[0001]The present invention relates to a vehicle front structure.
BACKGROUND
[0002]Recently, in view of global environmental protection, improved fuel economy of automobiles has been required. On the other hand, maintenance of the collision safety of the vehicle and improved it is required. To satisfy these requirements, the development of high strength and lightweight vehicle body structure has been advanced. For example, around the frame members, such as frames or pillars, the application of high-strength steel sheet thin is promoted.
[0003]
　For example, the vehicle front, the cabin (the cabin), the dash lower panel is provided to partition a front box for accommodating a device, such as an engine or motor which is disposed in front cabin. The dash lower panel, such as the front side member or floor member is bonded to the frame member provided in front of the vehicle.
[0004]
　A vehicle front structure comprising such a dash lower panel and a frame member, the collision by the collision of the vehicle front, or collision safety against collision load by the secondary collision of the engine such as receipt of an impact due to the collision object the development of technology to improve has been promoted. For example, the following Patent Document 1 is provided with a member reinforcement on top of the front side member, techniques in which the member reinforcement is joined to the dash cross member provided in the dash panel is disclosed. Such techniques can improve the load carrying capacity for the collision load. Further, the following Patent Document 2, a technique for connecting the lower dashboard and the floor frame as the ridge line of the ridge line and the floor frame of the bead formed to project the cabin side in the dashboard lower overlap in the vertical direction is disclosed ing. Such techniques, it is possible to transmit the collision load dashboard lower receives efficiently floor frame.
CITATION
Patent Document
[0005]
Patent Document 1: JP 2013-10424 JP
Patent Document 2: JP 2012-11959 JP
Summary of the Invention
Problems that the Invention is to Solve
[0006]
　To accommodate fuel efficiency standards for automobiles being future stringent, it is required to further reduce the weight of the body structure. However, when aiming to further thinning of the skeleton members such as front side members or floor member, there are many cases where the absorption performance of the collision energy is lower than the performance that was assumed at the time of design. Therefore, for example, in the structure as to absorb voluntarily collision energy to the skeletal member disclosed in Patent Documents 1 and 2, both the additional weight of the body structure and desired impact energy absorbing performance is difficult is there.
[0007]
　To further promote the weight reduction of the body structure while maintaining the collision safety against collision from the front of the vehicle is not only the skeletal member of the conventional merely collide to the dash lower panel and plays the role of only divide the space the present inventors and it is useful to absorb energy thought. To this end, high-strength and weight of the dash lower panel is required.
[0008]
　However, simply welded to the frame member of the dash lower panel, it is difficult to obtain the weld strength sufficiently. This is because, when a collision load from the front of the vehicle acts on the dash lower panel is the dash lower panel and welded portion between the skeletal member is broken, because they may possibly be peeled off. In this case, the dash lower panel detached from the frame member is made easy to bend the cabin side by the collision load from the front of the vehicle. Therefore, it is impossible to receive the impact load adequately by dash lower panel, impactor and apparatus of an engine or the like which is stacked on the front box is likely to enter the cabin side. Thus, there is a possibility that the vehicle collision safety may be impaired.
[0009]
　The present invention has been made in view of the above problems, it is an object of the present invention, while maintaining the collision safety in the event of an impact against the vehicle front, it is possible to reduce the weight of the body structure possible to provide a new and improved vehicle front structure.
Means for Solving the Problems
[0010]
　In order to solve the above problems, according to an aspect of the present invention, provided in the vehicle length direction from the front box toward the cabin, and the framework member of the channel-shaped having side walls, fitted inside said frame member having a side wall includes a groove for engagement, the side walls of the said framework member in the groove is bonded, it comprises a dash lower panel, the vehicle front structure is provided.
[0011]
　Side wall and the side wall of the frame member of the groove is joined by joints, the joints, welds, fastening portion, may be at least one of the bonding portion or the caulking joint.
[0012]
　The weld may be formed in a linear shape continuous with bent in the vehicle length direction.
[0013]
　The welds may be formed by laser welding and / or arc welding.
[0014]
　The welds may be formed by spot welding or arc spot welding.
[0015]
　At least a portion of the side wall of the groove, is provided first groove extending in the vehicle height direction, in the side wall of said frame member, a second fitting groove corresponding to the first groove is provided the first groove may be fitted into the second fitting groove.
[0016]
　Inside the groove, abutting contact member may be provided for each of the side walls facing each other in the groove.
[0017]
　The contact member may be formed of resin or metal.
[0018]
　The depth of the groove may be of 15mm or more.
[0019]
　Said groove is a pair arranged in the vehicle width direction in the dash lower panel, the intermediate portion located between the pair of the groove in the dash lower panel, from one end to the other end in the vehicle width direction of the intermediate portion, the high rigidity region may be provided having a higher rigidity than the rigidity in the vehicle width direction outer side portion of said intermediate portion of the dash lower panel.
[0020]
　Thickness of the metal plate in the high rigidity region may be larger than the plate thickness of the metal plate in the portion other than the high rigidity region in the dash lower panel.
[0021]
　The metal plate in the high rigidity region, the sheet member made of a resin may be bonded.
[0022]
　The metal plate in the high rigidity region, connects the cylinder of a plurality of the same height, the top surface of the cover one end portion of each of the cylindrical body, and the respective other ends of the cylinder base resin structure provided in, are joined through the top surface, the said base of the resin structure, a sheet member made of resin or paper may be joined.
[0023]
　The metal plate in the high rigidity region may have an irregular shape.
[0024]
　Said groove is a pair arranged in the vehicle width direction in the dash lower panel, the intermediate portion located between the pair of the groove in the dash lower panel, from one end to the other end in the vehicle width direction of the intermediate portion, the high intensity regions may be provided with a higher tensile strength than the tensile strength of the vehicle width direction outer side portion of said intermediate portion of the dash lower panel.
[0025]
　The thickness of the dash lower panel may be 1.0mm or more and 2.0mm or less.
[0026]
　The tensile strength of the dash lower panel may be greater than or equal to 340MPa.
[0027]
　It said frame member is at least may include any of the front side member or floor member.
[0028]
　According to the above configuration, the side walls of the frame member of the groove of the dash lower panel is joined. In this case, the collision load from the front of the vehicle is applied to the dash lower panel, rupture mode of the joint portion becomes shear fracture mode. In the high strength steel plate, towards the shear breaking mode than plugs breaking mode in which two members is broken in the direction of cleavage is because the tensile strength is increased, breakage of the joint portion is less likely to occur. Therefore, even the collision load from the front of the vehicle acts on the dash lower panel, breakage of the joint portion is less likely to occur. Accordingly, the dash lower panel since difficult to bend the cabin side, it is possible to sufficiently absorb the collision energy. Thus, not only the weight of the dash lower panel, may be also performs weight of the skeletal member. Thus, without impairing crashworthiness, it is possible to realize weight reduction of the vehicle body.
Effect of the invention
[0029]
　According to the present invention described above, while maintaining the collision safety in the event of an impact against the vehicle front, it is possible to reduce the weight of the vehicle body structure.
BRIEF DESCRIPTION OF THE DRAWINGS
[0030]
FIG. 1 is a perspective view showing a schematic configuration of a vehicle front structure according to an embodiment of the present invention.
It is a cross-sectional view of the frame member and the dash lower panel in FIG. 2] II-II section line of Figure 1.
3 is a diagram showing an example of the behavior of the dash lower panel when a collision load to the dash lower panel is applied according to the embodiment.
[FIG 4A] is a diagram showing a first example of the high rigidity region provided in an intermediate portion according to the embodiment.
[FIG. 4B] is a diagram showing a second example of the high-rigidity region provided in an intermediate portion according to the embodiment.
5 is a diagram showing a configuration example of a resin structure and the sheet member according to the embodiment.
6 is a diagram showing an example of a welded portion formed in a linear continuous while bent in the vehicle length direction.
[Figure 7A] first fitting groove is a side view showing a state of the skeleton members 2 and the groove portion 4A when fitted into the second fitting groove.
[FIG 7B] is a cross-sectional view in which the first groove is a first example showing the state of the frame member and the groove when being fitted to the second fitting groove.
[FIG. 7C] is a cross-sectional view in which the first groove is a second example showing the state of the frame member and the groove when being fitted to the second fitting groove.
A first example of FIG. 8A] contact member is a perspective view showing a schematic configuration of a vehicle front structure comprising a contact member.
A first example of FIG. 8B] contact member is a side view showing a schematic configuration of a vehicle front structure comprising a contact member.
A first example of FIG 8C] contact member, a cross-sectional view of the frame member and the dash lower panel in the vehicle front structure comprising a contact member.
It is a diagram showing a second example of FIG. 8D] contact member.
Is a perspective view showing the FIG. 9 schematic configuration of a conventional vehicle front structure.
DESCRIPTION OF THE INVENTION
[0031]
　Reference will now be described in detail preferred embodiments of the present invention. In the specification and the drawings, components having substantially the same function and structure are a repeated explanation thereof by referring to the figures.
[0032]
　In the following description, the terms indicating the context such as "front", "rear" or "rear" is, unless otherwise distinguishing, denote the direction or position related in the vehicle length direction L .
[0033]
　<< 1. Background >>
　Before describing the configuration of a vehicle front structure according to each embodiment of the present invention will be described background to conceive the present invention.
[0034]
　Figure 9 is a perspective view showing a schematic configuration of a conventional vehicle front structure. As shown in FIG. 9, the vehicle front structure 91 comprises a frame member 92, 92 and the dash lower panel 93,.
[0035]
　Frame member 92 is at least one of the frame members of the front side member or floor member is provided extending in the vehicle length direction L. Further, frame member 92 may be a member obtained by bonding the front portion of the rear and the floor member of the front side member. The frame member 92 has a groove-shaped portion 92A which upper side is opened, and a flange 921. Further, frame member 92 is curved shape is provided to offset the vehicle height direction V toward the front from the rear of the vehicle.
[0036]
　Dash lower panel 93 is a member that partitions the front box and the cabin of the vehicle. That is, the front box present on the vehicle front side of the dash lower panel 93, the rear side of the vehicle than the dash lower panel 93 is present cabin. Dash lower panel 93 is provided on the upper portion of the frame member 92. The dash lower panel 93 has an inclined wall 94, and the vertical wall 95. As shown in FIG. 9, portions of the halfway from the rear end of the inclined wall 94, the frame member 92 along the curved shape of the frame member 92 abuts. Also, toward the front from the middle of the rear inclined wall 94, inclined away from the frame member 92 is provided on the inclined wall 94. Incidentally, the rear end of the inclined wall 94 is joined to the floor panel (not shown).
[0037]
　As shown in FIG. 9, the vehicle front structure 91 includes a frame member 92 and the dash lower panel 93 is formed by being joined. Specifically, the rear portion of the flange 921 and the inclined wall 94, at the location indicated by the asterisk in FIG. 9, referred to as a joint 96 (joint portion by being joined by a joining means such as spot welding ), the vehicle front structure 91 is formed.
[0038]
　When receiving a collision from the vehicle front to the vehicle front structure 91 shown in FIG. 9, the load due to the collision acts on the frame member 92 and the dash lower panel 93. Role frame member 92 to absorb the impact energy by crushing due to the collision load.
[0039]
　Also, if when the low collision object probability of collision directly to the backbone member 92 collides with the vehicle, or any device such as an engine housed in the front box collision by the collision member is received like a utility pole, the dash lower panel sometimes it acts proactively collision load to 93. In this case, a collision load acting proactively to the dash lower panel 93 is transmitted from the dash lower panel 93 to the frame member 92 via a joint 96. Then, the collision energy by the collision load because the skeletal member 92 absorbs, in the case of direct collision load to the skeletal member 92 does not act, it is possible to maintain the crash safety of the vehicle.
[0040]
　Furthermore, the present inventors have by molding by a high-strength steel sheet of the dash lower panel 93, receiving the impact force due dash lower panel 93 collides, considered dash lower panel 93 can also absorb the impact energy by plastic deformation It was.
[0041]
　However, for higher strength and weight of the vehicle body, when the frame member 92 and the dash lower panel 93 is formed by a high-strength thin steel sheets, welding with increasing carbon content of the steel sheet softening or hardness, the stress concentration or the like of the joint portion due to the increase, the bonding strength is likely to decrease. Therefore, in the conventional vehicle front structure 91, when a collision load acts on the dash lower panel 93 is transmitted to the frame member 92 via the joint 96, the joint strength of the joint portion 96 is insufficient, the joint there is a high possibility that 96 will be broken. Then, the dash lower panel 93 which may receive a collision load will deflect the cabin side. Therefore, the collision member or device, such as an engine which has received the impact load due to the collision body, while deflecting the dash lower panel 93 on the vehicle rear side, is likely to enter the cabin side. That is, there is a possibility that the collision safety of the vehicle may be impaired.
[0042]
　Accordingly, the present inventors have studied intensively, the present inventors have found that the fracture mode of the joining portion of the dash lower panel and the frame member, the fracture mode of the shear direction rather than fracture mode of the peeling direction, joining enhanced strength, and conceived that it is possible to make it difficult to cause the breakage of the joint portion. Accordingly, the present inventors it is possible to exhibit the function of absorbing collision energy by the dash lower panel found. Accordingly, the present inventors have developed a vehicle front structure capable of realizing the function of absorbing collision energy by dash lower panel. As a result, while maintaining the collision safety was shown to be capable of achieving weight reduction of the overall body structure. The following describes the structure of the vehicle front structure according to an embodiment of the present invention.
[0043]
　<< 2. Embodiment
　>> <2.1. Configuration>
　FIG. 1 is a perspective view showing the schematic configuration of the vehicle front structure 1 according to an embodiment of the present invention. As shown in FIG. 1, the vehicle front structure 1 according to the present embodiment has a frame member 2,2, and the dash lower panel 3.
[0044]
　Frame member 2, in the right and left of the vehicle, are provided a pair extending in the vehicle length direction L. The frame member 2, for example, at least one member of the front side member or floor member. Frame member 2 according to the present embodiment is a member which is formed by the front end of the rear end and the floor member of the front side member is joined. Joining position in the vehicle length direction L of the front side member and the floor member is not particularly limited. As shown in FIG. 1, frame member 2 according to the present embodiment has a groove-shaped portion 2A which upper side is opened. Further, frame members 2 are curved shape is provided to offset the vehicle height direction V toward the front from the rear of the vehicle. Such frame member 2 is formed by, for example, a metal plate such as steel plate.
[0045]
　Dash lower panel 3 is a member that partitions the front box and the cabin of the vehicle. That is, the front box present on the vehicle front side of the dash lower panel 3, the vehicle rear side of the dash lower panel 3 there are cabins. The said front box, for example, an engine, various devices such as a motor or a battery can be housed. That is, the front box is an example of an engine room or the motor room. Further, the front box can be a trunk room for loading luggage and the like. Moreover, the cabin is a space passenger boarding. The dash lower panel 3 is provided on top of the frame member 2, 2.
[0046]
　The dash lower panel 3, the inclined wall 4, and a vertical wall 5. As shown in FIG. 1, the rear portion in the vehicle length direction L of the inclined wall 4 (hereinafter, simply referred to as the rear of the inclined wall 4) has an abutting shape the flange of the frame member 2. Portion from the rear end of the inclined wall 4 halfway abuts along the curved shape of the frame member 2 to the frame member 2. Further, from the middle of the rear of the inclined wall 4 to the front in the vehicle length direction L of the inclined wall 4, the inclination is provided on the inclined wall 4 away from the frame member 2. Incidentally, the rear end of the inclined wall 4, is joined to the floor panel (not shown).
[0047]
　Further, the inclined wall 4 of the dash lower panel 3 according to the present embodiment, the groove 4A is provided on the front box side along the vehicle length direction L. The groove 4A is provided on the inclined wall 4 to fit inside the groove-shaped portion 2A of the frame member 2, 2. Grooves 4A may be provided longitudinally in the vehicle length direction L of the inclined wall 4, as shown in FIG. 1, it may be partially provided at a rear portion of the inclined wall 4. Although details will be described later, the groove 4A is as long provided so as to partially fit in at least the groove-shaped portion 2A of the frame member 2, the length of the vehicle length direction L of the groove 4A is not particularly limited. Groove 4A is provided, for example, at the time of molding by press molding or the like of the dash lower panel 3.
[0048]
　Although not shown in FIG. 1, for example, in the central portion in the vehicle width direction W of the inclined wall 4, a tunnel portion that bulges may be formed upward. The tunnel section, when the engine in the front box is accommodated, may be provided to pass exhaust pipe passing exhaust gas discharged from an engine, or a drive shaft for driving the rear wheels to the vehicle underbody .
[0049]
　The upper end of the vertical wall 5 may be joined to the dash upper panel (not shown). In this case, the dash panel is formed by the dash lower panel 3 and the dash upper panel. Further, the vertical wall 5 may be an integral part with the dash upper panel. In this case, the dash lower panel is formed as the dash panel. Moreover, because of the strength of the dash lower panel 3 increase, for example, the dash cross member (not shown) may be provided on the front side of the vertical wall 5 along the vehicle width direction W.
[0050]
　Such dash lower panel 3, for example, flat metal plate can be obtained by molding such as press molding is made. Specifically, the dash lower panel 3 is obtained by press-molding a steel plate. The steel plate is preferably tensile strength of high-tensile steel of more than 340 MPa. The tensile strength of the steel sheet is more preferably not less than 980 MPa. Further, the thickness of the dash lower panel 3 is preferably 1.0mm or more and 2.0mm or less. Smaller than larger 2.0mm than the plate thickness 1.0 mm, while ensuring the strength, it is possible to sufficiently reduce the weight of the vehicle body. The thickness is appropriately set in accordance with the strength and weight required.
[0051]
　As shown in FIG. 1, the vehicle front structure 1 according to the present embodiment, the groove 4A of the dash lower panel 3 is fitted inside the frame member 2, the side walls of the groove 4A and the side wall of the frame member 2 is spot welding It is formed by being bonded by like. The following describes bonding of the frame member 2 and the dash lower panel 3.
[0052]
　Figure 2 is a cross-sectional view of the frame member 2 and the dash lower panel 3 in II-II section line of Figure 1. As shown in FIG. 2, frame member 2 includes a bottom wall 21, a pair of side walls 22, 22 upstanding from the bottom wall 21, a pair of flanges extending outwardly from the side wall 22 along the vehicle width direction W 23, 23 with the door. Further, the inclined wall 4 of the dash lower panel 3, a bottom wall 41, the groove 4A is formed is provided by a pair of side walls 42 upstanding from the bottom wall 41.
[0053]
　The shape of the bottom wall 41 of the bottom wall 21 and the groove 4A of the frame member 2 is not particularly limited. For example, bottom wall 21 and bottom wall 41 may be a flat shape as shown in FIG. 2, there may be uneven. Further, the bottom wall 21 and bottom wall 41 may have a plurality of surfaces. In this case, between the surface and the surface, for example, bent portions may be provided.
[0054]
　A pair of side walls 22 facing the frame member 2 extends vehicle length direction, also extends generally in the vehicle height direction. Be extended to match the side walls 22 completely in vehicle height direction is actually difficult to be ideal. Further, in the cross section of the vehicle length direction, the angle of the pair of side walls 22 facing the frame member 2 is preferably less 0 degrees and 30 degrees. The groove-shaped portion 2A of the thus frame member 2, a bottom wall 21 and a pair of side walls 22 are provided. Since the side walls 22 extending in the vehicle height direction, it is possible to secure the bonding strength of the frame member 2 and the groove 4A. For the mechanism will be described later. As for the angle between the pair of side walls 42 facing the groove 4A, it is similar. That is, the groove 4A, the bottom wall 41 and a pair of side walls 42 are provided. Incidentally, such a groove shape is a cross-sectional triangular bottom wall having no 21 (41) (i.e. there is no bottom surface) groove of the frame member and the inclined wall are not included in the scope of the present invention.
[0055]
　As shown in FIG. 2, the inner surface 22a of the side wall 22 of the frame member 2, and the outer surface 42a of the side wall 42 of the groove 4A of the dash lower panel 3 is in contact with. At this time, the portion indicated by a triangle in the drawing, the side walls 22 and side walls 42 are joined. The portion where the side wall 22 and the side wall 52 is joined, referred to as bonded part 6. In FIG. 1, the bonded part 6 at a position indicated by the asterisk is formed. As a means for realizing the joint 6, for example, they may be joined by spot welding. In this case, the bonded part 6 along the vehicle length direction L, may be provided at predetermined intervals. The predetermined distance is appropriately set by the size and material of the frame member 2. The position of the joint 6 in the height direction of the side wall 22 and the sidewall 42 (substantially vertical direction) is preferably approximately the middle position. Thus, the bonding area can be maximally secured.
[0056]
　Incidentally, as a joining technique other than spot welding for realizing the joint 6, TIG (tungsten inert gas) welding, MIG (Metal Inert Gas) welding, arc welding such as plasma welding, laser welding or electron beam welding known welding techniques may be used and the like. Also, as a joining technique for realizing a joint 6, fastening technique using rivets or bolts or the like, bonding technology by crimped or bonding technique using an adhesive or the like may be used.
[0057]
　Another example of a means for realizing such joints 6 will be described later.
[0058]
　Of the inclined wall 4 of the dash lower panel 3, the intermediate portion 4B located between the pair of grooves 4A, 4A shown in FIG. 1, a vehicle width direction outer side portion of the intermediate portion 4B (e.g., the outer groove 4A region having a higher stiffness than the stiffness of the outer plate portion 4C) (high-rigidity region) may be provided located. The high-rigidity region is at least, be provided from one end 401 in the vehicle width direction of the intermediate portion 4B toward the other end 402. As described later, the high rigidity region may be provided on all or part of the intermediate portion 4B.
[0059]
　The specific means of high rigidity in the high rigidity region of the intermediate portion 4B, will be described later.
[0060]
　Further, the intermediate portion 4B, vehicle width direction outer side portion of the intermediate portion 4B (e.g., outer plate portion 4C located outside of the groove 4A) region having a higher tensile strength than the tensile strength of the (high strength region) it may be provided. The high strength region, at least, be provided from one end 401 in the vehicle width direction of the intermediate portion 4B toward the other end 402. As described later, the high intensity regions may be provided on all or part of the intermediate portion 4B.
[0061]
　Such dash lower panel 3 including an intermediate portion 4B having a high strength region, for example, obtained by a tailored blank containing relatively high steel sheet portion a tensile strength of a portion corresponding to the intermediate portion 4B pressing.
[0062]
　<2.2. Function and Effect>
　FIG. 3 is a diagram showing an example of the behavior of the dash lower panel 3 when impact load F is applied to the dash lower panel 3 according to the present embodiment. A side wall and a side wall of the frame member 2 of the groove 4A which is provided on the inclined wall 4 is in contact, by forming a joint 6a ~ 6c with spot welding, and the dash lower panel 3 and the frame member 2 are joined that.
[0063]
　Then, when a collision load F acts proactively against the dash lower panel 3 from the front of the vehicle, the dash lower panel 3 shows a deformation mode as away from the frame member 2. In this case, the force pulling the in-plane direction of the bonding surface of the bonded part 6 of the side wall 22 of the sidewall 42 and the frame member 2 of the groove 4A of the dash lower panel 3 (shearing force) is generated in the dash lower panel and skeletal member. Then, as in the so-called shear fracture mode, behaves like the bonding surfaces is shifted in the plane direction is shown in the bonded part 6.
[0064]
　On the other hand, in the vehicle front structure 1 shown in FIG. 9, the dash lower panel 93 is joined via a flange 921 of the frame member 92. Then, when a collision load from the front of the vehicle with respect to the dash lower panel 93 is applied, the dash lower panel 93 indicating the mode of deforming in a direction away from the frame member 92. In this case, the force pulled in the direction perpendicular to the bonding surface of the dash lower panel 93 and the frame member 92 is caused to the dash lower panel 93 and the frame member 92. Then, as in the so-called plug fracture mode, behaves like the bonding surface is peeled is shown at the junction 96.
[0065]
　Generally, the tensile shear strength of one joint (Tensile Shear Strength: TSS) is cross tensile strength (Cross Tension Strength: CTS) tends to be higher than the. That is, the tensile strength of the shear direction of the bonding surface associated with the shear breaking mode, than the tensile strength of the peeling direction of the joint surface associated with the plug breaking mode is dominant. In the vehicle front structure 1 according to the present embodiment, by joining the side wall of the groove 4A in the side wall and the dash lower panel 3 of the frame member 2, it is possible to cause the shear fracture mode in the joint 6. That is, when the collision load acts on the dash lower panel 3, since the behavior of the shear breaking mode is indicated rather than a plug rupture mode, the bonding strength of the bonded portion 6 is increased substantially. Therefore, it is possible to hardly cause rupture of the joint 6. Therefore, peeling of the frame member 2 and the dash lower panel 3 is less likely to occur.
[0066]
　In this case, it is possible to increase as shown in FIG. 3, the time of the collision load F is applied from the vehicle front with respect to the dash lower panel 3, the bonding strength of the joint 6. That is, it is possible to hardly cause rupture of the joint 6. Then, a high impact load F is also act against the dash lower panel 3, fracture does not occur in the bonded part 6, sufficiently support the dash lower panel 3 frame member 2 via the bonding portion 6. Accordingly, the dash lower panel 3 which has received the impact load, not bend to the cabin side, may be plastically deformed receiving the impact load. Thus it is possible to absorb the collision energy by the dash lower panel 3. Therefore, it is possible to prevent ingress of transmission and collision and the like of the impact force to the cabin side. Therefore, it is possible to increase the vehicle collision safety.
[0067]
　Incidentally, according to strength and weight of the steel sheet, the shear fracture mode than plug fracture mode, be a further advantage with respect to the tensile strength has been shown by the present inventors. In particular, the tensile strength for the steel sheet is more than 780 MPa, the difference in tensile strength between two breaking modes described above has been shown that significantly greater. That is, by increasing the strength and weight of the steel sheet forming the dash lower panel 3, the bonding strength of the joint 6, further according to the present embodiment is increased, it is possible to hardly cause bonding fracture. Thus, by the steel sheet forming the dash lower panel 3 is high strength and light weight, collision safety exerted by a vehicle front structure according to the present embodiment is further increased.
[0068]
　In order to produce only shear fracture mode, a pair of side walls 22 facing the frame member 2 extends in the vehicle height direction, a pair of side walls 42 of the groove 4A also to extend in the vehicle height direction Ideally it is. That is, the angle between the pair of side walls 22 facing the frame member 2, and a pair of side walls 42 angle between the groove portion 4A is preferably both are 0 degrees. However, in the processing of actual groove configuration, since the spring-back or the like when produced by press molding or the like may occur, the angle between the pair of side walls 22 (a pair of side walls 42) may become larger than 0 degrees. That is, it is difficult to extend a pair of side walls 22 (a pair of side walls 42) matches the complete vehicle height direction. In this case, if the angle is 0 ° or more and 30 degrees or less of the pair of side walls 22 (a pair of side walls 42), since the shear fracture mode is mainly substantially possible to improve the bonding strength to become.
[0069]
　Further, by providing the high rigidity region to the intermediate portion 4B from one end 401 toward the other end 402 in the vehicle width direction of the intermediate portion 4B, the intermediate portion 4B is unlikely twist occupying the area of ​​most of the dash lower panel 3. In this case, also act from the collision load F is the front of the vehicle, it is hard twist dash lower panel 3, a pair of frame members 2 is less likely twisted relatively. Then, the skeleton member 2 is reliably restrained by the dash lower panel 3 at the time of collision. Thus, deformation mode of the frame member 2 is stabilized. Therefore, it is possible to maximize the collision safety of the vehicle front structure 1.
[0070]
　Further, by providing the high rigidity region to the intermediate portion 4B, it is possible to obtain the soundproof. Thus, the intermediate portion 4B shields noise and vibration, such as road noise, can be easily transmitted noise and vibration inside the vehicle. Thus, comfort of the vehicle interior can be improved.
[0071]
　Further, by increasing the tensile strength of the intermediate portion 4B, even when the object from the front of the vehicle to the portion of the intermediate portion 4B of the dash lower panel 3 collide, the intermediate portion 4B of the object in the vehicle direction intrusion it is possible to prevent. Further, when the high-rigidity region to the intermediate portion 4B is provided, by increasing the tensile strength of the intermediate portion 4B, it is possible to extend the possible range of elastic deformation to maintain the rigidity of the intermediate portion 4B. Thus, the frame member 2 is hardly twisted relatively. Therefore, it is possible to increase the collision safety of the vehicle front structure 1.
[0072]
　<2.3. Modification>
　The present invention is of course not limited to the example shown in the above embodiment. For example, as shown in FIGS. 2 and 3, the bottom wall 41 of the groove 4A, although partially abuts against the bottom wall 21 of the frame member 2, the present invention is not limited to such an example. More specifically, the bottom wall 41 of the groove 4A is may be abutted along the vehicle length direction L with respect to the bottom wall 21 of the frame member 2, the bottom wall 41 is not in contact against the bottom wall 21 it may be. However, a side wall 22 of the side wall 42 and the frame member 2 of the groove 4A in order to by spot welding or the like, the depth of the groove 4A (height of the side wall 42) is preferably sufficiently secured. The greater the depth of the groove 4A strength is improved, and it is possible to reduce the weight of the smaller the depth of the groove 4A structure. Specifically, the depth of the groove 4A is preferably 15mm or more. Depth of the groove 4A are set as appropriate according to the strength and weight required. Further, if the bottom wall 41 is in contact against the bottom wall 21 may be further joined by spot welding or the like in the contact portion. This makes it possible to further increase the bonding strength. The flange 23 of the frame member 2 may be joined to the inclined wall 4. This makes it possible to further increase the bonding strength. Incidentally, the flange 23 may not be necessarily in contact with the inclined wall 4.
[0073]
　Further, the groove 4A of the frame member 2 and the dash lower panel 3, the cross-sectional shape in a cross section perpendicular to the vehicle length direction L, but is not limited to the shape shown in FIG. For example, the cross-sectional shape of the frame member 2 and the groove portion 4A may be V-shaped like the U-shaped bottom wall is curved, or side walls are inclined. If the side wall 42 of the sidewall 22 and the groove 4A of the frame member 2 is joined via a joint 6, the shapes of the bottom wall, the cross-sectional shape of the frame member 2 and the groove 4A is not particularly limited. Further, the sectional shape of the cross-sectional shape and the groove 4A of the frame member 2 may not necessarily be identical or similar.
[0074]
　Further, the inside of the groove portion 4A, so as not enter the passenger's feet and foreign matter, the lid member may be provided on the upper portion of the groove 4A of the dash lower panel 3.
[0075]
　<2.4. Specific examples of the high rigidity>
　Next, in the vehicle front structure 1 according to the present embodiment, when the high-rigidity region is provided in the intermediate portion 4B of the dash lower panel 3, specifically the high rigidity of the high rigidity region It will be described an approach.
[0076]
　Figure 4A is a diagram showing a first example of the high rigidity region 410 provided in an intermediate portion 4B of the present embodiment. As shown in FIG. 4A, the high rigidity region 410 may be provided on the entire surface from one end 401 in the vehicle width direction of the intermediate portion 4B toward the other end 402. By high rigidity region 410 is provided in this manner, it is possible to suppress the relative twisting of ends of the intermediate portion 4B. Then, the relative twisting of the pair of frame members 2 is also suppressed. Thus, it is possible to absorb more impact during a collision.
[0077]
　Figure 4B is a diagram showing a second example of the high rigidity region 410 provided in an intermediate portion 4B of the present embodiment. As shown in FIG. 4B, the intermediate portion 4B plurality of high rigidity region 410a to be 410b is provided. Thus, the high rigidity region 410 only a portion of the intermediate portion 4B may be provided. The high rigidity region 410, as shown in FIG. 4B, may be provided with a plurality in parallel in the vehicle length direction. Further, a plurality of high rigidity region 410 in the intermediate portion 4B, may be provided so as to intersect. In short, the high rigidity region 410, at least a portion of the intermediate portion 4B, may be provided so as to be connected from one end to the other end in the vehicle width direction. Similarly, in at least part of the high intensity region is an intermediate portion 4B, it may be provided so as to be connected from one end to the other end in the vehicle width direction.
[0078]
　High rigidity of the high rigidity region 410 may be implemented by the following means. For example, the thickness of the metal plate in the high rigidity region 410 may be larger than the plate thickness of the portion other than the high rigidity region 410 in the dash lower panel 3. In the present embodiment, the thickness of the metal plate in the high rigidity region 410 may be greater than the thickness of the outer portion of the intermediate portion 4B (e.g. outer plate portion 4C). Thus, it is possible to increase the rigidity in the high rigidity region 410. Dash lower panel 3 the plate thickness of the metal plate includes a relatively large high-rigidity region 410 can be implemented, for example, by tailored blanks or tailor rolled blanks.
[0079]
　Further, the metal plate in the rigid region 410, the sheet member made of a resin may be bonded. Such sheet members may be joined to one or both sides of the metal plate in the rigid region 410. If the sheet member is bonded to any one side of the metal plate, the sheet member may be joined to either the inside or outside of the vehicle. By bonding the sheet member made of such a resin on a metal plate in the rigid region 410, it is possible to increase the rigidity of the high rigidity region 410.
[0080]
　The resin forming the sheet member is preferably, for example, a foam-curing resin. Further, the resin is more preferably provided with a damping performance. Method of joining the sheet member and the metal plate is not particularly limited. For example, when the resin forming the sheet member is a resin of the foamed curable, by an adhesive force of the resin formed on the surface of the metal plate and the sheet member and the metal plate may be joined.
[0081]
　Further, the metal plate in the rigid region 410, the resin structure may be joined together with the sheet member. Figure 5 is a diagram showing a configuration example of a resin structure 7 and the sheet member 8 according to this embodiment. Referring to FIG. 5, a resin structure 7 according to this embodiment, the tubular body 71 of a plurality of the same height, the top surface 72 to cover the respective one end portions 71a of the cylinder 71, and the cylindrical body 71 comprising a base portion 73 which connects each of the other end portion 71b to each other. Further, the base portion 73, the sheet member 8 made of a resin or paper is bonded.
[0082]
　By sandwiching the metal plate and the sheet member 8 of the intermediate portion 4B in the high rigidity region 410 such resin structure 7, it is possible to increase the overall thickness including the metal plate of the intermediate portion 4B in the high rigidity region 410 . The high rigidity of the high-rigidity area 410, by performing the resin a small density as compared with the metal plate, can be realized weight reduction per rigidity.
[0083]
　The structure of the resin structure 7 is not limited to the example shown in FIG. For example, the height of the cylindrical body 71, the in-plane direction of the size, pitch, and top surface shape of the 72 and the base 73 (e.g., a circle or honeycomb structures), etc., the high rigidity region resin structure 7 is applied 410 It may appropriately be set in accordance with the required performance and the like in.
[0084]
　Further, resin structure 7 can be joined to one or both sides of the metal plate in the rigid region 410. If resin structure 7 is joined to one side of the metal plate, resin structure 7 may be bonded to either the inside or outside of the vehicle. However, in order to avoid the reduction of the effects of high rigidity due to the damage caused by collision of the object from the outside, the resin structure 7 is preferably bonded to the inside of the vehicle. Further, on one surface of the metal plate in the rigid region 410 is joined resin structure 7 may be joined sheet member on the other side.
[0085]
　Further, the metal plate in the rigid region 410, irregularities may be formed. And such irregularities, for example, a shape constituted by concave or convex portions are formed on the surface of the metal plate. By the uneven shape is formed on the metal plate in the rigid region 410, the proportion of the flat surface (surface on which irregularities are not formed) of the rigid region 410 is reduced. This improves the rigidity of the metal plate in the rigid region 410. Such irregularities may, for example, may be formed by embossing or the like. More specifically, as irregularities, irregularities disclosed in WO 2013/94691 may be applied to the high rigidity region 410.
[0086]
　Further, the metal plate in the rigid region 410, means high rigidity as described above may be applied in combination as appropriate. For example, irregularities are formed by embossing the metal plate in the rigid region 410, and the resin structure and / or sheet member may be joined to the metal plate.
[0087]
　Incidentally, means high rigidity as described above is merely an example, possible to improve the rigidity in the high rigidity region, such as the intermediate portion 4B is possible, the technology according to the known high rigidity is to the high rigidity region It can be applied Te.
[0088]
　This completes the description of a specific example of the high rigidity.
[0089]
　<2.5. Specific examples of joint>
　Next, a specific example of the joint 6 according to the present embodiment.
[0090]
　Referring again to FIG. 2, the joint 6, is joined with the inner surface 22a of the side wall 22 of the frame member 2 and an outer surface 42a of the side wall 42 of the groove 4A of the dash lower panel 3. Incidentally, the joint 6 shown in FIG. 2 are those merely schematically shown, the actual position of the joint portion 6, the range and magnitude is not limited to the example shown in FIG. 2, in accordance with the bonding aspect different.
[0091]
　For example, the joint 6 shown in FIG. 2 may be a nugget formed between the side wall 22 and the side wall 42 by spot welding. In another example, the position of the joint 6 is formed (vehicle length direction or position in the vehicle height direction), all or part of the outer surface 42a and is in contact with each other portion of the inner surface 22a and the side wall 42 of the side walls 22 It can be in. Further, the range of the joint portion 6, the contact portion and the vicinity thereof may be a range that penetrates one or both of the side walls 42 of the side wall 22 and the groove 4A of the frame member 2, a side wall 22 and side walls 42 it may be. The size of the joint portion 6 can be appropriately set depending on the position or the like to be bonded unit and formation. It may also be formed as a joining portion 6 a plurality of joint portions is one of joining the outer surface 42a of the inner side surface 22a and the side wall 42 of the side wall 22.
[0092]
　Joint 6, for example, may be a weld. That is, the joint 6 can be a portion formed by welding. Such welding is not limited to the spot welding as described above, laser welding, it may be arc welding or arc spot welding. Furthermore, such welding can be a hybrid welding combines laser welding and arc welding.
[0093]
　Further, such welds may be formed in a linear shape continuous with bent in the vehicle length direction. Figure 6 is a diagram showing an example of a welding portion 60 formed in a linear shape continuous with bent in the vehicle length direction. As shown in FIG. 6, the weld 60 for joining the side wall 42 of the groove 4A in the side wall 22 and the dash lower panel 3 of the frame member 2, continuous in longitudinal direction of the vehicle, is formed in a wave that oscillates in the vehicle height direction it may be. This makes it possible to obtain more bonding wire length. Therefore, it is possible to increase the bonding strength between the frame member 2 and the dash lower panel 3.
[0094]
　Additional joint 6, for example, may be a fastening portion. Such fastening part, for example, bolts, may be implemented by a nut or rivet. Thus, the outer surface 42a of the side wall 42 of the inner side surface 22a and the groove 4A of the side wall 22 of the frame member 2 are joined by a fastening. The joining portion 6 may be, for example, an adhesive portion. Such adhesive may, for example, may be implemented by known adhesives such as a resin or the like. Thus, the outer surface 42a of the side wall 42 of the inner side surface 22a and the groove 4A of the side wall 22 of the frame member 2 are joined by adhesion. The joining portion 6 is, for example, may be a crimped portion. Such caulking joint, for example, in a state wherein the outer surface 42a is in contact of the side wall 42 of the inner side surface 22a and the groove 4A of the side wall 22 of the frame member 2 can be achieved by combining both members connecting the plastic deformation . Further, the caulking joint can be realized by caulking bonding using bonding member such as a rivet.
[0095]
　<2.6. Examples of other reinforcing means>
　(groove)
　will be described on the vehicle front structure 1 of the frame member 2 and the groove 4A of the present embodiment for example, each providing a mating groove.
[0096]
　First, some of the side wall of the groove 4A, the first groove extending in the vehicle height direction may be provided one or more. In this case, the side wall of the frame member 2, the second fitting groove corresponding to the first groove provided in the groove portion 4A is provided. Then, when the skeleton member 2 and the dash lower panel 3 is joined, a first fitting groove is fitted into the second fitting groove. These fitting grooves may be formed, for example, by such provision of the groove in the drawing die.
[0097]
　Figure 7A is a side view of the first fitting groove 80 is showing the state of the skeletal member 2 and the groove portion 4A when fitted into the second fitting groove 81. Further, FIG. 7B is a sectional view showing a first example of the first groove 80A is showing a state of the skeleton members 2 and the groove portion 4A when fitted into the second fitting groove 81A. Incidentally, FIG. 7B is a view of the cross section perpendicular to the vehicle height direction of the frame member 2 and the groove 4A.
[0098]
　As shown in FIGS. 7A and 7B, a portion of the side wall 42 of the portion of the sidewall 22 of the frame member 2 and the groove 4A is the portion bends in the vehicle length direction are provided. Of these, the portion that protrudes to the outside of the side wall 22 and side walls 42, a first groove 80A and a second fitting groove 81A. Since the first groove 80A is fitted into the second fitting groove 81A, the even part of the fitting groove, and the outer surface 42a of the side wall 42 of the inner side surface 22a and the groove 4A of the side wall 22 of the frame member 2 There abuts.
[0099]
　If each of the fitting groove is not provided to the skeletal member 2 and the groove portion 4A, when a collision load acts from the vehicle front with respect to the dash lower panel 3, the load transfer from the dash lower panel 3 to the frame member 2, joint 6 (6a, 6b, 6c) is carried out only through the joints, and the like. Then, when exceeding the load bonding strength transmitted, breaking the junction 6 between the frame member 2 and the dash lower panel 3 is caused, the transmission and the collision object such as penetration of the impact force to the vehicle inside may occur. Therefore, each of the fitting grooves provided in the frame member 2 and the groove 4A, by engaging with each other, the collision load through each abut each other part of the fitting groove is transferred from the dash lower panel 3 to the frame member 2 obtain. Therefore, it is possible to increase the overall bonding strength between the frame member 2 and the dash lower panel 3. Thus, it is possible to improve the collision safety.
[0100]
　Incidentally, the joint 6 shown in FIGS. 7A and 7B is provided in a position to be the outermost of the first groove 80A and the second fitting grooves 81A, can maintain the fitting state of the fitting groove but if the position of the joint 6 is provided in the vehicle length direction is not particularly limited. Further, the joint portion 6 separately, for example, in the portion where the first groove 80A and a second fitting groove 81A is fitted, and a flange 23 of the inclined wall 4 and the frame member 2 of the dash lower panel 3 abut moiety may be joined.
[0101]
　The first groove and the second groove shape (shape of the cross section) is not limited to the example shown in Figure 7B. 7C is a cross-sectional view showing a second example of the first groove 80B is showing the state of the skeletal member 2 and the groove portion 4A when fitted into the second fitting groove 81B. Incidentally, FIG. 7C is a view of the cross section perpendicular to the vehicle height direction of the frame member 2 and the groove 4A. As shown in FIG. 7C, the first groove 80B and the second groove 81B, respectively, it may have a U-shaped cross-sectional shape in a plan view. The shape of the first groove 80 and second groove 81 (the shape of the cross section) is not necessarily the same or similar. Other shapes of the first groove 80 and second groove 81, is that each of the fitting groove to contact with each other, if possible, not particularly limited.
[0102]
　Further, in the example shown in FIG. 7A ~ Figure 7C, first groove and the second groove, each side wall of the frame member 2 and the groove 4A had a shape protruding to the outside of the side wall but the present invention is not limited to such an example. For example, the first groove and the second groove is a portion where each of the side walls of the frame member 2 and the groove 4A is projected to the inside of the side wall is provided, in the fitting groove provided between the portions corresponding projecting it may be. Even in such a configuration, occurs effect that transmission of the impact load through a portion fitting groove are in contact with each other person, it is possible to increase the bonding strength.
[0103]
　The length in the vehicle width direction of the first groove and the second groove (i.e., the depth of the grooves in the fitting groove) is a same toward the bottom portion from the opening of the frame member 2 and the groove 4A it may be. The length in the vehicle width direction of each of the fitting groove may vary over the said bottom portion from the opening. For example, as shown in FIGS. 7B and 7C, when each of said fitting groove protrudes outside the side wall, the length in the vehicle width direction of each of said fitting groove, the bottom of the opening it may decrease over the part. Such a configuration is advantageous in terms of formability.
[0104]
　(Contact member)
　will now be described an example in which the inside of the groove 4A of the vehicle front structure 1 according to the present embodiment provided contact member.
[0105]
　Inside the groove 4A, it may be in contact with the contact member is provided to the side walls of both of opposing grooves 4A (or inner surfaces of both opposite). That is, such abutment member inside the groove 4A, it may be provided to connect the side walls of both.
[0106]
　Figure 8A ~ 8C are diagrams showing a first example of the abutting member. 8A is a perspective view showing the schematic configuration of the vehicle front structure 1 including the contact member 90A, FIG. 8B is a side view showing the schematic configuration of the vehicle front structure 1 including the contact member 90A, Figure 8C is a cross-sectional view of the frame member 2 and the dash lower panel 3 of the vehicle front structure 1 including a contact member 90A. As shown in FIGS. 8A ~ Figure 8C, the contact member 90A may be provided to fill the space inside the groove 4A. In this case, the contact member 90A is provided in contact with each of the side walls 42 facing each other.
[0107]
　When the dash lower panel 3 is subjected to a collision load is likely to deform in the direction in which the side wall 22 and side walls 42 away from each other by such a load. Specifically, by such load, there is a case where the side wall 42 of the groove 4A collapses inward of the groove 4A. Then, breaking is apt to occur due to peeling mode of joint 6.
[0108]
　Therefore, the contact member 90A by providing the inside of the groove portion 4A, it is possible to suppress the leaning in the inside of the side wall 42 of the groove 4A. Therefore, it is possible to prevent breakage due to separation mode junction 6. Therefore, it is possible to increase the bonding strength between the frame member 2 and the dash lower panel 3.
[0109]
　Note that abutment member may be provided in contact to the side walls of both of opposing grooves 4A. Figure 8D is a diagram showing a second example of the abutting member. As shown in FIG. 8D, it may contact member 90B is provided with a connecting part to each other (upper part of FIG. 8D in the side wall 42) of the side wall 42 of the groove 4A in the cross-sectional view perpendicular to the longitudinal direction of the vehicle. Thus, the side wall 42 by the impact load is also act a force collapses inside the groove 4A, it is possible to suppress the leaning by the contact member 90B. Appropriately set according to the size and the contact position of the contact member inside the groove 4A in the cross-sectional view perpendicular to the longitudinal direction of the vehicle, the strength of the vehicle front structure 1 is required, stiffness, weight and manufacturing costs, etc. It may be.
[0110]
　Also, the installation position of the contact member in the vehicle length direction is not particularly limited. However, in order to more reliably prevent fracture due to peeling mode of the bonded part 6, the bonded part 6 in the longitudinal direction of the vehicle (e.g., joints 6a shown in FIG. 8B, 6b, 6c) corresponding to the position provided that it is preferred that the contact member is provided. The installation position and the installation of the abutment member in the vehicle length direction, the strength of the vehicle front structure 1 is required, the rigidity can be set appropriately according to the weight and manufacturing cost.
[0111]
　The contact member may be formed, for example, a resin such as foaming and curing the resin. The contact member may for example be formed by a metal strip or metal plate. Further, the contact member may not necessarily be fixed to the inner surface of the side wall 42 of the groove 4A. That is, the contact member may not be bonded to the inner surface of the side wall 42, it is sufficient to contact at least a portion of the inner surface of the side wall 42.
[0112]
　<< 3. Conclusion >>
　has been described in detail preferred embodiments of the present invention with reference to the accompanying drawings, the present invention is not limited to such an example. It would be appreciated by those skilled in the relevant field of technology of the present invention, within the scope of the technical idea described in the claims, it is intended to cover various changes and modifications , also such modifications are intended to fall within the technical scope of the present invention.
DESCRIPTION OF SYMBOLS
[0113]
　1 vehicle front structure
　2 frame member
　3 dash lower panel
　4 inclined wall
　4A groove
　4B intermediate portion
　4C skin portion
　5 the vertical wall
　6 joints
　7 resin structure
　8 sheet member
　21 the bottom wall
　22 side wall
　23 flange
　41 bottom wall
　42 side wall
　71 cylinder body
　72 top surface
　73 the base portion
　80A, 80B first groove
　81A, 81B second fitting groove
　90A, 90B contact member
　410 rigid regions

WE CLAIM

Provided in the vehicle length direction from the front box toward the cabin, and the framework member of the channel-shaped having a side wall,
　provided with a groove to be fitted to the inside of the frame member has side walls, the side walls of the groove and the side wall of the frame member There are joined, and the dash lower panel,
　comprising a vehicle front structure.
[Requested item 2]
　Side walls of said frame member and side walls of the grooves are joined by a joining portion,
　the joint is welded portion, the fastening portion is at least one of the bonding portion or the caulking joints, vehicle front according to claim 1 Construction.
[Requested item 3]
　The weld is formed in a linear shape continuous with bent in the vehicle length direction, the vehicle front structure of claim 2.
[Requested item 4]
　The weld is formed by laser welding and / or arc welding, the vehicle front structure according to claim 2 or 3.
[Requested item 5]
　The weld is formed by spot welding or arc spot welding, the vehicle front structure of claim 2.
[Requested item 6]
　At least a portion of the side wall of the groove, is provided first groove extending in the vehicle height direction,
　the side wall of said frame member, a second fitting groove corresponding to the first fitting groove is provided ,
　the first fitting groove is fitted into the second fitting groove, the vehicle front structure according to any one of claims 1 to 5.
[Requested item 7]
　Wherein the inner side of the groove, the abutting contact member is provided for each of the side walls facing each other of the groove, the vehicle front structure according to any one of claims 1 to 6.
[Requested item 8]
　The abutting member is formed of resin or metal, the vehicle front structure of claim 7.
[Requested item 9]
　The depth of the groove is 15mm or more, the vehicle front structure according to any one of claims 1-8.
[Requested item 10]
　The grooves are a pair arranged in the vehicle width direction in the dash lower panel,
　the an intermediate portion located between the pair of the groove in the dash lower panel, from one end to the other end in the vehicle width direction of the intermediate portion, wherein high rigidity region having a higher rigidity than the rigidity in the vehicle width direction outer side portion of the intermediate portion of the dash lower panel is provided, the vehicle front structure according to any one of claims 1-9.
[Requested item 11]
　The high thickness of the metal plate in the rigid region, the greater than the plate thickness of the metal plate in the portion other than the high rigidity region in dash lower panel, the vehicle front structure of claim 10.
[Requested item 12]
　The high stiffness in the metal plate in the area, the sheet member made of a resin is bonded, the vehicle front structure according to claim 10 or 11.
[Requested item 13]
　The metal plate in the high rigidity region includes a base connecting the cylindrical body of a plurality of the same height, the top surface respectively cover one end portion of the cylindrical body, and the respective other ends of the cylindrical body resin structure comprising the are joined through said top surface,
　said base portion of the resin structure is a sheet member made of a resin or paper is bonded, either of claims 10-12 1 vehicle front structure according to claim.
[Requested item 14]
　The high metal plate in the rigid region has an uneven shape, the vehicle front structure according to any one of claims 10-13.
[Requested item 15]
　The grooves are a pair arranged in the vehicle width direction in the dash lower panel,
　the an intermediate portion located between the pair of the groove in the dash lower panel, from one end to the other end in the vehicle width direction of the intermediate portion, wherein high strength region is provided with a higher tensile strength than the tensile strength of the vehicle width direction outer side portion of the intermediate portion of the dash lower panel, the vehicle front structure according to any one of claims 1 to 14.
[Requested item 16]
　The thickness of the dash lower panel is 1.0mm or more and 2.0mm or less, the vehicle front structure according to any one of claims 1 to 15.
[Requested item 17]
　The tensile strength of the dash lower panel is more than 340 MPa, the vehicle front structure according to any one of claims 1 to 16.
[Requested item 18]
　The frame member includes at least one of the front side member or floor member, the vehicle front structure according to any one of claims 1 to 17.