JPH11208228A - Vehicle suspension member mounting structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrain retreat of a steering wheel as well as to inhibit a suspension member from intruding into a vehicle compartment by descending the suspension member from the pre-collision position when collision occurs. SOLUTION: A suspension member 10 is mounted on a side of a vehicle body 30 through fixtures 20. A first member 21 mounted on the suspension member 10, and a second member 22 mounted on the side of the vehicle body 30 and fitted to the first member 21 are provided with at least one of the fixtures 20. The first member 21 and the second member 22 are fitted in a way that allows relative displacement along the fitting axial line K with a load applied to the suspension member 10 at a predetermined level or more. In a side view of the vehicle, the fitting axial line K is inclined downward toward the center of the vehicle in the longitudinal direction X of the vehicle.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a suspension member mounting structure for mounting a suspension member on a vehicle body of a vehicle such as an automobile.

[0002]

2. Description of the Related Art FIG. 14 and FIG.
No. 8, which discloses an example of a conventional structure, FIG. 14 is an exploded perspective view, and FIG.
FIG. 15 is a sectional view taken along line VV in a state where the one shown in FIG. 14 is assembled.

[0003] This suspension member mounting structure,
A connecting member c for connecting the suspension member a to the vehicle body b, the connecting member c having a projection d extending in the vehicle front-rear direction X and being attached to the suspension member a; And a second member g which is attached to the vehicle body b and has a hole f into which the first member e is attached. The first member e is inseparable when a load larger than the normal load is applied to the suspension member a in the vehicle longitudinal direction X. And a fixture h for fixing the second member g.

For this reason, in this conventional structure, when the vehicle collides and a load larger than the normal load is applied to the suspension member a in the vehicle front-rear direction X, the first member e and the second member g are fixed by the fixture h. The fixation is released, the suspension member a is separated from the vehicle body b, and a part of the vehicle body b is deformed to absorb the collision energy and prevent the suspension member a from entering the passenger compartment.

FIGS. 16 and 17 show Japanese Patent Application Laid-Open No. 6-64421.
FIG. 16 is a perspective view showing another example of the conventional structure, and FIG. 17 is a cross-sectional view showing a fitting used in the conventional structure. FIG.
As shown in FIG. 1, this conventional structure attaches a rear suspension member A to a vehicle body.

In this conventional structure, as shown in FIG. 17, the elastic member B1 interposed between the suspension member A and the vehicle body has a diagonal directivity so that the suspension member A is mounted on the vehicle body. In the tool B, the inner peripheral surface B3 of the outer member B2 surrounding the elastic body B1 is inclined.

In this conventional structure, when the vehicle receives a load in the vehicle front-rear direction larger than the normal load from the rear side, such as at the time of a collision, the rear suspension member A becomes an elastic body B
It can descend toward the front of the vehicle against the spring constant of 1,
Accordingly, it is possible to suppress the rear suspension member A from entering the vehicle interior at the time of collision.

[0008]

In the conventional structure shown in FIG. 14, the first member e and the second member
Since the fitting axis of fitting with the member g extends in the vehicle front-rear direction X, the first member e and the second member g by the fixture h are used.
And the suspension member a is separated from the vehicle body b at the time of a vehicle collision, the suspension member a
Had a small effect of descending from the position before separation.

Further, since the steering rack is usually fixed to the suspension member a, if the suspension member a descends less during a vehicle collision, the steering rack descends less, and the steering wheel in the vehicle cabin connected to the steering rack. Since the effect of suppressing the backward movement of the steering wheel is reduced, a measure for suppressing the backward movement of the steering wheel at the time of the vehicle collision may be required.

In the conventional structure shown in FIG. 16, although the rear suspension member A can be suppressed to some extent from entering the vehicle interior at the time of a vehicle collision, the suspension member is provided by a stopper C provided below the mounting member B. Since the amount of downward displacement of A is limited, there have been cases where measures have to be taken to prevent the suspension member A from entering the passenger compartment during a vehicle collision.

Therefore, in the present invention, by lowering the suspension member from the position before the collision at the time of the vehicle collision, it is possible to suppress the retreat of the steering wheel at the time of the vehicle collision, and to invade the suspension member into the vehicle interior at the time of the vehicle collision. It is an object of the present invention to provide a vehicle suspension member mounting structure capable of suppressing the occurrence of a vehicle.

[0012]

According to a first aspect of the present invention, there is provided a vehicle having a suspension member for supporting a wheel supporting member for rotatably supporting a wheel so as to swing vertically. A vehicle suspension member mounting structure for mounting both sides in a width direction and both sides in a vehicle front-rear direction to a vehicle body via respective mounting members, wherein at least one of the mounting members is mounted on one of the suspension member or the vehicle body side. And a second member attached to the other member and fitted to the first member, wherein the fitting of the first member and the second member is performed by applying a load greater than or equal to a predetermined value applied to the suspension member. And allows relative displacement along the fitting axis, and the fitting axis is inclined downward toward the vehicle center in the front-rear direction of the vehicle when viewed from the side of the vehicle, It has adopted the cormorant configuration.

Therefore, according to the first aspect of the present invention, when a vehicle collides and a load equal to or more than a predetermined value is applied to the suspension member, the first member and the second member move relative to each other along the fitting axis. As a result, the suspension member can be lowered from the position before the collision toward the center of the vehicle in the front-rear direction of the vehicle.

According to a second aspect of the present invention, there is provided the vehicle suspension member mounting structure according to the first aspect, wherein the first member and the second member are fitted via an elastic body. Is what you do.

Therefore, according to the second aspect of the present invention, the suspension member can be attached to the vehicle body via the elastic body.

According to a third aspect of the present invention, there is provided the suspension member mounting structure for a vehicle according to the second aspect, wherein the first member is fitted and fixed to a mounting shaft provided on one of the suspension member and the vehicle body. An inner cylinder, an outer cylinder penetrating the inner cylinder, and an elastic body made of rubber interposed between the inner cylinder and the outer cylinder, wherein the second member is capable of sliding the outer cylinder. And a cylindrical member that fits and is fixed to the housing.

Therefore, according to the third aspect of the present invention, when a vehicle collides and a predetermined load or more is applied to the suspension member, the first member and the second member are moved between the outer cylinder of the first member and the cylindrical member of the second member. Sliding displacement occurs along the mating axis, resulting in
The suspension member can be lowered from the position before the collision toward the center in the front-rear direction of the vehicle.

According to a fourth aspect of the present invention, in the vehicle suspension member mounting structure according to the third aspect, the outer cylinder is formed longer than the cylindrical member, and the inner cylinder is formed longer than the outer cylinder. A stopper is provided on the distal end side of the mounting shaft portion, the stopper being opposed to one end side of the outer cylinder at an interval, and a contact surface facing the other end side of the outer cylinder at the base side of the mounting shaft portion at an interval. Is provided.

For this reason, in the invention of claim 4, usually,
The elastic body can be elastically displaced between the stopper and the contact surface provided on the base side of the mounting shaft, and the connection between the inner cylinder and the outer cylinder of the first member due to deterioration of the elastic body made of rubber or the like. When the first member is broken, the stopper can prevent the inner cylinder of the first member from coming off the outer cylinder.

According to the fourth aspect of the present invention, the outer cylinder of the first member is formed longer than the cylindrical member of the second member.
In the case where a load equal to or more than a predetermined value is applied to the suspension member due to the collision of the vehicle, similarly to the invention of claim 3, between the outer cylinder of the first member and the cylindrical member of the second member along the fitting axis. As a result, the suspension member can be lowered from the position before the collision toward the center in the front-rear direction of the vehicle.

According to a fifth aspect of the present invention, in the vehicle suspension member mounting structure according to the third or fourth aspect, a positioning flange is provided on the outer cylinder so as to abut on an end face of the cylindrical member. It is assumed that.

According to the fifth aspect of the present invention, when the outer cylinder of the first member is slidably fitted and fixed in the cylindrical member of the second member, the end face of the cylindrical member is attached to the positioning flange of the outer cylinder. By making contact, the outer cylinder can be fitted and fixed at a predetermined position in the cylindrical member.

According to a sixth aspect of the present invention, there is provided the suspension member mounting structure for a vehicle according to the first aspect, wherein the first member and the second member are rigid bodies.

Therefore, according to the invention of claim 5, claim 2
The structure of the first member and the second member is simpler than that of the invention, and the manufacture of the first member and the second member is easy.

According to a seventh aspect of the present invention, in the vehicle suspension member mounting structure according to the sixth aspect, the first member is fitted and fixed to a mounting shaft portion provided on one of the suspension member and the vehicle body. Wherein the second member includes a cylindrical member that slidably fits and fixes the inner cylinder member.

According to the present invention, when the vehicle collides and a load equal to or greater than a predetermined value is applied to the suspension member, the first member and the second member can be moved between the inner member and the second member. As a result, sliding displacement occurs along the fitting axis, and as a result, the suspension member can be lowered from the position before the collision toward the center in the front-rear direction of the vehicle.

According to an eighth aspect of the present invention, there is provided the vehicle suspension member mounting structure according to the seventh aspect, wherein the inner cylindrical member is formed longer than the cylindrical member.

Therefore, according to the invention of claim 8, in claim 7
Similarly to the invention of the first aspect, when a load equal to or more than a predetermined value is applied to the suspension member due to the collision of the vehicle, the slide along the fitting axis between the inner cylindrical member of the first member and the cylindrical member of the second member. Displacement occurs, and as a result, the suspension member can be lowered from the position before the collision toward the center in the front-rear direction of the vehicle.

According to a ninth aspect of the present invention, there is provided the suspension member mounting structure for a vehicle according to the seventh or eighth aspect, wherein a positioning flange is provided on the inner cylindrical member so as to be in contact with an end surface of the cylindrical member. It is a feature.

According to the ninth aspect of the present invention, when the inner cylindrical member of the first member is slidably fitted and fixed in the cylindrical member of the second member, the cylindrical member is fixed to the positioning flange of the inner cylindrical member. By abutting the end faces, fitting and fixing of the inner cylinder member within the cylindrical member can be performed at a predetermined position.

According to a tenth aspect of the present invention, in the vehicle suspension mounting structure according to any one of the second to fifth aspects, the elastic body has anisotropy in a direction of elastic displacement, and The mounting member including the member and the second member is disposed on at least one of both sides of the suspension member in the vehicle front-rear direction, and an arrangement position of the elastic body is different from that of the one side elastic body. The virtual elastic center determined in consideration of the characteristics is set at a position away from the mounting fixture on the other side in the front-rear direction of the vehicle.

In the tenth aspect of the present invention, since the elastic body has anisotropy in the direction of elastic displacement, the elastic body has a low rigidity direction in which rigidity is low and is easily displaced, and a rigid high direction in which rigidity is easily displaced. There are high rigidity directions that are difficult to perform, and both the low rigidity and high rigidity directions are substantially orthogonal or completely orthogonal.

Here, if a straight line extending in the direction of high rigidity is defined as an elastic axis of the elastic body, at least one of both sides in the vehicle longitudinal direction of the suspension member determined in consideration of the anisotropy of the elastic body. The virtual elastic center is the intersection of the elastic axes of the elastic bodies provided on at least one side.

According to the tenth aspect, the first member and the second member
The mounting position of the elastic body includes a virtual elastic center at which the elastic body is disposed in consideration of the anisotropy of the elastic body on the one side in the vehicle longitudinal direction from the mounting side on the other side. Since the distance is set at a distance, the distance between the elastic centers on both sides in the vehicle longitudinal direction of the suspension member can be expanded in the vehicle longitudinal direction by the virtual elastic center, and the yaw rigidity of the suspension member can be equivalently increased. .

According to an eleventh aspect of the present invention, in the vehicle suspension mounting structure according to any one of the second to fifth aspects, the elastic body has anisotropy in a direction of elastic displacement, and The attachment including the member and the second member is disposed on both sides in the vehicle longitudinal direction of the suspension member, and a position at which the elastic body is disposed is determined by a lateral force applied to a suspension roll center determined by a suspension geometry. The virtual elastic center on the front side determined in consideration of the anisotropy of the elastic body on the front side in the vehicle front-rear direction and the rear side determined in consideration of the anisotropy of the elastic body on the rear side in the vehicle front-rear direction. When the suspension member rotates around the virtual roll axis of the suspension member passing through the virtual elastic center on the side,
The present invention is characterized in that the steering characteristic is set at a position where the steering characteristic is in an understeer direction.

In the eleventh aspect of the present invention, since the elastic body has anisotropy in the direction of elastic displacement, the suspension member is determined in consideration of the anisotropy of the elastic body as described above. The virtual elastic center on the front side in the vehicle front-rear direction is the intersection of the elastic axes of the elastic bodies disposed on the front side,
The virtual elastic center on the rear side in the vehicle longitudinal direction of the suspension member determined in consideration of the anisotropy of the elastic body is the intersection of the elastic axes of the elastic bodies disposed on the rear side.

According to the eleventh aspect of the present invention, when a lateral force is applied to the suspension roll center determined from the suspension geometry, the suspension member rotates around the virtual roll axis passing through the virtual elastic centers on both sides in the vehicle longitudinal direction. A moment is generated to rotate.

According to the eleventh aspect of the present invention, the mounting member provided with the first member and the second member is arranged such that the position at which the elastic member is disposed is limited by the lateral force applied to the suspension roll center determined by the suspension geometry. When the suspension member is rotated around the virtual roll axis, the steering characteristic is set at a position where the steering characteristic is in the understeer direction, and thus occurs when the suspension member is rotated by a lateral force applied to the wheel when the vehicle turns. The change in the compliance toe angle of the wheel changes the steering characteristic of the vehicle in the understeer direction when the vehicle turns.

The twelfth aspect of the present invention provides the tenth or eleventh aspect.
The vehicle suspension member mounting structure according to the above, wherein the elastic body is rubber, and the anisotropy of the elastic body is:
It is characterized in that it is formed by providing a cavity along the fitting axis in an elastic body.

According to the twelfth aspect of the present invention, since the cavity along the fitting axis is provided in the elastic body made of rubber, the direction of the elastic body from the fitting axis to the cavity has low rigidity and is displaced. A direction that is easy to have a low rigidity direction, and a direction that is substantially orthogonal or completely orthogonal to the low rigidity direction is a high rigidity direction that has relatively high rigidity and is difficult to be displaced, and has anisotropy in the direction of elastic displacement. .

A thirteenth aspect of the present invention is the vehicle suspension member mounting structure according to any one of the second to fifth aspects, wherein the suspension member is a front suspension member, and the first member and the second member are connected to each other. The mounting fixture is provided only on the rear side of the front suspension member in the vehicle longitudinal direction, and the elastic body has elastic characteristics that have the largest elastic displacement amount in the fitting direction along the fitting axis. It is characterized by doing.

When the front wheels cross over the small protrusions while the vehicle is running, a normal load is applied to the front suspension member toward the rear in the vehicle longitudinal direction.

According to the thirteenth aspect of the present invention, when the front wheel goes over the small protrusion while the vehicle is running, the mounting member disposed on the rear side of the front suspension member in the front-rear direction of the vehicle includes the first member and the first member. Relative displacement occurs due to elastic displacement of the elastic body in the fitting direction between the two members, and the front suspension member slightly lowers the rear side in the vehicle front-rear direction along the fitting axis, and moves the wheel support member up and down. The oscillating shaft for oscillating support is lowered on the rear side in the vehicle front-rear direction, so that the wheel center trajectory of the front wheels is inclined backward.

According to a fourteenth aspect of the present invention, there is provided the vehicle suspension member mounting structure according to any one of the second to fifth aspects, wherein the suspension member is a rear suspension member, and the first member and the second member are connected to each other. The mounting member is provided only on the front side of the rear suspension member in the vehicle front-rear direction, and the elastic body has an elastic characteristic having a largest elastic displacement amount in a fitting direction along the fitting axis. It is characterized by doing.

When the rear wheel passes over the small protrusion while the vehicle is running, a normal load is applied to the rear suspension member toward the rear in the vehicle longitudinal direction.

Therefore, according to the fourteenth aspect of the present invention, when the rear wheel passes over the small protrusion while the vehicle is running, the mounting member disposed on the front side of the rear suspension member in the front-rear direction of the vehicle includes the first member and the first member. A relative displacement occurs between the second member and the second member due to the elastic displacement of the elastic body in the fitting direction, and the front side of the rear suspension member in the vehicle front-rear direction slightly rises along the fitting axis to move the wheel support member in the vertical direction. Raise the front side of the rocking shaft for rocking support
The wheel center locus of the rear wheel is inclined backward.

[0047]

According to the first aspect of the present invention, when a vehicle collides and a predetermined load or more is applied to the suspension member, the suspension member is lowered from the position before the collision toward the center of the vehicle in the longitudinal direction of the vehicle. Therefore, it is possible to suppress the suspension member from entering the passenger compartment at the time of a vehicle collision.

According to the first aspect of the present invention, when a vehicle collides and a load greater than a predetermined value is applied to the suspension member,
Since the suspension member can be lowered from the position before the collision toward the center of the vehicle, when the steering rack is fixed to the suspension member, the steering rack is lowered together with the suspension member during the vehicle collision, and Wheel retraction can also be suppressed.

According to the second aspect of the present invention, since the suspension member can be attached to the vehicle body via the elastic body, the vibration of the suspension member is absorbed by the elastic body.
The ride comfort of the vehicle can be improved.

According to the third aspect of the present invention, when a load equal to or more than a predetermined value is applied to the suspension member due to the collision of the vehicle, the outer member of the first member and the cylindrical member of the second member move along the fitting axis. Since the slide displacement occurs, the suspension member can be lowered from the position before the collision toward the center in the front-rear direction of the vehicle, so that the suspension member can be prevented from entering the vehicle interior at the time of the vehicle collision. Thus, the steering rack can be lowered together with the suspension member to suppress the retreat of the steering wheel.

According to the fourth aspect of the present invention, the elastic member, which is a rubber, can be elastically displaced between the stopper and the contact surface provided on the base side of the mounting shaft. It can be absorbed by the elastic body to improve the riding comfort of the vehicle.

According to the fourth aspect of the present invention, even if the connection between the inner cylinder and the outer cylinder of the first member is broken due to deterioration of the elastic body made of rubber, the inner cylinder of the first member comes off the outer cylinder. Can be prevented by the stopper, so that the suspension member can be prevented from falling off from the vehicle body.

Further, according to the invention of claim 4, when the vehicle collides and a predetermined load or more is applied to the suspension member, the outer cylinder of the first member and the cylindrical member of the second member are fitted. Sliding displacement occurs along the axis, and the suspension member can be lowered from the position before the collision toward the center in the front-rear direction of the vehicle. Therefore, in the event of a vehicle collision, the suspension member can be prevented from entering the passenger compartment. It is also possible to lower the steering rack together with the suspension member to suppress the retreat of the steering wheel.

According to the fifth aspect of the invention, when the outer cylinder of the first member is slidably fitted and fixed in the cylindrical member of the second member, the end face of the cylindrical member is brought into contact with the positioning flange of the outer cylinder. By doing so, the fitting and fixing of the outer cylinder in the tubular member can be performed at a predetermined position. The performance is improved.

According to the sixth aspect of the present invention, the structure of the first member and the second member is simpler than that of the second aspect of the invention, and the manufacture of the first member and the second member is easy. And the manufacturing cost of the fixture provided with the 2nd member can be reduced.

According to the seventh aspect of the present invention, when the vehicle collides and a load equal to or more than a predetermined value is applied to the suspension member, the inner member of the first member and the cylindrical member of the second member move along the fitting axis. As a result, the suspension member can be lowered from the position before the collision toward the center in the front-rear direction of the vehicle. And the steering rack can be lowered together with the suspension member to suppress the retreat of the steering wheel.

According to the eighth aspect of the present invention, when a load exceeding a predetermined level is applied to the suspension member due to the collision of the vehicle,
Sliding displacement occurs along the fitting axis between the inner cylindrical member of the first member and the cylindrical member of the second member, and lowers the suspension member from the position before the collision toward the center in the front-rear direction of the vehicle. Therefore, in the event of a vehicle collision, the suspension member can be prevented from entering the vehicle interior, and the steering rack can be lowered together with the suspension member to prevent the steering wheel from moving backward.

According to the ninth aspect of the invention, when the inner cylindrical member of the first member is slidably fitted and fixed in the cylindrical member of the second member, the end face of the cylindrical member is brought into contact with the positioning flange of the inner cylindrical member. By making contact, the fitting and fixing of the inner cylinder member within the tubular member can be performed at a predetermined position, so that the fitting and fixing of the inner cylinder member within the cylindrical member at the predetermined position can be performed. The workability of the fixing work is improved.

According to the tenth aspect, the distance between the elastic centers of the suspension member on both sides in the vehicle longitudinal direction can be increased in the vehicle longitudinal direction by the virtual elastic center.
Equivalently, the yaw stiffness of the suspension member can be increased, so that the suspension member is less likely to be affected by the input of a lateral disturbance such as when passing through a rut or the like during straight running. Therefore, the straight running stability of the vehicle can be improved.

According to the eleventh aspect of the present invention, the change in the compliance toe angle of the wheel caused by the rotation of the suspension member due to the lateral force applied to the wheel during the turning of the vehicle causes the steering characteristic of the vehicle during the turning of the vehicle to the understeer direction. Since it is changed, the steering stability during turning of the vehicle is improved.

According to the twelfth aspect of the present invention, in the elastic body made of rubber, the direction from the fitting axis to the cavity is a low rigidity direction in which rigidity is low and easy to be displaced, and is substantially orthogonal or completely orthogonal to the low rigidity direction. Direction becomes a high rigidity direction in which the rigidity is relatively high and the displacement is difficult, and the elastic body has anisotropy in the direction of the elastic displacement. By adjusting the arrangement position,
The elastic axis along the high rigidity direction of the elastic body can be set in a predetermined direction.

According to the thirteenth aspect of the present invention, when the front wheel goes over the small protrusion while the vehicle is running, the front suspension member slightly lowers the rear side in the vehicle front-rear direction along the fitting axis, and moves the wheel supporting member up and down. Lowers the back and forth direction of the rocking shaft for supporting the rocking direction in the vehicle front and rear direction to tilt the trajectory of the wheel center of the front wheels backward, so that the vehicle when the front wheels cross over the small protrusions while the vehicle is running The ride comfort is improved.

According to the fourteenth aspect of the present invention, when the rear wheel rides over the small protrusion while the vehicle is running, the front side of the rear suspension member rises slightly along the fitting axis in the front-rear direction of the vehicle, and the rear suspension member moves the wheel support member. By raising the front side of the rocking shaft for supporting the rocking in the vertical direction in the front-rear direction of the vehicle to tilt the wheel center trajectory of the rear wheel rearward, the rear wheel passes over the small protrusion while the vehicle is running. The riding comfort of the vehicle is improved.

[0064]

DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) FIG. 1 is a perspective view showing a first embodiment which is an example of an embodiment in which the inventions of claims 1 to 5 and 10 to 12 are combined. It is. 2A and 2B are explanatory diagrams illustrating the operation of the first embodiment, in which FIG. 2A illustrates a normal state, and FIG. 2B illustrates a state at the time of a vehicle collision. FIGS. 3A and 3B are cross-sectional views illustrating the attachment of the first embodiment, in which FIG. 3A illustrates a normal state, and FIG. 3B illustrates a state at the time of a vehicle collision.

As shown in FIG. 1, one end of the front suspension member 10 in the vehicle width direction Y is connected to the side member 31
, And the rear side of the vehicle body 3
0 is attached to the side member extension 32.

Although not shown, the other end of the front suspension member 10 in the vehicle width direction Y is also connected to the vehicle
Attached to the side. Therefore, the four corners of the front suspension member 10 are attached to the vehicle body 30 by the attachments 20.

A wheel support member 40, which is a suspension arm for rotatably supporting wheels, is attached to the front suspension member 10 via a bracket 41, and swings in a vertical direction Z about a swing shaft 42 as a swing center. A steering rack 2 which is movably supported and is continuous from a steering wheel in the vehicle compartment is fixed on the front suspension member 10.

As shown in FIG. 3A, all of the four attachments 20 for attaching the front suspension member 10 to the vehicle body 30 are the first members 21 attached to the front suspension member 10. And a second member 22 attached to the vehicle body 30.
The front suspension member 10 has the first
A mounting shaft 11 for mounting the member 21 is protruded toward the rear side of the vehicle, and a male screw 12 is provided at a tip end of the mounting shaft 11.
Are formed.

The first member 21 includes an inner cylinder 23 having a circular cross section fixed to the mounting shaft 11 of the front suspension member 10 and fixed by a nut 13 screwed to the male screw 12 of the mounting shaft 11, and the inner cylinder. 23, an outer cylinder 24 having a circular cross-section and a rubber elastic body 25 interposed between the inner cylinder 23 and the outer cylinder 24.
A hollow portion 26 called “curling” is formed along the axis of the mounting shaft portion 11.

The second member 22 is the outer cylinder 24 of the first member 21.
Cylindrical member 27 having a circular cross section for slidably fitting and fixing
The cylindrical member 27 is fixedly attached to the vehicle body 30 via a bracket 28 formed at the upper end thereof by welding or the like, and is vertically provided.

The outer cylinder 24 of the first member 21 is formed shorter than the inner cylinder 21 and longer than the cylindrical member 27 of the second member 22.
A positioning flange 29 protrudes from the front end on the vehicle rear side,
The end surface of the cylindrical member 27 on the vehicle rear side is in contact with the positioning flange 29.

The front suspension member 10 includes
An outer cylinder 24 of the first member 21 is provided on the distal end side of the mounting shaft portion 11.
The stopper 14 facing the one end side of the
The end surface of the inner cylinder 23 of the member 21 is fixed between the nut 13 and the nut 13, and a contact surface 15 is formed on the base side of the mounting shaft portion 11 to face the other end of the outer cylinder 24 with an interval.

The fitting of the outer cylinder 24 of the first member 21 and the cylindrical member 27 of the second member 22 causes the sliding displacement of the outer cylinder 24 of the first member 21 under a normal load applied to the front suspension member 10. If the load is greater than a predetermined value which is larger than the normal load and is not allowed, the outer cylinder 24 of the first member 21 is allowed to slide. As shown in FIG. The cabin 8 is located at the center of the vehicle in the front-rear direction X of the vehicle when viewed from the side of the vehicle.
It slopes down toward the side.

The front end 31a of the side member 31 of the vehicle body 30 is usually provided with an easily deformable portion such as a bead for absorbing the collision energy E when the vehicle collides from the front. However, when the collision energy E is very large, the front end 31a of the side member 31 alone cannot absorb the collision energy E, and the remaining collision energy E 'pushes the engine 4 and the transmission 6 into the vehicle compartment 8 side. It acts as a driving force F (see FIG. 3B).

A front suspension member 10 fixed to a side member 31 is generally disposed behind the engine 4 and the transmission 6, especially in an FF (front engine / front drive) vehicle. The front suspension member 10 has the strength to receive the load of the engine 4 and the jack-up load, and generally has rigidity to secure steering stability, and plastically deforms to reduce the collision energy E ′. The absorbing function is hard to expect.

For this reason, when the engine 4 and the transmission 6 are pushed toward the passenger compartment 8 at the time of a vehicle collision, the front suspension member 10 is pushed toward the passenger compartment 8 together with the engine 4 and the transmission 6 to enter the passenger compartment 8. try to. At this time, as shown in FIG. 4, when the front suspension member 10 is connected to the side member 31 so as not to move, the front suspension member 10 is in a stretched shape, and the rear end portion 31b of the side member 31 is Sometimes it breaks.

On the other hand, in the first embodiment, when the vehicle collides from the front and the pushing force F is applied to the front suspension member 10, the attachment 20 first moves to the front as shown in FIG. The inner cylinder 23 of the first member 21 fixed to the mounting shaft portion 11 of the suspension member 10 moves toward the passenger compartment together with the front suspension member 10, and the end face of the outer cylinder 24 on the vehicle front side is brought into contact with the front suspension member 10. It comes into contact with the contact surface 15.

For this reason, a pushing force acts on the outer cylinder 24 of the first member 21 via the front suspension member 10, and the outer cylinder 24 of the first member 21 is The two members 22 slide with respect to the cylindrical member 27, and descend together with the front suspension member 10 toward the vehicle interior 8 along the axis K of engagement with the cylindrical member 27.

Accordingly, in the first embodiment, when the vehicle collides from the front, as shown in FIG. 2B, the front suspension member 10 is connected to the fitting axis of the first member 21 and the second member 22 of the fixture 20. Since it descends to the cabin 8 side along K and does not stretch against the side member 31, the rear end 31b of the side member 31 is crushed, and the front end 31a and the rear end 31b of the side member 31 And the collision energy E
Can be absorbed.

In the first embodiment, the front suspension member 10 descends toward the cabin 8 at the time of a vehicle collision, so that the suspension member 10 can be prevented from entering the cabin 8 at the time of a vehicle collision. it can.

Further, in the first embodiment, at the time of a vehicle collision,
Since the steering rack 2 fixed to the front suspension member 10 descends together with the front suspension member 10, at the time of a vehicle collision, it is also possible to limit the retreat of the steering wheel in the cabin 8 continuous with the steering rack 2.

The operation and effect of the first embodiment in the case where the vehicle has a frontal collision have been described above. The operation and effect of the first embodiment during normal traveling will be described below. FIG.
FIG. 4 is an operation explanatory view of the first embodiment during turning of the vehicle,
FIG. 2A is a plan view, FIG. 2B is a front view illustrating an elastic center of a fitting on a vehicle front side, and FIG. 2C is a rear view illustrating an elastic center of a fitting on a vehicle rear side. FIG. 6 is an explanatory diagram of what is shown in FIG. 5 as viewed from the side of the vehicle.

Here, as shown in FIG. 5 (a), the reference numerals of the four attachments 20 are 20a for the front right side of the vehicle, 20b for the front left side of the vehicle, and 2 for the rear right side of the vehicle in plan view.
0c, the left rear side of the vehicle is distinguished from 20d.

As shown in FIGS. 5B and 5C, in the first embodiment, each of the fixtures 20a, 20b, 20c, 20d is provided.
A pair of hollow portions 26 facing each other is formed along the fitting axis K in the elastic body 25. Therefore, each elastic body 25 has a low rigidity direction G1 in which rigidity is low and easy to be displaced, and a high rigidity direction G2 in which rigidity is high and hard to be displaced, and each elastic body 25 is anisotropic in the direction of elastic displacement. Will be provided.
The low-rigidity and high-rigidity directions G1 and G2 are substantially orthogonal or completely orthogonal.

Here, if a straight line extending along the high rigidity direction G2 is defined as the elastic axis D of each elastic body 25,
The virtual elastic center P ′ on the front side of the vehicle of the front suspension member 10 which is determined in consideration of the anisotropy of the front suspension member 10 is the elastic body 2 of the mounting members 20a and 20b disposed on both sides on the front side of the vehicle.
5, the virtual elastic center Q 'on the rear side of the vehicle is connected to the two mounting members 20c, 2 disposed on both sides on the rear side of the vehicle.
It becomes the intersection of the elastic axis D of the elastic body 25 of 0d. A straight line passing through the virtual elastic centers P ′ and Q ′ on both sides in the vehicle front-rear direction X is a virtual roll axis n of the front suspension member 10.
(See FIG. 6).

In FIGS. 5 and 6, reference symbol P denotes a midpoint between the elastic members 25 of the two mounting members 20a and 20b disposed on the front side of the front suspension member 10 and the elastic member 25. Indicates the center of elasticity of the front side of the vehicle when there is no anisotropy, and the symbol Q indicates both mounting members 20c, 20 disposed on the rear side of the front suspension member 10 in the vehicle.
d is the midpoint between the elastic bodies 25 and indicates the elastic center on the vehicle rear side when the elastic bodies 25 have no anisotropy.

In the first embodiment, the positions of the hollow portions 26 of the two elastic members 25 on the front side of the vehicle are adjusted so that the virtual elastic center P ′ is located below the elastic center P. The arrangement position of the elastic body 25 is determined, and the arrangement of the hollow portions 26 of the two elastic bodies 25 on the vehicle rear side is adjusted, so that the virtual elastic center Q ′ is located above the elastic center Q on both sides of the vehicle. The arrangement position of the elastic body 25 is determined.

For this reason, in the first embodiment, as shown in FIG. 6, the virtual roll axis n of the front suspension member 10 is inclined rearward as viewed from the side of the vehicle. In addition, each fixture 2
When the elastic bodies 25 of 0a, 20b, 20c, and 20d have no anisotropy, the roll axis m of the front suspension member 10 is inclined forward when viewed from the side of the vehicle.

Here, a case where the virtual roll axis n and the roll axis m of the front suspension member 10 are located above the suspension roll center R determined from the suspension geometry will be described as an example. In this case, when the vehicle turns right, a lateral force J (see FIG. 5) acts on the suspension roll center R, and the front suspension member 10 generates a rotational moment M around its virtual roll axis n. .

In the first embodiment, since the virtual roll axis n of the front suspension member 10 is tilted rearward when viewed from the side of the vehicle, when the rotational moment M acts on the front suspension member 10, the front suspension member 10 becomes The elastic bodies 25 of the two attachments 20b and 20d on the left side in the direction Y are displaced downward toward the rear in the front-rear direction X of the vehicle, and the elastic bodies 25 of the two attachments 20a and 20c on the right side in the vehicle width direction are moved forward and backward of the vehicle. Displaced upward in the direction X forward.

As a result, the front suspension member 10 is displaced in a counterclockwise direction in a plan view of the vehicle, that is, in a lateral force toe-out direction, and the steering characteristic of the vehicle is in an understeer direction, and the steering stability during turning of the vehicle is improved. The performance is improved.

On the other hand, when the elastic body 25 has no anisotropy, the front suspension member 10 is displaced in the lateral force toe-in direction because a rotational moment M is generated around the roll axis m. However, the steering characteristic of the vehicle is in an oversteer direction, which is not preferable in terms of steering stability.

As described above, in the first embodiment,
With respect to the lateral force J applied to the suspension roll center R determined from the suspension geometry, the virtual elastic center P ′ determined in consideration of the anisotropy of the elastic bodies 25 of the two mounting components 20a and 20b on the front side of the vehicle. When the front suspension member 10 rotates about a virtual roll axis n passing through a virtual elastic center Q 'determined in consideration of the anisotropy of the elastic bodies 25 of the two mounting members 20c and 20d on the vehicle rear side. The elastic body 2 of each of the fixtures 20a, 20b, 20c, 20d is located at a position where the steering characteristic is in the understeer direction.
Since the arrangement position of No. 5 is set, the steering stability during turning of the vehicle can be improved.

In the first embodiment, each fixture 20
By inclining the elastic axis D of the elastic body 25 of a, 20b, 20c, and 20d, the distance S 'between the two virtual elastic centers P' and Q 'can be changed to the elastic center when the elastic body 25 has no anisotropy. The yaw stiffness of the front suspension member 10 can be increased equivalently since the distance S between the points P and Q is increased in the vehicle front-rear direction X, and as a result, the front suspension member 10 can pass through a rut or the like when traveling straight ahead. Suspension member 1
When 0 receives a disturbance input in the lateral direction, the influence of the disturbance input can be reduced, and the straight running stability of the vehicle can be improved.

Incidentally, it is possible to virtually provide an elastic center by inclining members outside or inside the elastic body B1 as in the case of the fixture B shown in FIG. Since the yaw rigidity cannot be increased, the straight running stability of the vehicle cannot be improved.

In the first embodiment, as shown in FIG. 3, the mounting shaft 11 of the front suspension member 10 is used.
A stopper 14 is provided at the distal end of the mounting member 20 so as to oppose the one end of the outer cylinder 24 of the attachment 20 at an interval. Is provided, the elastic body 25 can normally be elastically displaced between the contact surface 15 of the front suspension member 10 and the stopper 14, and the vibration of the front suspension member 10 is absorbed by the elastic body, so that the vehicle You can also improve the ride comfort.

In the first embodiment, even if the connection between the inner cylinder 223 and the outer cylinder 24 of the first member 21 is disconnected due to the deterioration of the elastic body 25 or the like, the inner cylinder 23 of the first member 21 is The front suspension member 10 can be prevented from falling off the vehicle body 30 because the stopper 14 can be prevented from coming off from the vehicle body 30.

Further, in the first embodiment, the outer cylinder 24 of the first member 21 is inserted into the cylindrical member 27 of the second member 22 of the fixture 20.
When the outer cylinder 24 is slidably fitted, the end surface of the cylindrical member 27 is brought into contact with the positioning flange 29 of the outer cylinder 24 so that the outer cylinder 24 is fitted and fixed in the cylindrical member 27 at a predetermined position. Since it can be performed, the workability of the fitting and fixing operation for fitting and fixing the outer cylinder 24 in the cylindrical member 27 at a predetermined position is improved.

In the first embodiment, the virtual elastic centers P 'and Q' are expanded in the vehicle front-rear direction X on both sides of the front suspension member 10 in the vehicle front-rear direction X, so that the yaw rigidity of the front suspension member 10 is equivalently increased. Was increased. However, the front suspension member 1
In order to increase the yaw stiffness of zero, the virtual elastic centers P ′ and Q ′ of the elastic body 25 may be expanded in the vehicle front-rear direction X on at least one side of the front suspension member 10 on both sides in the vehicle front-rear direction X.

(Second Embodiment) FIG. 7 is an explanatory diagram showing a second embodiment which is an example of an embodiment in which the inventions of claims 1 to 5 and 13 are combined, and FIG. , Second
It is explanatory drawing which shows the effect | action of embodiment, (a) has shown the state at the time of normal driving | running, and (b) has shown the state at the time of a small protrusion crossing. In the following description of the second embodiment, the same components as those of the first embodiment are denoted by the same reference numerals, and the description overlapping with the description of the first embodiment will be omitted.

The first embodiment and the second embodiment are different from the first embodiment in that all the fitting axes K of the four attachments 20 are inclined downward toward the center of the vehicle in the front-rear direction X of the vehicle. On the other hand, in the second embodiment, only the fitting axis K of the two attachments 20 'located on the vehicle rear side of the front suspension member 10 is inclined downward toward the vehicle center in the front-rear direction X of the vehicle. And two mounting fixtures 2 on the front side of the vehicle.
The fitting axis K of 0 'differs in that it extends along the vehicle front-rear direction X.

The elastic body 25 of the fixture 20 ′ of the second embodiment has a fitting direction H (see FIG. 8) along the fitting axis K of the fixture 20 ′. Since it is in the shearing direction, it has the largest elastic displacement in the fitting direction H.

In the second embodiment described above, when the vehicle collides from the front, the front suspension member 10
The vehicle moves in the front-rear direction X toward the cabin 8 located on the vehicle center side and does not squeeze against the side member 31, so that the rear end 31b of the side member 31 is moved in the same manner as in the first embodiment. It is possible to absorb the collision energy E by crushing.

In the second embodiment, the rear side of the front suspension member 10 descends toward the vehicle compartment 8 at the time of a vehicle collision. Intrusion into the inside can also be suppressed.

Further, in the second embodiment, at the time of a vehicle collision,
Since the steering rack 2 fixed to the front suspension member 10 descends together with the front suspension member 10, at the time of a vehicle collision, the retreat of the steering wheel in the cabin 8 continuous with the steering rack 2 is limited as in the first embodiment. You can also.

The operation and effect of the second embodiment when the vehicle has a frontal collision have been described above. The operation and effect of the second embodiment during normal traveling will be described below. FIG.
As shown in FIG. 7, when the front wheel 50 gets over the small protrusion t during traveling of the vehicle, a force T toward the rear of the vehicle is applied to the front suspension member 10.

At this time, the mounting member 20 'for the front suspension member 10 includes the first member 21 and the second member 22.
Relative to each other due to elastic displacement of the elastic body 25 in the fitting direction H between the front suspension member 10
, The front side slightly horizontally moves rearward, and the rear side slightly lowers rearward. As a result, the swing shaft 4 of the wheel support member 40 supported by the front suspension member 10
2, the rear side descends, the angle θ formed with the road surface decreases, and the trajectory of the wheel center 51 of the front wheel 50 is inclined backward.

Therefore, in the second embodiment, the trajectory of the wheel center 51 of the front wheel 50 tilts rearward when the front wheel 50 crosses the small protrusion t while the vehicle is running, and the vehicle is driven when the front wheel 50 crosses the small protrusion t. Comfort is improved.

FIG. 9 is an explanatory diagram showing the operation when the suspension member is the rear suspension member 60. As shown in FIG. 9, the rear suspension member 6
In the case of 0, only the mounting fixture 20 'on the front side of the rear suspension member 60 may be disposed so that the first fitting axis K is inclined downward toward the vehicle center in the front-rear direction X of the vehicle.

Then, when the rear wheel 70 rides over the small protrusion t while the vehicle is running, the force T applied to the rear suspension member 60 toward the rear of the vehicle causes the mounting member 20 'of the rear suspension member 60 to have the first member. A relative displacement occurs between the first member 21 and the second member 22 due to the elastic displacement of the elastic body 25 in the fitting direction H along the fitting axis K, and the front side of the rear suspension member 60 slightly rises rearward. Then, the rear side slightly horizontally moves rearward.

As a result, the rear suspension member 60
The rocking shaft 42 of the wheel supporting member 40 supported by the vehicle is raised on the front side, and the angle θ formed between the rocking shaft 42 and the road surface is reduced, so that the trajectory of the wheel center 71 of the rear wheel 70 is inclined backward.

Therefore, in the case of the rear suspension member 60, only the fitting 20 'on the front side of the rear suspension member 60 has its fitting axis K between the first member 21 and the second member 22 in the front-rear direction X of the vehicle. When the rear wheel 70 gets over the small protrusion t while the vehicle is running, the trajectory of the wheel center 71 of the rear wheel 70 is tilted rearward by disposing the vehicle so as to be inclined downward toward the vehicle center side. Riding comfort can be improved.

(Third Embodiment) FIG. 10 shows a third embodiment.
It is explanatory drawing which shows 3rd Embodiment which is an example of embodiment which carried out each invention described together, (a) has shown the normal state, (b) has shown the state at the time of a vehicle collision. . FIG.
FIG. 1 is a cross-sectional view showing a fixture according to a third embodiment,
(A) shows a normal state, and (b) shows a state at the time of a vehicle collision. In the following description of the third embodiment, the same components as those of the first embodiment are denoted by the same reference numerals, and the description that is the same as that of the first embodiment will be omitted.

As shown in FIG. 10A, the third embodiment has a suspension member mounting structure for mounting a rear suspension member 60 of an FR (front engine / rear drive) vehicle to a rear side member 33 of a vehicle body 30. The rear suspension member 60 has both ends on the front side in the vehicle width direction Y attached to the extension 34 of the side member 33 via the attachment 120, and both ends on the rear side in the vehicle width direction Y are attached via the attachment 120. It is attached to the member 33 and the four corners are attached to the vehicle body 30 via the attachments 120.

The rear suspension member 60 supports the differential 3 and a rear wheel support member (not shown). Behind the differential 3, a spare tire pan 7 for accommodating the spare tire 5 is provided. I have.

When the rear suspension member 60 is
Each of the four fixtures 120 attached to the side is shown in FIG.
As shown in FIG. 1A, a first member 121 is attached to the vehicle body 30 via a bracket 80, and a second member 122 is attached to the rear suspension member 60.

The bracket 80 is fixedly attached to the vehicle body 30 by welding or the like, and a mounting shaft portion 81 for mounting the first member 121 is provided at a lower end portion thereof so as to protrude toward the front of the vehicle. A male screw 82 is formed on the distal end side of the portion 81.

The first member 121 is an inner cylinder 123 having a circular cross section fixed to a mounting shaft 81 of a bracket 80 and fixed by a nut 83 screwed to a male screw 82 of the mounting shaft 81.
And an outer cylinder 124 having a circular cross-section
And an elastic body 125 made of rubber interposed between the inner cylinder 123 and the outer cylinder 124.

The second member 122 includes a cylindrical member 127 having a circular cross section for slidably fitting and fixing the outer cylinder 124 of the first member 121. The cylindrical member 127 is connected to the rear suspension member 60 by means such as welding. It is fixed with.

The outer cylinder 124 of the first member 121 is
3 is formed longer than the cylindrical member 127 of the second member 122, and a positioning flange 129 is protruded from a rear end located on the base side of the mounting shaft portion 81.
The rear end surface of the cylindrical member 127 is in contact with 29.

A bracket 80 fixed to the vehicle body 30
A stopper 8 is provided at the distal end side of the mounting shaft portion 81 so as to face the one end side of the outer cylinder 124 of the first member 121 with an interval.
4, a contact surface 85 is formed on the base side of the mounting shaft portion 81 to face the other end of the outer cylinder 124 at an interval.

The outer cylinder 124 of the first member 121 and the cylindrical member 127 of the second member 122 are fitted with each other under the normal load applied to the rear suspension member 60.
The second cylindrical member 127 is not fitted to allow the sliding displacement, and is fitted to allow the sliding displacement of the cylindrical member 127 of the second member 122 under a load larger than the normal load and a predetermined value or more, as shown in FIG. A fitting axis K coinciding with the axis of the mounting shaft portion 81 is inclined downward toward the vehicle compartment 8 located on the vehicle center side in the front-rear direction X of the vehicle when viewed from the side of the vehicle.

By the way, the rear end portion 33a of the side member 33 of the vehicle body 30 is usually provided with an easily deformable portion such as a bead for absorbing the collision energy E when the vehicle collides from behind. However, when the collision energy E is very large, the rear end 33a of the side member 33 alone cannot absorb the collision energy E, and the remaining collision energy E 'acts as a force for pushing the spare tire 5 into the vehicle compartment 8 side. I do.

However, the differential 3 is mounted in front of the spare tire 5, and the differential 3 is fixed to the rear suspension member 60. It will act as a pushing force to penetrate into the cabin 8 side.

At this time, in the third embodiment, FIG.
As shown in (b), the mounting member 120 is firstly pressed by the pushing force F acting on the rear suspension member 60 toward the vehicle interior, and the cylindrical member 127 of the second member 122 fixed to the rear suspension member 60 first. Moves toward the cabin 8 together with the outer cylinder 124 of the first member 121, and the front end surface of the outer cylinder 124 contacts the stopper 84 provided on the vehicle body 30 side.

Therefore, the outer cylinder 124 of the first member 121 is prevented from moving toward the cabin 8, and the cylindrical member 127 of the second member 122 slides with respect to the outer cylinder 124 of the first member 121. , Along with the rear suspension member 60 along the fitting axis K with the outer cylinder 124 toward the vehicle interior 8.

Therefore, in the third embodiment, when the vehicle collides from behind, as shown in FIG. 10B, the rear suspension member 60
The first member 122 descends toward the cabin 8 along the fitting axis K between the first member 122 and the second member 122, and does not stretch against the side member 33. As a result, the front end portion 33 b of the side member 33 during a vehicle collision And the collision energy E is applied not only to the rear end 33a of the side member 33 but also to the rear end 33b.
And the collision energy E by the side member 33 is absorbed.
Can be increased.

In addition, in the third embodiment, the rear suspension member 60 descends toward the cabin 8 at the time of a vehicle collision, so that the rear suspension member 60 is prevented from entering the cabin 8 at the time of a vehicle collision. You can also.

By the way, in the third embodiment, the attachment 12
No hollow portion called “curry” is formed in the elastic body 125 of “0”. However, also in the third embodiment, as in the first embodiment, by forming the cavity in the elastic body 125, the steering characteristics of the vehicle can be made to be in the understeer direction, and the steering stability during turning of the vehicle can be improved. Of course, the yaw rigidity of the rear suspension member 60 can be increased to improve the straight running stability of the vehicle.

The embodiments described above are merely examples of the embodiments of the present invention, and the specific configuration of the present invention is not limited to the configuration of each embodiment.

For example, in the second embodiment, at least one of the both sides of the suspension members 10, 60 in the vehicle front-rear direction X is lowered toward the center of the vehicle at the time of a vehicle collision. However, suspension member 1
If at least one of the positions 0 and 60 descends toward the center of the vehicle at the time of a vehicle collision, the suspension members 10 and 60 can be prevented from entering the passenger compartment 8 at the time of a vehicle collision. It is sufficient that at least one location of the vehicle 60 descends toward the center of the vehicle at the time of a vehicle collision.

Further, in each of the embodiments, the fittings 20, 12
0 has elastic bodies 25 and 125. However, in order to prevent the suspension members 10 and 60 from entering the cabin 8 at the time of a vehicle collision, the mounting members 20 and 120 are
There is no need to have 5,125. FIGS. 12A and 12B show an example of a fixture in which both the first and second members are rigid bodies. FIG. 12A shows a normal state, and FIG. 12B shows a state at the time of a vehicle collision.

As shown in FIG. 12A, this fixture 2
20 includes a first member 221 attached to the front suspension member 10 and a second member 222 attached to the vehicle body 30 side. A mounting shaft 11 for mounting the first member 221 is protruded from the front suspension member 10, and a male screw 12 is formed on a tip side of the mounting shaft 11.

The first member 221 is an inner cylindrical member 223 having a circular cross section fixed to the mounting shaft 11 of the front suspension member 10 and fixed by the nut 13 screwed to the male screw 12 of the mounting shaft 11. The two members 122 are cylindrical members 2 that slidably fit the inner cylindrical member 123.
The cylindrical member 224 is fixedly suspended from the vehicle body 30 via a bracket 225 by welding or the like.

The inner cylindrical member 223 is formed to be longer than the cylindrical member 224 of the second member 222, and has a positioning flange 226 protruding from the front end on the vehicle rear side. The cylindrical member of the second member 222 is formed on the positioning flange 226. 224 is in contact with the rear surface of the vehicle.

Then, the inner cylindrical member 223 and the cylindrical member 224
The fitting is such that the sliding displacement of the inner tubular member 223 is not allowed under the normal load applied to the front suspension member 10 and the sliding displacement of the inner tubular member 223 is allowed under a load greater than a predetermined value larger than the normal load. The fitting axis that coincides with the axis of the mounting shaft 11 is inclined downward toward the center in the front-rear direction of the vehicle when viewed from the side of the vehicle.

For this reason, when the vehicle collides from the front, FIG.
As shown in (b), the mounting member 220 is configured such that the inner cylindrical member 223 is attached to the cylindrical member 224 mounted on the vehicle body 30 side by a pushing force F acting on the vehicle interior side acting via the front suspension member 10. Slide against the cylindrical member 22
4 together with the front suspension member 10 along the axis of engagement with the vehicle 4 toward the center in the front-rear direction of the vehicle.

Therefore, even if both the first and second members 221 and 222 of the mounting member 220 are rigid, the first member 221 and the second member 22
2, the front suspension member 10 can be lowered toward the center in the front-rear direction of the vehicle along the axis of engagement with the vehicle 2;
Front suspension member 1 for side member
By releasing the tension of 0, the rear end of the side member is crushed, and the collision energy can be absorbed by the front end and the rear end of the side member.

Further, since the front suspension member 10 can be lowered toward the center in the front-rear direction of the vehicle at the time of a vehicle collision, it is possible to prevent the suspension member 10 from entering the passenger compartment at the time of a vehicle collision, and By lowering the steering rack fixed to 10 together with the front suspension member 10, it is also possible to limit the retreat of the steering wheel connected to the steering rack in the cabin.

Moreover, the mounting fixture 220 has a simple structure and can reduce the manufacturing cost as compared with the mounting fixture 22 of the first embodiment shown in FIG.

Further, the attachment 220 is attached to the inner cylindrical member 22.
3 has the positioning flange 226, so that when the inner cylindrical member 223 is slidably fitted and fixed in the cylindrical member 224, the positioning flange 22 of the inner cylindrical member 223 is fixed.
By bringing the end face of the cylindrical member 224 into contact with 6,
Fitting and fixing of the inner cylinder member 223 in the cylindrical member 224 can be performed at a predetermined position, and fitting and fixing work of fitting and fixing the inner cylindrical member 223 within the cylindrical member 224 at a predetermined position. Workability is improved.

FIGS. 13A and 13B show another example of a fixture in which both the first and second members are rigid. FIG. 13A shows a normal state, and FIG. 13B shows a state at the time of a vehicle collision. I have. The attachment 320 shown in FIG. 13 and the attachment 220 shown in FIG. 12 are different from the attachment 220 shown in FIG. 12 in that the bracket 225 of the second member 222 is fixed to the vehicle body 30 by welding or the like. The mounting member 320 shown in FIG.
2 in that the second bracket 325 is bolted to the vehicle body 30 side.

That is, FIG.
It is shown that the attachment of 0, 220, 320 to the vehicle body 30 may be fixed or fixed. And the mounting fixture 2
Suspension member 1 of 0, 120, 220, 320
Needless to say, attachment to 0 may be fixed or fixed. The operation and effect of the mounting fixture 320 shown in FIG. 13 at the time of a vehicle collision are the same as the operation and effect of the mounting fixture 220 shown in FIG. 12 at the time of a vehicle collision, and a description thereof will be omitted.

[Brief description of the drawings]

FIG. 1 is a perspective view showing a first embodiment.

FIG. 2 is an explanatory diagram showing an operation of the first embodiment,
(A) shows a normal state, and (b) shows a state at the time of a vehicle collision.

FIG. 3 is a cross-sectional view showing the mounting tool of the first embodiment,
(A) shows a normal state, and (b) shows a state at the time of a vehicle collision.

FIG. 4 is an explanatory view showing an operation at the time of a vehicle collision in a conventional structure.

FIGS. 5A and 5B are explanatory views showing the operation of the first embodiment during turning of the vehicle, wherein FIG. 5A is a plan view, FIG. 5B is a front view of a front-side mounting tool, and FIG. It is a rear view.

FIG. 6 is an explanatory view of the vehicle shown in FIG. 5 as viewed from the side of the vehicle.

FIG. 7 is an explanatory diagram showing a second embodiment.

FIG. 8 is an explanatory diagram showing the operation of the second embodiment,
(A) shows a state at the time of normal running, and (b) shows a state at the time of riding over a small protrusion.

FIG. 9 is an explanatory view similar to that shown in FIG. 8,
(A) shows a state at the time of normal running, and (b) shows a state at the time of riding over a small protrusion.

FIG. 10 is an explanatory view showing a third embodiment, in which (a)
Shows a normal state, and (b) shows a state at the time of a vehicle collision.

FIGS. 11A and 11B are cross-sectional views illustrating a fixture according to a third embodiment, wherein FIG. 11A illustrates a normal state, and FIG. 11B illustrates a state at the time of a vehicle collision.

FIG. 12 is a cross-sectional view illustrating an example of a fixture in which both the first and second members are rigid bodies, wherein FIG.
(B) shows a state at the time of a vehicle collision.

FIG. 13 is a cross-sectional view showing another example of a fixture in which both the first and second members are rigid bodies, wherein (a) shows a normal state,
(B) shows a state at the time of a vehicle collision.

FIG. 14 is an exploded perspective view showing an example of a conventional structure.

FIG. 15 is a diagram showing the VV of the assembly of FIG.
It is a line sectional view.

FIG. 16 is a perspective view showing another example of the conventional structure.

FIG. 17 is a sectional view showing a fixture used in a conventional structure.

[Explanation of symbols]

 Reference Signs List 10 front suspension member 11, 81 mounting shaft part 14, 84 stopper 15, 85 contact surface 20, 20 ', 120, 220, 320 mounting tool 21, 121, 221, 321 first member 22, 122, 222, 322 2 member 23,123 inner cylinder 24,124 outer cylinder 25,125 elastic body 26 hollow portion 27,127,224 cylindrical member 30 body 40 wheel support member 50 front wheel (wheel) 60 rear suspension member 70 rear wheel (wheel) 29 , 129, 226 Positioning flange 223 Inner cylinder member P ', Q' Virtual elastic center R Suspension roll center J Lateral force n Virtual roll axis Y Vehicle width direction X Vehicle longitudinal direction H Fitting direction K Fitting axis

 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Tamera Kasahara 2 Takaracho, Kanagawa-ku, Yokohama, Kanagawa Prefecture Inside Nissan Motor Co., Ltd.

Claims (14)

[Claims] 1. A vehicle in which both sides in a vehicle width direction and both sides in a vehicle front-rear direction of a suspension member that supports a wheel supporting member rotatably supporting a wheel so as to be able to swing up and down are respectively mounted on a vehicle body side via mountings. A suspension member mounting structure, wherein at least one of the mounting members is a first member mounted on one of the suspension member or the vehicle body side and a first member mounted on the other and fitted with the first member. The first member and the second member allow relative displacement along a fitting axis by a load applied to the suspension member over a predetermined level, and the fitting axis is a side surface of a vehicle. A suspension member mounting structure for a vehicle, characterized in that the vehicle is inclined downward toward the vehicle center in the front-rear direction of the vehicle. 2. The vehicle suspension member mounting structure according to claim 1, wherein the first member and the second member are fitted via an elastic body. Mounting structure. 3. The suspension member mounting structure for a vehicle according to claim 2, wherein the first member is fitted and fixed to a mounting shaft provided on one of the suspension member and the vehicle body; An outer cylinder penetrating the inner cylinder, and an elastic body made of rubber interposed between the inner cylinder and the outer cylinder, wherein the second member slidably fits and fixes the outer cylinder. A suspension member mounting structure for a vehicle, comprising a tubular member. 4. The vehicle suspension member mounting structure according to claim 3, wherein the outer cylinder is formed to be longer than the cylindrical member, the inner cylinder is formed to be longer than the outer cylinder, and the mounting shaft is provided. A stopper is provided on the distal end side of the portion, facing the one end side of the outer cylinder at an interval, and a contact surface facing the other end side of the outer cylinder at an interval is provided on the base side of the mounting shaft portion. Characteristic vehicle suspension member mounting structure. 5. The suspension member mounting structure for a vehicle according to claim 3, wherein a positioning flange that abuts on an end surface of the cylindrical member protrudes from the outer cylinder. Member mounting structure. 6. The vehicle suspension member mounting structure according to claim 1, wherein the first member and the second member are rigid bodies. 7. The vehicle suspension member mounting structure according to claim 6, wherein the first member is an inner cylindrical member fitted and fixed to a mounting shaft provided on one of the suspension member and the vehicle body. The suspension member mounting structure for a vehicle, wherein the second member includes a cylindrical member that slidably fits and fixes the inner cylindrical member. 8. The vehicle suspension member mounting structure according to claim 7, wherein the inner cylindrical member is formed longer than the cylindrical member. 9. The vehicle suspension member mounting structure according to claim 7, wherein a positioning flange that abuts on an end surface of the cylindrical member protrudes from the inner cylindrical member. Suspension member mounting structure. 10. The suspension member mounting structure for a vehicle according to claim 2, wherein the elastic body has anisotropy in a direction of elastic displacement, and
The mounting member including the member and the second member is disposed on at least one of both sides of the suspension member in the vehicle front-rear direction, and an arrangement position of the elastic body is different from that of the one side elastic body. A suspension member mounting structure for a vehicle, wherein the virtual elastic center determined in consideration of the performance is set at a position away from the mounting fixture on the other side in the vehicle front-rear direction. 11. The suspension member mounting structure for a vehicle according to claim 2, wherein the elastic body has anisotropy in a direction of elastic displacement, and
The attachment including the member and the second member is disposed on both sides in the vehicle longitudinal direction of the suspension member, and a position at which the elastic body is disposed is determined by a lateral force applied to a suspension roll center determined by a suspension geometry. The virtual elastic center on the front side determined in consideration of the anisotropy of the elastic body on the front side in the vehicle front-rear direction and the rear side determined in consideration of the anisotropy of the elastic body on the rear side in the vehicle front-rear direction. A steering characteristic set to a position where the steering characteristic is in an understeer direction when the suspension member rotates about a virtual roll axis of the suspension member passing through the virtual elastic center of the vehicle. 12. The suspension member mounting structure for a vehicle according to claim 10, wherein the elastic body is rubber, and the anisotropy of the elastic body elastically deforms a cavity along the fitting axis. A vehicle suspension member mounting structure formed by being provided on a body. 13. The vehicle suspension member mounting structure according to claim 2, wherein the suspension member is a front suspension member, and the mounting member includes the first member and the second member. Is disposed only on the rear side of the front suspension member in the front-rear direction of the vehicle, and the elastic body has an elastic characteristic in which an elastic displacement amount in a fitting direction along the fitting axis is the largest. Characteristic vehicle suspension member mounting structure. 14. The suspension member mounting structure according to claim 2, wherein the suspension member is a rear suspension member, and the mounting member includes the first member and the second member. Is disposed only on the front side in the vehicle front-rear direction of the rear suspension member, and the elastic body has an elastic characteristic having a largest elastic displacement amount in a fitting direction along the fitting axis. Characteristic vehicle suspension member mounting structure.