JP2953099B2 - suspension - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a flexible capacitance distribution of an elastic body.
The present invention relates to a suspension for an automobile using a suspension bush in which the suspension is changed .

[0002]

2. Description of the Related Art Conventionally, a parallel link type suspension has been known as an automobile suspension.
2 0, which has drawn a simplified parallel link suspension, 101 front parallel link, 102
Is a rear parallel link, 103 is an axle, 104 is a tire, and 105 is a vehicle body. In this parallel link type suspension, the toe angle of the tire 104 is elastically defined by the suspension link. Further, as shown in FIG. 2 1, in order to reduce the displacement of the tire due to the external force, there is a small and suspension bushings displacement of the bushing with respect to the external force. That is, the intermediate fitting 106 having the inclined wall 107 is fixed with the bush rubber 109 pre-pressed to the bush inner cylinder 108,
A preload portion is provided in a part of the bush rubber 109,
(See, for example, Japanese Utility Model Laid-Open No. 57-138708).

[0003]

The object of the invention is to be Solved However, Figure 2 0
In a conventional parallel link type suspension bush as shown in FIG.
When the wheel acts on the wheel center, a moment M in the toe-out direction due to the braking force F is generated. Therefore, it may be difficult to sufficiently secure the stability of the vehicle. In addition, there is a problem that a complicated suspension model must be used in order to solve the tendency of the vehicle to toe out during braking.

[0004] Further, in the suspension bushing shown in FIG. 2 1, under preload conditions of the bushing rubber 109,
Since it is necessary to fix by caulking or welding, an increase in the number of manufacturing steps and costs is unavoidable. In order to regulate the displacement, it is necessary to increase the spring constant of the preload portion of the bush rubber 109. Therefore, the spring constant of the entire bush in the axial direction also increases, and the noise and vibration transmitted through the suspension are reduced. There was a problem that the blocking performance was reduced.

The present invention has been made in view of such a conventional problem, and suppresses toe-out of a tire when a brake input is applied to a suspension and a wheel center is displaced rearward of a vehicle. as such, it is an object to provide a has the effect of moving the link pivot center, and using high bush in the barrier properties of the noise and vibration suspension.

[0006]

SUMMARY OF THE INVENTION Therefore, the present invention provides a suspension bush in which the distribution of the flexible capacity of an elastic body interposed between an outer cylinder and an inner cylinder is changed.
Is supported by the axle and the vehicle body, and the suspension
Is used to pin the center of rotation with respect to the
Offset behind the bot center while
The suspension bush on the side of the
Offset the center of rotation with respect to the weight ahead of the pivot center.
I let it go .

[0007]

[Action] For suspension bushing that flexible capacity of <br/> distribution of the elastic body is changed, the pivot center of the link when the input of twisting the bushing acts in the vertical direction with respect to the bushing axis Moving.

[0008] Because of this, the substantial length of the suspension link changes, and the suspension using these suspension bushes suppresses the tire from toeing out during braking.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the drawings. FIG. 1 is a view showing a first embodiment of the suspension bush of the present invention.

First, the configuration will be described. The suspension bush 1 is attached to an axle supporting a vehicle body or tires.
Inner cylinder 2 fixed by eye bolts (not shown), outer cylinder 6 and a part of suspension link 5, inner cylinder 2
And a bush rubber 4 as an elastic body interposed between the outer cylinder 6. Then, exchange of the collar 3 outer circumference rigidity Bush rubber 4 high cylindrical inner cylinder 2, the bushing axis shown FIG. A-A 'and the suspension link 5
The bush rubber 4 is fitted and flow-bonded in this state at a position offset toward the axis A 'from the pivot center e to be inserted.

Although the elastic constant of the bush rubber 4 is substantially the same at each part, the elastic capacity, which is an amount that allows compression depending on the part, differs due to the non-linear elastic characteristic of the bush rubber 4. That is, when viewed in cross section, as shown in FIG. 1 , the flexible capacity is small at the portions a and b where the cylindrical collar 3 exists, and the flexible capacity is large at the other portions c and d.

FIG. 2 shows a parallel link type suspension as an embodiment of the suspension according to the present invention, and FIG. 3 shows a simplified state of mounting a bush to a vehicle body and an axle in this embodiment.

In this embodiment, an axle 9 for supporting a vehicle body 7 and a tire 8 at positions indicated by (1) to (4) in FIG.
The bush 1 installed on the axis A-A 'shown in FIG.
It is mounted with the direction facing as shown in FIG. In FIG. 2, reference numeral 10 denotes a strut, 11 denotes a radius rod, and 12 denotes a stabilizer.

Next, the operation will be described with reference to FIGS. As shown in FIG. 4, when the braking force F acts on the tire 8, the suspension link 5 is displaced as shown by a dotted line. For this reason, torsion displacement input is applied to the bush 1 attached at the positions indicated by (1) to (4) in FIG. Thus, for example, (1) position the bushing 1 of location is modified as shown by dotted lines in FIG.

At this time, the displacement input of the torsion is applied to the bush 1
And the compression force of the b and c portions. However, part b has a smaller flexible capacity that allows compression than part c due to the presence of the cylindrical collar 3,
The deformation of the part is smaller than the deformation of the part c. Therefore, the twist displacement input from the suspension link 5 is applied to the bush 1
When entering, link 5 is in suspension link pivot
In heart e rather than rotating about the axis A-A 'of A' direction point offset in E. For this reason, pivot in mind e of the link 5 is moved to the e '. That is, the bush 1 attached to the positions (1) and (2) in FIG.
It has an action of pulling in the link 5 in response to a twist input.

Further, in the bush 1 which is attached to (3) position location of Figure 2, as shown in FIG. 6, because the pivot center e of the link 5 to move to point e ', the action of pushing the link 5 have.

That is, the rear link 5 shown in FIG.
The suspension bush (3) on the vehicle body side
During pivoting, the center of rotation E for the pry input load when moving
Offset from the center e, while the axle side
Suspension bush (4) is the input load for twisting during braking
The center of rotation E with respect to the weight forward of the center of pivot e.
It has been fsetted. In addition, the front link 5 on the rear side
In, the suspension bush (1) on the vehicle body side is
Pivot the center of rotation E against the input load of twisting during braking
Offset forward from center e while axle side
Of the suspension bush (2) is a twist input during braking
The center of rotation E with respect to the load is located behind the center of pivot e.
It has been offset.

For this reason, the parallel link type suspension shown in FIG. 2 using the bush 1 shown in FIG. 1 has a braking force F acting on the tire 8 as shown in FIG.
(1) the position of the bush the suspension pivot point f is retracted point f in the vehicle central direction ', and the (2) point drawn into the vehicle in the side direction with respect to the suspension link pivot point g is axle 9 in position g' Is the pivot center. In other words, the front-side suspension link 5 is substantially shortened, so that the axle 9 is pulled toward the center of the vehicle body at the front-side link.

In the position (3), the suspension link pivot point h is pushed out of the vehicle to the point h '.
Next, the suspension link pivot point i is extruded point i 'to the vehicle outside side with respect to the axle 9 is at the position (4), the rear suspension links in other words 5
Is substantially longer, so that the axle 9 is pushed out of the vehicle body.

Therefore, even if the suspension does not originally have a special function of turning the tire in the toe-in direction at the time of braking, the use of the bush 1 according to the present invention allows the axle 9 to respond to the input of the braking force. Can be turned in the toe-in direction, or the tendency of toe-out with respect to the input during braking can be suppressed. Therefore, for example, stability during braking during turning is sufficiently ensured.

FIG. 8 shows a case of a wishbone type suspension as another embodiment of the suspension of the present invention. In this embodiment, the bush 1 of the first embodiment of the suspension bush described above uses the bush 1 at the position indicated by (5) and (6) in the drawing of the toe control link 13 with the axis AA 'shown in the illustrated direction. It was done.
In the figure, reference numeral 14 denotes an axle.

The operation will be described with reference to FIG. When the tire 8 is displaced rearward due to the input of the braking force F, a torsion control input 13 receives a torsion displacement input, and FIG.
By the same mechanism as described by
Side attachment point j is j 'and axle 14 side attachment point k is k'
Go to Therefore, since the rear portion of the axle 14 is displaced to the outside of the vehicle body, the axle 14 shifts in the toe-in direction in response to the input of the braking force, and the stability during braking can be more sufficiently secured.

FIG. 10 shows a second embodiment of the suspension bush of the present invention. In this embodiment, an annular projection 16 corresponding to the cylindrical collar 3 of the first embodiment (see FIG. 1) is formed integrally with an inner cylinder 15. According to this embodiment, the same effects as those of the first embodiment can be obtained, and the trouble of mounting the cylindrical collar 3 is eliminated.

FIG. 11 shows a third embodiment of the suspension bush of the present invention. In this embodiment, the thickness of the inner cylinder 17 is changed from the direction A to the axis A 'of the axis A-A' of the bush, and the cross section of the inner cylinder 17 is tapered to be large on the A 'side and small on the A side. Things. According to this embodiment, the same effects as those of the above embodiments can be obtained, and the force applied to the inner and outer cylinders changes smoothly.

FIG. 12 shows a fourth embodiment of the suspension bush of the present invention. In this embodiment, a link-shaped groove is formed at one end of the bush rubber 4 and a link-shaped collar 18 having higher rigidity than the bush rubber 4 is inserted into the groove. Also in the present embodiment, the collar 18 reduces the flexible capacity of the bush rubber 4 on the A 'side of the axis AA', so that the same effect as in the first embodiment can be obtained.

FIG. 13 shows a fifth embodiment of the suspension bush of the present invention. In this embodiment, the properties of the bush rubber are changed in the axial direction. That is, the axis A
A relatively soft bush rubber 19 on the A side of A ';
On the A 'side, a relatively hard bush rubber 20 is used,
In this case, the elastic center of the bush is moved to the A 'side.

The operation will be described with reference to FIG. When the displacement input of the twist is input to the bush, the twist is mainly taken by the compressive force of the portion b and the portion c. However, the spring constant of the portion b is smaller than the spring constant of the portion c. Since it is high, the deformation amount of the part b is smaller than that of the part c. As a result, the pivot center e of the link is displaced to e '. According to this embodiment, the same effect as that of the first embodiment can be obtained, and the pivot point can be displaced by merely changing the bush rubber.

FIG. 15 shows a sixth embodiment of the suspension bush of the present invention. In this embodiment, the inner cylinder 2 of the bush is used.
And, using a normal cylindrical inner and outer cylinder for the outer cylinder 6, the shape of the bush rubber 21 is thinner on the A side 21a of the axis A-A ',
The A 'side 21b is formed thick and is press-fitted into the outer cylinder 6. According to the present embodiment, on the A 'side where the press-in allowance is large, the spring constant becomes relatively high due to the non-linearity of elasticity of the bush rubber 21, and on the A side where the press-in allowance is small, the spring constant becomes relatively low. Therefore, the same effect as in the fifth embodiment can be obtained.

FIGS. 16 and 17 show a suspension bush according to a seventh embodiment and an eighth embodiment of the present invention. In these embodiments, ordinary cylindrical cylinders are used for the inner cylinder 2 and the outer cylinder 6, and in the seventh embodiment shown in FIG. In the eighth embodiment, a bush rubber 24 is provided with a grind 25, and the bush rubbers 22, 24 are pressed into the outer cylinder 6. Since the press-in allowance on the side of the axis A is small and the pressure receiving area is also small, the spring constant on the A side is relatively smaller than the spring constant on the A 'side. Therefore, the same effects as in the fifth embodiment can be obtained.

FIGS. 18 and 19 show a ninth embodiment of the suspension bush of the present invention. In this embodiment, after molding the bush rubber 4 and press-fitting it into the outer cylinder 6, a drawing process is performed on the A ′ side of the axis A-A ′ of the bush outer cylinder 6 to form a recess 26, and the bush on the A ′ side is formed. The spring constant is increased by placing the rubber 4 in a pre-compressed state, and the flexible capacity of the bush rubber 4 on the A 'side is reduced by the concave portion 26. Also according to the present embodiment, the spring constant of the bush rubber increases on the A 'side, and the flexible capacity is small due to the concave portion 26.
The same effects as in the above embodiment can be obtained.

In the embodiment of the suspension shown in FIGS. 2 and 8, the case where the suspension bush of the first embodiment is used as the suspension bush for convenience of explanation has been described. Example 2 to Example 9 of suspension bush
May be used, and the same effect is obtained.

[0032]

As described above, according to the present invention, the toe-out of the tire during braking can be suppressed, so that the stability of the vehicle can be greatly improved.

Further, since the characteristics of the bush alone are used, the characteristics can be changed without changing the geometry of the suspension, and the deformation of the bush itself is very small.

[Brief description of the drawings]

FIG. 1 is a plan sectional view showing a first embodiment of a suspension bush of the present invention.

FIG. 2 is a perspective view showing one embodiment of the suspension of the present invention.

FIG. 3 is a plan view schematically showing a mounting state of a suspension bush to a vehicle body and an axle.

FIG. 4 is a plan view illustrating that a tire moves rearward when a braking force is applied and a prying input is input to a suspension bush;

FIG. 5 is a plan view illustrating a state when a twist input is applied to the suspension bush of the first embodiment.

FIG. 6 is a plan view illustrating a state in which a prying input is applied to the suspension bush of the first embodiment.

FIG. 7 is a plan view illustrating that a tire is directed in a toe-in direction when a braking force is applied to the suspension according to the embodiment of the present invention shown in FIG. 2;

FIG. 8 is a perspective view showing another embodiment of the suspension of the present invention.

FIG. 9 is a plan view illustrating that a tire is directed in a toe-in direction when a braking force is applied to a suspension according to another embodiment of the present invention shown in FIG. 8;

FIG. 10 is a plan sectional view showing a second embodiment of the suspension bush of the present invention.

FIG. 11 is a plan sectional view showing a third embodiment of the suspension bush of the present invention.

FIG. 12 is a plan sectional view showing a fourth embodiment of the suspension bush of the present invention.

FIG. 13 is a plan sectional view showing a fifth embodiment of the suspension bush of the present invention.

14 is a fifth view of the suspension bush shown in FIG.
FIG. 4 is a plan view illustrating the operation of the embodiment.

FIG. 15 is a perspective view showing a sixth embodiment of the suspension bush of the present invention.

FIG. 16 is a perspective view showing a suspension bush according to a seventh embodiment of the present invention.

FIG. 17 is a perspective view showing an eighth embodiment of the suspension bush of the present invention.

FIG. 18 is a perspective view showing a ninth embodiment of the suspension bush of the present invention.

FIG. 19 is a plan sectional view showing a ninth embodiment of the suspension bush.

FIG. 20 shows a conventional parallel link suspension.
FIG .

FIG. 21 is a plan view showing a conventional suspension bush .
FIG .

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Suspension bush 2 ... Inner cylinder 3 ... Cylindrical collar 4 ... Bush rubber 5 ... Suspension link 6 ... Outer cylinder 9 ... Axle 13 ... Toe control link 14 ... Axle 16 ... Annular projection 18 ... Ring collar 23, 25 ... 26, 27, 28 ... recess

Continuation of the front page (56) References JP-A-55-119510 (JP, A) JP-A-58-71209 (JP, A) JP-A-63-82610 (JP, U) JP-A-63-1221837 (JP, A) , U) (58) Field surveyed (Int.Cl. ⁶ , DB name) B60G 7/02

Claims (1)

(57) [Claims] 1. A suspension bush in which a distribution of a flexible capacity of an elastic body interposed between an outer cylinder and an inner cylinder is changed.
Both ends of the link are supported by the axle and the vehicle body via the
Suspension bushing
Offset the center of rotation to the rear of the pivot center
The suspension bush on the axle side
Pivot center for rotation center for twist input load during motion
Suspend <br/> Nsho down, characterized in that is offset forward from.