JP2006207725A - Shock absorbing member - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a shock absorbing member applicable to a crush box constituting an automobile body adopting a so-called short-nose design or to a front side member, e.g, having a shorter total length for more efficiently absorbing impact energy. <P>SOLUTION: The shock absorbing member comprises cylinder bodies 5-8 which are buckled to absorb the impact energy by receiving impact load ranging from one end in the axial direction to a direction approximately parallel to the axial direction. The cross section of each of the cylinder bodies 5-8 in at least part in the axial direction is shaped as a closed cross section with a plurality of peaks. No flange is provided outside the closed cross section. The basic cross section of the maximum contour obtained by linearly connecting parts of the plurality of peaks to each other has a protruded polygonal shape out of which at least one side is wholly formed non-linear to pass through the protruded polygonal shape. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an impact absorbing member. Specifically, the present invention relates to an impact absorbing member that can absorb impact energy generated when a vehicle such as an automobile collides.

  As is well known, the body of many current automobiles is constituted by a monocoque body that supports the load by the entire body integrated with the frame in order to achieve both weight reduction and high rigidity. The body of an automobile must have a function of suppressing damage to the functions of the vehicle and protecting the lives of passengers in the cabin in the event of a vehicle collision. In order to reduce the damage to the cabin as much as possible by absorbing the impact energy at the time of vehicle collision and reducing the impact force on the cabin, it is effective to preferentially crush spaces other than the cabin, such as the engine room and trunk room It is. Because of these safety requirements, impacts to actively absorb impact energy by collapsing when an impact load at the time of a collision is applied to an appropriate location such as the front, rear, or side of the vehicle body. An absorbent member is provided. Conventionally, as such an impact absorbing member, a front side member, a side sill, a rear side member, and the like are known.

  In recent years, a shock absorbing member having a short length of about 200 mm, which is called a crash box, is attached to the front end of the front side member by appropriate means such as fastening or welding, thereby improving the safety of the vehicle body and the vehicle body caused by a light collision. Attempts have been made to reduce the repair cost by substantially eliminating the damage. The crash box is preferentially buckled in an accordion shape in the axial direction by an impact load applied in a direction substantially parallel to the axial direction (in this specification, the longitudinal direction of the shock absorbing member). It is a member for absorbing impact energy by deformation.

  Specifically, the shock absorbing performance generally required for the shock absorbing member is that when an impact load is applied in the axial direction, it is repeatedly buckled in the axial direction to deform into a bellows shape, The average load at the time is high, and further, the maximum reaction force generated at the time of crushing is suppressed within a range that does not destroy other automobile body members disposed in the vicinity of the shock absorbing member.

  Furthermore, recent automobiles tend to use a so-called short nose design in which the length of the engine room located in front of the cabin is shortened in order to ensure sufficient cabin space with emphasis on comfort. It is in. For this reason, it has been demanded that the impact energy can be sufficiently absorbed with a shorter overall length (that is, a deformation stroke) even for the front side member and the crash box attached to the front end of the front side member. In other words, the impact absorbing member is required to effectively absorb the impact energy by buckling and deforming in a bellows shape more efficiently even with a shorter overall length than before.

  Many materials and shapes for improving the shock absorbing performance of the shock absorbing member have been developed so far. A shock absorbing member that has been widely used in general is, for example, by spot welding a back plate via a flange provided at the edge of a hat-shaped cross-sectional member as disclosed in Patent Document 1. A box-shaped member having a square cross section is used. In the present specification, the “flange” means a flat plate-like portion protruding outward from the outline in the cross section.

  On the other hand, in Patent Document 2, the cross-sectional shape from one end to the other end is continuously changed from a convex polygon having a quadrangle or more to another convex polygon having more sides than the convex polygon. There has been disclosed an invention relating to an impact absorbing member that has a closed cross-sectional structure that changes, and that has improved impact absorption while reducing the initial load of collision. In the present specification, the “convex polygon” means a polygon having all inner angles of less than 180 degrees.

Patent Document 3 discloses an invention relating to an impact absorbing member having a partition inside and having a contour cross-sectional shape of a convex polygon.
Further, in Patent Document 4, an impact with increased strength is obtained by forming a groove portion having a substantially right isosceles triangle shape toward the inside at four corners including four apexes of a material having a quadrangular cross section. An invention relating to an absorbent member is disclosed.

  Further, in Patent Document 5, a bead extending in the axial direction is formed on a side surface of a front side frame having a hat-shaped cross section having a flange, whereby the front side frame when an impact load is applied is formed. An invention for suppressing bending is disclosed.

JP-A-8-128487 Japanese Patent Laid-Open No. 9-277753 JP 2003-48569 A JP 2002-284033 A JP-A-8-108863

  However, according to any of these conventional inventions, the impact energy can be absorbed more efficiently with a shorter overall length than before, so that, for example, a vehicle body of a so-called short nose design is adopted. It is impossible to provide an impact absorbing member that can be sufficiently applied to a crash box, a front side member, and the like.

  That is, the impact absorbing member according to the invention disclosed in Patent Document 1 is difficult to repeatedly buckle and deform in the axial direction when an impact load is applied in a direction substantially parallel to the axial direction. There is a risk that it will not deform. In addition, the use of the shock absorbing member having a convex polygonal cross-sectional shape such as a simple regular polygon according to the invention disclosed in Patent Document 1 is the cross-sectional shape of the shock absorbing member used in the body of an automobile. It is difficult in the first place because it is flat in most cases.

  Moreover, in the impact-absorbing member according to the invention disclosed in Patent Document 2, the cross-sectional shape thereof gradually changes over substantially the entire length. For this reason, depending on the position in the axial direction, there is a high possibility that the cross-sectional shape is inevitably stable and not suitable for buckling deformation. For this reason, when the impact load is applied in a direction substantially parallel to the axial direction, it is difficult for the impact absorbing member to be stably buckled and deformed in the axial direction, and may not be deformed into a bellows shape.

  Further, in the impact absorbing member according to the invention disclosed in Patent Document 3, the strength of the portion provided with the partition wall is excessively higher than the strength of the portion not provided with the partition wall, and an impact load is applied. As the crushing progresses, the partition provided inside is folded and rigidized, and the folded and rigidized partition becomes resistance to the progress of buckling deformation of the shock absorbing member and reaches a predetermined crushing stroke. Before the buckling deformation of the shock absorbing member is completed, the buckling deformation of the shock absorbing member is constrained and the destruction of other members disposed in the vicinity of the shock absorbing member is started (in this specification, “ There is a risk of producing “bottom”. Thus, when the impact load is applied in a direction substantially parallel to the axial direction, the impact absorbing member cannot be repeatedly and stably buckled in the axial direction, and may not be deformed into a bellows shape. Furthermore, since the increase in the weight of the shock absorbing member cannot be avoided by the amount of the partition wall provided, the present invention goes against the demand for reducing the weight of the automobile body.

  Further, in the impact absorbing member according to the invention disclosed in Patent Document 4, since the corner portion having high strength is further processed to provide the notch portion, the strength of the notch portion is excessively increased and stabilized. You may not be able to buckle. Therefore, in this shock absorbing member, similarly to the shock absorbing member disclosed in Patent Document 3, there is a possibility that the amount of shock energy absorbed may be insufficient and the bottoming may occur at an early stage. When a load is applied in a direction parallel to the direction, it cannot repeatedly buckle stably in the axial direction, and may not be deformed into a bellows shape.

  Furthermore, the shock absorbing member according to the invention disclosed in Patent Document 5 has a hat-shaped cross-sectional shape having a flange. For this reason, according to the present invention, it is considered that the bending due to the applied impact load can surely be suppressed. However, according to the present invention, when an impact load is applied in a direction parallel to the axial direction, it cannot repeatedly buckle stably in the axial direction and may not be deformed into a bellows shape.

  Accordingly, an object of the present invention is to absorb impact energy more efficiently with a shorter overall length than before, so that, for example, a crash box or a front that constitutes a vehicle body of a car adopting a so-called short nose design. An object of the present invention is to provide an impact absorbing member that can be applied to a side member or the like.

  In other words, the object of the present invention is to increase the amount of displacement (stroke) until bottoming occurs when crushing progresses when an impact load is applied. It is providing the impact-absorbing member which can ensure.

The present inventors have made various studies in view of the problems of the above-described conventional techniques, and as a result, obtained the new and important findings (I) to (III) listed below, and completed the present invention.
(I) The cross-sectional shape of the cylindrical body constituting the shock absorbing member is a closed cross section having a plurality of vertices, the flange is not provided outside the closed cross section, and a part of the plurality of vertices is straight. The basic cross section consisting of the maximum contour obtained by connecting is a convex polygon, and the entire area of at least one side of the convex polygon is formed in a non-straight line passing through the inside of the convex polygon; By doing so, it is possible to ensure a long amount of displacement (stroke) until bottoming occurs, thereby stably securing the amount of impact energy absorbed.

(II) When this convex polygon has 2n vertices (n is a natural number of 2 or more), every other n sides of the 2n sides are inside the convex polygon. By making it consist of non-straight lines that pass through, it is possible to form buckling wrinkles that are repeatedly generated with the progress of crushing so that they are always directed in alternate directions between adjacent sides, thereby achieving bottoming To further increase the amount of shock energy absorbed by improving the crushing stroke. And (III) In these cases, the non-straight line is an arc, and the length (l) of the arc and the length (L) of one side are 1.005 ≦ (l / L) ≦ 1.207. By satisfying the relationship, it is possible to further secure the amount of displacement (stroke) until bottoming occurs.

  The present invention is an impact-absorbing member comprising a cylindrical body for absorbing impact energy by buckling with an impact load applied from one end in the axial direction in a direction substantially parallel to the axial direction. The cross-sectional shape of the cylindrical body in at least a part of the axial direction is a closed cross section having a plurality of vertices, the flange is not provided outside the closed cross section, and a part of the plurality of vertices is a straight line. The basic cross section consisting of the maximum contour obtained by connecting is a convex polygon, and the entire area of at least one side of the convex polygon is formed in a non-linear line passing through the inside of the convex polygon. This is a characteristic shock absorbing member.

  In the shock absorbing member according to the present invention, the convex polygon has 2n vertices (n is a natural number of 2 or more), and at least one of the sides of the convex polygon is out of 2n sides. It is desirable that there are n sides every other.

  In these shock absorbing members according to the present invention, the non-straight line is an arc, and the length (l) of the arc and the length (L) of at least one side are 1.005 ≦ (l / L It is desirable to satisfy the relationship of ≦ 1.207.

  Further, these impact absorbing members according to the present invention are deformed into a bellows shape by buckling under an impact load.

  According to the present invention, impact energy can be absorbed more efficiently with a shorter overall length than before, for example, shaft collapse under the condition of a collision speed of 64 km / h on an impact absorbing member having a length of 200 mm is bottomed out. When the FEM numerical analysis is performed until an increase in load occurs due to the fact that (stroke to bottom / total length of impact absorbing member) × 100 is 85% or more, the impact absorbing member according to the present invention is, for example, so-called It can be sufficiently applied to a crash box, a front side member, and the like that constitute a car body of a short nose design.

  In other words, according to the present invention, it is possible to lengthen the amount of displacement (stroke) until bottoming occurs when crushing progresses by being loaded with an impact load, thereby stabilizing the amount of shock energy absorbed. Thus, an impact absorbing member that can be secured can be provided.

Hereinafter, the best mode for carrying out an impact absorbing member according to the present invention will be described in detail with reference to the accompanying drawings.
The cylindrical body constituting the shock absorbing member of the present embodiment is a closed cross section in which at least a part of the cross section in the axial direction has a plurality of vertices, and a flange is not provided outside the closed cross section. The basic cross section consisting of the maximum contour obtained by connecting a part of the vertices with a straight line is a convex polygon, and the entire area of at least one side of the convex polygon is inside the convex polygon. It is formed in a non-straight line that passes through. Therefore, this cylindrical body will be described.

  This cylindrical body is for absorbing impact energy by buckling with an impact load applied from one end portion in the axial direction toward a direction substantially parallel to the axial direction. This cylindrical body is configured to have a closed cross section having a plurality of apexes as a hollow cylindrical body made of, for example, a high-tensile steel plate.

Further, this cylinder does not include a flange toward the outside, that is, a flat plate-like portion protruding outward from the contour in the cross section. The reason for this will be explained.
For example, an impact absorbing member provided with a cylindrical body having a flange facing outward, which serves as a joining margin when joining two or more members formed by press molding or the like, for example, by spot welding, and the like. The behavior of the crushing when an impact load was applied to each of the impact absorbing members provided with the cylinders not to be analyzed was analyzed by FEM numerical analysis.

  FIG. 1 is an explanatory view showing how a shock absorbing member having a quadrangular cross section is collapsed by FEM numerical analysis, and FIG. 1 (a) is a hat-shaped cross section having flanges 1a and 1b facing outward. FIG. 1 (b) shows a shock absorbing member 2 having a closed cross-sectional cylinder having a rectangular cross-sectional shape without a flange facing outward. Show.

  As shown in FIG. 1A, when the shock absorbing member 1 has flanges 1a and 1b directed outward, the buckling generated in the shock absorbing member 1 loaded with a shock load becomes extremely unstable, and the shock absorbing member 1 absorbs the shock. The member 1 is bent in the longitudinal direction as schematically shown by an arrow in FIG. Since this bending reduces the deformation amount of the bellows-like buckling, the impact energy cannot be absorbed sufficiently.

  On the other hand, as shown in FIG. 1 (b), if the shock absorbing member 2 does not have an outward flange, the shock absorbing member 2 is schematically shown by an arrow in FIG. 1 (b) without bending in the longitudinal direction. As shown in the figure, since it buckles and deforms in a bellows shape throughout the axial direction, it is possible to sufficiently absorb impact energy. In this FEM numerical analysis, the shock absorbing members 1 and 2 having a quadrangular cross-sectional shape are taken as an example. However, an impact absorbing member having a polygonal cross-sectional shape other than a quadrangle is also subjected to an impact load in the longitudinal direction. In this case, if the cylinder has a flange facing outward, the buckling that occurs in the shock absorbing member loaded with an impact load becomes extremely unstable, and the shock absorbing member Bends in the longitudinal direction along the way.

  In this way, when the cylindrical body has a flange directed to the outside, the amount of bellows-like buckling deformation is reduced by bending in the longitudinal direction that occurs during the crushing, and the impact energy can be sufficiently absorbed. Therefore, in the present embodiment, the cylindrical body constituting the impact absorbing member is limited to a closed cross section that does not include an outward flange.

  In addition, the cylindrical body has a convex polygonal basic cross section formed by connecting a part of a plurality of vertices with a straight line, and at least one of the sides of the convex polygon. Is formed in a non-straight line passing through the inside of the convex polygon. This point will be described.

First, “convex polygon” means a polygon having all inner angles of less than 180 °, as in the mathematical definition.
When conceptually explaining the impact absorbing member of the present embodiment, at least one plane of a material made of a cylindrical body having a cross-sectional shape consisting of a convex polygon having a plurality of apexes is partially or entirely in the axial direction. In the region, it is replaced with a non-planar shape such as a curved surface that is convex toward the inside of the cylinder. For this reason, the impact-absorbing member of the present embodiment has a basic section of a convex polygon having a maximum contour obtained by connecting a part of a plurality of vertices with straight lines.

  Further, the convex polygon is not less than a convex quadrilateral, preferably not less than a convex hexagon and not more than a convex dodecagon, assuming that it is applied as a normal shock absorbing member mounted on an automobile body. That is, the amount of impact energy absorbed by the impact absorbing member is determined by the buckling strength of the ridgeline of the cylinder, and the greater the number of ridgelines, that is, the greater the number of vertices in the cross section, the more advantageous. From such a viewpoint, the convex polygon which is the basic cross-sectional shape is a convex quadrangle or more, preferably a convex hexagon or more. On the other hand, if it exceeds the convex hexagon, the cross-sectional shape approaches a circle, and the angle of the inner angle of each ridge line part constituting the convex polygon (the angle of the inner angle of each vertex in the cross-section) becomes large. As the angle increases, before the ridgelines of the cylindrical body begin to buckle, the ridgelines and the sides sandwiching them are deflected as a whole, and the crushing behavior becomes unstable. For this reason, when the basic cross-sectional shape is not less than a convex heptagon, the crushing behavior in the entire axial direction of the shock absorbing member becomes unstable and is not practical.

  In addition, the convex polygon that is the basic cross-sectional shape does not need to be a regular convex polygon such as a regular octagon or a regular dodecagon, for example, a flat shape that is frequently used as a cross-sectional shape of an actual shock absorbing member. It may be a convex polygon with a cross-sectional shape. That is, in general, it is rare that a regular polygon can be applied as the cross-sectional shape of the shock-absorbing member due to restrictions on the space where the shock-absorbing member is installed (for example, engine compartment or floor). In many cases, it is unavoidable. In the case of a convex polygon having a flat cross-sectional shape, the ratio of the long side to the short side length in the rectangle having the shortest short side length among the rectangles circumscribing the contour in the cross section of the shock absorbing member ( The flatness defined as (long side length / short side length) is preferably 1.0 or more and 3.5 or less. If the flatness exceeds 3.5, buckling may become unstable and the amount of shock absorption may be insufficient, and the maximum reaction force generated in the cylindrical body at the initial stage of crushing exceeds the strength of other members. This is because other members may be damaged.

  In this case, the length of each side constituting the convex polygonal cross-sectional shape is preferably 4 t (mm) or more and 65 t (mm) or less when the thickness of the material is t (mm). . If a side shorter than 4 t (mm) is present, the side rigidity becomes too high, and it is difficult to obtain a behavior of buckling and collapsing into a bellows while repeatedly generating wrinkles in the entire area of the shock absorbing member in the axial direction. In addition, if there is a side longer than 65 t (mm), the stiffness of the side becomes too weak, and the side that bends greatly during crushing causes bending (bending deformation) in the entire axial direction of the shock absorbing member. This is because the amount of impact energy absorbed decreases.

  Next, as an example of an impact absorbing member including a cylindrical body having a cross-sectional shape composed of a convex polygon having a plurality of vertices, a cross-sectional shape composed of a regular octagon having a size inscribed in a circle having a diameter of 120 mm and the outside Using an impact absorbing member (axial length: 200 mm) having a cylindrical body that does not have a flange toward the shaft, axial collapse under the condition of a collision speed of 64 km / h until a sudden increase in load due to bottoming occurs Analysis was performed by performing FEM numerical analysis. FIG. 2 is a graph showing the analysis result (displacement-load curve) of this axial crushing.

  As shown in the graph of FIG. 2, a load vibration in which the load fluctuates periodically occurs in the impact absorbing member at the time of shaft collapse (refer to the range of 0 to 170 mm in FIG. 2). Here, since the area between the displacement-load curve and the horizontal axis in the graph of FIG. 2 indicates the amount of impact energy absorbed by the impact absorbing member, the load may have a high value and a small amount of variation. This means that the impact absorbing member efficiently absorbs impact energy at the time of collision. That is, it is effective that the displacement-load curve in the graph of FIG. 2 is as flat as possible and exists in the region of a high load value.

  However, as shown in the graph of FIG. 2, the impact absorbing member having a cylindrical body that has a cross-sectional shape made of a convex polygon and does not have an outward flange has a very large amount of fluctuation in periodic load. Therefore, it is not possible to ensure a sufficient amount of absorption of impact energy until a predetermined amount of destruction.

  In this example, if the load suddenly rises to 400 kN is regarded as the occurrence of bottoming, the stroke to the bottoming is 168.8 mm, which is only 83.05% of the total length of the shock absorbing member. .

  Therefore, as a result of examining in detail the situation in which the load drops when the shaft is collapsed and the situation in which bottoming occurs, the peak with the higher load (positions A to E in FIG. 2) has a convex shape that is the cross-sectional shape of the cylindrical body. The apex of the square is generated by the yield strength when plastic buckling deformation occurs. On the other hand, a sudden drop in load after the ridge portion buckles (AA ′, BB ′, CC in FIG. 2). It has been found that ', DD' and EE ') occur because the plane portion existing between the two ridge lines bends and deforms.

  For this reason, the shock absorbing member of the present embodiment does not have an outward flange, has a basic cross-sectional shape made up of a convex polygon having a plurality of vertices in at least part of the axial direction, and has a convex shape. By constructing the cylindrical body so that the entire area of at least one side of the square has a non-linear shape, the cross-sectional peripheral length of the plane portion existing between the two vertices is increased. Increases the crushing load when the part is bent. For this reason, according to the impact absorbing member of the present embodiment, it is possible to suppress the amount of load drop during axial crushing and to increase the amount of impact energy absorbed at a predetermined amount of crushing.

  However, in general, when a cylinder having a convex polygonal cross section is deformed at the time of axial collapse due to an impact load, an initial elastic deflection occurs in the cross section of the cylinder at the moment when the impact load is input. The stress which tries to inflate each side of this to the outer side arises. At this time, if the side of the convex polygon described above is formed in a non-linear shape that passes through the outside of the convex polygon, the amount of elastic deflection that bulges the side outward increases, and the axial direction increases. It becomes difficult to stably buckle and deform in a bellows shape.

  Therefore, in the present embodiment, the entire region of at least one of the sides of the convex polygon is formed to be a non-straight line passing through the inside of the convex polygon. As a result, the amount of elastic deflection toward the outside of the convex polygon at the initial stage of axial crushing is increased while increasing the crushing load at the time of bending of the flat part by increasing the cross-sectional circumference of the flat part that may cause bending during axial crushing. Since the increase in the pressure can be suppressed, the cylindrical body can be buckled and deformed in an accordion shape in the entire axial direction, so that the impact energy can be sufficiently absorbed.

  The side formed to be a non-straight line passing through the inside of the convex polygon may be at least one side of the sides of the convex polygon. For example, all the sides may be used, as described later, every other side in the circumferential direction of the convex polygon, or only a specific side.

  Moreover, if the side formed so as to be a non-straight line passing through the inside of the convex polygon is arranged point-symmetrically with respect to the center of the convex polygon, it is possible to prevent falling in one direction with respect to the impact load from the front. Therefore, it is desirable. That is, the cross-sectional shape of the cylindrical body in the present embodiment has a cross-sectional shape in which the cylindrical body is pointed with respect to the inner center point when an impact load parallel to the axial direction is applied from the front. It is desirable. In this case, as described later, the convex polygon is an even-numbered polygon, and the entire area of every other n sides of all sides is formed in a non-straight line passing through the inside of the convex polygon. It is desirable.

  On the other hand, when it is assumed that an impact load is applied to the impact absorbing member in an oblique direction, such as offset collision and oblique projection, which are particularly important in recent years, the convex polygon is not only an even number but also an odd number. The sides that are formed in a non-straight line may be adjacent to each other on the side on which the impact load is first applied, and may be continuously present on the other side. There may be no side. That is, in the region given the shape that is convex inward, the initial deflection is preferentially generated, so it becomes easier to generate the wrinkle first, and the side on which the impact force first acts is preferentially collapsed, and the impact energy By starting this absorption, stable crushing can be realized in the entire axial direction of the shock absorbing member.

  Furthermore, the non-linear line passing through the inside of the convex polygon may be constituted by a single curve having a single radius of curvature, such as a circle or an ellipse, but a composite of a plurality of curves having different radii of curvature. You may comprise by a curve. However, if it is composed of a line that combines a straight line and a curve, both ends of this straight line become new vertices and become the base point of buckling, so this ridgeline generates a new resistance force against crushing and the crushing behavior May be unstable, which is not desirable.

  As described above, the impact absorbing member of the present embodiment has a closed cross section in which at least a part of the cross section in the axial direction has a plurality of vertices, and does not include a flange outside the closed cross section. The basic cross section consisting of the maximum outline obtained by connecting a part of the vertices with a straight line is a convex polygon, and the entire area of at least one side of the convex polygon passes through the inside of the convex polygon. Since it is provided with a cylindrical body having the characteristic of being formed in a non-linear manner, it is possible to ensure a long amount of displacement (stroke) until bottoming occurs when crushing proceeds by being loaded with an impact load, Thereby, the stable shock absorption amount can be ensured.

Next, the suitable aspect of the impact-absorbing member which concerns on this Embodiment is demonstrated.
In the impact absorbing member of the present embodiment described above, the convex polygon which is the basic cross-sectional shape of the cylinder has 2n vertices (n is a natural number of 2 or more) and one of 2n sides. It is desirable that the entire area of each of every n sides be formed in a non-straight line passing through the inside of the convex polygon. Therefore, this point will be described.

In general, when a member that is crushed by an impact load in the axial direction is deformed, phenomena (i) to (v) listed below occur.
(I) In a region close to the input end side of the impact load, compressive strain in the axial direction is accumulated on each ridge line constituting the cylindrical body.

(Ii) At the same time, in the cross section of the region where the compressive strain is accumulated, the deflection toward the inner side or the outer side in the cross section occurs at the side portion between the ridge lines.
(Iii) The ridge line portion in which the compressive strain is accumulated causes plastic buckling, and then a wrinkle that protrudes in the deflection direction occurs at the side portion between each ridge line.

  (Iv) After the formation of the wrinkle is completed and the upper and lower sides of the wrinkle contact (close the mouth), a region different from the item (i) above, specifically, the ridgeline, for the next occurrence of buckling In the region existing on the side opposite to the input end side, the axial compressive strain is accumulated on the ridgeline as in the above item (i).

(V) Thereafter, the same phenomenon is repeated to sequentially repeat buckling.
As a typical example of the deformation behavior in the axial crushing of a general regular convex polygon, FIG. 3 shows the shape during the crushing of the impact absorbing members 3 and 4 having cylindrical bodies having regular octagonal and regular dodecagonal cross sections. This is schematically shown by FEM analysis.

As understood from FIG. 3, the characteristics of the crushing behavior of a general regular convex polygon are the following two points.
(A) The direction of wrinkles generated on the sides between the ridge lines is alternately generated in the order of the inner side of the cross section and the outer side of the cross section in the axial direction of the cylinder.
(B) The direction of wrinkles generated on the sides between the ridge lines is generated in the same direction with respect to the circumferential direction of the cylinder.

  Here, the wrinkles generated in the flat portion of the cylindrical body due to the plastic buckling deformation that occurs during the axial collapse of the cylindrical body generally means that the buckling occurs in a shorter cycle as it is formed more finely. However, if the fine wrinkles that are formed are in contact with each other and are continuously connected in the crushing direction, the region where these wrinkles are in contact with each other will not be further buckled and deformed. A sudden increase in load occurs at an early stage, that is, bottoming out. Furthermore, as described with reference to FIG. 3, in the shock absorbing member including a cylindrical body having a cross-sectional shape made of a 2n polygon such as a regular octagon, for example, the buckling wrinkle formed in a certain flat portion is Since buckling wrinkles formed in adjacent flat portions come into contact with each other and restrain each other, bottoming is further easily generated.

  Here, from the characteristics described in the above item (a), once the formation direction of the wrinkle is determined on the collision end side, the subsequent side portions are crushed while alternately replacing the inside and outside of the wrinkle. If the direction of the first wrinkle generated in step 2 can be controlled in the opposite direction at the adjacent sides, the wrinkles of the adjacent sides are different in the inner and outer directions, so that the behavior of contacting and restraining in the circumferential direction can be reduced. , The occurrence of bottoming can be delayed.

  Therefore, in the present embodiment, when the convex polygon that is the basic cross-sectional shape of the cylinder has 2n vertices (n is a natural number of 2 or more), every other 2n sides. By forming the entire area of each of the n sides in a non-straight line passing through the inside of the convex polygon, wrinkles generated in adjacent sides of the convex polygon in the cross section are formed in opposite directions. In addition, for example, the buckling wrinkle of a certain flat surface portion is formed toward the center of the cross section, and the buckling wrinkle of the flat surface portion adjacent to the flat surface portion is formed toward the outer side of the cross section, which is the opposite direction. Control the crush deformation mode.

  This eliminates the interference of wrinkles formed adjacently in the circumferential direction, can extend the stroke until the wrinkles that have been folded thinly in the axial direction and overlapped become rigid, and early occurrence of bottoming Since this can be prevented, it is possible to secure a longer displacement (stroke) until bottoming occurs when crushing progresses when an impact load is applied.

  FIG. 4 is an explanatory view showing the cross-sectional shape of the cylindrical bodies 5 to 8 whose basic cross-sectional shape is a regular octagon or a regular dodecagon, and FIG. 4 (a) is a cross-sectional shape of the cylindrical body 5. FIG. 4 (b) shows a case of a regular octagon having sides 5a to 5h, and FIG. 4 (b) shows every other four of the eight sides 6a to 6h of the cylinder 6 whose basic cross-sectional shape is a regular octagon. FIG. 4C shows a case where the entire areas of the sides 6b, 6d, 6f, and 6h are each formed in a non-straight line (arc) passing through the inside of the convex polygon, and FIG. FIG. 4 (d) shows a case where each of the twelve sides 8a to 8l of the cylindrical body whose basic cross-sectional shape is a regular dodecagon. A case is shown in which each of the six sides 8a, 8c, 8e, 8g, 8i, and 8k is formed as a non-straight line (arc) passing through the inside of the convex polygon.

  As shown in FIG. 4 (a) or FIG. 4 (c), when the cross-sectional shape of the cylinder is a 2n polygon (regular octagon or regular dodecagon), the direction of the wrinkle generated at the start of crushing is any side. In 5a to 5h and 7a to 7l, the octagonal shape or the regular dodecagonal shape is outward and the same. For this reason, the buckling wrinkles that are repeatedly generated as the crushing progresses are always in the same direction between adjacent sides, so that the buckling wrinkles that are formed in a certain plane portion are adjacent to the adjacent plane portions. Since the buckling wrinkles formed on each other come into contact with each other and restrain each other, bottoming is more likely to occur. Specifically, the stroke up to the bottom / the total length of the shock absorbing member) × 100 is only about 83%.

  On the other hand, as shown in FIG. 4B or FIG. 4D, every other side of the cylindrical body whose basic cross-sectional shape is a 2n polygon (regular octagon or regular dodecagon). If the entire area of each side is formed in a non-linear line (arc) passing through the inside of the convex polygon, the direction of wrinkles generated at the start of crushing is non-linear part 6b, 6d, 6f, 6h or 8a, 8c, 8e, 8g. 8i and 8k are inward, whereas the straight portions 6a, 6c, 6e and 6g or 8b, 8d, 8f, 8h, 8j and 8l are outward. For this reason, since buckling wrinkles that are repeatedly generated with the progress of crushing are always alternated between adjacent sides, the seats formed on a certain flat surface portion (for example, 6a, 8a) The buckling wrinkles are eliminated from contacting and restraining the buckling wrinkles formed on the adjacent flat portions (for example, (6b, 6h), (8b, 8l)), and bottoming is less likely to occur. As a result, the crushing stroke to the bottom can be made larger than that shown in FIG. 4A or 4C, and the amount of impact energy absorbed can be improved. Specifically, the stroke to the bottom / the total length of the shock absorbing member) × 100 shows a very good value of 85% or more.

FIG. 5 shows a load-displacement curve (dashed line) at the time of axial collapse of the cylinder 5 shown in FIG. 4 (a) and a load-displacement curve (solid line) at the time of axial collapse of the cylinder 6 shown in FIG. 4 (b). It is a graph which shows.
As described above, when the load suddenly rises to 400 kN is regarded as occurrence of bottoming, the stroke until the step of the cylindrical body 5 shown in FIG. / Total length of impact absorbing member) × 100 is about 83% at most, whereas the stroke until the step of the cylinder 6 shown in FIG. 4B is 172.2 mm, and the stroke / impact absorption up to the bottom is shown. (Member total length) × 100 is greatly improved to 85% or more.

In addition, it can be seen that the cylindrical body 6 is greatly improved in the sudden drop of the load described with reference to the graph of FIG.
Furthermore, in the impact absorbing member of the present embodiment, forming the sides of the convex polygon in the basic cross section into a non-linear line passing through the inside of the convex polygon, for example, an arc, increases the manufacturing cost of the cylinder. It is the most effective for suppressing. That is, the non-straight line bulging into the convex polygon is an arc, and the length (l) of the arc and the length (L) of one side are 1.005 ≦ (l / L). It is desirable to satisfy the relationship of ≦ 1.207. This point will be described.

  FEM numerical value of axial crushing with a 590 MPa class high-strength steel plate with a thickness of 1.6 mm as a target material when the convex polygonal side which is the basic cross section of a 200 mm long cylindrical body is a non-linear arc. Analysis was conducted to examine the curvature of the arc to be given to the original side, which can stabilize the buckling and ensure the stroke to the bottom. Axial crushing collapsed until bottoming occurred at a speed of 64 km / h.

  In addition, as shown in FIG. 4 mentioned above as a typical convex polygon, two types of regular octagon and regular dodecagon are selected, and the diameter of the circle inscribed by the regular octagon and regular dodecagon is 120 mm. It was.

  And about the thing whose convex polygon is a regular octagon, the non-linear part of the circular arc was formed every other side of eight, and the axial crushing analysis was performed by changing the curvature of the circular arc variously. Similarly, in the case where the convex polygon is a regular dodecagon, the non-linear portion of the arc is formed on every other side of the twelve sides, and the axial crush analysis is performed by variously changing the curvature of the arc. went.

  Results of axial crush analysis (relationship between the ratio (l / L) of the length of the arc portion (l) and the length of one side (L) to the unit circumference long bottom EA and bottom stroke S) Are collectively shown in a graph in FIG. FIG. 6 (a) shows the relationship between the ratio (l / L) of 0.95 or more and 1.05 or less and the relationship between the unit circumference base EA and FIG. 6 (b) is a regular octagon. 6 shows the relationship between the ratio (l / L) of 0.9 to 1.5 and the relationship between the unit circumference bottom EA, and FIG. 6C shows the ratio (l / L) for a regular dodecagon. ) Shows a relationship between a range of 0.9 to 1.5 and the relationship between the unit circumference bottom EA. 6A to 6C, the large plot indicates the bottomed stroke S, and the small plot indicates the unit circumferential long bottom EA.

  As shown in the graph of FIG. 6A, when the ratio of the regular octagon (l / L) is 1.005 or more, the absorption amount of impact energy increases rapidly, and the stroke amount to the bottom is greatly increased. Can be increased. On the other hand, as shown in the graph of FIG. 6B, when the ratio of the regular octagon (l / L) exceeds 1.207, the amount of shock energy absorbed decreases and the stroke to the bottom also decreases. To do. When the ratio (l / L) exceeds 1.207, the ridgeline of the cylindrical body that is the ends of the non-linear arc is sharpened, the strength of the ridgeline becomes excessively strong, and it can be bent without repeatedly buckling. While it becomes easy to generate | occur | produce, since the circumferential direction length of a circular arc becomes large and the volume of each wrinkle increases, it becomes easy to produce bottoming at an early stage. However, in the regular dodecagon, as shown in FIG. 6C, the stroke amount until the bottom is reached when the ratio (l / L) is 1.0, which is sufficiently effective.

  As described above, when the regular octagon and the regular dodecagon are studied, it is understood that the ratio (l / L) is preferably 1.005 or more and 1.207 or less, but the wrinkles generated at the edges between the ridge lines. The generation condition is not dependent on the number of ridge lines in the cross section, but is determined for each side by the shape of each side and the buckling behavior of the ridge lines at both ends thereof. The same holds for the convex hexagon.

  For this reason, the non-straight line bulging into the inside of the convex polygon is an arc, and the ratio (l / L) between the length (l) of the arc portion and the length (L) of one side is 1. It is desirable that it is 0.005 or more and 1.207 or less. From the same viewpoint, the ratio (l / L) is desirably 1.01 or more and 1.200 or less.

  Thus, in the shock absorbing member of the present embodiment, the cross-sectional shape of the cylindrical body in at least a part in the axial direction is a closed cross section having a plurality of vertices, and no flange is provided outside the closed cross section. In addition, the basic cross section formed of the maximum contour obtained by connecting 2n (n is a natural number of 2 or more) of a plurality of vertices with a straight line is a convex polygon, and at least one of the convex polygons The whole area of the side is formed in an arc passing through the inside of the convex polygon, and the length (l) of the arc part and the length (L) of at least one side are 1.005 ≦ (l / L). It is an impact-absorbing member provided with the cylinder which satisfies the relationship of <= 1.207. When an impact load is applied from one end portion in the axial direction toward a direction substantially parallel to the axial direction, the cylindrical body sufficiently absorbs impact energy by buckling. As a result, the impact energy can be absorbed more efficiently with a shorter overall length than before, for example, shaft collapse under the condition of a collision speed of 64 km / h on an impact absorbing member having a length of 200 mm is caused by bottoming. When FEM numerical analysis is performed until an increase in load occurs (stroke to bottom / total length of impact absorbing member) × 100 is 85% or more, the impact absorbing member of this embodiment is, for example, a so-called The present invention can also be applied to a crash box, a front side member, and the like that constitute a car body of a car adopting a short nose design.

  Although the impact absorbing member of the present embodiment is configured as described above, the impact absorbing member may further have a crush bead at a portion between ridge lines, or may be subjected to drilling or the like. It is also effective to further increase the strength by performing post-treatment such as induction hardening or laser hardening after the assembly is completed.

  Thus, according to the present embodiment, it is possible to lengthen the displacement (stroke) until the bottoming occurs when the crushing progresses by being loaded with an impact load. It is possible to provide an impact absorbing member capable of ensuring the above.

Furthermore, the present invention will be described more specifically with reference to examples.
The effect of the impact absorbing member according to the present invention was verified by performing a collision test described below.

  A high-tensile steel plate having a thickness of 590 MPa and a thickness of 1.6 mm was used as the material, and a weight weighing 200 kgf was dropped freely from a height of 16.1 m and was made to collide with the shock absorbing member in the axial direction at 64 km / h.

At this time, the length of each of the shock absorbing members was 200 mm, and the cross-sectional shape of each shock absorbing member was constant without changing over the entire length.
And the comparative example 1 provided with the cylinder which has the cross-sectional shape of the regular octagon (one side length 45.9mm) inscribed in the circle of diameter 120mm, and the regular dodecagon (length of one side) inscribed in the circle of diameter 120mm. Comparison with Comparative Example 2 including a cylinder having a cross-sectional shape of 31 mm) and Example 1 in which every other regular octagonal side of Comparative Example 1 is an arc with a radius of 60 mm that protrudes toward the inside. Example 2 in which every other octagonal side of Example 1 has an arc with a radius of 25 mm that is convex toward the inside, and every other regular dodecagon side of Comparative Example 2 is convex toward the inside Example 3 which is an arc with a radius of 26 mm that is convex toward the inner side, and an arc with a radius of 17 mm that is convex toward the inner side every other side of the regular dodecagon of Comparative Example 2 Example 4 with a stroke with a bottom and a bottom Was compared with the absorption amount of impact energy at the time came.

  Table 1 shows the initial maximum load and the amount of absorption of impact energy up to 140 mm for Comparative Examples 1 and 2 and Examples 1 to 4.

  In Examples 2 and 4 shown in Table 1, the impact absorbing member deformed to swell greatly like a drum in the middle of crushing, and the crushing load was reduced.

  Further, in Examples 1 and 3, wrinkles between adjacent sides in the circumferential direction are sequentially generated in a staggered direction, and the crushing stroke is increased as compared with Comparative Examples 1 and 2 which are the original polygons. Increased energy absorption.

By comparing Comparative Examples 1 and 2 in Table 1 with Examples 1 to 4, the cross-sectional shape of the cylindrical body constituting the shock absorbing member is a closed cross section having a plurality of vertices, and the outside of this closed cross section The basic cross section consisting of the maximum contour obtained by connecting some of the vertices with straight lines is a convex polygon, and the entire area of at least one side of the convex polygon By forming a non-linear structure that passes through the inside of this convex polygon, it is possible to secure a long displacement amount (stroke) until bottoming occurs, thereby reducing the amount of shock energy absorbed. It can be seen that it can be secured stably.

  Further, by comparing Comparative Examples 1 and 2 with Examples 1 and 3 in Table 1, when the convex polygon that is the basic cross-sectional shape has 2n vertices (n is a natural number of 2 or more), The buckling is repeatedly generated as the crushing progresses by making the entire area of every second n side out of 2n sides consist of non-linear lines passing through the inside of the convex polygon. It can be seen that the wrinkles can always be formed so as to be directed alternately in adjacent sides, thereby further improving the crushing stroke to the bottom and further increasing the amount of impact energy absorbed.

  By comparing Comparative Examples 1 and 2 in Table 1 with Examples 1 to 4, the entire area of at least one of the sides of the convex polygon is a non-linear arc, and the length of this arc portion ( l) and the length of one side (L) satisfy the relationship of 1.005 ≦ (l / L) ≦ 1.207, thereby further ensuring the amount of displacement (stroke) until bottoming occurs. I understand.

It is explanatory drawing which shows the mode of the crushing of the impact-absorbing member which has a square cross section by FEM numerical analysis, FIG.1 (a) shows an impact-absorbing member provided with the cylinder which comprises the flange toward the exterior, FIG. (B) shows the impact-absorbing member provided with the cylinder which does not comprise the flange toward the outside. It is a graph which shows the FEM numerical analysis result (displacement-load curve) of axial crushing. It is explanatory drawing which shows typically the shape in the middle of crushing of the impact-absorbing member provided with the cylinder which has a cross section of a regular octagon and a regular dodecagon by FEM analysis. FIG. 4A is an explanatory diagram showing a cross-sectional shape of a cylinder whose basic cross-sectional shape is a regular octagon or a dodecagon, and FIG. 4A shows a case where the cross-sectional shape of the cylinder is a regular octagon, 4 (b) is a non-straight line (arc) passing through the inside of the convex polygon through every other four sides of the eight sides of the cylinder whose basic cross-sectional shape is a regular octagon. 4 (c) shows the case where the cross-sectional shape of the cylinder is a regular dodecagon, and FIG. 4 (d) shows the cylinder whose basic cross-sectional shape is a regular dodecagon. The case where the entire area of every other six sides of the twelve sides of the body is formed in a non-straight line (arc) passing through the inside of the convex polygon is shown. A load-displacement curve (dashed line) at the time of axial crushing of a cylinder having a regular octagonal cross-sectional shape shown in FIG. 4 (a), and a cylinder whose basic cross-sectional shape is a regular octagon shown in FIG. 4 (b). A load-displacement curve (solid line) at the time of axial crushing of a cylindrical body in which every other four sides of the eight sides are formed in a non-straight line (arc) passing through the inside of the convex polygon ). Graph showing the results of axial crush analysis (relationship between the ratio (l / L) of the length (l) of the arc portion and the length of one side (L) and the unit circumference base EA) 6 (a) shows the relationship between the ratio (l / L) of 0.95 to 1.05 and the relationship between the unit circumference bottom EA and the regular octagon, FIG. 6 (b). Indicates the relationship between the ratio (l / L) of 0.9 to 1.5 for the regular octagon and the relationship between the unit circumference long bottom EA, and FIG. 6C shows the ratio for the regular dodecagon ( 1 / L) shows the relationship between the range of 0.9 to 1.5 and the relationship between the unit circumferential length bottom EA.

Explanation of symbols

1-8 Shock absorbing member (cylinder)
5a-5h, 6a-6h, 7a-7l, 8a-8l sides

Claims (3)

  An impact-absorbing member comprising a cylindrical body for absorbing impact energy by buckling with an impact load applied from one end in the axial direction in a direction substantially parallel to the axial direction, wherein the axial direction The cross-sectional shape of the cylindrical body in at least a part of the cylinder is a closed section having a plurality of vertices, the flange is not provided outside the closed section, and a part of the plurality of vertices is connected by a straight line. The basic cross section consisting of the maximum contour obtained in this way is a convex polygon, and the entire area of at least one side of the convex polygon is formed in a non-straight line passing through the inside of the convex polygon. Shock absorbing member.   2. The convex polygon has 2n vertices (n is a natural number of 2 or more), and the at least one side is every other n sides out of 2n sides. Shock absorbing member.   The non-straight line is an arc, and the length (l) of the arc portion and the length (L) of the at least one side satisfy the relationship of 1.005 ≦ (l / L) ≦ 1.207. The impact-absorbing member according to claim 1 or 2.

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