JPH04345510A - Suspension bush and suspension - Google Patents

Abstract

PURPOSE:To enable a tire to move in a toe-in direction when braked, and improve the stability of a vehicle only via a change in the characteristics of a suspension bush. CONSTITUTION:A suspension bush 1 is constituted of an inner cylinder 2, an outer cylinder 6 forming a part of a suspension ring 5 and bush rubber 4. Furthermore, a cylindrical collar 3 having higher rigidity than the rubber 4 is coupled to the outer surface of the inner cylinder 2 at a position offset from a pivotal point (e). When a braking force is applied, therefore, a suspension link 5 is displaced, and a pinching force acts on the suspension bush 1. Then, the section (b) in the illustration is subjected to less deformation, due to the existence of the collar section 3 and less flexibility than the section (c). As a result, the pivotal point (e) shifts in a vertical direction with a bush axial line A-A', thereby causing an actual change in the length of the suspension link 5.

Description

[Detailed description of the invention]

0001

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a suspension bush and an automobile suspension using the suspension bush.

0002

2. Description of the Related Art Parallel link suspensions have been known as suspensions for automobiles. Figure 28 is a simplified drawing of a parallel link type suspension, where 101 is a front parallel link, 102 is a front parallel link, and 102 is a front parallel link.
103 is an axle, 104 is a tire, and 105 is a vehicle body. In this parallel link suspension, the toe angle of the tire 104 is elastically defined by the suspension links. Furthermore, as shown in FIG. 29, there is a suspension bush in which the displacement of the bush with respect to external force is reduced in order to reduce the displacement of the tire due to external force. That is, the intermediate fitting 106 having the inclined wall 107 is fixed to the bushing inner cylinder 108 with the bushing rubber 109 preloaded.
A preload portion is provided in a part of the bushing rubber 109 (
For example, see Utility Model Application Publication No. 57-138708, etc.).

0003

[Problem to be solved by the invention] However, FIG.
In the conventional parallel link type suspension bush as shown in the figure, the braking force F is generally reduced as shown in the figure.
acts on the wheel center, a moment M is generated in the toe-out direction due to the braking force F, so the toe angle of the tire 104 tends to toe-out, as shown by the dotted line in the figure, and when braking is performed during a turn, , it may be difficult to ensure sufficient vehicle stability. Moreover, in order to solve the tendency of toe-out during braking, it is necessary to use a complicated suspension type.

Furthermore, in the suspension bush shown in FIG. 29, under the preload condition of the bush rubber 109,
Since it is necessary to fix by caulking or welding, it is inevitable that the number of man-hours and cost of manufacturing will increase. In addition, in order to restrict displacement, it is necessary to increase the spring constant of the preloaded part of the bushing rubber 109, which also increases the spring constant of the entire bush in the direction perpendicular to the axis, which reduces noise and vibration transmitted through the suspension. There was a problem that the interrupting performance deteriorated.

[0005] The present invention has been made in view of these conventional problems, and is a method for suppressing toe-out of a tire when a braking input is applied to the suspension and the wheel center is displaced to the rear of the vehicle. It is an object of the present invention to provide a bush that has the function of moving the link pivot center and has excellent noise and vibration isolation properties, and a suspension using the bush.

[0006]

[Means for Solving the Problems] Therefore, the present invention includes an outer cylinder forming a part of the link, an elastic body fitted to the outer cylinder, and an inner cylinder fitted to the elastic body. In the suspension bush, a hard part that is harder than the elastic body is provided between the inner cylinder and the outer cylinder. In addition, the material or filling state of the elastic body was varied depending on the position. Also, the outer cylinder was partially deformed toward the inner cylinder. Additionally, the amount of press-fitting of the elastic body into the outer cylinder was changed in the axial direction.

Furthermore, from among the above-mentioned suspension bushes, the selected suspension bush is installed at at least one of the connecting portion between the axle supporting the tire and the link, and the connecting portion between the link and the vehicle body, and prevents tire toe-out during braking. A suspension was constructed using the restraining direction.

[0008]

[Operation] When the flexible capacity or elasticity distribution of the elastic body of the suspension bushing changes and a prying input is applied to the bushing, the pivot center of the link moves in a direction perpendicular to the bushing axis.

[0009] As a result, the substantial length of the suspension link changes, so a suspension using these suspension bushes suppresses tire toe-out during braking.

0010

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be explained below based on the drawings. FIG. 1 is a diagram showing a first embodiment of a suspension bush of the present invention.

First, the configuration will be explained. Suspension bush 1 is attached to the axle that supports the vehicle body or tires.
An inner cylinder 2 fixed by an eye bolt (not shown), an outer cylinder 6 forming a part of the suspension link 5, and an inner cylinder 2
and a bushing rubber 4 interposed between an outer cylinder 6 and an outer cylinder 6. A cylindrical collar 3, which is more rigid than the bush rubber 4, is arranged on the outer periphery of the inner cylinder 2, and is offset toward the axis A' side from the suspension link pivot point e of the bush axis A-A', which is shown with direction. The bushing rubber 4 is fitted into the position, and in this state, the bushing rubber 4 is molded and hot-glued.

The elastic constant of the bushing rubber 4 is approximately the same in each part, but the flexibility capacity, which is the amount that allows compression, differs depending on the part due to the nonlinear elastic properties of the bushing rubber 4. In other words, when viewed in cross section,
As shown in Figure 2, parts a and b where the cylindrical collar 3 is present
The flexible capacitance is small in the section c and d, and the flexible capacitance is large in the other sections c and d.

FIG. 2 shows a parallel link type suspension which is one embodiment of the suspension of the present invention, and FIG. 3 shows a simplified state of attachment of a bush to a vehicle body and an axle in one embodiment.

In this embodiment, the vehicle body 7 and the axle 9 supporting the tires 8 are located at the positions shown in (1) to (4) in the figure.
A bushing 1 shown in FIG. 1 is attached to a bushing fixed to the bushing with its axis AA' directed in the direction shown in FIG. In addition, in FIG. 2, 10 is a strut, 11 is a radius rod, and 12 is a stabilizer.

Next, the operation will be explained with reference to FIGS. 4 to 7. As shown in FIG. 4, when the braking force F acts on the tire 8, the suspension link 5 is displaced as shown by the dotted line. Therefore, a prying displacement input is applied to the bush 1 attached to the positions shown in (1) to (4) in FIG. Therefore, for example, the bush 1 in the (1) and (2) positions is deformed as shown by the dotted line in FIG.

At this time, the displacement input of the prying is applied to the bush 1.
This will be handled by the compressive force of parts b and c.

However, since the cylindrical collar 3 is present in the part b, the flexible capacity, which is the capacity that allows compression, is smaller than that in the part c, so the amount of deformation of the part b is smaller than the amount of deformation of the part c.

Therefore, when a prying displacement input is applied to the bush 1 from the suspension link 5, the link 5 is moved not to the suspension link pivot center point e but to the axis A-
It rotates around point E which is offset from A' in the A' direction.

Therefore, the pivot center point e of the link 5 moves to e'. In other words, (1) and (2) in Figure 2
) The bush 1 installed at the position has the effect of pulling the link 5 in response to a displacement input from a prying operation.

Furthermore, as shown in FIG. 6, in the bush 1 installed at positions (3) and (4) in FIG.
Since the pivot point e of link 5 moves to point e', it has the effect of pushing out link 5.

Therefore, in the parallel link type suspension shown in FIG. 2 using the bush 1 shown in FIG. 1, when a braking force F is applied to the tire 8, as shown in FIG.
In position (2), the suspension pivot point f of the bushing is pulled toward the center of the vehicle and becomes point f', and in position (2), the suspension link pivot point g is pulled toward the outside of the vehicle relative to the axle 9, and point g' becomes the pivot center. becomes. In other words, since the front suspension link 5 becomes substantially shorter, the axle 9 in the front link is pulled toward the center of the vehicle body.

Furthermore, in position (3), the suspension link pivot point h is pushed out to the outside of the vehicle and becomes a point h'.
In position (4), the suspension link pivot point i is pushed inward of the vehicle relative to the axle 9 and becomes point i. In other words, the rear suspension link 5 becomes substantially longer, so the axle 9 is closer to the vehicle body. It will be pushed outward.

Therefore, even if the suspension does not originally have a special action to direct the tire in the toe-in direction during braking, by using the bush 1 according to the present invention, the axle can be adjusted in response to the braking force input. It is possible to suppress the tendency toward toe-in or toe-out in response to input during braking. Therefore, stability during braking during turning, for example, is more fully ensured.

FIG. 8 shows 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 is used as the bush at the positions (5) and (6) in the figure of the toe control link 13, with the axis A-A' in the direction shown in the figure. This is what I did. Note that 14 in the figure is an axle.

The operation will be explained with reference to FIG. When the tire 8 is displaced rearward due to the input of the braking force F, a prying displacement input is applied to the toe control link 13, and as shown in FIG.
By a mechanism similar to that explained by
The attachment point j on the side is j', and the attachment point k on the axle 14 side is k'
Move to. Therefore, since the rear portion of the axle 14 is displaced toward the outside of the vehicle body, the axle 14 is displaced in the toe-in direction in response to input braking force, and stability during braking can be more fully ensured.

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 integrally formed on the inner cylinder 15.

According to this embodiment, the same effects as in the first embodiment can be obtained, and moreover, the trouble of attaching 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 A direction to the A' direction of the axis A-A' of the bushing, and the cross section of the inner cylinder 17 is tapered to be larger on the A' side and smaller on the A side. It is something.

This embodiment also provides the same effects as those of the embodiments described above, and is also characterized in that the forces applied to the inner and outer cylinders change 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 bushing rubber 4, and then a link-shaped collar 18 having higher rigidity than the bushing rubber 4 is inserted into the groove.

Also in this embodiment, the flexible capacity of the bushing rubber 4 is reduced on the A' side of the axis A-A' due to the collar 18, 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 bushing rubber are changed in the axial direction. That is, axis A
A relatively soft bushing rubber 19 is used on the A side of -A', a relatively hard bushing rubber 20 is used on the A' side, and the center of elasticity of the bushing is moved to the A' side.

The operation will be explained with reference to FIG. When a displacement input from a prying enters this bush, the prying is mainly handled by the compressive force of parts b and c, but since the spring constant of part b is higher than that of part c, The amount of deformation of the portion is smaller than that of the portion c. As a result, the pivot center e of the link is displaced to e'.

According to this embodiment, the same effects as in the first embodiment can be obtained, and moreover, the pivot point can be displaced simply by changing the bushing 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
For the outer cylinder 6, normal cylindrical inner and outer cylinders are used, and the shape of the bushing rubber 21 is such that the A side 21a of the axis A-A' is narrower and the A side 21a of the axis A-A' is narrower.
' side 21b is formed thicker and press-fitted into the outer cylinder 6.

According to this embodiment, on the A' side where the press-fitting allowance is large, the spring constant becomes relatively high due to the nonlinearity of the elasticity of the bushing rubber 21, and on the A side where the press-fitting allowance is small, the spring constant becomes relatively high. Therefore, the same effect as in the fifth embodiment can be obtained.

FIGS. 16 and 17 show a seventh embodiment and an eighth embodiment of the suspension bush of the present invention.

In these embodiments, normal cylindrical tubes are used for the inner tube 2 and the outer tube 6, and in the seventh embodiment shown in FIG. In the illustrated eighth embodiment, a hollow 25 is provided in the bushing rubber 24, and the bushing rubbers 22, 24 are press-fitted into the outer cylinder 6.

Since the press-fitting allowance on the axis A-A' side is small and the pressure-receiving area is also small, the spring constant on the A side is relatively small compared to 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 the bushing rubber 4 is molded and press-fitted into the outer cylinder 6, a drawing process is performed on the A' side of the axis A-A' of the bushing outer cylinder 6 to form a recess 26, and the bushing on the A' side The rubber 4 is preloaded to increase the spring constant, and the flexible capacity of the bushing rubber 4 on the A' side is reduced by the recess 26.

In this embodiment as well, the spring constant of the bushing rubber is larger on the A' side, and the flexible capacity is also smaller due to the recess 26, so that the same effect as in the previous embodiment can be obtained.

20 and 21 show a tenth embodiment of the suspension bushing of the present invention. This example is
After molding and press-fitting the bushing rubber 4, drawing is performed on both the A side and the A' side of the axis A-A' at a position opposite to the mounting position of the suspension link 5 of the bushing outer cylinder 6 to form a recess 27. , 28 are provided to increase the spring constant of the portion, increase the flexibility constant of the bushing rubber 4, and reduce the flexibility capacity of the bushing rubber 4.

When this bush receives a prying displacement input as shown in FIG. 21, the prying is taken care of by the compression of portions b and c, so that the same effect as in the ninth embodiment can be obtained.

If the bush of this example is used in the parts (1) to (4) of the suspension shown in FIG. 2, it will have the effect of directing the tire in the toe-in direction during braking, as in the previous examples. This can improve the stability of the vehicle.

Moreover, according to this embodiment, since the suspension bushings are formed symmetrically with respect to the plane containing the suspension links, they can be used regardless of the direction of the prying input, and all suspension bushings of the suspension have the same shape. Bush can be used.

FIG. 22 shows an eleventh embodiment of the suspension bush of the present invention. In this embodiment, the effective length of the bushing rubber 4a on the side where the suspension link 5 is present is made shorter than the effective length of the bushing rubber 4b on the side where the suspension link 5 is not present.

As shown in FIG. 23, when a displacement input from a prying force is applied to this bush in the direction of the arrow in the figure, the prying force is taken care of by the compression of the c section of the bushing rubber 4a and the b section of the bushing rubber 4b. Since the effective length of the bushing rubber 4a is shorter than the effective length of the bushing rubber 4a, the spring constant of the section b is higher than that of the section c. Therefore, the amount of deformation of portion b is smaller than that of portion c. As a result, the pivot center of the link is displaced as in FIG. 14 of the fifth embodiment. Therefore, the same effects as in the fifth embodiment can be obtained.

FIG. 24 shows a twelfth embodiment of the suspension bush of the present invention. In this embodiment, a relatively soft rubber material is used for the bushing rubber 29 on the side where the suspension link 5 is present, and a relatively hard material rubber is used for the bushing rubber 30 on the side where the suspension link 5 is not present.

As shown in FIG. 25, when a displacement input from a prying force is applied to this bush in the direction of the arrow in the figure, the prying force is taken care of by the compression of the c section of the bushing rubber 29 and the b section of the bushing rubber 30. Therefore, the fifth embodiment,
The same effects as in the eleventh embodiment can be obtained.

26 and 27 show a thirteenth embodiment of the suspension bush of the present invention. This example is
To the bush rubber 4 on the side without the suspension link 5,
By inserting the insert 29 that is more rigid than the bushing rubber 4, the flexibility capacity of the bushing rubber on that side is reduced, and when a prying displacement input is input, the difference in the flexibility capacity of the bushing rubber 4 causes This utilizes the relative difference in spring constant.

This embodiment also provides the same effects as the twelfth embodiment.

In the suspension embodiments shown in FIGS. 2 and 8, for convenience of explanation, the case where the suspension bush of the first embodiment is used as the suspension bush has been described, but of course the suspension bush is not limited to this. Example 2 to Example 1 of suspension bush
Any of 3 may be used and the same effect can be obtained.

[0053]

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

Furthermore, since the characteristics of the bush itself are utilized, the characteristics can be changed without changing the geometry of the suspension, and furthermore, the bush itself has the advantage of being only minimally deformed.

[Brief explanation of drawings]

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

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

FIG. 3 is a plan view schematically showing how the suspension bush is attached to the vehicle body and axle.

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

FIG. 5 is a plan view illustrating a state when a prying 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;

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

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

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

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

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

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

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

[Fig. 14] The fifth suspension bush shown in Fig. 13.
FIG. 3 is a plan view illustrating the operation of the embodiment.

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

FIG. 16 is a perspective view showing a seventh embodiment of the suspension bushing of the present invention.

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

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

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

FIG. 20 is a perspective view showing a tenth embodiment of the suspension bushing of the present invention.

FIG. 21 is a plan view illustrating the operation of the tenth embodiment of the suspension bush.

FIG. 22 is a cross-sectional plan view showing an eleventh embodiment of the suspension bushing of the present invention.

FIG. 23 is a plan view illustrating the operation of the eleventh embodiment of the suspension bush.

FIG. 24 is a cross-sectional plan view showing a twelfth embodiment of the suspension bushing of the present invention.

FIG. 25 is a plan view illustrating the operation of the twelfth embodiment of the suspension bush.

FIG. 26 is a perspective view showing a thirteenth embodiment of the suspension bushing of the present invention.

FIG. 27 is a plan cross-sectional view of the 13th embodiment of the suspension bushing.

FIG. 28 is a simplified plan view of a conventional parallel link suspension.

FIG. 29 is a cross-sectional plan view showing a conventional suspension bush.

[Explanation 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 protrusion 18...Ring-shaped collar 23, 25...currant 26, 27, 28... recess

Claims (5)

[Claims] Claim 1: A suspension bush comprising an outer cylinder constituting a part of the link, an elastic body fitted to the outer cylinder, and an inner cylinder fitted to the elastic body, wherein the inner cylinder and the outer cylinder are connected to each other. A suspension bush characterized in that a hard part harder than the elastic body is provided between the parts to change the distribution of the flexible capacity of the elastic body inside the bush. 2. A suspension bush comprising an outer cylinder forming part of a link, an elastic body fitted to the outer cylinder, and an inner cylinder fitted to the elastic body, the material or filling of the elastic body being A suspension bush characterized by varying the state depending on the position and changing the distribution of elasticity inside the bush of an elastic body. 3. A suspension bush comprising an outer cylinder constituting a part of the link, an elastic body fitted to the outer cylinder, and an inner cylinder fitted to the elastic body, in which the outer cylinder is moved in the direction of the inner cylinder. A suspension bush characterized by partially deforming to change the distribution of flexible capacity inside the bush of an elastic body. 4. A suspension bush comprising an outer cylinder forming a part of the link, an elastic body fitted to the outer cylinder, and an inner cylinder fitted to the elastic body, in which the elastic body is connected to the outer cylinder. A suspension bushing characterized by changing the press-fitting allowance in the axial direction and changing the distribution of elasticity inside the elastic bushing. 5. In a suspension using a suspension bush comprising an outer cylinder constituting a part of the link, an elastic body fitted to the outer cylinder, and an inner cylinder fitted to the elastic body, the inner cylinder Suspension bushes that have a hard part harder than the elastic body between the outer cylinder and the elastic body, Suspension bushes that have different materials or filling conditions for the elastic body depending on the position, Suspension bushes that have the outer cylinder partially deformed towards the inner cylinder. , a suspension bush in which the amount of press-fitting of the elastic body into the outer cylinder is changed in the axial direction. A suspension characterized by being used at certain locations and in a direction that suppresses tire toe-out during braking.