JP3216528B2 - Body side structure - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a vehicle body side structure, and more particularly to a vehicle body side structure in a vehicle such as an automobile.

[0002]

2. Description of the Related Art Conventionally, in a vehicle such as an automobile, there is known a vehicle body side structure in which rigidity of a vehicle body side is increased to efficiently absorb impact immediately after a side collision. No. 17253.

As shown in FIG. 11, in this vehicle body side structure, a rear end portion 72A of a door beam 72 provided in a side door 70 is positioned at a center when viewed from the vehicle body side (the direction of arrow S in FIG. 11). It overlaps with the pillar 74 and the door beam 7
A bracket 76 having a U-shape in a plan view is fixed to the rear end 72A of the second member 72 toward the center pillar 74. Therefore, immediately after the side collision, the bracket 76 is attached to the door inner panel 7.
8 is in contact with the center pillar 74.

[0004]

However, in this vehicle body side structure, an input load (arrow G in FIG. 11) acting on the center pillar 74 via the door beam 72 and the bracket 76 at the time of a side collision is applied to the center pillar 74. It is offset from the shear center P of the input section to the front of the vehicle. For this reason, the center pillar 74
In addition, since a moment in the direction of arrow M in FIG. 11 is generated and the center pillar 74 is torsionally deformed, it is difficult to withstand a high input load.

The present invention has been made in consideration of the above circumstances, and has as its object to obtain a vehicle body side structure capable of suppressing torsional deformation of a center pillar and withstanding a higher input load.

[0006]

Means for Solving the Problems The present onset light of claim 1, wherein
The vehicle body side structure further comprising input load supporting means for aligning an input load center to the center pillar at the time of a side collision with a shear center of an input section of the center pillar.
The load support means is designed to reduce the input load in the event of a side collision from an oblique direction.
Disperse from the path facing each other across the shear center of the
Of the shear center of the center pillar
A first input load support member located outside the vehicle width direction;
1 Prescribed on the opposite side of the door hinge to the input load support member
A second input load supporting member arranged at a distance of
It is characterized by comprising .

Therefore, at the time of a side collision, the input load acting on the center pillar from an oblique direction is located across the shear center of the center pillar.
Arranged so that input is distributed from paths facing each other
Located outside the center pillar shear center in the vehicle width direction
A first input load supporting member and a first input load supporting member
Disposed of at a predetermined distance on the other side of the door hinges for
The second input load supporting member is transmitted to the center pillar. At this time, the center of the input load to the center pillar coincides with the shear center of the cross section of the input portion of the center pillar. For this reason, no moment is generated in the center pillar, and the torsional deformation of the center pillar can be suppressed.

[0008] According to a second aspect of the invention, arranged an input load supporting means for matching the input load center to center pillar of a side collision to a shear center of the input unit section of the center pillar
In the vehicle body side structure, the input load supporting means, the side
The path of the input load to the center pillar at the time of collision is
The outer center in the vehicle width direction is formed in an arc shape centered on the center of the center pillar so that the center of the center pillar coincides with the center of the center pillar.

Therefore, at the time of a side collision, the input load acting on the center pillar from an oblique direction is applied to the center pillar at the time of a side collision.
Path of force load coincides with the center of shear of center pillar
As shown in the figure, the outer part in the vehicle width direction is
Is the input load support member in an arc shape centered on the center
It is transmitted to Luo center pillar. At this time, go to the center pillar
Of the input load of the center pillar coincides with the shear center of the input section of the center pillar. For this reason, no moment is generated in the center pillar, and the torsional deformation of the center pillar can be suppressed.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A comparative example of a vehicle body side structure according to the present invention will be described with reference to FIGS.

In the drawings, an arrow FR indicates a forward direction of the vehicle, an arrow UP indicates an upward direction of the vehicle, and an arrow IN indicates an inward direction of the vehicle width.

As shown in FIG. 3, a center pillar 10 of the vehicle body of the present comparative example has a center pillar outer panel 12 forming the vehicle outer portion of the center pillar 10 and a center pillar inner panel forming the vehicle inner portion of the center pillar 10. And a closed cross-sectional structure along the vehicle up-down direction.

An opening 16 for a front side door is formed in front of the center pillar 10. The opening 16 for the front side door is formed in the front side door 1.
8 makes it possible to close. Also, center pillar 1
An opening 20 for a rear side door is formed at the rear of 0, and the opening 20 for the rear side door can be closed by a rear side door 22.

As shown in FIG. 1, the rear side door 22
Is a rear side door outer panel 24 forming the vehicle outer side of the rear side door 22, and a rearant side door 18
Side door inner panel 2 that forms the inside of the vehicle
6 and the front edge 24A of the rear side door outer panel 24 and the rear side door inner panel 2
6 is joined to the front end 26A by hemming.

A front side wall portion 26B of the rear side door inner panel 26 is fixed to a door side mounting portion 30 of a rear door hinge 28 constituting a part of the input load supporting means. Is connected to a pillar-side mounting portion 34 by a shaft 32.

The cross section of the center pillar outer panel 12 as viewed from above the vehicle has a hat shape with an opening directed toward the inside of the vehicle, and a front flange 12 formed at the end of the opening.
A and the rear flange 12B are joined to the front edge 14A and the rear edge 14B of the center pillar inner panel 14, respectively.

A pillar-side mounting portion 34 of the rear door hinge 28 is fixed to a rear portion of the outer wall 12C in the vehicle width direction of the center pillar outer panel 12.
At the front end of 2C, a protruding portion 12D protruding outward in the vehicle width direction is provided.
Are formed.

The front side door 18 includes a front side door outer panel 38 forming the vehicle outside portion of the front side door 18 and a front side door inner panel 40 forming the vehicle inside portion of the front side door 18.
The rear edge 38A of the front side door outer panel 38 and the rear edge 40A of the front side door inner panel 40 are joined by hemming.

In the front side door 18, a bracket 42 as an input load supporting member constituting a part of the input load supporting means is provided.

As shown in FIG. 3, the bracket 42
Is formed in a box shape with an opening directed inward in the vehicle width direction, and a flange 42A formed at an end of the opening is joined to a rear portion 40B of the front side door inner panel 40.

As shown in FIG. 1, the bracket 42
The bracket 4 is disposed at a position facing the convex portion 12D of the center pillar outer panel 12 along the vehicle width direction.
2 and a distance L1 (L1) between the portion of the front side door 18 on which the center panel 2 is disposed and the convex portion 12D of the center pillar outer panel 12.
1 = AB) is substantially equal to the distance L2 (L1 = DC) between the rear door hinge 28 and the rear side door outer panel 24. The deformation strength of the bracket 42 is also substantially equal to the deformation strength of the rear door hinge 28.

The front side door 18 is attached to a front pillar (not shown) via a door hinge.

Next, the operation of this comparative example will be described.

In the vehicle body side structure of this comparative example , as shown in FIG. 2, when the opposing vehicle 60 collides with the side of the vehicle body from the outside in the vehicle width direction, the input load to the center pillar 10 is reduced by the front side door 18. The rear portion, ie, the bracket 42, and the front portion of the rear side door 22, ie, the rear door hinge 28, cause two input loads (FIG. 2) to be input from a path facing each other across the shear center N of the input section of the center pillar 10. Arrows F1 and F2), and the input load center (the arrow F in FIG. 2) of these two input loads coincides with the shear center N.

Therefore, the center pillar 10 has the shear center N
No peripheral moment is generated, and the torsional deformation of the center pillar 10 in plan view can be suppressed. For this reason, FIG.
The input load of the comparative example shown by the solid line becomes higher than the input load of the conventional structure shown by the broken line (see FIG. 11), this comparative
The examples can withstand higher input loads than conventional structures.

Further, in the vehicle body side structure of the comparative example , FIG.
As shown in (A), the rocker 11 in which the lower end of the center pillar 10 is connected and the front cross member 13 and the center cross member 15 are connected also undergoes bending deformation indicated by a two-dot chain line during a side collision. I do.

At this time, also in the rocker 11, the input load (the arrow 1 / 2.F in FIG. 5A) is dispersed. Therefore, as shown in FIG. 5B, the input load, the reaction force F3 of the front cross member 13 and the center cross member 15
The maximum bending moment K1 applied to the rocker 11 caused by the reaction force F4 is X (X = X) compared with the maximum bending moment K2 when the input load is not dispersed (in the case of the conventional structure), as indicated by the two-dot chain line arrow F. K1-K2). As a result, if there is no change in the bending strength of the rocker 11 between the present comparative example and the conventional example , the present comparative example shows the conventional (K1 + X)
/ K1 input load.

In the vehicle body side structure of this comparative example , the bracket 42 is provided as an input load supporting member. Instead, as shown in FIG. 6, the rear portion 50A of the door beam 50 is used as the input load supporting member. May be arranged so as to overlap the center pillar 10 in a vehicle side view.
In this case, the deformation strength and the vehicle width direction dimension of the rear portion 50A of the door beam 50 are set similarly to the bracket 42 of the comparative example . Therefore, in this configuration, it is not necessary to add the bracket 42, and the number of parts and the number of assembly operations can be reduced.

Next, a first embodiment of the vehicle body side structure according to the present invention will be described with reference to FIGS.

The same members as those of the comparative example are denoted by the same reference numerals, and description thereof will be omitted.

[0031] As shown in FIG. 7, according to the vehicle side structure of the first embodiment, two brackets 51 as an input load bearing member to the rear of the front door 18 (second input load supporting
Holding member) and a bracket 52 ( first input load supporting member), and the two brackets 51 and 52 are joined to the rear portion 40 </ b> B of the front side door inner panel 40. The bracket 52 on the vehicle rear side is located outside the shear center N of the input section of the center pillar 10 in the vehicle width direction.

The brackets 51 and 52 are arranged at a predetermined distance in the front-rear direction of the vehicle. As shown in FIG. The load is controlled by the brackets 51 and 52.
The input is distributed and input from two paths facing each other across the shear center N of the input section of the center pillar 10, and the center of the two input loads (arrows F1 and F2 in FIG. 8) (arrows in FIG. 8) F) coincides with the shear center N.

Therefore, in the vehicle body side structure according to the first embodiment, as shown in FIG. 8, even if the opponent vehicle 60 collides with the side surface of the vehicle body from diagonally forward, as shown in FIG.
The input load center (arrow F in FIG. 8) coincides with the shear center N. Therefore, no moment about the shear center N is generated in the center pillar 10, so that the torsional deformation in plan view can be suppressed, and a higher input load can be endured.

In the first embodiment, as shown by a two-dot chain line in FIG. 8, the same effect can be obtained even when the opponent vehicle 60 collides with the side surface of the vehicle body diagonally from behind.

Next, a description will be given of a second embodiment of the vehicle side structure of the present invention according to FIGS.

The same members as those of the comparative example are denoted by the same reference numerals, and description thereof will be omitted.

As shown in FIG. 9, in the vehicle body side structure according to the second embodiment, a bracket 54 as an input load support member is provided at the rear of the front door 18, and the bracket 54 is connected to the front side door. Inner panel 4
0 at the rear portion 40B. The vehicle width direction outer portion 54A of the bracket 54 has a circular arc shape in which the rear end side of the vehicle projects outward from the vehicle front end side in the vehicle width direction in plan view.

Therefore, as shown in FIG. 10, when the rear portion of the front door 18 is deformed at the time of a side collision, the outer portion 54A of the bracket 54 in the vehicle width direction and the outer portion of the rear door hinge 28 in the vehicle width direction are seen in plan view. But the center pillar 1
The input section of zero is located on an arc 56 centered on the shear center N.

Next, the operation of the second embodiment will be described.

In the second embodiment, as shown in FIG. 10, when the opponent vehicle 60 collides with the side surface of the vehicle body from an oblique front side, the vehicle width direction outer portion 54A of the bracket 54 and the vehicle width of the rear door hinge 28 Center pillar 1
0 is located on the arc 56 centered on the shear center N of the input section. Therefore, the center pillar 1
The path of the input load to zero (arrow F in FIG. 10) coincides with the shear center N of the input section of the center pillar 10. For this reason, no moment about the shear center N is generated in the center pillar 10, so that the torsional deformation in plan view can be suppressed, and a higher input load can be endured.

In the second embodiment, even when the opponent vehicle collides with the side of the vehicle body from an obliquely rear side, the load input to the center pillar 10 via the rear door hinge 28 (the imaginary line in FIG. 10). Arrow F) coincides with the shear center N. Therefore, the center pillar 10 has the shear center N
No peripheral moment is generated, torsional deformation in plan view can be suppressed, and a higher input load can be endured.

In the above, the present invention has been described in detail with respect to a specific embodiment. However, the present invention is not limited to such an embodiment, and various other embodiments are within the scope of the present invention. It is clear to a person skilled in the art that is possible. For example, in each of the above-described embodiments, the rear door hinge 28 is used as a part of the input load supporting means. However, instead of the rear door hinge 28, another input load supporting means such as a bracket may be used.

[0043]

[Effect of the Invention The present onset light according to claim 1 is disposed an input load supporting means for matching the input load center to center pillar of a side collision to a shear center of the input unit section of the center pillar
The input load support means in the
The input load at the time of side collision from the direction is the shear center of the center pillar
Is distributed and input from the path facing each other
Is located outside the center pillar shear center in the vehicle width direction.
For the first input load supporting member and the first input load supporting member
To the opposite side of the door hinge with a predetermined distance
A second input load bearing member, since made of, obliquely
In the event of a side collision, the torsional deformation of the center pillar is suppressed,
It has an excellent effect that it can withstand higher input loads.

[0044] According to a second aspect of the invention, arranged an input load supporting means for matching the input load center to center pillar of a side collision to a shear center of the input unit section of the center pillar
In the vehicle body side structure, the input load supporting means, side impact
Path of the input load to the center pillar
The outer part in the vehicle width direction is aligned with the center of the
It has an arc shape centered on the center pillar shear center.
Therefore, there is an excellent effect that the torsional deformation of the center pillar can be suppressed and a higher input load can be endured even in the case of a side collision from an oblique direction.

[Brief description of the drawings]

FIG. 1 is a plan sectional view showing a vehicle body side structure according to a comparative example of the present invention on the right side of the vehicle.

FIG. 2 is a plan cross-sectional view showing a state of a side collision of a vehicle body side structure according to a comparative example of the present invention on the right side of the vehicle.

FIG. 3 is a perspective view of a vehicle body side structure according to a comparative example of the present invention, which is a partial cross section shown on the left side of the vehicle, viewed from diagonally outside the vehicle front;

FIG. 4 is a graph showing a relationship between an amount of deformation of a vehicle body side structure and a load.

FIG. 5A is a schematic plan view showing a rocker near a center pillar of a vehicle body side structure according to a comparative example of the present invention,
(B) is a diagram showing a bending moment of a rocker portion of a vehicle body side structure according to a comparative example of the present invention.

FIG. 6 is a perspective view of a vehicle body side structure according to a modified example of the comparative example of the present invention, which is a partial cross-section shown on the left side of the vehicle, viewed from diagonally outside front of the vehicle.

FIG. 7 is a cross-sectional plan view showing the vehicle body side structure according to the first embodiment of the present invention on the right side of the vehicle.

FIG. 8 is a plan cross-sectional view showing a state of a side collision of the vehicle body side structure according to the first embodiment of the present invention on the right side of the vehicle.

FIG. 9 is a plan sectional view showing a vehicle body side structure according to a second embodiment of the present invention on the right side of the vehicle.

FIG. 10 is a plan sectional view showing a state of a side collision of a vehicle body side structure according to a second embodiment of the present invention on the right side of the vehicle.

FIG. 11 is a plan sectional view showing a vehicle body side structure according to a conventional embodiment on the left side of the vehicle.

[Explanation of symbols]

 Reference Signs List 10 center pillar 12 center pillar outer panel 12D projection of center pillar outer panel 18 front side door 22 rear side door 28 rear door hinge (part of input load support means) 38 front side door outer panel 40 front side door inner panel 51 bracket (input load support) 52) Bracket (input load supporting member) 54 Bracket (input load supporting member)

Claims (2)

(57) [Claims] 1. A vehicle body side structure provided with input load supporting means for aligning the center of an input load to a center pillar at the time of a side collision with the shear center of a cross section of an input portion of the center pillar.
Thus, the input load supporting means is provided in the case of a side collision from an oblique direction.
Input loads face each other across the center pillar shear center
In front of the center pillar so that the input is distributed from the route
First input load support located outside the shear center in the vehicle width direction
Member and a door hinge with respect to the first input load support member.
A second input load support disposed at a predetermined distance from the other side;
And a holding member . 2. A vehicle body side structure provided with input load support means for aligning the center of an input load to a center pillar at the time of a side collision with a shear center of a cross section of an input portion of the center pillar.
The input load supporting means is connected to the center pillar at the time of a side collision.
The input load path is centered on the center pillar shear center.
Matching manner, the car body side structure you characterized in that the vehicle transverse direction outer side portion is an arc shape centered on the shear centers of the center pillar and.