JPH07132720A - Mounting structure for suspension member - Google Patents

Abstract

PURPOSE:To provide a mounting structure for a suspension member wherein steering responsiveness and an underster characteristic can be improved, needless to say, obtaining excellent riding comfortableness while a confined sound in a cabin can be sufficiently reduced. CONSTITUTION:In a rear suspension member 11, a car body longitudinal direction front side is supported through soft mounts 12a, 12b having low rigidity in a car body longitudinal direction and vertical direction and high rigidity in a lateral direction, and a car body longitudinal direction rear side is supported through a watt link 80. In a front suspension member, car body longitudinal direction front side is supported through the watt link 80, and a car body longitudinal direction rear side is supported through the soft mounts 12a, 12b having low rigidity in a car body longitudinal direction and vertical direction and high rigidity in a lateral direction.

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, and more particularly to an improvement of a suspension member mounting portion to a vehicle body.

[0002]

2. Description of the Related Art As a conventional suspension member,
For example, the structure disclosed in Japanese Utility Model Publication No. 1-165769 is known. An example of this suspension pension member is shown in FIG. That is, FIG. 15 is a perspective view of a multi-link type rear suspension in which the right suspension is omitted, as seen from the front of the vehicle body, and includes a suspension member 101 whose front side extends outward and is commonly used for the left and right sides.

This suspension member 101 is shown in FIG.
Describing the left suspension shown in FIG. 5, between the left side portion 101a of the suspension member 101 extending in the vehicle front-rear direction and the wheel hub 103, a lower arm 104, a front upper arm 105, and a toe control arm that constitute the left suspension. 106 and a rear upper arm 107, and a structure in which a strut 109 is connected between the wheel hub 103 and the strut tower 108 of the vehicle body.

The suspension member 101
Is a soft mount 1 placed at the front, back, left and right corners
It is attached to the vehicle body via 02A, 102B, 102C and 102D. When the vertical acceleration P acts on the center of gravity of the suspension member 101 attached to the vehicle body as shown in FIG. 16 (a), a vibration mechanism as shown in FIG. 16 (b) is obtained.

Further, as shown in FIG. 17A, when an acceleration moment M about the center of gravity acts on the suspension member 101, a vibration mechanism as shown in FIG. 17B is obtained. Therefore, in the above-mentioned conventional structure, the inertia moment I of the rear suspension may be changed due to other design conditions.
(Moment of inertia of suspension member 101) and soft mounts 102A, 102B to 102C, 1
Even if the distance L _{1 to} 02D is already determined, by adjusting the spring constant K ₃ of the soft mounts arranged at the front and rear of the vehicle body, specifically, by reducing K ₃ , the vehicle at medium speed It is possible to set the pitching resonance frequency, which has a great influence on the muffled sound in the room, to a sufficiently low frequency. Therefore, there is an advantage that it is possible to sufficiently reduce the muffled sound in the vehicle compartment at the middle speed.

[0006]

However, in the conventional suspension member 101, the soft mounts 102A, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102A, 102B, 102B, 102B, 102B, 102A, 102B, 102A, 102B, 102A, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102B, 102A, 102B, 102B, 102A, 102B, 102A, 102B, 102B, 102B, 102A, 102B, 102A, 102B, 102B, 102A, 102B, 102B, 102A, 102 </ b> B, and 102 </ b> B in order to sufficiently reduce the muffled noise in the passenger compartment at a medium speed, 10
The longitudinal spring constants of 2C and 102D are small, that is,
The rigidity is reduced. Therefore, when a lateral force is applied to the vehicle body, the vehicle body is easily deformed, and the suspension member 10
However, there is a problem that the entire steering wheel 1 is displaced and the alignment of the wheels is changed, so that excellent steering response cannot be obtained.

Furthermore, considering the turning of the vehicle body,
When lateral force is input during turning, it becomes difficult to obtain rigidity in the lateral direction of the vehicle body, and the desired compliance steer, specifically, the toe-in of the rear suspension and the toe-out of the front suspension on the turning outer wheel, can be sufficiently secured. In addition, there is a problem that excellent running stability cannot be obtained due to understeering due to such compliance steering.

An object of the present invention is to solve such a conventional problem, and it is of course possible to sufficiently reduce the muffled noise in the passenger compartment and to obtain an excellent riding comfort. It is an object of the present invention to provide a suspension member mounting structure capable of improving steering response and traveling stability.

[0009]

In order to achieve this object, the invention according to claim 1 is interposed between a vehicle body and a front wheel or rear wheel suspension, and the front side in the longitudinal direction of the vehicle body. And a mounting structure of a suspension member having a support portion on the rear side, in which the front-rear direction front side support portion of the vehicle body of the front wheel suspension member is supported via a watt link arranged in the vehicle body lateral direction, The suspension member mounting structure is characterized in that the front-rear direction rear side support portion of the vehicle body is supported via an elastic bush having low rigidity in the front-rear direction and up-down direction of the vehicle body and high rigidity in the lateral direction. It is provided.

The invention according to claim 2 is a vehicle body,
The present invention relates to a suspension member mounting structure that is interposed between a front wheel or rear wheel suspension and that has front and rear support portions in the vehicle front-rear direction.
The front-rear direction front side support portion of the vehicle body of the rear wheel suspension member is supported via an elastic bush having low rigidity in the front-rear direction and up-down direction of the vehicle body and high rigidity in the lateral direction, and the front-rear direction of the vehicle body. (EN) A suspension member mounting structure characterized in that a rear side support portion is supported via a watt link arranged in the lateral direction of a vehicle body.

[0011]

First, the operation of the suspension member mounting structure according to claim 1 will be described. When an input in the lateral direction of the vehicle body (input of lateral force) occurs, an optimum amount of toe-out is secured in the front suspension. That is, the front suspension member according to the present invention has a structure in which the front side in the front-rear direction of the vehicle body is supported by the vehicle body via the watt link arranged in the vehicle body lateral direction. The elastic center of the entire front suspension member with respect to the input is the center point of the watt link (center support point of the watt link with respect to the vehicle body). The center point of this watt link, that is, the elastic center, does not move laterally when a lateral force is input.

On the other hand, since an elastic bush is provided on the rear side of the front suspension member in the front-rear direction of the vehicle body, some movement is permitted. Therefore, when a lateral force is input, when viewed from above, the front suspension member rotates about the center point of the watt link, that is, the vehicle rear side about the front side of the vehicle. This causes the outer wheel on the front side of the turn toe out by the lateral force input during the turn, so the compliance steer of the vehicle changes in the understeer direction.

Here, on the rear side of the front suspension member in the vehicle front-rear direction corresponding to the outer peripheral portion of the rotational movement (circular movement) about the center point of the watt link, an elastic bush having a high rigidity in the lateral direction is interposed. Since it is supported by the vehicle body in an unpredictable manner, it is possible to prevent unnecessary excessive toe-out. Therefore, the optimum toe-out is always secured for the input of the lateral force.

On the other hand, when there is an input in the vertical direction of the vehicle body, the center point of the watt link can be easily moved in the vertical direction of the vehicle body with almost no displacement in the lateral direction and longitudinal direction of the vehicle body due to the rotation of each link arm. Be moved. Further, since the elastic bush has low rigidity in the vertical direction of the vehicle body, it can be easily moved in the vertical direction of the vehicle body. Therefore, since the front suspension member is entirely displaced in the vertical direction of the vehicle body, the suspension geometry does not change.

Further, when there is an input in the front-rear direction of the vehicle body, the center point of the watt link can be easily moved in the vehicle body front-rear direction without being displaced in the vehicle body lateral direction and vertical direction by the rotation of the link arms. Be moved. Further, since the elastic bush has low rigidity in the front-rear direction of the vehicle body, it can be easily moved in the front-rear direction of the vehicle body. Therefore, the front suspension member is entirely displaced in the front-rear direction of the vehicle body, so that the suspension geometry does not change.

Next, the operation of the suspension member mounting structure according to the second aspect will be described. When an input in the lateral direction of the vehicle body (input of lateral force) occurs, the rear suspension ensures an optimum amount of toe-in. That is, the rear suspension member according to the present invention has a structure in which the rear side of the vehicle body in the front-rear direction is supported by the vehicle body via the watt link arranged in the vehicle body lateral direction. The elastic center of the entire rear suspension member with respect to the input is the center point of the watt link. The center point of the watt link does not move laterally when lateral force is input.

On the other hand, since an elastic bush is arranged on the rear side of the rear suspension member in the vehicle front-rear direction,
Some movement is allowed. Therefore, when lateral force is input, the rear suspension member rotates in the front side of the vehicle around the center point of the watt link, that is, the rear side of the vehicle when viewed from above. This causes the outer wheel on the rear side of the turn toe in due to the lateral force input during the turn, so that the compliance steer of the vehicle changes in the understeer direction.

Here, on the front side in the vehicle front-rear direction of the rear suspension member, which corresponds to the outer peripheral portion of the rotational movement (circular movement) about the center point of the watt link, an elastic bush having a high lateral rigidity is provided. Since it is supported by the vehicle body, unnecessary excessive toe-in is prevented. Therefore, the optimum toe-in is always secured for the input of the lateral force.

On the other hand, when there is an input in the vertical direction of the vehicle body, the center point of the watt link is moved in the vertical direction of the vehicle body by the rotation of each link arm without being substantially displaced in the lateral direction of the vehicle body and the front-back direction. . Further, since the elastic bush has low rigidity in the vertical direction of the vehicle body, it can be easily moved in the vertical direction of the vehicle body. Therefore, since the rear suspension member is entirely displaced in the vehicle body vertical direction, the suspension geometry does not change.

Further, when there is an input in the front-rear direction of the vehicle body, the center point of the watt link is moved in the vehicle body front-rear direction by the rotation of each link arm without being substantially displaced in the vehicle body lateral direction and the vertical direction. It Further, since the elastic bush has low rigidity in the front-rear direction of the vehicle body, it can be easily moved in the front-rear direction of the vehicle body. Therefore, since the rear suspension member is entirely displaced in the vehicle body vertical direction, the suspension geometry does not change.

[0021]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, a position embodiment according to the present invention will be described with reference to the drawings. (Embodiment 1) FIG. 1 is a perspective view of a rear suspension according to Embodiment 1 of the present invention viewed from the front of a vehicle body, FIG. 2 is a plan view of the rear suspension shown in FIG. 1, and FIG. 3 is shown in FIG. FIG. 4 is a right side view of the rear suspension shown in FIG. 1. In addition, in FIG.
The right suspension is omitted.

The rear suspension 1 shown in FIGS. 1 to 4 is provided with a suspension member 11 which is formed in a substantially H shape in which the front side of the vehicle body is widened and is common to the left and right. The rear suspension 1 will be described with reference to the left suspension. The left side portion 11a of the rear suspension member 11 extending in the vehicle front-rear direction and the wheel hub 1 are described.
A lower arm 14, which constitutes a left suspension, a front upper arm 15, a toe control arm 16 and a rear upper arm 17 are connected to the part 03.

The wheel hub 13 and the strut tower 18 of the vehicle body are connected by struts 19. A soft mount 12a is provided at the vehicle body front side end of the left side portion 11a, and the vehicle body front side end of the left side portion 11a is formed by the soft mount 12a.
It is attached to the vehicle body via.

The soft mount 12a is particularly shown in FIG.
As shown in Fig. 2, a total of two curls 12a ₁ and 12a are placed in the front-rear direction of the vehicle body with a connecting hole formed in the center therebetween.
₃ is formed. Therefore, the soft mount 12a
The rigidity of the vehicle body is low in the front-rear direction and the vertical direction of the vehicle body, and is high in the lateral direction. Although a part of the right suspension is omitted in FIG. 1, the rear suspension member 11 is similar to the left suspension.
A lower arm, a front upper arm, a toe control arm, and a rear upper arm are connected between the right side portion 11b extending in the vehicle front-rear direction and a wheel hub (not shown). A strut is connected between the wheel hub and the strut tower of the vehicle body.

At the vehicle body front side end portion of the right side portion 11b,
The soft mount 12b is provided, and the right side portion 1
The front end of the vehicle body 1b is attached to the vehicle body via a soft mount 12b. In this soft mount 12b,
In particular, as shown in FIG. 2, a total of two curls 12b ₁ and 12b ₃ are formed in the front-rear direction of the vehicle body with a connecting hole formed in the center therebetween. Therefore, the rigidity of the soft mount 12b is low in the front-rear direction and the vertical direction of the vehicle body and high in the lateral direction.

In the first embodiment, the soft mounts 12a and 12b described above correspond to the elastic bushing described in claim 2. A tip of the left side portion 11a on the rear side of the vehicle body,
The front end of the right side portion 11b on the rear side of the vehicle body is a differential cross plate 5 to which the differential 50 is attached.
It is fixed at 1.

This differential cross plate 5
1 is fastened by a bolt 56a to a supporting member 50a formed on the rear side surface of the vehicle body of the differential 50.
Fixed. Further, as shown in FIG. 4 in particular, one end of an inverted U-shaped bracket 53 as viewed from the side of the vehicle body is fixed to the rear side of the differential 50 mounting surface of the differential cross plate 51 by bolts 56a. .

On the other hand, the other end of the bracket 53 is bolted to the center point O of the watt link 80 (specifically, the center point O of the link 84 described later) via the ball joint 57.
It is fastened and fixed by 6b. An insulator 55 is provided inside the bracket 53 above the vehicle body,
At the center point of the insulator 55, a bolt through hole through which a bolt 121a described later penetrates is opened. The bracket 53 is fixed to the bracket 121 attached to the vehicle body side via the insulator 55.

That is, the bolt through hole opened in the bracket 121 and the bolt through hole opened in the insulator 55 are communicated with each other, the bolt 121a is passed through these through holes, and the bolt 121a is tightened by the nut 121b. It is fixed by wearing it. Watlink 80 is particularly shown in FIG.
As shown in FIG. 3, it is composed of three links 84, 85 and 86 which are made of a rod-shaped member and are arranged in the lateral direction of the vehicle.

The watt link 80 is an upper link 85.
To one end of the connecting link 8 via a ball joint 58.
One end of 4 is swingably connected (this connecting part is
The lower end of the lower link 86 is swingably connected to the other end of the connecting link 84 via a ball joint 59 (this connecting portion is referred to as C).

The other end of the upper link 85 (the end facing B) is attached to a bracket 122 attached to the vehicle body.
The ball joint 87 is swingably connected (this connecting portion is referred to as A). On the other hand, the other end (end facing C) of the lower link 86 is swingably connected to the bracket 123 attached to the vehicle body via a ball joint 88 (this connecting part is referred to as D). There is.

The center point of the link 84 is swingably connected to the bracket 53 (this connecting portion is referred to as O) via a ball joint 57. The point O, which is the connecting portion, becomes the center point O of the watt link 80. Next, the rear suspension member 11 according to the first embodiment.
The specific operation of will be described with reference to the drawings.

In this embodiment, regarding the rear suspension member 11, there is a lateral input of the vehicle body, a vertical input of the vehicle body, and a longitudinal input of the vehicle body. , Will be described. First, regarding the rear suspension member 11, a case where there is an input in the lateral direction of the vehicle body will be described.

FIG. 5 is a schematic plan view showing the left rear wheel 130 and the rear suspension member 11, in which the lateral force F is not input to the rear suspension member 11.
The case where the lateral force F is input is shown. Note that FIG.
Then, the solid line shows the state in which the lateral force F is not input,
The broken line shows the state in which the lateral force F is input. As shown in FIG. 5, when the vehicle body turns right, the lateral force F is applied to the wheels 130.
Is entered. At this time, in the rear suspension member 11 according to the first embodiment, the elastic center of the entire rear suspension member 11 with respect to the input of the lateral force F is the watt link 80.
Is the center point O of the link 84 constituting the. Since this elastic center is always determined by the structure of the watt link 80, that is, the position of the center point O of the link 84, it does not move laterally when the lateral force F is input.

On the other hand, a soft mount 12a is provided at the front end of the left side portion 11a in the front-rear direction of the vehicle body.
At the front end of the vehicle body front-rear direction of b, the soft mount 12b
Since this is provided, this portion is slightly moved by the input of the lateral force F. Therefore, when the lateral force F is input due to this right turn, the rear suspension member 11
When viewed from above, it rotates clockwise around the center point O (in the direction of arrow X in the drawing), and the center of the front end in the vehicle front-rear direction of the left side portion 11a is the point P in FIG. To P ₁ point, the center of the front end in the vehicle front-rear direction of the right side portion 11 b moves from Q point to Q ₁ point. For this reason, at the time of this right turn, the rear suspension member 11 moves to the watt link 80.
The vehicle makes a right turn around the center point O of the vehicle, and as a result, the rear left wheel 130, which is a turning outer wheel, becomes toe-in, and the compliance steer of the vehicle body changes in the understeer direction.

Here, the vehicle front-rear direction front end of the left side portion 11a and the vehicle front-rear direction front end of the right wheel side portion 11b are outer circumferences of the rotational movement around the center point O of the watt link 80. The soft mounts 12a and 12b, which correspond to the portions, have high rigidity in the lateral direction, so that the points P and Q can be prevented from moving unnecessarily large. Therefore, it is possible to prevent an excessive toe-in from occurring unnecessarily, so that the optimum toe-in is always secured for the input of the lateral force F.

Next, regarding the rear suspension member 11, a case where there is an input in the vertical direction of the vehicle body will be described. FIG. 6 is a schematic view of the movement of the watt link 80 when the rear suspension member 11 is input in the upward direction of the vehicle body, as viewed from above the vehicle body, and FIG. 7 is the rear suspension member 11 in the upward direction of the vehicle body. Is a schematic view of the movement of the watt link 80 when there is an input from the rear of the vehicle body. FIG.
FIG. 9 is a schematic view of the movement of the watt link 80 seen from above the vehicle body when there is an input from below the vehicle body. FIG. 9 shows the rear suspension member 11 when there is an input from below the vehicle body, that is, the rear suspension. It is the schematic diagram which looked at the movement of the watt link 80 when 1 bounced from the back of the vehicle body.

7 and 9, the solid line shows the state in which the vertical force is not input, and the broken line shows the state in which the vertical force is input. First, the case where the rear suspension member 11 receives an input in the upward direction of the vehicle body will be described. As shown in FIGS. 6 and 7, when there is an upward input of the vehicle body, the point B is
It rotates counterclockwise about the point A (in the direction of the arrow Y ₁ shown in FIG. 7) and moves to the point B ₁ .

On the other hand, point C rotates clockwise around point D.
(Arrow Z shown in FIG. 7₁Direction) and rotate to C₁Move to a point
It Therefore, the O point shifts in the lateral direction and the front-back direction of the vehicle body.
Without going up, that is, O₁Move to a point
It At this time, the front end of the left side portion 11a in the front-rear direction of the vehicle body
The soft mount 12a installed on the₁
And 12a₃Is the front side of the right side 11b in the vehicle front-rear direction
The soft mount 12b arranged at the side end has a currant 1
2b₁And 12b ₃Is provided, so this soft
The rigidity of the mounts 12a and 12b is the upper and lower sides of the vehicle body.
It has low rigidity in the horizontal direction and high rigidity in the horizontal direction. Obey
If there is an upward input from the vehicle,
You can easily move upwards of the vehicle without moving
It

Next, with respect to the rear suspension member 11, a case where there is an upward input of the vehicle body, that is, a case where the rear suspension member 1 rebounds will be described. As shown in FIGS. 8 and 9, when there is a downward input of the vehicle body, the point B rotates clockwise about the point A (arrow Y ₂ direction shown in FIG. 9) and rotates B ₂ Move to a point.

On the other hand, point C rotates counterclockwise about point D (in the direction of arrow Z ₂ shown in FIG. 9) and moves to point C ₂ . Therefore, the point O moves to the downward direction of the vehicle body, that is, the O ₂ point without shifting in the lateral direction and the front-back direction of the vehicle body. Also at this time, similarly to the above, the soft mounts 12a and 12b have low rigidity in the vertical direction of the vehicle body and high rigidity in the lateral direction. Therefore, the soft mounts 12a and 12b can be easily moved downward in the vehicle body without moving in the lateral direction of the vehicle body. You can move. Therefore, both bound and rebound, the suspension geometry does not change, and steering response is secured.

Next, with respect to the rear suspension member 11, a case where there is an input in the front-back direction of the vehicle body will be described. FIG. 10 shows the rear suspension member 11,
FIG. 11 is a schematic view of the movement of the watt link 80 seen from above the vehicle body when there is an input in the front direction of the vehicle body. FIG. 11 shows the watt link 80 when there is an input in the front direction of the vehicle body with respect to the rear suspension member 11. 13 is a schematic view of the movement of the watt link 80 seen from the rear of the vehicle body. FIG. 12 is a schematic view of the movement of the watt link 80 when the rear suspension member 11 is input in the rearward direction of the vehicle seen from above the vehicle body. FIG. 4 is a schematic diagram of the rear suspension member 11 showing the movement of the watt link 80 when there is an input in the rear direction of the vehicle body as seen from the rear side of the vehicle body.

In FIGS. 11 and 13, the solid line is
It shows the state where no force is input in the front-back direction, and the broken line
It shows a state in which a force in the front-back direction is input. First, regarding the rear suspension member 11, a case where there is an input in the front direction of the vehicle body will be described. 10 and 11
As shown in, when there is input from the front of the vehicle,
Point B rotates around point A in the direction of arrow Y ₃ shown in FIGS. 10 and 11 and moves to point B ₃ .

On the other hand, point C rotates about point D in the direction of arrow Z ₃ shown in FIGS. 10 and 11 and moves to point C ₃ . Therefore, the point O moves to the front direction of the vehicle body, that is, to the O ₃ point without shifting in the lateral direction and the vertical direction of the vehicle body. At this time, the soft mounts 12a and 12b arranged at the front end in the vehicle front-rear direction of the left side portion 11a and the front end in the vehicle front-rear direction of the right side portion 11b have low rigidity in the vertical direction of the vehicle body and Since the direction is highly rigid, it is possible to easily move in the front direction of the vehicle body without moving in the lateral and vertical directions of the vehicle body.

Next, the rear suspension member 11 will be described.
Will be explained when there is a rearward input from the vehicle body.
It As shown in FIGS. 12 and 13,
When there is an input, point B is centered around point A
12 and arrow Y shown in FIG._FourRotate in the direction B _Fourpoint
Move to.

On the other hand, point C rotates about point D in the direction of arrow Z ₄ shown in FIGS. 12 and 13 and moves to point C ₄ . Therefore, the point O moves to the rearward direction of the vehicle body, that is, the point O ₄ without shifting in the lateral direction and the vertical direction of the vehicle body. At this time as well, since the soft mounts 12a and 12b have low rigidity in the vertical direction of the vehicle body and high rigidity in the lateral direction, the soft mounts 12a and 12b do not move in the lateral direction of the vehicle body,
Easy to move to the rear of the vehicle. Therefore, the suspension geometry does not change even with respect to an input from the front-rear direction of the vehicle body, and steering response is secured.

In the rear suspension 1 of this embodiment, the steering geometry does not change due to bound / rebound and front / rear inputs, and the steering response during turning is changed to an appropriate understeer direction to provide excellent steering response and running stability. The ride comfort can be improved by appropriately setting the spring constants of the soft mounts 12a and 12b while ensuring the stability.

In the first embodiment, the front end portion of the rear suspension member 11 in the vehicle front-rear direction is supported by the vehicle body via the soft mounts 12a and 12b, and the rear end portion of the rear suspension member 11 in the vehicle front-rear direction is Although the structure is such that the vehicle body is supported via the watt link 80, the present invention is not limited to this, and the rear suspension member 11 supports the front side in the front-rear direction of the vehicle body to the vehicle body via the soft mounts 12a and 12b. Any structure may be used as long as the rear side is supported via the watt link 80.

In the first embodiment, the soft mounts 12a and 1 used as the elastic bushes according to the second aspect of the invention.
By providing a total of two curls 12a ₁ and 12a ₃ in 2b in the longitudinal direction of the vehicle body with the center point sandwiched therebetween, the rigidity of the soft mounts 12a and 12b is low in the longitudinal direction and the vertical direction of the vehicle body, Although the lateral direction has high rigidity, the elastic bush according to the present invention is not limited to this, and may be composed of another elastic member other than the soft mount,
Also, the front and rear direction and the up and down direction of the vehicle body have low rigidity,
If the lateral direction has high rigidity, the number of currants formed may be determined as desired. The rigidity of the elastic bush is low in the front-rear direction and the up-down direction of the vehicle body instead of providing a currant in the front-rear direction of the vehicle body. Elastic bushes having other structures may be used as long as they have high rigidity.

In the first embodiment, the front side of the rear suspension member 11 in the front-rear direction of the vehicle body is supported by the vehicle body at a total of two places via the elastic bushes (soft mounts 12a and 12b), but the present invention is not limited to this. The number of supporting portions for the vehicle body on the front side in the vehicle front-rear direction of the rear suspension member 11 may be determined as desired. Further, in the first embodiment, the watt link 80 is installed on the differential 50 via the differential plate 51 and the bracket 53, but the mounting method of the watt link 80 is as follows.
It is not limited to this. (Second Embodiment) Next, a case where the suspension member according to the first embodiment is used on the front side, that is, a case where the suspension member is used as a front suspension member will be described.

Since the structure of the front suspension member is the same as that of the rear suspension 11 described in the first embodiment, the description thereof will be omitted. In the second embodiment, the vehicle front-rear direction front side of the rear suspension member 11 described in the first embodiment is disposed on the vehicle body front-rear direction rear side, and the rear suspension member 11 vehicle body front-rear direction rear side is disposed on the vehicle body front-rear direction front side. .

Then, points A and D explained in the first embodiment.
Similarly, the point is supported by the vehicle body, and the point O is the Wattlink 80.
It is the central point of. Next, a specific operation of this front suspension member will be described. Figure 14
Left front wheel 131 and front suspension member 132
FIG. 6 is a schematic plan view showing the case where the lateral force F is not input to the front suspension member 132, and the lateral force F.
When is input, is shown. In addition, in FIG. 14, the solid line indicates a state in which the lateral force F is not input, and the broken line indicates a state in which the lateral force F is input.

As shown in FIG. 14, when the vehicle body turns right, the lateral force F is input to the wheels 131. At this time, in the front suspension member 132 according to the second embodiment, the front suspension member 132 with respect to the input of the lateral force F.
The entire elastic center becomes the center point O of the link 84 that constitutes the watt link 80. This elastic center is always determined by the structure of the Watt link 80, ie the link 8
Since it is determined by the position of the center point O of 4, the lateral force F does not move in the lateral direction.

On the other hand, similarly to the first embodiment, the left side portion 11
At the rear end of the vehicle body in the front-rear direction, a soft mount 12a
However, since the soft mount 12b is disposed at the rear end of the right side portion 11b in the vehicle front-rear direction, the lateral force F
By input of, this part is moved to some extent. Therefore, when the lateral force F is input due to the right turn, the front suspension member 132 rotates counterclockwise (in the direction of arrow X _{1 in the} figure) about the center point O when viewed from above, and the left side The center of the vehicle front-rear direction rear side end portion of the portion 11a is from R point to R ₁ point in FIG. 14, and the vehicle body front-rear direction rear side end center of the right side portion 11b is from S point to S ₁ point. Moving. Therefore, during this right turn, the front suspension member 132 turns left about the center point O of the watt link 80, and the front left wheel 131, which is the turning outer wheel,
It becomes toe-out, and the compliance steering of the car body is
Change to understeer direction.

Here, the rear end of the left side 11a in the vehicle front-rear direction and the rear end of the right side 11b in the vehicle front-rear direction are rotated about the center point O of the watt link 80. The soft mounts 12a and 12b arranged in this portion have high rigidity in the lateral direction, so that the R point and the S point can be prevented from moving unnecessarily large. . Therefore, it is possible to prevent unnecessary excessive toe-out, so that the lateral force F
For the input of, the optimum toe-out is always secured.

On the other hand, the front suspension member 132
Regarding the above, when there is an input in the vertical direction of the vehicle body, as in the first embodiment, the points B and C move, and the point O moves in the vehicle vertical direction without shifting in the vehicle lateral direction and the longitudinal direction. To do. At this time, the soft mounts 12a and 12
Due to its rigidity, b can easily move in the vertical direction of the vehicle body without moving in the lateral direction of the vehicle body.

Therefore, both bound and rebound, the suspension geometry does not change, and steering response is secured. Next, regarding the front suspension member 123, when there is an input in the front-back direction of the vehicle body,
Similarly, point B and point C move, and point O moves in the vehicle body front-rear direction without shifting in the vehicle body lateral direction and vertical direction.

Therefore, the suspension geometry does not change even when an input is applied from the front-rear direction of the vehicle body, and steering response is secured. Front suspension 1 of this embodiment
In 32, the steering geometry does not change due to bound / rebound and front / rear input, and by changing the compliance steer during turning to an appropriate understeer direction, while maintaining excellent steering response and running stability, the soft mount 12a By appropriately setting the spring constants of 12 and 12b, the riding comfort can be improved.

In the second embodiment, the rear end of the front suspension member 132 in the vehicle front-rear direction is supported by the vehicle body via the soft mounts 12a and 12b, and the front end of the front suspension member 132 in the vehicle front-rear direction is Although the structure is such that it is supported on the vehicle body via the watt link 80, the structure is not limited to this, and the front suspension member 132 may include the soft mount 12 on the rear side of the vehicle body in the front-rear direction.
The structure may be such that it is supported on the vehicle body via a and 12b, and the front side in the front-rear direction of the vehicle body is supported via the watt link 80.

The suspension member mounting structure according to the present invention may be simultaneously applied to both the front suspension and the rear suspension.

[0061]

As described above, in the front suspension member according to claim 1, the front side of the vehicle body in the front-rear direction is supported via the watt link arranged in the vehicle body lateral direction, and When an input is made from the lateral direction of the vehicle body, the rear side of the vehicle body has a low rigidity in the front and rear direction and the vertical direction of the vehicle body, and the mounting structure is supported through an elastic bushing that has a high lateral direction. In addition, the front suspension member can perform an optimum rotational movement around the center point of the watt link, and always secures an optimum toe-out to the outer wheel after turning in response to the input of lateral force accompanying turning of the vehicle body. Can be made. Also, if there is an input in the vertical direction of the vehicle body or an input in the front-back direction,
The front suspension member easily moves in the vertical direction or the front-back direction of the vehicle body without being laterally displaced, and the suspension geometry does not change. As a result, it is possible to sufficiently reduce the muffled sound in the vehicle compartment, obtain an excellent riding comfort, and obtain excellent steering response and understeer characteristics.

In the rear suspension member according to a second aspect of the present invention, the rear side of the vehicle body in the front-rear direction is supported via a watt link arranged laterally of the vehicle body, and the front side of the vehicle body in the front-rear direction is the front-rear direction of the vehicle body. Since the mounting structure is supported through the elastic bushes that have low rigidity in the vertical and vertical directions and high rigidity in the lateral direction, the rear suspension member is supported when the vehicle body is input from the lateral direction. , It is possible to perform an optimum rotational movement around the center point of the watt link, and it is possible to always ensure an optimum toe-in for the outer wheel before turning with respect to the input of lateral force accompanying turning of the vehicle body. Further, when there is an input in the vertical direction of the vehicle body or an input in the longitudinal direction, the rear suspension member easily moves in the vehicle vertical direction or the longitudinal direction without shifting in the lateral direction, and the suspension geometry does not change. . As a result, it is possible to sufficiently reduce the muffled sound in the vehicle compartment, obtain an excellent riding comfort, and obtain excellent steering response and understeer characteristics.

[Brief description of drawings]

FIG. 1 is a perspective view of a rear suspension according to a first embodiment of the present invention as seen from the front of a vehicle body.

FIG. 2 is a plan view of the rear suspension shown in FIG.

FIG. 3 is a rear view of the rear suspension shown in FIG.

FIG. 4 is a right side view of the rear suspension shown in FIG.

FIG. 5 is a schematic plan view showing a left rear wheel and a rear suspension member according to the first embodiment of the present invention.

FIG. 6 is a schematic view of the movement of the watt link when the rear suspension member according to the first embodiment of the present invention receives an upward input from the vehicle body as seen from above the vehicle body.

FIG. 7 is a schematic diagram of the movement of the watt link when the rear suspension member according to the first embodiment of the present invention receives an upward input from the vehicle body as viewed from the rear of the vehicle body.

FIG. 8 is a schematic view of the movement of the watt link when the rear suspension member according to the first embodiment of the present invention receives a downward input from the vehicle body as viewed from above the vehicle body.

FIG. 9 is a schematic view of the movement of the watt link when the rear suspension member according to the first embodiment of the present invention receives a downward input from the vehicle body as viewed from the rear of the vehicle body.

FIG. 10 is a schematic diagram of the movement of the watt link when the rear suspension member according to the first embodiment of the present invention receives an input in the front direction of the vehicle body as viewed from above the vehicle body.

FIG. 11 is a schematic view of the movement of the watt link when the rear suspension member according to the first embodiment of the present invention receives an input in the front direction of the vehicle body as viewed from the rear side of the vehicle body.

FIG. 12 is a schematic diagram of the movement of the watt link when the rear suspension member according to the first embodiment of the present invention receives an input in the rear direction of the vehicle body, as viewed from above the vehicle body.

FIG. 13 is a schematic view of the movement of the watt link when the rear suspension member according to the first embodiment of the present invention receives a rearward input from the vehicle body as viewed from the rear side of the vehicle body.

FIG. 14 is a schematic plan view showing a left front wheel and a front suspension member according to a second embodiment of the present invention.

FIG. 15 is a perspective view of a conventional rear suspension as seen from the front of the vehicle body.

FIG. 16 is a model diagram showing a bounce vibration mode of a conventional rear suspension.

FIG. 17 is a model diagram showing a pitching vibration mode of a conventional rear suspension.

[Explanation of symbols]

1 Rear Suspension 11 Rear Suspension Member 12a Soft Mount 12b Soft Mount 12a ₁ Cursed 12a ₂ Cursed 12a ₃ Cursed 12b ₁ Cursed 12b ₂ Cursed 12b ₃ Cursed 50 Differential 51 Differential Cross Plate 53 Bracket 80 Watt Link

Claims (2)

[Claims] 1. A mounting structure of a suspension member, which is interposed between a vehicle body and a suspension for a front wheel or a rear wheel and has support portions on a front side and a rear side with respect to a longitudinal direction of the vehicle body. The front-rear direction front support portion of the vehicle body is supported via a watt link arranged in the vehicle body lateral direction, and the front-rear direction rear support portion of the vehicle body has low rigidity in the front-rear direction and the up-down direction. The suspension member mounting structure is characterized by being supported via an elastic bush having high rigidity in the lateral direction. 2. A suspension member mounting structure, which is interposed between a vehicle body and a suspension for a front wheel or a rear wheel and has support portions on a front side and a rear side in a front-rear direction of the vehicle, the suspension member for a rear wheel. The front-rear direction front support portion of the vehicle body is supported via an elastic bush having low rigidity in the front-rear direction and up-down direction of the vehicle body and high rigidity in the lateral direction, and the front-rear direction rear support portion of the vehicle body is supported. A suspension member mounting structure, characterized in that the suspension member is supported via a watt link arranged in the lateral direction of the vehicle body.