Vehicle bumper reinforcement structure

Abstract

A vehicle bumper reinforcement structure to increase energy absorption capacity is provided. The vehicle bumper reinforcement structure comprises a base member extending in the width direction of the vehicle that is attached to the vehicle at both width ends, and a first reinforcement member and a second reinforcement member attached to the base member at a width center of the vehicle. Widths of the reinforcement members are differentiated in such a manner to cause fracture of the base member at width ends of the reinforcement members by a predetermined collision impact applied to the width center of the base member.

Claims

1. A vehicle bumper reinforcement structure for a vehicle attached to a front side of the vehicle and extending in a width direction of the vehicle to be deformed by a collision impact to absorb collision energy, comprising: a base member extending in the width direction of the vehicle that is attached to the vehicle at both width ends; a first reinforcement member and a second reinforcement member respectively attached to the base member at a width center of the vehicle; and a bead formed by depressing a rear wall of the base member towards the front side of the vehicle, wherein widths of the first reinforcement member and the second reinforcement member are differentiated in such a manner as to cause fracture of the base member at width ends of the first reinforcement member and at width ends of the second reinforcement member by a predetermined collision impact applied to the width center of the base member, wherein the base member is shaped into a hollow structure, wherein at least one of the first reinforcement member and the second reinforcement member is attached to the rear wall of the base member, and wherein at least one of the first reinforcement member and the second reinforcement member has a protrusion inserted into the bead.

2. The vehicle bumper reinforcement structure as claimed in claim 1, wherein the widths of the first reinforcement member and the second reinforcement member are individually determined based on a bending moment applied to each width end of the reinforcement member by the collision impact to the width center of the base member, and a maximum allowable bending moment of the reinforcement member.

3. The vehicle bumper reinforcement structure as claimed in claim 1, wherein the widths of the first reinforcement member and the second reinforcement member are determined in such a manner to increase the maximum allowable bending moment of the base member stepwise from the width end of the base member to the width end of the second reinforcement member and from the width end of the base member to the width end of the first reinforcement member at a same increasing rate.

4. The vehicle bumper reinforcement structure as claimed in claim 1, wherein the first reinforcement member is attached to any of a front wall and a rear wall of the base member symmetrically across the width center of the vehicle, and wherein the second reinforcement member is attached to the other front wall or rear wall of the base member symmetrically across the width center of the vehicle.

5. The vehicle bumper reinforcement structure as claimed in claim 1, further comprising: a pair of side members extending from the width ends of the vehicle; and wherein the base member is connected to the vehicle through the side members at width ends.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Features, aspects, and advantages of exemplary embodiments of the present invention will become better understood with reference to the following description and accompanying drawings, which should not limit the invention in any way.

(2) FIG. 1 is a perspective view showing one example of the bumper assembly according to the preferred example;

(3) FIG. 2 is a cross-sectional view showing a cross-section of the bumper assembly in which an inner bracket and an outer plate are attached to the base member;

(4) FIG. 3 is a perspective view showing another example of the inner bracket;

(5) FIG. 4 is a graph indicating bending moment acting on the bumper assembly shown in FIG. 1;

(6) FIG. 5 is a graph indicating energy absorption of the bumper assembly shown in FIG. 1; and

(7) FIG. 6 is a schematic illustration showing an example of installation of the bumper assembly to the vehicle.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT(S)

(8) The bumper reinforcement structure is attached to the front or rear of a vehicle at both width ends, and adapted to be deformed inwardly by a collision impact to absorb kinetic energy. Referring now to FIG. 6, there is shown one example of a bumper assembly 1 attached to the front side of the vehicle. In FIG. 6, a pole barrier B is erected in front of the width center of the vehicle.

(9) In the example shown in FIG. 6, the bumper assembly 1 is connected to a front side of a frame of the vehicle at both width ends through a pair of side members 2. That is, a collision impact to the bumper assembly 1 propagates to the frame via the side members 2. As known in the conventional art, the frame is comprised of a plurality of members to dissipate the kinetic energy generated by collision impact. The side member 2 is formed of metal material having high rigidity, and shaped to have a cross-sectional shape possible to enhance buckling strength.

(10) Each width end of the bumper assembly 1 is attached individually to a leading end of the side member 2 by a bolt (not shown) so that a width center Ce of the bumper assembly 1 is deformed inwardly by a collision impact to absorb collision energy. Optionally, a conventional crush box (not shown) may be interposed between the leading end of the sider member 2 and the bumper assembly 1 to absorb kinetic energy generated by collision impact. Alternatively, a weakened portion may be formed in the leading end of the side member 2 instead of the crush box. In addition, a not shown ornamental bumper member is attached to the front side of the bumper assembly 1. As illustrated in FIG. 6, an engine room 3 is formed on the rear side of the bumper assembly 1, and an engine and a powertrain including a transmission and so on are arranged in the engine room 3.

(11) Here will be explained a structure of the bumper assembly 1 in more detail with reference to FIG. 1. As illustrated in FIG. 1, the bumper assembly 1 comprises a base member 4 connected to the side members 2 at its width ends, an inner bracket 5 attached to a back face of the base member 4 (facing to the engine room 3) at the width center Ce, and an outer plate 6 fitted onto the front face of the bumper assembly 1 at the width center Ce. Accordingly, the inner bracket 5 serves as the claimed first reinforcement member and the outer plate 6 serves as the claimed second reinforcement member to enhance bending strength of the bumper assembly 1. Here, the bending strength of the bumper assembly 1 can be calculated by dividing a maximum bending moment to cause fracture of the bumper assembly 1 by a cross-sectional coefficient of the bumper assembly 1.

(12) The base member 4 is formed by a roll-forming method using a metal sheet having a constant thickness. Specifically, in order to trim weight of the bumper assembly 1, the base member 4 is shaped into a hollow structure such as an arcuate rectangular pipe. In addition, in order to prevent a deformation of the base member 4 by a relatively small impact, a height center of a rear wall of the base member 4 facing to the vehicle body is depressed to form a laterally extending first bead 7. According to the preferred example, therefore, bending strength of the base member is constant in widthwise.

(13) Turning to FIG. 2, there is shown a cross-section of the bumper assembly 1 in which the inner bracket 5 and the outer plate 6 are attached to the base member 4. As illustrated in FIG. 1, the inner bracket 5 comprises a base plate 8 and a plurality of protrusions 9 at predetermined intervals. The protrusions 9 of the inner bracket 5 are inserted into the first bead 7 of the base member 4, and the base plate 8 of the inner bracket 5 is fixed to a back face of the base member 4 by a bolt or welding method. That is, a length of each of the protrusions 9 of the inner bracket 5 is substantially identical to a depth of the first bead 7 of the base member 4, and the inner bracket 5 is inserted into the first bead 7 symmetrically across the width center Ce.

(14) Thus, the bending strength of the base member 4 is enhanced at the width center Ce by the inner bracket 5. To this end, material, configuration, bending strength etc. of the inner bracket 5 may be altered arbitrarily according to need. Turning now to FIG. 3, there is shown another example of the inner bracket 5. According to the example shown in FIG. 3, the inner bracket 5 is formed of three rectangular aluminum pipes 10 individually formed by an extrusion method, the base plate 8 made of resin by an injection method, and a holder 11 integrated with the base plate 8 to bundle the aluminum pipes 10. The holder 11 thus holding the aluminum pipes 10 is inserted into the first bead 7, and the base plate is fixed to the back face of the base member 4 by a bolt.

(15) Turning back to FIG. 1, the above-explained outer plate 6 is fitted onto the front face of the base member 4 in a symmetrical manner across the width center Ce. This means that the bending strength of the outer plate 6 is homogeneous in both sides of the width center Ce. In addition, a length of the outer plate 6 in the width direction of the vehicle is longer than that of the inner bracket 5. Specifically, the outer plate 6 comprises a front wall 12 covering the front wall of the base member 4, an upper wall 13 formed by bending an upper portion of the front wall 12 toward the vehicle body, and a lower wall 14 formed by bending a lower portion of the front wall 12 toward the vehicle body. A leading end of the upper wall 13 is bent into L-shape to be fixed to the upper wall of the base member 4, and a leading of the lower wall 14 is also bent into L-shape to be fixed to the lower wall of the base member 4. In order to enhance bending strength of the outer plate 6, a height center of a front wall of the outer plate 6 is depressed toward the base member 4 to form a laterally extending second bead 15, and a bottom wall of the second bead 15 is brought into contact to the front wall of the base member 4. For example, the outer plate 6 thus structured may be formed by a press method and a roll method.

(16) The bending moment applied to the bumper assembly 1 by a maximum collision impact to the width center Ce is indicated in FIG. 4. In FIG. 4, the horizontal axis represents the width of the vehicle, and the vertical axis represents a magnitude of the bending moment. In FIG. 4, in addition, the maximum allowable bending moment at each point of the bumper assembly 1 is also indicated.

(17) As described, the bending strength of the base member 4 is homogeneous entirely widthwise. The outer plate 6 the bending strength thereof is also homogeneous entirely widthwise is attached to the front wall of the base member 4 in a symmetrical manner across the width center Ce so that the bending strength of the outer plate 6 is added to the base member 4 equally on both sides of the width center Ce. In addition, the inner bracket 5 the bending strength thereof is also homogeneous entirely widthwise is attached to the rear wall of the base member 4 in a symmetrical manner across the width center Ce so that the bending strength of the inner bracket 5 is further added to the base member 4 equally on both sides of the width center Ce. Since each of the base member 4, the inner bracket 5 and the outer plate 6 is individually formed into the symmetrical shape, a section modulus of the bumper assembly 1 at the intermediate portion where the inner bracket 5 and the outer plate 6 are attached to the base member 4 is entirely homogeneous widthwise. As indicated in FIG. 4, therefore, the maximum allowable bending moment of the bumper assembly 1 is increased stepwise toward the intermediate portion at which the bending strength thereof is enhanced by the inner bracket 5 and the outer plate 6. Here it is to be noted that only the left part of the bumper assembly 1 will be explained for the sake of convenience. In FIG. 4, specifically, c represents a width end point of the base member 4, b represents a width end point of the outer plate 6, and a represents a width end of the inner bracket 5. As can be seen from FIG. 4, the maximum allowable bending moment is increased stepwise at the points b and a.

(18) When the collision impact is applied to the bumper assembly 1 at the width center Ce, the bumper assembly 1 is subjected to the bending moment between the width end points c. The bending moment at each point of the bumper assembly 1 can be calculated by multiplying a distance from the width end point c by a load applied to the width center Ce. That is, the bending moment acting on the bumper assembly 1 is increased proportionally from the width end point c toward the width center Ce.

(19) Specifically, the bumper assembly 1 is bent at a point where the bending moment acting thereon exceeds the maximum allowable bending moment. As shown in FIG. 4, when the collision impact is applied to the width center Ce of the bumper assembly 1, the bumper assembly 1 will be subjected to the bending moment greater than the maximum allowable bending moment thereof at the point a and the point b, but the bending moment applied to the point c will not exceed the maximum allowable bending moment. That is, when the collision impact is applied to the bumper assembly 1 at the width center Ce, the bumper assembly is fractured at the point a and the point b.

(20) That is, the most significant collision impact is applied to the width center Ce of the bumper assembly 1 and hence the width center Ce is subjected to the bending moment most significantly. Such bending moment is lightened proportionally toward the both width end points c. In FIG. 4, specifically, the slopes extending downwardly on both sides of the width center Ce get steeper with an increase in the collision impact applied to the width center Ce. As described, the bumper assembly 1 is fractured at the width end points a of the inner bracket 5 shown in FIG. 4 and at the width end points b of the outer plate 6 shown in FIG. 4 by the collision impact to the width center Ce. According to the preferred example, widths of the inner bracket 5 and the outer plate 6 are determined to cause fracture at the width end points a and b by a target maximum collision impact to the width center Ce at a peak of the slope representing the bending moment in FIG. 4. Specifically, as indicated in FIG. 4, the widths of the inner bracket 5 and the outer plate 6 are determined in such a manner to increase the maximum allowable bending moment of the bumper assembly 1 stepwise from the width end point c to the width end point and b and from the width end point c to the width end point and a at a same increasing rate. In other words, an inclination of the slope indicating the maximum bending moment of the bumper assembly 1 is identical between the points c and b and between the points c and a.

(21) Thus, according to the preferred example, the bumper assembly 1 is fractured by the target maximum collision impact to the width center Ce at the width end points a and b. Energy absorption of the bumper assembly in this situation is schematically indicated in FIG. 5. In FIG. 5, the vertical axis represents deformation of the bumper assembly toward the vehicle body, the horizontal axis represents the width of the vehicle, the solid polygonal line represents a situation in which the bumper assembly 1 is fractured at both width end points a and b of the inner bracket 5 and the outer plate 6, the dashed lines represent a situation in which the bumper assembly 1 is fractured only at the width end points a of the inner bracket 5, and the dashed-dotted line represents a situation in which the bumper assembly 1 is fractured at the width center Ce. Specifically, energy absorption of the bumper assembly 1 can be calculated by multiplying the deformation of the fractured point by the reaction itself. That is, given that the reaction of the bumper assembly 1 is constant, the energy absorption of the bumper assembly 1 can be increased by increasing an area in FIG. 5 enclosed by any of the above-mentioned lines and the horizontal axis. As indicated in FIG. 5, the energy absorption capacity of the bumper assembly 1 is increased when fractured at both width end points a and b of the inner bracket 5 and the outer plate 6 in the amount of hatched area, in comparison with that of the case in which the bumper assembly 1 is fractured only at the width end points a of the inner bracket 5.

(22) According to the preferred example, the energy absorption capacity of the bumper assembly 1 can be increased by thus attaching the inner bracket 5 and the outer plate 6 to the base member 4 having the above-explained widths.

(23) Specifically, both of the inner bracket 5 and the outer plate 6 are attached to the base member 4 symmetrically across the width center Ce of the vehicle to increase the energy absorption capacity of the bumper assembly 1 as well as to prevent fracture of the bumper assembly 1 at the width center Ce. That is, the bending strength of the bumper assembly 1 can be increased without increasing the bending strength of the base member 4. For this reason, a smaller base member 4 can be employed to downsize the bumper assembly 1.

(24) It is to be understood that various modifications may made in the bumper assembly within the spirit of the present invention. For example, more than three reinforcement members may be attached to the base member 4 while adjusting widths and bending strength thereof in the above-explained manner. In addition, configurations of the inner bracket 5 and the outer plate 6 may be altered according to need. For example, the inner bracket 5 may also be formed longer than the outer plate 6 widthwise. Further, the bracket 5 may be attached to the front wall of the base member 4 while attaching the plate 6 to the rear wall of the base member 4.