Front body structure for vehicle
Abstract
This record has no abstract on file.
Term
Term ended
Expired 29 October 2021, 4.9 years ago.
- Priority and filed
- Granted
- Expired
- Today
17 claims: 2 independent, 15 dependent
- 1フロントコンパートメントの下側部で、該フロントコンパートメントの骨格メンバと、キャビンのフロア骨格メンバとに跨ってサブフレームを結合配置し、該サブフレームに車両ユニット部品を搭載支持した構造であって、前記サブフレームは、前後方向に延在した左右一対のサイドフレームと、該サブフレームの後側で前記左右のサイドフレームに車幅方向に連設したリヤフレームと、を備えていて、該サブフレームの後側部に、一方のサイドフレームの前端側から軸方向に作用する衝突荷重を、前記一方のサイドフレームに対して車幅方向内側に指向して前記リヤフレームを介して他方のサイドフレーム側に荷重伝達する第1経路と、前記一方のサイドフレームに対して車幅方向外側に指向して前記フロア骨格メンバに 車両後方かつ車幅方向外側へ押し出すように 荷重伝達する第2経路と、 で車幅方向に広がる荷重成分に変換する 2つの荷重伝達経路を構成したことを特徴とする車体前部構造。
- 2フロントコンパートメントの下側部で、該フロントコンパートメントの前後方向骨格メンバを構成する左右一対のサイドメンバの下面と、キャビンのフロア骨格メンバの下面とに跨ってサブフレームを結合配置し、該サブフレームに車両ユニット部品を搭載支持した構造であって、前記サブフレームは、前後方向に延在した左右一対のサイドフレームと、該サブフレームの後側部で左右一対のサイドフレームに車幅方向に連設したリヤフレームと、各サイドフレームの後端部で、リヤフレーム側に向けて延びる内側ブランチ部と、サイドフレームよりも車幅方向外側に張り出す外側ブランチ部と、に分岐した2股部と、を備え、前記各サイドフレームの前端部を前側マウント部を介してサイドメンバの下面に結合すると共に、前記各2股部の外側ブランチ部を後側マウント部を介してフロア骨格メンバの下面に結合して、前記2股部により、一方のサイドフレームの前端側から軸方向に作用する衝突荷重を、内側ブランチ部からリヤフレームを介して他方のサイドフレーム側に荷重伝達する第1経路と、外側ブランチ部を介してフロア骨格メンバに 車両後方かつ車幅方向外側へ押し出すように 荷重伝達する第2経路と、 で車幅方向に広がる荷重成分に変換する 2つの荷重伝達経路を構成したことを特徴とする車体前部構造。
- 3フロア骨格メンバを、サイドメンバの後端部からキャビンのフロア下面に廻り込んで前後方向に延在するエクステンションサイドメンバと、前記キャビンのフロア側部に前後方向に延在配置したサイドシルと、前記エクステンションサイドメンバの前端部とサイドシルの前端部とを結合したアウトリガーと、で構成したことを特徴とする請求項2に記載の車体前部構造。
- 4後側マウント部をサイドシルの前端部付近に結合したことを特徴とする請求項3に記載の車体前部構造。
- 5後側マウント部をアウトリガー付近に結合したことを特徴とする請求項3に記載の車体前部構造。
- 6後側マウント部をエクステンションサイドメンバの前端部付近に結合したことを特徴とする請求項3に記載の車体前部構造。
- 7サイドフレームを、その前端から2股部に向けて略直線状に形成したことを特徴とする請求項2~6の何れかに記載の車体前部構造。
- 8サイドフレームを、車幅方向内側に向けて弯曲して形成したことを特徴とする請求項2~6の何れかに記載の車体前部構造。
- 9サイドフレームは、最大弯曲部の車幅方向外側の側縁部に、衝突荷重に対して車幅方向内側への屈曲変形を促す脆弱部を設けたことを特徴とする請求項8に記載の車体前部構造。
- 10リヤフレームを略直線状に形成したことを特徴とする請求項2~9の何れかに記載の車体前部構造。
- 11リヤフレームの車幅方向中央部の前縁部に、衝突荷重に対して後方への屈曲変形を促す脆弱部を設けたことを特徴とする請求項2~10の何れかに記載の車体前部構造。
- 12リヤフレームを上方に向けて弯曲して形成したことを特徴とする請求項2~10の何れかに記載の車体前部構造。
- 132股部を、内側ブランチ部と外側ブランチ部とがサイドフレームから平面略Y字状に分岐するように形成したことを特徴とする請求項2~12の何れかに記載の車体前部構造。
- 142股部の後側の内側ブランチ部と外側ブランチ部との境界部に脆弱部を設けたことを特徴とする請求項2~12の何れかに記載の車体前部構造。
- 15左右のサイドフレームの後端部をそれぞれ車幅方向外側へ向けて弯曲して延設し、これらサイドフレームの弯曲基部間に跨ってリヤフレームを結合して、サイドフレームの後方延設部を外側ブランチ部とし、リヤフレームのサイドフレームとの結合基部を内側ブランチ部として2股部を形成したことを特徴とする請求項2~12の何れかに記載の車体前部構造。
- 162股部をサイドフレームと別体に形成し、該2股部をサイドフレームの後端部に接続固定すると共に、左右の2股部の内側ブランチ部間に、別体成形したリヤフレームを接続固定したことを特徴とする請求項2~14の何れかに記載の車体前部構造。
- 17サブフレームは、左右のサイドフレームの前端部を車幅方向に連設するフロントフレームを備えていることを特徴とする請求項1~15の何れかに記載の車体前部構造。
Independent claims17
84 paragraphs, as filed
[Technical field to which the invention belongs] The present invention relates to a vehicle body front structure of an automobile.
[0002] In general, a vehicle body front structure of an automobile absorbs collision energy by laterally crushing and deforming a side member which is a front-rear skeleton member of the front compartment when the vehicle collides in front. It is designed to.
[0003] However, due to the fact that the shape of the side member is not always straight and that a power unit such as a heavy engine or a drive motor is attached, the side member may be bent and deformed at the time of a collision.
[0004] Further, in an offset frontal collision, the collision input is concentrated on one side member, so that the collision energy may not be sufficiently absorbed. Therefore, as described in Japanese Patent Application Laid-Open No. 9-119322. In addition, a large subframe for suspending vehicle unit parts such as the power unit and suspension parts is formed separately, and the subframe is mounted on the side member from below, so that not only the side member but also the subframe is mounted in the event of a frontal collision. Is also known to be deformed at the same time to increase the amount of collision energy absorbed.
[0005] The subframe is formed by forming the left and right side frames and the cross members before and after connecting the left and right side frames on the front end side and the rear end side into a plane rectangle having substantially the same width as between the left and right side members. There are mounts provided at the four corners thereof, and the mounts are connected to the lower surfaces of the left and right side members via the mounts.
[0006] [Problems to be Solved by the Invention] Since the front and rear mounting portions of the subframe are set on the extension of the straight side frame in a plan view, from the front end side of the side frame at the time of a frontal collision. When a collision input acts in the axial direction, a load tends to act on the joint portion of the rear mount portion in the axial collision input line direction of the side frame.
[0007] In order to prevent the joint portion of the rear mount portion from moving backward due to the collision input and suppress the deformation of the cabin, the periphery of the joint portion of the rear mount portion is reinforced to increase the rigidity. At the same time, it is necessary to increase the rigidity of the front part of the cabin, which is undeniably disadvantageous in terms of weight and cost.
[0008] Therefore, the present invention can efficiently disperse and transmit the collision input at the time of frontal collision to the floor skeleton member of the cabin on the rear end side of the subframe, without adopting a sufficient reinforcing structure with a small weight increase. It provides a vehicle body front structure that can protect the cabin.
[Means for Solving the Problems] In the present invention, the subframe on which the unit parts of the vehicle are mounted and supported is the lower portion of the front compartment, and the skeleton member of the front compartment and the floor of the cabin. The subframe is connected and arranged across the skeleton members, and the subframe is connected to a pair of left and right side frames extending in the front-rear direction and the left and right side frames on the rear side of the subframe in the vehicle width direction. A rear frame is provided, and a collision load acting in the axial direction from the front end side of one side frame is directed inward in the vehicle width direction with respect to the one side frame on the rear side portion of the subframe. Then, the load is transmitted to the other side frame side via the rear frame, and the floor skeleton member is directed outward in the vehicle width direction with respect to the one side frame.<u style="single">Push it to the rear of the vehicle and outward in the width direction</u>The second path for load transmission and<u style="single">Converts to a load component that spreads in the vehicle width direction</u>The gist is that two load transmission paths are constructed.
[Effect of the Invention] According to the present invention, when the collision input is concentrated on one side frame of the subframe due to the offset frontal collision and the collision input acts in the axial direction from the front end side of one side frame, the collision input acts. This collision input is a load transmitted to the other side frame via the rear frame at the rear side of the one side frame, directed inward in the vehicle width direction with respect to the one side frame by the first path. It is dispersed into a component and a load component that is directed outward in the vehicle width direction with respect to the one side frame by the second path and is transmitted to the floor frame member.
[0011] As a result, the retreating load of the subframe does not immediately press the front part of the floor of the cabin, but is replaced with a load that spreads in the vehicle width direction and is efficiently dispersed and absorbed by the floor skeleton members of the cabin, and the cabin. Deformation can be suppressed.
[Embodiments of the Invention] Hereinafter, embodiments of the present invention will be described in detail together with drawings.
[0013] In FIG. 1, side members 1 which are skeletal members in the front-rear direction are arranged on both left and right sides of the front compartments F and C.
The pair of left and right side members 1.1 are connected by a bumper rain force 3 extending in the vehicle width direction at their front ends, while the rear ends of the side members 1 are front compartment F. The extension side member 2 extending in the front-rear direction is formed by wrapping around the lower surface of the floor 5 from the dash panel 4 that separates C and the cabin C and joining them.
Side sill 6 which is a skeleton member in the front-rear direction is arranged on both left and right sides of the floor 5, and the front end of the side sill 6 and the front end of the extension side member 2 are connected by an outrigger 7. is there.
[0016] Therefore, in the present embodiment, the extension side member 2, the side sill 6, and the outrigger 7 constitute the floor skeleton member 8 of the cabin C.
[0017] At the lower end of the front compartments F and C, a subframe 11 for mounting and supporting vehicle unit parts such as suspension parts (not shown) including a power unit 10 such as an engine and a drive motor is arranged. ..
As shown in FIGS. 2 and 4, the subframe 11 is connected to a pair of left and right side frames 12 extending in the front-rear direction and the left and right side frames 12 at the rear side of the subframe 11 in the vehicle width direction. It includes a rear frame 13 provided and a bifurcated portion 14 provided at the rear end of the side frame 12.
2 The crotch portion 14 is a rear end portion of the side frame 12, and has an inner branch portion 14a extending toward the rear frame 13 side and an outer branch portion 14b extending outward in the vehicle width direction from the side frame 12. It is branched and configured.
[0020] In the present embodiment, the outer branch portion 14b is formed so as to project obliquely backward from the inner branch portion 14a in a plan view.
[0021] Further, in the present embodiment, the left and right side frames 12 and the rear frame 13 are integrally formed. Therefore, the inner branch portion 14a of the two crotch portions 14 is the side frame 12 of the rear frame 13. Continuous installation<u style="single">Basic</u>Refers to the area around the club.
[0022] The side frame 12 and the rear frame 13 are formed by superimposing an upper panel 11a formed in an inverted hat-shaped cross section and a flat plate lower panel 11b and forming a closed cross section by welding or riveting or the like. In the example shown in (1), these upper panels 11a and lower panels 11b are bonded and fixed by rivets 15 at the overlapping portion.
[0023] Further, the subframe 12 of the present embodiment includes a separately molded front frame 16 that connects the front ends of the left and right side frames 12 in the vehicle width direction.
[0024] A front mount portion 17 and a rear mount portion 18 are formed at the front end of the side frame 12 and the protruding end of the outer branch portion 14b of the two crotch portions 14.
[0025] The side frame 12, the rear frame 13, and the front frame 16 are all formed in a substantially linear shape in a plan view.
[0026] The subframe 11 composed of the frames 12, 13, 16 and the two crotch portions 14 is the lower surface of the seat portion 19 projecting downward from the front end portion of the side member 1 via the front mount portion 17. While being connected to the floor skeleton by fastening members such as bolts and nuts, it is also connected to the lower surface of the floor skeleton member 8 via the rear mount portion 17, and is connected and arranged across the side members 1 and the floor skeleton member 8. It is done.
[0027] As a result, the collision load F acting axially from the front end portion of one side frame, for example, the right side frame 12R, is transmitted from the inner branch portion 14a to the other left side frame 12L side via the rear frame 13. It constitutes two load transmission paths, a first path A to be loaded and a second path B to transmit the load to the floor skeleton member 8 via the outer branch portion 14b.
[0028] In the present embodiment, as shown in FIG. 4, the rear mount portion 18 is coupled to the vicinity of the front end portion of the extension side member 2.
[0029] Further, the power unit 10 described above is mounted and supported across the left and right side frames 12, 12.
[0030] According to the structure of the first embodiment described above, when the right side of the front end of the vehicle collides with the obstacle M in an offset manner as shown in FIG. 4, the right side frame 12R of the subframe 11 collides in the axial direction from the front end side. Input F works intensively.
This collision input F is the bifurcated portion 14 at the rear end of the right side frame 12R, and the inner branch portion 14a along the first path A directed inward in the vehicle width direction with respect to the right side frame 12R. The load component Fa transmitted to the left side frame 12L via the rear frame 13 and the floor skeleton via the outer branch portion 14b along the second path B directed outward in the vehicle width direction with respect to the right side frame 12R. It is dispersed in the load component Fb transmitted to the member 8.
[0032] At the joint portion of the rear mount portion 18 in the second path B, the load component Fc in the front-rear direction remains as long as the front-rear rigidity of the subframe 11 exists, but as described above, the vehicle is formed at the two crotch portion 14. By generating the load components Fa and Fb in the width direction, the load component Fc in the front-rear direction can be made smaller than the front end input load F.
As a result, the retreating load of the subframe 11 does not immediately press the front portion of the floor 5 of the cabin C, but replaces the load so as to spread in the vehicle width direction and is efficient for the floor skeleton member 8 of the cabin C. It is dispersed and absorbed in the cabin C, and the deformation of the cabin C can be suppressed.
[0034] Here, the above-mentioned load method<u style="single">Mukai</u>Two patterns shown in (A) and (B) of Fig. 5 can be considered as the conversion action of.
[0035] FIG. 5 (A) shows a pattern in which the bifurcated portion 14 is deformed, and the angle θ formed by the inner branch portion 14a and the outer branch portion 14b expands due to the front-rear load transmitted from the right side frame 12R. By deforming in the direction, the rear frame 13 is compressed in the direction of the bifurcated portion 14 of the left side frame 12L on the opposite side, and the outer branch portion 14b pushes the rear mounting portion 18 to the rear of the vehicle and outward in the vehicle width direction. Acts on.
[0036] FIG. 5B is a pattern in which the right side frame 12R, the inner branch portion 14a, and the rear frame 13 connected thereto are deformed. The collision load input to the front end of the right side frame 12R deforms the right side frame 12R, the inner branch portion 14a, and the rear frame 13. Since the length of the outer branch portion 14b is shorter than that of the right side frame 12R and the rear frame 13, the two crotch portions 14 are indicated by the arrow a in the figure because they are not deformed or only slightly deformed with respect to the load. Rotate counterclockwise as indicated by. As a result, the rear frame 13 is compressed in the direction of the bifurcated portion 14 of the left side frame 12L on the opposite side, and as a reaction, the outer branch portion 14b makes the rear mount portion 18 behind the vehicle and outside in the vehicle width direction. Acts to push to.
[0037] In this way, the conversion load acting so as to push the rear mount portion 18 of the outer branch portion 14b to the rear of the vehicle and outward in the vehicle width direction by the bifurcated portion 14 of the right side frame 12R is the floor side portion. It is received by the assembly part of the most rigid extension side member 2, the outrigger 7, and the side sill 6, and is dispersed and absorbed by each of these skeleton members 2, 7, and 6.
[0038] On the other hand, since the rear frame 13 is formed to be substantially linear in a plan view, the load component Fa distributed inward in the vehicle width direction from the bifurcated portion 14 of the side frame 12R on the collision side. Can be efficiently transmitted to the bifurcated 14 side of the opposite side frame 12L.
[0039] Further, since the rear mount portion 18 of the outer branch portion 14b of the two crotch portions 14 is coupled to the vicinity of the front end portion of the extension side member 2, the load transmitted from the rear mount portion 18 is applied. Supported by the resistance of the extension side member 2 and the floor panel around it, the load can be distributed and transmitted well, and the amount of protrusion of the outer branch portion 14b from the side frame 12 can be reduced, so that the subframe 11 can be supported. Can be made smaller and lighter.
[0040] Further, in the present embodiment, since the subframe 11 includes a front frame 16 that connects the front ends of the left and right side frames 12 and 12 in the vehicle width direction, the frame rigidity is high and vehicle unit parts such as the power unit 10 are provided. In addition, since each frame including the side frame 12 is formed in a substantially linear shape in a plan view, the formability is good and the side frame 11 can be easily formed. it can.
FIG. 6 shows a second embodiment of the present invention. In the present embodiment, the rear frame 13 of the subframe 11 in the first embodiment is formed by bending upward. is there.
[0042] According to the structure of the second embodiment, in addition to the effect of the first embodiment, the load component Fa dispersed from the bifurcated portion 14 of one side frame 12R and directed to the first path A is provided. While being transmitted to the other side frame 12L side by the rear frame 13, the rear frame 13 can be plastically deformed in the bending direction by this load component Fa to absorb a part of the collision energy.
[0043] Further, since the rear frame 13 is curved upward, these parts are present in a vehicle having an exhaust pipe, a drive shaft, or the like extending from the inside of the front compartments F and C to the lower side of the floor 5. The layout that avoids interference with is easy.
FIG. 7 shows a third embodiment of the present invention. In the present embodiment, the rear side of the bifurcated portion 14 of the subframe 11 in the first embodiment, the inner branch portion 14a and the outer side. A notch 19 as a fragile portion is provided at the boundary with the branch portion 14b.
[0045] According to the structure of the third embodiment, in addition to the effect of the first embodiment, a notch 19 is provided at the boundary between the inner branch portion 14a and the outer branch portion 14b of the two crotch portions 14. Therefore, due to the collision load transmitted in the axial direction from the front end side of the side frame 12, the two crotch portions 14 are deformed so as to split the boundary between the inner branch portion 14a and the outer branch portion 14b starting from the notch 19. Therefore, the load conversion in the vehicle width direction to the first route A and the second route B can be promoted.
[0046] FIG. 8 shows a fourth embodiment of the present invention. In the present embodiment, the bifurcated portion 14 of the side frame 11 in the first embodiment is provided with the inner branch portion 14a and the outer branch portion 14b. Is formed so as to branch from the side frame 12 in a substantially Y-shaped plane.
[0047] According to the structure of the fourth embodiment, in addition to the effect of the first embodiment, the inner branch portion 14a and the outer branch portion 14b of the two crotch portions 14 are branched into a substantially Y-shape in a plane. Therefore, the load can be distributed substantially evenly in the load transmission paths of the first path A and the second path B, and the load transmission efficiency can be improved.
[0048] Further, as in the third embodiment, due to the axial load of the side frame 12, the inner branch portion 14a and the outer branch portion 14a and the outer branch portion start from the notch portion at the boundary between the inner branch portion 14a and the outer branch portion 14b. It can be deformed so that the boundary with 14b is torn, and the load conversion in the vehicle width direction to the first path A and the second path B can be promoted.
FIG. 9 shows a fifth embodiment of the present invention. In the present embodiment, the rear frame 13 of the subframe 11 in the first embodiment has a front edge portion at the center in the vehicle width direction. Is provided with a notch 21 as a fragile portion that promotes bending and deformation backward with respect to a collision load.
[0050] According to the structure of the fifth embodiment, in addition to the effect of the first embodiment, the load component Fa dispersed from the bifurcated portion 14 of one side frame 12R and directed to the first path A. While being transmitted to the other side frame 12L side by the rear frame 13, the rear frame 13 can be bent and deformed backward from the notch 21 by the load component Fa to absorb a part of the collision energy.
At this time, since the rear frame 13 is bent and deformed so that the front edge side having the notch 21 is compressed and the rear edge side is extended, the rear mount portion 18 is pushed outward in the vehicle width direction, and the floor. The reaction force generated by the skeleton member 8 can be effectively used for the bending deformation.
FIG. 10 shows a sixth embodiment of the present invention. In the present embodiment, the side frame 12 of the subframe 11 in the first embodiment is curved inward in the vehicle width direction. Is formed.
[0053] According to the structure of the sixth embodiment, in addition to the effect of the first embodiment, the side frame 12 transmits the collision load input to the front end side of the side frame 12 to the two crotch portions 14. Due to the curve, it bends and deforms inward in the vehicle width direction, and can absorb a part of the collision energy.
At this time, since the bending deformation of the side frame 12 propagates in the curved inward direction and interferes with the power unit 10, the resistance force generated from this interference can enhance the absorption effect of the collision energy.
FIG. 11 shows a seventh embodiment of the present invention. In the present embodiment, the vehicle of the side frame 12 curved inward in the vehicle width direction of the subframe 11 in the sixth embodiment. A notch 22 as a fragile portion that promotes bending and deformation inward in the vehicle width direction in response to a collision load is formed on the lateral edge portion on the outer side in the width direction, preferably on the lateral edge portion on the outer side in the vehicle width direction at a substantially maximum curve. is there.
Therefore, according to the structure of the seventh embodiment, in addition to the effect of the sixth embodiment, the side frame 12 is inside the vehicle width direction with respect to the collision load starting from the notch 22 of the maximum curved portion thereof. It is possible to promote the bending deformation to the surface, and to specify the interference point with the power unit 10 due to the bending deformation to further enhance the collision energy absorption effect.
[0057] FIGS. 12 and 13 show an eighth embodiment of the present invention. In the present embodiment, the fifth embodiment is attached to the front edge of the rear frame 13 of the subframe 11 in the seventh embodiment. A notch 21 is provided as a fragile portion similar to the embodiment.
FIG. 13 shows the deformation behavior of the subframe 12 of the present embodiment when an offset frontal collision occurs.
[0059] When the collision input F concentrates in the axial direction from the front end side of one side frame 12R, the side frame 12R starts from the notch 22 in the vehicle width direction while transmitting this collision load to the two crotch portions 14. The rear frame 13 is bent and deformed inward to obtain the same effect as that of the seventh embodiment, and the rear frame 13 is moved rearward from the notch 21 due to the load component Fa distributed in the first path A at the two crotch portions 14. The collision energy absorption effect can be further enhanced by bending and deforming toward.
FIG. 14 shows a ninth embodiment of the present invention. In the present embodiment, the rear end portion of the side frame 12 of the subframe 11 in the first embodiment is directed outward in the vehicle width direction. The rear frame 13A, which is curved and extended and separately formed across these curved bases, is combined to form the rear extension portion of the side frame 12 as the outer branch portion 14b, and the side frame 12 of the rear frame 13A. The bifurcated portion 14 is formed with the binding base of the inner branch portion 14a as the inner branch portion 14a.
[0061] Therefore, according to the structure of the ninth embodiment, in addition to the effect of the first embodiment, the side frame 12 and the rear frame 13 are formed separately, so that vehicles having different vehicle widths are formed. The side frame 12 can be shared between the two, and the lengths of the rear frame 13 and the front frame 16 can accommodate different vehicle widths.
FIG. 15 shows a tenth embodiment of the present invention. In the present embodiment, the bifurcated portion 14A of the subframe 11 in the first embodiment is provided with a lightweight metal material such as an aluminum alloy. On the other hand, the side frame 12A and the rear frame 13B are extruded and molded using the same metal material to separate them, and the two crotch portions 14A are connected and fixed to the rear end portion of the side frame 12A, and the left and right 2 parts are formed. The rear frame 13B is connected and fixed between the inner branch portions 14a and 14a of the crotch portions 14A and 14A.
[0063] Therefore, according to the structure of the tenth embodiment, in addition to the effect of the first embodiment, the design and molding of the two crotch portion 14A can be easily performed, and the rear as in the ninth embodiment. The lengths of the frame 13B and front frame 16 can accommodate different vehicle widths.
[0064] In the first embodiment, the rear mount portion 18 of the subframe 11 is coupled to the vicinity of the front end portion of the extension member 2, but in addition to this, as in the eleventh embodiment shown in FIG. The amount of protrusion of the outer branch portion 14b of the portion 14 to the outside in the vehicle width direction can be increased so that the rear mount portion 18 can be connected to the vicinity of the front end portion of the side sill 6.
[0065] In this way, by connecting the rear mount portion 18 to the vicinity of the front end portion of the side sill 6, the distributed load from the rear mount portion 18 is transferred to the side sill 6 having the highest rigidity among the floor skeleton members 8. It can be transmitted directly, and the absorption effect of the distributed load can be enhanced.
[0066] Further, as in the twelfth embodiment shown in FIG. 17, the rear mount portion 18 can be coupled to the outrigger 7, and in this case, the distributed load from the rear mount portion 18 is applied to the side sill 6. In addition to improving transmissibility, it is also possible to absorb part of the collision energy due to the plastic deformation of the outrigger 7.
BRIEF DESCRIPTION OF THE DRAWINGS [FIG. 1] A perspective view of a front portion of an automobile adopting the structure of the present invention as viewed from below.
FIG. 2 is a perspective view of a subframe according to the first embodiment of the present invention.
3 is a cross-sectional view taken along the AA line of FIG.
FIG. 4 is a plan explanatory view showing a first embodiment of the present invention transparently.
FIG. 5 is an image diagram illustrating the deformation behavior of the bifurcated portion of the subframe according to the first embodiment of the present invention with respect to the pattern (A) and the pattern (B).
FIG. 6 is a perspective view of a subframe according to a second embodiment of the present invention.
FIG. 7 is a perspective view of a subframe according to a third embodiment of the present invention.
FIG. 8 is a perspective view of a subframe according to a fourth embodiment of the present invention.
FIG. 9 is a perspective view of a subframe according to a fifth embodiment of the present invention.
FIG. 10 is a plan explanatory view showing a sixth embodiment of the present invention transparently.
FIG. 11 is a perspective view of a subframe according to a seventh embodiment of the present invention.
FIG. 12 is a perspective view of a subframe according to an eighth embodiment of the present invention.
FIG. 13 is a plan explanatory view showing a perspective view of the deformation behavior of the eighth embodiment of the present invention.
FIG. 14 is a perspective view of a subframe according to a ninth embodiment of the present invention.
FIG. 15 is a perspective view of a subframe according to a tenth embodiment of the present invention.
FIG. 16 is a plan explanatory view showing a perspective view of the eleventh embodiment of the present invention.
FIG. 17 is a plan explanatory view perspectively showing a twelfth embodiment of the present invention.
[Code description] 1 ... Side member (skeleton member of front compartment) 2 ... Extension side member 3 ... Bumper reinforcement 5 ... Floor 6 ... Side sill 7 ... Outrigger 8. .Floor skeleton member 10 ... Power unit (vehicle unit parts) 11 ... Subframe 12,12A ... Side frame 13,13A, 13B ... Rear frame 14,14A ... 2 Crotch 14a .. .Inner branch 14b ... Outer branch 16 ... Front frame 17 ... Front mount 18 ... Rear mount 19,21,22 ... Notch (fragile) F C .. .Front compartment C ... Cabin A ... Load transmission first path B ... Load transmission second path F ... Collision load
Every citation, both ways
| Document | Relation | Office |
|---|---|---|
| JP09240291A | Cites | Japan |
| JP46034325B1 | Cites | Japan |
| JP01116777U | Cites | Japan |
| JP11222152A | Cites | Japan |
| JP58035471U | Cites | Japan |
| JP03091282U | Cites | Japan |
10 members in 4 offices
Priority claims2
| Document | Office | Kind | Date |
|---|---|---|---|
| 2001330734 | Japan | A | |
| JP20010330734 | – | – | – |
Members10
| Document | Office | Kind | |
|---|---|---|---|
| US2003080587A1 | United States of America | A1 | |
| EP1306289A1 | European Patent Office (EPO) | A1 | |
| JP2003127893A | Japan | A | |
| JP3606250B2This record | Japan | B2 | |
| US6843524B2 | United States of America | B2 | |
| EP1676769A2 | European Patent Office (EPO) | A2 | |
| EP1676769A3 | European Patent Office (EPO) | A3 | |
| EP1306289B1 | European Patent Office (EPO) | B1 | |
| DE60216034D1 | Germany | D1 | |
| DE60216034T2 | Germany | T2 |
8 legal events, as the office reported them to INPADOC
Over the term
Point at a mark for the eventEvents
| Event | Code | |
|---|---|---|
| Cancellation because of no payment of annual feesLAPS | LAPS | |
| Certificate of patent or registration of utility modelJAPANESE INTERMEDIATE CODE: R150R150 | R150 | |
| First payment of annual fees (during grant procedure)JAPANESE INTERMEDIATE CODE: A61A61 | A61 | |
| Written decision to grant a patent or to grant a registration (utility model)JAPANESE INTERMEDIATE CODE: A01A01 | A01 | |
| Decision of grant or rejection writtenTRDD | TRDD | |
| Written amendmentJAPANESE INTERMEDIATE CODE: A523A521 | A521 | |
| Notification of reasons for refusalJAPANESE INTERMEDIATE CODE: A131A131 | A131 | |
| Report on retrievalJAPANESE INTERMEDIATE CODE: A971007A977 | A977 |
Numbers
- Publication
- 3606250
- Publication, DOCDB
- 3606250
- Publication, EPODOC
- JP3606250B
- Application
- 330734
- Application, DOCDB
- 2001330734
- Application, EPODOC
- JP20010330734
Titles2
- Japanese
- 車体前部構造
- English
- Body front structure
Classification
- CPC, 2
- B62D21/155
- B60G2206/016
- IPC, 3
- B62D25 20
- B62D21 00
- B62D21 15