JP2008189155A - Car body strength adjusting device of vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To surely exhibit the shock absorbing effect by preventing a fall of buckling plates of a collapse strength variable device when a collision load in the oblique direction is applied to a bumper beam. <P>SOLUTION: The collapse strength variable device 13 having a front base board 35 fixed to the bumper beam and having a rear base board 16 fixed to a car body frame, has the right-left buckling plates 24 and 25 absorbing a shock by buckling by the load inputted in the car body longitudinal direction along the axis L, and a trapezoidal fall preventive plate 39 arranged between the right-left bucking plates 24 and 25 and preventing the fall of the buckling plates 24 and 25 by the load inputted in the inclined direction to the car body longitudinal direction. Thus, even when the load is inputted in the inclined direction to the car body longitudinal direction, the shock absorbing effect can be exhibited by surely buckling the buckling plates 24 and 25 by a component in the car body longitudinal direction of the load by preventing the fall of the buckling plates 24 and 15 by the fall preventive plate 39. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a vehicle body strength adjusting device for a vehicle in which a crushing strength variable device is provided between a bumper beam and a vehicle body frame, and a crushing strength variable device that can be crushed by receiving a collision load in the longitudinal direction of the vehicle body.

  A bumper beam attached to the front end of the front side frame of an automobile is composed of a pair of front and rear beam members arranged in parallel to each other and a plurality of variable crushing strength devices arranged at predetermined intervals between both beam members. Is known from Patent Document 1 below.

The crushing strength variable device has a plurality of shape memory alloy buckling plates arranged adjacent to each other so as to buckle by the impact of a collision, and these buckling plates are integrally connected and separated from each other. It is possible to increase the impact energy that can be absorbed by increasing the buckling strength when the buckling plates are connected together, and the buckling strength when the buckling plates are separated from each other. Can be absorbed to reduce the impact energy that can be absorbed.
JP 2006-8106 A

  By the way, when the vehicle collides head-on and a load in the longitudinal direction of the vehicle body is input to the bumper beam, the buckling plate of the variable crushing strength device can buckle without falling laterally and exert an impact absorbing effect. However, if the vehicle collides diagonally and a load in the direction inclined with respect to the longitudinal direction of the vehicle body is input to the bumper beam, the buckling plate falls down in the lateral direction without buckling, and a sufficient impact absorbing effect is obtained. You may not be able to demonstrate it.

  The present invention has been made in view of the above-described circumstances, and when the bumper beam is subjected to an oblique collision load, the buckling plate of the variable crushing strength device is prevented from falling and the shock absorbing effect is reliably exhibited. With the goal.

  In order to achieve the above object, according to the first aspect of the present invention, a crushing strength varying device capable of varying a crushing strength that is crushed by receiving a collision load in the longitudinal direction of the vehicle body between the bumper beam and the vehicle body frame. In the vehicle body strength adjusting device of the vehicle, the crushing strength varying device inputs the buckling plate that buckles by a load input in the longitudinal direction of the vehicle body and absorbs the impact, and the direction that is inclined with respect to the longitudinal direction of the vehicle body. There is proposed a vehicle body strength adjusting device for a vehicle, comprising a fall prevention plate for preventing the buckling plate from falling due to a load.

  According to the second aspect of the present invention, in addition to the configuration of the first aspect, the fall prevention plate is inclined in the vehicle longitudinal direction rather than the buckling rigidity with respect to the load input in the vehicle longitudinal direction. A vehicle body strength adjusting device is proposed in which the buckling rigidity with respect to the load inputted to the vehicle is set high.

  The front side frame 12 of the embodiment corresponds to the body frame of the present invention, and the first and second buckling plates 24 and 25 of the embodiment correspond to the buckling plate of the present invention. The first and second fall prevention plates 39, 39A, 39B, and 41 correspond to the fall prevention plates of the present invention.

  According to the configuration of the first aspect, the variable crushing strength device disposed between the bumper beam and the vehicle body frame includes a buckling plate that buckles by a load input in the vehicle longitudinal direction and absorbs an impact, and the vehicle longitudinal direction. The anti-falling plate prevents the buckling plate from collapsing due to the load input in the direction inclined to the buckling plate. By preventing the tilting of the body, the buckling plate can be reliably buckled by the component of the load in the longitudinal direction of the vehicle body, and the impact absorbing effect can be exhibited.

  According to the second aspect of the present invention, the buckling rigidity of the fall prevention plate against the load input in the direction inclined with respect to the vehicle longitudinal direction is greater than the buckling rigidity of the fall prevention plate against the load inputted in the vehicle longitudinal direction. Since it is set high, when a load is input in the longitudinal direction of the vehicle body, the fall prevention plate is easily buckled so as not to affect the load characteristics of the buckling plate, and in a direction inclined with respect to the longitudinal direction of the vehicle body. When a load is input, it is difficult to buckle the fall-preventing plate to prevent the buckling plate from falling, and the buckling plate can be reliably buckled to fully exhibit the shock absorbing performance.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  1 to 13 show a first embodiment of the present invention. FIG. 1 is a plan view of a front part of a vehicle body of a vehicle, FIG. 2 is an enlarged view of part 2 of FIG. 1, and FIG. 4 is an exploded perspective view of the crushing strength varying device, FIG. 5 is a cross-sectional view taken along line 5-5 in FIG. 2, FIG. 6 is a cross-sectional view taken along line 6-6 in FIG. 7 is a sectional view taken along the line 7; FIG. 8 is a view taken in the direction of the arrow 8 in FIG. 2; FIG. FIG. 12 is a diagram for explaining the action of the first and second buckling plates during buckling, and FIG. 13 is a diagram for explaining the action of the bumper beam extending and deforming at the time of collision.

  As shown in FIG. 1, a bumper beam 11 disposed at the front of a vehicle body of a four-wheel vehicle is inclined toward the rear of the vehicle body from a body portion 11a extending linearly in the vehicle width direction and from both left and right ends of the body portion 11a. Left and right inclined portions 11b, 11b. Front ends of front side frames 12, 12 arranged in the front-rear direction on both sides of the vehicle body and left and right inclined portions 11 b, 11 b of the bumper beam 11 are connected by crushing strength variable devices 13, 13 that can change the crushing strength. The Since the left and right crushing strength varying devices 13 and 13 have substantially the same structure, the structure will be described below by taking the left crushing strength varying device 13 as an example.

  As shown in FIGS. 2 to 7, the mounting plate 14 of the crushing strength varying device 13 is fixed to the end plate 12a that closes the front end opening of the front side frame 12 having a box cross section with four bolts 15. A rear substrate 16 composed of a disk-shaped thick plate is fixed to the front surface of 14 with four bolts 17. A spacer plate 18, a hinge support plate 19 and a block member 20 are superimposed on the front surface of the rear substrate 16, and four bolts 21 inserted backward from the inside of the lightening holes 20a of the block member 20 are hinges. The support plate 19 and the spacer plate 18 are penetrated and fastened to the rear substrate 16.

  The hinge plates 22 respectively disposed on the left and right sides of the block member 20 have a pair of lock pin support portions 22a and 22a bent in a cylindrical shape, and first and second extending so as to be separated from the lock pin support portions 22a and 22a. Second hinge arms 22b and 22c are provided. The rear end of the first hinge arm 22b is welded to the corner of the outer end of the hinge support plate 19 (see FIG. 3), and the second hinge arm 22c is welded to the outer surface of the first buckling plate 24 made of iron (W2 ( 3). The first buckling plate 24 includes a rib 24a for adjusting the buckling strength at the center portion and four fixing claws 24b. A rectangular second buckling plate 25 formed of a shape memory alloy and approximately the same size as the first buckling plate 24 is superimposed on the inner surface of the first buckling plate 24 by the four fixing claws 24b. Fixed to.

  Since the second buckling plate 25 made of shape memory alloy is difficult to process and unsuitable for welding, it is difficult to integrate the first and second buckling plates 24 and 25 by bolting or welding. Since the first and second buckling plates 24 and 25 are integrated with the fixing claws 24b provided on the first buckling plate 24 made of iron that is easy to process, the first and second seats are reduced while reducing the processing cost. The bent plates 24 and 25 can be reliably integrated.

  Although the positions of the front ends of the first and second buckling plates 24 and 25 are aligned, the rear end of the second buckling plate 25 extends slightly rearward from the rear end of the first buckling plate 24. (See FIG. 2). That is, the longitudinal length of the first buckling plate 24 is slightly shorter than the longitudinal length of the second buckling plate 25.

  Support grooves 20b and 20b having a U-shaped cross section extending in the vertical direction are formed on the left and right sides of the front surface of the block member 20, and a cylindrical bush 26 is fixed to each support groove 20b. Two lock pins 27, 27 are slidably supported inside the bush 26, and a common pinion 28 meshes with racks 27a, 27a formed on the side surfaces of the lock pins 27, 27 facing each other. To do. The pinions 28 are fixed to both ends of a rotating shaft 29a of a motor 29 supported by a motor support hole 20c formed in front of the lightening hole 20a of the block member 20. Therefore, when the pinion 28 is rotated by the motor 29, the two lock pins 27, 27 having the racks 27a, 27a driven by the pinion 28 move in directions toward and away from each other.

  Usually, the tapered engaging portions 27 b and 27 b at the tips of the two lock pins 27 and 27 protrude from the ends of the bush 26, and the engaging portions 27 b and 27 b at the tips are a pair of locks of the hinge plate 22. When the lock pins 27, 27 are driven by the motor 29 and are pulled into the bush 26 when engaged with the receiving members 51, 51 press-fitted into the pin support portions 22 a, 22 a (see solid lines in FIGS. 5 and 6). The engaging portions 27b, 27b at the tips are separated from the pair of receiving members 51, 51 of the hinge plate 22 (see the chain lines in FIGS. 5 and 6).

  The two divided first motor support plates 30, 30 are fixed around the motor support hole 20 c of the block member 20 with two bolts 31, 31, respectively, and the second motor support plate 32 is a motor of the block member 20. It is fixed around the support hole 20c by four bolts 33, and the motor 29 is supported so as to be sandwiched between the first and second motor support plates 30, 30;

  On the other hand, on the front surface of the block member 20, a pair of left and right inner buckling plate support plates 34, 34 and an outer buckling plate support plate 36 integrally provided with a thick disc-shaped front substrate 35 are superimposed, The eight bolts 37..., 38. And the buckling plate support part 34a which bent the left-right direction outer end of each inner buckling plate support plate 34 at the groove shape is engaged with the front end of the 1st, 2nd buckling plates 24 and 25 which were piled up. The first buckling plate 24 is welded W3 (see FIG. 3).

  The first fall-preventing plate 39 having a triangular rib 39a formed at the intermediate portion is provided with front and rear flanges 39b and 39c. The front flange 39b is the bolts 37 and 37 and the inner buckling plate support plate 34 and the outer side are provided. While being fastened together with the buckling plate support plate 36, the rear flange 39 c is fixed to the flange 30 a of the first motor support plate 30 with two bolts 40, 40. Further, the second fall prevention plate 41 having a triangular rib 41a formed at the intermediate portion is provided with front and rear flanges 41b and 41c, and the front flange 41b is formed by the bolts 38 and 38 with the inner buckling plate support plate 34 and While being fastened to the outer buckling plate support plate 36, the rear flange 41 c is fastened to the second motor support plate 32 by the bolts 33 and 33.

  The first and second fall prevention plates 39, 41 are substantially trapezoidal members, and the front edges corresponding to the upper bases thereof are fixed to the inner buckling plate support plate 34 and the outer buckling plate support plate 36, respectively. The rear edge corresponding to the lower base is fixed to the block member 20, and the left and right side edges corresponding to the pair of oblique sides face the inner surface of the second buckling plate 25 with a slight gap α (see FIG. 2). .

  As apparent from FIGS. 2 and 8, the mounting bracket 42 for connecting the bumper beam 11 and the crushing strength varying device 13 is inclined with respect to the axis L extending in the longitudinal direction of the vehicle body, and the inclined portion of the bumper beam 11 is inclined. 11b, a first mounting portion 42a parallel to the crushing strength variable device 13, a second mounting portion 42b parallel to the front substrate 35, and the first and second mounting portions 42a, 42b extending in the longitudinal direction of the vehicle body. And a plurality of thin ribs 42c. Four first bolt holes 11c, which are long in the left-right direction, are formed on the rear surface of the inclined portion 11b of the bumper beam 11, and the first bolt holes 11c ... and the first mounting portions 42a of the mounting bracket 42 are provided. The two bolt holes 42d are fastened by four bolts 43 and four nuts 44. Then, the second mounting portion 42 b of the mounting bracket 42 and the front substrate 35 of the crushing strength varying device 13 are fastened by two bolts 45, 45.

  As shown in FIGS. 1 and 2, the crushing strength varying device 13 configured as described above is housed in a stretchable rubber boot 46, and the rear opening 46 a of the boot 46 is a circular rear substrate. The front opening 46 b of the boot 46 is fitted to the outer periphery of the circular front substrate 35 and fastened by the band 48. As a result, the boot 46 can block water and mud from adhering to the crushing strength varying device 13, thereby improving the durability and ensuring the reliability of the operation.

  As apparent from FIGS. 1 to 4, the harness 49 extending from the motor 29 passes through the opening 30 b of the first motor support plate 30, 30, and then the opening 20 d of the block member 20, the opening 19 a of the hinge support plate 19, It passes through the grommet 52 attached to the opening 18a of the spacer plate 18 and the opening 16a of the rear substrate 16, and further passes through the opening 14a of the mounting plate 14 and the opening 12b of the end plate 12a of the front side frame 12, and Led inside. Accordingly, it is not necessary to form a hole in the boot 46 and pull out the harness 49 to ensure the waterproof property of the boot 46, and the harness 49 is guided to the inside of the front side frame 12 having a closed cross section. Can be protected from water and mud.

  Next, the operation of the first embodiment of the present invention having the above configuration will be described.

  Normally, the lock pins 27 and 27 of the variable crushing strength device 13 protrude from both ends of the bush 26, and therefore the engaging portions 27 b and 27 b at the tips of the lock pins 27 and 27 are formed on the receiving members 51 and 51 of the hinge plate 22. They are engaged (see solid lines in FIGS. 5 and 6). When the vehicle collides head-on in this state and a collision load to the rear of the vehicle body is applied to the bumper beam 11, the front board 35 and the rear board 16 of the crushing strength varying device 13 disposed between the bumper beam 11 and the front side frame 12. Is compressed in the front-rear direction.

  At this time, as shown in FIG. 9, the lock pin support portions 22a and 22a of the hinge plate 22 are restricted from moving in the left and right directions by the lock pins 27 and 27, and the lock pins 27 and 27 are strong block members. Since the rearward movement is restricted by 20, the overlapped first and second buckling plates 24 and 25 are compressed in the front-rear direction and buckled, so that the crushing strength varying device 13 absorbs a large collision energy. (High load mode).

  On the other hand, when a collision that requires a reduction in impact is predicted from the external situation detected by a radar device or a TV camera mounted on the vehicle and the vehicle speed detected by the vehicle speed sensor, the motor 29 is activated and the pinion 28 is operated. Further, by retracting the pair of lock pins 27, 27 into the bush 26 via the racks 27a, 27a, the engaging portions 27b, 27b of the lock pins 27, 27 are detached from the receiving members 51, 51 of the hinge plate 22. (See the chain line in FIGS. 5 and 6). As a result, the lock pin support portions 22a and 22a of the hinge plate 22 can move in the left-right direction, and the first and second buckling plates 24 and 25 are folded without buckling as shown in FIG. The crushing strength varying device 13 crushes with a small load and allows the bumper beam 11 to retreat (low load mode).

  In both the high load mode and the low load mode described above, the first and second fall prevention plates 39 and 41 are buckled by receiving a compressive load in the front-rear direction, but originally the first and second fall prevention plates 39. , 41 are formed of thin plates, and triangular ribs 39a, 41a are formed at the center, so that they are buckled very easily when subjected to a load in the front-rear direction, and energy in the front-rear direction of the crushing strength varying device 13 Does not affect the absorption characteristics. Accordingly, even in the low load mode in which the crushing strength varying device 13 is desired to be crushed with a low load, there is no possibility that the crushing strength varying device 13 is not easily crushed by the first and second collapse prevention plates 39 and 41. 9 and 10, the first and second fall prevention plates 39 and 41 are not shown.

  The first and second fall prevention plates 39 and 41 perform their functions when a collision load inclined with respect to the longitudinal direction of the vehicle body is applied to the bumper beam 11 during an oblique collision. The collision load at the time of the oblique collision is decomposed into a front-rear direction load that moves the bumper beam 11 rearward of the vehicle body and a left-right direction load that moves the bumper beam 11 in the vehicle width direction.

  As schematically shown in FIG. 11A, when a lateral load is input to the crushing strength varying device 13, a shearing force acts between the front substrate 35 and the rear substrate 16, and therefore the first and second on the right side. There is a possibility that the buckling plates 24 and 25 and the first and second buckling plates 24 and 25 on the left side will collapse in the left-right direction without buckling, and even in the high load mode, the energy absorbing performance cannot be exhibited. There is.

  However, as shown in FIG. 11B, in the present embodiment, a total of four first and second collapses in a trapezoidal space sandwiched between the left and right second buckling plates 25, 25 facing each other. Since the prevention plates 39 and 41 are arranged, these first and second fall prevention plates 39 and 41 fall on the left and right first and second buckling plates 24 and 25 in the state shown in FIG. The crushing strength varying device 13 can be reliably crushed in the front-rear direction, and the energy absorption performance can be efficiently exhibited.

  In addition, since the triangular ribs 39a and 41a (see FIG. 7) are formed on the first and second collapse prevention plates 39 and 41, the load at which buckling is started can be reduced, and a characteristic with little load fluctuation can be obtained. it can. A slight gap α (see FIG. 2) exists between the first and second collapse prevention plates 39 and 41 and the second buckling plate 25, but the first and second buckling plates 24 and 25 are present. Since the second buckling plate 25 comes into contact with the first and second fall prevention plates 39 and 41 when there is a slight fall, there is no problem.

  By the way, in the high load mode in which the variable crushing strength device 13 is crushed with a large load, the first and second buckling plates 24 and 25 that buckle generate a constant high load from the start to the end of the crushing. Is desirable.

  As is apparent from the graph showing the relationship between time (displacement) and load in FIG. 12, the first buckling plate 24 made of a general iron material has a peak due to a sudden increase in load as the amount of displacement increases. It has a characteristic of gradually decreasing after reaching the limit. On the other hand, the second buckling plate 25 made of a shape memory alloy has a characteristic in which the load rapidly increases as the displacement increases, reaches a peak, rapidly decreases, reaches the bottom, and gradually increases from there. Have. Therefore, even if the first buckling plate 24 and the second buckling plate 25 are used alone, it is impossible to generate a constant high load from the start to the end of crushing. However, if the first buckling plate 24 is set to start deformation when the second buckling plate 25 starts deformation at time t1 and reaches a peak at time t2, the time t3 is changed from time t2 to time t3. After that, since the decrease / increase characteristic of the load of the second buckling plate 25 and the increase / decrease characteristic of the load of the first buckling plate 24 are symmetric in the vertical direction until time t4, they are added together. The characteristic can be an ideal characteristic indicated by a solid line, that is, a characteristic that generates a constant high load from the start to the end of crushing.

  The difference in timing at which the first and second buckling plates 24 and 25 start to deform can be obtained as follows. That is, the length in the front-rear direction of the first and second buckling plates 24 and 25 that are overlapped and integrated by the fixing claws 24b is the same as that of the second buckling plate 25 made of shape memory alloy. Since it is slightly longer than one buckling plate 24, the longer second buckling plate 25 starts to deform first (time t1), and after the second buckling plate 25 is compressed by a predetermined amount, The shorter first buckling plate 24 can be deformed together with the first buckling plate 25 (time t2).

  Since the second buckling plate 25 made of shape memory alloy is difficult to process compared to the iron material, the cost is reduced as a simple plate shape, but the thickness of the first buckling plate 24 made of iron material that is easy to process is reduced. Is set or a rib 24a having a predetermined shape is formed, so that a load symmetrical to the load generated by the second buckling plate 25 after time t2 can be generated. The load generation characteristics can be adjusted.

  In the embodiment, the first buckling plate 24 is made of iron, but other materials such as aluminum can be used.

  By the way, as shown in FIG. 13, when the vehicle collides head-on and a rearward load is applied to the bumper beam 11, the fragile ribs 42c of the mounting bracket 42 are crushed and tilted backward with respect to the main body 11a. Since the angle of the inclined portion 11b is deformed so as to be substantially parallel to the main body portion 11a, the dimension in the left-right direction of the bumper beam 11 is extended by β. At this time, if the bumper beam 11 and the crushing strength varying device 13 are coupled so as not to move relative to each other in the left-right direction, the crushing strength varying device 13 falls to the outside of the vehicle body due to the bumper beam 11 extending in the left-right direction. Therefore, there is a possibility that the collision load cannot be absorbed effectively.

  However, in the present embodiment, as shown in FIG. 8, the first bolt holes 11 c formed on the rear surface of the inclined portion 11 b of the bumper beam 11 are elongated holes in the left-right direction. The inclined portion 11b of the bumper beam 11 can slide to the outside of the vehicle body with respect to the bolts 43 passing through the bolt holes 11c and the second bolt holes 42d of the mounting bracket 42. Therefore, even if the bumper beam 11 extends in the left-right direction at the time of a frontal collision, the crushing strength varying device 13 can be prevented from falling to the outside of the vehicle body, and the function of the crushing strength varying device 13 can be exhibited reliably.

  Furthermore, since it becomes easy to deform in the front-rear direction in the low load mode, it is possible to set a target load without reducing the compressive strength of the first and second fall prevention plates 39 and 41. Accordingly, it is possible to prevent a decrease in the lateral collapse strength in the left-right direction.

  Next, a second embodiment of the present invention will be described with reference to FIG.

  The second embodiment is a modification of the first embodiment, in which two slits 39d and 39d are formed along the tops of the ribs 39a of the first fall prevention plate 39. By the slits 39d and 39d, the first fall prevention plate 39 can be more easily buckled by the load in the longitudinal direction of the vehicle body, with almost no decrease in buckling rigidity against the load in the oblique direction. A similar slit can be provided in the second fall prevention plate 41.

  Next, a third embodiment of the present invention will be described with reference to FIG.

  In the first embodiment, the first fall prevention plate 39 includes a triangular rib 39a. However, in the third embodiment, the entire first fall prevention plate 39 is curved in an arc shape. Therefore, the first fall prevention plate 39 can be easily buckled by a load in the longitudinal direction of the vehicle body while exhibiting a strong buckling rigidity against a load in an oblique direction. Note that the second fall prevention plate 41 can have a similar arc shape.

  Next, a fourth embodiment of the present invention will be described with reference to FIGS.

  In the first embodiment, the first and second fall prevention plates 39 and 41 made of a thin plate are provided. However, as shown in FIG. 16, in the fourth embodiment, the fall of a thick plate divided into two parts is performed. Prevention plates 39A and 39B are provided. The outer ends in the left-right direction of both fall prevention plates 39A, 39B are fixed to the side edges of the first buckling plate 24, and the inner ends are opposed to each other with a slight gap γ.

  When the first and second buckling plates 24 and 25 are buckled in the high load mode, the fall prevention plates 39A and 39B are peeled off and separated from the first buckling plate 24, and the first and second seats in the low load mode. When the bent plates 24 and 25 fall down, the fall prevention plates 39A and 39B move so as to widen the gap γ, so that they hardly affect the crushing of the crushing strength varying device 13 (see FIG. 17A). ).

  However, when the load in the oblique direction is input and the first and second buckling plates 24, 25 on the right side and the left side are about to fall sideways, the gap γ disappears and the fall prevention plates 39A, 39B hit each other. By contacting and supporting the shearing force, the left and right first and second buckling plates 24 and 25 can be reliably prevented from falling in the lateral direction (see FIG. 17B).

  Therefore, also according to the fourth embodiment, the same operational effects as those of the first to third embodiments can be achieved.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, the embodiment has described the crushing strength varying device 13 for the bumper beam 11 of the front bumper, but the present invention can also be applied to the crushing strength varying device 13 for the bumper beam of the rear bumper.

The top view of the vehicle body front part of the vehicle which concerns on 1st Embodiment 2 enlarged view of FIG. Perspective view of variable crushing strength device Exploded perspective view of variable crushing strength device Sectional view along line 5-5 in FIG. 6-6 sectional view of FIG. Sectional view along line 7-7 in FIG. 8 direction arrow view of FIG. Action diagram of low load mode Action diagram of high load mode Action explanatory view of the first and second fall prevention plates Action explanatory diagram at the time of buckling of the first and second buckling plates Action explanatory diagram of bumper beam elongation deformation at the time of collision The figure which shows the shape of the fall prevention board which concerns on 2nd Embodiment The figure which shows the shape of the fall prevention board which concerns on 3rd Embodiment The figure corresponding to said 2 based on 4th Embodiment Action explanatory diagram of the fall prevention plate

Explanation of symbols

11 Bumper beam 12 Front side frame (body frame)
13 Crushing strength variable device 24 1st buckling plate (buckling plate)
25 Second buckling plate (buckling plate)
39 First fall prevention plate (fall prevention plate)
39A First fall prevention plate (fall prevention plate)
39B First fall-prevention plate (fall-prevention plate)
41 Second falling prevention plate (falling prevention plate)

Claims (2)

In a vehicle body strength adjusting device for a vehicle, in which a crushing strength varying device (13) is provided between the bumper beam (11) and the vehicle body frame (12), and the crushing strength variable device (13) that is crushed by receiving a collision load in the longitudinal direction of the vehicle body is arranged.
The variable crushing strength device (13) includes a buckling plate (24, 25) that buckles by a load input in the vehicle longitudinal direction and absorbs an impact, and the load that is input in a direction inclined with respect to the vehicle longitudinal direction. A vehicle body strength adjusting device for a vehicle, comprising a fall prevention plate (39, 39A, 39B, 41) for preventing the buckling plate (24, 25) from falling.   The fall prevention plates (39, 41) are characterized in that the buckling rigidity with respect to the load input in the direction inclined with respect to the vehicle longitudinal direction is set higher than the buckling rigidity with respect to the load input in the vehicle longitudinal direction. The vehicle body strength adjusting device for a vehicle according to claim 1.

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