WO2011126146A1 - Collision energy absorbing structure - Google Patents
Collision energy absorbing structure Download PDFInfo
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- WO2011126146A1 WO2011126146A1 PCT/JP2011/059223 JP2011059223W WO2011126146A1 WO 2011126146 A1 WO2011126146 A1 WO 2011126146A1 JP 2011059223 W JP2011059223 W JP 2011059223W WO 2011126146 A1 WO2011126146 A1 WO 2011126146A1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/12—Vibration-dampers; Shock-absorbers using plastic deformation of members
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D21/00—Understructures, i.e. chassis frame on which a vehicle body may be mounted
- B62D21/15—Understructures, i.e. chassis frame on which a vehicle body may be mounted having impact absorbing means, e.g. a frame designed to permanently or temporarily change shape or dimension upon impact with another body
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
- B60R19/00—Wheel guards; Radiator guards, e.g. grilles; Obstruction removers; Fittings damping bouncing force in collisions
- B60R19/02—Bumpers, i.e. impact receiving or absorbing members for protecting vehicles or fending off blows from other vehicles or objects
- B60R19/24—Arrangements for mounting bumpers on vehicles
- B60R19/26—Arrangements for mounting bumpers on vehicles comprising yieldable mounting means
- B60R19/34—Arrangements for mounting bumpers on vehicles comprising yieldable mounting means destroyed upon impact, e.g. one-shot type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/12—Vibration-dampers; Shock-absorbers using plastic deformation of members
- F16F7/121—Vibration-dampers; Shock-absorbers using plastic deformation of members the members having a cellular, e.g. honeycomb, structure
- F16F7/122—Vibration-dampers; Shock-absorbers using plastic deformation of members the members having a cellular, e.g. honeycomb, structure characterised by corrugations, e.g. of rolled corrugated material
Definitions
- the present invention relates to a collision energy absorbing structure used for automobiles and the like.
- a vehicle body such as an automobile is provided with a structure that deforms and absorbs collision energy in the event of a collision in order to mitigate a collision with an occupant or the vehicle body at the time of the collision.
- a collision energy absorbing structure As performance required for such a collision energy absorbing structure, from the viewpoint of reducing the weight of the vehicle body in consideration of recent environmental problems, it is required to increase the energy absorption efficiency and make the cross section compact or thin.
- Such a collision energy absorption structure is required to have high energy absorption efficiency, that is, the deformation resistance load is highly stable even after deformation starts and has high energy absorption ability. Since the collision energy absorbing structure cannot sufficiently absorb the collision energy when the deformation at the time of collision is unstable deformation as shown in FIG. 21 (a), as shown in FIG. 21 (b), large and small concentric circles are formed. It is made of a tubular structure and absorbs collision energy by plastic deformation while the small diameter tube is immersed in the large diameter tube with respect to the collision load in the axial direction (immersion type; for example, Patent Document 1), or FIG. As shown in (c), a structure in which the structure is plastically deformed in a bellows shape against an axial collision load (for example, Patent Documents 2 to 7) is required.
- Patent Document 2 is a polygonal cross section provided with a recess in the cross section of the structure, and Patent Document 3 has a radial intermediate beam connecting each corner portion from the center of the cross section.
- Patent Document 4 has an 8-shaped cross-sectional structure, and both increase the cross-sectional line length and the number of ridge lines to obtain a structure with good energy absorption efficiency.
- Patent document 5 improves collision absorption performance by providing a filler inside a structure.
- Patent Documents 6 and 7 are provided with concavities and convexities in the vertical direction with respect to the axial direction mainly subjected to the collision load, and are continuously buckled even when receiving an axial impact including an oblique load.
- the deformation shape is controlled so that the bellows-like plastic deformation shown in FIG.
- Patent Document 1 has a complicated structure, which causes an increase in the molding process and has problems in cost and productivity.
- Patent Documents 2 to 7 that are plastically deformed in a bellows shape have the following problems.
- Patent Document 2 is effective as a method for improving energy absorption efficiency while effectively utilizing a limited space, but greatly buckles when subjected to an axial impact including an oblique load, The deformation load may not be stable, and in such a case, energy absorption efficiency is reduced.
- the present invention has been made in view of the above points, the structure is not complicated, press working is possible, lightweight and compact, a stable deformed shape is obtained, and the resistance load in the deformation process It is an object of the present invention to provide a collision energy absorption structure that is highly stable and has high energy absorption efficiency.
- a collision energy absorbing structure that is cylindrical and deforms in the axial direction to absorb collision energy,
- the cross-sectional shape of the cross section perpendicular to the axial direction is a polygon that is point-symmetric and non-symmetric with respect to the center of the cross-section, and the aspect ratio when the outer shape of the cross-section is a square is less than 1.5.
- a collision energy absorbing structure characterized in that a ratio of lengths of adjacent sides among polygon sides constituting a cross section is 2.3 or less.
- the cross-sectional shape of the cross section perpendicular to the axial direction is point symmetric with respect to the center of the cross section and non-axisymmetric, and the aspect ratio is less than 1.5 when the outer shape of the cross section is rectangular.
- the ratio of the lengths of adjacent sides among the sides of the polygon forming the cross section is 2.3 or less, a stable deformed shape can be obtained. Therefore, a collision energy absorption structure having high energy absorption efficiency can be obtained by pressing without impairing productivity, and the structure can be made compact and lightweight.
- FIG. 1 shows a collision energy absorbing structure according to an embodiment of the present invention, in which (a) is a perspective view and (b) is a cross-sectional view.
- the collision energy absorbing structure is basically formed of a cylindrical body, and one end (for example, the upper end) is a collision tip, and collides with the collision tip. When an object collides, it is deformed in the direction of the axis L to absorb collision energy.
- the shape of the cross section perpendicular to the direction of the axis L is a polygon that is point-symmetric and non-axisymmetric with respect to the center O of the cross section.
- the figure shows a case where the cross-sectional shape is a hexagon including a recess.
- the shape of the cross section perpendicular to the axis L into a polygon like this, it can be produced by press working and the cross section line length can be made long, so that the collision performance is improved in a limited space. be able to.
- the load at the time of collision is not limited to being input in the axial direction, for example, and it is assumed that an oblique load having an angle with respect to the axial direction is received.
- the deformation of the member becomes unstable due to large buckling or local bending, the deformation load is reduced and the energy absorption ability is remarkably reduced, but the cross section perpendicular to the axis L of the cylindrical body
- point buckling and non-linear symmetric cause deviation in the progress of buckling on opposite sides, and it is difficult for large deformations such as buckling, lying down, and folding with a large period to occur.
- the quadrilateral R forming the polygonal outline constituting the cross section has an aspect ratio of less than 1.5.
- the aspect ratio is a value of long side / short side (a / b in the example in the figure).
- the aspect ratio is 1, and the aspect ratio is always 1 or more.
- the ratio of the lengths of adjacent sides among the sides of the polygon constituting the cross section is 2.3 or less.
- the ratio of the lengths of adjacent sides is the value of the longer side / shorter side.
- the ratio of the lengths of the adjacent sides is 1, and the ratio of the lengths of the adjacent sides is always 1 or more.
- the combination having the maximum ratio of the lengths of adjacent sides is a combination of the side L1 and the side L2 (L1> L2), and L1 / L2 ⁇ 2.3.
- the ratio of the lengths of adjacent sides among the sides of the polygon constituting the cross section is 2.3 or less is that the deformation form is stabilized thereby. This is probably because large deformation is likely to occur in the longer side of the adjacent sides, and in order to suppress such large deformation, the side of the shorter side of the adjacent sides This is probably because the length is important and there is an optimal ratio between these adjacent sides.
- the collision energy absorbing structure is tapered in the axial direction as shown in FIG.
- the taper in this case is preferably formed so as to spread from the front end (collision front end) to the rear end, as shown in the figure. This is considered to be because it is possible to specify the part where the deformation starts by attaching a taper, and the deformation starts stably.
- a part where deformation starts similarly by forming a notched shape N such as a notch at the tip (collision tip), and stably start the deformation. be able to.
- the collision energy absorbing structure of the present embodiment is preferably configured by press-molding a metal plate.
- the metal plate to be applied include a hot-rolled steel plate, a cold-rolled steel plate, a plated steel plate obtained by subjecting a steel plate to electroplating such as electrogalvanizing or hot-dip galvanizing, and a stainless steel plate (SUS).
- a hot dip galvanized steel sheet an alloying treatment may be performed.
- the plated steel sheet may be further subjected to an organic film treatment after plating.
- a steel plate having a tensile strength of 270 to 1500 MPa is preferable.
- other metal materials such as aluminum, magnesium, and these alloys other than a steel plate, can also be used.
- one metal plate shown in (a) is formed as shown in (b) using a die and a die made of a punch, and this is made into a closed cross-section by bending, and the end portions are aligned. Are joined to obtain the structure shown in (c).
- the die (die and punch) used for press molding is the above-mentioned cross-sectional shape (a point-symmetrical and non-axisymmetric polygon with respect to the center of the cross-section, and the aspect ratio when the outer shape of the cross-section is a rectangle) Is less than 1.5, and the ratio of the lengths of adjacent sides among the sides of the polygon forming the cross section is 2.3 or less).
- FIGS. 4 and 5 the case where a structure is manufactured by manufacturing and bonding a molded part having a predetermined cross-sectional shape from one or two metal plates has been described. However, three or more metal plates are used. It is also possible to form the respective parts by using and to manufacture the structure by joining them. As methods for joining the end faces, various methods such as spot welding, laser welding, arc welding, caulking, rivet joining, and application of an adhesive can be employed.
- the characteristics of the collision energy absorption structure of various shapes were grasped by simulation.
- general-purpose dynamic explicit software LS-DYNA ver. 971 was used for the simulation.
- the applied material was a steel plate having a tensile strength of 440 MPa and a plate thickness of 1.6 mm.
- a flat indenter without curvature was caused to collide at a speed of 15 km / h. The crushing performance of time was simulated.
- Examples 1 to 7 of the present invention which are within the scope of the present invention, are plastically deformed continuously and stably in a bellows shape during crushing, and the average load per unit weight during crushing is It was confirmed that the absorption energy efficiency was high and high.
- Comparative Examples 1 to 8 outside the scope of the present invention it was confirmed that bending in the axial direction and buckling with a large period occurred, the deformed shape was unstable, and the average load per unit weight was low. It was done.
- the cross-sectional shape of the cross section perpendicular to the axial direction is a point-symmetrical and non-axisymmetric polygon with respect to the center of the cross-section as in the present invention, and the outline of the cross-section is a rectangle
- the aspect ratio is less than 1.5 and the ratio of the lengths of adjacent sides among the polygon sides constituting the cross section is 2.3 or less, a stable deformed shape can be obtained, and the resistance load It has been confirmed that a collision energy absorption structure with high energy absorption efficiency and high energy absorption efficiency can be obtained.
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Abstract
Description
(1)筒状をなし、軸方向に変形して衝突エネルギーを吸収する衝突エネルギー吸収構造体であって、
軸方向に垂直な断面の断面形状が、断面の中心に対して点対称で、かつ非線対称の多角形であって、その断面の外郭を四角形としたときのアスペクト比が1.5未満であり、かつ断面を構成する多角形の辺のうち隣接する辺の長さの比が2.3以下であることを特徴とする衝突エネルギー吸収構造体。
(2)軸方向にテーパー状をなしていることを特徴とする(1)に記載の衝突エネルギー吸収構造体。
(3)先端部に、軸方向に凹む凹み部を有することを特徴とする(1)または(2)に記載の衝突エネルギー吸収構造体。
(4)金属板をプレスして成形されたプレス成形材から構成されることを特徴とする(1)から(3)のいずれかに記載の衝突エネルギー吸収構造体。
(5)少なくとも2つの前記プレス成形材を接合して構成されることを特徴とする(4)に記載の衝突エネルギー吸収構造体。
(6)前記プレス成形材を構成する前記金属板は、270~1500MPaの引張強度を有する鋼板であることを特徴とする(4)または(5)に記載の衝突エネルギー吸収構造体。 The above problems are solved by the following inventions (1) to (6).
(1) A collision energy absorbing structure that is cylindrical and deforms in the axial direction to absorb collision energy,
The cross-sectional shape of the cross section perpendicular to the axial direction is a polygon that is point-symmetric and non-symmetric with respect to the center of the cross-section, and the aspect ratio when the outer shape of the cross-section is a square is less than 1.5. A collision energy absorbing structure characterized in that a ratio of lengths of adjacent sides among polygon sides constituting a cross section is 2.3 or less.
(2) The collision energy absorbing structure according to (1), which is tapered in the axial direction.
(3) The collision energy absorbing structure according to (1) or (2), wherein the tip has a recess that is recessed in the axial direction.
(4) The collision energy absorbing structure according to any one of (1) to (3), wherein the collision energy absorbing structure is formed of a press-molded material formed by pressing a metal plate.
(5) The collision energy absorbing structure according to (4), wherein at least two of the press-molded materials are joined.
(6) The collision energy absorbing structure according to (4) or (5), wherein the metal plate constituting the press-formed material is a steel plate having a tensile strength of 270 to 1500 MPa.
図1は、本発明の一実施形態に係る衝突エネルギー吸収構造体を示すものであり、(a)は斜視図であり、(b)は断面図である。 <Shape of structure>
FIG. 1 shows a collision energy absorbing structure according to an embodiment of the present invention, in which (a) is a perspective view and (b) is a cross-sectional view.
本実施形態の衝突エネルギー吸収構造体は、金属板をプレス成形して構成することが好ましい。適用される金属板としては、熱延鋼板、冷延鋼板、あるいは鋼板に電気亜鉛系めっきや溶融亜鉛系めっき等のめっきを施しためっき鋼板、さらにはステンレス鋼板(SUS)を挙げることができる。溶融亜鉛系めっき鋼板の場合には、合金化処理を施してもよい。また、めっき鋼板には、めっき後、さらに有機皮膜処理を施してもよい。鋼板としては270~1500MPaの引張強度を有するものが好ましい。また、金属板としては、鋼板の他、アルミニウム、マグネシウム、これらの合金等、他の金属材料を用いることもできる。 <Applicable materials for structures>
The collision energy absorbing structure of the present embodiment is preferably configured by press-molding a metal plate. Examples of the metal plate to be applied include a hot-rolled steel plate, a cold-rolled steel plate, a plated steel plate obtained by subjecting a steel plate to electroplating such as electrogalvanizing or hot-dip galvanizing, and a stainless steel plate (SUS). In the case of a hot dip galvanized steel sheet, an alloying treatment may be performed. The plated steel sheet may be further subjected to an organic film treatment after plating. A steel plate having a tensile strength of 270 to 1500 MPa is preferable. Moreover, as a metal plate, other metal materials, such as aluminum, magnesium, and these alloys other than a steel plate, can also be used.
次に、このような衝突エネルギー吸収構造体の製造方法の例について説明する。
ここでは、プレス成形により衝突エネルギー吸収体を製造する場合を示す。図4の例では、(a)に示すように2枚の金属板を準備し、これらをダイおよびパンチからなる金型を用いて(b)に示すように成形し、(c)に示すように、得られた成形品の端面同士を接合することで、(d)に示す構造体を得る。具体的には、図1の構造体を製造するために、2枚の金属板からプレス成形により同じ形状の成形品を製造し、これらを接合する。図5の例では、(a)に示す1枚の金属板を、ダイおよびパンチからなる金型を用いて(b)に示すように成形し、これを曲げ加工により閉断面化して端部同士を接合することによって(c)に示す構造体を得る。プレス成形に用いる金型(ダイおよびパンチ)は、上記断面形状(断面の中心に対して点対称で、かつ非線対称の多角形であって、その断面の外郭を四角形としたときのアスペクト比が1.5未満であり、かつ断面を構成する多角形の辺のうち隣接する辺の長さの比が2.3以下)を考慮して設計されている。 <Manufacturing method>
Next, an example of a manufacturing method of such a collision energy absorbing structure will be described.
Here, the case where a collision energy absorber is manufactured by press molding is shown. In the example of FIG. 4, two metal plates are prepared as shown in (a), and these are formed as shown in (b) using a die and die, as shown in (c). Further, by joining the end faces of the obtained molded product, the structure shown in (d) is obtained. Specifically, in order to manufacture the structure of FIG. 1, a molded product having the same shape is manufactured by press molding from two metal plates, and these are joined. In the example of FIG. 5, one metal plate shown in (a) is formed as shown in (b) using a die and a die made of a punch, and this is made into a closed cross-section by bending, and the end portions are aligned. Are joined to obtain the structure shown in (c). The die (die and punch) used for press molding is the above-mentioned cross-sectional shape (a point-symmetrical and non-axisymmetric polygon with respect to the center of the cross-section, and the aspect ratio when the outer shape of the cross-section is a rectangle) Is less than 1.5, and the ratio of the lengths of adjacent sides among the sides of the polygon forming the cross section is 2.3 or less).
シミュレーションには、汎用の動的陽解法ソフトLS−DYNA ver.971を用いた。適用材料は、引張強度が440MPa、板厚が1.6mmの鋼板とした。本発明の範囲内の形状を有する本発明例1~7の構造体、および本発明の範囲から外れる比較例1~8の構造体について、曲率のない平面状の圧子を時速15kmで衝突させた時の圧潰性能をシミュレーションした。圧潰性能は、変形開始後の変形抵抗荷重で評価するため、圧潰距離が20mmから70mmにおける荷重−ストローク曲線から平均荷重を求め、単位重量あたりの平均荷重および変形後の形状にて評価した。その結果を表1にまとめて示す。本発明例1~7の構造体の断面形状、衝突前後の形状、荷重−ストローク曲線を図6~12に示す。比較例1~8の構造体の断面形状、衝突前後の形状、荷重−ストローク曲線を図13~20に示す。表1において、変形形状の欄は、○が連続的に蛇腹状に変形したものであり、×が折れ曲がりや周期の大きな座屈が発生したものである。また、図6~20において、(a)が断面形状、(b)が衝突前後の形状、(c)が荷重−ストローク曲線である。これらに示すように、本発明の範囲内である本発明例1~7では、圧潰時に連続して安定して蛇腹状に塑性変形しており、また、圧潰時の単位重量あたりの平均荷重が高く、吸収エネルギー効率が高いことが確認された。一方、本発明の範囲から外れる比較例1~8では、軸方向に折れ曲がりや周期の大きな座屈が生じており、変形形状が不安定で、単位重量あたりの平均荷重が低位であることが確認された。 Here, the characteristics of the collision energy absorption structure of various shapes were grasped by simulation.
For the simulation, general-purpose dynamic explicit software LS-DYNA ver. 971 was used. The applied material was a steel plate having a tensile strength of 440 MPa and a plate thickness of 1.6 mm. For the structures of Invention Examples 1 to 7 having shapes within the scope of the present invention and the structures of Comparative Examples 1 to 8 that deviate from the scope of the present invention, a flat indenter without curvature was caused to collide at a speed of 15 km / h. The crushing performance of time was simulated. In order to evaluate the crushing performance by the deformation resistance load after the start of deformation, the average load was obtained from the load-stroke curve when the crushing distance was 20 mm to 70 mm, and the average load per unit weight and the shape after deformation were evaluated. The results are summarized in Table 1. 6 to 12 show cross-sectional shapes, shapes before and after the collision, and load-stroke curves of the structures of Examples 1 to 7 of the present invention. Cross-sectional shapes, shapes before and after the collision, and load-stroke curves of the structures of Comparative Examples 1 to 8 are shown in FIGS. In Table 1, in the column of deformed shape, ◯ is continuously deformed into a bellows shape, and X is bent or a buckling with a large period occurs. 6 to 20, (a) is a cross-sectional shape, (b) is a shape before and after the collision, and (c) is a load-stroke curve. As shown in these examples, Examples 1 to 7 of the present invention, which are within the scope of the present invention, are plastically deformed continuously and stably in a bellows shape during crushing, and the average load per unit weight during crushing is It was confirmed that the absorption energy efficiency was high and high. On the other hand, in Comparative Examples 1 to 8 outside the scope of the present invention, it was confirmed that bending in the axial direction and buckling with a large period occurred, the deformed shape was unstable, and the average load per unit weight was low. It was done.
Claims (6)
- 筒状をなし、軸方向に変形して衝突エネルギーを吸収する衝突エネルギー吸収構造体であって、
軸方向に垂直な断面の断面形状が、断面の中心に対して点対称で、かつ非線対称の多角形であって、その断面の外郭を四角形としたときのアスペクト比が1.5未満であり、かつ断面を構成する多角形の辺のうち隣接する辺の長さの比が2.3以下であることを特徴とする衝突エネルギー吸収構造体。 A collision energy absorbing structure that is cylindrical and deforms in the axial direction to absorb collision energy,
The cross-sectional shape of the cross section perpendicular to the axial direction is a polygon that is point-symmetric and non-symmetric with respect to the center of the cross-section, and the aspect ratio when the outer shape of the cross-section is a square is less than 1.5. A collision energy absorbing structure characterized in that a ratio of lengths of adjacent sides among polygon sides constituting a cross section is 2.3 or less. - 軸方向にテーパー状をなしていることを特徴とする請求項1に記載の衝突エネルギー吸収構造体。 2. The collision energy absorbing structure according to claim 1, wherein the structure is tapered in the axial direction.
- 先端部に、軸方向に凹む凹み部を有することを特徴とする請求項1または請求項2に記載の衝突エネルギー吸収構造体。 3. The collision energy absorbing structure according to claim 1 or 2, wherein the tip has a recess that is recessed in the axial direction.
- 金属板をプレスして成形されたプレス成形材から構成されることを特徴とする請求項1から請求項3のいずれか1項に記載の衝突エネルギー吸収構造体。 The collision energy absorbing structure according to any one of claims 1 to 3, wherein the collision energy absorbing structure is formed of a press-molded material formed by pressing a metal plate.
- 少なくとも2つの前記プレス成形材を接合して構成されることを特徴とする請求項4に記載の衝突エネルギー吸収構造体。 5. The collision energy absorbing structure according to claim 4, wherein at least two of the press molding materials are joined.
- 前記プレス成形材を構成する前記金属板は、270~1500MPaの引張強度を有する鋼板であることを特徴とする請求項4または請求項5に記載の衝突エネルギー吸収構造体。 6. The collision energy absorbing structure according to claim 4, wherein the metal plate constituting the press-formed material is a steel plate having a tensile strength of 270 to 1500 MPa.
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CN201180017895.4A CN102834641B (en) | 2010-04-08 | 2011-04-07 | Collision energy absorbing structure |
KR1020127026307A KR101427020B1 (en) | 2010-04-08 | 2011-04-07 | Collision energy absorbing structure |
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JP2010089202A JP4930620B2 (en) | 2010-04-08 | 2010-04-08 | Impact energy absorbing structure |
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WO2011126146A1 true WO2011126146A1 (en) | 2011-10-13 |
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PCT/JP2011/059223 WO2011126146A1 (en) | 2010-04-08 | 2011-04-07 | Collision energy absorbing structure |
Country Status (4)
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JP (1) | JP4930620B2 (en) |
KR (1) | KR101427020B1 (en) |
CN (1) | CN102834641B (en) |
WO (1) | WO2011126146A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014073084A1 (en) * | 2012-11-08 | 2014-05-15 | Jfeスチール株式会社 | Impact absorbing member |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6156514B2 (en) | 2013-11-27 | 2017-07-05 | 新日鐵住金株式会社 | Shock absorbing parts |
CN103982208A (en) * | 2014-05-19 | 2014-08-13 | 辽宁工程技术大学 | Mine inner and outer turnover resistive energy-absorption anti-impact device |
JP6044624B2 (en) * | 2014-12-17 | 2016-12-14 | マツダ株式会社 | Vehicle frame structure |
CN107606019B (en) * | 2017-08-09 | 2019-06-21 | 西北工业大学 | A kind of double overturning endergonic structures of the double-deck end seal with high efficiency buffer energy absorption characteristics |
JP7238867B2 (en) * | 2020-08-18 | 2023-03-14 | Jfeスチール株式会社 | Automobile collision energy absorbing part, method for manufacturing the automobile collision energy absorbing part |
US20230356680A1 (en) | 2020-10-20 | 2023-11-09 | Nippon Steel Corporation | Impact absorbing member |
CN114857193B (en) * | 2022-04-19 | 2023-04-14 | 福建工程学院 | Clamping groove type thin-walled tube energy absorption system easy to disassemble and assemble and capable of achieving three-dimensional self-locking |
Citations (3)
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JP2006123887A (en) * | 2004-09-28 | 2006-05-18 | Aisin Seiki Co Ltd | Shock absorbing implement for vehicle and shock absorbing structure for vehicle |
JP2006207725A (en) * | 2005-01-28 | 2006-08-10 | Sumitomo Metal Ind Ltd | Shock absorbing member |
JP2009096225A (en) * | 2007-10-12 | 2009-05-07 | Kobe Steel Ltd | Energy absorbing member |
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DE602004027144D1 (en) * | 2003-07-28 | 2010-06-24 | Sumitomo Metal Ind | IMPACT-ABSORBING LINK |
JP4280153B2 (en) * | 2003-11-28 | 2009-06-17 | キョーラク株式会社 | Shock absorber for vehicle |
JP4471904B2 (en) | 2005-08-01 | 2010-06-02 | 豊田鉄工株式会社 | Bumper beam for automobile |
JP5011516B2 (en) | 2007-07-20 | 2012-08-29 | キョーラク株式会社 | Shock absorber for vehicle |
JP5330674B2 (en) * | 2007-11-05 | 2013-10-30 | 豊田鉄工株式会社 | Crash box |
JP2009227037A (en) * | 2008-03-21 | 2009-10-08 | Toyota Motor Corp | Bumper structure of vehicle and energy absorbing body |
KR101010177B1 (en) * | 2008-05-14 | 2011-01-20 | 성준엽 | Energy absorber for a car |
-
2010
- 2010-04-08 JP JP2010089202A patent/JP4930620B2/en active Active
-
2011
- 2011-04-07 KR KR1020127026307A patent/KR101427020B1/en active IP Right Grant
- 2011-04-07 CN CN201180017895.4A patent/CN102834641B/en not_active Expired - Fee Related
- 2011-04-07 WO PCT/JP2011/059223 patent/WO2011126146A1/en active Application Filing
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2006123887A (en) * | 2004-09-28 | 2006-05-18 | Aisin Seiki Co Ltd | Shock absorbing implement for vehicle and shock absorbing structure for vehicle |
JP2006207725A (en) * | 2005-01-28 | 2006-08-10 | Sumitomo Metal Ind Ltd | Shock absorbing member |
JP2009096225A (en) * | 2007-10-12 | 2009-05-07 | Kobe Steel Ltd | Energy absorbing member |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014073084A1 (en) * | 2012-11-08 | 2014-05-15 | Jfeスチール株式会社 | Impact absorbing member |
Also Published As
Publication number | Publication date |
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CN102834641A (en) | 2012-12-19 |
KR101427020B1 (en) | 2014-08-05 |
KR20120135314A (en) | 2012-12-12 |
CN102834641B (en) | 2015-07-08 |
JP2011218935A (en) | 2011-11-04 |
JP4930620B2 (en) | 2012-05-16 |
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