WO2023166582A1 - クロスメンバ構造 - Google Patents
クロスメンバ構造 Download PDFInfo
- Publication number
- WO2023166582A1 WO2023166582A1 PCT/JP2022/008761 JP2022008761W WO2023166582A1 WO 2023166582 A1 WO2023166582 A1 WO 2023166582A1 JP 2022008761 W JP2022008761 W JP 2022008761W WO 2023166582 A1 WO2023166582 A1 WO 2023166582A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- plate member
- cross
- cross member
- vehicle
- plate
- Prior art date
Links
- 230000001154 acute effect Effects 0.000 claims abstract description 7
- 230000005540 biological transmission Effects 0.000 abstract description 4
- 229910000831 Steel Inorganic materials 0.000 description 8
- 239000010959 steel Substances 0.000 description 8
- 238000005452 bending Methods 0.000 description 7
- 238000004519 manufacturing process Methods 0.000 description 7
- 239000000463 material Substances 0.000 description 7
- 238000001816 cooling Methods 0.000 description 6
- 238000000034 method Methods 0.000 description 4
- 230000035939 shock Effects 0.000 description 4
- 238000003466 welding Methods 0.000 description 4
- 239000004743 Polypropylene Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000006261 foam material Substances 0.000 description 2
- 238000005304 joining Methods 0.000 description 2
- -1 polypropylene Polymers 0.000 description 2
- 229920001155 polypropylene Polymers 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- 238000007796 conventional method Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 230000000116 mitigating effect Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- 238000002834 transmittance Methods 0.000 description 1
Images
Classifications
-
- 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
- B60R19/04—Bumpers, i.e. impact receiving or absorbing members for protecting vehicles or fending off blows from other vehicles or objects formed from more than one section in a side-by-side arrangement
Definitions
- This case relates to the structure of the cross member attached to the front end of the side member of the vehicle.
- a vehicle body structure in which a cross member is provided at the front end of the side member of the vehicle.
- Crossmembers of this kind are called, for example, first crossmembers, or they are also called front end crossmembers or bumper beams.
- the first cross member has the function of transmitting the load at the time of collision to the side members, and also has the function of increasing the rigidity of the frame. Further, it has been proposed to improve the cushioning performance by attaching an energy absorbing member or a cushioning material to the front side of the first cross member (see Patent Document 1).
- the cross-sectional shape of the first cross member described in Patent Document 1 is a vertically long rectangular closed cross-sectional shape.
- the vertical dimension of the side member connected to the rear of the first cross member is often smaller than the vertical dimension of the first cross member. Therefore, there is a problem that it is difficult to improve the load transferability from the first cross member to the side members at the time of collision.
- the step between the first cross member and the side members becomes larger, which may reduce the load transmissibility.
- One of the purposes of this case was to provide a cross member structure that was invented in light of the above problems, and that can improve load transmission with a simple configuration.
- the disclosed cross-member structures can be implemented in the aspects or applications disclosed below to solve at least some of the problems set forth above.
- the disclosed cross member structure is a structure of a cross member attached to the front ends of a pair of side members extending in the longitudinal direction of a vehicle.
- a first cross member having a substantially trapezoidal closed cross-sectional structure with two obtuse angles is provided.
- FIG. 4 is a cross-sectional view of a first cross member to which the cross member structure is applied;
- FIG. 4 is a perspective view of a first cross member;
- A) is a top view of the first cross member,
- B) is its front view,
- C) is its left side view, and
- D is its rear view.
- FIG. 4 is a perspective view of a bracket attached to the first cross member;
- FIG. 4 is a side view of the first cross member;
- FIG. 1 is a cross-sectional view of a first cross member 4 to which a cross member structure as an embodiment is applied
- FIG. 2 is a perspective view of the first cross member 4.
- FIG. 3(A) is a top view of the first cross member
- FIG. 3(B) is its front view
- FIG. 3(C) is its left side view
- FIG. 3(D) is its rear view.
- 4 is a perspective view of the bracket 7 attached to the first cross member 4.
- FIG. FIG. 5 is a side view of the first cross member 4.
- the first cross member 4 is provided at the front end of the vehicle frame 1 and attached to the front ends of the side members 2 .
- the frame 1 referred to here includes, in addition to the first cross member 4, side members 2, a suspension cross member (not shown), a floor cross member, and the like.
- the side members 2 extend in the vehicle front-rear direction and are provided in a pair on the left and right with a space therebetween in the vehicle width direction.
- a first cross member 4 is positioned closest to the front of the vehicle among the cross members connecting the left and right side members 2 in the vehicle width direction.
- An end plate 3 having insertion holes for fasteners 8 is fixed to the front end of each side member 2 .
- the end plate 3 is a plate-like member fixed so as to close the front end of the side member 2 , and is formed in a rectangular shape slightly larger than the contour of the cross section of the side member 2 .
- the first cross member 4 is fastened and fixed to the side member 2 via the end plate 3 and fasteners 8 .
- the front side of the first cross member 4 may be equipped with an energy absorbing member or a cushioning material (for example, foamed PP material) (not shown).
- the first cross member 4 has a substantially trapezoidal closed cross-sectional structure.
- the orientation of the trapezoid is such that, as shown in Fig. 1, the upper base (the shorter of the two parallel sides) is located at the rear of the vehicle in the cross section when the first cross member 4 is divided in the vehicle width direction. and the lower bottom (longer of the two parallel sides) is oriented in front of the vehicle.
- each of the upper base and the lower base is substantially vertical (the direction of the normal is substantially horizontal).
- the first cross member 4 is formed by combining a first plate member 5 and a second plate member 6 .
- the first plate member 5 is a member arranged on the front side of the first cross member 4 .
- the first plate member 5 has a substantially L-shaped cross section.
- the second plate member 6 is a member arranged on the rear side of the first cross member 4 and is joined to the rear side of the first plate member 5 .
- the second plate member 6 has a substantially U-shaped cross section.
- Each of the first plate member 5 and the second plate member 6 is manufactured, for example, by pressing (bending) a steel plate.
- the second plate member 6 is made of a steel plate having a thickness greater than that of the first plate member 5 .
- the first plate member 5 is provided with a front surface 11 and a first upper surface 12 .
- the front surface 11 is a planar portion whose normal line (the normal line extending toward the outside of the first cross member 4 in the cross section shown in FIG. 1) faces the front of the vehicle.
- the first upper surface 12 is a surface connected to the upper edge of the front surface 11, and is a planar portion whose normal line is slightly inclined toward the rear of the vehicle from the vertical upward direction, forming a downward slope toward the rear of the vehicle. is.
- the angle A between the front surface 11 and the first upper surface 12 is formed to be an acute angle (an angle of less than 90 degrees).
- the dimension F of the first upper surface 12 in the longitudinal direction of the vehicle is set to be shorter than the dimension E of the first cross member 4 in the longitudinal direction of the vehicle.
- dimension F is set to be less than half the dimension E (ie F ⁇ E/2).
- the first cross member 4 is deformed stepwise by an external force from the front surface 11 toward the rear of the vehicle. That is, upon receiving an external force, the first plate member 5 is first deformed so as to be compressed in the longitudinal direction of the vehicle, and then the second plate member 6 is compressed in the longitudinal direction of the vehicle, and the external force is transferred to the side member 2 side. and communicate. As a result, the external force input to the front surface 11 is easily transmitted to the side members 2, thereby improving the load transmittance.
- the second plate member 6 is provided with a second upper surface 17 , a rear surface 18 and a lower surface 19 .
- the second upper surface 17 is a planar portion whose normal is slightly inclined toward the rear of the vehicle from the vertically upward direction, forming a downward slope toward the rear of the vehicle.
- the second upper surface 17 is arranged parallel to the first upper surface 12 .
- the first upper surface 12 and the second upper surface 17 are overlapped and joined. Examples of joining methods include lap welding and spot welding.
- the rear surface 18 is a surface connected to the rear edge of the second upper surface 17, and is a planar portion whose normal faces the rear of the vehicle.
- the angle C formed between the second upper surface 17 and the rear surface 18 is an obtuse angle (an angle exceeding 90 degrees).
- the sum of angles A and C is approximately 180 degrees.
- the lower surface 19 is a surface connected to the lower end side of the rear surface 18, and is a planar portion whose normal line is slightly inclined toward the rear of the vehicle from the vertical downward direction, forming a downward slope toward the front of the vehicle. .
- the angle D formed by the rear surface 18 and the lower surface 19 is an obtuse angle (an angle exceeding 90 degrees).
- the lower surface 19 is abutted and joined to the back side of the front surface 11 . Examples of joining methods include butt welding and fillet welding.
- An angle B formed between the lower surface 19 and the front surface 11 is formed to be an acute angle (an angle of less than 90 degrees). The sum of angles B and D is approximately 180 degrees.
- the contact point of the lower surface 19 with respect to the front surface 11 is set above the lower end 15 of the front surface 11 .
- the lower end 15 of the front surface 11 protrudes below the abutting position with the lower surface 19 .
- the dimension J of the first plate member 5 in the vehicle width direction is set larger than the dimension K of the second plate member 6 in the vehicle width direction.
- the first plate member 5 is formed in a shape that protrudes outward in the vehicle width direction (left and right outer sides) from the second plate member 6 . As a result, the pressure-receiving area of the front surface 11 at the time of collision is increased, and the cushioning performance of the vehicle can be improved.
- the lower end 15 of the front surface 11 is formed to have an uneven shape when viewed from the front.
- the pressure-receiving area of the front surface 11 is further increased, and the shock absorbing performance of the vehicle can be further improved.
- the rear end 16 of the first upper surface 12 is formed to have an uneven shape when viewed from above, corresponding to the uneven shape of the lower end 15 . be done.
- the uneven shapes of the adjacent first plate members 5 are arranged so as to correspond to each other. Waste can be reduced and yield can be improved.
- a front opening 13 is provided near the center of the front surface 11 in the vehicle width direction, as shown in FIG. 3(B).
- a rear surface opening 20 is provided near the center of the rear surface 18 in the vehicle width direction, as shown in FIG. 3(D).
- the front surface 11 has a concave portion 14 formed in a shape in which the central portion in the vertical direction is concaved toward the rear of the vehicle.
- the depth of the recess 14 is irrelevant.
- the dimension G corresponding to the depth of the recess 14 is set smaller than the dimension F.
- the concave portion 14 is formed over substantially the entire width from the left end to the right end of the front surface 11 except for the front opening portion 13 .
- a bracket 7 is fixed to the lower portion of the first cross member 4 for attaching the skid plate 26 to the vehicle.
- a pair of brackets 7 are provided on the left and right with an interval in the vehicle width direction. The position of the bracket 7 in the vehicle width direction is set at a position that avoids the side member 2 when viewed from above. In the examples shown in FIGS. 3A and 3D, etc., the bracket 7 is positioned inside the pair of side members 2 .
- the bracket 7 of this embodiment functions to prevent deformation such that the angle D increases due to an external force at the time of collision. It is attached to the mountain fold portion where the lower surface 19 is connected).
- the bracket 7 is shaped to sandwich the rear surface 18 and the lower surface 19 from the outside.
- the bracket 7 illustrated in FIG. 4 is provided with a pair of wall portions 21 and a bottom portion 23 connecting them.
- the wall portion 21 is a planar portion arranged perpendicular to the rear surface 18 and the lower surface 19 .
- the wall portion 21 is provided with a fitting portion 22 having a recessed shape so as to fit into the corner portion formed by the rear surface 18 and the lower surface 19 .
- the bracket 7 is fixed to the first cross member 4 in a state in which the fitting portion 22 is fitted to the mountain fold portion connecting the rear surface 18 and the lower surface 19 of the second plate member 6. be.
- the bottom portion 23 is a planar portion that is arranged substantially horizontally when the bracket 7 is attached to the first cross member 4 , and is connected to the lower edges of the pair of wall portions 21 .
- a mounting hole 24 for mounting a skid plate 26 is drilled in the bottom portion 23 .
- the first cross member 4 has a substantially trapezoidal closed shape with two acute angles A and B on the front side and obtuse angles C and D on the rear side. It has a cross-sectional structure. With such a configuration, compared to the case where the first cross member 4 has a rectangular closed cross section, it is possible to reduce the vertical step at the connecting portion of the first cross member 4 and the side members 2 .
- the distance between the upper end of the rear end of the first cross member 4 and the upper end of the front end of the side member 2 can be shortened.
- the distance between the lower end of the rear end of the first cross member 4 and the lower end of the front end of the side member 2 can also be shortened.
- the load transmitted from the first cross member 4 to the side members 2 can flow smoothly. Therefore, the load transferability from the first cross member 4 to the side members 2 can be improved with a simple configuration.
- the vertical dimension of the front surface 11 of the first cross member 4 can be increased compared to when the first cross member 4 has a rectangular closed cross section.
- the pressure receiving area for the collision load can be increased, and the cushioning performance of the vehicle can be improved.
- the upper surface (first upper surface 12, second upper surface 17) of the first cross member 4 can be sloped downward toward the rear of the vehicle, thereby providing the first cross member 4 that is less likely to impede the flow of cooling air. That is, the flow of cooling air passing near the first cross member 4 can be naturally guided obliquely downward toward the rear of the vehicle as shown in FIG. Therefore, the cooling air flows smoothly to the radiator 25 arranged behind the first cross member 4, and the cooling performance of the radiator 25 can be improved.
- the first cross member 4 includes a first plate member 5 arranged on the front side and having a substantially L-shaped cross section, and a second plate member 5 joined to the rear side of the first plate member 5 and having a substantially U-shaped cross section. and a plate member 6 .
- the first plate member 5 is substantially L-shaped, it can be manufactured by bending a single steel plate only once, which saves labor, cost, time, etc. for manufacturing.
- the second plate member 6 has two bent portions, both bending angles are obtuse angles, so it is possible to manufacture the second plate member 6 by bending once. That is, by simultaneously bending the second upper surface 17 and the lower surface 19 at right angles with the rear surface 18 as a reference, the angles C and D become slightly larger than 90 degrees due to springback. Therefore, the second plate member 6 having the shape shown in FIG. 1 can be obtained by one bending process, and the labor, cost, time, etc. of manufacturing can be saved.
- the abutting portion between the lower surface 19 of the second plate member 6 and the front surface 11 of the first plate member 5. is difficult to come off the bonded state. That is, even if the first plate member 5 is deformed so as to be compressed in the vehicle front-rear direction, the irregular quadrilateral closed cross-sectional structure is easily maintained. Therefore, it is possible to suppress a decrease in rigidity of the first cross member 4 and the frame 1 at the time of collision.
- the dimension F of the first upper surface 12 in the longitudinal direction of the vehicle can be set shorter than half the dimension E. With such a setting, buckling of the first upper surface 12 can be prevented, and the shape stability of the first cross member 4 can be improved.
- the lower end 15 of the front surface 11 of the first plate member 5 is formed to have an uneven shape when viewed from the front.
- the pressure receiving area of the front surface 11 can be increased at the time of collision, and the shock absorbing performance of the vehicle can be improved.
- the rear end 16 of the first upper surface 12 may be formed to have an uneven shape when viewed from above, corresponding to the uneven shape of the lower end 15 .
- the first plate member 5 is formed in a shape that protrudes further outward in the vehicle width direction than the second plate member 6 does.
- the second plate member 6 can be made of a thicker steel plate than the first plate member 5 .
- the first plate member 5 is first deformed so as to be compressed in the longitudinal direction of the vehicle.
- the second plate member 6 is compressed in the longitudinal direction of the vehicle and transmits the external force to the side member 2 side.
- the stress transmission efficiency to the side member 2 can be improved.
- the front surface 11 of the first plate member 5 is provided with a recess 14 formed by recessing the center portion of the front surface 11 in the vertical direction toward the rear of the vehicle.
- the rigidity of the front surface 11 can be increased, and the shape stability of the first cross member 4 can be improved.
- a cushioning material having a rectangular cross section polypropylene foam material or the like
- the cushioning material can be inserted into the recess 14 at the time of collision to secure a deformation allowance. Therefore, the cushioning performance of the vehicle can be improved.
- the first cross member 4 includes a bracket 7 having a pair of walls 21 formed thereon.
- This bracket 7 is attached to the corner portion formed by the lower surface 19 and the rear surface 18 of the second plate member 6 .
- the wall portion 21 is arranged perpendicular to the lower surface 19 and the rear surface 18 of the second plate member 6 .
- first cross member 4 having the first plate member 5 and the second plate member 6 is illustrated, but a single first cross member 4 is formed by bending a single steel plate multiple times. good too. At least, by forming a substantially trapezoidal closed cross-sectional structure in which two corners located on the front side are formed at acute angles and two corners located on the rear side are formed at obtuse angles, the same effect as the above embodiment can be obtained. will play.
- This case can be used in the manufacturing industry of cross members attached to vehicles. It can also be used in the manufacturing industry for vehicles with frames that include cross members.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Body Structure For Vehicles (AREA)
Abstract
Description
開示のクロスメンバ構造は、車両前後方向に延在する一対のサイドメンバの前端に取り付けられるクロスメンバの構造であって、前側に位置する二つの角が鋭角に形成されるとともに後側に位置する二つの角が鈍角に形成された略台形型の閉断面構造を持つファーストクロスメンバを備える。
図1は、実施例としてのクロスメンバ構造が適用されたファーストクロスメンバ4の断面図であり、図2は、ファーストクロスメンバ4の斜視図である。図3(A)はファーストクロスメンバの上面図、図3(B)はその正面図、図3(C)はその左側面図、図3(D)はその後面図である。図4は、ファーストクロスメンバ4に取り付けられるブラケット7の斜視図である。図5は、ファーストクロスメンバ4の側面図である。
(1)上記のファーストクロスメンバ4は、前側に位置する二つの角A,Bが鋭角に形成されるとともに後側に位置する二つの角C,Dが鈍角に形成された略台形型の閉断面構造となっている。このような構成により、ファーストクロスメンバ4を矩形閉断面にした場合と比較して、ファーストクロスメンバ4及びサイドメンバ2の接続箇所における上下方向の段差を減少させることができる。
さらに、ファーストクロスメンバ4の上面(第一上面12,第二上面17)を車両後方に向かう下り勾配にすることができ、冷却風の流れを阻害しにくいファーストクロスメンバ4を提供できる。すなわち、ファーストクロスメンバ4の近傍を通過する冷却風の流れを、図5に示すように車両後方に向かって斜め下方向へと自然に誘導することができる。したがって、ファーストクロスメンバ4の後方に配置されるラジエータ25への冷却風の流れがスムーズになり、ラジエータ25の冷却性能を向上させることができる。
上記の実施例はあくまでも例示に過ぎず、本実施例で明示しない種々の変形や技術の適用を排除する意図はない。本実施例の各構成は、それらの趣旨を逸脱しない範囲で種々変形して実施できる。また、本実施例の各構成は、必要に応じて取捨選択でき、あるいは、適宜組み合わせることができる。
2 サイドメンバ
3 エンドプレート
4 ファーストクロスメンバ
5 第一板部材
6 第二板部材
7 ブラケット
8 締結具
11 前面
12 第一上面(上面)
13 前面開口部
14 凹部
15 下端
16 後端
17 第二上面(上面)
18 後面
19 下面
20 後面開口部
21 壁部
22 嵌合部
23 底部
24 取付孔
25 ラジエータ
26 スキッドプレート
Claims (10)
- 車両前後方向に延在する一対のサイドメンバの前端に取り付けられるクロスメンバの構造であって、
前側に位置する二つの角が鋭角に形成されるとともに後側に位置する二つの角が鈍角に形成された略台形型の閉断面構造を持つファーストクロスメンバを備える
ことを特徴とする、クロスメンバ構造。 - 前記ファーストクロスメンバが、前側に配置され断面略L字型を有する第一板部材と、前記第一板部材の後側に接合され断面略コの字型を有する第二板部材とを有する
ことを特徴とする、請求項1記載のクロスメンバ構造。 - 前記第一板部材の上面と前記第二板部材の上面とが重ね合わされて接合されるとともに、前記第二板部材の下面が前記第一板部材の前面に突き当てられて接合される
ことを特徴とする、請求項2記載のクロスメンバ構造。 - 前記第一板部材の上面と前記第二板部材の上面との重ね合わせ位置が、前記ファーストクロスメンバにおける車両前後方向の中央よりも前方に位置する
ことを特徴とする、請求項3記載のクロスメンバ構造。 - 前記第一板部材の前面の下端が、前記第二板部材との突き当て位置よりも下方に突出している
ことを特徴とする、請求項3または4記載のクロスメンバ構造。 - 前記第一板部材の前面の下端が、正面視で凹凸形状になるように形成される
ことを特徴とする、請求項2~5のいずれか1項に記載のクロスメンバ構造。 - 前記第一板部材が、前記第二板部材よりも車幅方向の外側に突出した形状に形成される
ことを特徴とする、請求項2~6のいずれか1項に記載のクロスメンバ構造。 - 前記第二板部材が、前記第一板部材よりも厚い板厚を有する
ことを特徴とする、請求項2~7のいずれか1項に記載のクロスメンバ構造。 - 前記第一板部材の前面が、上下方向中央部を車両後方へ凹ませた形状に形成された凹部を有する
ことを特徴とする、請求項2~8のいずれか1項に記載のクロスメンバ構造。 - 前記第二板部材の後面と下面とのなす角部分に取り付けられ、前記下面及び前記後面に対して垂直な一対の壁部が形成されたブラケットを備える
ことを特徴とする、請求項2~9のいずれか1項に記載のクロスメンバ構造。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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AU2022444880A AU2022444880A1 (en) | 2022-03-02 | 2022-03-02 | Cross member structure |
PCT/JP2022/008761 WO2023166582A1 (ja) | 2022-03-02 | 2022-03-02 | クロスメンバ構造 |
JP2024504064A JPWO2023166582A1 (ja) | 2022-03-02 | 2022-03-02 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2022/008761 WO2023166582A1 (ja) | 2022-03-02 | 2022-03-02 | クロスメンバ構造 |
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WO2023166582A1 true WO2023166582A1 (ja) | 2023-09-07 |
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PCT/JP2022/008761 WO2023166582A1 (ja) | 2022-03-02 | 2022-03-02 | クロスメンバ構造 |
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Citations (5)
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US5080411A (en) * | 1991-04-15 | 1992-01-14 | Chrysler Corporation | Vehicle bumper structure |
US6412836B1 (en) * | 2000-10-11 | 2002-07-02 | Ford Global Technologies, Inc. | Bumper system for motor vehicles |
JP2010173596A (ja) * | 2009-02-02 | 2010-08-12 | Fuji Heavy Ind Ltd | 衝撃吸収部材及び車両用バンパ構造 |
US20170361793A1 (en) * | 2014-04-28 | 2017-12-21 | Shape Corp. | Multi-strip beam for a vehicle |
JP2018202897A (ja) * | 2017-05-30 | 2018-12-27 | 株式会社Subaru | バンパビーム構造 |
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2022
- 2022-03-02 WO PCT/JP2022/008761 patent/WO2023166582A1/ja active Application Filing
- 2022-03-02 JP JP2024504064A patent/JPWO2023166582A1/ja active Pending
- 2022-03-02 AU AU2022444880A patent/AU2022444880A1/en active Pending
Patent Citations (5)
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US5080411A (en) * | 1991-04-15 | 1992-01-14 | Chrysler Corporation | Vehicle bumper structure |
US6412836B1 (en) * | 2000-10-11 | 2002-07-02 | Ford Global Technologies, Inc. | Bumper system for motor vehicles |
JP2010173596A (ja) * | 2009-02-02 | 2010-08-12 | Fuji Heavy Ind Ltd | 衝撃吸収部材及び車両用バンパ構造 |
US20170361793A1 (en) * | 2014-04-28 | 2017-12-21 | Shape Corp. | Multi-strip beam for a vehicle |
JP2018202897A (ja) * | 2017-05-30 | 2018-12-27 | 株式会社Subaru | バンパビーム構造 |
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