Technical field [0001]The present invention relates to a shock absorbing component used in the transport of automobiles. BACKGROUND [0002]Safety standards of transportation has increased year by year, at the time of collision, even if the damage to the function of transportation, to protect an occupant of the cabin has become the most important. Therefore, the ambient cabin frame, absorbs collision energy, in order to mitigate the impact transmitted to the cabin, progress in the application of high-strength steel sheet, the improvement of collision safety is achieved. [0003] 　Furthermore, in recent years, not collision safety alone, in consideration of repairability after the collision, the vehicle type to absorb the impact is increasing with replaceable shock absorbing component such as a crash box. The shock absorbing component, the front and rear surfaces of the cabin, the shock-absorbing direction of the shock absorbing component is mounted so that the longitudinal direction of the vehicle by the shock absorbing component is crushed deformed shock absorbing direction during a collision, the impact energy Absorb. Therefore, to the shock absorbing component is required the following characteristics. [1] has high impact energy absorption capability. [2] for an automobile collision is not always parallel to the shock-absorbing direction of the shock absorbing component in a direction intersecting the shock absorbing direction (e.g., oblique angle of intersection of 10 degrees with the shock-absorbing direction) impact load from the load even if it is, it can absorb the collision energy. [3] In order to ensure the fuel efficiency, it is lightweight. [0004] 　Shape of the shock absorbing parts, Society of Automotive Engineers of Japan Papers, no. 7 (1974), p. As described in 60), a hollow shape such as a box-shaped closed cross-section with a welded back plate via a flange provided on the part of the hat-shaped cross-sectional shape (see FIG. 1E) is generally . [0005] 　The deformation behavior when the impact absorbing part absorbs the impact energy will be described with reference to FIGS 1A ~ FIG 1H. Here, FIGS. 1A ~ 1D are perspective views of before deformation to the first buckling deformation completed. The shock absorbing direction as referred to herein, when the ridge line direction of the shock absorbing component 1 is placed so that the vertical direction and the direction perpendicular to the installation surface 4 (arrow P2 in Fig. 1A). Further, FIG. 1E ~ FIG 1G shows the shape of the horizontal cross-section perpendicular to the shock-absorbing direction in each deformation (arrow P2). The dotted line in FIG. 1B shows the deformation behavior of the central portion of the side surface 2 immediately after the shock is applied, the dotted line in FIGS. 1F and 1G is a horizontal cross-section before deformation. [0006] 　When an impact load P1 is applied to the impact absorbing direction (arrow P2), first, rigid small at the center portion of the side surface 2 (the plane, the direction penetrating vertically) plane direction of bulges (or concave) periodic elastic deformation occurs (period H) (solid line a dotted line in FIG. 1B and FIG. 1F). On the other hand, a large ridge 3 of rigid, compressed and deformed in the height direction. Here, the elastic deformation is caused by side, Timoshenko al, seat 屈理 theory, Corona Publishing, 1971, p221-225 (hereinafter, simply referred to as. "Timoshenko") simply supported elastic buckling of the plate peripheral as shown in and it is equivalent, from the variational principle, the seat 屈波 length H is equal to the plate width (aspect 2 of the width (distance between the edge line)). [0007] 　Further, when the deformation in the impact absorbing direction (arrow P2) progresses, the elastic deformation of the side surface 2 is spread in the direction of the ridge 3 from the central portion, and also increases the deformation of the out-of-plane direction. On the other hand, even ridge 3, the amount of compressive strain is increased. The out-of-plane deformation of the side surface 2 upon reaching the ridge 3, and stress concentration in the highest position the elastic deformation amount, broken edges 3 may occur. And in both sides 2 and ridgelines 3 starts the local plastic buckling (wrinkle-like deformation) (dotted lines and Fig. 1G in Fig 1C). Further deformation progresses, the ridge line 3, the side surface 2 is contacted completely broken, buckling deformation of the first cycle is completed (FIG. 1D). Crushing displacement at this time is consistent with the period H. The same buckling deformation in a different cross-section begins. By repeating the above-described buckling deformation, shock absorbing component 1, crushed deformed like bellows (accordion-like) as shown in FIG. 1H, absorbing the impact energy has been known (the Society of Automotive Engineers Proceedings). [0008] 　Incidentally, since, in the present specification, H seat 屈波 length during crushing deformation, shock-absorbing direction to the deformation to deform crushing the axial collapse in a bellows shape as shown in FIG. 6, was cut vertically in the shock absorbing direction to define the cross-section and part cross-section. [0009] 　Next, the relationship between the shock-absorbing direction of displacement and load at this time is described with reference to FIG. Impact load is applied folded edges 3 occurs (FIGS. 1B corresponds to the deformation between FIG. 1C) until the load is increased (Fig. 2, O → A), the maximum load Pm during the initial buckling deformation 1 reaches the to. Then, when starting the plastic buckling edges 3, since the amount of energy that can be absorbed by the edge line 3 together (corresponding to the deformation between FIGS. 1C 1D) proceeds plastic buckling is reduced, the load is reduced (FIG. 2, A → B). If side 2 completes the first buckling contact completely broken, the second period of the deformation starts similarly, the load increase until break ridge line 3 (Fig. 2, B → C), topically until completion, such plastic buckling has started to descend (Fig. 2, C → D). After that, the displacement - repeating the load behavior. As a result, the period H of the bellows with the (accordion-like) deformation load even rise at a period H as shown in FIG. 2 applied, repeated down. Here, C point, E point in FIG. 2, each maximum load Pm during the second buckling deformation 2 maximum load Pm during, third buckling deformation 3 is. Further, Pm 1 the maximum load the second and subsequent is less than the axial vibration is generated by the initial buckling, because load applied to the ridge line 3 after 2 cycles become unbalanced load. [0010] 　Shock absorbing component Fig. 1A ~ diagram as described above 1H, the displacement of 2 - load curve profile, exhibits a crushing deformation, in order to satisfy the above [1], must take the following measures. [0011] 　Absorbing collision energy, the displacement - load curve bottom area, i.e.,: equal to (W Average Load) × (displacement). Therefore, it is important to increase the W, Pm i (i = 1, 2, 3 · · ·, n), and the larger the buckling number n, W is increased. For this purpose, Pm increases the tensile strength or bending moment of the sheet material constituting i increasing, and it is effective to increase the buckling number n to reduce the seat屈波length. [0012] 　Further, when loaded with the shock load from the oblique direction, load applied to the shock absorbing component becomes unbalanced load. Therefore, even for unbalanced load, displacement - it is necessary to design the part shape, the material strength so that it can increase the load curve lower area. [0013] 　On the other hand, in recent years CO 2 reduction and, in terms of fuel efficiency, weight reduction of the vehicle body is strongly demanded. Further, in the next-generation vehicles such as electric vehicles, significant CO 2 although reduction can be expected, since the vehicle body total weight is increased by mounting the battery, it is impossible to obtain a sufficient driving range is next-generation vehicles It has been a major barrier in order to spread. From this viewpoint, much lighter materials and components constituting the vehicle has been demanded strongly. [0014] 　To reduce the weight of the above-mentioned [3] is not only lighter components themselves, it is also important to prevent the increase in capacity of the peripheral members by reducing the component volume. For this purpose, at the same time it constitutes a part lightweight member, it is necessary to design materials that can improve the impact absorption energy of abbreviating and volume per constituent material, shape. [0015] 　Conventionally, in order to satisfy the characteristics of the above-mentioned [1] to [3], such as the following techniques are known. From both surfaces of the material and part geometry, measures have been taken. [0016] 　For example, in Japanese Patent No. 2783100 publication, it is disclosed that the form of the residual austenite affects the shock absorbing ability. Then, by defining chemical components and manufacturing processes can be obtained in the form of residual austenite steels exhibit good crash performance, invention to improve the crashworthiness of the steel sheet having a residual austenite is disclosed. This, Pm improves the tensile strength of the steel sheet i are intended to be increased. However, since there is no effect of reducing the seat屈波length H, buckling deformation number is not increased. As a result, Pm i even increases, significant increase of absorbed energy is difficult. In particular, reducing the shock-absorbing direction of the shock absorbing component, because it is difficult to sufficiently absorb the shock, it is difficult to lightweight and compact components. [0017] 　Further, in JP-A 7-224874 and JP-shock absorbing component is disclosed comprising a fiber-reinforced resin. Sequential destruction caused by the use of a resin material having a brittleness, it is possible to increase the impact energy absorption efficiency. And, by reinforced with high strength fibers, and in order to increase the buckling strength. In the present invention, due to the use of brittle materials, unlike the deformable plastic material, such as steel, can absorb the impact energy throughout the buckling deformation portion, a high impact energy absorption efficiency. Furthermore, Pm by the reinforcing fibers i is also increased. And, because it consists of a lightweight material, it can be easily be lighter. However, low productivity, a problem that is costly. Further, since the brittle fracture, debris scatter around, which people around, is a possibility to hang out及harm to the object. [0018] 　Automotive Technology, vol. 47, no. 4 (1993), p. The 57, shock absorbing component is disclosed in which by processing a notch called crash bead side. This can be achieved by machining a notch serving as a starting point for buckling deformation at the time of collision on a side surface at small intervals, to reduce the seat屈波length, is a technique that aims to increase the buckling deformation of times. However, by inserting a notch, materials inherent Pm i likely can not be expressed, can not be efficiently increased W. Further with respect to impact load in the direction intersecting with the impact-absorbing direction, may notch does not function as a buckling initiator origin, it can not be reduced seat屈波length. [0019] 　Furthermore, in JP 2006-207724, constituted by polygonal closed cross section having a recessed groove toward the interior, and the shock absorbing component is disclosed in which a difference in bending moment to a portion of the cross section . Can reduce the distance of the edge line by a polygonal cross-section, it is possible to reduce the seat 屈波 length. Further, by forming a groove recessed toward the inner and outer opposite direction, the unbalanced load can be prevented by suppressing the axial vibration of the ridge. As a result, stably crush deformation. Then, by providing a difference in bending moment, can also correct the crushing deformation in the axial direction with respect to a collision from an oblique direction, it is possible to sufficiently impact energy absorption. However, the seat 屈波 length determined depending on a distance between the ridge line, in order to increase the W and sufficiently small seat 屈波 length has to correspond small ridge spacing, there are restrictions on the freedom of shape. Further, the shock absorbing component, on the shape is the shape constrained because it is complicated, since it is composed of a single steel significant weight of the vehicle body is difficult. [0020] 　Further, JP-A-2012-81826, a number of sandwich panels with metal core member having openings is bonded across the skin material made of two metal is disclosed. However, the peripheral edge of the sandwich panel is a solid portion where a large number of openings is not formed, the rigidity than the opening forming portion is high, the seat 屈波 length is increased, impact energy absorption decreases. Moreover, since the rigidity change in one of the panels is large, it is difficult to stably crush deformation. [0021] 　As described above, although the measures by the structure of the material and the shock absorbing component have been made, have yet to the development of the shock absorbing component characteristics can sufficiently satisfy. Summary of the Invention Problems that the Invention is to Solve [0022] 　The present invention, (a) can be stably bellows collapse deformation. (B) maximum load Pm during buckling deformation i is large. (C) the seat屈波length H is small. (D) regardless of the load direction of the impact load, capable of expressing (a) ~ (c). (E) the shape constraint is relatively small, capable of expressing (a) ~ (d). (F) the impact energy absorbing efficiency is improved in a simple component shapes are possible significant weight reduction. And an object thereof is to provide an absorbent shock capable of expressing characteristic components. Means for Solving the Problems [0023] 　The present inventors have made intensive studies in order to solve the above problems and found the following items. That applies a pair of the cross section uniform laminated metal plate becomes a core layer bonded laminated between the surface layer made of a metal plate, the shock absorbing component obtained by molding into a shape having at least two ridge lines. Thus, when loaded with the shock load to one end of the shock absorbing direction of the component, higher average load, found that it is possible to stably bellows collapse deformation, the present invention based on this finding the has been completed. [0024] 　The present invention is directed to a gist the following. (1) at one end of the shock absorbing direction of the component when the impact load is loaded, a shock absorbing component for absorbing impact energy, a large Young's modulus and density than the core layer on both sides of the core layer surface to be joined laminated cross section a uniform laminated metal plate made of a metal plate, a member formed by molding into a shape having at least two edges, comprise more than 50% the maximum circumferential length of the part cross-sectional configuration is, the thickness of the surface layer (t f thickness of) and said core layer (t c thickness ratio of the) (t c / t f shock absorbing component) is 10.0 or less. (2) the shock absorbing component according to the shape of the part cross section of the shock absorbing component are all open cross-sectional shape (1). (3) the shock absorbing component according to the shape of the part cross section of the shock absorbing component is part open cross-sectional shape (1). (4) the shape of the part cross section of the shock absorbing component is shock absorbing component according to any a closed section (1). (5) the laminated metal plate has a Young's modulus of the surface layer (E f the Young's modulus) of said core layer (E c Young's modulus ratio of the) (E c / E f ) is 1/10 ~ 1 / 100,000 there (1) shock absorbing component according to any of the - (4). (6) the Young's modulus ratio (E c / E f shock absorbing component according to any of) is 1 / 10-1 / 1000 (1) to (5). (7) Impact-absorbing component according to any interval of the ridge is at least 10 mm (1) ~ (6). (8) shock absorbing component according to any of the shear bond strength between the surface layer and the core layer is not less than 25 MPa (1) ~ (7). (9) bonding lamination of the surface layer and the core layer, an adhesive in the brazing material or a conductive adhesive (1) shock absorbing component according to any of the - (8). (10) when loaded with the shock load to one end of the shock absorbing direction of the component, a shock absorbing component for absorbing impact energy, the metal plate Young's modulus than the core layer on both sides of the core layer is greater surface is laminated, the surface layer of the plate thickness (t consisting of f thickness of) and said core layer (t c thickness ratio (t a) c / t f in) is 2.0 to 7.0 constructed shock absorbing parts member with cross section formed by molding a uniform laminated metal plate. (11) the plate thickness ratio (t c / t f shock absorbing component according to) is 3.5-5.0 (10). (12) the Young's modulus ratio (E c / E f shock absorbing component according to) is 1 / 10-1 / 1000 (10) or (11). (13) the metal plate stack is formed into a shape having at least four edges, interval of the ridge, the impact absorption according to one of respectively 50 ~ 80mm (10) ~ ( 12) parts. (14) the metal plate stack further comprises a bonding layer between said surface layer and said core layer, the shear modulus of the bonding layer is 30 ~ 500 MPa (10) ~ according to any one of (13) shock-absorbing parts. The invention's effect [0025] 　According to the present invention, the (a) can be provided - a shock absorbing component which satisfies the (e). As a result, the use of shock absorbing component of the present invention can protect an occupant of the cabin against collision from an oblique direction not front only. And, because it absorbs the impact energy without damaging the junction member, the maintenance is easy, and it is efficient. Further shock absorbing component of the present invention, it is possible to sufficiently absorb the impact energy with respect to the collision with a relatively small shape constrained, can compact storage, does not cause weight gain around the member. And it can weight reduction component itself because it is constructed from a lightweight material. As a result, it is effective to improve fuel efficiency. BRIEF DESCRIPTION OF THE DRAWINGS [0026] Figure 17 [Figure 1A] Figure 1 according to the first embodiment. Figure 1A is a perspective view showing a typical deformation behavior when a load in the impact absorbing direction. Perspective view of a typical deformation behavior when a load in FIG 1B] shock-absorbing direction. Perspective view of a typical deformation behavior when a load in FIG 1C] shock-absorbing direction. Perspective view of a typical deformation behavior when a load in FIG 1D] shock-absorbing direction. Sectional view showing a typical deformation behavior when a load in FIG 1E] shock-absorbing direction. Sectional view showing a typical deformation behavior when a load in FIG 1F] shock-absorbing direction. Sectional view showing a typical deformation behavior when a load in FIG 1G] shock-absorbing direction. Photographs showing typical deformation behavior when a load in FIG 1H] shock-absorbing direction. [2] A typical load when a load in the impact absorbing direction - displacement curves. [Figure 3] a cross-sectional view showing a configuration of a laminated metal sheet. [Figure 4A] schematic diagram showing a deformation behavior of the surface layer and the core layer during buckling deformation of the metal plate stack. [Figure 4B] schematic diagram showing a deformation behavior of the surface layer and the core layer during buckling deformation of the metal plate stack. [Figure 4C] a schematic diagram illustrating a deformation behavior of the surface layer and the core layer during buckling deformation of the metal plate stack. [Figure 4D] a schematic diagram illustrating a deformation behavior of the surface layer and the core layer during buckling deformation of the metal plate stack. [Figure 4E] a schematic diagram illustrating a deformation behavior of the surface layer and the core layer during buckling deformation of the metal plate stack. [5] a perspective view showing a deformation behavior in the case of a load in the impact absorbing direction member has only one form ridges. Photos showing representative shaft wobble in the case of a load in FIG. 6 shock absorbing direction. [Figure 7A] a perspective view showing a shock absorbing component of some open cross-section used in Examples. [Figure 7B] shows a shock absorbing component of some open cross-sectional shape as used in Example, cross-sectional view taken along A in Figure 7A. [Figure 7C] shows a shock absorbing component of some open cross-sectional shape as used in Example, cross-sectional view taken along B of Figure 7A. Photograph showing the FIG. 8] "V-shaped" deformation. [Figure 9A] a schematic diagram illustrating a buckling deformation when the thickness constitution was changed in the metal plate stack. [FIG 9B] a schematic diagram illustrating a buckling deformation when the thickness constitution was changed in the metal plate stack. [10] a perspective view showing an application example of the shock absorbing component of the present invention. [Figure 11A] sectional view showing a shock absorbing component of open cross section used in Examples. [Figure 11B] a perspective view showing a shock absorbing component of open cross section used in Examples. [Figure 12A] sectional view showing a shock absorbing component of the closed section used in Examples. [Figure 12B] a perspective view showing a shock absorbing component of the closed section used in Examples. [13] explanatory view showing a member having a polygonal part cross-sectional shape having a plurality of ridge lines used in Examples. [14] a perspective view showing a shock absorbing component of some open cross-section used in Examples. [Figure 15A] sectional view showing a shock absorbing component of cylindrical shape used in Comparative Example. [Figure 15B] shows a shock absorbing component of cylindrical shape used in Comparative Example, cross-sectional view taken along C of Figure 15A. [Figure 16A] a perspective view showing a member of the ridge was only one form used in Comparative Example. [Figure 16B] shows the member ridges have only one form used in Comparative Examples, sectional view taken along a D in Figure 16A. [17] a cross-sectional view of a stacked metal plate having a wire mesh in the core layer. Figure 20 From Figure 18A] Figure 18A according to a second embodiment. Figure 18A is a perspective view showing an example of the shape of the shock absorbing component. [Figure 18B] a perspective view showing another example of the shape of the shock absorbing component. [19] Example 103 and Comparative Examples 101 and 102, E c / E f graph showing the average seat屈波length for. [Figure 20] diagram showing an average seat屈波length for the shape of the shock absorbing component. DESCRIPTION OF THE INVENTION [0027] 　Hereinafter, the embodiments of the present invention will be described with reference to FIG. In the specification and the drawings, in the elements having substantially the same function and structure are a repeated explanation thereof by referring to the figures. [0028] [First Embodiment] 　The present embodiment, an impact load when loaded into one end of the shock absorbing direction of the component, a shock absorbing component for absorbing impact energy. The shock absorbing component, a proper Young's modulus and density sided uniform cross section becomes a metal plate joined laminated to a laminated metal sheet of the core layer of, made by molding in a shape having at least two ridge members configured to include a. In this specification, the ridge line and the case where the shape of the cross section perpendicular to the shock-absorbing direction of the shock absorbing component has a straight portion, a corner portion formed by the linear portion between (angle 0 ° Ultra 180 the ° below), a line connecting sequentially the shock absorbing direction (see ridge 3 of FIG. 1). [0029] 　As shown in FIG. 3, the laminated metal plate 9 constituting the shock absorbing component of the present embodiment, a structure respectively metal plates on both surfaces (surface layer 5A, 5B) are laminated in the core layer 10, i.e., on the surface layer 5A the core layer 10 are stacked, has a further structure the surface layer 5B is laminated thereon. This embodiment, the core layer 10, the Young's modulus (E of the surface layer 5A, 5B f ) less than the Young's modulus (E c is a plate-like layer having a density). It is preferred that a uniform core layer 10 present in the entire cross section of the metal plate stack 9. Young's modulus of the core layer 10 (E c ) can be evaluated by a tensile test according to JIS Z2241 (metal material) and JIS-K7113. If the core layer 10 of a plurality of materials are combined structure, the Young's modulus (E c ) is a proportional constant of the coaxial direction of the strain and the stress (modulus of longitudinal elasticity) for the structure. [0030] 　Here, the uniform cross section, means that there is uniform surface and core layer to the entire cross-section of the metal plate stack. Uniformly also include those that are configured periodically (regularly) as wire mesh. Period is not limited to a constant, it may be somewhat changed. In entire cross section, the periodic portion and a like aperiodic part are combined is not included in the uniform. [0031] 　Shock absorbing component of the present embodiment can absorb by utilizing axial crush deformation of the metal plate stack 9 was processed into a shape having at least two ridge lines (Figure 1H), efficiently impact energy. Thus, when absorbing impact energy, more than 50% of the deformation mode of the shock absorbing component is assumed that the impact load is applied from the direction of extent of deformation in the axial crush mode. Input direction of the impact load that satisfy the conditions, the magnitude of the impact load varies depending on the speed, the crossing angle with respect to the impact-absorbing direction of 0 ° or more, is a measure less than 60 °. For more than 60 °, the deformation mode of the parts due to an impact load is often crushed deformation mode bending by the lateral load rather than axial collapse (shock absorption direction perpendicular load) becomes main. Preferably, the input direction of the impact load, 45 ° or less, and more preferably is to install so that the 30 ° or less. Thereby, the ratio of the axial crush deformation mode becomes larger, it can be absorbed more efficiently impact energy. Further, it is assumed also applied to the shock absorbing component of the transportation, the rate subject to shock loads, assumes the following 1 m / h or more 500 km / h. [0032] 　Here, the core layer 10 of the laminated metal plate 9 is a plate-like layer having a low Young's modulus and density of a metal plate constituting the surface layer 5A, a 5B. Plate layer has a Young's modulus and density surface layer 5A, may be lower than 5B, it is not particularly define the material and structure as described below. Therefore, if ridge 3 is one 1 "L-shape", and has two or more ridges are machined shape over one position to the "U-shape or S-shape". Note that the ridge line 3 of the hat-shaped in FIG. 1E is four. [0033] 　Then, the shock absorbing component of the present embodiment, the reason why can be efficiently energy absorption will be described in detail. [0034] 　Shock absorbing component of the present embodiment, since the configuration at the junction laminate of the core layer 10 of low density metal plate 5, the density is small compared to a single metal plate. As a result, even when increasing the thickness of the core layer 10, it is possible to minimized the increase in mass of the metal plate stack 9. Therefore, compared to a single metal plate mass equivalent, it can exhibit a high flexural rigidity. As disclosed in Timoshenko, maximum load Pm during buckling deformation i is a function of the flexural rigidity of the plate which constitutes ((1) see formula), Pm as the flexural rigidity is large i increases. Therefore, the rigidity increasing effect of the metal plate stack 9, Pm i can be increased. 　Pm i = k [pi] 2 D /　　　　b 2 · · · (1) Incidentally, k is a proportional constant, D is the flexural rigidity, b is the width of the shock absorbing component side. [0035] 　On the other hand, the small wavelength of the buckling deformation is caused by the following mechanism is achieved. [0036] 　Laminated metal plate 9 constituting the shock absorbing component of the present embodiment, since the core layer 10 of the low Young's modulus is bonded restrain the metal plates 5 of the double-sided, two surface layer material was restrained each other by an elastic spring 20 It can be modeled as 21 (FIG. 4A). Although there are differences in the deformation degree of freedom of the surface layer member 21, the axial crush deformation mode of the two plates is equivalent to crush deformation mode of the elastic floor plate (Figure 4B). Elastic foundation 22 corresponds to the elastic spring 20. In the two surface layer member 21 is restrained by the elastic spring 20 (FIG. 4A), the two plates (surface layer member 21) both non-fixed, a surface layer on the elastic bed 22 material 21 (FIG. 4B), 1 plates ( the surface layer member 21) only is non-stationary. However, both the axial crush energy is absorbed by the deformation of the elongation deformation and the surface material 21 of the elastic spring 20. And, from the variational principle, it is deformed deformation energy sum is minimized. Here, as the surface metal plates are described in Timoshenko, when deformed at a wavelength equal to the distance between the ridge line H1 (FIG. 4C), the energy e f is minimized. On the other hand, deformation of the elastic bed, it is possible to reduce the energy better to minimize the elongation. As a result, smaller wavelengths H than the distance between the ridge line as shown in FIG. 4D 2 when deformed, energy e c is minimized. Therefore, the seat屈波length of the plate on the elastic foundation 22, e c , e f determined by the balance of the size of, H 1 less than, and H 2 becomes larger than (FIG. 4C, FIG. 4D). [0037] 　The same principle laminated metal plate 9 constituting the present embodiment can be explained that the small wavelength. That is, the surface 5A, 5B, the deformation energy is reduced if the buckled larger wavelengths. The core layer 10, the deformation energy is reduced if the buckled with small wavelengths. Laminated metal plate 9, and balanced by the magnitude of the deformation energy of the surface layer 5A, 5B and the core layer 10, and the sum of both deformation energy is buckling deformation at a wavelength such that a minimum. Because of the deformation contributions prone core layer 10 becomes smaller wavelength, as compared to the configured shock absorbing component in a single material, the shock absorbing component of the present embodiment makes it possible to crush deformation at low wavelengths. [0038] 　On the other hand, the Young's modulus of the surface layer 5A of the core layer 10 of the laminated metal sheet 9, the deformation of the case of the above 5B can be modeled as two metal plates restrained by rigid. In this case, the core layer is maintained (FIG. 4C, FIG. 4D) without elongation deformation such as the distance of the rigid body 23 two surface layer member 21 constant. Deformation energy is a plan holding (cross section was perpendicular to Zaijiku before deformation, also in cross section perpendicular to the timber axis after deformation) and deformation is minimized when the (Figure 4E). As a result, it is impossible to reduce the seat 屈波 length. Therefore, the Young's modulus of the core layer 10 of the laminated metal sheet 9 constituting the present embodiment must be less than the surface layer 5A, 5B Young's modulus of. [0039] 　Further, the laminated metal plate 9 in this embodiment, must be processed into a shape having at least two ridge 3. Co By configuring the ridge 3 - can donors. Since the corner portion is stiffer than the side surface 2 is greater, maximum load Pm during buckling deformation i a can be further increased. Furthermore, the ridge line 3 must be 2 or more. If the ridge line 3 is one, one of the peripheral end face of the side sandwiching the ridge line 3 becomes free end face. This results in a deformation mode as to enlarge the angle of the side surface as shown in FIG. 5 when the crushing load is applied. Thus, the boundary conditions change, without buckling deformation stable cause torsional deformation, can not be sufficiently express the benefits of the above metal plate stack. [0040] 　For the above reasons, the shock absorbing component of the present embodiment, the maximum load Pm at high buckling deformation i maintaining, and, since it buckling deformation in a small wavelength, the average higher by increasing the number of seat屈回load W There can be realized. As a result, it is possible to increase the impact energy absorption. Furthermore, without boundary conditions change during the deformation, buckling stably. As a result, it can be efficiently absorb impact energy. [0041] 　As another effect of buckling deformation in the small wavelength, it is possible to suppress the occurrence of phenomena such as the axial shake during buckling deformation in a single metal plate (FIG. 6). As a result, buckling stabilize the can be absorbed with good reproducibility impact energy. At the same time (these applied to the shock absorbing component as unbalanced load) load from a direction intersecting obliquely with respect to the shock-absorbing direction relative, it is possible to stably and energy absorption. [0042] 　Shock absorbing component of the present embodiment, the Young's modulus and density need only be configured to include a member obtained by processing the above conditions are satisfied proper laminated metal plate 9 in a shape having at least two edges 3, particularly It does not limit the form of ridge 3. Thus, the ridge line 3 may be two or more, also parallel to the shock-absorbing direction, be arranged in a flared against an impact load application direction, or may be reversed. The number of preferred ridge 3 is not more than 25 lines. It becomes 25 present than, shaping becomes difficult. [0043] 　The shape of the shock absorbing component of the present embodiment also, it is sufficient to satisfy the above conditions, is not particularly specified. Or in the form of such machining shock absorbing component which imparts a crash bead as described in JP-A-2006-207724 to the side surface to the specific forms, it is not a requirement of the present embodiment. Therefore, less shape constrained as compared with the prior art, can be selected form according to the purpose. For example, if molding a shock absorbing component in a simple process, simple U-shaped or S-shaped, and a square-type, such as a hat-type can be selected. Further, the energy absorption of the load from the oblique direction, from the form, in order to further stabilize the cross-sectional shape perpendicular with respect to the impact load direction, the polygonal (square greater) form with multiple ridge, more like It can also be in a square form. More preferably, the balance between the stability of the energy absorption capacity for formability and oblique load is six to eight square cross-section. Furthermore, the two ridges of which are disposed diverging relative to the impact load application direction in a shape having at least a cross-sectional shape of the end face is also possible to different forms. The shape, by reducing the side cross-section for receiving the impact load initially, Pm 1 (originally, Pm 1 > Pm j (j> 1)) to reduce the, the impact load is propagated to other members is effective to more reliably suppress the. Alternatively, it is also possible to shape having at least two ridges of which is arranged to butt bud against an impact load application direction reversed. In this case, since the side cross-section for receiving the impact load initially be large, Pm 1 can be increased. As a result, it can be suitably applied to the part of the initial impact strength applications that require (applications such as unbreakable parts). [0044] 　Furthermore, the height h of the shock absorbing component of the present embodiment is not particularly specified even. Here, the height h of the shock absorbing component, a height of projecting the impact absorption axis of the shock absorbing component, often means a substantial shock absorbing component height. Because impact energy absorption capability per buckling one wavelength is determined by the material of the component cross section and configuration, preferred component height can be determined according to these. For example, impact energy absorption capability per buckling one wavelength, plasticity bending moment M of the laminate constituting p, the maximum circumferential length of the part cross section L m is a function of the product of the. Therefore, the energy absorption amount U targeted 0 When, component height h ≦ (U 0 / M 0 ) L m when, with only the shock absorbing component may not be absorbed impact energy. Therefore, h> (U 0 / M p ) L m in it is preferably, more preferably h> 2 × (U 0 / M p ) L m is. On the other hand, h ≦ (100 × U 0 / M p ) L m is preferably. h> (100 × U 0 / M p ) L m For, not involved in the impact energy remains healthy site number, may decrease the shock absorbing ability per mass. [0045] 　Moreover, the form of the part cross section of the shock absorbing component of the present embodiment, the opening cross-section (FIG. 11A, see FIG. 11B), closed cross-section (FIG. 12A, see FIG. 12B), or closing of an opening portion in a part of the cross section may be cross section (see FIG. 14). Also, treated forms beads on the side surface, forms a part which is provided with holes on the side surface in the open cross section (FIGS. 7A ~ Figure 7C), the form may be like containing the partially cut-away to collision start point. [0046] 　When importance is attached to light weight (in the examples described below sides defining a back plate) at one side while ensuring two ridge lines is omitted, it is preferable that the component cross-section in the open section. Shock absorbing component of the present embodiment, since it is constituted by a member formed proper laminated metal plate 9 in a shape having two or more ridge lines, stably buckled in small wavelengths. As a result, be omitted back plate in the open cross-section, as shown in the examples below, deformed into a bellows shape without deforming the shock absorbing component is "V-shaped". On the other hand, when molded of a single metal plate into a shape having two or more edges, the shock absorbing component is distance equal wavelength H between ridge 1 buckled in. As a result, if you open cross section, resulting modification are entering the large inside at the free ends as shown in Comparative Examples described later, deformed into "V-shape", it can not be formed bellows wrinkles stably (Figure 8). As a result, when composed of a single metal plate, the open cross-section is difficult to absorb efficiently an impact energy. Therefore, it can absorb is stable impact energy in an open cross-section, which is one of features of this embodiment. As another effect of the part cross section in the open cross-section, omitting the welding, (because of the open cross-section, such as can be bolted through the L-shaped plate) fastening flexibility up the component and the vehicle body is also like. [0047] 　Further, when importance is attached to light weight and torsional stiffness of the shock absorbing component is closed section provided with openings in some parts cross-section, it is desirable to partially open cross-section provided with a holes on the sides. Torsional rigidity is increased by providing the closed cross-section portion. Shock absorbing component of the present embodiment, originally, there is a potential to energy absorption by deformation into an accordion shape stable even in the open cross-section, the opening side surfaces is enough to suppress the "V-shaped deformation" there is no need to have the strength of the. As a result, compared to the shock absorbing component made of a single metal plate, a large degree of freedom in design. [0048] 　Further, when importance is attached to the torsional rigidity and flexural rigidity of the shock absorbing component further, it is preferable to make the parts cross section all closed section. [0049] 　Further, the shock absorbing component of the present embodiment is formed by machining an appropriate laminated metal plate 9 in a shape having two or more ridge member constituting at least 50% of the circumferential length of the part cross section having the longest circumference it is sufficient to, it need not be all of the material forming the metal plate stack 9. The purpose, it is also possible to replace a part in a single metal plate. For example, if the shock absorbing component of hat-shaped type of FIG. 1E, it is also possible to replace the back plate 13 to a single metal plate. For welding between the metal plate stack 9, there are cases where bonding of the core layer and the surface layer metal plates are released by the heat input during welding. As a result, the metal plate, it is necessary to set the welding conditions can be rejoined core layers, it may welding is difficult. If the back plate 13 to a single metal plate, the condition is not required for the back plate 13, it can be welded condition more easily set. However, laminated metal sheet 9 must not be less than 50% of the maximum circumferential length of the part cross section of the shock absorbing component. When configured as a mixture of the metal plate stack 9 and the single metal plate, I buckling propagated from laminated metal plate 9 to a single metal plate part, the wavelength increases coalesce integration. If a single metal plate became 50 percent, deformation in the coalesced seat 屈波 length is a major modification of the buckling energy absorbing efficiency is reduced. Preferred in order to reduce the effects of at coalesced seat 屈波 length is further preferably 70% ratio occupying in the cross-sectional circumferential length of the laminated metal sheet 9, at least 85%. [0050] 　Young's modulus ratio of the surface layer 5A, 5B and the core layer 10 of the laminated metal sheet 9 (E c / E f ) is preferably 1/10 ~ 1 / 100,000, a Young's modulus ratio (E c / E f ) is , 1 / 10-1 / 1000 is more preferred. The reason will be described below. [0051] 　E c / E f in 1/10 greater than the Young's modulus of the core layer 10 (E c ) is too large, the core layer 10 is shear hardly deformed to buckling deformation slightly smaller wavelength than a single material There are estimated. Thus, in the shock absorbing component made of a member obtained by molding a laminated metal sheet 9 of the Young's modulus ratio, there is a possibility that the impact energy absorption efficiency is not greatly improved. [0052] Also, E c / E f is less than is 1/100000, the Young's modulus E of the core layer 10 c so is very small, the core layer 10 is easily deformed. Deformation energy of the core layer 10 in this case, E c for a very small, even if large amount of deformation, the deformation energy is reduced. As a result, the deformation energy of the surface layer 5A, the core layer 10 occupying the sum of the deformation energy of 5B and the core layer 10 is almost negligible, the surface layer 5A, is deformed to reduce the deformation energy of 5B prone. That, E c / E f if is less than 1/100000, laminated metal plate 9, it is estimated that buckling deformation slightly smaller wavelength than a single material. Thus, in the shock absorbing component made of a member obtained by molding a laminated metal sheet 9 of the Young's modulus ratio, there is a possibility that the impact energy absorption efficiency is not greatly improved. [0053] 　Furthermore, E c / E f if is less than 1/1000, the shock absorbing component 1 made of a member obtained by molding a laminated metal plate 9, even possible small seat屈波length, E c reduction in the maximum load Pm during buckling deformation i sometimes decreases. This can result in an average load W is reduced. [0054] 　Thus, the surface layer 5A of the laminated metal sheet 9, the Young's modulus ratio of 5B and the core layer 10 (E c / E f preferably) is 1 / 10-1 / 100,000, a Young's modulus ratio (E c / E f ) is 1 / 10-1 / 1000 is more preferred. [0055] 　Further, it is preferable that the above 10mm spacing ridge third member made of a metal plate stack 9. When the Young's modulus of the core layer 10 within the above range, the above-mentioned reason, it is possible to especially reduce the seat屈波length, often becomes 10mm or less. Therefore, even if the distance of the ridge line 3 over 10mm, can seat屈波length of the shock absorbing component 1 to 10mm below. Surface layer 5A of the laminated metal sheet 9, 5B and Young's modulus ratio of the core layer 10 (E c / E f if) is 1 / 10-1 / 100,000, easier to implement. If a large distance between the two edge lines, processing in the production of the shock absorbing component is facilitated. On the other hand, in the case of a configuration using a single metal plate, the seat屈波length is equal to the distance between the two edges. Therefore, in order to seat屈波length less than 10mm must the distance between the two edge lines to less than 10mm. Also the shape constraint can be further reduced by configuring a proper laminated metal plate 9, which is one of features of this embodiment. [0056] 　Further, the surface layer 5A, the thickness of 5B (t of laminated metal plate 9 constituting the shock absorbing component of the present embodiment f the plate thickness (t) c thickness ratio of the) (t c / t f ) is preferably 10.0 or less. Further, the surface layer 5A constituting the laminated metal plate 9, slightly varies depending on the specific gravity of 5B and the core layer 10, in consideration of the weight of the metal plate stack 9, t c / t f it is 2.0 or more preferably, and more preferably 3.5 or more. [0057] 　ItaAtsuhi (t c / t f if) is 10.0-fold, since the core layer 10 as compared surface 5A, 5B and is very thick, rigidity and surface layer 5A of the laminated metal sheet 9, 5B large deviation occurs in the and rigidity. As a result, the surface layer 5A during buckling deformation, symmetrical deformation is likely to occur, respectively 5B each other. [0058] 　Specifically, ItaAtsuhi (t c / t f if) is 10.0 or less, the rigidity and surface 5A of the laminated metal sheet 9, the difference between the stiffness of 5B is relatively small. Thus, the laminated metal plate 9 is the same as the bending deformation and a sheet of a single material. That is, the surface layer 5A whereas the bending deformation outward, by a surface layer 5B is that bending deformation in the core layer 10 direction, the surface layer 5A, 5B is an asymmetric bending deformation (Fig. 9A). [0059] 　On the other hand, ItaAtsuhi (t c / t f if) is 10.0 greater, as shown in FIG. 9B, the surface layer 5A whereas the bending deformation outward, also the surface layer 5B bent outward deformation . Consequently, the laminated metal plate 9 (to open lantern) expands such a thickness direction deformation occurs, the surface layer 5A, the peeling portion 9a of the 5B and the core layer 10 occurs. Therefore, the shock absorbing component constructed by molding a laminated metal plate 9, when loaded with an impact load in the height direction, there is a possibility that it is impossible to obtain a stable bellows-like collapse deformation. [0060] 　ItaAtsuhi (t c / t f if) is less than 2.0, the thickness of the metal plate stack 9, the surface layer 5A, the proportion of the thickness of 5B is 50% or more. Surface 5A, 5B, because the specific gravity as compared to the core layer 10 is large, the mass of the metal plate stack 9 is greatly increased. As a result, there is a possibility that can not be achieved sufficient weight reduction of the shock absorbing component made of a laminated metal sheet 9. [0061] 　Thus, the thickness ratio of the surface layer 5A, 5B and the core layer 10 of the laminated metal sheet 9 constituting the shock absorbing component of the present embodiment (t c / t f ) is preferably 10.0 or less, more preferably 7.0 or lower, further preferably 5.0 or less. [0062] 　Surface 5A, 5B of the present embodiment is not particularly limited, carbon steel, aluminum, titanium, copper, magnesium and a metal plate such as these alloys can be used. More specifically, if the steel sheet, for example, tin, a thin tin-plated steel sheets, electrolytic chromic acid treated steel sheet (tin-free steel), and a steel sheet for cans of nickel-plated steel plate, galvanized steel sheets, fused zinc - iron alloy plated steel sheet, molten zinc - aluminum - magnesium alloy plated steel sheet, molten aluminum - silicon alloy plated steel sheet, molten lead - and dip plated steel sheets such as tin-alloy plated steel sheet, electro-galvanized steel sheets, electrolytic zinc - nickel-plated steel plate, electro zinc - iron alloy plated steel sheet, electrolytic zinc - chromium alloy-plated steel sheet surface-treated steel sheet such as electric plated steel sheet or the like, can be used cold-rolled steel sheet, hot-rolled steel sheet, stainless steel or the like. [0063] 　Further, the surface layer 5A having a Young's modulus of the same type of metal plate is made of a metal plate is different nature of comparable, between 5B, it is also possible to laminate the core layer 10. Specifically, bending, in the drawing like applications requiring strength is a core layer 10 is laminated between the different steel plates, using a mild steel severe surface machining small radius of curvature, the intensity on the other side for securing, it is also possible such as the use of high tensile steel. In the case where the surface layer 5A, the two metal plates Young's modulus of the 5B different, the Young's modulus ratio as defined herein (E c / E f E of) f employs a small surface layer of the values of Young's modulus it is assumed that. [0064] 　Further, the surface layer 5A, 5B surface according to the present embodiment, since the adhesion and corrosion resistance improvement, it is also possible to apply a known surface treatment. Such surface treatment, for example, chromate treatment (reactive, coating type, electrolysis) and Nonkuro treatment, phosphate treatment, and organic resin treatment and the like, but not limited to. [0065] 　The preferred surface layer 5A, 5B thickness is 0.2mm or more. Surface layer 5A, the 5B thickness is less than 0.2mm, and during bending in the production of the shock absorbing component, the surface layer 5A, 5B easily fracture occur, a desired cross-sectional shape can not be obtained. On the other hand, the surface layer 5A, 5B thickness is liable to become insufficient weight reduction effect exceeds 2.0 mm. From the viewpoint of weight reduction, the surface layer 5A, 5B of the thickness is preferably 2.0mm or less. [0066] 　Further, the surface layer 5A of joining laminated above and below the core layer 10, 5B thickness may be different in the vertical. For example, in order to prevent the above bending when the surface layer 5A, the breakage of 5B, it is also possible to increase the surface tensile deformation. However, when changing the surface layer 5A, 5B thickness, the thickness of the surface layer (T to thicken L ) Tomo one surface layer of a thickness (T s thickness ratio of the) (T L / T S ) is 1 to 1. and it is preferred that the 5. Because the thickness of the surface layer to be thicker (T L ) Tomo one surface layer of a thickness (T s thickness ratio of the) (T L / T S if) was greater than 1.5, the metal plate stack 9 not only leads to significant weight increase, the shock absorbing component constructed by molding the metal plate stack 9 may not be obtained a stable bellows-like collapse deformation. [0067] 　Incidentally, the surface layer 5A, if the 5B thickness differs vertically, a large thickness surface layer of the thickness (T to place above and below the core layer 10 L plate thickness ratio of (tthe), c / t f ) the thickness of the (t f a). [0068] 　Next, a description for the core layer 10 of the laminated metal sheet 9 according to this embodiment. The core layer 10, the surface layer 5A, the Young's modulus of 5B (E f if plate layer having a) Specifically, as the material of the core layer 10, Al alloys, titanium, metals and ceramics, such as copper, resin, fiber reinforced resin, and non-metallic materials, such as paper. [0069] 　Furthermore, as the core layer 10, the materials and Fe alloy, imparting material known structure such as stainless steel, for example, net-like structure, a honeycomb structure, a structure having pores, such as expanded, corrugated structures, corrugated structure, the roll structure, and a foam. [0070] 　Further, as the core layer 10, two more than the combination complexed with core layer of the above materials, for example, composite materials and filled with pores foamed resin of the honeycomb structure, it was successively laminated a resin sheet and the network structure complex material and the like. In the case of two or more combinations composite material and the core layer 10, the Young's modulus of the complex Young's modulus of the core layer 10 (E c is). [0071] 　In the case of using a resin which is an insulating material as the core layer 10, the aluminum powder in a resin, aluminum alloy powder, nickel powder, zinc powder, Fe-based metal powder (Fe-Si alloy, Fe-Cr alloy, Fe-Co alloys, such as Fe-Mn) and an electrical resistivity × 10 1.0 -7 ~ 1.9 × 10 -4 borides Omega · cm, carbides, nitrides, and non-oxide ceramic particles, such as silicides by containing, it is possible to ensure the necessary conductivity in ensuring weldability. [0072] 　It will now be described bonding between the surface layer 5A, 5B and the core layer 10 in the present embodiment. There is no particular limitation on the bonding material and the bonding method, it may be a known bonding material and the bonding method. For example, as the bonding material, in detail but will be described later, the adhesive, conductive adhesive, brazing material, as the joining method, adhesive bonding, brazing, welding, and the like. [0073] 　Laminated metal plate 9, to place the wire mesh 30 between the metal plate (surface layer 5A, 5B), may be one filled with cement 37 into the gap (see FIG. 17). In other words, it may constitute the core layer 10 by a wire mesh 30 and the bonding agent 37. The bonding agent 37, and a polyester resin or a conductive adhesive or the like. This wire mesh 30 is periodically configuration, the metal plate stack 9 can be considered as cross section uniform. Note that this period is not limited to a constant, may vary. [0074] 　Surface layer 5A of the laminated metal sheet 9 constituting the shock absorbing component of the present embodiment, the 5B and the core layer 10, preferably be joined by a shear adhesion strength of at least 5 MPa, even more preferably be at least 25 MPa. Here, the shear adhesive strength, the maximum load when the surface layer 5A, 5B and the core layer 10 is peeled off, a value obtained by dividing the area being bonded. [0075] 　If the shear adhesive strength between the surface layer 5A, 5B and the core layer 10 of the laminated metal sheet 9 constituting the shock absorbing component of the present embodiment is less than 5 MPa, when the impact load loaded, the both surfaces of the core layer 10 surface 5A peeling 5B occurs, laminated metal plate 9 may not be deformed together. As a result, in the shock absorbing component may not be obtained a stable bellows-like collapse deformation. [0076] 　Further, when crushing deformation of the shock absorbing component, both sides and the surface layer 5A of the core layer 10 by the shearing force generated by the laminated metal plate 9, in order to prevent the peeling between 5B, more able to shear bond strength than 25MPa preferable. Incidentally, the shear bond strength can be evaluated by a tensile shear test based on JIS-K6850. [0077] 　Bonding lamination of the surface layer 5A, 5B and the core layer 10 of the laminated metal sheet 9 constituting the shock absorbing component of the present embodiment, for example, bonding layer 7A, it is preferable 7B is bonded via. Bonding layer 7A, 7B are formed by a known bonding material, for example, adhesives, brazing material may be formed by a conductive adhesive. [0078] 　The brazing material, e.g., lead, tin, antimony, cadmium, soft solder consisting of an alloy of zinc (solder), Ni-Cr-based brazing material, copper solder, gold wax, palladium wax, silver solder, aluminum wax such as hard solder, and the like of. [0079] 　As the conductive adhesive, for example, the adhesive described later, aluminum powder, and a film obtained by adding a predetermined amount of metal powders such as nickel powder or iron powder. Furthermore, welding the electrical resistance of the conductive adhesive to allow it stable, 1.0 × 10 -3 ~ 1.0 × 10 -4 is preferably Omega · cm. [0080] 　Surface layer 5A of the laminated metal sheet 9, is bonded laminate between 5B and the core layer 10, by a joint with the brazing material or a conductive adhesive, when the core layer 10 is a conductive material, welded metal plate stack 9 It can be secured sex, shock absorbing component of a technique such as welding is made possible to manufacture. [0081] 　Further, the surface layer 5A of the laminated metal sheet 9, the shear strength of the joint between 5B and the core layer 10 is preferably at 5MPa or more, and more preferably not less than 25 MPa. If the shear strength of the joint portion is less than 5 MPa, fracture (cohesive failure) occurs at the joint portion by shearing force. As a result, in the shock absorbing component may not be obtained a stable bellows-like collapse deformation. Further, when crushing deformation of the shock absorbing component, in order to prevent cohesive failure of the joint by the shearing force generated by the metal plate stack 9, be more 25MPa shear strength of the joint, and more preferred. [0082] 　When performing the surface layer 5A, the bonding between 5B and the core layer 10 by adhesive bonding, although the use of an adhesive as the bonding material, for holding a heat shape stability even after machining, 100 ° C. ~ 160 ° C. of the adhesive storage modulus G 'at, is preferably less than 0.05 MPa 100 GPa. If it is less than 0.05 MPa, heating the laminated metal plate 9 by the residual stress of the surface layer / adhesive interface which occurs when forming the shock absorbing component, a molded article of a laminated metal sheet 9 to the temperature (100 ℃ ~ 160 ℃) then, the joint is creep deformation, or destruction joints, sometimes or cause peeling starting from the junction. To more reliably prevent the creep deformation of the joint, 'more preferably is not less than 1.0 MPa, G' G and further preferably is 5MPa or more. On the other hand, in the case of 100GPa greater, since a normal temperature of G 'becomes larger, processability followability is lowered to break during processing, it may become liable to occur peeling starting from the junction. Incidentally, the storage elastic modulus G of the adhesive 'can be evaluated by the maximum value of the storage modulus of the adhesive was measured at a frequency 0.1 ~ 10 Hz. For thermosetting adhesive, with an adhesive film which is crosslinked and cured by applying the same thermal history and lamination conditions in the case of thermoplastic adhesive by molding the adhesive film, a known dynamic viscosity It can be measured by the acoustic measuring device. [0083] 　Furthermore, loss modulus G at 100 ° C. ~ 160 ° C. glue "and the storage modulus G 'ratio of tanδ (= G" / G') is preferably tanδ <1, tanδ <0.8 more preferably, more preferably from tanδ <0.5, tanδ 　load during drop weight test - from displacement curves were calculated impact absorption energy up 100mm crushing. Furthermore, in order to evaluate the weight of the parts, by dividing the impact absorption energy by the mass of the components, the impact absorption energy per unit mass, were compared and evaluated. [0118] 　Further, the impact absorbing energy when loaded with oblique load, since the load tilted 10 ° from the axial direction is loaded, the load was corrected tilt amount - was calculated from displacement curves. [0119] 　seat屈波length, displacement during drop weight test (amount shock absorbing component is pushed by weight) - than load curve, was calculated. [0120] 　More specifically, for each cycle the load is vertically was measured displacement displacement and load increase of the load is started is minimized. Then, by subtracting the displacement load is initiated rise of the load from the displacement became minimum was calculated seat 屈波 length of each period. Similarly calculated seat 屈波 length in each cycle, and calculates the average seat 屈波 length and finally averaged. The average seat 屈波 length was seating 屈波 length as in the embodiment of the present invention were evaluated. The test results are shown in Table 2 and Table 3. [0121] [Table 2] [0122] [table 3] [0123] 　Note that "A" in the column of variation in Table 2, show that stable bellows-like collapse deformation occurs, a "B", of the crushing deformation generated in the entire part, the seat part It indicates that the site 屈波 length is greater occurs. The "C" indicates that the deformation bends the first buckling position caused to deform initially whole part 'V shaped' as a starting point occurs. [0124] 　As shown in Table 2, the shock absorbing component of Examples 1 to 13 are impact absorption energy> 6.6 per unit mass, as compared to the shock absorbing component made of high-tensile steel of Comparative Example 4, high It shows the impact energy absorption capability were found to be excellent in lightweight property. Specifically, when comparing Example 1 and Comparative Example 4, the case of obtaining the same impact absorption energy, the shock absorbing component of Example 1 for Comparative Example 4, enables weight reduction 40% Weak became. [0125] 　Furthermore, the average seat 屈波 length of the shock absorbing component of Examples 1-13 is below all the 7.1 mm ~ 9.8 mm 10 mm, the average seat 屈波 length of the shock absorbing component made of high-tensile steel of Comparative Examples 4-5 it has been found very small even compared to. [0126] 　Further, Further, as shown in Table 3, the impact absorption energy and the seat 屈波 length per unit mass in the case of adding an impact load from the oblique direction if the addition of impact load in the axial direction are approximately equal. On the other hand, the shock absorbing component of Comparative Example 4, when the comparison as above, the impact absorbing energy and the seat 屈波 length was found to be different. Accordingly, in embodiments of the present invention, even if the input direction of load is varied somewhat, by stable bellows-shaped crushing deformation in small seat 屈波 length, it was found that high impact absorption capability can be realized . [0127] 　Further, the shock absorbing component of Comparative Example 4 and Example 2, the shape is identical, the seat 屈波 length were different. Seat 屈波 length of the shock absorbing component of Comparative Example 4, the distance between the ridge line of the parts and have almost the same, the seat 屈波 length, it can be seen that depending on the spacing of the ridge. On the other hand, the seat 屈波 length of the shock absorbing component of Example 2, does not coincide with the interval of the ridge line of the parts, the shock absorbing component consisting of laminated metal plate, regardless of the distance of the ridge, the seat 屈波 length it has been found that it is possible to reduce. [0128] 　Shock absorbing component of Examples 1 and 3 to 8, FIG. 11A, shown in FIG. 11B, are all open cross-sectional shape. Shock absorbing component of Example 2,10,13 each view 12A, shown in FIGS. 12B and 13 are all closed section. Shock absorbing component of Example 11 is a partially open cross-sectional shape shown in FIG. 14. These shock absorbing component, all stable bellows-shaped crushing deformation is obtained. That is, the shock absorbing component consisting of laminated metal plate, regardless of the shape of the part, it was found that it is possible to obtain a stable bellows-like collapse deformation. [0129] 　In Example 1, a comparison of Example 2 and Example 11, impact absorption energy per unit mass, Example 1 (all open cross-sectional shape)> Example 11 (partially open cross-sectional shape)> Example 2 was found to be (all closed cross section). This is in order to part or all closed cross section, a back plate 13 which is spot welded through the flange 12 is smaller contribution to impact absorption energy, presumably because not obtained the effect of the weight increase. [0130] 　Example 8 of the embodiments of the present invention, the seat 屈波 length is smallest, the impact absorption energy per unit mass is relatively small. This is because the maximum load during a single buckling deformation is small, since the average load decreased, is considered to have failed to effectively increase the impact energy absorption. [0131] 　Example 9 Young's modulus ratio of the surface layer and the core layer of the laminated metal plate constituting the shock absorbing component (E c / E f ) is less than 1/10000. Therefore, as compared with Examples 1 to 8, 10 and 11, it is estimated that the seat屈波length is increased. [0132] 　Example 5, the thickness ratio of the surface layer and the core layer of the laminated metal plate constituting the shock absorbing component (t c / t f ) is 10-fold. Therefore, while indicating good energy absorption capacity, as crushing deformation progresses, the surface layer of the peeling, unstable crush deformation occurs in some. However, as a whole member was found to exhibit excellent deformation mode. [0133] 　Results of shear bond strength of the joint was measured shear bond strength of the laminated metal plate constituting the shock absorbing component in Examples 1 to 5 and 7 to 11 was the 25MPa than the shock absorbing component of Example 6 shear bond strength of laminated metal plate constituting was found to be 15 MPa. Therefore, while indicating good energy absorption capacity, as crushing deformation progresses, the surface layer of the peeling, unstable crush deformation occurs in some. However, as a whole member, it is estimated to show a good deformation mode. [0134] 　Shock absorbing component of Example 2,10,11,12,13 is joined by each other spot welding the metal plate stack was prepared. Bonding lamination of the surface layer and the core layer of the laminated metal plate constituting the shock absorbing component, because it was joined with brazing material or a conductive adhesive, can be ensured good conductivity become possible bonding by spot welding It was. [0135] 　Shock absorbing component of Example 12 has been replaced with only the back plate with a single metal plate, since accounting for 60% of the circumferential length of the part cross-section having a maximum peripheral length of a laminated metal sheet, other implementations example stable bellows-shaped crushing deformation is considered to have occurred in the same wavelength less. [0136] 　The core layer of the laminated metal plate constituting the shock absorbing component of Comparative Example 1 is equal to the surface layer Young's modulus. Therefore, the seat 屈波 length similar to the shock absorbing component consisting of high-tensile steel of Comparative Example 5 is large, the whole part of the first buckling position caused to deform initially starting point bending deformation occurs. [0137] 　Shock absorbing component of Comparative Example 2, compared to Example, the impact absorption energy per unit mass is small. This is the shape of the shock absorbing component, since a cylindrical absence ridge, but the seat 屈波 length is small, as compared with the embodiment, since the maximum load is small, can be effectively increased impact energy absorption It considered that there was no. [0138] 　Shock absorbing component of Comparative Example 3, because the ridge line was only free L-shaped one, not occur buckling deformation is stabilized, the corner spreads such variations (Fig. 5), twisting shock absorbing component variations such as has occurred. [0139] 　Thus, the shock absorbing component having a laminated metal sheet having a constitution satisfying the present invention is excellent in lightweight property. Further, regardless of the input direction of the impact load, high maximum load, by stable bellows-shaped crushing deformation in small seat 屈波 length enables higher impact energy absorption, shows a good crash performance. [0140] [Second Embodiment] (Overview) 　shock absorbing component according to the present embodiment is the surface layer is bonded laminate formed of a metal plate Young's modulus than the core layer on both sides is larger in the core layer, a surface layer thickness of the metal plate stack (t f ) and the thickness of the core layer (t c thickness ratio of the) (t c / t f ) is the 2.0 to 7.0 cross-section formed by molding a uniform laminated metal plate composed of members. The shock absorbing component, the impact energy absorbing efficiency is high, it is possible to achieve a significant weight reduction in a simple shape. [0141] 　Specifically, the laminated metal sheet, the surface layer of the plate thickness of the laminated metal sheet (t f and) the thickness of the core layer (t c thickness ratio of the) (t c / t f ) 2.0 to with 7.0, it is possible to further reduce the seat屈波length. Therefore, such a shock absorbing part formed by laminating metal plates, it is possible to improve the impact energy absorption efficiency. [0142] 　Further, the shock absorbing component according to the present embodiment, the surface layer of the plate thickness of the metal plate stack (t f and) the thickness of the core layer (t c thickness ratio of the) (t c / t f only), impact it is possible to improve the energy absorbing efficiency. Therefore, complexity is not necessary to process the shape of the shock absorbing component, it is possible to further simplify the shape. Furthermore, it is not necessary to change the Young's modulus of the surface layer and the core layer of the laminated metal sheet in order to further reduce the seat屈波length, it is possible to improve the impact energy absorbing efficiency without changing the intensity of the shock absorbing component . [0143] 　In the following, the laminated metal plate constituting the shock absorbing component will be described in terms of a mechanism that can reduce the seat 屈波 length. [0144] 　The surface layer laminated metal plate bonded laminated on both sides of the core layer, as described above, deformation energy U of the core layer c and the surface layer of the deformation energy U f seat during buckling deformation so that the sum of is minimum屈波length is determined. Here, deformation energy U of the core layer c , and the surface of the deformation energy U f is expressed by the following equation (2) and (3). [0145] The U- C = E C /2.6×V C × · · · gamma] of formula (2) the U- F = E F × V F. × · · · [epsilon] of formula (3) [0146] 　In the above formula (1) and (2), E c represents the Young's modulus of the core layer, V c represents the volume involved in the deformation of the core layer, gamma represents a deformed amount of the core layer. Also, E F represents the surface layer Young's modulus, V F represents the volume involved in the surface layer of the deformation, epsilon represents the amount of deformation of the surface layer. Incidentally, while the surface layer of the deformation is bending deformation, the deformation of the core layer is shear deformation, and the elastic modulus of the shear deformation of the Young's modulus divided by 2.6. [0147] 　In the case where the core layer is shear deformation, as described with reference to FIGS. 4A ~ 4E in the first embodiment, basically, the deformation energy U of the core layer c becomes smaller as the seat屈波length decreases , the surface layer of the deformation energy U f decreases as the seat屈波length increases. Therefore, in order to reduce the seat屈波length, U c >> U f and, in the sum of the deformation energy, deformation energy U of the core layer c is preferably set to dominate the. [0148] 　For example, when the ratio of the surface layer and the core layer in the laminated metal plate is equal, the core layer and the surface layer Young's modulus E c and E f by controlling, U c >> U f To realize, E c and E f It must be close to. However, E c and E f for behavior modification during axial collapse deformation as the metal plate stack difference between becomes smaller closer to the metal plate of a single material, deviate from the above-mentioned theories, the decline of the seat屈波length there is a problem that small. Also, E c when increasing the often even higher density of the core layer, the mass of the metal plate stack is increased. On the other hand, the shock absorbing component is to weight is mounted on an automobile or the like required in order to ensure fuel economy. Therefore, the laminated metal sheet, was not suitable as constituting the shock absorbing component. [0149] 　Therefore, in the laminated metal plate constituting the shock absorbing component according to the present embodiment, in the formula (2) and (3), U c and U f V is another parameter for controlling the c and V f controls by, U c >> U f is used for realizing the. Specifically, the proportion of the core layer in the laminated metal sheet (i.e., thickness) by increasing the, V c increases the, and V f to decrease the. As a result, the laminated metal sheet, the surface layer of the deformation energy U f with respect to the deformation energy U of the core layer c can be increased. Therefore, the shock absorbing component according to the present embodiment, it is possible to further reduce the seat屈波length during axial collapse deformation. [0150] 　(Configuration shock absorbing component) 　below, with reference to FIGS. 3, 18A and 18B, explanation of the structure of the shock absorbing component. Figure 3 is a sectional view showing a configuration of a laminated metal sheet 9. The metal plate stack 9 are the same as the first embodiment, a description of common items omitted. Figure 18A is a perspective view showing an example of the shape of the shock absorbing component. 18B is a perspective view showing another example of the shape of the shock absorbing component. [0151] 　In laminated metal plate 9, the thickness of the surface layer 5A and 5B (t f and), the thickness of the core layer 10 (t c thickness ratio of the) (t c / t f in) is 2.0 to 7.0 is there. As demonstrated in the second embodiment described later, the thickness ratio (t c / t f if) is the value of these ranges, the shock absorbing component according to the present embodiment, the seat屈波length it can be reduced. [0152] 　Specifically, ItaAtsuhi (t c / t f if) is less than 2.0, since the contribution of the deformation energy of the core layer 10 in the deformation energy at the axial crushing deformation is reduced, reducing the seat屈波length Can not do it. The thickness ratio (t c / t f if) exceeds 7.0, since the core layer 10 against the surface 5A and 6B is very thick, and the surface layer 5A and 5B, between the core layer 10, large deviation in rigidity occurs. Therefore, the shock absorbing component, the bonding layer 7A and 7B is destroyed, there is a stable and may not be a bellows-shaped axial crush deformation. [0153] 　Further, in the laminated metal plate 9, the surface layer 5A and 5B thickness of (t f and), the thickness of the core layer 10 (t c thickness ratio of the) (t c / t f ) is preferably 3. 5 - may be a 5.0. The thickness ratio (t c / t f if) is the value of these ranges, the shock absorbing component according to the present embodiment, the seat屈波length and smaller, stable bellows-like axial collapsing deformation it is possible to cause. Specifically, ItaAtsuhi (t c / t f if) is 3.5-5.0, and deformation energy of the core layer 10 during axial collapse deformation, balanced deformation energy of the surface layer 5A and 5B since the preferred, it is possible to further reduce the seat屈波length. [0154] 　Further, in the laminated metal sheet 9, the Young's modulus E of the surface layer 5A and 5B f and Young's modulus E of the core layer 10 c Young's modulus ratio of the (E c / E f ) is 1 / 10-1 / 1000 met it may be. The Young's modulus ratio (E c / E f if) is the value of this range, the shock absorbing component according to the present embodiment, it is possible to improve the impact energy absorption efficiency. [0155] 　Specifically, the Young's modulus ratio (E c / E f if) is less than 1/1000, laminated metal plate 9, although reducing the seat屈波length of the shock absorbing component can be, E c by reduction of reduce the average load W during buckling deformation is not preferable because thereby lowering the impact energy absorption efficiency. The Young's modulus ratio (E c / E f if) exceeds 1/10, the Young's modulus E of the core layer 10 c is larger, less likely to shear deformation. Therefore, behavior during axial collapse deformation, becomes close to the metal plate of a single material, undesirably becomes impossible to reduce the seat屈波length. Note that the Young's modulus, for example, can be measured by a tensile test or the like conforming to ASTM-D638. [0156] 　The bonding layer 7A and 7B, it is preferable to control the shear deformation of the layer composed of the core layer 10 bonding layer 7A and 7B, the shear modulus of 30 ~ 500 MPa. If this shear modulus is less than 30 MPa, by the bonding layer 7A and 7B are excessively shear deformation, there is a possibility that the surface layer 5A and 5B are independently deformed together, it becomes stable buckling deformation hardly occurs undesirable since. Further, if the shear modulus is more than 500 MPa, the core layer 10, since the shear deformation of the layer formed of an adhesive layer 7A and 7B are less likely to occur, there is a possibility that the seat 屈波 length increases undesirably. Note that the shear modulus of the above can be measured by a tensile shear test based on JIS-K6850. [0157] 　(The shape of the shock absorbing component) 　will now be described the shape of the shock absorbing component according to the present embodiment. As shown in FIGS. 18A and 18B, the shock absorbing component 20A and 20B, for example, be molded into a shape having at least four ridge lines. [0158] 　Specifically, as shown in FIG. 18A, the shock absorbing component 20A is valley folded laminated metal plate from one end in order, mountain fold, mountain fold, a hat-shaped open cross section structure that is the valley fold it may be. [0159] 　Further, as shown in FIG. 18B, the shock absorbing component 20B is mountain-folded laminated metal plate from one end in order, mountain fold, mountain fold, is a mountain fold, closed cross section which ends are joined by welding or the like or it may be of cylindrical shape. [0160] 　Incidentally, in the shock absorbing component 20A and 20B, ridge direction is the shock absorbing direction. [0161] 　Further, in the shock absorbing component 20A and 20B, each of the spacing of the edge lines each other, it may be 50 ~ 80 mm. Here, the distance between the ridge line between, for example, a distance L shown in FIGS. 18A and 18B. If the spacing of the edge lines each other in this range, the shock absorbing component 20A and 20B, it is possible to cause the bellows-shaped axial crush deformation at stable small seat 屈波 length. [0162] 　Specifically, when each of the spacing ridges to each other is less than 50 mm, the shape becomes complicated, unfavorably for receiving the shape constrained. Further, if each of the distance of the ridge line between exceeds 80 mm, rigidity becomes large sides the elastic deformation is small, the seat 屈波 length is increased, and stable for the bellows-shaped axial crushing deformation is unlikely to occur with preferably Absent. [0163] 　The shape of the shock absorbing component according to the present embodiment, it is not limited to the illustrated shape, is the same as the first embodiment. [0164] 　As described above, the shock absorbing component 20A and 20B according to this embodiment, the thickness of the surface layer 5A and 5B of the metal plate stack 9 constituting the shock absorbing component 20A and 20B (t f and), the core layer 10 thickness (t of c sheet thickness ratio of the) (t c / t f by a) 2.0 to 7.0 can be made smaller seat屈波length, improving the impact energy absorption efficiency . [0165] 　Further, the shock absorbing component 20A and 20B according to this embodiment, it is not necessary to complicate the shape, it is possible to improve the impact energy absorption efficiency in a more simple shape. Further, the shock absorbing component 20A and 20B, it is not necessary to lower the Young's modulus ratio of the surface layer 5A and 5B and the core layer 10 of the laminated metal plate 9 in order to further smaller seat 屈波 length. Therefore, without changing the strength of the shock absorbing component 20A and 20B, it is possible to improve the impact energy absorption efficiency. [0166] [Second Embodiment] The following describes a second embodiment of the shock absorbing component according to the present embodiment. [0167] (Production of a laminated metal sheet) 　First, by laminating the bonding surface layer and the core layer are shown in Table 3, to prepare a laminated metal sheet. Further, the bonding between the surface layer and the core layer, using a bonding material as shown in Table 4. Bonding material on the surface layer, the core layer, the bonding material, laminated in this order of the surface layer, and heated to 80 ° C.-180 ° C., contact pressure 40 kgf / cm 2 (3.92 MPa) at 20 to 30 minutes heat and pressure, then room temperature until it cooled Vent to produce a laminated metal sheet according to each of examples and Comparative examples. [0168] [Table 4] [0169] 　In Table 4, the adhesive 1 is a base material is an adhesive of epoxy resin, the coating amount 200g / m2,180 ℃ warming, crimping force 40 kgf / cm 2 (3.92 MPa), the bonding in bonding time 20 minutes used. The adhesive 2 is substrate adhesive of the urethane resin, the coating amount 200g / m2,80 ℃ warming, crimping force 40 kgf / cm 2 (3.92 MPa), was used in the bonding with bonding time 30 minutes . Furthermore, the adhesive 3 is an adhesive obtained by dispersing an elastic rubber adhesive 2, the coating amount 200g / m2,80 ℃ warming, crimping force 40 kgf / cm 2 (3.92 MPa), at bonding time 20 minutes It was used in the bonding. Moreover, in the brazing, the brazing material (low temperature brazing material, Sn-Pb-based, mp 183 ° C.) was used in amount 15 g / m @ 2. Incidentally, the shear modulus of the bonding material was measured by a tensile shear test based on JIS-K6850. [0170] 　In Table 4, the polypropylene used as the core layer has a density of 0.94 g / cm 3 is also wire diameter of a wire mesh used as the core layer 0.6 mm, the gap between the wires is 1.6mm . Further, as described above, Ec is the Young's modulus of the core layer, Ef is the Young's modulus of the surface layer, tc is the thickness of the core layer, tf is the thickness of the surface layer. [0171] 　(Crash performance evaluation test) 　was then performed collision performance evaluation of the shock absorbing component made of a laminated metal sheet according to each of Examples and Comparative Examples prepared above. Specifically, by using the laminated metal plate according to the examples and comparative examples of the configuration shown in Table 4, it was molded at bending by press brake, length 200mm, shown in FIGS. 11A and 11B the hat-shaped shock absorbing component were prepared. 11A is a shock absorbing component according to the present embodiment is a sectional view taken along a cross section perpendicular to the ridge line direction is a shock absorbing direction. 11B is a perspective view thereof. [0172] 　Collision performance evaluation of the shock absorbing component produced was carried out by drop weight test. Specifically, the shock absorbing component, the ridge line direction is disposed such that the collision absorption direction, the weight was fixed at jig end opposite to the end of collision. Thereafter, by free fall of the mass of the weight of 120kg from a height of 3.5 m, it was the weight to collide at a speed of 30 km / h against collision end of the shock absorbing component. [0173] 　Load in drop weight test as described above - the displacement curve, was calculated impact energy absorption of up to 100mm crushing. Impact energy absorption, in order to evaluate the weight of the shock absorbing component, by dividing the impact energy absorption by the mass of the component, and the impact energy absorption per unit mass. [0174] 　Moreover, the load of the drop weight test - was calculated average seat 屈波 length from displacement curves. More specifically, for each cycle the load moves up and down, to measure the displacement load is minimized, the displacement load becomes minimum just before, by subtracting the next displacement load becomes minimum, the period It was calculated seat 屈波 length of the unit. Calculating a seat 屈波 length in each cycle in the same manner, it was calculated average seat 屈波 length by taking the arithmetic mean. The impact energy absorption amount and the average seat 屈波 length evaluation results of the per unit mass calculated by the above shown in Table 5. In Table 5, "A" in the column of the buckling form, the meaning of "B", "C", "A" variant of Table 2, the same as the meaning of "B", "C" is there. [0175] [table 5] [0176] 　Referring to Table 5, the shock absorbing component according to Examples 101 to 109 of the present invention, an impact-absorbing component according to Comparative Examples 101 to 103, the average seat屈波length is reduced, the impact energy absorption per unit mass it can be seen that the amount is increasing. Specifically, Comparative Examples 101 and 102, t c / t f since it is less than 2.0, the average seat屈波length is increased, it can be seen that the impact energy absorption is decreased. In Comparative Example 103, t c / t f but is included in the scope of the present invention, the Young's modulus of the core layer, since the surface layer Young's modulus is the same, the shock absorbing component made of a single material substantially shows the behavior similar buckling average seat屈波length is increased, impact energy absorption it can be seen that substantially reduced. [0177] 　In Examples 102, 103 and 105 to 109, t c / t f to is included in the preferable range of the present embodiment, the average seat屈波length becomes smaller, the impact energy absorption per unit mass it can be seen that the increase further. On the other hand, examples 101, t c / t f since it is less than 3.5, the average seat屈波length from Examples 102, 103 and 105 to 109 is increased. In Example 104, t c / t f for exceeds 5.0, buckling form is "B". [0178] 　In Examples 101 to 107 and 109, since the shear modulus of the bonding layer is included within the preferred range in the present embodiment, it can be seen that the average seat 屈波 length becomes smaller. On the other hand, Example 108, since the shear modulus of the bonding layer is greater than 500 MPa, in contrast to Example 105 other things being equal, the average seat 屈波 length is increased, impact energy absorption amount is reduced ing. [0179] 　In Examples 101-108, the core layer and the surface layer Young's modulus ratio (E c / E f ) is, because it contains within the preferred range in the present embodiment, more impact energy absorption per unit mass it can be seen that increased. On the other hand, Example 109, the core layer and the surface layer Young's modulus ratio (E c / E f ) is × 10 1 -3 for less than for example 105 other things being equal, impact energy absorbing the amount is decreasing. [0180] 　Further, the metal plate stack according to Example 103, Comparative Examples 101 and 102, in the simulation, the Young's modulus ratio of the surface layer and the core layer (E c / E f while (Echanging), c / E f were evaluated changes in mean seat屈波length for). Simulation using Marc is a nonlinear analysis program was performed buckling eigenvalue analysis. The evaluation results are shown in FIG 19. Here, FIG. 19, Example 103, in the shock absorbing component according to a comparative example 101 and 102, the Young's modulus ratio (E c / E f is a diagram showing the average seat屈波length for). 19, the vertical axis represents the average seat屈波length, the horizontal axis is the Young's modulus ratio (E c / E f is a logarithm of). [0181] 　As shown in FIG. 19, Example 103 (total thickness 2.0 mm, t c / t f = 4.3), the Young's modulus ratio of either surface layer and the core layer (E c / E f also in) Comparative example 101 (total thickness 1.0 mm, t c / t f = 1.1) with respect to, it can be seen that the average seat屈波length decreases. That is, Example 103, t c / t f to be included within the scope of the present embodiment, the Young's modulus ratio of the surface layer and the core layer (E c / E f regardless), in Comparative Examples 101 and 102 it can be seen that reducing the average seat屈波length against. [0182] 　Furthermore, the bending stiffness of Example 103 and Comparative Example 102, 9.6 × 10 4 N · cm 2 is, bending rigidity of Comparative Example 101, 1.7 × 10 4 N · cm 2 is. That is, Example 103, to the comparative example 102, the strength of the laminated metal plates (specifically, the flexural rigidity) can be reduced average seat屈波length without decreasing. [0183] 　Still referring to FIG. 19, Example 103, to the comparative examples 102 and 103, in particular, the Young's modulus ratio of the surface layer and the core layer (E c / E f ) is × 10 1 -3 ~ 1 × 10 - 1 in the range, it is possible to further reduce the average seat屈波length. Specifically, the Young's modulus ratio of the surface layer and the core layer (E c / E f ) is × 10 1 -1 if exceeding undesirable because the amount of decrease in the average seat屈波length is small. The Young's modulus ratio of the surface layer and the core layer (E c / E f ) is × 10 1 -3 For less than, the Young's modulus E of the core layer c reduces the average load W during buckling deformation by lower, undesirable because the impact energy absorption efficiency decreases. [0184] 　Next, the a in simulation using similarly Marc, 50 mm spacing L of the ridge line, respectively, 65 mm, 80 mm and the hat-shaped member Young's modulus ratio of the surface layer and the core layer in (E c / E f average over) It was to evaluate the change of seat屈波length. The evaluation results are shown in FIG 20. Here, FIG. 20 is a diagram showing the average seat屈波length for the shape of the shock absorbing component. In Figure 20, the vertical axis represents the average seat屈波length, the horizontal axis is the Young's modulus ratio (E c / E f is a logarithm of). [0185] 　Referring to FIG. 20, when the distance L of the ridge line of the shock absorbing component is 50 ~ 80 mm, preferably the Young's modulus ratio in the present embodiment (E c / E f 1 × 10 ranges) -3 ~ 1 × 10 -1 at, it can be seen that the average seat屈波length is reduced more remarkably. On the other hand, if the distance L of the ridge line is more than 80 mm, the average seat屈波length is increased, and since the stable bellows-like axial crushing deformation is unlikely to occur, undesirably. Further, when the distance L of the ridge is less than 50 mm, the shape of the shock absorbing component becomes complicated, unfavorably for receiving the shape constrained. [0186] 　Above As can be seen from the results, according to the shock absorbing component according to the present embodiment, a surface layer made of a metal plate Young's modulus than the core layer is greater on both sides of the core layer bonded laminate, a surface layer of thickness t f and the core thickness t of the layer c by constructing a laminated metal plate was 2.0 to 7.0, it is possible to reduce the seat屈波length, improving the impact energy absorption efficiency. [0187] 　Further, according to the shock absorbing component according to the present embodiment, it is possible to reduce the seat 屈波 length without complicated processing the shape of the shock absorbing component, it is possible to further simplify the shape of the shock absorbing component . Further, the shock absorbing component according to the present embodiment, in order to further reduce the seat 屈波 length, since it is not necessary to lower the Young's modulus ratio between the surface layer and the core layer of the laminated metal sheet further the strength of the shock absorbing component it is possible to improve the impact energy absorbing efficiency without decreasing. [0188] 　Further, the shock absorbing component according to the present embodiment, since the conventional shock absorbing component, the Young's modulus is small and relatively proportion of less dense core layer is composed of a large metal plate stack, more light weight it can be achieved. Therefore, the shock absorbing component according to the present embodiment, it is possible to achieve a more lightweight. [0189] 　Having described in detail a second embodiment of the present invention with reference to the accompanying drawings, the present invention is not limited to such an example. It would be appreciated by those skilled in the relevant field of technology of the present invention, within the scope of the technical idea described in the claims, it is intended to cover various modifications, combinations, for even such modifications are intended to fall within the technical scope of the present invention. [0190] 　All documents described herein, patent applications, and technical standards, each individual publication, patent applications, and to the same extent as if it is marked specifically and individually incorporated by techniques standard reference, It incorporated by reference herein. Industrial Applicability [0191] 　The present invention is not passenger car only, can be suitably applied track light cars, an automobile in general lead to large vehicles such as buses, as a shock absorbing component of transportation such as a train. [0192] (Description of 　symbols) 1 shock absorbing component 　2 side 　3 ridgeline 　5A, 5B surface 　7A, 7B bonding layer 　9 the metal plate stack 10 core layer hat member 11 open cross section 12 flange 13 back panel 14 holes 15 end 16 side end part 25 core layer The scope of the claims [Requested item 1] 　When loaded with the shock load to one end of the shock absorbing direction of the component, a shock absorbing component for absorbing impact energy, 　the Young's modulus than said core layer on both sides of the core layer and the density is larger metal plate comprising a surface layer and becomes joined laminated cross section uniform laminated metal plate, is composed of members formed by molding into a shape having at least two edges, comprise more than 50% of the maximum circumferential length of the part cross-section, wherein surface layer thickness (t f ) and a plate thickness of the core layer (t c thickness ratio (t a) c / t f shock absorbing component) is 10.0 or less. [Requested item 2] 　Shock absorbing component of claim 1 shape of the component cross section of the shock absorbing component are all open cross-sectional shape. [Requested item 3] 　Shock absorbing component of claim 1 shape of the component cross section of the shock absorbing component is part open cross-sectional shape. [Requested item 4] 　Shock absorbing component of claim 1 shape of the component cross section of the shock absorbing component are all closed section. [Requested item 5] 　The laminated metal sheet has a Young's modulus of the surface layer (E f the Young's modulus) of said core layer (E c Young's modulus ratio of the) (E c / E f claims) is 1 / 10-1 / 100,000 shock absorbing component according to any one of 1-4. [Requested item 6] 　The Young's modulus ratio (E c / E f ) an impact-absorbing component according to any one of claims 1 to 5, which is 1 / 10-1 / 1000. [Requested item 7] 　Shock absorbing component according to any one of claims 1 to 6 intervals of the ridge is at least 10 mm. [Requested item 8] 　Shock absorbing component according to any one of claims 1 to 7 shear bond strength between the surface layer and the core layer is not less than 25 MPa. [Requested item 9] 　The bonding lamination of the surface layer and the core layer, the shock absorbing component according to any one of claims 1 to 8, an adhesive in the brazing material or a conductive adhesive. [Requested item 10] 　When loaded with the shock load to one end of the shock absorbing direction of the component, a shock absorbing component for absorbing impact energy, 　the surface layer having a Young's modulus than the core layer on both sides of the core layer is made of a large metal plate There are laminated, the thickness of the surface layer (t f thickness of) and said core layer (t c thickness ratio of the) (t c / t f cross section) is 2.0 to 7.0 constructed shock absorbing component in member formed by molding the uniform laminate metal plate. [Requested item 11] 　The plate thickness ratio (t c / t f shock absorbing component of claim 10) is 3.5-5.0. [Requested item 12] 　The Young's modulus ratio (E c / E f shock absorbing component according to claim 10 or claim 11) is 1 / 10-1 / 1000. [Requested item 13] 　The laminated metal sheet is formed into a shape having at least four edges, 　interval of the ridge, the shock absorbing component according to any one of claims 10 to claim 12 each of which is 50 - 80 mm . [Requested item 14] 　The laminated metal plate, further comprising a surface layer and a bonding layer between the core layer, 　the impact of any one of the shear modulus of the bonding layer is 30 ~ 500 MPa claims 10 to claim 13 absorption parts. Corrected claims (Convention Article 19) [July 9, 2014 (09.07.2014) The International Bureau acceptance] [1] When the impact load loaded on the one end portion of the impact-absorbing direction of the corrected] parts, a shock absorbing component for absorbing impact energy by buckling, 　Young than the core layer on both sides of the core layer the rate and density is bonded laminate surface layer consisting of a large metal plate section is uniform laminated metal plate, a member formed by molding into a shape having at least two edges, the longest peripheral length of the part cross-section 50 % or more comprise are configured, the thickness of the surface layer (t f thickness of) and said core layer (t c thickness ratio (t a) c / t f shock absorbing component) is 10.0 or less. [2] 　Shock absorbing component of claim 1 shape of the component cross section of the shock absorbing component are all open cross-sectional shape. [3] 　Shock absorbing component of claim 1 shape of the component cross section of the shock absorbing component is part open cross-sectional shape. [4] 　Shock absorbing component of claim 1 shape of the component cross section of the shock absorbing component are all closed section. [5] 　The laminated metal sheet has a Young's modulus of the surface layer (E f the Young's modulus) of said core layer (E c Young's modulus ratio of the) (E c / E f claims) is 1 / 10-1 / 100,000 shock absorbing component according to any one of 1-4. [6] 　The Young's modulus ratio (E c / E f ) an impact-absorbing component according to any one of claims 1 to 5, which is 1 / 10-1 / 1000. [7] 　Shock absorbing component according to any one of claims 1 to 6 intervals of the ridge is at least 10 mm. [8] 　Shock absorbing component according to any one of claims 1 to 7 shear bond strength between the surface layer and the core layer is not less than 25 MPa. [9] 　The bonding lamination of the surface layer and the core layer, the shock absorbing component according to any one of claims 1 to 8, an adhesive in the brazing material or a conductive adhesive. [10] When the impact load loaded on the one end portion of the impact-absorbing direction of the corrected] parts, a shock absorbing component for absorbing impact energy by buckling, 　Young than the core layer on both sides of the core layer rates are surface laminated consisting of large metal plate, the plate thickness of the surface layer (t f thickness of) and said core layer (t c thickness ratio of the) / t f ) is 2.0 shock absorbing component constructed of a member-7.0 cross section formed by molding a uniform laminated metal plate. [11] 　The plate thickness ratio (t c / t f shock absorbing component of claim 10) is 3.5-5.0. [12] 　The Young's modulus ratio (E c / E f shock absorbing component according to claim 10 or claim 11) is 1 / 10-1 / 1000. [13] 　The laminated metal sheet is formed into a shape having at least four edges, 　interval of the ridge, the shock absorbing component according to any one of claims 10 to claim 12 each of which is 50 - 80 mm . [14] 　The laminated metal plate, further comprising a surface layer and a bonding layer between the core layer, 　the impact of any one of the shear modulus of the bonding layer is 30 ~ 500 MPa claims 10 to claim 13 absorption parts. Instructions under the Convention Article 19 (1) 　For claims 1 and 10, the shock absorbing component is made clear that this is intended to absorb the impact energy by buckling deformation. 　The literature 1, the door structure in consideration of the side collision of the vehicle has been described, the input and the deformation direction of the load is the thickness direction of the door. If that buckling deformation of the door, that direction, ridge laminated steel sheet 3,4 extending direction, that is considered the vehicle front-rear direction. Accordingly, the door structure of the document 1 is not intended to absorb impact energy by buckling deformation. 　Shock absorbing component according to the present invention has the advantage that stable bellows-shaped collapsible deformation possible, a large maximum load Pmi during buckling deformation, capable of expressing characteristics such as seat屈波length H is small.