JP4979400B2 - Vehicle body strength adjusting device - Google Patents

Vehicle body strength adjusting device Download PDF

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JP4979400B2
JP4979400B2 JP2007025848A JP2007025848A JP4979400B2 JP 4979400 B2 JP4979400 B2 JP 4979400B2 JP 2007025848 A JP2007025848 A JP 2007025848A JP 2007025848 A JP2007025848 A JP 2007025848A JP 4979400 B2 JP4979400 B2 JP 4979400B2
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vehicle body
buckling
plate
crushing strength
plates
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JP2008189156A (en
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俊次 鈴木
雄太 漆山
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Honda Motor Co Ltd
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Description

本発明は、バンパービームと車体フレームとの間に、車体前後方向の衝突荷重を受けて圧壊する圧壊強度が可変な圧壊強度可変装置を配置した車両の車体強度調整装置に関する。   The present invention relates to a vehicle body strength adjusting device for a vehicle in which a crushing strength variable device is provided between a bumper beam and a vehicle body frame, and a crushing strength variable device that can be crushed by receiving a collision load in the longitudinal direction of the vehicle body.

自動車のフロントサイドフレームの前端に取り付けられるバンパービームを、相互に平行に配置された前後一対のビーム部材と、両ビーム部材間に所定間隔で配置された複数の圧壊強度可変装置とで構成したものが、下記特許文献1により公知である。   A bumper beam attached to the front end of the front side frame of an automobile is composed of a pair of front and rear beam members arranged in parallel to each other and a plurality of variable crushing strength devices arranged at predetermined intervals between both beam members. Is known from Patent Document 1 below.

前記圧壊強度可変装置は衝突の衝撃で座屈するように隣接して配置された複数の形状記憶合金製の座屈板と、それらの座屈板を一体に連結した状態および相互に分離した状態に切り換えるアクチュエータとを備えており、座屈板を一体に連結した状態では座屈強度を高めて吸収可能な衝突エネルギーを増加させることができ、また座屈板を相互に分離した状態では座屈強度を低めて吸収可能な衝突エネルギーを減少させることができる。
特開2006−8106号公報
The crushing strength variable device has a plurality of shape memory alloy buckling plates arranged adjacent to each other so as to buckle by the impact of a collision, and these buckling plates are integrally connected and separated from each other. It is possible to increase the impact energy that can be absorbed by increasing the buckling strength when the buckling plates are connected together, and the buckling strength when the buckling plates are separated from each other. Can be absorbed to reduce the impact energy that can be absorbed.
JP 2006-8106 A

ところで、車両の衝突荷重を効果的に吸収するには座屈板の圧壊の開始から終了までの間、高い荷重を維持することが望ましい。しかしながら、鉄材やアルミニウム材で構成した座屈板では、その変形量の増加に伴って荷重が急激に高まってピークに達した後に漸減する特性を有しており、一定の高い荷重を維持することは困難である。また形状記憶合金で構成した座屈板では、その変位量の増加に伴って荷重が急激に高まってピークに達した後に急激に減少してボトムに達し、そこから漸増する特性を有しており、やはり一定の高い荷重を維持することは困難である。   By the way, in order to effectively absorb the collision load of the vehicle, it is desirable to maintain a high load from the start to the end of the buckling plate collapse. However, buckling plates made of iron or aluminum have the property that the load increases rapidly and reaches a peak as the amount of deformation increases, and then gradually decreases, maintaining a constant high load. It is difficult. In addition, the buckling plate made of shape memory alloy has the characteristic that the load suddenly increases with the increase of the displacement, reaches the peak, decreases rapidly, reaches the bottom, and gradually increases from there. Again, it is difficult to maintain a constant high load.

本発明は前述の事情に鑑みてなされたもので、車両の衝突時に圧壊強度可変装置の座屈板の座屈による衝撃吸収効果を最大限に発揮させる。   The present invention has been made in view of the above-described circumstances, and maximizes the impact absorption effect due to buckling of the buckling plate of the variable crushing strength device at the time of vehicle collision.

上記目的を達成するために、請求項1に記載された発明によれば、バンパービームとその後方に存する車体フレームとの間に、車体前後方向の衝突荷重を受けて圧壊する圧壊強度が可変な圧壊強度可変装置を配置した車両の車体強度調整装置において、前記圧壊強度可変装置は、前記車体フレームの前部に固定されるブロック部材と、そのブロック部材の左右両側にそれぞれ配置されて前記車体フレームの前部に連結される左右一対のヒンジ板と、その両ヒンジ板にそれぞれ設けたロックピン支持部に係脱可能として前記ブロック部材に摺動可能に嵌合、支持される左右一対のロックピンと、前記バンパービームに結合した座屈板支持板の左右両端部と前記左右一対のヒンジ板との間にそれぞれ介装されて、前記ロックピンの前記ロックピン支持部への係合状態では前記衝突荷重により一体に座屈するように相互に重ね合わせられる左右各一対の第1座屈板および第2座屈板と、その左側の第1,第2座屈板の重合体及び右側の第1,第2座屈板の重合体間で左右から、また前記座屈板支持板及び前記ブロック部材間で前後からそれぞれ挟まれて左右の各第1,第2座屈板の左右方向の倒れに対抗する薄板よりなる倒れ防止板とを備え、前記第2座屈板は形状記憶合金で、また前記第1座屈板は形状記憶合金以外の材料でそれぞれ構成されると共に、それら第1、第2座屈板の車体前後方向の長さが異ならせて設定されることを特徴とする車両の車体強度調整装置が提案される。 In order to achieve the above object, according to the invention described in claim 1, the crushing strength to be crushed by receiving a collision load in the longitudinal direction of the vehicle body between the bumper beam and the vehicle body frame existing behind the bumper beam is variable. In the vehicle body strength adjusting device for a vehicle in which the crushing strength varying device is arranged, the crushing strength varying device is arranged on each of the block member fixed to the front portion of the body frame and the left and right sides of the block member. A pair of left and right hinge plates connected to the front portion of the two and a pair of left and right lock pins slidably fitted to and supported by the block member so as to be detachable from the lock pin support portions provided on the hinge plates, respectively. The lock pin of the lock pin is interposed between the left and right ends of the buckling plate support plate coupled to the bumper beam and the pair of left and right hinge plates, respectively. A first seat屈板and second seat屈板right of each pair are superimposed on each other such buckled together by the collision load in the engaged condition to the lifting portion, the first, second buckling of the left The first and second left and right sandwiched between the polymer of the plate and the polymer of the first and second buckling plates on the right side, and from the front and rear, respectively, between the buckling plate support plate and the block member. and a prevention plate collapse consisting sheet against falling in the lateral direction of the seat屈板, the second seat屈板a shape memory alloy and said first seat屈板each composed of a material other than a shape memory alloy is Rutotomoni, they first, adjusting the rigidity of vehicle body apparatus for a vehicle, wherein the vehicle longitudinal direction length of the second seat屈板is set at different are proposed.

また請求項2に記載された発明によれば、請求項1の構成に加えて、前記倒れ防止板の車体前後方向の中間部には、左右方向に延びる横断面三角状のリブが形成されることを特徴とする車両の車体強度調整装置が提案される。 According to the second aspect of the present invention, in addition to the configuration of the first aspect, a rib having a triangular cross section extending in the left-right direction is formed in the middle portion of the vehicle body front-rear direction of the fall prevention plate. A vehicle body strength adjusting device for a vehicle is proposed.

また請求項3に記載された発明によれば、請求項1または請求項2の構成に加えて、前記第1座屈板に形成した固定爪を折り曲げて前記第2座屈板を一体に固定したことを特徴とする車両の車体強度調整装置が提案される。   According to the invention described in claim 3, in addition to the configuration of claim 1 or claim 2, the fixing buckle plate formed on the first buckling plate is bent to fix the second buckling plate integrally. A vehicle body strength adjusting device for a vehicle characterized by the above is proposed.

また請求項4に記載された発明によれば、請求項1〜3の何れかの構成に加えて、前記圧壊強度可変装置を覆うブーツの開口を、前記圧壊強度可変装置を車体フレームに固定する固定部材にその外周を覆うように固定するとともに、前記圧壊強度可変装置から延びるハーネスを、前記固定部材に形成した開口を通して前記車体フレームの内部に導いたことを特徴とする車両の車体強度調整装置が提案される。According to the invention described in claim 4, in addition to the structure of any one of claims 1 to 3, the opening of the boot covering the crushing strength varying device is fixed to the vehicle body frame. A vehicle body strength adjusting device for a vehicle, wherein the vehicle body strength adjusting device is fixed to a fixing member so as to cover an outer periphery thereof, and a harness extending from the crushing strength varying device is led into the body frame through an opening formed in the fixing member. Is proposed.

尚、実施の形態のフロントサイドフレーム12は本発明の車体フレームに対応する。   The front side frame 12 of the embodiment corresponds to the vehicle body frame of the present invention.

請求項1の構成によれば、衝突荷重により一体に座屈するように重ね合わせた第1座屈板および第2座屈板のうち、第2座屈板を変形の初期を除く領域で変位量の増加に伴って荷重が増加する傾向を有する形状記憶合金で構成し、第1座屈板を変形の初期を除く領域で変位量の増加に伴って荷重が減少する傾向を有する形状記憶合金以外の材料で構成したので、衝突の過程において第1、第2座屈板の荷重の和を略一定の高い値に保ち、圧壊強度可変装置の衝撃吸収効果を最大限に発揮させることができる。しかも第1、第2座屈板の車体前後方向の長さを異ならせたので、第1座屈板が圧縮されて荷重を発生するタイミングと第2座屈板が圧縮されて荷重を発生するタイミングとを異ならせ、第1、第2座屈板の荷重の和をより精度良く一定の値に近づけることができる。 According to the configuration of the first aspect, of the first buckling plate and the second buckling plate that are overlapped so as to be integrally buckled by a collision load, the second buckling plate is displaced in a region excluding the initial stage of deformation. Other than the shape memory alloy, which is composed of a shape memory alloy having a tendency that the load increases with an increase in the thickness, and the first buckling plate has a tendency that the load decreases with an increase in the displacement amount in a region excluding the initial stage of deformation. Therefore, the sum of the loads of the first and second buckling plates can be maintained at a substantially constant high value in the course of the collision, and the impact absorbing effect of the variable crushing strength device can be maximized. Moreover, since the lengths of the first and second buckling plates in the longitudinal direction of the vehicle body are made different, the timing when the first buckling plate is compressed and the load is generated and the second buckling plate is compressed and the load is generated. By making the timing different, the sum of the loads of the first and second buckling plates can be brought closer to a constant value with higher accuracy.

また特に車両が正面衝突してバンパービームに車体後方への衝突荷重が加わる場合において、圧壊強度可変装置のロックピンがヒンジ板のロックピン支持部に係合した高荷重モードの状態では、相互に重ね合わされた第1、第2座屈板が前後方向に圧縮されて座屈することで、圧壊強度可変装置は大きな衝突エネルギーを吸収することができるが、ロックピンがヒンジ板のロックピン支持部から後退した低荷重モードの状態では、第1、第2座屈板は座屈することなく折り畳まれ、圧壊強度可変装置は小さな荷重で圧壊してバンパービームの後退を許容する。そして、その何れの場合にも、第1、第2倒れ防止板は前後方向の圧縮荷重を受けて座屈するが、元々第1、第2倒れ防止板は薄板で構成されていて、前後方向の荷重を受けると容易に座屈し、圧壊強度可変装置の前後方向のエネルギー吸収特性に影響を及ぼすことはなく、即ち、倒れ防止板によって圧壊強度可変装置が圧壊し難くなる虞はない。それに対し、車両の斜め衝突によってバンパービームに車体前後方向に対して傾斜した衝突荷重が加わった場合には、右側の第1、第2座屈板と左側の第1、第2座屈板とが座屈することなく左右方向に倒れて、高荷重モードの状態であっても殆どエネルギー吸収性能を発揮できなくなる可能性があるが、本発明では、前記倒れ防止板により、左右の第1、第2座屈板が倒れるのを抑制し、圧壊強度可変装置を前後方向に確実に圧壊してエネルギー吸収性能を効率的に発揮させることができる。Also, especially when the vehicle collides head-on and a collision load is applied to the bumper beam from the rear of the vehicle body, in the high load mode state where the lock pin of the crushing strength varying device is engaged with the lock pin support part of the hinge plate, When the superposed first and second buckling plates are compressed in the front-rear direction and buckled, the crushing strength variable device can absorb a large amount of collision energy, but the lock pin is separated from the lock pin support portion of the hinge plate. In the retreated low load mode, the first and second buckling plates are folded without buckling, and the crushing strength varying device crushes with a small load to allow the bumper beam to retreat. In either case, the first and second fall prevention plates are buckled by receiving a compressive load in the front-rear direction, but the first and second fall prevention plates are originally composed of thin plates, When a load is applied, it easily buckles and does not affect the energy absorption characteristics of the crushing strength varying device in the front-rear direction, that is, the collapse preventing plate does not cause the crushing strength varying device to be difficult to crush. On the other hand, when a collision load that is inclined with respect to the longitudinal direction of the vehicle body is applied to the bumper beam due to the oblique collision of the vehicle, the first and second buckling plates on the right side and the first and second buckling plates on the left side May fall in the left-right direction without buckling, and even if it is in a high load mode, the energy absorption performance may hardly be exhibited. 2 It is possible to suppress the buckling plate from collapsing, and to reliably collapse the variable crushing strength device in the front-rear direction so as to efficiently exhibit energy absorption performance.

また請求項2の構成によれば、倒れ防止板の車体前後方向の中間部には、左右方向に延びる横断面三角状のリブが形成されるので、倒れ防止板を設けても、第1,第2座屈板の座屈が開始される荷重を低下させ、荷重変動の少ない特性を得ることができる。 According to the second aspect of the present invention, since the rib in the cross-sectional direction extending in the left-right direction is formed in the middle portion of the vehicle body longitudinal direction of the fall prevention plate, The load at which buckling of the second buckling plate is started can be reduced, and characteristics with little load fluctuation can be obtained.

また請求項3の構成によれば、第1座屈板に形成した固定爪を折り曲げて第2座屈板を一体に固定するので、加工が難しい形状記憶合金製の第2座屈板に特別の加工を施すことなく、第1、第2座屈板を一体化することができる。   Further, according to the third aspect of the present invention, since the second buckling plate is integrally fixed by bending the fixing claw formed on the first buckling plate, the second buckling plate made of shape memory alloy is difficult to process. The first and second buckling plates can be integrated without performing the above process.

また請求項4の構成によれば、圧壊強度可変装置に水や泥が付着するのをブーツで遮り、その耐久性を高めるとともに作動の確実性を保証することができる。また、ブーツに孔を形成してハーネスを引き出すことなくブーツの防水性が確保される上、ハーネスを車体フレームの内部に導いてハーネスを水や泥から保護することができる。According to the fourth aspect of the present invention, it is possible to prevent water and mud from adhering to the crushing strength varying device with the boot, thereby improving the durability and ensuring the reliability of the operation. Further, the waterproofness of the boot is ensured without forming a hole in the boot and pulling out the harness, and the harness can be guided to the inside of the vehicle body frame to protect the harness from water and mud.

以下、本発明の実施の形態を添付の図面に基づいて説明する。   Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

図1〜図13は本発明の第1の実施の形態を示すもので、図1は車両の車体前部の平面図、図2は図1の2部拡大図、図3は圧壊強度可変装置の斜視図、図4は圧壊強度可変装置の分解斜視図、図5は図2の5−5線断面図、図6は図5の6−6線断面図、図7は図2の7−7線断面図、図8は図2の8方向矢視図、図9は高荷重モードの作用説明図、図10は低荷重モードの作用説明図、図11は第1、第2倒れ防止板の作用説明図、図12は第1、第2座屈板の座屈時の作用説明図、図13は衝突時のバンパービームの伸び変形の作用説明図である。   1 to 13 show a first embodiment of the present invention. FIG. 1 is a plan view of a front part of a vehicle body of a vehicle, FIG. 2 is an enlarged view of part 2 of FIG. 1, and FIG. 4 is an exploded perspective view of the crushing strength varying device, FIG. 5 is a cross-sectional view taken along line 5-5 in FIG. 2, FIG. 6 is a cross-sectional view taken along line 6-6 in FIG. Fig. 8 is a sectional view taken along line 7, Fig. 8 is a view taken in the direction of arrow 8 in Fig. 2, Fig. 9 is an explanatory diagram of the operation in the high load mode, Fig. 10 is an explanatory diagram of the operation in the low load mode, FIG. 12 is a diagram for explaining the action of the first and second buckling plates during buckling, and FIG. 13 is a diagram for explaining the action of the bumper beam extending and deforming at the time of collision.

図1に示すように、四輪の車両の車体前部に配置されたバンパービーム11は、車幅方向に直線状に延びる本体部11aと、本体部11aの左右両端から車体後方に向けて傾斜する左右の傾斜部11b,11bとを備える。車体の両側部に前後方向に配置されたフロントサイドフレーム12,12の先端とバンパービーム11の左右の傾斜部11b,11bとが、圧壊強度を変更可能な圧壊強度可変装置13,13により接続される。左右の圧壊強度可変装置13,13は実質的に同じ構造を有しているため、以下、左側の圧壊強度可変装置13を例に取って構造を説明する。   As shown in FIG. 1, a bumper beam 11 disposed at the front of a vehicle body of a four-wheel vehicle is inclined toward the rear of the vehicle body from a body portion 11a extending linearly in the vehicle width direction and from both left and right ends of the body portion 11a. Left and right inclined portions 11b, 11b. Front ends of front side frames 12, 12 arranged in the front-rear direction on both sides of the vehicle body and left and right inclined portions 11 b, 11 b of the bumper beam 11 are connected by crushing strength variable devices 13, 13 that can change the crushing strength. The Since the left and right crushing strength varying devices 13 and 13 have substantially the same structure, the structure will be described below by taking the left crushing strength varying device 13 as an example.

図2〜図7に示すように、ボックス断面を有するフロントサイドフレーム12の前端開口を閉塞する端板12aに圧壊強度可変装置13の取付板14が4本のボルト15…で固定され、取付板14の前面に円板状の厚板で構成される後部基板16が4本のボルト17…で固定される。後部基板16の前面にスペーサ板18と、ヒンジ支持板19と、ブロック部材20とが重ね合わされ、ブロック部材20の肉抜き孔20aの内部から後向きに挿入された4本のボルト21…が、ヒンジ支持板19およびスペーサ板18を貫通して後部基板16に締結される。   As shown in FIGS. 2 to 7, the mounting plate 14 of the crushing strength varying device 13 is fixed to the end plate 12a that closes the front end opening of the front side frame 12 having a box cross section with four bolts 15. A rear substrate 16 composed of a disk-shaped thick plate is fixed to the front surface of 14 with four bolts 17. A spacer plate 18, a hinge support plate 19 and a block member 20 are superimposed on the front surface of the rear substrate 16, and four bolts 21 inserted backward from the inside of the lightening holes 20a of the block member 20 are hinges. The support plate 19 and the spacer plate 18 are penetrated and fastened to the rear substrate 16.

ブロック部材20の左右にそれぞれ配置されるヒンジ板22は、筒状に曲げられた一対のロックピン支持部22a,22aと、ロックピン支持部22a,22aから相互に離反するように延びる第1、第2ヒンジアーム22b,22cとを備える。第1ヒンジアーム22bの後端はヒンジ支持板19の外端の角部に溶接W1(図3参照)され、第2ヒンジアーム22cは鉄材製の第1座屈板24の外面に溶接W2(図3参照)される。第1座屈板24は中央部に座屈強度を調整するためのリブ24aを備えるとともに、外周部に4個の固定爪24b…を備える。形状記憶合金で第1座屈板24と概ね同寸法に形成した矩形状の第2座屈板25が、前記4個の固定爪24b…によって第1座屈板24の内面に重ね合わされるように固定される。   The hinge plates 22 respectively disposed on the left and right sides of the block member 20 have a pair of lock pin support portions 22a and 22a bent in a cylindrical shape, and first and second extending so as to be separated from the lock pin support portions 22a and 22a. Second hinge arms 22b and 22c are provided. The rear end of the first hinge arm 22b is welded to the corner of the outer end of the hinge support plate 19 (see FIG. 3), and the second hinge arm 22c is welded to the outer surface of the first buckling plate 24 made of iron (W2 ( 3). The first buckling plate 24 includes a rib 24a for adjusting the buckling strength at the center portion and four fixing claws 24b. A rectangular second buckling plate 25 formed of a shape memory alloy and approximately the same size as the first buckling plate 24 is superimposed on the inner surface of the first buckling plate 24 by the four fixing claws 24b. Fixed to.

形状記憶合金製の第2座屈板25は加工が難しく溶接にも適さないため、第1、第2座屈板24,25をボルト止めや溶接で一体化するのは困難であるが、第1、第2座屈板24,25を、加工が容易な鉄材製の第1座屈板24に設けた固定爪24b…で一体化したので、加工コストを削減しながら第1、第2座屈板24,25を確実に一体化することができる。   Since the second buckling plate 25 made of shape memory alloy is difficult to process and unsuitable for welding, it is difficult to integrate the first and second buckling plates 24 and 25 by bolting or welding. Since the first and second buckling plates 24 and 25 are integrated with the fixing claws 24b provided on the first buckling plate 24 made of iron that is easy to process, the first and second seats are reduced while reducing the processing cost. The bent plates 24 and 25 can be reliably integrated.

第1、第2座屈板24,25の前端の位置は揃っているが、第2座屈板25の後端は第1座屈板24の後端よりも僅かに後方にまで延びている(図2参照)。即ち、第1座屈板24の前後方向長さは、第2座屈板25の前後方向長さよりも僅かに短くなっている。   Although the positions of the front ends of the first and second buckling plates 24 and 25 are aligned, the rear end of the second buckling plate 25 extends slightly rearward from the rear end of the first buckling plate 24. (See FIG. 2). That is, the longitudinal length of the first buckling plate 24 is slightly shorter than the longitudinal length of the second buckling plate 25.

ブロック部材20の前面の左右両側に、上下方向に延びる断面U字状の支持溝20b,20bが形成されており、各々の支持溝20bに円筒状のブッシュ26が固定される。ブッシュ26の内部には2本のロックピン27,27が摺動自在に支持されており、相対向するロックピン27,27の側面にそれぞれ形成されたラック27a,27aに共通のピニオン28が噛合する。ブロック部材20の肉抜き孔20aの前方に形成されたモータ支持孔20cに支持されたモータ29の回転軸29aの両端に前記ピニオン28が固定される。よって、モータ29によりピニオン28が回転すると、ピニオン28にラック27a,27aを駆動された2本のロックピン27,27が相互に接近・離反する方向に移動する。   Support grooves 20b and 20b having a U-shaped cross section extending in the vertical direction are formed on the left and right sides of the front surface of the block member 20, and a cylindrical bush 26 is fixed to each support groove 20b. Two lock pins 27, 27 are slidably supported inside the bush 26, and a common pinion 28 meshes with racks 27a, 27a formed on the side surfaces of the lock pins 27, 27 facing each other. To do. The pinions 28 are fixed to both ends of a rotating shaft 29a of a motor 29 supported by a motor support hole 20c formed in front of the lightening hole 20a of the block member 20. Therefore, when the pinion 28 is rotated by the motor 29, the two lock pins 27, 27 having the racks 27a, 27a driven by the pinion 28 move in directions toward and away from each other.

通常、2本のロックピン27,27の先端のテーパー状の係合部27b,27bはブッシュ26の端部から突出しており、その先端の係合部27b,27bがヒンジ板22の一対のロックピン支持部22a,22aに圧入した受け部材51,51にそれぞれ係合する(図5および図6の実線参照)。そして、ロックピン27,27がモータ29により駆動されてブッシュ26の内部に引き込まれると、その先端の係合部27b,27bがヒンジ板22の一対の受け部材51,51から離脱する(図5および図6の鎖線参照)。 Usually, the tapered engaging portions 27 b and 27 b at the tips of the two lock pins 27 and 27 protrude from the ends of the bush 26, and the engaging portions 27 b and 27 b at the tips are a pair of locks of the hinge plate 22. It engages with receiving members 51 and 51 press-fitted into the pin support portions 22a and 22a, respectively (see solid lines in FIGS. 5 and 6) . Then , when the lock pins 27 and 27 are driven by the motor 29 and pulled into the bush 26, the engagement portions 27b and 27b at the tips thereof are disengaged from the pair of receiving members 51 and 51 of the hinge plate 22 (FIG. 5). And the dashed line in FIG. 6).

2分割された第1モータ支持板30,30がブロック部材20のモータ支持孔20cの周囲にそれぞれ2本のボルト31,31で固定されるとともに、第2モータ支持板32がブロック部材20のモータ支持孔20cの周囲に4本のボルト33…で固定されており、モータ29は第1、第2モータ支持板30,30;32に挟まれるように支持される。   The two divided first motor support plates 30, 30 are fixed around the motor support hole 20 c of the block member 20 with two bolts 31, 31, respectively, and the second motor support plate 32 is a motor of the block member 20. It is fixed around the support hole 20c by four bolts 33, and the motor 29 is supported so as to be sandwiched between the first and second motor support plates 30, 30;

一方、ブロック部材20の前面に、左右一対の内側座屈板支持板34,34と、厚肉円板状の前部基板35を一体に備えた外側座屈板支持板36とが重ね合わされ、その内側座屈板支持板34,34及び外側座屈板支持板36間が8本のボルト37…,38…で一体に結合される。そして、各内側座屈板支持板34の左右方向外端を溝状の屈曲させた座屈板支持部34aが、重ね合わされた第1、第2座屈板24,25の前端に係合し、第1座屈板24に溶接W3(図3参照)される。 On the other hand, on the front surface of the block member 20, a pair of left and right inner buckling plate support plates 34, 34 and an outer buckling plate support plate 36 integrally provided with a thick disc-shaped front substrate 35 are superimposed, The inner buckling plate support plates 34 and 34 and the outer buckling plate support plate 36 are integrally coupled by eight bolts 37. And the buckling plate support part 34a which bent the left-right direction outer end of each inner buckling plate support plate 34 at the groove shape is engaged with the front end of the 1st, 2nd buckling plates 24 and 25 which were piled up. The first buckling plate 24 is welded W3 (see FIG. 3).

中間部に三角状のリブ39aが形成された第1倒れ防止板39は前後のフランジ39b,39cを備えており、前側のフランジ39bが前記ボルト37,37で内側座屈板支持板34および外側座屈板支持板36に共締めされるとともに、後側のフランジ39cが前記第1モータ支持板30のフランジ30aに2本のボルト40,40で固定される。また中間部に三角状のリブ41aが形成された第2倒れ防止板41は前後のフランジ41b,41cを備えており、前側のフランジ41bが前記ボルト38,38で内側座屈板支持板34および外側座屈板支持板36に共締めされるとともに、後側のフランジ41cが前記第2モータ支持板32に前記ボルト33,33で共締めされる。   The first fall-preventing plate 39 having a triangular rib 39a formed at the intermediate portion is provided with front and rear flanges 39b and 39c. The front flange 39b is the bolts 37 and 37 and the inner buckling plate support plate 34 and the outer side are provided. While being fastened together with the buckling plate support plate 36, the rear flange 39 c is fixed to the flange 30 a of the first motor support plate 30 with two bolts 40, 40. Further, the second fall prevention plate 41 having a triangular rib 41a formed at the intermediate portion is provided with front and rear flanges 41b and 41c, and the front flange 41b is formed by the bolts 38 and 38 with the inner buckling plate support plate 34 and While being fastened to the outer buckling plate support plate 36, the rear flange 41 c is fastened to the second motor support plate 32 by the bolts 33 and 33.

第1、第2倒れ防止板39,41は概ね台形状の部材であって、その上底に対応する前縁が内側座屈板支持板34および外側座屈板支持板36に固定され、その下底に対応する後縁がブロック部材20に固定され、その一対の斜辺に対応する左右の側縁が第2座屈板25の内面に僅かな隙間α(図2参照)を介して対向する。   The first and second fall prevention plates 39, 41 are substantially trapezoidal members, and the front edges corresponding to the upper bases thereof are fixed to the inner buckling plate support plate 34 and the outer buckling plate support plate 36, respectively. The rear edge corresponding to the lower base is fixed to the block member 20, and the left and right side edges corresponding to the pair of oblique sides face the inner surface of the second buckling plate 25 with a slight gap α (see FIG. 2). .

図2および図8から明らかなように、バンパービーム11と圧壊強度可変装置13とを接続する取付ブラケット42は、車体前後方向に延びる軸線Lに対して斜めに傾斜してバンパービーム11の傾斜部11bと平行な第1取付部42aと、圧壊強度可変装置13の前部基板35と平行な第2取付部42bと、車体前後方向に延びて第1、第2取付部42a,42bを連結する複数の薄肉のリブ42c…とを備える。バンパービーム11の傾斜部11bの後面には左右方向に長い4個の第1ボルト孔11c…が形成されており、これらの第1ボルト孔11c…と取付ブラケット42の第1取付部42aの第2ボルト孔42d…とが4本のボルト43…および4個のナット44…で締結される。そして取付ブラケット42の第2取付部42bと圧壊強度可変装置13の前部基板35とが2本のボルト45,45で締結される。   As apparent from FIGS. 2 and 8, the mounting bracket 42 for connecting the bumper beam 11 and the crushing strength varying device 13 is inclined with respect to the axis L extending in the longitudinal direction of the vehicle body, and the inclined portion of the bumper beam 11 is inclined. 11b, a first mounting portion 42a parallel to the crushing strength variable device 13, a second mounting portion 42b parallel to the front substrate 35, and the first and second mounting portions 42a, 42b extending in the longitudinal direction of the vehicle body. And a plurality of thin ribs 42c. Four first bolt holes 11c, which are long in the left-right direction, are formed on the rear surface of the inclined portion 11b of the bumper beam 11, and the first bolt holes 11c ... and the first mounting portions 42a of the mounting bracket 42 are provided. The two bolt holes 42d are fastened by four bolts 43 and four nuts 44. Then, the second mounting portion 42 b of the mounting bracket 42 and the front substrate 35 of the crushing strength varying device 13 are fastened by two bolts 45, 45.

このように構成された圧壊強度可変装置13は、図1および図2に示すように、伸縮自在なゴム製のブーツ46内に収納された状態で、ブーツ46の後部開口46aが円形の後部基板16の外周に嵌合してバンド47で締結され、ブーツ46の前部開口46bが円形の前部基板35の外周に嵌合してバンド48で締結される。これにより圧壊強度可変装置13に水や泥が付着するのをブーツ46で遮り、その耐久性を高めるとともに作動の確実性を保証することができる。   As shown in FIGS. 1 and 2, the crushing strength varying device 13 configured as described above is housed in a stretchable rubber boot 46, and the rear opening 46 a of the boot 46 is a circular rear substrate. The front opening 46 b of the boot 46 is fitted to the outer periphery of the circular front substrate 35 and fastened by the band 48. As a result, the boot 46 can block water and mud from adhering to the crushing strength varying device 13, thereby improving the durability and ensuring the reliability of the operation.

図1〜図4から明らかなように、モータ29から延びるハーネス49は、第1モータ支持板30,30の開口30bを通過した後、ブロック部材20の開口20d、ヒンジ支持板19の開口19a、スペーサ板18の開口18aおよび後部基板16の開口16aに装着したグロメット52を通過し、更に取付板14の開口14aおよびフロントサイドフレーム12の端板12aの開口12bを通過してフロントサイドフレーム12の内部に導かれる。従って、ブーツ46に孔を形成してハーネス49を引き出す必要がなくなってブーツ46の防水性が確保されるだけでなく、ハーネス49を閉断面のフロントサイドフレーム12の内部に導くことにより、ハーネス49を水や泥から保護することができる。   As apparent from FIGS. 1 to 4, the harness 49 extending from the motor 29 passes through the opening 30 b of the first motor support plate 30, 30, and then the opening 20 d of the block member 20, the opening 19 a of the hinge support plate 19, It passes through the grommet 52 attached to the opening 18a of the spacer plate 18 and the opening 16a of the rear substrate 16, and further passes through the opening 14a of the mounting plate 14 and the opening 12b of the end plate 12a of the front side frame 12, and Led inside. Accordingly, it is not necessary to form a hole in the boot 46 and pull out the harness 49 to ensure the waterproof property of the boot 46, and the harness 49 is guided to the inside of the front side frame 12 having a closed cross section. Can be protected from water and mud.

次に、上記構成を備えた本発明の第1の実施の形態の作用を説明する。   Next, the operation of the first embodiment of the present invention having the above configuration will be described.

通常時、圧壊強度可変装置13のロックピン27,27はブッシュ26の両端から突出しており、従ってロックピン27,27の先端の係合部27b,27bはヒンジ板22の受け部材51,51に係合している(図5および図6の実線参照)。この状態で車両が正面衝突してバンパービーム11に車体後方への衝突荷重が加わると、バンパービーム11およびフロントサイドフレーム12間に配置された圧壊強度可変装置13の前部基板35および後部基板16が前後方向に圧縮される。   Normally, the lock pins 27 and 27 of the variable crushing strength device 13 protrude from both ends of the bush 26, and therefore the engaging portions 27 b and 27 b at the tips of the lock pins 27 and 27 are formed on the receiving members 51 and 51 of the hinge plate 22. They are engaged (see solid lines in FIGS. 5 and 6). When the vehicle collides head-on in this state and a collision load to the rear of the vehicle body is applied to the bumper beam 11, the front board 35 and the rear board 16 of the crushing strength varying device 13 disposed between the bumper beam 11 and the front side frame 12. Is compressed in the front-rear direction.

このとき、図9に示すように、ヒンジ板22のロックピン支持部22a,22aはロックピン27,27によって左右方向への移動が規制されており、かつロックピン27,27は強固なブロック部材20によって後方への移動が規制されているため、重ね合わされた第1、第2座屈板24,25が前後方向に圧縮されて座屈することで、圧壊強度可変装置13は大きな衝突エネルギーを吸収することができる(高荷重モード)。   At this time, as shown in FIG. 9, the lock pin support portions 22a and 22a of the hinge plate 22 are restricted from moving in the left and right directions by the lock pins 27 and 27, and the lock pins 27 and 27 are strong block members. Since the rearward movement is restricted by 20, the overlapped first and second buckling plates 24 and 25 are compressed in the front-rear direction and buckled, so that the crushing strength varying device 13 absorbs a large collision energy. (High load mode).

一方、車両に搭載されたレーダー装置やテレビカメラで検知した外部状況と、車速センサで検知した車速とから、衝撃を小さくする必要がある衝突が予測されると、モータ29が作動してピニオン28およびラック27a,27aを介して一対のロックピン27,27をブッシュ26の内部に後退させることで、ロックピン27,27の係合部27b,27bをヒンジ板22の受け部材51,51から離脱させる(図5および図6の鎖線参照)。その結果、ヒンジ板22のロックピン支持部22a,22aは左右方向への移動が可能になり、図10に示すように、第1、第2座屈板24,25は座屈することなく折り畳まれ、圧壊強度可変装置13は小さな荷重で圧壊してバンパービーム11の後退を許容する(低荷重モード)。   On the other hand, when a collision that requires a reduction in impact is predicted from the external situation detected by a radar device or a TV camera mounted on the vehicle and the vehicle speed detected by the vehicle speed sensor, the motor 29 is activated and the pinion 28 is operated. Further, by retracting the pair of lock pins 27, 27 into the bush 26 via the racks 27a, 27a, the engaging portions 27b, 27b of the lock pins 27, 27 are detached from the receiving members 51, 51 of the hinge plate 22. (See the chain line in FIGS. 5 and 6). As a result, the lock pin support portions 22a and 22a of the hinge plate 22 can move in the left-right direction, and the first and second buckling plates 24 and 25 are folded without buckling as shown in FIG. The crushing strength varying device 13 crushes with a small load and allows the bumper beam 11 to retreat (low load mode).

上述した高荷重モードおよび低荷重モードの何れの場合にも、第1、第2倒れ防止板39,41は前後方向の圧縮荷重を受けて座屈するが、元々第1、第2倒れ防止板39,41は薄板で構成されており、かつ中央部に三角形のリブ39a,41aが形成されているため、前後方向の荷重を受けると極めて容易に座屈し、圧壊強度可変装置13の前後方向のエネルギー吸収特性に影響を及ぼすことはない。従って、圧壊強度可変装置13を低荷重で圧壊させたい低荷重モードにおいても、第1、第2倒れ防止板39,41によって圧壊強度可変装置13が圧壊し難くなる虞はない。尚、図9および図10において第1、第2倒れ防止板39,41は図示を省略している。   In both the high load mode and the low load mode described above, the first and second fall prevention plates 39 and 41 are buckled by receiving a compressive load in the front-rear direction, but originally the first and second fall prevention plates 39. , 41 are formed of thin plates, and triangular ribs 39a, 41a are formed at the center, so that they are buckled very easily when subjected to a load in the front-rear direction, and energy in the front-rear direction of the crushing strength varying device 13 Does not affect the absorption characteristics. Accordingly, even in the low load mode in which the crushing strength varying device 13 is desired to be crushed with a low load, there is no possibility that the crushing strength varying device 13 is not easily crushed by the first and second collapse prevention plates 39 and 41. 9 and 10, the first and second fall prevention plates 39 and 41 are not shown.

第1、第2倒れ防止板39,41が機能を発揮するのは、斜め衝突時によってバンパービーム11に車体前後方向に対して傾斜した衝突荷重が加わった場合である。斜め衝突時の衝突荷重は、バンパービーム11を車体後方に移動させる前後方向荷重と、バンパービーム11を車幅方向に移動させる左右方向荷重とに分解される。   The first and second fall prevention plates 39 and 41 perform their functions when a collision load inclined with respect to the longitudinal direction of the vehicle body is applied to the bumper beam 11 during an oblique collision. The collision load at the time of the oblique collision is decomposed into a front-rear direction load that moves the bumper beam 11 rearward of the vehicle body and a left-right direction load that moves the bumper beam 11 in the vehicle width direction.

図11(A)に模式的に示すように、左右方向荷重が圧壊強度可変装置13に入力すると、前部基板35および後部基板16間に剪断力が作用するため、右側の第1、第2座屈板24,25と左側の第1、第2座屈板24,25とが座屈することなく左右方向に倒れてしまい、高荷重モードであっても殆どエネルギー吸収性能を発揮できなくなる可能性がある。   As schematically shown in FIG. 11A, when a lateral load is input to the crushing strength varying device 13, a shearing force acts between the front substrate 35 and the rear substrate 16, and therefore the first and second on the right side. There is a possibility that the buckling plates 24 and 25 and the first and second buckling plates 24 and 25 on the left side will collapse in the left-right direction without buckling, and even in the high load mode, the energy absorbing performance cannot be exhibited. There is.

しかしながら、図11(B)に示すように、本実施の形態では、相対向する左右の第2座屈板25,25に挟まれた台形状の空間に合計4枚の第1、第2倒れ防止板39,41が配置されているため、これらの第1、第2倒れ防止板39,41が、左右の第1、第2座屈板24,25が図11(A)の状態に倒れるのを抑制し、圧壊強度可変装置13を前後方向に確実に圧壊してエネルギー吸収性能を効率的に発揮させることができる。   However, as shown in FIG. 11B, in the present embodiment, a total of four first and second collapses in a trapezoidal space sandwiched between the left and right second buckling plates 25, 25 facing each other. Since the prevention plates 39 and 41 are arranged, these first and second fall prevention plates 39 and 41 fall on the left and right first and second buckling plates 24 and 25 in the state shown in FIG. The crushing strength varying device 13 can be reliably crushed in the front-rear direction, and the energy absorption performance can be efficiently exhibited.

また第1、第2倒れ防止板39,41に三角形状のリブ39a,41a(図7参照)を形成したので、座屈が開始される荷重を低下させ、荷重変動の少ない特性を得ることができる。尚、第1、第2倒れ防止板39,41と第2座屈板25との間には僅かな隙間α(図2参照)が存在するが、第1、第2座屈板24,25が僅かに倒れると第2座屈板25が第1、第2倒れ防止板39,41に接触するので支障はない。   In addition, since the triangular ribs 39a and 41a (see FIG. 7) are formed on the first and second collapse prevention plates 39 and 41, the load at which buckling is started can be reduced, and a characteristic with little load fluctuation can be obtained. it can. A slight gap α (see FIG. 2) exists between the first and second collapse prevention plates 39 and 41 and the second buckling plate 25, but the first and second buckling plates 24 and 25 are present. Since the second buckling plate 25 comes into contact with the first and second fall prevention plates 39 and 41 when there is a slight fall, there is no problem.

ところで、圧壊強度可変装置13が大きな荷重で圧壊する高荷重モードでは、座屈する第1、第2座屈板24,25が、圧壊の開始から終了までの間、一定の高い荷重を発生することが望ましい。   By the way, in the high load mode in which the variable crushing strength device 13 is crushed with a large load, the first and second buckling plates 24 and 25 that buckle generate a constant high load from the start to the end of the crushing. Is desirable.

図12の時間(変位量)および荷重の関係を示すグラフから明らかなように、一般的な鉄材よりなる第1座屈板24は、変位量の増加に伴って荷重が急激に高まってピークに達した後に漸減する特性を有している。それに対して、形状記憶合金よりなる第2座屈板25は、変位量の増加に伴って荷重が急激に高まってピークに達した後に急激に減少してボトムに達し、そこから漸増する特性を有している。従って、第1座屈板24および第2座屈板25を単独で使用しても、圧壊の開始から終了まで一定の高い荷重を発生することは不可能である。しかしながら、先ず時刻t1に第2座屈板25が変形を開始して時刻t2にピークに達したときに、第1座屈板24の変形が開始するように設定すると、時刻t2から時刻t3を経て時刻t4に至る間の第2座屈板25の荷重の減少・増加特性と、第1座屈板24の荷重の増加・減少特性とが上下対称な特性となるため、それらを足し合わせた特性を実線で示す理想的な特性、つまり圧壊の開始から終了まで一定の高い荷重を発生する特性とすることができる。   As is apparent from the graph showing the relationship between time (displacement) and load in FIG. 12, the first buckling plate 24 made of a general iron material has a peak due to a sudden increase in load as the amount of displacement increases. It has a characteristic of gradually decreasing after reaching the limit. On the other hand, the second buckling plate 25 made of a shape memory alloy has a characteristic in which the load rapidly increases as the displacement increases, reaches a peak, rapidly decreases, reaches the bottom, and gradually increases from there. Have. Therefore, even if the first buckling plate 24 and the second buckling plate 25 are used alone, it is impossible to generate a constant high load from the start to the end of crushing. However, if the first buckling plate 24 is set to start deformation when the second buckling plate 25 starts deformation at time t1 and reaches a peak at time t2, the time t3 is changed from time t2 to time t3. After that, since the decrease / increase characteristic of the load of the second buckling plate 25 and the increase / decrease characteristic of the load of the first buckling plate 24 are symmetric in the vertical direction until time t4, they are added together. The characteristic can be an ideal characteristic indicated by a solid line, that is, a characteristic that generates a constant high load from the start to the end of crushing.

第1、第2座屈板24,25が変形を開始するタイミングの差は、次のようにして得ることができる。即ち、重ね合わされて固定爪24b…で一体化された第1、第2座屈板24,25の前後方向長さは、形状記憶合金製の第2座屈板25の方が鉄材製の第1座屈板24よりも僅かに長くなっているので、長い方の第2座屈板25が先に変形を開始し(時刻t1)、第2座屈板25が所定量圧縮された後に、短い方の第1座屈板24を第1座屈板25と共に変形させることができる(時刻t2)。   The difference in timing at which the first and second buckling plates 24 and 25 start to deform can be obtained as follows. That is, the length in the front-rear direction of the first and second buckling plates 24 and 25 that are overlapped and integrated by the fixing claws 24b is the same as that of the second buckling plate 25 made of shape memory alloy. Since it is slightly longer than one buckling plate 24, the longer second buckling plate 25 starts to deform first (time t1), and after the second buckling plate 25 is compressed by a predetermined amount, The shorter first buckling plate 24 can be deformed together with the first buckling plate 25 (time t2).

形状記憶合金製の第2座屈板25は鉄材に比べて加工が難しいため、単純な板形状としてコストを低減しているが、加工が容易な鉄材製の第1座屈板24の板厚を設定したり所定の形状のリブ24aを形成したりすることで、時刻t2以降に第2座屈板25が発生する荷重と上下対称な荷重を発生し得るように、第1座屈板24の荷重発生特性を調整することができる。   Since the second buckling plate 25 made of shape memory alloy is difficult to process compared to the iron material, the cost is reduced as a simple plate shape, but the thickness of the first buckling plate 24 made of iron material that is easy to process is reduced. Is set or a rib 24a having a predetermined shape is formed, so that a load symmetrical to the load generated by the second buckling plate 25 after time t2 can be generated. The load generation characteristics can be adjusted.

尚、実施の形態では第1座屈板24を鉄材製としているが、アルミニウム材等の他の材料を採用することができる。   In the embodiment, the first buckling plate 24 is made of iron, but other materials such as aluminum can be used.

ところで、図13に示すように、車両が正面衝突してバンパービーム11に後向きの荷重が作用すると、取付ブラケット42の脆弱なリブ42c…が圧壊することで、本体部11aに対して後方に傾斜していた傾斜部11bの角度が本体部11aと略平行になるように変形するため、バンパービーム11の左右方向の寸法がβだけ伸びることになる。このとき、仮にバンパービーム11と圧壊強度可変装置13とが左右方向に相対移動不能に結合されていると、バンパービーム11が左右方向に伸びたことで圧壊強度可変装置13が車体外側に倒れてしまい、衝突荷重を効果的に吸収できなくなる可能性がある。   By the way, as shown in FIG. 13, when the vehicle collides head-on and a rearward load is applied to the bumper beam 11, the fragile ribs 42c of the mounting bracket 42 are crushed and tilted backward with respect to the main body 11a. Since the angle of the inclined portion 11b is deformed so as to be substantially parallel to the main body portion 11a, the dimension in the left-right direction of the bumper beam 11 is extended by β. At this time, if the bumper beam 11 and the crushing strength varying device 13 are coupled so as not to move relative to each other in the left-right direction, the crushing strength varying device 13 falls to the outside of the vehicle body due to the bumper beam 11 extending in the left-right direction. Therefore, there is a possibility that the collision load cannot be absorbed effectively.

しかしながら、本実施の形態では、図8に示すように、バンパービーム11の傾斜部11bの後面に形成された第1ボルト孔11c…が左右方向に長い長孔とされているため、その第1ボルト孔11c…および取付ブラケット42の第2ボルト孔42d…を貫通するボルト43…に対して、バンパービーム11の傾斜部11bが車体外側にスライドすることができる。よって、正面衝突時にバンパービーム11が左右方向に伸びても圧壊強度可変装置13が車体外側に倒れるのを防止し、圧壊強度可変装置13の機能を確実に発揮させることができる。   However, in the present embodiment, as shown in FIG. 8, the first bolt holes 11 c formed on the rear surface of the inclined portion 11 b of the bumper beam 11 are elongated holes in the left-right direction. The inclined portion 11b of the bumper beam 11 can slide to the outside of the vehicle body with respect to the bolts 43 passing through the bolt holes 11c and the second bolt holes 42d of the mounting bracket 42. Therefore, even if the bumper beam 11 extends in the left-right direction at the time of a frontal collision, the crushing strength varying device 13 can be prevented from falling to the outside of the vehicle body, and the function of the crushing strength varying device 13 can be exhibited reliably.

更に、低荷重モードにおいて前後方向に変形し易くなるため、第1、第2倒れ防止板39,41の圧縮強度を低下させることなく目標の荷重設定が可能となる。従って、左右方向の横倒れ強度の低下を防止することができる。   Furthermore, since it becomes easy to deform in the front-rear direction in the low load mode, it is possible to set a target load without reducing the compressive strength of the first and second fall prevention plates 39 and 41. Accordingly, it is possible to prevent a decrease in the lateral collapse strength in the left-right direction.

次に、図14に基づいて本発明の第2の実施の形態を説明する。   Next, a second embodiment of the present invention will be described with reference to FIG.

第2座屈板25の変位量に対する荷重の特性は、図12で説明したもの以外に、その形状記憶合金の成分を変化させることで、種々に設定することができる。また鉄材製の第1座屈板14の変位量に対する荷重の特性も、その形状を変化させることで若干調整することができる。   The characteristics of the load with respect to the displacement amount of the second buckling plate 25 can be variously set by changing the components of the shape memory alloy other than those described with reference to FIG. Further, the load characteristic with respect to the displacement amount of the first buckling plate 14 made of iron can be slightly adjusted by changing its shape.

図12で説明した形状記憶合金製の第2座屈板25は、変位量の増加に伴って荷重が急激に高まってピークに達した後に急激に減少してボトムに達し、そこから漸増する特性を有している。一方、図14(A)に示す第2の実施の形態の第2座屈板25の特性は、変位量の増加に伴って荷重が急激に高まってピークに達してから僅かに減少した後、緩やかに増加する特性を有している。この場合には、第1の実施の形態とは逆に、鉄材製の第1座屈板24を形状記憶合金製の第2座屈板25よりも若干長く形成し、先ず時刻t1に第1座屈板24の圧縮を開始し、それに遅れて時刻t2に第2座屈板25の圧縮を開始することで、第1、第2座屈板24,25の荷重を足し合わせた特性(実線参照)を概ね一定の理想的な特性に近づけることができる。   The second buckling plate 25 made of shape memory alloy described in FIG. 12 has a characteristic in which the load rapidly increases and reaches a peak as the amount of displacement increases, then decreases rapidly, reaches the bottom, and gradually increases from there. have. On the other hand, the characteristics of the second buckling plate 25 of the second embodiment shown in FIG. 14 (A) are decreased slightly after the load rapidly increases and reaches a peak as the amount of displacement increases. It has a slowly increasing characteristic. In this case, contrary to the first embodiment, the first buckling plate 24 made of iron is formed slightly longer than the second buckling plate 25 made of shape memory alloy, and first the first buckling plate 24 at time t1. By starting the compression of the buckling plate 24 and starting the compression of the second buckling plate 25 at a time t2 later than that, the characteristics of adding the loads of the first and second buckling plates 24 and 25 (solid line) Can be approximated to a certain ideal characteristic.

また図14(B)に示す第3の実施の形態の第2座屈板25の特性は、変位量の増加に伴って荷重が急激に高まってから、増加率が減少して荷重が緩やかに増加する特性を有している。この場合には、鉄材製の第1座屈板24と形状記憶合金製の第2座屈板25とを同じ長さに形成し、時刻t1に第1座屈板24および第2座屈板25の圧縮を同時に開始することで、第1、第2座屈板24,25の荷重を足し合わせた特性(実線参照)を概ね一定の理想的な特性に近づけることができる。   In addition, the characteristic of the second buckling plate 25 of the third embodiment shown in FIG. 14B is that the load increases rapidly as the amount of displacement increases, and then the rate of increase decreases and the load becomes gentle. Has increasing properties. In this case, the first buckling plate 24 made of iron and the second buckling plate 25 made of shape memory alloy are formed to the same length, and the first buckling plate 24 and the second buckling plate are formed at time t1. By starting the compression of 25 at the same time, the characteristic (see solid line) obtained by adding the loads of the first and second buckling plates 24 and 25 can be brought close to a substantially constant ideal characteristic.

以上、本発明の実施の形態を説明したが、本発明はその要旨を逸脱しない範囲で種々の設計変更を行うことが可能である The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention .

第1の実施の形態に係る車両の車体前部の平面図The top view of the vehicle body front part of the vehicle which concerns on 1st Embodiment 図1の2部拡大図2 enlarged view of FIG. 圧壊強度可変装置の斜視図Perspective view of variable crushing strength device 圧壊強度可変装置の分解斜視図Exploded perspective view of variable crushing strength device 図2の5−5線断面図Sectional view along line 5-5 in FIG. 図5の6−6線断面図6-6 sectional view of FIG. 図2の7−7線断面図Sectional view along line 7-7 in FIG. 図2の8方向矢視図8 direction arrow view of FIG. 低荷重モードの作用説明図Action diagram of low load mode 高荷重モードの作用説明図Action diagram of high load mode 第1、第2倒れ防止板の作用説明図Action explanatory view of the first and second fall prevention plates 第1、第2座屈板の座屈時の作用説明図Action explanatory diagram at the time of buckling of the first and second buckling plates 衝突時のバンパービームの伸び変形の作用説明図Action explanatory diagram of bumper beam elongation deformation at the time of collision 第2の実施の形態に係る、前記図12に対応する図The figure corresponding to the said FIG. 12 based on 2nd Embodiment

11 バンパービーム
12 フロントサイドフレーム(車体フレーム)
13 圧壊強度可変装置
16 固定部材
16a 固定部材の開口
20 ブロック部材
22 ヒンジ板
22a ロックピン支持部
24 第1座屈板
24b 固定爪
25 第2座屈板
27 ロックピン
36 座屈板支持板
39 倒れ防止板
46 ブーツ
46a ブーツの開口
49 ハーネス
11 Bumper beam 12 Front side frame (body frame)
13 Crushing strength variable device
16 fixing members
16a fixing member opening
20 block members
22 hinge plate
22a Lock pin support portion 24 First buckling plate 24b Fixed claw 25 Second buckling plate
27 lock pin
36 buckling plate support plate
39 fall prevention plate
46 boots
46a boot opening
49 harness

Claims (4)

バンパービーム(11)とその後方に存する車体フレーム(12)との間に、車体前後方向の衝突荷重を受けて圧壊する圧壊強度が可変な圧壊強度可変装置(13)を配置した車両の車体強度調整装置において、
前記圧壊強度可変装置(13)は、前記車体フレーム(12)の前部に固定されるブロック部材(20)と、そのブロック部材(20)の左右両側にそれぞれ配置されて前記車体フレーム(12)の前部に連結される左右一対のヒンジ板(22)と、その両ヒンジ板(22)にそれぞれ設けたロックピン支持部(22a)に係脱可能として前記ブロック部材(20)に摺動可能に嵌合、支持される左右一対のロックピン(27)と、前記バンパービーム(11)に結合した座屈板支持板(36)の左右両端部と前記左右一対のヒンジ板(22)との間にそれぞれ介装されて、前記ロックピン(27)の前記ロックピン支持部(22a)への係合状態では前記衝突荷重により一体に座屈するように相互に重ね合わせられる左右各一対の第1座屈板(24)および第2座屈板(25)と、その左側の第1,第2座屈板(24,25)の重合体及び右側の第1,第2座屈板(24,25)の重合体間で左右から、また前記座屈板支持板(36)及び前記ブロック部材(20)間で前後からそれぞれ挟まれて左右の各第1,第2座屈板(24,25)の左右方向の倒れに対抗する薄板よりなる倒れ防止板(39)とを備え、
前記第2座屈板(25)は形状記憶合金で、また前記第1座屈板(24)は形状記憶合金以外の材料でそれぞれ構成されると共に、それら第1、第2座屈板(24,25)の車体前後方向の長さが異ならせて設定されることを特徴とする車両の車体強度調整装置。
A vehicle body strength of a vehicle in which a crushing strength varying device (13) is provided between the bumper beam (11) and a vehicle body frame (12) located behind the bumper beam (11), and the crushing strength variable device (13) is variable. In the adjustment device,
The crushing strength varying device (13) includes a block member (20) fixed to the front portion of the vehicle body frame (12) and the left and right sides of the block member (20). A pair of left and right hinge plates (22) connected to the front portion of the door and a lock pin support portion (22a) provided on each of the hinge plates (22) are slidable on the block member (20). A pair of left and right lock pins (27) fitted to and supported by, a left and right end portions of a buckling plate support plate (36) coupled to the bumper beam (11), and a pair of left and right hinge plates (22). A pair of left and right first pins that are interposed between each other so that the lock pins (27) are overlapped with each other so as to be buckled together by the collision load when engaged with the lock pin support portion (22a). Buckling (24) and a second seat屈板(25), first the left, the first polymer and the right side of the second seat屈板(24, 25), a second seat屈板of (24, 25) Left and right of each of the left and right first and second buckling plates (24, 25) sandwiched between the polymers from the left and right and between the buckling plate support plate (36) and the block member (20) from the front and the rear. With a fall prevention plate (39) made of a thin plate that resists the fall of the direction ,
Said second seat屈板(25) is a shape memory alloy and said first seat屈板(24) are each configured of a material other than a shape memory alloy Rutotomoni, they first, second seat屈板(24 25) The vehicle body strength adjusting device for a vehicle is characterized in that the length in the longitudinal direction of the vehicle body is set differently .
前記倒れ防止板(39)の車体前後方向の中間部には、左右方向に延びる横断面三角状のリブ(39a)が形成されることを特徴とする、請求項1に記載の車両の車体強度調整装置。 The vehicle body strength of the vehicle according to claim 1, characterized in that a rib (39a) having a triangular cross section extending in the left-right direction is formed in an intermediate portion of the vehicle body longitudinal direction of the fall prevention plate (39). Adjustment device. 前記第1座屈板(24)に形成した固定爪(24b)を折り曲げて前記第2座屈板(25)を一体に固定したことを特徴とする、請求項1または請求項2に記載の車両の車体強度調整装置。   The fixed buckle (24b) formed on the first buckling plate (24) is bent to fix the second buckling plate (25) integrally. Vehicle body strength adjustment device. 前記圧壊強度可変装置(13)を覆うブーツ(46)の開口(46a)を、前記圧壊強度可変装置(13)を車体フレーム(12)に固定する固定部材(16)にその外周を覆うように固定するとともに、前記圧壊強度可変装置(13)から延びるハーネス(49)を、前記固定部材(16)に形成した開口(16a)を通して前記車体フレーム(12)の内部に導いたことを特徴とする、請求項1〜3の何れかに記載の車両の車体強度調整装置。The opening (46a) of the boot (46) covering the crushing strength varying device (13) is covered with the fixing member (16) that fixes the crushing strength varying device (13) to the vehicle body frame (12). The harness (49) extending from the crushing strength varying device (13) is guided to the inside of the vehicle body frame (12) through an opening (16a) formed in the fixing member (16). The vehicle body strength adjusting device for a vehicle according to any one of claims 1 to 3.
JP2007025848A 2007-02-05 2007-02-05 Vehicle body strength adjusting device Expired - Fee Related JP4979400B2 (en)

Priority Applications (2)

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JP2007025848A JP4979400B2 (en) 2007-02-05 2007-02-05 Vehicle body strength adjusting device
US12/009,614 US7708323B2 (en) 2007-02-05 2008-01-21 Crushable body strength adjusting device for a vehicle

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CN104999980B (en) * 2015-08-14 2017-04-12 吉林大学 Sleeve type shape memory alloy car crash energy absorption box

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JP4305053B2 (en) * 2003-05-20 2009-07-29 株式会社カネカ Collision energy absorption device for vehicle bumper
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