JPH1148728A - Suspension device for steering wheel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve straight advancing performance of a vehicle and a finding easiness of a neutral position in steering, by selecting a king pin shaft and a spring axial line to a straight line in a twist position, so that moment rotating in a toe-in direction around the king pin shaft is transmitted to a wheel support member by spring reaction force of a spring member. SOLUTION: In a strut type suspension, a spring axial line LB of a coil spring 13L(13R) interposed in a strut member 7L(7R) is set to a straight line in a twist position so as to be in a car width direction inner side in a car body upward side as viewed by front surface and in a vehicle rearward side as viewed by side surface relating to a king pin shaft LK, by spring reaction force of the coil spring 13L(13R), moment M in a toe-in direction around the king pin shaft is given to a knuckle 4L(4R), and by mounting a tie rod in the knuckle 4L(4R) so as to give an Ackermann steering characteristic, returning force to a neutral position is applied to act relating to a steering mechanism.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a suspension device for a steering wheel of an automobile.

[0002]

2. Description of the Related Art As a conventional steering wheel suspension device, for example, there is one described in Japanese Utility Model Laid-Open No. 54-130213.

In this conventional example, a shock absorber composed of a piston and a cylinder, a coil spring disposed coaxially with the shock absorber, a steering knuckle provided in a cylinder of the shock absorber, and a shock absorber A strut-type suspension system comprising a lower arm pivotally attached to the lower end of a cylinder and a strut bar extending forward of the vehicle connected to the lower arm, wherein an end of a piston rod of a shock absorber is detachable from a vehicle body. A vehicle suspension device is described which is configured to be mounted eccentrically with respect to a center axis of a cylindrical assembly mounted on a vehicle so that a tilt angle of a shock absorber that determines a caster angle can be selected.

[0004]

However, in the above-mentioned conventional suspension apparatus for a steered wheel, the caster angle can be selected according to whether or not the steering apparatus is a power steering. Although it is possible to set an appropriate caster angle according to it, since the shock absorber and the coil spring are arranged coaxially, the coil spring has only the function of supporting the vehicle body, so the straightness of the vehicle And the neutral position of the steering cannot be easily understood.

[0005] In order to improve the straightness of the vehicle and the clarity of the neutral position of the steering, it is necessary to understeer by means of a steering characteristic adjusting means such as a roll steer and a compliance steer. In the means, there is an unsolved problem that the adjustment allowance is small and it is difficult to sufficiently improve the straightness and the clarity of the neutral position of the steering.

Accordingly, the present invention has been made in view of the above-mentioned unsolved problems of the prior art, and utilizes the spring force of a spring member to improve the straightness of the vehicle and the clarity of the neutral position of steering. It is an object of the present invention to provide a steering wheel suspension device that can be improved.

[0007]

In order to achieve the above object, according to the first aspect of the present invention, a wheel is rotatably supported,
A wheel support member that is steerable about a kingpin axis and is swingably supported in a vertical direction with respect to the vehicle body, and is provided between the wheel support member and the vehicle body via one of a strut member and a shock absorber. In a suspension device for a steered wheel including an inserted spring member and a tie rod that performs a turning operation of the wheel support member, the tie rod includes:
The mounting point on the wheel support member side, on an arc drawn with a predetermined knuckle arm radius around the kingpin axis,
A moment for rotating the tie rod in the toe-in direction around the kingpin axis is transmitted to the wheel supporting member by a spring reaction force of the spring member provided inside an intersection of a tangent line drawn from the vehicle body side attachment point of the tie rod with respect to the arc. As described above, the kingpin axis and the spring axis are selected as a straight line at a twist position.

According to the first aspect of the present invention, since the kingpin axis and the spring axis are selected as straight lines at the torsion position, two straight lines which are not on the same plane in the three-dimensional Euclidean space are formed, and the spring reaction force is applied. A moment for rotating in the toe-in direction around the kingpin axis is transmitted to the wheel support member.

On the other hand, the attachment point of the tie rod to the wheel support member is set on the vehicle inner side from the intersection of the tangent drawn from the attachment point of the tie rod on the vehicle body side on an arc drawn with a predetermined knuckle arm radius centered on the kingpin axis. By
When turning, the turning angle of the turning inner wheel is larger than the turning angle of the turning outer wheel. Therefore, the change amount of the steering angle on the inner wheel side is larger than the unit movement amount of the steering mechanism, and the equivalent knuckle arm radius on the inner wheel side as viewed from the steering system is smaller than the outer wheel side. It will be shorter than the equivalent knuckle arm radius.

For this reason, when the tie rod is located rearward (or forward) from the kingpin axis during turning, a pulling force (or a compressive force) acts on the tie rod, but these acting forces are compared with those on the turning outer wheel side. As a result, the inner working side of the turning wheel becomes large, and the difference between the acting forces becomes a force for returning the steering mechanism to the neutral position side, so that the neutral position of the steering can be easily understood and the straightness of the vehicle is improved.

According to a second aspect of the present invention, there is provided a wheel support member rotatably supporting a wheel and capable of turning around a kingpin axis, a lower portion rigidly connected to the wheel support member and an upper portion connected to a vehicle body side member. A supported strut member, a spring member interposed between the strut member and the vehicle body, a lower link having one end interposed between a lower portion of the wheel support member and a vehicle body-side member, and the wheel In a strut-type steering wheel suspension device including a tie rod that performs a turning operation of a support member, the tie rod draws an attachment point on the wheel support member side at a predetermined knuckle arm radius around the kingpin axis. The tie rod is provided on the inner side of the intersection of a tangent line drawn from the vehicle body-side mounting point of the tie rod with respect to the arc and the wheel support member is kinked by a spring reaction force of the spring member. As the moment for rotating the toe direction of the pin axis is transmitted, the kingpin axis and the spring axis is characterized in that it is selected a straight line skewed.

According to the second aspect of the present invention, the first aspect of the present invention is the same as the first aspect of the invention except that the suspension device is configured in a strut type.
Since it has the same configuration as the invention according to the first aspect, the same operation as the first aspect of the invention can be obtained.

Further, the invention according to claim 3 is based on claim 2.
In the invention according to the present invention, the spring axis is inclined so as to enter the inside of the vehicle on the vehicle upper side with respect to the kingpin axis when viewed from the front of the vehicle, and with the vehicle rear side on the vehicle lower side with respect to the kingpin axis in a vehicle side view. It is characterized in that the spring axis and the kingpin axis are selected as a straight line at the twist position.

According to the third aspect of the present invention, the intersection between the spring axis and the kingpin axis is different between the front view and the side view, so that the two become a straight line at the twist position.
In addition, since the point of action of the spring reaction force on the wheel support member is on the outside of the vehicle with respect to the kingpin shaft when viewed from the front and on the vehicle rear side when viewed from the side, a moment for rotating the wheel support member around the kingpin axis in the toe-in direction is given. .

According to a fourth aspect of the present invention, a wheel is rotatably supported, a wheel support member capable of turning around a kingpin axis, and one end is rotatably attached to a lower portion of the wheel support member. A lower link having one end rotatably supported on the vehicle body-side member, an upper link rotatably mounted on one end above the wheel support member, and the other end supported on the vehicle body-side member so as to be vertically rockable; A shock absorber inserted between the wheel support member and the vehicle body-side member, and a spring member inserted between the shock absorber and the vehicle body-side member,
In a double wishbone type steering wheel suspension device provided with a tie rod that performs a turning operation of the wheel support member, the tie rod is configured such that an attachment point on the wheel support member side is fixed to a predetermined knuckle around the kingpin axis. On the arc drawn by the arm radius, provided inside the intersection of the tangent drawn from the vehicle body side attachment point of the tie rod with respect to the arc, and the wheel support member around the kingpin axis by the spring reaction force of the spring member The kingpin shaft and the spring axis are selected as a straight line at a torsion position so that a moment for rotating in the toe-in direction is transmitted.

According to a fourth aspect of the present invention, in the first aspect of the invention, the same configuration as the first aspect of the invention is provided except that the suspension device is configured in a double wishbone type. Therefore, the same operation as the first aspect of the invention can be obtained.

Still further, according to a fifth aspect of the present invention, in the fourth aspect of the invention, the shock absorber and the spring member are coaxially arranged, and the shock absorber is a wheel support member on the vehicle inner side of the kingpin shaft. And mounted so as to incline toward the vehicle front side on the vehicle upper side with respect to the kingpin axis when viewed from the side of the vehicle.

According to the fifth aspect of the present invention, since the shock absorber arranged coaxially with the spring member is selected to have a relationship between the kingpin axis and the torsion position, the wheel support member is caused by the reaction force of the spring member. To the toe-in direction about the kingpin axis.

The invention according to claim 6 is characterized in that, in the invention according to any of claims 2 to 5, the lower link is constituted by two link members. In the invention according to claim 6, the kingpin axis at the time of turning can be used as the virtual kingpin axis on the lower link side.

Further, the invention according to claim 7 is based on claim 4.
The invention according to any one of the first to sixth aspects, wherein the upper link is constituted by two link members.

In the invention according to claim 7, the kingpin axis at the time of turning can be used as the virtual kingpin axis even on the upper ring side.

[0022]

According to the first aspect of the present invention, the tie rod exerts the Akkaman characteristic at the time of turning, and the spring axis and the kingpin axis are set as a straight line of the twist position, and the wheel support member is used as a reaction force of the spring member. By applying a moment in the toe-in direction about the kingpin axis to the steering system, a force to return the steering system to the neutral position is given, thereby improving the straight running performance and improving the clarity of the neutral position of the steering. The effect is obtained.

According to the second aspect of the present invention, since the suspension according to the first aspect has the same configuration as that of the first aspect except that the suspension device is configured in a strut form, The same effect as the first aspect can be obtained by the suspension device of the type.

Further, according to the invention according to claim 3, in the invention according to claim 2, the spring axis is inclined so as to enter the vehicle inside on the vehicle upper side with respect to the kingpin axis when viewed from the front of the vehicle, and Since the vehicle is inclined so as to be positioned below the vehicle with respect to the kingpin axis and toward the rear of the vehicle when viewed from the side of the vehicle, a moment in the toe-in direction can be given to the wheel support member around the kingpin axis as a reaction force of the spring member. The effect is obtained.

Further, according to the fourth aspect of the present invention, in the first aspect of the present invention, except that the suspension device is configured in a double wishbone type, the configuration is the same as that of the first aspect. Therefore, it is a double wishbone type suspension device.
The same effect as described above can be obtained.

Still further, according to the fifth aspect of the present invention, in the fourth aspect of the invention, the shock absorber arranged coaxially with the spring member is selected according to the relationship between the kingpin shaft and the position of the torsion. Thus, an effect is obtained that a moment for rotating the wheel support member in the toe-in direction around the kingpin axis can be given to the wheel support member by the reaction force of the spring member.

According to the sixth aspect of the present invention, since the lower link is composed of two links, a virtual kingpin can be formed even when the lower link is used as the kingpin at the time of steering, and the brake rotor and the like are provided. There is an effect that the kingpin can be set at the optimum position without considering interference with other components.

Further, according to the invention of claim 7, since the upper link is constituted by two link members, the king pin at the time of turning can be formed as a virtual king pin even with the upper link. The effect that the king pin can be set to the optimum position without taking into consideration the interference with the other components is obtained.

[0029]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a perspective view showing a schematic configuration showing one embodiment of the present invention, in which 1 is a suspension member attached to a vehicle body, and a side member extending in a vehicle front-rear direction at a predetermined interval. 1a, 1b and a connecting member 1c for connecting between the intermediate portions thereof, are formed in an H shape, are attached to the vehicle body at front and rear end portions of both side members 1a, 1b, and further, are rear end portions of both side members 1a, 1b. The spaces are connected by a crossbar 1d.

The suspension member 1 is provided as a wheel member for supporting the wheels 3L, 3R via transverse links 2 as lower links extending outward in the vehicle width direction at left and right ends of the connecting member 1c. Knuckle 4
L, 4R are mounted to be swingable up and down.
A tension rod 5 is attached to the front ends of a and 1b so as to be vertically swingable.

At the upper ends of the knuckles 4L, 4R, knuckle arms 6L, 6R are integrally formed extending inward in the vehicle width direction, and strut members 7L, 7R are rigidly connected to tips of the knuckle arms 6L, 6R. ing.

Each of the strut members 7L and 7R is shown in FIG.
As is apparent with reference to (a), the cylinder tube 8a is connected to the knuckle arms 6L and 6R, and the upper ends of the piston rods 8b protruding from the upper ends of the cylinder tubes 8a are connected to the mount rubbers 9L and 9R and the mounting plate 10R.
L, 10R, and upper spring seats 11L, 11R attached to the lower surfaces of the attachment plates 10L, 10R around the piston rod 8b. It comprises cylindrical coil springs 13L, 13R as spring members interposed between lower spring seats 12L, 12R attached to the upper end of the cylinder tube 8a.

[0033] Here, the shock absorber 8L, the central axis of 8R, as shown in FIG. 2 (a) representing the front view, the strut member 7L, the vehicle body side attachment point of the 7R P _S and transverse link 2 and the knuckle 4L , is inclined so that the inward relative to the kingpin axis L _K connecting the attachment point P _T of the 4R, and as shown in FIG. 2 (b) representing a side view, forming a predetermined caster angle is inclined slightly vertically relative to the kingpin axis L _K to.

On the other hand, the coil springs 13L, 13R
Spring axis L_BIs a kin in FIG. 2A showing a front view.
Gpin axis L_KThe upper end position of the cylinder tube 7a
At the intersection, and as you move upward,
On the lower side, the link axis L of the transverse link 2
_TAnd the vertical line L passing through the wheel center WC_WIntersection P with _LW
FIG. 2B, which is inclined so as to pass through and shows a side view.
And the kingpin axis L _KOf the piston rod 8b
Body mounting point P_SAt the intersection and go down below
It is set in a substantially vertical direction on the rear side of the vehicle.

As a result, the kingpin axis L _K and the spring axis L
_B is different in the intersection position between the front view and the side view, and is a two straight line that is not on the same plane in the three-dimensional Euclidean space, and is set as a straight line at the twist position.

[0036] Thus, by setting the kingpin axis L _K and the spring axis L _B a straight line skewed, yet the vehicle width direction at the vehicle upper side in the front view with respect to the spring axis L _B is the kingpin axis L _K inclined to become the inside, by inclining the vehicle rear side in side view, kingpin axis L _K coil springs 13L, the spring reaction force F _B at 13R knuckle 4L as the wheel supporting member, relative 4R It acts as a rotational moment in the toe-in direction around.

Further, the knuckle 4L, tie rods 15L on the rear side of the kingpin axis L _K of 4R, 15R are connected via a ball joint (not shown), these tie rods 15L, the vehicle width direction inner ends of the 15R body For example, a steering mechanism 16 of a rack and pinion type, which is fixedly supported on the rack shaft, is connected to both ends of a rack shaft.

Here, the mounting positions of the tie rods 15L, 15R with respect to the knuckles 4L, 4R are shown in plan view in FIG.
As shown in, on kingpin axis L _K arc drawn centered at the knuckle arm radius of the radius of the C, the vehicle width direction than the intersection point P _R when drawn tangent from the attachment point P _TI of the steering mechanism 16 side Tie rod 15 at the inner mounting point P _TO
By attaching L, 15R, the so-called Akkaman steer characteristic in which the steering angle on the turning inner wheel side is larger than the steering angle on the turning outer wheel side in a steered state during turning traveling is set. In this case, tie rods 15L, knuckle 4L of 15R, by setting the mounting position at the intersection P _R for 4R, steering angle of the inner and outer rings is equal parallel steering characteristic from each other during a turn.

Next, the operation of the above embodiment will be described. Coil springs 13L, spring axis L _B of 13R is as shown in FIG. 2 (a) and (b) with respect to the kingpin axis L _K, is set to a straight line of a so-called skewed without a spatially intersection, space manner, since the direction of the spring axis L _B are arranged so that the vehicle rear side of the kingpin axis L _K, the coil springs 13L, 13R of the spring reaction force F _SPR
The knuckles 4L and 4R are shown in FIG. 2 (a) and FIG.
As shown in FIG. 7, a moment M for rotating the king pin in the toe-in direction around the axis is transmitted.

On the other hand, in the case of a steering wheel suspension, in order to realize smooth turning of the vehicle in a low-speed large steering angle region such as when making a U-turn, an inner wheel side steering angle called so-called Akkaman steer characteristic is used. In general, the tie rods 15L and 15R are attached to the knuckles 4L and 4R by a king pin as shown in FIG. on the axis L arc _K drawn centered at the knuckle arm radius of the radius of the C, intersection P _R a vehicle width direction inner side than the mounting point P when drawn tangent from the attachment point P _TI of the steering mechanism 16 side By setting it to _TO , the inner and outer wheel steering angle characteristics tend to be Akkaman steer characteristics.

Here, the fact that the inner and outer wheel steering angle characteristics having the tendency of the Akkaman steer characteristic are given means that the inner wheel side is compared with the outer wheel side with respect to the unit movement amount of the rack shaft of the steering mechanism. That is, the change amount of the steering angle is large. This means that the equivalent knuckle arm radius on the inner wheel side when viewed from the steering system is shorter than the equivalent knuckle arm radius on the outer wheel side.

Therefore, as shown in FIG. 4, a moment M for rotating the knuckles 4L and 4R in the toe-in direction around the kingpin axis by the spring reaction force F _SPR of the coil springs 13L and 13R is input. The tie rods 15L and 15R arranged rearward of the vehicle from the transverse link 2 serving as the lower link receive tensile forces Fo and Fi.

Here, as described above, with turning,
Since the equivalent knuckle arm radius is different between the inner ring side and the outer ring side, and the equivalent knuckle arm radius is closer on the inner ring side, the magnitude relationship between the pulling forces Fo and Fi input to the tie rods 15L and 15R is Fo. <Fi,
The rack shaft 16a receives a force in the direction in which the rudder returns by this difference in the force.

By this operation, the rise of the reaction force of the steering system is improved, and the neutral position (center) of the steering system can be easily understood, and the straightness of the vehicle can be improved.

Next, a second embodiment of the present invention will be described with reference to FIGS. In the second embodiment, FIG.
1 has the same configuration as that of FIG. 1 except that the tie rods 15L and 15R are arranged on the vehicle front side with respect to the transverse link 2 serving as the lower link.

[0046] According to the second embodiment, as shown in FIG. 6, by the first embodiment as well as a spring axis L _B and kingpin axis L _K is set to a straight line skewed Due to the spring reaction force F _SPR of the coil springs 13L, 13R, a moment M in the toe-in direction around the kingpin axis is input to the knuckles 4L, 4R.

The tie rod 15L is generated by the moment M.
And 15R generate forces Fi and Fo in the compression direction,
At this time, since the inner and outer wheel steering angle characteristics of the Akkaman steer characteristics are given, the equivalent knuckle arm radius is shorter on the inner wheel side than on the outer wheel side.

Therefore, the tie rods 15L and 15R
Is smaller than Fo <Fi.
Since the large compressive force Fi acts in the direction of pushing back the rack shaft 16a, the rise of the reaction force of the steering system is improved, and the center of the steering system is easily understood, and the straightness of the vehicle is improved.

In the first and second embodiments, the transverse link 2 as the lower link is
Although the description has been made of the case where the link member is constituted by the book link member, the present invention is not limited to this.
And the tension rod 5 is omitted, and instead of these, the outer ends of the two link members mounted on the suspension member 1 so as to be able to swing up and down are knuckles 4L and 4L, respectively.
May be attached via a connecting member such as separately ball joint to the lower end side of the 4R, in this case, the kingpin axis L _K and a vehicle body side mounting point and a knuckle-side attachment point of each lower link members, shock absorber 8L, becomes a line of intersection of two planes containing the vehicle body side attaching point P _S of 8R, at the height of the lower link member does not pass through the attachment point between the link member and the knuckle, be a kingpin axis in the virtual Yes, regardless of interference with other parts such as the brake rotor,
There is an advantage that the kingpin shaft can be set at an optimum position.

Next, a third embodiment of the present invention will be described with reference to FIGS. In the third embodiment, the present invention is applied to a double wishbone type in place of the strut type suspension in the first and second embodiments.

In the third embodiment, as shown in FIGS. 7A and 7B, knuckles 4L and 4R are provided with A-shaped arms 21 and 22, respectively, which project from the upper and lower ends thereof. The vertices of the upper link 23 and the lower link 24 formed in a shape are connected via ball joints 25 and 26, and the front end and the rear end of the other end of the upper link 23 and the lower link 24 are respectively a vehicle body such as a suspension member. Each of the side members is supported so as to be vertically swingable.

Then, the upper link 23 and the arm 21
King pin axis L connecting the center point P _UB of the ball joint 25 serving as a point of attachment to the lower link 24 and the center point P _LB of the ball joint 26 serving as a point of attachment to the arm 22.
_K is inclined so that the inside of the vehicle body as it goes upward in FIG. 8 representing the front view becomes the rear side of the vehicle body as it goes upward in FIG. 9 and represents a side view, a vertical line so that a predetermined caster angle is obtained Is inclined clockwise with respect to.

On the other hand, a shock absorber 30 is interposed between the knuckles 4L, 4R and the upper body-side member, and a cylinder tube 30a is mounted on the knuckles 4L, 4R so as to be swingable up and down. The upper end of the piston rod 30b protruding upward from is mounted on the vehicle body side member.

A coil spring 31 is inserted around the piston rod 30b coaxially with the upper end of the coil rod 31 and the lower end thereof is supported by the cylinder tube 30a.

Here, the shock absorber 30 has its central axis L _S coincident with the vertical line inside the kingpin axis L _{K in the} vehicle width direction in FIG. 7A showing the front view and FIG. is inclined in a counterclockwise direction with respect to the vertical line so as to be substantially symmetrical with respect to the vertical line in (b) with respect to the kingpin axis L _K.

Next, the operation of the third embodiment will be described. In the third embodiment, with respect to the spring axis L _B is the kingpin axis L _K of the coil spring 31 is provided to be inclined toward the front of the vehicle in and side view in the vehicle width direction inner side in the front view, both since the first and similarly skewed straight lines and the second embodiment described above, the spring reaction force F _SPR, knuckle 4L, the moment the toe direction kingpin axis L _K around the 4R M is transmitted .

On the other hand, since the shock absorber 30 is attached to the knuckles 4L and 4R inside the vehicle with respect to the kingpin shaft L _K , as shown in FIG. 8, the knuckles of the shock absorber 30 are turned as the wheels 3L and 3R are steered. The 4L, 4R side mounting point P _SAB is indicated by the arrow A on the outer ring side due to the caster angle.
It falls as shown by o, and the inner wheel side rises as shown by arrow Ai, and moves up and down.

[0058] This movement of the attachment point P _SAB, spring loaded, increases in inner ring, results in a decrease in the outer ring, the kingpin axis L _K around the knuckle 4L, even moment M to rotate the 4R The inner ring side is larger than the outer ring side.

As a result, also in the third embodiment, as in the first and second embodiments described above, the rising of the steering system is improved, and the center of the steering system is easily understood, and the straightness of the vehicle is improved. Can be done.

[0060] Moreover, in the third embodiment, the spring load increases in the inner ring by the action of the caster angle during turning, so decreases in the outer side, tie rods 15L, 15 is a vehicle rear side of the kingpin axis L _K , Or the difference between the compressive forces Fo and Fi when attached to the front side of the vehicle with respect to the kingpin axis L _{K is} larger than that of the first and second embodiments. The center of the steering system can be more easily understood, and the straightness of the vehicle can be further improved.

In the third embodiment, the case where the lower link 24 is formed by one A-shaped link member has been described. However, the present invention is not limited to this. The knuckles 4L and 4R may be divided and supported, and in this case, the kingpin axis at the time of turning is determined by the intersection of the link axes of both link members, the upper link 23, and the arm 21 of the knuckles 4L and 4R. It can be a virtual kingpin axis that does not pass through the lower link knuckle side attachment point, and the kingpin axis can be set to the optimum position regardless of interference with other parts such as the brake rotor. There are advantages.

Further, the spring axis L in each of the above-described embodiments is used.
The linear relationship of the torsional position between _B and the kingpin axis L _K is set to an arbitrary inclination angle as long as the moment in the toe-in direction around the kingpin axis can be transmitted to the knuckles 4L and 4R by the spring reaction force of the spring coils 13L and 13R. Can be selected.

Further, in each of the above-described embodiments, the case where the coil springs 13L, 13R and 31 are formed in a cylindrical shape has been described. However, the present invention is not limited to this. And the like can be applied.

Further, in each of the above embodiments, the case where the present invention is applied to the front suspension has been described. However, the present invention is not limited to this, and the present invention is applied to the rear suspension of a four-wheel steering vehicle. In other words, the present invention can be applied to any steering suspension.

[Brief description of the drawings]

FIG. 1 is a perspective view showing a first embodiment when the present invention is applied to a front suspension device.

FIGS. 2A and 2B are schematic configuration diagrams of FIG. 1, wherein FIG. 2A is a schematic front view as viewed from the front of the vehicle body, and FIG. 2B is a schematic side view as viewed from the side of the vehicle in FIG.

FIG. 3 is a schematic plan view of FIG. 1 showing a mounting relationship of a tie rod.

FIG. 4 is a schematic plan view for explaining the operation of the first embodiment.

FIG. 5 is a perspective view showing a second embodiment when the present invention is applied to a front suspension device.

FIG. 6 is a schematic plan view for explaining the operation of the second embodiment.

FIGS. 7A and 7B are schematic views showing a third embodiment of the present invention, wherein FIG. 7A is a front view as viewed from the front of the vehicle body, and FIG. 7B is a side view as viewed from the side of the vehicle body.

FIG. 8 is a diagram illustrating an operation of the third embodiment;
It is a side view similar to (b).

[Explanation of symbols]

Reference Signs List 1 suspension member 2 transverse link (lower link) 3L, 3R wheel 4L, 4R knuckle 5 tension rod 7L, 7R strut member 8L, 8R shock absorber 13L, 13R coil spring 15L, 15R tie rod 16 steering mechanism 16a rack shaft L _K kingpin Shaft L _B Spring axis 21, 22 Arm part 23 Upper link 24 Lower link 25 Elastic bush (body side) 24 Rotary axis 31 Shock absorber 32 Spring L _S Shock absorber axis

Claims (7)

[Claims] 1. A wheel support member rotatably supporting a wheel, capable of turning around a kingpin axis, and supported swingably in a vertical direction with respect to a vehicle body, and between the wheel support member and the vehicle body. A suspension member for a steered wheel, comprising a spring member inserted through any one of a strut member and a shock absorber, and a tie rod for performing a turning operation of the wheel support member. A mounting point on a side of an arc drawn with a predetermined knuckle arm radius about the kingpin axis, inside an intersection of a tangent drawn from the vehicle body side mounting point of the tie rod with respect to the arc, and the spring The kingpin axis and the spring axis are transmitted so that a moment for rotating in the toe-in direction around the kingpin axis is transmitted to the wheel support member by the spring reaction force of the member. Is selected as the straight line of the twist position. 2. A wheel support member rotatably supporting a wheel and capable of turning around a kingpin axis, a strut member having a lower portion rigidly connected to the wheel support member and an upper portion supported by a vehicle body side member, A spring member inserted between a strut member and a vehicle body, a lower link having one end inserted between a lower portion of the wheel support member and a vehicle body-side member, and a turning operation of the wheel support member. In a strut-type steering wheel suspension device provided with a tie rod, the tie rod has an attachment point on the wheel support member side on an arc drawn with a predetermined knuckle arm radius around the kingpin axis. On the other hand, the tie rod is provided inside the intersection of the tangent line drawn from the vehicle body side attachment point, and the toe-in direction around the kingpin axis is applied to the wheel support member by the spring reaction force of the spring member. The suspension device for a steered wheel, wherein the kingpin shaft and the spring axis are selected as a straight line at a twist position so that a moment to rotate is transmitted. 3. The vehicle according to claim 1, wherein the spring axis is inclined so as to enter the vehicle inside on the vehicle upper side with respect to the kingpin axis when viewed from the front of the vehicle, and is connected to the vehicle rear side on the vehicle lower side with respect to the kingpin axis in a vehicle side view. The suspension apparatus for a steered wheel according to claim 2, wherein the spring axis and the kingpin axis are selected as a straight line at a twist position. 4. A wheel support member rotatably supporting a wheel and capable of turning around a kingpin axis, one end rotatably mounted below the wheel support member, and the other end swinging up and down on a vehicle body side member. A lower link that is rotatably supported, an upper link rotatably attached at one end to an upper portion of the wheel support member, and an upper link rotatably supported at the other end by the vehicle body-side member, and the wheel support member and the vehicle body-side member. A double wishbone type comprising a shock absorber interposed between the shock absorber, a spring member interposed between the shock absorber and the vehicle body side member, and a tie rod for turning the wheel support member. In the steering device for a steered wheel, the tie rod is configured such that an attachment point on the wheel support member side is on an arc drawn with a predetermined knuckle arm radius around the kingpin axis with respect to the arc. The tie rod is provided inside the intersection of a tangent drawn from the vehicle body side attachment point, and the moment for rotating in the toe-in direction around the kingpin axis is transmitted to the wheel support member by the spring reaction force of the spring member. A suspension device for a steered wheel, wherein a kingpin axis and a spring axis are selected as straight lines at a twist position. 5. The shock absorber and a spring member are coaxially arranged, the shock absorber is mounted on a wheel support member inside the vehicle with respect to the kingpin axis, and the vehicle is located above the kingpin axis with respect to the kingpin axis when viewed from the side of the vehicle. The suspension device for a steered wheel according to claim 4, wherein the suspension device is mounted so as to be inclined forward. 6. The steering device for a steered wheel according to claim 2, wherein the lower link includes two link members. 7. The suspension device for a steered wheel according to claim 4, wherein the upper link is constituted by two link members.