JP5942871B2 - Vehicle body structure - Google Patents

Description

  The present invention relates to a vehicle body structure having a reinforcing body coupled to the inside of a vehicle body member having a closed cross section formed by one or more members.

In general, a vehicle frame such as a floor frame, a side sill, a pillar, a roof rail, and a floor cross member has a closed cross section formed by one or more members.
In the vehicle body member having such a closed cross-section portion, various techniques are known that are configured to reduce vibration transmitted to the vehicle body member in order to improve riding comfort performance while being lightweight.

  For example, Patent Document 1 discloses a partition wall member (so-called partition wall member) in which a closed cross-section portion including a frame member (frame member) having a cross-sectional hat shape and a panel member (secondary material) is provided, and a bead is integrally formed in the closed cross-section portion. And a flange portion formed integrally with the partition wall member and an inner wall of the frame member having a hat-shaped cross section to increase the strength and rigidity of the frame member.

  In the conventional structure disclosed in Patent Document 1, the above-described partition wall member (node member) suppresses the collapse of the cross-section of the closed cross-section portion, thereby increasing the strength and rigidity of the frame member, and by increasing the strength and rigidity, Although the vibration can be reduced to some extent, there is a problem that the vibration cannot be effectively suppressed because it is not yet sufficient.

JP 2006-131125 A

  Therefore, the present invention can effectively suppress vibration while ensuring rigidity. In particular, the present invention not only attenuates vibration in the torsion mode and rhombus mode, but also attenuates vibration in the bending mode. It is an object of the present invention to provide a vehicle body structure that can enhance the damping effect.

The vehicle body structure of the vehicle according to the present invention is a vehicle body structure having a reinforcing body coupled to the inside of a vehicle body member having a closed cross section formed by one or two or more members, wherein the closed cross section and the reinforcement are provided. The joint part with the body includes a rigid joint part joined in a state of abutting each other, a soft joint part joined via a damping member disposed between the closed cross-section part and the reinforcing body, The flexible coupling part includes a first flexible coupling part substantially parallel to the closed cross-sectional direction of the closed cross-sectional part, and a second flexible joint part substantially perpendicular to the closed cross-sectional direction of the closed cross-sectional part. The reinforcing body includes a first node member substantially parallel to the closed section direction of the closed section, and a second node member substantially perpendicular to the closed section direction of the closed section, the first node member being A plate-like node member and a plurality of joint flange portions formed by bending the node member. And a plurality of joint flange portions formed by bending the joint member. The first flexible joint portion includes one joint flange portion of the first joint member and an inner wall of the closed cross section. The second flexible joint portion is formed between the joint flange portion of the second knuckle member and the inner wall portion of the closed cross-sectional portion by way of the attenuation member. The rigid joint portion is formed by joining the other flange portion of the first joint member and the inner wall portion of the closed cross-section portion in contact with each other, and the other joint portion of the second joint member. It is formed by joining the flange portion and the inner wall portion of the closed cross-section portion in contact with each other, and the damping member has a temperature of 20 ° C. and a vibration force frequency of 30 Hz. Storage modulus is 0.6 to 500 MPa, loss factor is 0.2 or more It has been at + those composed of viscoelastic member is.
The vehicle body member described above may be set to a vehicle frame such as a floor frame, a side sill, a front pillar, a center pillar, a rear pillar, a roof rail, and a floor cross member.
Moreover, you may comprise the above-mentioned rigid coupling part by the fastening joining by fastening members, such as welding joining by spot welding etc., the adhesive joining by an adhesive agent, and a volt | bolt and a nut.

According to the said structure, since the reinforcement body is couple | bonded with the closed cross-section part of the vehicle body member by the said rigid coupling part, the rigidity of a vehicle body member is securable.
In addition, the first soft coupling portion that is substantially parallel to the closed cross-section direction of the closed cross-section portion can attenuate vibrations of the torsion mode and the rhombus mode, and the second soft coupling is substantially perpendicular to the closed cross-section direction of the closed cross-section portion The vibration of the bending mode can be attenuated at the part. Therefore, the vibration damping effect can be enhanced.
In short, vibration can be effectively suppressed while securing rigidity, and in particular, not only the vibration of the torsion mode and the rhombus mode is attenuated, but also the vibration of the bending mode is also attenuated, thereby reducing the vibration damping effect. Therefore, riding comfort can be improved and noise can be reduced.

Furthermore, the damping member is a viscoelastic member having a storage elastic modulus of 0.6 to 500 MPa and a loss factor of 0.2 or more under the conditions that the temperature is 20 ° C. and the frequency of the excitation force is 30 Hz. Thus, the strain energy sharing ratio of the damping member (that is, the ratio of the strain energy applied to the target damping member when the strain energy of the entire structure is 100% in a certain mode) Therefore, the vibration damping effect can be further enhanced.
Incidentally, when the storage elastic modulus is less than 0.6 MPa or exceeds 500 MPa, the strain energy sharing ratio becomes insufficient.

  In one embodiment of the present invention, the second flexible joint portion is provided so as to intersect the first flexible joint portion.

  According to the above configuration, since the second flexible coupling portion is arranged to intersect the first flexible coupling portion, the vibration damping effect of the bending mode by the second flexible coupling portion can be increased.

In one embodiment of the present invention, the first flexible coupling portion is disposed so as to include a bending point of the bending mode of the vehicle body member.
The bending point of the above bending mode means a portion where the curvature is maximum in the bending mode.

The above configuration has the following effects.
That is, the damping effect of the flexible joint portion is basically higher as the amount of deformation is larger. Therefore, by arranging the first flexible joint portion so as to include the bending point of the vehicle body member, vibration damping The effect can be further enhanced.

  In one embodiment of the present invention, the vehicle body member is a frame member formed by joining a cross-sectional hat-shaped member and a flat plate, a flange portion of the cross-sectional hat-shaped member and a flat plate, or two cross-sectional hat shapes. A frame member formed by joining the flange portions of the member, wherein the flexible coupling portion is formed between an inner wall portion substantially parallel to the flange portion and the reinforcing body.

  According to the above configuration, the frame member is more likely to generate a bending mode in a direction perpendicular to the surface of the flange portion than in a direction parallel to the surface of the flange portion. By providing (the first flexible coupling portion and the second flexible coupling portion), it is possible to further enhance the vibration damping effect, particularly the bending mode vibration damping effect.

  In one embodiment of the present invention, the second flexible coupling portion is provided so as to include a central portion in the width direction of the frame member.

The above configuration has the following effects.
That is, in the bending mode, the central portion of the frame member in the width direction is deformed inward and outward of the closed cross section. The vibration damping effect of the bending mode can be further enhanced by providing the second flexible coupling portion at the center portion in the width direction in which the degree of deformation is greatest.

In one embodiment of the present invention, the damping member has a storage elastic modulus of 0.7 to 200 MPa under a condition where the temperature is 20 ° C. and the frequency of the excitation force is 30 Hz. It is characterized by .

  According to the present invention, the joint between the closed cross-section and the reinforcing body includes a rigid joint that is joined in contact with each other, and a damping member disposed between the closed cross-section and the reinforcing body. A flexible coupling portion coupled via a first flexible coupling portion substantially parallel to the closed cross-sectional direction of the closed cross-sectional portion and the closed cross-sectional direction of the closed cross-sectional portion. Since the vertical second flexible coupling portion is provided, it is possible to effectively suppress vibration while ensuring rigidity, and in particular, not only attenuate vibrations in torsion mode and rhombus mode, Bending mode vibrations can also be damped, and the vibration damping effect can be enhanced.

The perspective view which shows the vehicle body structure of the vehicle of this invention 1 is a longitudinal sectional view of FIG. 1 is an enlarged perspective view of the main part of FIG. Illustration in bending mode A longitudinal sectional view showing a vehicle body structure of a comparative example Explanatory drawing at the time of bending mode in the comparative example Characteristic diagram showing the change in strain energy sharing ratio at the bending moment between the product of this example and the comparative product The characteristic figure which shows the change of the strain energy share to the storage elastic modulus of the damping member The perspective view which shows the other Example of the vehicle body structure of a vehicle The perspective view which shows the further another Example of the vehicle body structure of a vehicle

The object is to effectively suppress vibration while ensuring rigidity, and in particular to not only attenuate torsional and rhombus mode vibrations but also to attenuate bending mode vibrations to enhance the vibration damping effect. or in the vehicle structure of a vehicle having a reinforcing member coupled to the interior of the vehicle body member having a closed-section portion which is formed by two or more members, the joint between the reinforcing member and the closed-section portion has mutually abutting A rigid coupling portion coupled in a state and a flexible coupling portion coupled via a damping member disposed between the closed cross-section portion and the reinforcing body, and the flexible coupling portion is A first flexible joint portion substantially parallel to the closed cross-sectional direction of the cross-sectional portion and a second soft joint portion substantially perpendicular to the closed cross-sectional direction of the closed cross-sectional portion, and the reinforcing body closes the closed cross-sectional portion. A first knot member substantially parallel to the cross-sectional direction and a first knot substantially perpendicular to the closed cross-sectional direction of the closed cross-sectional portion. A node member, and the first node member includes a plate-like node member and a plurality of joint flange portions formed by bending the node member, and the second node member includes a plate-like node. And a plurality of joint flange portions formed by bending the joint member. The first flexible joint portion includes a joint flange portion of the first joint member and an inner wall portion of the closed cross section. Formed by interposing a damping member therebetween, the second flexible joint portion is formed by interposing the attenuation member between one joint flange portion of the second knuckle member and the inner wall portion of the closed cross-section portion, The rigid coupling part is coupled with the other joint flange part of the first joint member in contact with the inner wall part of the closed cross section, and with the other joint flange part of the second joint member. It is formed by combining the closed wall with the inner wall of the closed section. The damping member is composed of a viscoelastic member having a storage elastic modulus of 0.6 to 500 MPa and a loss coefficient of 0.2 or more under the condition that the temperature is 20 ° C. and the frequency of the excitation force is 30 Hz. It was realized by the configuration that is Ru is.

An embodiment of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a perspective view showing the vehicle body structure, FIG. 2 is a longitudinal sectional view thereof, and FIG. 3 is an enlarged perspective view of a main part of FIG.
In FIG. 1 to FIG. 3, a frame member 40 in which a closed cross-section portion 30 is formed by a cross-sectional hat-shaped member 10 and a panel member 20 (see FIG. 2) as a flat plate is provided. ing.

The above-described cross-section hat-shaped member 10 (frame member) is outward from the base wall 11, the pair of side walls 12, 13 continuous to the base wall 11, and the end portions of the side walls 12, 13 on the opposite base wall side. This is a vehicle member in which extending flange portions 14 and 15 are integrally formed.
Moreover, although the flat flat plate member was illustrated as the above-mentioned panel member 20, this may be a member with a hat-shaped cross section like the cross-sectional hat-shaped member 10.

As shown in FIG. 2, the frame member 40 described above is formed by joining the flange portions 14 and 15 of the cross-sectional hat-shaped member 10 and the panel member 20.
In the frame member 40 formed of two members (the cross-sectional hat-shaped member 10 and the panel member 20) and having the closed cross-section portion 30, the node members 50 and 60 are provided as reinforcing members. 1, the first knot member 50 substantially parallel to the closed section direction (arrow X direction) of the closed section 30, and substantially perpendicular to the closed section direction (arrow X direction) of the closed section 30 (arrow Y direction). Two second node members 60, 60, and the second node members 60, 60 extending in the arrow Y direction intersect with the first node member 50 extending in the arrow X direction. As seen from the opening direction of the cross-sectional hat-shaped member 10, these joint members 50, 60 are combined in a cross shape.
Here, the closed cross-sectional direction is a direction parallel to the depth direction and the width direction, that is, a direction parallel to the first knot member 50.

As shown in FIG. 3, the first knot member 50 described above includes a plate-like knot member 51, joint flange portions 52 and 53 integrally formed on the left and right sides of the knot member 51, and a knot body 51. And flange portions 54 and 55 integrally bent at both upper and lower ends.
Further, as shown in the figure, each of the above-mentioned second knot members 60, 60 includes a plate-like knot body 61 and a joint flange 62 formed by bending integrally with the knot body 61 on the first knot member 50 side. And joint flange portions 63 and 64 integrally formed at both upper and lower end portions of the node main body 61.
Here, each joint flange 52, 53, 62 described above extends in the depth direction of the closed cross section 30, each joint flange 54, 55 extends in the arrow X direction, and each joint flange. 63 and 64 extend in the arrow Y direction.

  As shown in FIG. 3, the joint flange portions 62, 62 of the second node members 60, 60 extending in the arrow Y direction are brought into contact with the center portion in the width direction of the first node member 50 extending in the arrow X direction. The plate members are joined and fixed at spot welds a and a shown in FIG.

As shown in FIG. 2, the joint flange portion 55 at the lower part of the first knot member 50 is brought into contact with the inner surface of the base wall 11 of the cross-sectional hat-shaped member 10, and both of them are joined by a plurality of spot welds b and b. Bonded and fixed.
Further, as shown in FIG. 2, a joint flange portion 52 on one side of the first knot member 50 is brought into contact with the inner surface of the corresponding side wall 12 of the cross-sectional hat-shaped member 10, and both of these 52 and 12 are connected to a plurality of spots. It is bonded and fixed at the welds c and c.

  Similarly, as shown in FIG. 2, the joint flange portion 53 on the other side portion of the first knot member 50 is brought into contact with the inner surface of the corresponding side wall 13 of the cross-sectional hat-shaped member 10. Joined and fixed at spot welds d and d.

Further, as shown in FIG. 2, the joint flange portions 64 below the second joint members 60 and 60 are brought into contact with the inner surface of the base wall 11 of the cross-sectional hat-shaped member 10, and both the 64 and 11 are attached to the spot welded portion e. Are fixed.
That is, the joint portion between the closed cross-section portion 30 and the first and second joint members 50 and 60 that are the reinforcing members has a rigid joint portion that is joined in a state of being in contact with each other. Each spot weld b, c, d, e forms a rigid coupling. In addition, the number of the welding locations by each spot welding part b, c, d, e is not limited to the number of the example of illustration.
As the above-described rigid coupling portion, instead of the above-described spot welded portion, a fastening coupling portion such as a bolt or a nut may be used, or an adhesive joint portion using an adhesive may be used. Here, the adhesive used for the adhesive bonding of the rigid bond has a storage elastic modulus of 2000 MPa or more and a loss factor of 0.05 or less under conditions where the temperature is 20 ° C. and the frequency of the excitation force is 30 Hz. A viscoelastic member is used.

Furthermore, as shown in FIGS. 1-3, the soft coupling | bond part 71 couple | bonded via the damping member 70 arrange | positioned between the above-mentioned closed cross-section part 30 and the node members 50 and 60 as a reinforcement body, In this embodiment, the flexible coupling portions 71 and 72 are joined to the inner wall portion 21 of the panel member 20 substantially parallel to the flange portions 14 and 15 of the cross-sectional hat-shaped member 10 and the node members 50 and 60. It is formed between the upper surfaces of the flange portions 54 and 63.
And the above-mentioned flexible coupling parts 71 and 72 are the 1st flexible coupling part 71 substantially parallel to the closed sectional direction (arrow X direction) of the closed sectional part 30, and the closed sectional direction (arrow X direction) of the closed sectional part 30. 2nd flexible coupling part 72 of the direction (arrow Y direction) substantially perpendicular to this.

The first flexible coupling portion 71 extending in the arrow X direction attenuates vibrations in the torsion mode and the rhombus mode, and the second flexible coupling portion 72 extending in the arrow Y direction is configured to attenuate bending mode vibrations. ing.
Further, the two second flexible coupling portions 72, 72 extending in the arrow Y direction described above intersect with one first flexible coupling portion 71 extending in the arrow X direction, and are viewed from the opening direction of the cross-section hat-shaped member 10. It is provided so as to have a cross shape, and is configured to increase the vibration damping effect of the bending mode by the second flexible coupling portions 72, 72.

FIG. 4 is an explanatory view in the bending mode, and is an explanatory view in a state where both ends in the longitudinal direction (arrow Y direction) of the frame member 40 are restrained by restraining portions 80 and 80.
The bending point of the bending mode is when the thickness of the cross-sectional hat-shaped member 10 constituting the frame member 40 and the thickness of the panel member 20 are uniform in the longitudinal direction and the cross-sectional shape is uniform in the longitudinal direction. Is formed between the restraining portions 80 and 80, specifically, at the central portion.
Therefore, the first flexible coupling portion 71 described above is disposed so as to include the central portion or the substantially central portion of the restraining portions 80 and 80 so as to include the bending point of the bending mode. It is configured to further increase.

Here, it is as follows when the above-mentioned restraint part 80 is illustrated.
When the frame member 40 is applied to the floor cross member, the restraining portion 80 is set to the side sill and the tunnel portion, and when the frame member 40 is applied to the center pillar, the restraining portion 80 includes the roof side rail and the side sill. When the frame member 40 is applied to the dash cross member, the restraining portion 80 is set to the left and right hinge pillars. Thus, the restraining portion 80 restrains both ends of the frame member 40 in the longitudinal direction. It is set to the member.

Further, as shown in FIG. 2, the first and second flexible coupling portions 71, 72 have the inner wall portion 21 of the panel member 20 that is substantially parallel to the flange portions 14, 15 of the cross-sectional hat-shaped member 10, 60, the vibration damping effect is further enhanced.
That is, the frame member 40 tends to generate a bending mode in a direction perpendicular to the surfaces of the flange portions 14 and 15 as shown in FIG. 4 rather than in a direction parallel to the surfaces of the flange portions 14 and 15. By providing the flexible coupling portions 71 and 72 on the above-described inner wall portion 21 that is enlarged, the vibration damping effect, particularly the bending mode vibration damping effect, is further enhanced.

Furthermore, as shown in FIG. 1, the second flexible coupling portion 72 described above is provided so as to include the center portion in the width direction of the frame member 40, thereby further improving the vibration damping effect of the bending mode. It is comprised so that it may aim.
That is, in the bending mode, the central portion in the width direction of the frame member 40 is deformed in the inner and outer directions of the closed cross section 30. For example, the panel member 20 swells upward in the drawing in FIG. 2 or dents downward in the drawing (deformation in the cross-sectional direction in the bending mode). By providing the above-mentioned second flexible coupling portion 72 at the center portion in the width direction where the degree of deformation at that time becomes the largest, the vibration damping effect of the bending mode is further enhanced.

Since the damping member 70 forming the first and second flexible coupling portions 71 and 72 cannot perform vibration damping when there is no relative displacement, the degree of deformation of the frame member 40 (deformation amount). In order to enhance the vibration damping effect, it is effective to provide the damping member 70 at a portion where the maximum vibration ()) is the largest.
Further, the damping member 70 constituting each of the first and second flexible coupling portions 71 and 72 has a storage elastic modulus under the condition that the temperature is 20 ° C. and the frequency of the excitation force is 30 Hz. As shown in FIG. 8, it is comprised by the viscoelastic member whose loss coefficient is 0.2 or more in the range of 0.6-500 MPa.
Here, the above-described storage elastic modulus is more preferably in the range of 0.7 to 200 MPa, and further preferably in the range of 0.9 to 60 MPa.

In the characteristic diagram shown in FIG. 8, the horizontal axis represents the storage elastic modulus (unit: MPa) of the damping member, and the vertical axis represents the strain energy share (unit: percent) of the damping member. The storage elastic modulus of the damping member that maximizes the share of strain energy accumulated in the member is obtained by simulation.
From this analysis result, when the storage elastic modulus is in the range of 0.6 to 500 MPa, the strain energy sharing ratio is large, the vibration damping effect is high, and when the storage elastic modulus is in the range of 0.7 to 200 MPa, the strain energy sharing ratio. Is greater, the vibration damping effect is higher, and when the storage elastic modulus is in the range of 0.9 to 60 MPa, the strain energy share is further increased, and the vibration damping effect is further enhanced.

  By the way, as shown in FIG. 2, the notch recessed part 56 is each formed in the four corners of the 1st node member 50. As shown in FIG. The notch recess 56 avoids interference between the cross-section hat-shaped member 10 having the corner radius portion and the first knot member 50 when the first knot member 50 is disposed in the closed cross-section portion 30, and the frame member. This is to prevent the first knot member 50 from blocking the electrodeposition liquid when the anticorrosion coating is performed by immersing 40 in the electrodeposition tank.

  FIG. 5 is a longitudinal sectional view showing a comparative example of the vehicle body structure of the vehicle, in which the two second joint members 60 and 60 and the second flexible coupling portion 72 are removed from the embodiment shown in FIGS. . Also in FIG. 5, the other configurations are the same as those of the embodiment of FIGS. 1 to 3, and therefore the same parts in FIG. doing.

  The example product shown in FIG. 2 (so-called cross-shaped structure) and the comparative product shown in FIG. 5 (so-called I-shaped structure) are shown in FIG. 4 (example product) and FIG. 6 (comparative example product), respectively. As shown in FIG. 7, the strain energy sharing ratio when the vibration is applied under the same condition so that the bending mode is generated is obtained, and the result of comparison of the strain energy sharing ratio is shown in FIG.

  As is apparent from FIG. 7, the example product having both the first flexible coupling portion 71 and the second flexible coupling portion 72 with respect to the strain energy sharing ratio of the comparative example product having only the first flexible coupling portion 71. It was proved that the strain energy share was sufficiently large and the vibration damping effect was increased.

It has also been found that it is more effective to make the lengths of the second flexible joint portions 72, 72 on both sides of the crossing portion shown in FIG.
Furthermore, the effect is higher when the sum of the lengths of the two second flexible coupling portions 72, 72 in the arrow Y direction is longer than the length of the first flexible coupling portion 71 in the arrow X direction shown in FIG. That is, in the bending mode, the radius of curvature that bends in the longitudinal direction (arrow Y direction) is larger than that in the closed cross-sectional direction (arrow X direction), so that the two second flexible joint portions are longer than the length of the first flexible joint portion 71. The longer the sum of the lengths of arrows 72 and 72 in the arrow Y direction, the higher the vibration damping effect.
9 and 10 show another embodiment of a vehicle body structure.

  In the embodiment shown in FIG. 3, one first flexible coupling portion 71 and two second flexible coupling portions 72, 72 are combined in a cross shape. However, in the embodiment shown in FIG. One second joint member 60 and one second flexible coupling portion 72 are removed from the example, one first flexible coupling portion 71 extending in the arrow X direction, and extending in the arrow Y direction, and in the center in the width direction And a second joint member 60 located in a T-shape.

In the embodiment shown in FIG. 10, the second extending in the same direction (arrow Y direction) at the same position on both sides in the arrow Y direction on both ends in the width direction of one first flexible coupling portion 71 extending in the arrow X direction. A total of four joint members 60, 60 and second flexible coupling portions 72, 72 are provided, and these are combined in an H-shape.
9 and 10, the same parts as those in FIG. 3 are denoted by the same reference numerals, and detailed description thereof is omitted.
The H-shaped one shown in FIG. 10 also has the second flexible coupling portion 72 in addition to the first flexible coupling portion 71, so that the vibration damping effect in the bending mode can be particularly improved.

The T-shaped one shown in FIG. 9 has the second flexible coupling portion 72 and the second flexible coupling portion 72 is provided at the center in the width direction. A higher vibration damping effect can be ensured.
In the cross-shaped thing shown in FIG. 3, it has the 2nd flexible coupling part 72, and this 2nd flexible coupling part 72 is provided in the center of the width direction, and the arrow of the 1st flexible coupling part 71 Since the second flexible coupling portions 72 and 72 are provided on both sides in the Y direction, respectively, a higher vibration damping effect can be exhibited with respect to the T-shaped one.

  Thus, the vehicle body structure of the vehicle according to the above-described embodiment is a vehicle body member (see the frame member 40) having the closed cross-section portion 30 formed by one or more members (see the cross-sectional hat-shaped member 10 and the panel member 20). Vehicle body structure having a reinforcing body (refer to the node members 50 and 60) coupled to the interior of the vehicle, wherein the joint between the closed cross section 30 and the reinforcing body (the node members 50 and 60) corresponds to each other. A rigid coupling portion (see spot welded portions b, c, d, e) coupled in contact with each other, and a damping member disposed between the closed cross-section portion 30 and the reinforcing body (node members 50, 60). Flexible coupling portions 71 and 72 coupled via 70, wherein the flexible coupling portions 71 and 72 are first flexible layers substantially parallel to the closed sectional direction of the closed sectional portion 30 (see the arrow X direction). Nearly perpendicular to the closed section direction of the coupling section 71 and the closed section section 30 (see arrow Y direction) A second flexible joint section 72, those having a (FIGS. 2, 3, 9, see Fig. 10).

According to this configuration, the reinforcing bodies (node members 50, 60) are coupled to the closed cross-section portion 30 of the vehicle body member (frame member 40) by the rigid coupling portions (spot welds b, c, d, e). The rigidity of the vehicle body member (frame member 40) can be ensured.
In addition, the first flexible coupling portion 71 substantially parallel to the closed cross-section direction (arrow X direction) of the closed cross-section portion 30 can attenuate vibrations in the torsion mode and the rhombus mode, and the closed cross-section direction of the closed cross-section portion 30 The second flexible coupling portion 72 that is substantially perpendicular to the (arrow X direction) (arrow Y direction) can attenuate the vibration in the bending mode, thereby enhancing the vibration damping effect.
In short, vibration can be effectively suppressed while securing rigidity, and in particular, not only the vibration of the torsion mode and the rhombus mode is attenuated, but also the vibration of the bending mode is also attenuated, thereby reducing the vibration damping effect. Can be increased.
Further, the second flexible coupling portion 72 is provided so as to intersect the first flexible coupling portion 71 (see FIGS. 1, 2, and 3).

According to this configuration, since the second flexible coupling portion 72 is arranged so as to intersect the first flexible coupling portion 71, the vibration damping effect of the bending mode by the second flexible coupling portion 72 can be increased.
Further, the first flexible coupling portion 71 is disposed so as to include a bending point of the bending mode of the vehicle body member (frame member 40) (see FIGS. 3, 9, and 10).

This configuration has the following effects.
That is, since the damping effect of the flexible joint portion basically becomes higher as the amount of deformation increases, the first flexible joint portion 71 is disposed so as to include the bending point of the vehicle body member (frame member 40). By doing so, the vibration damping effect can be further enhanced.
In addition, the vehicle body member is formed by joining the cross-sectional hat-shaped member 10 and the flat plate (refer to the panel member 20), and joining the flange portions 14 and 15 of the cross-sectional hat-shaped member 10 and the flat plate (panel member 20). The frame member 40 or a frame member formed by joining the flange portions of the two cross-sectional hat-shaped members, wherein the flexible coupling portions 71 and 72 are inner wall portions substantially parallel to the flange portions 14 and 15. 21 and the reinforcing body (refer to the node members 50 and 60) (see FIG. 2).

According to this configuration, since the frame member 40 is more likely to generate a bending mode in a direction perpendicular to the surfaces of the flange portions 14 and 15 than in a direction parallel to the surfaces of the flange portions 14 and 15, the bending mode becomes larger. By providing the inner wall portion 21 with the flexible coupling portions (the first flexible coupling portion 71 and the second flexible coupling portion 72), it is possible to further enhance the vibration damping effect, in particular, the bending mode vibration damping effect.
In addition, the second flexible coupling portion 72 is provided so as to include the central portion in the width direction of the frame member 40 (see FIGS. 3 and 9).

This configuration has the following effects.
That is, in the bending mode, the central portion in the width direction of the frame member 40 is deformed in the inner and outer directions of the closed cross section 30. By providing the second flexible coupling portion 72 at the central portion in the width direction where the degree of deformation is greatest at that time, the vibration damping effect of the bending mode can be further enhanced.
Furthermore, the damping member 70 has a storage elastic modulus of 0.6 to 500 MPa and a loss factor of 0.2 or more under the conditions that the temperature is 20 ° C. and the frequency of the excitation force is 30 Hz. It is comprised by the member (refer FIG. 8).

According to this configuration, the strain energy sharing ratio of the damping member 70 (that is, the ratio of strain energy applied to the target damping member when the strain energy of the entire structure is 100% in a certain mode) is increased. Therefore, the vibration damping effect can be further enhanced.
Incidentally, when the storage elastic modulus is less than 0.6 MPa or exceeds 500 MPa, the strain energy sharing ratio becomes insufficient.

In the correspondence between the configuration of the present invention and the above-described embodiment,
One or more members of the present invention correspond to the cross-sectional hat-shaped member 10 and the panel member 20 of the embodiment,
Similarly,
The vehicle body member corresponds to the frame member 40,
The reinforcing body corresponds to the node members 50, 60,
The rigid joints correspond to spot welds b, c, d, e,
The flat plate corresponds to the panel member 20,
The present invention is not limited to the configuration of the above-described embodiment.

For example, in the said Example, the cross-sectional hat-shaped member 10 and the flat plate (panel member 20) may be formed by joining the flange parts 14 and 15 of the cross-sectional hat-shaped member 10, and a flat plate. .
Further, when it is predicted that a plurality of bending points in the bending mode are generated in the frame member, the first and second flexible coupling portions 71 and 72 are provided corresponding to the bending points in the plurality of bending modes. It is preferable to provide it.
Furthermore, the vehicle body structure of the vehicle of the present invention includes a front side frame, a rear side frame, a floor cross member, a dash cross member, a tunnel member, a side sill, a front pillar, a center pillar, a rear pillar, a quarter pillar, a hinge pillar, a roof side rail, and a floor frame. It can apply to each part of vehicles, such as.

  As described above, the present invention is useful for a vehicle body structure having a reinforcing body coupled to the inside of a vehicle body member having a closed cross section formed by one or more members.

DESCRIPTION OF SYMBOLS 10 ... Cross-section hat-shaped member 14, 15 ... Flange part 20 ... Panel member (flat plate)
21 ... Inner wall 30 ... Closed section 40 ... Frame member (vehicle body member)
50 ... First section member (reinforcing body)
51 ... Plate-like node member
52, 53 ... Joint flange
60 ... Second section member (reinforcing body)
61 ... Flat node body (node member)
63, 64 ... Joint flange part 70 ... Damping member 71 ... First flexible joint part 72 ... Second flexible joint part b, c, d, e ... Spot welded part (rigid joint part)

Claims (6)

A vehicle body structure for a vehicle having a reinforcing body coupled to the inside of a vehicle body member having a closed cross section formed by one or more members,
The joint part between the closed cross-section part and the reinforcing body is a rigid joint part joined in a state of being in contact with each other;
A flexible coupling portion coupled via a damping member disposed between the closed cross-section portion and the reinforcing body,
The flexible coupling portion includes a first flexible coupling portion that is substantially parallel to the closed sectional direction of the closed sectional portion, and
A second flexible coupling portion substantially perpendicular to the closed cross-sectional direction of the closed cross-sectional portion ,
The reinforcing body includes a first node member substantially parallel to the closed section direction of the closed section, and a second node member substantially perpendicular to the closed section direction of the closed section,
The first knot member includes a flat knot member and a plurality of joint flange portions formed by bending the knot member.
The second knot member includes a flat knot member and a plurality of joint flange portions formed by bending the knot member.
The first flexible joint portion is formed by interposing a damping member between one joint flange portion of the first knot member and the inner wall portion of the closed cross-section portion,
The second flexible joint portion is formed by interposing a damping member between one joint flange portion of the second node member and the inner wall portion of the closed cross section,
The rigid coupling part is coupled with the other joint flange part of the first joint member in contact with the inner wall part of the closed cross section, and with the other joint flange part of the second joint member. It is formed by joining the closed wall with the inner wall of the closed section,
The damping member has a temperature of 20 ° C. and a vibration force frequency of 30 Hz.
A vehicle body structure of a vehicle constituted by a viscoelastic member having a storage elastic modulus of 0.6 to 500 MPa and a loss coefficient of 0.2 or more . The vehicle body structure of the vehicle according to claim 1, wherein the second flexible coupling portion is provided so as to intersect the first flexible coupling portion. The vehicle body structure according to claim 1 or 2, wherein the first flexible coupling portion is disposed so as to include a bending point of a bending mode of the vehicle body member. The vehicle body member is formed by joining a cross-sectional hat-shaped member and a flat plate, a frame member formed by joining a flange portion and a flat plate of the cross-sectional hat-shaped member, or joining each flange portion of two cross-sectional hat-shaped members. A formed frame member,
The vehicle body structure according to any one of claims 1 to 3, wherein the flexible coupling portion is formed between an inner wall portion substantially parallel to the flange portion and the reinforcing body. The vehicle body structure according to claim 4, wherein the second flexible coupling portion is provided so as to include a central portion in the width direction of the frame member. The damping member has a storage elastic modulus of 0.7 to 200 MPa under a condition where the temperature is 20C and the frequency of the excitation force is 30 Hz. Item 6. The vehicle body structure according to any one of Items 1 to 5.

Images