, since the lateral bead is formed on the outer strength member and the vertical bead is formed on the inner strength member, the bellows deformation of the outer strength member is promoted and the inner strength member of the inner strength member is accelerated. Bending is suppressed.
【００１５】請求項６記載の発明は、内側強度部材の径
φが、外側強度部材の断面幅ｂと、該外側強度部材が荷
重を受けて蛇腹変形する際の波長λとの差（ｂ−λ）以
下に設定されている。According to a sixth aspect of the invention, the diameter φ of the inner strength member is the difference between the cross-sectional width b of the outer strength member and the wavelength λ when the outer strength member undergoes bellows deformation under load (b- λ) or less.
【００１６】請求項６記載の発明によれば、φ≦（ｂ−
λ）という関係にすることにより、外側強度部材が蛇腹
変形しても、その内側へ突出する部分が内側強度部材に
当たることがなく、該外側強度部材の十分な蛇腹変形が
確保される。According to the invention of claim 6, φ≤ (b-
With the relationship of λ), even if the outer strength member is bellows-deformed, the portion protruding inward does not hit the inner strength member, and sufficient bellows deformation of the outer strength member is ensured.
【００１７】請求項７記載の発明は、前記二重緩衝部材
を、該二重緩衝部材の一端を車体の第１支持部材に取付
け且つ他端を第２支持部材に取付けて使用した車体構造
である。According to a seventh aspect of the present invention, there is provided a vehicle body structure in which the double cushioning member is used by attaching one end of the double cushioning member to a first support member of a vehicle body and the other end to a second support member. is there.
【００１８】請求項７記載の発明によれば、二重緩衝部
材の一端を車体の第１支持部材に取付け、他端を第２支
持部材に取付けることにより、該二重緩衝部材の車体へ
の適用が可能となる。According to the invention of claim 7, one end of the double cushioning member is attached to the first support member of the vehicle body, and the other end is attached to the second support member, whereby the double cushioning member is attached to the vehicle body. Applicable.
【００１９】請求項８記載の発明は、二重緩衝部材がフ
ロントサイドメンバとして用いられ、第１支持部材がフ
ロントバンパの取付部分で、第２支持部材がダッシュパ
ネルである。According to an eighth aspect of the present invention, the double cushioning member is used as a front side member, the first supporting member is a mounting portion of the front bumper, and the second supporting member is a dash panel.
【００２０】請求項８記載の発明によれば、二重緩衝部
材をフロントサイドメンバとして用いることにより、車
両の前面衝突等による荷重を受けても、その荷重のエネ
ルギーを十分且つ理想的に吸収することができる。According to the eighth aspect of the present invention, by using the double cushioning member as the front side member, even if a load such as a frontal collision of the vehicle is received, the energy of the load is sufficiently and ideally absorbed. be able to.
【００２１】請求項９記載の発明は、二重緩衝部材がリ
ヤサイドメンバとして用いられ、第１支持部材がリヤバ
ンパの取付部分で、第２支持部材がシートバックパネル
である。According to a ninth aspect of the invention, the double cushioning member is used as a rear side member, the first supporting member is a mounting portion of the rear bumper, and the second supporting member is a seat back panel.
【００２２】請求項９記載の発明によれば、二重緩衝部
材をリヤサイドメンバとして用いることにより、車両の
後面衝突等による荷重を受けても、その荷重のエネルギ
ーを十分且つ理想的に吸収することができる。According to the invention described in claim 9, by using the double cushioning member as the rear side member, even if a load due to a rear collision of the vehicle is received, the energy of the load can be absorbed sufficiently and ideally. You can
【００２３】請求項１０記載の発明は、二重緩衝部材が
ステアリングコラムとして用いられ、第１支持部材がダ
ッシュパネルで、第２支持部材がステアリングホイール
である。According to a tenth aspect of the present invention, the double cushioning member is used as a steering column, the first supporting member is a dash panel, and the second supporting member is a steering wheel.
【００２４】請求項１０記載の発明によれば、二重緩衝
部材をステアリングコラムとして用いることにより、車
両の前面衝突等による偏荷重を受けても、その荷重のエ
ネルギーを十分且つ理想的に吸収することができると共
に折れにくい。According to the tenth aspect of the present invention, by using the double cushioning member as the steering column, even if an unbalanced load due to a frontal collision of the vehicle is received, the energy of the load is sufficiently and ideally absorbed. It is possible and hard to break.
【００２５】[0025]
【発明の実施の形態】以下、この発明の好適な実施形態
を図面に基づいて説明する。まず、図３を用いて、この
発明に係る二重緩衝部材１の基本構造を説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT A preferred embodiment of the present invention will be described below with reference to the drawings. First, the basic structure of the double cushioning member 1 according to the present invention will be described with reference to FIG.
【００２６】この二重緩衝部材１は、基本的に外側強度
部材２と、内側強度部材３と、案内部材４とから構成さ
れる。この二重緩衝部材１は、一端１ａが第１支持部材
５に取付けられ、他端１ｂが第２支持部材６にそれぞれ
取付けられて使用される。すなわち、外側強度部材２と
内側強度部材３の各一端２ａ、３ａは第１支持部材５に
取付けられ、外側強度部材２の他端２ｂと案内部材４と
は第２支持部材６に取付けられている。尚、内側強度部
材３の他端３ｂと案内部材４との間には所定の隙間Ｓが
設けられている。The double cushioning member 1 basically comprises an outer strength member 2, an inner strength member 3 and a guide member 4. The double buffer member 1 is used with one end 1a attached to the first support member 5 and the other end 1b attached to the second support member 6, respectively. That is, one ends 2a and 3a of the outer strength member 2 and the inner strength member 3 are attached to the first support member 5, and the other end 2b of the outer strength member 2 and the guide member 4 are attached to the second support member 6. There is. A predetermined gap S is provided between the other end 3b of the inner strength member 3 and the guide member 4.
【００２７】外側強度部材２は所定の断面幅ｂを有する
断面正方形部材であり、且つその長手方向にわたって内
側へ凸（凹でも可）の横ビード７が一定間隔λごとに形
成されている。内側強度部材３は径φの断面円形部材
で、その長手方向にわたって内側へ凸（凹でも可）の縦
ビード８が形成されている。The outer strength member 2 is a square member having a predetermined sectional width b, and lateral beads 7 that are convex (or concave) inward are formed at regular intervals λ in the longitudinal direction. The inner strength member 3 is a circular cross-section member having a diameter φ, and a vertical bead 8 that is convex (or concave) inward is formed in the longitudinal direction of the inner strength member 3.
【００２８】ここで、前記内側強度部材３の径φは、外
側強度部材２の断面幅ｂと、該外側強度部材２が荷重を
受けて蛇腹変形する際の波長（横ビード７の間隔に相
当）λとの差（ｂ−λ）以下に設定されている。すなわ
ち、φ≦（ｂ−λ）という関係になっている。Here, the diameter φ of the inner strength member 3 is the cross-sectional width b of the outer strength member 2 and the wavelength at which the outer strength member 2 undergoes bellows deformation under load (corresponding to the interval between the lateral beads 7). ) It is set to be equal to or less than the difference (b-λ) from λ. That is, the relationship is φ ≦ (b−λ).
【００２９】この内側強度部材３の他端３ｂは前記案内
部材４の先端に若干挿入した状態になっていると共に、
その他端３ｂには外側へ若干押し出された形状の初期た
わみ部９が形成されている。The other end 3b of the inner strength member 3 is slightly inserted into the tip of the guide member 4, and
The other end 3b is formed with an initial flexure 9 which is slightly extruded outward.
【００３０】次に、この二重緩衝部材１を、自動車強度
部材としてのフロントサイドメンバ１０、リヤサイドメ
ンバ１１、ステアリングコラム１２として利用する場合
の具体例を説明する（図１参照）。Next, a specific example in which the double cushioning member 1 is used as the front side member 10, the rear side member 11 and the steering column 12 as the automobile strength member will be described (see FIG. 1).
【００３１】フロントサイドメンバとして利用する場
合：図１に示すように、フロントサイドメンバ１０はエ
ンジンルームＥ内に前後方向に沿って配されるもので、
前端（一端）１０ａがフロントバンパ１３の取付部分
（第１支持部材）１４に取付けられ、後端（他端）１０
ｂがダッシュパネル（第２支持部材）１５に取付けられ
ている。When used as a front side member
Combination: As shown in FIG. 1, the front side member 10 is arranged in the engine room E along the front-rear direction,
A front end (one end) 10 a is attached to a mounting portion (first support member) 14 of the front bumper 13, and a rear end (other end) 10 a
b is attached to the dash panel (second support member) 15.
【００３２】このフロントサイドメンバ１０には車両の
前面衝突時に、その前端１０ａから真っ直ぐな荷重Ｆ1
が加わる。このような荷重Ｆ1 を受けると、まず外側強
度部材２が横ビード７をきっかけとして蛇腹状に変形す
る。このように外側強度部材２の蛇腹変形が先に誘発さ
れるのは、内側強度部材３の他端３ｂと案内部材４との
間に隙間Ｓが設けられているためである。次に、内側強
度部材３の他端３ｂに形成した初期たわみ部９が案内部
材４に当たり、該他端３ｂが押し出し方向に塑性変形す
る（図５参照）。内側強度部材３の他端３ｂに初期たわ
み部９が形成されており、且つ該初期たわみ部９と案内
部材４との間に前記隙間Ｓが設けられていることによ
り、初期たわみ部９が案内部材４に勢いよく当たって、
前記押し出し変形が促進される。The front side member 10 has a straight load F 1 from its front end 10a when a frontal collision of the vehicle occurs.
Is added. Upon receiving such a load F 1 , the outer strength member 2 is first deformed into a bellows shape with the lateral beads 7 as a trigger. The bellows deformation of the outer strength member 2 is first induced in this manner because the gap S is provided between the other end 3b of the inner strength member 3 and the guide member 4. Next, the initial bending portion 9 formed on the other end 3b of the inner strength member 3 contacts the guide member 4, and the other end 3b is plastically deformed in the pushing direction (see FIG. 5). Since the initial flexure 9 is formed at the other end 3b of the inner strength member 3 and the gap S is provided between the initial flexure 9 and the guide member 4, the initial flexure 9 is guided. Hit the member 4 vigorously,
The extrusion deformation is promoted.
【００３３】このように、荷重Ｆ1 による蛇腹変形の進
行によって外側強度部材２が短くなり、且つ内側強度部
材３の他端３ｂが押し出し変形されることにより、前記
荷重Ｆ1 のエネルギーを短いストロークで確実に吸収で
きるようになる。この実施形態のフロントサイドメンバ
１０におけるＦ−Ｓ特性を、該フロントサイドメンバ１
０と同じ断面積をもつ従来構造のフロントサイドメンバ
と比較して図２に示した。As described above, the outer strength member 2 is shortened and the other end 3b of the inner strength member 3 is extruded and deformed by the progress of the bellows deformation due to the load F 1 , so that the energy of the load F 1 is shortened. You will be able to absorb it with certainty. The F-S characteristic of the front side member 10 of this embodiment is calculated as follows.
It is shown in FIG. 2 in comparison with a conventional front side member having the same cross-sectional area as 0.
【００３４】この図２から明らかなように、この実施形
態のフロントサイドメンバ１０によれば、広範な変形ス
トローク範囲において、従来構造よりも高くて変動
（波）の少ない反力を示すことができる。特に、変形ス
トロークの後半においても反力が低下せず、最も理想的
とされる「油圧ダンパー」に近いＦ−Ｓ特性を示す。As is apparent from FIG. 2, according to the front side member 10 of this embodiment, it is possible to exhibit a reaction force that is higher and has less fluctuation (wave) than the conventional structure in a wide deformation stroke range. . In particular, the reaction force does not decrease even in the latter half of the deformation stroke, and the F-S characteristic close to that of the most ideal "hydraulic damper" is exhibited.
【００３５】また、この実施形態によれば、前記のφ≦
（ｂ−λ）という関係が保たれていることから、外側強
度部材２が蛇腹変形する際に、外側強度部材２の内側へ
突出する部分が内側強度部材３に当たることがなく、該
外側強度部材２の十分な外蛇腹変形が確保される。すな
わち、外側強度部材２は横ビード７の間隔λを波長とし
て蛇腹変形するため、最大に変形した状態では、外側強
度部材２の隣接する横ビード７間の側面部が完全に半分
に折りたたまれた状態となり、その間隔λの半分（λ／
２）に相当する分だけ、外側強度部材２の両側から内部
の内側強度部材３に向けて突出することになる。従っ
て、外側強度部材２の断面幅ｂから、前記両側から突出
する部分の量〔（λ／２）×２＝λ〕を引いた余りの寸
法（ｄ−λ）が、内側強度部材３の径φよりも大きけれ
ば当たらない。According to this embodiment, φ ≦
Since the relationship of (b−λ) is maintained, when the outer strength member 2 undergoes bellows deformation, the portion of the outer strength member 2 that protrudes inward does not hit the inner strength member 3 and the outer strength member 2 is prevented. 2, sufficient outer bellows deformation is ensured. That is, since the outer strength member 2 undergoes bellows deformation with the interval λ between the lateral beads 7 as a wavelength, in the maximum deformed state, the side surface portion between the adjacent lateral beads 7 of the outer strength member 2 is completely folded in half. And half of the interval λ (λ /
The portion corresponding to 2) is projected from both sides of the outer strength member 2 toward the inner strength member 3 inside. Therefore, the remainder dimension (d−λ) obtained by subtracting the amount [(λ / 2) × 2 = λ] of the portion protruding from both sides from the cross-sectional width b of the outer strength member 2 is the diameter of the inner strength member 3. If it is larger than φ, it will not hit.
【００３６】加えて、この実施形態では、外側強度部材
２に横ビード７が形成されているため、該外側強度部材
２の蛇腹変形が促進される。また、内側強度部材３に縦
ビード８が形成されているため、該内側強度部材３の折
れ、及びフロントサイドメンバ１０全体の折れが防止さ
れる。In addition, in this embodiment, since the lateral beads 7 are formed on the outer strength member 2, the bellows deformation of the outer strength member 2 is promoted. Further, since the vertical beads 8 are formed on the inner strength member 3, the inner strength member 3 and the entire front side member 10 are prevented from being broken.
【００３７】リヤサイドメンバとして利用する場合：図
１に示すように、リヤサイドメンバ１１はトランクルー
ムＴの下方に前後方向に沿って配されるもので、後端
（一端）１１ａがリヤバンパ１６の取付部分（第１支持
部材）１７に取付けられ、前端（他端）１１ｂがシート
バックパネル（第２支持部材）１８に取付けられてい
る。When used as a rear side member: As shown in FIG. 1, the rear side member 11 is arranged below the trunk T along the front-rear direction, and the rear end (one end) 11a thereof is attached to the rear bumper 16 ( It is attached to the first support member 17 and the front end (other end) 11 b is attached to the seat back panel (second support member) 18.
【００３８】このリヤサイドメンバ１１には車両の後面
衝突時に、その後端１１ｂから真っ直ぐな荷重Ｆ1 が加
わるが、先のフロントサイドメンバ１０の場合と同様
に、該荷重Ｆ1 のエネルギーを十分且つ確実に吸収する
ことができる。A straight load F 1 is applied from the rear end 11b to the rear side member 11 at the time of collision of the rear surface of the vehicle, but as in the case of the front side member 10, the energy of the load F 1 is sufficient and secured. Can be absorbed into.
【００３９】ステアリングコラムとして利用する場合：
図１に示すように、ステアリングコラム１２は車室内Ｒ
において、後ろ上がり斜め状態で配されるもので、前端
（一端）１２ａがダッシュパネル（第１支持部材）１５
に取付けられ、後端（他端）１２ｂがステアリングホイ
ール（第２支持部材）１９に取付けられている。このス
テアリングコラム１２は先のフロントサイドメンバ１０
やリヤサイドメンバ１１に比べて、小さい断面で細く形
成されている。When used as a steering column:
As shown in FIG. 1, the steering column 12 has a passenger compartment R.
In the above, the front end (one end) 12a is arranged in an obliquely rearward rising state, and the front end (one end) 12a is a dash panel (first support member) 15
The rear end (the other end) 12 b is attached to the steering wheel (second support member) 19. The steering column 12 is the front side member 10 described above.
Compared to the rear side member 11 and the rear side member 11, it has a smaller cross section and is formed thinner.
【００４０】このステアリングコラム１２には車両の前
面衝突時に、その前端１２ａから斜めの偏荷重Ｆ2 が加
わる（図３参照）。このような偏荷重Ｆ2 が加わって
も、折れにくく、該偏荷重Ｆ2 のエネルギーを効率良く
吸収することができる。At the time of a frontal collision of the vehicle, an oblique eccentric load F 2 is applied to the steering column 12 from its front end 12a (see FIG. 3). Even subjected to any such unbalanced load F 2, bending hardly, it is possible to efficiently absorb the energy of polarization load F 2.
【００４１】尚、以上の実施形態では、内側強度部材３
の他端３ｂに外向きの初期たわみ部９を形成し、該他端
３ｂを案内部材４により押し出し変形させる例を示した
が、図６及び図７に示すように、内側強度部材３の他端
３ｂに内向きの初期たわみ部２０を形成し、該他端２０
を別の形状をした案内部材４により押し込み変形させる
ようにしても前記と略同様の効果が得られる。In the above embodiment, the inner strength member 3 is used.
An example is shown in which the other end 3b is formed with an outward initial flexure 9 and the other end 3b is pushed out and deformed by the guide member 4. However, as shown in FIG. 6 and FIG. An inward initial flexure portion 20 is formed at the end 3b, and the other end 20
Even if is deformed by pushing the guide member 4 having a different shape, substantially the same effect as described above can be obtained.
【００４２】また、外側強度部材２として断面正方形部
材を例としたが、それ以外の断面五角形、断面六角形…
…等の多角形状でも良し、断面円形でも良い。製法とし
ては、押出成形により形成してもよいし、２つ以上の部
材を接合して形成しても良い。内側強度部材３も円形断
面に限定されない。Although a square member having a square cross section is taken as an example of the outer strength member 2, a pentagonal cross section, a hexagonal cross section ...
It may be a polygonal shape such as ... Or a circular cross section. As a manufacturing method, it may be formed by extrusion molding or may be formed by joining two or more members. The inner strength member 3 is not limited to the circular cross section either.
【００４３】更に、この発明の二重緩衝部材１は、荷重
を受け得るあらゆる強度部材として利用することがで
き、前記のフロントサイドメンバ１０等の他にも、各種
のフロントピラー、センタピラー、クロスメンバ等にも
利用可能である。Further, the double cushioning member 1 of the present invention can be used as any strength member capable of receiving a load, and in addition to the front side member 10 and the like, various front pillars, center pillars, crosses, and the like. It is also available to members.
【００４４】[0044]
【発明の効果】請求項１記載の発明によれば、外側強度
部材の内部に内側強度部材を設け且つその内側強度部材
の他端を案内部材により押し出し変形させることができ
るため、エネルギー吸収効率が高まると共に、理想的な
Ｆ−Ｓ特性が得られ、更に偏荷重を受けても折れにくく
なる。According to the invention described in claim 1, since the inner strength member can be provided inside the outer strength member and the other end of the inner strength member can be pushed out and deformed by the guide member, the energy absorption efficiency can be improved. As it increases, an ideal F-S characteristic can be obtained, and even if it receives an unbalanced load, it becomes difficult to break.
【００４５】請求項２記載の発明によれば、内側強度部
材の他端を押し込み変形させても前記同様の効果が得ら
れる。According to the second aspect of the invention, the same effect as described above can be obtained even when the other end of the inner strength member is pushed and deformed.
【００４６】請求項３記載の発明によれば、内側強度部
材の他端に初期たわみ部が形成されているため、押し出
し変形又は押し込み変形が促進されて、より理想的なＦ
−Ｓ特性が得られる。According to the third aspect of the invention, since the initial bending portion is formed at the other end of the inner strength member, pushing deformation or pushing deformation is promoted, and a more ideal F
-S characteristics are obtained.
【００４７】請求項４記載の発明によれば、内側強度部
材の他端と案内部材との間に所定の隙間が設けられてい
るため、外側強度部材の蛇腹変形を先に誘発させると共
に、内側強度部材の他端が案内部材に当たる際の衝撃に
より、該他端の押し出し変形又は押し込み変形が促進さ
れて、より理想的なＦ−Ｓ特性が得られる。According to the fourth aspect of the present invention, since the predetermined gap is provided between the other end of the inner strength member and the guide member, the bellows deformation of the outer strength member is induced first and the inner strength member is guided. The impact when the other end of the strength member hits the guide member promotes the push-out deformation or the push-in deformation of the other end, thereby obtaining a more ideal F-S characteristic.
【００４８】請求項５記載の発明によれば、外側強度部
材に横ビードが形成され、内側強度部材に縦ビードが形
成されているため、外側強度部材の蛇腹変形が促進さ
れ、内側強度部材の折れが抑制される。According to the fifth aspect of the present invention, since the lateral bead is formed on the outer strength member and the vertical bead is formed on the inner strength member, the bellows deformation of the outer strength member is promoted and the inner strength member is formed. Bending is suppressed.
【００４９】請求項６記載の発明によれば、φ≦（ｂ−
λ）という関係にすることにより、外側強度部材が蛇腹
変形しても、その内側へ突出する部分が内側強度部材に
当たることがなく、該外側強度部材の十分な蛇腹変形が
確保される。According to the invention of claim 6, φ ≦ (b−
With the relationship of λ), even if the outer strength member is bellows-deformed, the portion protruding inward does not hit the inner strength member, and sufficient bellows deformation of the outer strength member is ensured.
【００５０】請求項７記載の発明によれば、二重緩衝部
材の一端を車体の第１支持部材に取付け、他端を第２支
持部材に取付けることにより、該二重緩衝部材の車体へ
の適用が可能となる。According to the invention of claim 7, one end of the double cushioning member is attached to the first support member of the vehicle body, and the other end is attached to the second support member, whereby the double cushioning member is attached to the vehicle body. Applicable.
【００５１】請求項８記載の発明によれば、二重緩衝部
材をフロントサイドメンバとして用いることにより、車
両の前面衝突等による荷重を受けても、その荷重のエネ
ルギーを十分且つ理想的に吸収することができる。According to the eighth aspect of the present invention, by using the double cushioning member as the front side member, even if a load such as a frontal collision of the vehicle is received, the energy of the load is sufficiently and ideally absorbed. be able to.
【００５２】請求項９記載の発明によれば、二重緩衝部
材をリヤサイドメンバとして用いることにより、車両の
後面衝突等による荷重を受けても、その荷重のエネルギ
ーを十分且つ理想的に吸収することができる。According to the ninth aspect of the present invention, by using the double cushioning member as the rear side member, even if a load due to a rear collision of the vehicle is received, the energy of the load can be absorbed sufficiently and ideally. You can
【００５３】請求項１０記載の発明によれば、二重緩衝
部材をステアリングコラムとして用いることにより、車
両の前面衝突等による偏荷重を受けても、その荷重のエ
ネルギーを十分且つ理想的に吸収することができると共
に折れにくい。According to the tenth aspect of the present invention, by using the double cushioning member as the steering column, even if an unbalanced load due to a frontal collision of the vehicle is received, the energy of the load is sufficiently and ideally absorbed. It is possible and hard to break.
【図１】この発明の実施形態を説明するための自動車側
面図。FIG. 1 is a side view of an automobile for explaining an embodiment of the invention.
【図２】Ｆ−Ｓ特性を示すグラフ。FIG. 2 is a graph showing F-S characteristics.
【図３】二重緩衝部材の基本構造を示す斜視図。FIG. 3 is a perspective view showing a basic structure of a double cushioning member.
【図４】図３中矢示ＳＡ−ＳＡ線に沿う断面図。FIG. 4 is a sectional view taken along the line SA-SA shown in FIG. 3;
【図５】押し出し変形後の状態を示す図４相当の断面
図。FIG. 5 is a cross-sectional view corresponding to FIG. 4 showing a state after being deformed by extrusion.
【図６】押し込み変形用の内側強度部材及び案内部材を
示す図４相当の断面図。FIG. 6 is a cross-sectional view corresponding to FIG. 4, showing an inner strength member and a guide member for pushing deformation.
【図７】押し込み変形後の状態を示す図６相当の断面
図。FIG. 7 is a cross-sectional view corresponding to FIG. 6 showing a state after being deformed by pushing.
１ 二重緩衝部材 ２ 外側強度部材 ２ａ 外側強度部材の一端 ２ｂ 外側強度部材の他端 ３ 内側強度部材 ３ａ 内側強度部材の一端 ３ｂ 内側強度部材の他端 ４、 ２１ 案内部材 ５ 第１支持部材 ６ 第２支持部材 ７ 横ビード ８ 縦ビード ９、２０ 初期たわみ部 １０ フロントサイドメンバ １１ リヤサイドメンバ １２ ステアリングコラム １３ フロントバンパ １４ フロントバンパの取付部分（第１支持部材） １５ ダッシュパネル（第１・第２支持部材） １６ リヤバンパ １７ リヤバンパの取付部分（第１支持部材） １８ シートバックパネル（第２支持部材） １９ ステアリングホイール（第２支持部材） Ｆ1 荷重 Ｆ2 偏荷重 Ｓ 隙間 Ｅ エンジンルーム Ｒ 車室内 Ｔ トランクルームDESCRIPTION OF SYMBOLS 1 Double buffer member 2 Outer strength member 2a One end of outer strength member 2b The other end of outer strength member 3 Inner strength member 3a One end of inner strength member 3b The other end of inner strength member 4, 21 Guide member 5 First support member 6 Second support member 7 Horizontal bead 8 Vertical bead 9, 20 Initial flexure 10 Front side member 11 Rear side member 12 Steering column 13 Front bumper 14 Front bumper mounting part (first support member) 15 Dash panel (first and second) Support member 16 Rear bumper 17 Rear bumper mounting portion (first support member) 18 Seat back panel (second support member) 19 Steering wheel (second support member) F 1 load F 2 Unbalanced load S Gap E engine room R vehicle interior T trunk room
Claims (10)
外側強度部材内に、閉断面形状の内側強度部材を設け、
且つ前記外側強度部材の他端に内側強度部材の他端を受
容して該他端の押し出し変形の態様を特定する案内部材
を設けたことを特徴とする二重緩衝部材。1. An inner strength member having a closed cross-sectional shape is provided in an outer strength member having a closed cross-sectional shape capable of receiving a load from one end side.
A double shock-absorbing member, characterized in that a guide member is provided at the other end of the outer strength member to receive the other end of the inner strength member and to specify a form of extrusion deformation of the other end.
に代えて、押し込み変形の態様を特定する案内部材を設
けた請求項１記載の二重緩衝部材。2. The double shock-absorbing member according to claim 1, further comprising a guide member for specifying a mode of push-in deformation, instead of the guide member for specifying a mode of push-out deformation.
るための初期たわみ部が形成されている請求項１又は請
求項２記載の二重緩衝部材。3. The double cushioning member according to claim 1 or 2, wherein an initial flexure portion for promoting deformation is formed at the other end of the inner strength member.
所定の隙間が設けられている請求項１〜３のいずれか１
項に記載の二重緩衝部材。4. A predetermined gap is provided between the other end of the inner strength member and the guide member.
The double cushioning member according to the item.
側強度部材に縦ビードが形成されている請求項１〜４の
いずれか１項に記載の二重緩衝部材。5. The double cushioning member according to claim 1, wherein a horizontal bead is formed on the outer strength member and a vertical bead is formed on the inner strength member.
断面幅ｂと、該外側強度部材が荷重を受けて蛇腹変形す
る際の波長λとの差（ｂ−λ）以下に設定されている請
求項１〜５のいずれか１項に記載の二重緩衝部材。6. A diameter φ of the inner strength member is set to be equal to or less than a difference (b−λ) between a cross-sectional width b of the outer strength member and a wavelength λ when the outer strength member undergoes a bellows deformation under load. The double cushioning member according to any one of claims 1 to 5.
重緩衝部材を、該二重緩衝部材の一端を車体の第１支持
部材に取付け且つ他端を第２支持部材に取付けて使用し
た車体構造。7. The double cushioning member according to claim 1, wherein one end of the double cushioning member is attached to a first support member of a vehicle body and the other end is attached to a second support member. Used body structure.
して用いられ、第１支持部材がフロントバンパの取付部
分で、第２支持部材がダッシュパネルである請求項７記
載の車体構造。8. The vehicle body structure according to claim 7, wherein the double cushioning member is used as a front side member, the first supporting member is a mounting portion of the front bumper, and the second supporting member is a dash panel.
用いられ、第１支持部材がリヤバンパの取付部分で、第
２支持部材がシートバックパネルである請求項７記載の
車体構造。9. The vehicle body structure according to claim 7, wherein the double cushioning member is used as a rear side member, the first supporting member is a mounting portion of the rear bumper, and the second supporting member is a seat back panel.
して用いられ、第１支持部材がダッシュパネルで、第２
支持部材がステアリングホイールである請求項７記載の
車体構造。10. The double cushioning member is used as a steering column, the first supporting member is a dash panel, and the second supporting member is a dash panel.
The vehicle body structure according to claim 7, wherein the support member is a steering wheel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9438296A JPH09277960A (en) | 1996-04-16 | 1996-04-16 | Double cushioning member, and chassis frame and body construction using it |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9438296A JPH09277960A (en) | 1996-04-16 | 1996-04-16 | Double cushioning member, and chassis frame and body construction using it |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09277960A true JPH09277960A (en) | 1997-10-28 |
Family
ID=14108761
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9438296A Pending JPH09277960A (en) | 1996-04-16 | 1996-04-16 | Double cushioning member, and chassis frame and body construction using it |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH09277960A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006329429A (en) * | 2001-08-17 | 2006-12-07 | Alcoa Inc | Energy absorption assembly, taper, and flare device |
| JP2008302791A (en) * | 2007-06-07 | 2008-12-18 | Mazda Motor Corp | Energy absorption member |
| JP2009287749A (en) * | 2008-05-30 | 2009-12-10 | Nissan Motor Co Ltd | Energy absorber and energy absorbing method |
| JP2011021644A (en) * | 2009-07-14 | 2011-02-03 | Sumitomo Metal Ind Ltd | Shock absorbing member |
-
1996
- 1996-04-16 JP JP9438296A patent/JPH09277960A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006329429A (en) * | 2001-08-17 | 2006-12-07 | Alcoa Inc | Energy absorption assembly, taper, and flare device |
| JP2008302791A (en) * | 2007-06-07 | 2008-12-18 | Mazda Motor Corp | Energy absorption member |
| JP2009287749A (en) * | 2008-05-30 | 2009-12-10 | Nissan Motor Co Ltd | Energy absorber and energy absorbing method |
| JP2011021644A (en) * | 2009-07-14 | 2011-02-03 | Sumitomo Metal Ind Ltd | Shock absorbing member |
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