Patent Description:
When the vehicle has a small overlap collision (i.e., a collision load partially acts on an area of <NUM>/<NUM> or less, in a vehicle width direction, of a front face of the vehicle in a vehicle frontal collision), the collision load is applied to a front end portion of either one of a pair of side sills which constitute both-side frames of a lower part of a vehicle body rearwardly and inwardly via a front wheel positioned at a forward side of the side sill. Consequently, there is a concern that the front end portion of the side sill may be bent inwardly, so that a space of a cabin may be improperly narrowed. Conventionally, various vehicle-body structures haven been proposed to prevent this bending deformation in the small overlap collision.

In a vehicle-body structure disclosed in <CIT> (<CIT>), a side sill (rocker) having a closed-cross section structure extending in a vehicle longitudinal direction is provided, and plural reinforcing members are provided inside of a front end portion of a side sill outer which constitutes an outward-side portion of a side sill in order to reinforce the side sill. Each of the reinforcing members is joined to a front face portion (a face positioned on a vehicle's forward side), a side face portion (a face directed to a vehicle's inward side), a lower face portion, and others of an inner face of the side sill outer, so that it is attained that the front end portion of the side sill outer is reinforced from the inside, thereby preventing the bending deformation of the side sill in the small overlap collision of the vehicle.

However, while the above-described vehicle-body structure is provided with the reinforcing members at the front end portion of the side sill outer for countermeasures of the small overlap collision, there is a problem that in a case where the collision load increases in the small overlap collision because of a large vehicle size or the like, the weight and costs of the reinforcing members may improperly increase for preventing deformation against the large collision load.

<CIT> discloses a lower vehicle-body structure according to the preamble of claim <NUM>.

The present invention has been devised in view of the above-described matters, and an object of the present invention is to provide a lower vehicle-body structure of a vehicle which can properly suppress the deformation of the side sill, without increasing the weight and manufacturing costs, in the small overlap collision of the vehicle.

The lower vehicle-body structure of the vehicle according to the present invention is defined in claim <NUM>. Preferred embodiments are defined in dependent claims. The lower vehicle-body structure comprises a side sill having a closed-cross section jointly formed by a side sill outer and a side sill inner which extend in a vehicle longitudinal direction, and a cross member joined to the side sill inner of the side sill at a position located on a rearward side, in the vehicle longitudinal direction, relative to a front end portion of the side sill and extending toward an inward side, in a vehicle width direction, from the side sill, wherein the side sill inner comprises an upper face portion and a lower face portion which is downwardly away from the upper face portion, each of which comprises a bending portion, a slant face portion, and a vehicle-width-direction face portion which are respectively located at least in an area, in the vehicle longitudinal direction, between the front end portion of the side sill and the cross member, the bending portion being formed by each of the upper face portion and the lower face portion bent toward an inside of the side sill, the slant face portion being configured to extend from the bending portion toward the side sill outer in an oblique direction such that a width (or a length), in a vertical direction, of the side sill inner gradually increases, the vehicle-width-direction face portion being configured to extend in the vehicle width direction toward the inward side, in the vehicle width direction, from the bending portion.

According to the present invention, while a bending load is applied to the side sill with a support point of a joint portion of the cross member and the side sill inner when the collision load is applied to the front end portion of the side sill rearwardly and inwardly in the small overlap collision, in a process of the respective bending portions of the upper face portion and the lower face portion being deformed toward an inside of the side sill, the respective slant face portions change their inclinations (angles) such that a width, in a vertical direction, of the side sill inner increases, whereas the respective vehicle-width-direction face portions can keep their mostly parallel states to an application direction of the collision load. Thereby, a large reaction force can be generated by the side sill inner itself, so that the bending deformation of the side sill can be suppressed. Accordingly, since it is unnecessary in the above-described structure that the reinforcing members are provided inside the side sill like the conventional structure, the deformation of the side sill can be properly suppressed, without increasing the weight and manufacturing costs, in the small overlap collision of the vehicle.

In the above-described lower vehicle-body structure of the vehicle, an upper face of the cross member may be located at the same level as the vehicle-width-direction face portion of the upper face portion of the side sill inner.

According to this structure, the cross member can properly support the side sill which receives the bending load in the small overlap collision, suppressing torsion of the side sill.

In the above-described lower vehicle-body structure of the vehicle, the cross member may comprise a first flange portion which is joined to the vehicle-width-direction face portion of at least one of the upper face portion and the lower face portion of the side sill inner.

According to this structure, since the vehicle-width-direction face portion of at least one of the upper face portion and the lower face portion of the side sill inner is joined to the first flange portion, in the deformation process of the side sill in the small overlap collision, deformation of the vehicle-width-direction face portion of the side sill inner is so suppressed that the vehicle-width-direction face portion can securely keep its mostly parallel state to the application direction of the collision load.

In the above-described lower vehicle-body structure of the vehicle, the side sill inner may comprise a vertical wall portion which extends in the vertical direction at an end portion of an inward side, in the vehicle width direction, of the side sill inner and interconnects the upper face portion and the lower face portion, and the cross member may comprise a second flange portion which is joined to the vertical wall portion of the side sill inner.

According to this structure, since the vertical wall portion of the side sill inner is joined to the second flange portion of the cross member, the side sill receiving the bending load in the small overlap collision can be securely supported by the cross member.

In the above-described lower vehicle-body structure of the vehicle, the side sill inner may comprise a vertical wall portion which extends in a vertical direction at an end portion of the inward side, in the vehicle width direction, of the side sill inner and interconnects the upper face portion and the lower face portion, and the vertical wall portion may have a bead which extends in the vehicle longitudinal direction.

According to this structure, the rigidity of a whole part of the side sill including the side sill inner against the bending deformation can be improved.

In the above-described lower vehicle-body structure of the vehicle, the bead may extend from the front end portion of the side sill at least up to a rear end portion of the cross member.

According to this structure, since the rigidity of a part of the side sill which is positioned from the front end portion of the side sill to a rear end portion of the cross member is improved by the bead, the bending deformation of the side sill can be effectively prevented when the collision load is applied to the front end portion of the side sill in the small overlap collision.

In the above-described lower vehicle-body structure of the vehicle, the side sill inner may further comprise a pair of upper-and-lower flange portions which are provided at respective end portions, on a side of the side sill outer, of the upper face portion and the lower face portion, and the side sill may further comprise a connecting plate portion which interconnects the pair of upper-and-lower flange portions of the side sill inner.

According to this structure, while a force to make the upper face portion and the lower face portion of the side sill inner move in a direction where these portions go away from each other in a vertical direction is generated when the collision load is applied to the front end portion of the side sill in the small overlap collision, since the respective upper-and-lower flange portions of the upper face portion and the lower face portion are connected by the connecting plate portion, a sectional collapse of the upper face portion and the lower face portion of the side sill inner can be suppressed by a tension of the connecting plate portion.

In the above-described lower vehicle-body structure of the vehicle, the connecting plate portion may be arranged at a part of the side sill, in the vehicle longitudinal direction, which forms a door opening portion of a vehicle body.

While the door opening portion of the vehicle body is an area with no pillar extending in the vertical direction where the support rigidity of the side sill is low, since the connecting plate portion is arranged at the part of the side sill which forms the door opening portion of the vehicle body as described above, the sectional collapse of the upper face portion and the lower face portion of the side sill inner can be securely suppressed even in the area with no pillar.

In the above-described lower vehicle-body structure of the vehicle, the connecting plate portion may be configured to have smaller bending strength than the side sill outer and the side sill inner. In other words, the bending strength of the connecting plate portion may be less than the bending strength of the side sill outer and the bending strength of the side sill inner.

According to this structure, the suppression of the sectional deformation of the side sill inner can be attained along with suppression of the weight and costs of the connecting plate portion.

As described above, the lower vehicle-body structure of the vehicle according to the present invention can properly suppress the deformation of the side sill, without increasing the weight and manufacturing costs, in the small overlap collision of the vehicle.

The present invention will become apparent from the following description which refers to the accompanying drawings.

Hereafter, a lower vehicle-body structure of a vehicle according to an embodiment of the present invention will be described specifically referring to the drawings. All of the features as shown in the drawings may not necessarily be essential.

As shown in <FIG>, a vehicle body <NUM> to which the lower vehicle-body structure of the vehicle according to the embodiment of the present invention is applied comprises, as frame members forming frames of the vehicle body <NUM>, a pair of side sills <NUM> which extend in a vehicle longitudinal direction X at both sides, in a vehicle width direction Y, of the vehicle body <NUM> and a cross member <NUM> which extends in the vehicle width direction Y and interconnects the pair of side sills <NUM>. Further, as other frame members, a hinge pillar <NUM>, a center pillar <NUM>, and a rear pillar <NUM> are provided to stand in order, in the vehicle longitudinal direction X, at intervals at each of both sides, in the vehicle width direction Y, of the vehicle body <NUM>. The side sill <NUM> of the present embodiment extends in the vehicle longitudinal direction X between the hinge pillar <NUM> and the rear pillar <NUM>. Further, a front pillar <NUM> which extends upwardly Z1 and rearwardly X2 toward an upper end of the center pillar <NUM> from an upper end of the hinge pillar <NUM> is provided. A door opening portion <NUM> at a vehicle front side is formed by these side sill <NUM>, hinge pillar <NUM>, center pillar <NUM>, and front pillar <NUM>. A door, not illustrated, is to be attached to the door opening portion <NUM> (specifically, a portion forming the door opening portion <NUM> at the hinge pillar <NUM>) so as to open or close the door opening portion <NUM>. Further, a floor panel <NUM> which forms a vehicle-body floor portion is provided between the pair of side sills <NUM> of the vehicle body <NUM>.

As shown in <FIG> and <FIG>, the side sill <NUM> may be a roughly cylindrical member which extends in the vehicle longitudinal direction X at the both-side portions of the vehicle body <NUM> and has a closed-cross section C, which comprises a pair of flange portions <NUM> and a pair of flange portions <NUM> which protrude upwardly Z1 and downwardly Z2, respectively.

The side sill <NUM> as the frame member of the vehicle body <NUM> comprises a side sill outer <NUM>, a side sill inner <NUM> which is positioned on an inward side Y2, in the vehicle width direction Y, relative to the side sill outer <NUM>, and a connecting plate portion <NUM> which is interposed between the side sill outer <NUM> and the side sill inner <NUM>.

The side sill outer <NUM> may be formed by two sheets of plate members, such as steel plates (a main plate member <NUM> and a patch <NUM>), and the side sill inner <NUM> and the connecting plate portion <NUM> may be respectively formed by a sheet of plate member, such as the steel plate.

The side sill outer <NUM> may comprise a pair of upper-and-lower flange portions <NUM> and constitutes a part of an outward side Y1, in the vehicle width direction, of the side sill <NUM>. The side sill inner <NUM> may comprise a pair of upper-and-lower flange portions <NUM> and constitutes a part of an inward side Y2, in the vehicle width direction, of the side sill <NUM>.

The flange portions <NUM> of the side sill outer <NUM> and the flange portions <NUM> of the side sill inner <NUM> are joined together, thereby forming the side sill <NUM>. That is, the closed-cross section C of the side sill <NUM> is formed together (specifically, joined) by the side sill outer <NUM> and the side sill inner <NUM> which extend in the same direction (the vehicle longitudinal direction X in the present embodiment).

Hereafter, the structure of the side sill outer <NUM> will be described more specifically. As shown in <FIG> and <FIG>, the side sill outer <NUM> of the present embodiment may be formed by the two sheets of plate members, e.g., steel plates, of the main plate member <NUM> and the patch <NUM>, which are joined together and then pressed in a shape having a hat-shaped cross section (i.e., a shape having the pair of flange portions <NUM>).

The side sill outer <NUM> particularly comprises a vertical wall portion <NUM> which extends in a vertical direction Z, an upper-side side face portion 22A and a lower-side side face portion 22B as a pair of side face portions <NUM> which extend toward the side sill inner <NUM>, i.e., toward the inward side Y2, from both end portions of the vertical wall portion <NUM>, expanding in the vertical direction Z, and the pair of flange portions <NUM> which extend toward an upward side Z1 and a downward side Z2, respectively, from respective ends of the inward sides Y2 of the pair of side face portions <NUM>. The lower-side side face portion 22B is downwardly away from the upper-side side face portion 22A.

Each of the pair of side face portions <NUM> (i.e., the upper-side side face portion 22A and the lower-side side face portion 22B) may comprise a first bending portion <NUM> which is formed by the side face portion <NUM> which is bent toward an inside of the side sill <NUM>, a first portion <NUM> which is positioned on a side of the vertical wall portion <NUM> relative to the first bending portion <NUM>, and a second portion <NUM> which is positioned on a side away from the vertical wall portion <NUM> relative to the first bending portion <NUM>.

The first bending portion <NUM> may be formed by the side face portion <NUM> being bent toward the inside of the side sill <NUM> (specifically, a portion of the main plate member <NUM> which corresponds to the side face portion <NUM>).

When a bending load B2 (see <FIG>) operative to bend the side sill <NUM> toward a vehicle inside is applied to the side sill <NUM> in a vehicle side collision (when an obstacle or the like hits against a vehicle side from an outward side) or the like, a compressive stress is generated at the vertical wall portion <NUM>. Further, at the pair of side face portions <NUM>, the compressive stress is generated at the first portion <NUM> and also a tensional stress is generated at the second portion <NUM>.

Accordingly, the side sill outer <NUM> of the present embodiment is configured such that the first portion <NUM> (first portion) has the larger rigidity than the second portion <NUM> (second portion) against the bending load B2 to compress the vertical wall portion <NUM>. In other words, the rigidity of the first portion <NUM> is larger than the rigidity of the second portion <NUM> (second portion) against the bending load B2 to compress the vertical wall portion <NUM>.

In the present embodiment, the first portion <NUM> may be formed by the two sheets of the plate members (the main plate member <NUM> and the patch <NUM>) joined together. The patch <NUM> shown in <FIG> may be joined to an inside of the main plate member <NUM>. The patch <NUM> may comprise a body portion 13a and a pair of both-side portions 13b which are formed by both-side portions of the body portion 13a which are bent. The body portion 13a may be joined to the vertical wall portion <NUM>, and the both-side portions 13b may be joined to the first portion <NUM>. A position of a tip of each of the both-side portions 13b may match a position of the first bending portion <NUM>. Thereby, the vertical wall portion <NUM> of the side sill outer <NUM> and the first portion <NUM> of each of the side face portions <NUM> have high (or higher) rigidity, whereas the second portion <NUM> where the patch <NUM> does not exist has low (or lower) rigidity.

Further, the first portion <NUM> of the side face portion <NUM> of the present embodiment may be formed by the main plate member <NUM> and the patch <NUM> which are joined together, whereas the second portion <NUM> may be formed by the main plate member <NUM> only. Thereby, the rigidity of the side face portion <NUM> is configured to change discontinuously at the first bending portion <NUM> as a border. In other words, while the first portion <NUM> and the second portion <NUM> of the present embodiment have the constant rigidity in their respective areas, the side face portion <NUM> is configured such that the rigidity of the first portion <NUM> and the rigidity of the second portion <NUM> substantially change from each other at the first bending portion <NUM>.

While the patch <NUM> can be joined to either face of the outward side Y1 and the inward side Y2 of the main plate member <NUM>, the outward side Y1 face is preferable because the first portion <NUM> may not be easily crushed (deformed) in the vehicle collision.

Since the rigidity of the side face portion <NUM> of the present embodiment is configured to change discontinuously at the first bending portion <NUM> as the border as described above, the side sill <NUM> easily has the buckling at the first bending portion <NUM> when the bending load B2 (see <FIG>) is applied to the side sill <NUM> in the vehicle side collision. Accordingly, even if an angle θ of the first bending portion <NUM> between an extension line of the first portion <NUM> and the second portion <NUM> is set at <NUM> degrees or less as shown in <FIG>, the buckling of the side sill <NUM> can be attained securely.

Next, the structure of the side sill inner <NUM> will be described specifically. As shown in <FIG> and <FIG>, the side sill inner <NUM> may be formed by a single sheet of plate member, e.g., steel plate, which is pressed in a shape having a hat-shaped cross section (i.e., a shape having the pair of flange portions <NUM>).

The side sill inner <NUM> specifically comprises a vertical wall portion <NUM> which extends in the vertical direction Z at an end portion of the inward side Y2, a pair of side face portions <NUM> (i.e., an upper-side side face portion 32A (upper face portion) and a lower-side side face portion 32B (lower face portion) which extend toward the side sill outer <NUM>, i.e., toward the outward side Y1, from both end portions of the vertical wall portion <NUM>, expanding in the vertical direction Z, and the pair of flange portions <NUM> which extend toward the upward side Z1 and the downward side Z2, respectively, from respective ends of the outward sides Y1 (i.e., on the side of the side sill outer <NUM>) of the upper-side side face portion 32A and the lower-side side face portions 32B. The lower-side side face portion 32B (lower face portion) is arranged downwardly Z2 away from the upper-side side face portion 32A (upper face portion). Herein, when the bending load B2 (see <FIG>) is applied to the side sill <NUM>, a tensional stress is generated at the vertical wall portion <NUM>.

As shown in <FIG> and <FIG>, a bead 31a to reinforce the side sill inner <NUM> may be provided to extend in an extension direction of the side sill inner <NUM> (i.e., in the vehicle longitudinal direction X) at a middle portion, in the vertical direction Z, of the vertical wall portion <NUM>. The bead 31a is formed by recessing a part of the middle portion of the vertical wall portion <NUM> inwardly (toward the outward side Y1). As shown in <FIG>, the bead 31a of the present embodiment may extend from an end portion 2b of a forward side X1 of the side sill <NUM> (a connection portion of the hinge pillar <NUM>) up to a position E of an end portion of a rearward side X2.

The upper-side side face portion 32A (upper face portion) and the lower-side side face portion 32B (lower face portion) comprises respective second bending portions <NUM> (bending portions) which are bent toward the inside of the side sill <NUM> and respective two faces which extend in the vehicle width direction Y (see faces <NUM>, <NUM>, <NUM>, <NUM> shown in <FIG>). That is, each of the upper-side side face portion 32A and the lower-side side face portion 32B has a roughly step-shaped cross section having two steps.

Specifically, the upper-side side face portion 32A of the pair of side face portions <NUM> may comprise a first upper face portion <NUM> which extends in the vehicle width direction Y, an upper-side slant face portion <NUM> (slant face portion) which extends obliquely toward the inward side Y2 and the downward side Z2 from an end portion 35a of the inward side Y2 of the first upper face portion <NUM>, and a second upper face portion <NUM> (vehicle-width-direction face portion) which extends toward the inward side Y2 from an end portion of the inward side Y2 of the upper-side slant portion <NUM>, forming the second bending portion <NUM> (bending portion).

Further, the lower-side side face portion 32B may comprise a first lower face portion <NUM> which extends in the vehicle width direction Y at a position downwardly away from the first upper face portion <NUM>, a lower-side slant face portion <NUM> (slant face portion) which extends obliquely toward the inward side Y2 and the upward side Z1 from an end portion 38a of the inward side Y2 of the first lower face portion <NUM>, and a second lower face portion <NUM> (vehicle-width-direction face portion) which extends toward the inward side Y2 from an end portion of the inward side Y2 of the lower-side slant portion <NUM>, forming the second bending portion <NUM> (bending portion). The lower-side side face portion 32B is linearly symmetrical to the upper-side side face portion 32A. Accordingly, in the vehicle width direction Y, the first lower face portion <NUM> has the same width as the first upper face portion <NUM>, the lower-side slant face portion <NUM> has the same width and slant angle as the upper-side slant face portion <NUM>, and the second lower face portion <NUM> has the same width as the second upper face portion <NUM>.

That is, the side sill inner <NUM> is configured to have the pair of upper-and-lower bending portions <NUM> which are respectively bent toward the inside of the cross section of the side sill <NUM> at a point between the second upper face portion <NUM> and the upper-side slant portion <NUM> and another point between the second lower face portion <NUM> and the lower-side slant portion <NUM> as the bending portions which are formed by bending the upper-side side face portion 32A (upper face portion) and the lower-side side face portion 32B (lower face portion) toward the inside of the side sill <NUM>.

Further, each of the upper-side side slant portion <NUM> and the lower-side slant portion <NUM> is configured to extend from the second bending portion <NUM> toward the side sill outer <NUM> in an oblique direction such that the width, in the vertical direction Z, of the side sill inner <NUM> gradually increases. Moreover, each of the second upper face portion <NUM> and the second lower face portion <NUM> as the vehicle-width-direction face portion extends in the vehicle width direction Y toward the inward side Y2, in the vehicle width direction, from the second bending portion <NUM>.

In the present embodiment, the upper-side side face portion 32A (upper face portion) and the lower-side side face portion 32B (lower face portion) of the side sill inner <NUM> comprise the second bending portions <NUM> (bending portions), the upper-side side slant portion <NUM> and the lower-side slant portion <NUM> (slant face portions), and the second upper face portion <NUM> and the second lower face portion <NUM> (vehicle-width-direction face portions), which are respectively located at least in an area, in the vehicle longitudinal direction X, between the front end portion 2b of the side sill <NUM> and the cross member <NUM>, in order to suppress the bending deformation of the side sill <NUM> in the small overlap collision. However, the above-described portions may be located over a whole length, in the vehicle longitudinal direction X, of the side sill <NUM>.

The vertical wall portion <NUM> extends in the vertical direction Z and interconnects respective end portions of the inward side Y2 of the second upper face portion <NUM> and the second lower face portion <NUM>, thereby attaining connection of the upper-side side face portion 32A (upper face portion) and the lower-side side face portion 32B (lower face portion).

As shown in <FIG> and <FIG>, an end portion of the cross member <NUM> extending in the vehicle width direction Y is joined to the side sill inner <NUM>. In the present embodiment, the cross member <NUM> is joined to the side sill inner <NUM> at a position located on the rearward side X2, in the vehicle longitudinal direction X, relative to the front end portion 2b of the side sill <NUM> and extends toward an inward side Y2, in the vehicle width direction Y, from the side sill <NUM>.

The cross member <NUM> may have one or more, particularly three flange portions, a first flange portion <NUM>, a second flange portion <NUM>, and a third flange portion <NUM> at its end portion. The first flange portion <NUM> extends toward the outward side Y1 from an upper face 3a of the cross member <NUM> and is joined to a second upper face portion <NUM> of the side sill inner <NUM>. The second flange portion <NUM> extends in the vehicle longitudinal direction X from an end edge of the outward side Y1 of a side face 3b (a face directed toward the vehicle longitudinal direction X) of the cross member <NUM> and is joined to the vertical wall portion <NUM> of the side sill inner <NUM>. The third flange portion <NUM> extends toward the upward side Z1 (i.e., toward an inside of the cross member <NUM>) from an end edge of the outward side Y1 of a bottom wall portion of the cross member <NUM> and is joined to the vertical wall portion <NUM>.

It is preferable that the upper face 3a of the cross member <NUM> be located at the same level as the second upper face portion <NUM> (vehicle-width-direction face portion) of the side sill inner <NUM> in order to suppress torsion of the side sill <NUM> in the small overlap collision.

While the above-described first flange portion <NUM> extends toward the outward side Y1, in the vehicle width direction Y, from the upper face 3a of the cross member <NUM> and is joined to the second upper face portion <NUM> of the side sill inner <NUM>, there may be provided an additional first flange portion <NUM> which extends toward the outward side Y1 from a lower face of the cross member <NUM> and is joined to the second lower face <NUM>.

As shown in <FIG>, the side sill <NUM> of the present embodiment may be configured such that a width L2, in a specified direction where the side sill outer <NUM> and the side sill inner <NUM> are arranged in a row (vehicle width direction Y), of the first portion <NUM> positioned on the outward side Y1 is set at <NUM>/<NUM> or less relative to a whole width L1, in the specified direction (vehicle width direction Y), of the side sill <NUM>. Thereby, when the bending load B2 (see <FIG>) is applied in the vehicle side collision or the like, the side sill <NUM> can have the buckling securely at the first bending portions <NUM>.

Further, as shown in <FIG>, since a width L3 , in the specified direction where the side sill outer <NUM> and the side sill inner <NUM> are arranged in a row (vehicle width direction Y), of the second upper face portion <NUM> and the second lower face portion <NUM> is set at <NUM>/<NUM> or less relative to the whole width L1, in the specified direction (vehicle width direction Y), of the side sill <NUM>, the side sill <NUM> can have the buckling securely at the second bending portions <NUM>, while suppressing buckling at the second upper face portion <NUM> and the second lower face <NUM>, when the bending load B2 is applied in the vehicle side collision or the like.

Further, as show in <FIG>, while the respective flange portions <NUM>, <NUM> (particularly, the flange portions <NUM>, <NUM> which protrude upwardly Z1) of the side sill outer <NUM> and the side sill inner <NUM> become a standard position (or a reference position) of the door opening portion <NUM> in <FIG>, a sufficient cabin space can be secured because the above-described flange portions are arranged on the outward side Y1 of a sectional center O of the side sill <NUM>.

As shown in <FIG> and <FIG>, the connecting plate portion <NUM> may interconnect the pair of upper-and-lower flange portions <NUM>, <NUM> of the side sill outer <NUM> and the side sill inner <NUM> in a state where the connecting plate portion <NUM> is interposed between the respective pair of upper-and-lower flange portions <NUM>, <NUM> of the side sill outer <NUM> and the side sill inner <NUM>.

While the connecting plate portion <NUM> can be located at any position in the vehicle longitudinal direction X as long as it is located inside the side sill <NUM>, it is preferable that the connecting plate portion <NUM> be arranged as shown in <FIG> so as to promote the buckling at a portion 2a of the side sill <NUM> which forms the door opening portion <NUM> of the vehicle body <NUM> in the vehicle longitudinal direction X by reinforcing this portion 2a and the like.

The connecting plate portion <NUM> may be configured to have smaller bending strength than the side sill outer <NUM> and the side sill inner <NUM>. In other words, the connecting plate portion <NUM> may be configured to have the bending strength smaller than the bending strength of the side sill outer <NUM> and the bending strength of the side sill inner <NUM>. Specifically, the connecting plate portion <NUM> is made of a plate member having a smaller thickness than the main plate member <NUM> and the patch <NUM> which forms the side sill outer <NUM> and the side sill inner <NUM>.

The first bending portions <NUM> of the pair of side face portions <NUM> are provided to be equidistance from the vertical wall portion <NUM>. That is, the both first bending portions <NUM> of the side sill outer <NUM> are positioned vertically symmetrically.

According to this structure, as shown in <FIG>, <FIG> and <FIG>, a collision load A is applied to the front end portion 2b of the side sill <NUM> rearwardly X2 and inwardly Y2 via a front wheel W of the vehicle in the small overlap collision of the vehicle. Herein, a bending load B1 is applied to the side sill <NUM> with a support point of a joint portion of the cross member <NUM> and the side sill inner <NUM> (around an end portion of the cross member <NUM> where the first - third flange portions <NUM> - <NUM> are provided).

As shown in <FIG>, in a process of the respective second bending portions <NUM> of the upper-side side face portion 32A and the lower-side side face portion 32B which are deformed toward the inside of the side sill <NUM> after the bending load B1 is applied, the upper-side slant face portion <NUM> and the lower-side slant face portion <NUM> which extend toward the side sill outer <NUM> from the second bending portions <NUM> change their inclinations (angles) such that the width, in the vertical direction Z, of the side sill inner <NUM> increases, whereas the second upper face portion <NUM> and the second lower face portion <NUM> which extend toward the inward side Y2, in the vehicle width direction Y, from the second bending portions <NUM> can keep their mostly parallel states to an application direction of the collision load A (specifically, the same direction as a load element, in the vehicle width direction Y, of the collision load A). Thereby, a large reaction force can be generated by the side sill inner <NUM> itself, so that the bending deformation of the side sill <NUM> can be suppressed. Accordingly, since it is unnecessary in the above-described structure that the reinforcing members are provided inside the side sill <NUM> like the conventional structure, the deformation of the side sill <NUM> can be properly suppressed, without increasing the weight and manufacturing costs, in the small overlap collision of the vehicle. Herein, while the connecting plate portion <NUM> is provided inside the side sill <NUM> in <FIG> and <FIG>, this connecting plate portion <NUM> is not indispensable for the present invention, and the structure without the connection plate portion <NUM> can provide the above-described effects as well, of course.

Herein, in order to verify the above-described effects, verification results are shown by a curve I in <FIG>. This verification was conducted by studying the reaction force of the side sill <NUM> against the bending load B1 in a case where the collision load A was applied to the front end portion 2b of the side sill <NUM> rearwardly X2 and inwardly Y2 via the front wheel W of the vehicle in the small overlap collision as shown in <FIG>, <FIG> and <FIG>. A graph of <FIG> shows time changes of respective bending loads F which were generated at the side sill as the reaction force. Specifically, the curve I of <FIG> shows the time change of the bending load at the side sill <NUM> of the present embodiment, and a curve II of <FIG> shows the time change of the bending load at a conventional side sill <NUM> which is shown in <FIG>.

Herein, the conventional side sill <NUM> shown in <FIG> is formed by a side sill outer <NUM> and a side sill inner <NUM> which have the same plate thickness, has a structure in which a pair of flange portions 51a of the side sill outer <NUM> and a pair of flange portions 52a of the side sill inner <NUM> are joined together, and is joined to an end portion of the cross member <NUM>. This side sill <NUM> does not comprise the second bending portion <NUM>, the slant face portion (the upper-side slant face <NUM> and the lower-side slant face portion <NUM>), and the vehicle-width-direction face portion (the second upper face portion <NUM> and the second lower face portion <NUM>) which are provided for increasing the reaction force generated at the side sill inner <NUM> like the present embodiment.

As apparent from the graph of <FIG>, the side sill <NUM> of the present embodiment can maintain the large bending load as the reaction force against the bending load in the small overlap collision for a long period of time as shown by the curve I. Meanwhile, it is apparent as shown by the curve II that in a case of the side sill <NUM> of the comparative example shown in <FIG>, the bending load which is generated as the reaction force in the small overlap collision is smaller than that of the curve I over a roughly whole period of time.

Further, when the side sill <NUM> of the present embodiment and the side sill <NUM> of the comparative example shown in <FIG> are compared regarding a distribution of stress acting on the side sill in the small overlap collision, it is apparent that in the case of the side sill <NUM> of the present embodiment, an area with the large (high) stress (a dark portion in <FIG>) extends over a wide range around the joint portion of the side sill <NUM> to the cross member <NUM>, so that the large reaction force is generated at a whole part of the side sill <NUM>. Meanwhile, it is apparent that in the case of the side sill <NUM> of the comparative example shown in <FIG>, the area with the large (high) stress (a dark portion in <FIG>) occurs intensively in a narrow small range around the joint portion of the side sill <NUM> to the cross member <NUM>, so that the small reaction force is generated at the side sill <NUM> as a whole.

Moreover, in order to further verify the effects of the side sill according to the present invention, a modified example of the present invention was also tested. This modified example is configured such that the bead 31a (see <FIG>) formed at the side sill <NUM> extends not to the rear end position of the cross member <NUM> but just to the front end portion of the cross member <NUM>. For this modified example, the reaction force of the side sill against the bending load B1 in the small overlap collision was studied in the same conditions described above. Results of this are shown by a curve I' of a graph shown in <FIG>. It is apparent from the graph of <FIG> that the bending load, as the reaction force generated in the small overlap collision, of the modified example of the present invention (the bead 31a is short) (curve I') is larger than that of the side sill <NUM> of the above-described comparative example shown in <FIG> (curve II) over a long period of time.

Accordingly, it can be found from the results shown by the graph of <FIG> that the structure, in which the second bending portions <NUM>, the slant face portions (the upper-side slant face portion <NUM> and the lower-side slant face portion <NUM>), and the vehicle-width-direction face portions (the second upper face portion <NUM> and the second lower face portion <NUM>) are provided in order to increase the reaction force like the side sill <NUM> of the present embodiment, can keep the bending load as the reaction force at the large level even in a case where the bead 31a extends just to the front end portion of the cross member <NUM>.

Herein, since the maximum magnitude of the bending load as the reaction force regarding the modified example of the present invention (the bead 31a is short) (the curve I' of <FIG>) is slightly smaller than that regarding the side sill <NUM> of the present embodiment (the curve I of <FIG>) and also the period of time when the bending load is large regarding the modified example of the present invention is slightly shorter than that regarding the side sill <NUM> of the present embodiment, the structure of the side sill <NUM> of the present embodiment in which the bead 31a extends up to the rear end portion of the cross member <NUM> is preferable because the large bending load as the reaction force can be obtained for a long period of time.

Further, since the cross member <NUM> of the present embodiment further comprises the third flange portion <NUM> which is joined to the vertical wall portion <NUM> as shown in <FIG> in addition to the second flange portion <NUM>, the side sill <NUM> can be supported by the cross member <NUM> more securely.

According to this structure, while the force to make the upper-side side face portion 32A and the lower-side side face portion 32B of the side sill inner <NUM> move in the direction where these portions go away from each other in the vertical direction is generated when the collision load A is applied to the front end portion 2b of the side sill <NUM> in the small overlap collision, since the respective upper-and-lower flange portions <NUM> of the upper-side side face portion 32A and the lower-side side face portion 32B are connected by the connecting plate portion <NUM>, a sectional collapse of the upper-side side face portion 32A and the lower-side side face portion 32B of the side sill inner <NUM> can be suppressed by a tension of the connecting plate portion <NUM>.

Subsequently, the deformation process of the side sill <NUM> when the bending load B2 is applied to the side sill <NUM> in the vehicle side collision will be described referring to <FIG>.

In the vehicle side collision, i.e., when an obstacle S hits against the side sill <NUM> from the outward side Y1 toward the inward side Y2 in the vehicle width direction Y, a collision load is applied to the side sill <NUM> from the side as shown in <FIG>. Thereby, the bending load B2 to bend the side sill <NUM> toward vehicle inward side is inputted to the side sill <NUM> which is fixed at both sides, in the vehicle longitudinal direction X, thereof by vehicle-body structural members, such as the hinge pillar <NUM> and the center pillar <NUM> as shown in <FIG>.

As shown in <FIG>, in an initial stage of the vehicle side collision, when the compressive stress acts on the vertical wall portion <NUM> of the side sill outer <NUM> of the side sill <NUM>, the vertical wall portion <NUM> is going to move toward the side sill inner <NUM> (the inward side Y2), and also the compressive stress acts on the first portion <NUM> and the tensile stress acts on the second portion <NUM> at the pair of side face portions <NUM> of the side sill outer <NUM>. Since the first portion <NUM> having the patch <NUM> has the higher rigidity than the second portion <NUM>, moving of the first bending portions <NUM> toward the inside of the side sill <NUM> is promoted (induced) even if the first bending portions <NUM> have the small angle (<NUM> degrees or less).

The second portion <NUM> is tension-deformed toward the inside of the side sill <NUM> in accordance with the above-described moving of the first bending portions <NUM> toward the inside of the side sill <NUM>, so that the buckling is generated at the side sill <NUM>. Herein, in the midway of the process of the moving of the first bending portions <NUM> toward the inside of the side sill <NUM>, the first portions <NUM> having the high rigidity become a state where they are roughly parallel to the direction of the collision load (i.e., the moving direction of the vertical wall portion <NUM> toward the side sill inner <NUM>, specifically, the vehicle width direction Y) in the deformation process. Thereby, a large reaction force against the bending load B2 is generated by the first portion <NUM>. Further, in this compression state, the connecting plate portion <NUM> suppresses the upper-and lower flanges <NUM>, <NUM> of the side sill <NUM> from moving in a direction where these flange portions <NUM>, <NUM> go away from each other in the vertical direction, so that the large reaction force against the bending load B2 is generated.

The above-described reaction force is apparent from a graph of <FIG> in which a bending moment MB rises at the time t1 in a curve III. The graph of <FIG> shows a time change of the bending moment MB which is generated at the side sill as the reaction force. The curve III of <FIG> shows the time change of the bending moment generated at the side sill <NUM> of the present embodiment, whereas a curve IV shows a time change of a bending moment generated at a conventional side sill <NUM> which is shown in <FIG> as a comparative example. Herein, the conventional side sill <NUM> shown in <FIG> does not have any bending portion like the first bending portions <NUM> or the second bending portions <NUM> of the present embodiment which cause the buckling.

The state shown in <FIG> of the present embodiment corresponds to the time t1 in the graph shown in <FIG>, when the curve III shows that the large bending moment as the reaction force of the side sill <NUM> is generated. Meanwhile, the curve IV at the time t1 shows that the small bending moment as the reaction force of the conventional side sill <NUM> is generated.

In a state shown in <FIG> where the time has passed further from the start of the vehicle side collision, deformation of the side sill inner <NUM> also progresses together with the deformation of the side sill outer <NUM>. In the process of the deformation of the side sill inner <NUM>, respective end portions (a pair of flange portions <NUM> and their surrounding portions) of the outward side Y1 of the pair of side face portions <NUM> (the upper-side side face portion 32A and the lower-side side face portion 32B) of the side sill inner <NUM> are extended upwardly Z1 and the downwardly Z2, respectively, so that the side sill inner <NUM> is going to be deformed such that the first and second upper face portions <NUM>, <NUM> and the first and second lower face portions <NUM>, <NUM> protrude toward the outside of the cross section of the side sill <NUM>. At the same time, since the respective second bending portions <NUM> of the pair of side face portions <NUM> of the side sill inner <NUM> are going to be deformed toward the outside of the cross section of the side sill <NUM>, the first and second upper face portions <NUM>, <NUM> and the first and second lower face portions <NUM>, <NUM> can keep their roughly-parallel state to the direction of the side-collision load (i.e., the moving direction of the vertical wall portion <NUM> toward the side sill inner <NUM>, specifically, the vehicle width direction Y). Accordingly, the first and second upper face portions <NUM>, <NUM> and the first and second lower face portions <NUM>, <NUM> of the side sill inner <NUM> can support the side sill outer <NUM> which is under process of the deformation and generate the larger reaction force, so that the bending deformation of the side sill <NUM> can be properly suppressed.

The above-described reaction force of the side sill inner <NUM> is also apparent from the large bending moment at the time t2 in the curve III of the graph of <FIG>. That is, when the side sill <NUM> of the present embodiment has the state shown in <FIG>, which corresponds to the time t2 in the graph of <FIG>, the curve III shows a state where the large bending moment as the reaction force of the side sill <NUM> is maintained. Thus, it is apparent from the curve III that the buckling of the side sill <NUM> toward the inward side Y2 can be suppressed effectively and the reaction force of the side sill <NUM> can be maintained because not only the side sill outer <NUM> has the first bending portions <NUM> but also the side sill inner <NUM> has the second bending portions <NUM>.

Meanwhile, the state of the curve IV at the time t2 shows that the bending moment as the reaction force of the conventional side sill <NUM> does not reach the bending moment of the curve III.

Further, in a state where the time has passed further from the start of the vehicle side collision as shown in <FIG>, the side sill inner <NUM> is more deformed such that the second bending portions <NUM> move outwardly and the side sill inner <NUM> protrudes outwardly, so that the reaction force is generated.

The state of the side sill <NUM> shown in <FIG> of the present embodiment corresponds to the time t3 in the graph shown in <FIG>. It is apparent from <FIG> that the bending moment as the reaction force of the side sill <NUM> at the time t3 in the curve III is going down, but its reaction force is still kept at a sufficiently higher level than the reaction force of the conventional side sill <NUM> shown in the curve IV.

In the above-described explanation, the reaction force as the bending moment of the side sill <NUM> when the bending load B2 is applied to the side sill <NUM> in the vehicle side collision has been referred to regarding the bending deformation of the side sill <NUM>. However, since the side sill <NUM> of the present embodiment comprises the first bending portions <NUM> and the second bending portions <NUM>, the larger reaction force can be generated even in a case where a torsional moment around an axis extending in the vehicle longitudinal direction X is applied.

In a graph of <FIG>, a time change of a torsional moment MT as the reaction force of the side sill <NUM> of the present embodiment is shown by a curve V, whereas a time change of a torsional moment MT of the conventional side sill <NUM> of <FIG> is shown by a curve VI. As apparent from the graph of <FIG>, the side sill <NUM> of the present embodiment (the curve V) and the conventional side sill <NUM> (the curve VI) generate substantially the equal level of torsional moment as the reaction force in an initial stage when the torsional moment starts to be applied, but after this timing the side sill <NUM> of the present embodiment keeps the larger torsional moment than the conventional side sill <NUM> as the reaction force.

(<NUM>)
In the lower vehicle-body structure of the present embodiment, in order to obtain the large reaction force in the vehicle collision even in a case where the width of the cross section of the side sill <NUM> is reduced for securing the sufficient cabin space, not only the first bending portions <NUM> is provided at the side sill outer <NUM> but also the second bending portions <NUM> and the upper-and-lower four faces extending in the vehicle width direction Y (the first upper face portion <NUM>, the second upper face portion <NUM>, the first lower face portion <NUM>, and the second lower face portion <NUM>) (i.e., lateral walls at four points) are provided at the side sill inner <NUM>.

According to this structure, when the collision load is applied to the side sill <NUM> from the vehicle side in the vehicle side collision, the respective first bending portions <NUM> are deformed toward the inside of the side sill <NUM> at the upper-side side face portion 22A and the lower-side side face portion 22B of the side sill outer <NUM>. The first portion <NUM> of each of the upper-side side face portion 22A and the lower-side side face portion 22B which is positioned on the outward side, in the vehicle width direction, relative to the first bending portion <NUM> becomes roughly parallel to a direction of collision load's application in a process of the deformation, so that this portion comes to be crushed in the vehicle width direction Y, generating the large reaction force.

Herein, in the process of the deformation of the side sill inner <NUM>, the respective end portions (the pair of flange portions <NUM> and their surrounding portions) of the outward side Y1, in the vehicle width direction, of the upper-side side face portion 32A and the lower-side side face portion 32B of the side sill inner <NUM> are expanded (extended) upwardly Z1 and downwardly Z2, respectively, so that the side sill inner <NUM> is going to be deformed such that the first upper face portion <NUM>, the second upper face portion <NUM>, the first lower face portion <NUM>, and the second lower face portion <NUM> of the side sill inner <NUM> protrude toward the outside of the cross section of the side sill <NUM>. However, since the respective second bending portions <NUM> of the upper-side side face portion 32A and the lower-side side face portion 32B of the side sill inner <NUM> are going to move toward the outside of the cross section at the same time, the first upper face portion <NUM>, the second upper face portion <NUM>, the first lower face portion <NUM>, and the second lower face portion <NUM> can keep a state where they are roughly parallel to the direction of collision load's application (i.e., the moving direction of the vertical wall portion <NUM> toward the side sill inner <NUM>, specifically, the vehicle width direction Y). Accordingly, the first upper face portion <NUM>, the second upper face portion <NUM>, the first lower face portion <NUM>, and the second lower face portion <NUM> of the side sill inner <NUM> support the side sill outer <NUM> which is under process of the deformation, thereby generating the larger reaction force, so that the bending deformation of the side sill can be suppressed.

Thereby, the side sill <NUM> can generate the large reaction force against the collision load applied from the vehicle side by means of both of the side sill outer <NUM> and the side sill inner <NUM>, thereby properly increasing the bending resistance of the side sill <NUM> without increasing its weight and manufacturing costs.

In other words, the first-and-second upper face portions <NUM>, <NUM> and the first-and-second lower face portion <NUM>, <NUM> of the side sill inner <NUM> of the present embodiment can support the side sill outer <NUM> under process of the deformation and thereby generate the large reaction force. Herein, in a case where only the second bending portions <NUM> are provided at the upper-side side face portion 32A (upper face portion) and the lower-side side face portion 32B of the side sill inner <NUM>, i.e., the upper-side side face portion 32A and the lower-side side face portion 32B are configured to have a bent-shaped cross section merely, an area (portion) of each of the upper-side side face portion 32A and the lower-side side face portion 32B which comes to be parallel to the direction of collision load's application in the process where the second bending portions <NUM> move toward the outside of the side sill <NUM> is so limited (small) that the sufficiently large reaction force cannot be obtained.

(<NUM>)
In the lower vehicle-body structure of the present embodiment, the width L2, in the specified direction where the side sill outer <NUM> and the side sill inner <NUM> are arranged in a row (vehicle width direction Y), of the first portion <NUM> which is positioned on the outward side Y1 relative to the first bending portion <NUM> is set at <NUM>/<NUM> or less relative to the whole width L1, in the above-described specified direction, of the side sill <NUM>.

According to this structure, when the vehicle has the collision, the buckling of the side sill <NUM> at the first portions <NUM> of the upper-side side face portion 22A and the lower-side side face portion 22B of the side sill outer <NUM> is suppressed and also the secure bending of the upper-side side face portion 22A and the lower-side side face portion 22B at the first bending portions <NUM> as the border between the first portion <NUM> and the second portion <NUM> becomes possible, so that the large reaction force can be generated at the upper-side side face portion 22A and the lower-side side face portion 22B.

Herein, the best position, in the whole width of the side sill, of the bending portion to promote the buckling will be studied referring to <FIG> and <FIG>. First, as shown in <FIG>, a portion of the whole width, in the vehicle width direction, of the side sill is considered as a model of a single vertical plate <NUM>. Upper-and-lower end portions of the vertical wall <NUM> are connected to end plates <NUM>, <NUM> and thereby restrained.

It can be considered that the bending portion <NUM> as a shape changing point (i.e., a buckling point of the vertical plate <NUM>) is provided at the vertical plate <NUM> for approaching an all plastic moment as an all potential which the vertical plate <NUM> has originally, i.e., an index of the ideal buckling resistance of the vertical plate <NUM>. Herein, by using the model where the vertical plate <NUM> has buckling at the bending portion <NUM> and is bent when a vertical-directional bending load is applied to the vertical plate <NUM> as shown in <FIG>, a buckling-resistance ratio R, which may become a criteria of the magnitude of a rection force of the vertical plate <NUM> in which the bending portion <NUM> is provided at a position which is distance b' away from the upper end of the vertical plate <NUM> having a whole height b, has been obtained by computer simulation. As a result, as shown by a graph of <FIG> which shows a relationship between a ratio b/b' of the distance b' to the whole height b of the vertical plate <NUM> and the buckling-resistance ratio R (a ratio to the ideal buckling resistance), it has been found that the buckling resistance shows its largest magnitude in a case where the bending portion <NUM> is provided at a position located at <NUM>/<NUM> of the whole height b of the vertical plate <NUM>.

It can be considered from the above-described results that the buckling resistance increases the most when the first bending portion <NUM> of the side sill <NUM> is <NUM>/<NUM> × L1 away from the vertical wall portion <NUM> (L1 = the whole width of the side sill <NUM>). Based on the above-described studies, the following results can be obtained. That is, by setting the width L2 of the first portion <NUM> at <NUM>/<NUM> or less relative to the whole width L1, in the specified direction (vehicle width direction Y), of the side sill <NUM>, the buckling of the side sill <NUM> in the first portion <NUM> can be properly suppressed and also the bending of the side face portions <NUM> at the first bending portions <NUM> as the border between the first portion <NUM> and the second portion <NUM> can be bent, so that the large reaction force can be generated at the upper-side side face portion 22A and the lower-side side face portions 22B.

(<NUM>)
In the lower vehicle-body structure of the present embodiment, the width L3, in the specified direction where the side sill outer <NUM> and the side sill inner <NUM> are arranged in a row (vehicle width direction Y), of each of the second upper face portion <NUM> and the second lower face portion <NUM> is set at <NUM>/<NUM> or less relative to the whole width L1, in the specified direction (vehicle width direction Y), of the side sill <NUM>. Thereby, the side sill <NUM> can have the buckling securely at the second bending portions <NUM>, suppressing buckling at the second upper face portion <NUM> and the second lower face portion <NUM>, when the bending load is applied in the vehicle side collision or the like.

Herein, this setting of the width L3 can be also induced from the same logical explanation regarding the above-described stetting of the width L2 which uses the above-described <FIG> and <FIG>.

Further, when the vehicle has the small overlap collision, the front end portion 2b of the side sill <NUM> is deformed in a cantilever shape, so that the side sill inner <NUM> is compression-deformed. Herein, by setting the width L3 of the second upper face portion <NUM> and the second lower face portion <NUM> as described above, the large reaction force can be obtained at the side sill inner <NUM> as well, so that the large deformation of the cross section of the side sill <NUM> can be prevented.

(<NUM>)
In the lower vehicle-body structure of the present embodiment, each of the pair of side face portions <NUM> (the upper-side side face portion 22A and the lower-side side face portion 22B) of the side sill outer <NUM> comprises the first portion <NUM> which is positioned on the outward side Y1, in the vehicle width direction Y, relative to the first bending portion <NUM> and the second portion <NUM> which is positioned on the inward side Y2, in the vehicle width direction Y, relative to the first bending portion <NUM>. The first portion <NUM> is configured to have the higher rigidity than the second portion <NUM>. Accordingly, even in a case where the angle θ of the first bending portion <NUM> between the extension line of the first portion <NUM> and the second portion <NUM> is set at <NUM> degrees or less, since the second portion <NUM> of each of the upper-side side face portion 22A and the lower-side side face portion 22B of the side sill outer <NUM> is configured to have the lower rigidity than the first portion <NUM>, the second portions <NUM> are tension-deformed toward the inside of the side sill <NUM> and also the first bending portions <NUM> move toward the inside of the side sill <NUM> in the vehicle side collision, so that the buckling of the side sill <NUM> can be securely generated.

That is, according to the side sill <NUM> of the present embodiment, even in a case where the angle θ of the first bending portion <NUM> of the side sill outer <NUM> cannot be secured sufficiently in the structure in which the sufficient width of each of the upper-and-lower side face portions <NUM> (the upper-side side face portion 22A and the lower-side side face portion 22B) of the side sill outer <NUM> is not secured, the first bending portions <NUM> of the side face portions <NUM> can be deformed toward the inside of the cross section of the side sill <NUM> and thereby the side sill <NUM> can have the buckling securely.

(<NUM>)
Further, in the structure of the side sill outer <NUM>, each of the side face portions <NUM> (the upper-side side face portion 22A and the lower-side side face portion 22B) comprises the first portion <NUM> which is positioned on the side of the vertical wall portion <NUM> relative to the first bending portion <NUM> and the second portion <NUM> which is positioned on the side away from the vertical wall portion <NUM> relative to the first bending portion <NUM>, and the first portion <NUM> is configured to have the higher rigidity than the second portion <NUM> against the bending load B2 operative to compress the vertical wall portion <NUM>. In other words, the rigidity of the side face portion <NUM> is configured to change discontinuously at the first bending portion <NUM> as the border from the rigidity of the first portion <NUM> to the rigidity of the second portion <NUM>. Accordingly, when the vehicle has the side collision, as shown in <FIG>, the second portion <NUM> is tension-deformed toward the inside of the side sill <NUM> in accordance with the first bending portions <NUM> moving toward the inside of the side sill <NUM> and also the first bending portions <NUM> move toward the inside of the side sill <NUM>, so that the buckling of the side sill <NUM> can be generated. Herein, in the midway of the process of the moving of the first bending portions <NUM> toward the inside of the side sill <NUM>, the first portion <NUM> becomes the state where it is roughly parallel to the moving direction toward the side sill inner <NUM> in the deformation process of the first portion <NUM> having the high rigidity of each of the pair side face portions <NUM>. Accordingly, since the large reaction force is generated against the bending load B by the first portion <NUM>, the bending deformation of the side sill <NUM> can be suppressed. Consequently, the side sill <NUM> can attain the proper impact absorption by securely generating the buckling, suppressing its bending deformation, when the bending load B2 is applied to the side frame <NUM> in the vehicle side collision.

(<NUM>)
In the lower vehicle-body structure of the present embodiment, as shown in <FIG>, the respective flange portions <NUM>, <NUM> of the side sill outer <NUM> and the side sill inner <NUM> which form the side sill <NUM> are arranged on the outward side Y1, in the vehicle width direction Y, relative to the sectional center O of the side sill <NUM>. According to this structure, the position of the door opening portion <NUM> of the vehicle body <NUM> which is partitioned by these flange portions <NUM>, <NUM> can be easily located outwardly Y1 in the vehicle width direction Y, so that the cabin space can be secured properly. Accordingly, this structure can secure the sufficient cabin space properly, attaining suppressing of the bending deformation of the side sill <NUM> and maintaining of the impact absorption performance.

(<NUM>)
In the lower vehicle-body structure of the present embodiment, the side sill <NUM> comprises the connecting plate portion <NUM>. The connecting plate portion <NUM> interconnects the pair of upper-and-lower flange portions <NUM>, <NUM> of the side sill outer <NUM> and the side sill inner <NUM> in the state where the connecting plate portion <NUM> is interposed between the respective pair of upper-and-lower flange portions <NUM>, <NUM> of the side sill outer <NUM> and the side sill inner <NUM>. According to this structure, even if the pair of upper-and-lower flange portions <NUM>, <NUM> are going to move in the direction where these flange portions <NUM>, <NUM> go away from each other in the vertical direction Z in the process of the bending deformation of the side sill <NUM> in the vehicle side collision, that vertical moving of the flange portions <NUM>, <NUM> in the vertical direction Z is suppressed (i.e., the pair of flange portions <NUM> (and the pair of flange portions <NUM>) are suppressed from going away from each other in the vertical direction Z) by the connecting plate portion <NUM>. Therefore, the secure buckling of the side sill <NUM> at the first and second bending portions <NUM>, <NUM> can be attained.

(<NUM>)
In the lower vehicle-body structure of the present embodiment, the connecting plate portion <NUM> is arranged at the part 2a (see <FIG>) of the side sill <NUM>, in the vehicle longitudinal direction X, which forms the door opening portion <NUM> of the vehicle body <NUM>. While the door opening portion <NUM> of the vehicle body <NUM> is an area with no pillar extending in the vertical direction Z where the support rigidity of the side sill <NUM> is low, since the connecting plate portion <NUM> is arranged at the part 2a of the side sill <NUM> which forms the door opening portion <NUM> of the vehicle body <NUM> as described above, the buckling of the side sill <NUM> at the first and second bending portions <NUM>, <NUM> can be attained securely even in the area with no pillar.

(<NUM>)
In the lower vehicle-body structure of the present embodiment, the first portion <NUM> of the side sill outer <NUM> is formed by two sheets of plate members, i.e., the main plate member <NUM> and the patch <NUM> which are joined together. According to this structure, since the first portion <NUM> of the side face portion <NUM> of the side sill outer <NUM> is formed by the two sheets of plate members, the side sill <NUM> capable of having the buckling can be easily manufactured by the two sheets of plate members joined together at the side sill outer <NUM>.

Claim 1:
A lower vehicle-body structure of a vehicle, comprising:
a side sill (<NUM>) having a closed-cross section (C) jointly formed by a side sill outer (<NUM>) and a side sill inner (<NUM>) which extend in a vehicle longitudinal direction (X); and
a cross member (<NUM>) joined to the side sill inner (<NUM>) of the side sill (<NUM>) at a position located on a rearward side, in the vehicle longitudinal direction (X), relative to a front end portion (2b) of the side sill (<NUM>) and extending toward an inward side, in a vehicle width direction (Y), from the side sill (<NUM>),
and characterised in that
the side sill inner (<NUM>) comprises an upper face portion (32A) and a lower face portion (32B) which is downwardly away from the upper face portion (32A), each of which comprises a bending portion (<NUM>), a slant face portion (<NUM>), and a vehicle-width-direction face portion (<NUM>) which are respectively located at least in an area, in the vehicle longitudinal direction (X), between the front end portion (2b) of the side sill (<NUM>) and the cross member (<NUM>), the bending portion (<NUM>) being formed by each of the upper face portion (32A) and the lower face portion (32B) bent toward an inside of the side sill (<NUM>), the slant face portion (<NUM>) being configured to extend from the bending portion (<NUM>) toward the side sill outer (<NUM>) in an oblique direction such that a width, in a vertical direction (Z), of the side sill inner (<NUM>) gradually increases, the vehicle-width-direction face portion (<NUM>) being configured to extend in the vehicle width direction (Y) toward the inward side, in the vehicle width direction (Y), from the bending portion (<NUM>).