JP2001280387A - Vibration damping bush - Google Patents

Abstract

PROBLEM TO BE SOLVED: To further efficiently exhibit the component force action to an input load to either one side of the shaft direction and the direction perpendicular to the axis in a vibration damping bush. SOLUTION: A first inner inclined plate 22 and a first outer inclined plate 36 are formed so as to slantingly project outward in the shaft direction from an inner shaft member 12 and an outer cylinder member 14, and first compression rubber 40 is interposed between these both inclined plates. A second inner inclined plate 24 and a second outer inclined plate 38 respectively slantingly projecting inward in the shaft direction toward the radial directional outside from the inner shaft member and the outer cylinder member, are formed on the radial directional opposite sides sandwiching the axis, and second compression rubber 42 is interposed between these both inclined plates. The above component force action is respectively exhibited between the first inner inclined plate and the first outer inclined plate and between the second inner inclined plate 24 and the second outer inclined plate 38.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an anti-vibration bush which is suitably used as a suspension bush or a suspension member mount of an automobile, and more particularly to a case where a load is input in any one of an axial direction and a direction perpendicular to the axial direction. In addition, the present invention relates to a vibration-isolating bush that can be advantageously used, for example, to suppress lateral force compliance steer of an automobile by generating a component force in either the bush axial direction or the direction perpendicular to the axis.

[0002]

BACKGROUND ART A member constituting a vibration transmission system having a structure in which an inner shaft metal fitting and an outer cylindrical metal fitting arranged radially apart from each other are connected by a main rubber elastic body interposed therebetween. As one type of cylindrical anti-vibration mount interposed therebetween, as disclosed in Japanese Patent Application Laid-Open No. 9-104212, an axially outer end of one of the inner shaft fittings in the axial direction is conventionally used. An inner inclined plate is provided that projects obliquely outward in one radial direction and that is inclined in one direction in the radial direction. The outer inclined plate protruding toward the inner inclined plate and spaced apart from and opposed to the inner inclined plate is formed, and compression rubber is interposed between the opposed surfaces of the inner inclined plate and the outer inclined plate. The anti-vibration bush It has been. In such a vibration-isolating bush, when a load is applied between the inner shaft and the outer tube in either the axial direction or the direction perpendicular to the axis, the compression rubber is compressed between the inner inclined plate and the outer inclined plate. Is applied to the inner shaft fitting and the outer cylinder fitting in either the axial direction or the direction perpendicular to the axis. Accordingly, for example, such an anti-vibration bush is provided at a portion where the trailing arm of the automobile is attached to the suspension member or the like, or at a portion where the suspension member is attached to the vehicle body side. By using it for mounting, etc., it is possible to adjust the change of the rear wheel toe angle etc. during turning of the vehicle to suppress lateral force compliance steer, achieve moderate understeer, or suppress roll displacement during turning of the vehicle. You can do it.

However, the present inventor has studied such an anti-vibration bush. In some cases, it is difficult to obtain a sufficient component force effect only by the component force action of the inner inclined plate and the outer inclined plate. Therefore, for example, by applying to a suspension member mount for an automobile, a lateral force generated at the time of cornering is exerted in the axial direction of the bush, and based on a component force action in the vehicle front-rear direction between the two inclined plates, a rear wheel is formed. In adjusting the toe angle, there is a problem that it is difficult to produce a required change in the toe angle or the like.

The anti-vibration bush exerts a component force on the other side with respect to an input load applied to either the axial direction or the direction perpendicular to the axis exerted on the inner shaft fitting and the outer cylindrical fitting. In Japanese Patent Application Laid-Open No. 8-177917, radially inclined projections are formed on the outer peripheral surface of the inner shaft fitting and the inner peripheral surface of the outer cylindrical fitting, and a main rubber elastic body is provided between the inclined surfaces of the inclined projections. An interposed structure has also been proposed, but in such a case where an inclined projection is formed between the facing surfaces of the inner shaft fitting and the outer cylinder fitting, the space for disposing the inclined projection is defined by the inner shaft fitting and the outer cylinder fitting. To be restricted
It was difficult to ensure a large opposing area of the inclined projections, and it was difficult to obtain a sufficient component action as in the case of the vibration isolating bush provided with the inner inclined plate and the outer inclined plate as described above.

[0005]

The present invention has been made in view of the above-mentioned circumstances, and an object of the present invention is to provide an input load to one of an axial direction and a direction perpendicular to the axial direction. An object of the present invention is to provide a vibration damping bush having a novel structure capable of more efficiently obtaining a component force on the other side.

[0006]

An embodiment of the present invention which has been made to solve such a problem will be described below. The components employed in each of the embodiments described below can be employed in any combination as possible. In addition, aspects or technical features of the present invention are not limited to those described below, but are described in the entire specification and drawings, or based on the invention ideas that can be understood by those skilled in the art from the descriptions. It should be understood that it is recognized on the basis of.

A first aspect of the present invention provides an inner shaft member,
In an anti-vibration bush in which an outer cylindrical member spaced apart on the outer peripheral side thereof is connected by a main rubber elastic body interposed therebetween, the vibration isolating bush is located on one end side in the axial direction of the inner shaft member. A first inner inclined plate which inclines outward in the direction and projects obliquely outward toward one side in the radial direction, and inclines inward in the axial direction and obliquely projects inward toward the opposite side in the radial direction The second inner inclined plate is fixedly mounted, and is located at one axial end of the outer cylindrical member, and is inclined outward in the axial direction and obliquely outward toward one side in the radial direction. The first outer inclined plate protruding, and the second outer inclined plate inclined inward in the axial direction and projecting obliquely inward toward the opposite side in the radial direction are fixed, while the first inner inclined plate is fixed. The plate and the first outer inclined plate are spaced apart on substantially parallel opposing surfaces,
The first compression rubber is interposed between the opposing surfaces, and the second inner inclined plate and the second outer inclined plate are spaced apart from each other on the substantially parallel opposing surfaces, and the second inner inclined plate and the second outer inclined plate are separated from each other by the second inclined surface. The feature is that compression rubber is interposed.

In the vibration isolating bush having the structure according to this aspect, the inner inclined plate and the outer inclined plate that exert a component force in the direction perpendicular to the axis are formed in the direction perpendicular to the axis with the inner shaft member interposed therebetween. They are provided on both sides, respectively, and the inner inclined plate and the outer inclined plate on both sides exert a component force action in the same direction.

Therefore, when an input load is applied to one of the axial direction and the direction perpendicular to the axis, the component force generated on the other side can be increased, and the input load is applied between the inclined plates on both sides in the direction perpendicular to the axis. Load sharing performance can be improved by being shared. In addition, since the inclined plate that generates the component force can be arranged almost symmetrically on both sides of the inner shaft member, the occurrence of irregular stress such as twisting force is reduced, and the operation is stable. And durability can be improved.

According to a second aspect of the present invention, in an anti-vibration bush having a structure according to the first aspect, an outer flange portion is integrally formed on one outer peripheral edge of an outer cylindrical member in an axial direction. It is characterized in that first and second outer inclined plates are formed by extending diagonally outward portions of the outer flange portion facing each other in one radial direction. In this aspect, the first and second outer inclined plates can be integrally formed with the outer cylinder member with a simple structure. In addition, since the outer flange portion is integrally formed with the outer cylinder member, a large drag force can be obtained on one side in the axial direction when the outer cylinder member is mounted by press-fitting and fixing the mounting member into the mounting hole.

According to a third aspect of the present invention, there is provided an anti-vibration bush having a structure according to the first or second aspect, wherein a separate plate fitting is welded to one axial end of the inner shaft member. Then, the first and second inner inclined plates are formed by extending obliquely outwardly the portions of the separate plate fittings that face each other in one radial direction. In such an embodiment, the first and second inner inclined plates can be formed with a simple structure with respect to the inner shaft member.

Further, a fourth aspect of the present invention is directed to a vibration isolating bush having a structure according to any one of the first to third aspects, wherein each of the first outer inclined plate and the second outer inclined plate is provided. A feature is that the protruding base end portion is set at substantially the same position in the axial direction. According to a fifth aspect of the present invention, in a vibration-isolating bush having a structure according to any one of the first to fourth aspects, the projecting base end of the first inner inclined plate is provided with a second inner inclined plate. It is characterized in that it is set axially outward in the inner shaft member rather than the protruding base end of the plate. In each of the fourth and fifth aspects, while ensuring sufficient axial lengths of the cylindrical portions of the inner shaft member and the outer cylindrical member, the axial length accompanying the formation of the inclined plate is sufficient. Can be suppressed, and the size can be reduced.

According to a sixth aspect of the present invention, there is provided an anti-vibration bush having a structure according to any one of the first to fifth aspects, wherein the first and second compression rubbers are formed by a rubber elastic body. It is characterized by being integrally formed. In this embodiment, since the first and second compression rubbers can be integrally formed at the same time as the main rubber elastic body, the manufacturability of the vibration isolating bush can be improved and the structure can be simplified. .

According to a seventh aspect of the present invention, there is provided an anti-vibration bush having a structure according to any of the first to sixth aspects, wherein the first and second inner inclined plates, the first and second inner inclined plates are provided. In the radial direction in which the two outer inclined plates protrude, a pair of bore holes extending in the axial direction between radially opposed surfaces of the inner shaft member and the outer cylindrical member are provided. In this aspect, the spring characteristics in the direction perpendicular to the axis where the inclined plate protrudes can be set softly by the sharpening portion, so that the spring ratio in the direction perpendicular to the axis and the direction perpendicular to the axis can be set large. The relative displacement in the direction perpendicular to the axis with respect to the input of the axial load between the member and the outer cylinder member can be more efficiently generated.

Further, an eighth aspect of the present invention is directed to the vibration-isolating bush having the structure according to the seventh aspect, wherein the through hole is formed to have a circumferential width gradually increasing from the outer cylinder member toward the inner shaft member. In addition, the inner shaft member and the outer cylinder member are brought closer to each other with the gap between the inner cylinder member and the outer cylinder member by arranging a stopper in the bore hole and supporting the outer cylinder member side. In this case, the inner peripheral side of the stopper abuts on the circumferential side wall of the hole prior to abutting on the inner shaft member side.

In the vibration-isolating bush having the structure according to this embodiment, a load in a direction perpendicular to the axis is applied,
When the inner shaft member and the outer cylinder member are displaced close to each other across the hole, the stopper comes into contact with the circumferential side wall of the hole and the elastic deformation of the circumferential side wall is limited. Accordingly, in the main rubber elastic body, the amount of change in the inner angle at both circumferential corners in the outer peripheral portion of the hole is limited. Thereby, the expansion / contraction or bending deformation range of both circumferential corners in the outer peripheral portion of the hole is reduced, and the occurrence of cracks and the like in the main rubber elastic body can be avoided.

Further, when a large load is input in the direction perpendicular to the axis, the circumferential side wall portion of the bore hole in which the stopper supported on the outer cylinder member is brought into contact first is formed of a rubber elastic body. Therefore, the rise of the spring constant becomes gentle even at the time of the contact of the stopper, and it is possible to avoid the occurrence of shocking vibration. In addition, when the input load further increases, the stopper finally comes into contact with the inner shaft member, and a direct compressive force is applied to the stopper between the inner shaft member and the outer cylinder member. Thus, the relative displacement between the inner shaft member and the outer cylinder member can be reliably and cushioned.

In this embodiment, the stopper may be in contact with the circumferential side wall of the hole from the beginning when the anti-vibration bush is mounted. Further, the material and hardness of the stopper can be appropriately set according to the required anti-vibration characteristics and the like. For example, by forming the stopper with a rubber elastic body, the rise of the load-deflection characteristic can be set more gently. In addition, the stopper made of rubber elastic body can be reinforced with a reinforcing material, or the stopper can be made of a hard material such as a synthetic resin material, so that the rise of the load-deflection characteristic can be increased, It becomes possible to limit the relative displacement between the member and the outer cylindrical member in a buffered and small manner. When the stopper is formed of a rubber elastic body, for example, the main rubber elastic body and the stopper may be integrally formed. When the stopper is formed of a hard material such as a synthetic resin material, a cushioning material layer is formed of a main rubber elastic body on the surface of the inner shaft member to which the stopper is brought into contact, so that a tapping sound or the like can be obtained. It is desirable to relax. On the other hand, when the stopper is formed of a soft material such as a rubber elastic body, the stopper may be directly in contact with an inner shaft member formed of a rigid material.

Further, it is not necessary that the through hole penetrates between the inner shaft member and the outer cylinder member in the axial direction, and the hole is opened only on one side in the axial direction or a bottomed hole opened on both sides in the axial direction. It may be shaped. Further, it is also possible to dispose a stopper only in one of the pair of holes provided on both sides of the inner shaft member. In addition,
The stopper does not need to be fixed to the outer cylinder member.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, in order to clarify the present invention more specifically, embodiments of the present invention will be described in detail with reference to the drawings.

First, FIGS. 1 to 3 show a suspension member mount 10 according to an embodiment of the present invention. In this suspension member mount 10, an inner cylindrical member 12 as an inner shaft member and an outer cylindrical member 14 as an outer cylindrical member are arranged radially apart from each other, and between the inner and outer cylindrical members 12, 14. It has a structure in which a main rubber elastic body 16 is interposed and the two metal fittings 12, 14 are elastically connected.

More specifically, the inner cylindrical fitting 12 has a small-diameter cylindrical shape, and has a substantially flat plate-like shape as a whole near one axial end (left side in FIG. 1). The plate 18 is fixed. The fixing plate 18 is formed of a rigid member such as a press fitting, and has a circular fitting hole 20 at a substantially central portion. And
The inner cylindrical fitting 12 is inserted into the fitting hole 20, and a peripheral portion of the fitting hole 20 is welded to the inner cylindrical fitting 12, so that the fixing plate 18 is positioned at one axial end of the inner cylindrical fitting 12 (see FIG. 1 (left end in FIG. 1).

Here, the fixing plate 18 has radially opposite sides extending across the fitting hole 20 and extends outward, and each of the fixing plates 18 has a substantially fan-shaped first shape that expands in the circumferential direction as the distance from the inner cylindrical fitting 12 increases. The inner inclined plate 22 and the second inner inclined plate 24 are integrally formed. In the present embodiment, both the first and second inner inclined plates 22 and 24 have a width dimension on the center side substantially equal to the outer diameter dimension of the inner cylinder fitting 12 and a width dimension on the outer periphery side of the outer cylinder. It is formed with a size substantially equal to the outer diameter of the metal fitting 14. Further, the protruding distal end surfaces (outer peripheral surfaces) of the first and second inner inclined plates 22 and 24 are each formed in an arc shape having the center axis of the inner cylindrical fitting 12 as a center.

The first inner inclined plate 22 and the second inner inclined plate 24 of the fixed plate 18 are axially oriented at substantially the same angle with respect to the center axis of the fitting hole 20 (the inner metal fitting 12). It is formed so as to be inclined and spread toward the opposite side. That is, the first inner inclined plate 22 is inclined obliquely outward in the axial direction, while the second inner inclined plate 24 is inclined obliquely inward in the axial direction. These first inner inclined plates 22
The second inner inclined plate 24 is formed so as to spread on a substantially parallel plane on both radial sides of the fitting hole 20. Further, the annular plate-like portion 26 around the fitting hole 20 in the fixing plate 18 is provided with the first inner inclined plate 2.
The second inner inclined plate 24 is bent along a bending line orthogonal to the facing direction of the second inner inclined plate 24, whereby the second inner inclined plate 24 is tilted more than the base end on the center side of the first inner inclined plate 22. The base end on the center side of the plate 24 is located axially outward of the inner cylinder fitting 12. Thereby, the axial dimension between the protruding tip portions of the first inner inclined plate 22 and the second inner inclined plate 24 is reduced.

On the other hand, the outer tube fitting 14 has a large diameter cylindrical shape, and is externally inserted into the inner tube fitting 12 so as to be coaxially spaced apart from the inner tube fitting 12 radially outward. It is arranged. Note that the axial length of the outer cylinder 14 is shorter than that of the inner cylinder 12, and the outer cylinder 14 is positioned at a substantially central portion in the axial direction of the inner cylinder 12. The openings on both sides in the axial direction of the outer tube fitting 14 are reduced in diameter by drawing or the like, so that the small-diameter portions 28 and 2 having small inner and outer diameters.
8 is set. As shown by the phantom line in FIG. 1, the large diameter portion 30 at the axial center portion is press-fitted and fixed to a mounting hole 32 formed in a vehicle suspension member 31 as a housing member. It has become.

Further, one of the outer tube fittings 14 in the axial direction (FIG. 1)
A flange-like portion 34 as an outer flange portion that protrudes radially outward and extends continuously in the circumferential direction is formed integrally with the peripheral edge of the opening (left in the middle). The flange-like portion 34 extends radially outward on both sides facing each other in one radial direction (vertical direction in FIG. 1), and has a substantially semicircular or fan-like shape. Outer inclined plate 3
6 and the second outer inclined plate 38 are integrally formed.

In this case, the first outer inclined plate 36 and the second outer inclined plate 38 are inclined and spread toward the opposite sides in the axial direction by substantially the same angle with respect to the center axis of the outer cylinder fitting 14. It is formed as follows. That is, the first outer inclined plate 36 is inclined obliquely outward in the axial direction, while the second outer inclined plate 38 is inclined obliquely inward in the axial direction. The first outer inclined plate 36 and the second outer inclined plate 38 are formed so as to spread on substantially parallel planes on both radial sides of the outer cylinder 14. In addition, the first outer inclined plate 36 and the second outer inclined plate 38
Are formed in a flat plate shape extending in the direction perpendicular to the axis, and the inner peripheral edges of the first outer inclined plate 36 and the second outer inclined plate 38 extend in the direction perpendicular to the axis. It is located on a plane. The first and second outer inclined plates 36 and 38 have a circumferential length greater than that of the first and second inner inclined plates 22 and 24. , 24 projecting from both sides in the circumferential direction.

As shown in FIG. 1, the first inner inclined plate 22 and the first outer inclined plate 36 project toward the same radial direction, and the second inner inclined plate 24
In a state where the and the second outer inclined plate 38 protrude toward the same radial direction, the inner cylinder fitting 12 and the outer cylinder fitting 14 are relatively positioned in the circumferential direction with respect to each other.
The first inner inclined plate 22 and the first outer inclined plate 36 are
The second inner inclined plate 24 and the second outer inclined plate 38 are opposed to each other while being substantially parallel to each other.
However, they are opposed to each other so as to be substantially parallel to each other.

Further, the main rubber elastic body 16 has a substantially thick cylindrical shape as a whole, and is interposed substantially entirely between the radially opposed surfaces of the inner cylindrical fitting 12 and the outer cylindrical fitting 14. ing. Then, the inner and outer peripheral surfaces of the main rubber elastic body 16 are vulcanized and bonded to the outer peripheral surface of the inner cylinder fitting 12 and the inner peripheral surface of the outer cylinder fitting 14, respectively.
Are formed as an integrally vulcanized molded product having the inner and outer cylindrical fittings 12 and 14.

The main rubber elastic body 16 is also provided between the first inner inclined plate 22 and the first outer inclined plate 36 and between the second inner inclined plate 24 and the second outer inclined plate 38. Each of the first compression rubbers 40 is extended between the facing surfaces of the first inner inclined plate 22 and the first outer inclined plate 36 in a filled state.
And the second inner inclined plate 24 and the second outer inclined plate 38
A second compression rubber 42 interposed in a filled state between the opposing surfaces of the main rubber elastic body 16 is formed integrally with the main rubber elastic body 16.

Further, the inner cylindrical fitting 12 is sandwiched between the main rubber elastic body 16 in the radial direction in which the first and second inner inclined plates 22 and 24 and the first and second outer inclined plates 36 and 38 project. On both sides, a pair of holes 44 are formed as a pair of holes extending in the axial direction between the inner and outer tube fittings 12 and 14. Furthermore, a pair of slits 46, 46 extending in the axial direction between the inner and outer cylinders 12, 14 are provided on both sides of the inner cylinder 12 in the radial direction orthogonal to the facing direction of the pair of bulges 44, 44. Is formed. Each of the pair of bulges 44, 44 and the slits 46, 46 is opened at the axial end face on the opposite side (right side in FIG. 1) from the first and second compression rubbers 40, 42, It has a length reaching the position close to the fixed plate 18, and has a constant cross-sectional shape and is linearly formed in the axial direction.

Further, each of the pair of bulges 44, 44 and the slits 46, 46 has a
A substantially sector shape in which the circumferential width gradually decreases as going radially inward from the outer tube fitting 14 toward the inner tube fitting 12, in other words, the circumferential width gradually increases as going radially outward. It has a cross-sectional shape. Each of the straightening portion 44 and the slit 46 has a radial dimension substantially extending from the outer circumferential surface of the inner cylindrical fitting 12 to the inner circumferential surface of the outer cylindrical fitting 14. Only the thin rubber layer formed on the surface of the inner and outer cylindrical fittings 12 and 14 at the portion where the 46 is formed is formed due to the mold opening / closing property at the time of molding the rubber elastic body 16.

That is, with respect to the main rubber elastic body 16,
By forming the pair of burrs 44, 44 and the slits 46, 46, the inner rubber elastic body 16 extends radially between the burrs 44 and the slit 46 which are circumferentially adjacent to each other. Four radial connecting portions 48 for connecting the metal fitting 12 and the outer cylindrical metal fitting 14 are formed. And, by these radial connecting portions 48, the forming portion 44 is formed.
Further, side wall portions on both sides in the circumferential direction of the slit 46 are formed.

Further, the pair of burrs 44, 44
Each of the stoppers 50 has a substantially trapezoidal cross section that protrudes radially inward from a substantially central portion in the circumferential direction of the outer peripheral side wall surface. Then, the inner cylinder fitting 12 and the outer cylinder fitting 14
When the stoppers 50 are mutually displaced in the approaching direction with the stopper 50 interposed therebetween, the stopper 50 is compressed and deformed between the inner cylinder fitting 12 side and the outer cylinder fitting 14 side. Is limited in a buffer-like manner. Here, the stopper 50 is
The main rubber elastic body 16 is formed integrally with the rubber elastic body 16 and is formed of a rubber elastic body.
It is smaller than 4. The protruding distal end surface of the stopper 50 has a substantially flat distal end surface that is wider in the circumferential direction than the inner peripheral end surface of the straightening portion 44, and the both corners in the circumferential direction are curved in a substantially arc shape. Beveled.
Then, in the radial direction where the pair of straightening portions 44, 44 face each other, the projecting distal end surface of the stopper 50 and
Is smaller than the distance between the opposing surfaces with the inner peripheral end face of the inner cylinder fitting 12 side: the distance between the opposing surfaces between the two corners in the circumferential direction of the stopper 50 and the circumferential side wall surface of the straightening portion 44 is smaller than a. Have been.

Accordingly, when the inner and outer cylindrical fittings 12 and 14 are relatively displaced in the approaching direction, the stopper 50 first has a circumferential end portion which serves as a radial side wall of the straightening portion 44 as a circumferential side wall portion. It is configured to be brought into contact with the connecting portion 48. Then, after the stopper 50 and the radial connecting portion 48 come into contact with each other and are elastically deformed, the stopper 50 comes into direct contact with the inner cylinder fitting 12 side,
The stopper 50 can be directly compressed and deformed between the inner and outer tube fittings 12 and 14. Here, when the stopper 50 abuts on the radial connecting portion 48, in addition to the fact that the radial connecting portion 48 is an elastic body, the acting direction of the contact force between the stopper 50 and the radial connecting portion 48 is pure. Since it is exerted in the shearing direction without being compressed, a large buffering action is exerted by the soft spring characteristic. On the other hand, when the stopper 50 comes into direct contact with the inner cylinder fitting 12 side,
In addition to the inner cylinder fitting 12 being substantially a rigid material,
Since the acting direction of the contact force to the stopper 50 is substantially pure compression, the buffering action by the hard spring characteristic and the regulating action of the large displacement allowance can be exhibited, and the nonlinear action as a whole is non-linear. The rising of the spring characteristic is exhibited. The corner from the circumferential side surface of the bulging portion 44 to the side wall of the stopper 50 is formed with an arc-shaped continuous surface, so that the concentration of stress due to the elastic deformation of the stopper 50 and the radial connecting portion 48 is reduced or reduced. Is to be avoided.

Moreover, the stopper 50 is connected to the radial connecting portion 48.
, The deformation of the radial connecting portion 48 in the direction of falling into the straightening portion 44 is restricted, and the deformation of the outer peripheral portion of the straightening portion 44 in the direction in which the inner angles of the circumferential side corners are reduced. As a result, when a load is input in a direction perpendicular to the axis where the fixing plate 18 protrudes, the range of expansion and contraction or bending deformation of both circumferential corners in the outer peripheral portion of the burring portion 44 can be reduced. . As a result, stress concentration in the radial connecting portion 48 is reduced or avoided, and the occurrence of cracks or the like in the main rubber elastic body 16 can be prevented. It is possible to obtain a stable under the.

The integral vulcanization molded product of the main rubber elastic body 16 as described above is subjected to a drawing process to the outer cylindrical metal fitting 14 as necessary to reduce the diameter, so that the main rubber elastic body 16 is formed. Precompression is applied to the body 16 to improve durability.

The suspension member mount 10 having such a structure is mounted on the mounting hole 32 formed in the suspension member 31 constituting a semi-trailing arm type suspension mechanism or the like, for example.
4, the inner cylinder fitting 12 is fixed to the body via a rod or the like, so that the left side is the outside of the vehicle and the right side is the inside of the vehicle in FIG. The vehicle is mounted so that the direction is the vehicle left-right direction and the vertical direction in the figure is the vehicle front-rear direction. The suspension member 31 is symmetrically mounted on each of the left and right ends of the vehicle. As a result, as described in Japanese Patent Application Laid-Open No. 9-104212, when a lateral force due to the cornering of the vehicle is input in the axial direction of the mount, the lateral force is protruded from the inner and outer cylindrical metal fittings 12 and 14 so as to protrude. The relative displacement in the radial direction between the inner and outer cylindrical fittings 12 and 14 is caused by a component force between the inclined plates 22 and 36 and the inclined plates 24 and 38 which are opposed to each other with the second compression rubbers 40 and 42 interposed therebetween. The force is exerted, so that the compliance steer (lateral force steer) and the vehicle body roll displacement during the turning of the vehicle can be reduced.

In this suspension member mount 10, the first and second components are located on both radial sides of the inner and outer cylindrical fittings 12, 14 and exert a component force against the axial load and the load perpendicular to the axial direction. Inner inclined plates 22, 24 and first and second outer inclined plates 36,
38 are opposed to each other, the inclined area for exerting the component force is set large, and the component force in the direction perpendicular to the axis when the axial load is input is efficiently generated. Thus, the required change in the toe angle or the like can be easily generated.

Further, the first inner inclined plate 22 and the first outer inclined plate 36 and the second inner inclined plate 24 and the second outer inclined plate 38, which exert a component force, respectively, are formed by the inner and outer cylindrical metal fittings 12. , 14 on both sides of the central axis, a component force with respect to the axial load and the load perpendicular to the shaft is generated in a well-balanced manner, and the inner and outer cylindrical fittings 12, 1 are formed.
The relative displacement of 4 is also produced in a well-balanced manner.
Thereby, the stability of the operation can be achieved, and there is no problem in that the durability is deteriorated due to the irregular deformation of the main rubber elastic body 16.

Furthermore, in the suspension member mount 10 of this embodiment, the base ends of the first and second outer inclined plates 36 and 38 are set at substantially the same position in the axial direction, The base end of the second inner inclined plate 24 extending obliquely inward in the axial direction is positioned radially outward from the base end of the first inner inclined plate 22 extending obliquely outward. Therefore, the first and second inner inclined plates 22 and 24 and the first and second outer inclined plates 36 and 38 can be reduced in size as a whole in the axial direction as a whole, and the arrangement space can be reduced. .

In the suspension member mount 10 according to the present embodiment, the spring characteristics in the vertical direction of the vehicle are set to be soft by the pair of slits 46, 46, so that a further improvement in riding comfort can be realized. It is.

The embodiment of the present invention has been described in detail above, but this is merely an example.
By the specific description in the above embodiment,
It is not to be construed as limiting.

For example, the inner shaft member and the outer cylinder member
In consideration of a static load or the like exerted under the mounted state, the eccentric position may be set in a direction perpendicular to the axis under a non-load input state before mounting.

Further, as shown in the above embodiment,
By using a pair of anti-vibration bushes provided with an inner inclined plate and an outer inclined plate on one side in the axial direction, the axial end faces of the respective anti-vibration bushes on which the inclined plate is not formed are overlapped and mounted. It is also possible to obtain an axial or perpendicular component based on a greater component action.

In addition, the present invention provides various types of suspension member mounts, such as a suspension member mount for suppressing roll displacement, a suspension member mount for realizing an appropriate understeer tendency, and a suspension bush for suppressing lateral force compliance steer. A compression rubber interposed between the inclined surfaces of the inner shaft member and the outer cylindrical member, such as a suspension member mount, a suspension bush, or a subframe mount interposed between an automobile subframe and a body, and the inclined plates thereof For various cylindrical anti-vibration mounts that make use of the component force action between the
Needless to say, it can be advantageously applied to various types of anti-vibration bushes used in automobiles and other various devices that do not have such a slope that exerts a component force. Needless to say, it is applicable.

Further, by sealing the hole and the slit with respect to the external space and sealing the incompressible fluid into the inside, the anti-vibration based on the flow action such as resonance action and viscous resistance of the sealed fluid. The present invention is also applicable to a fluid-filled vibration-proof bush so as to obtain an effect.

In addition, although not enumerated one by one, the present invention
Based on the knowledge of those skilled in the art, various changes, modifications, improvements, and the like can be made, and unless such embodiments depart from the spirit of the present invention.
Both are included in the scope of the present invention,
Needless to say.

[0049]

As is apparent from the above description, in the vibration isolating bush having the structure according to the present invention, the inner inclined plate and the outer inclined plate which exert a component force are provided on both sides of the center axis. By disposing the compression rubber so as to oppose each other, a component force in the axial direction or in the direction perpendicular to the axial direction can be obtained more efficiently.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a suspension member mount as one embodiment of the present invention, and is a sectional view taken along a line I in FIG.
It is a figure corresponding to -I cross section.

FIG. 2 is a sectional view taken along line II-II in FIG.

FIG. 3 is a left side view in FIG.

[Explanation of symbols]

 10 Suspension Member Mount 12 Inner Tube Fitting 14 Outer Tube Fitting 16 Body Rubber Elastic Body 22 First Inner Inclined Plate 24 Second Inner Inclined Plate 36 First Outer Inclined Plate 38 Second Outer Inclined Plate 40 First Compression Rubber 42 Second compression rubber

Claims (8)

[Claims] An anti-vibration bush in which an inner shaft member and an outer cylinder member spaced apart from the outer peripheral side thereof are connected by a main rubber elastic body interposed therebetween, wherein an axial direction of the inner shaft member is provided. A first inner inclined plate which is located on one end side and is inclined outward in the axial direction and projects obliquely outward toward one side in the radial direction, and a radially inclined inward in the axial direction and A second inner inclined plate projecting obliquely inward toward the opposite side is fixedly provided, and is located at one axial end of the outer tubular member, and is inclined outward in the axial direction. A first outer inclined plate projecting obliquely outward toward one side in the radial direction, and a second outer inclined plate inclined obliquely inward in the axial direction and projecting obliquely inward toward the opposite side in the radial direction. , Respectively, while the first inner inclined plate and the first outer inclined plate are substantially parallel to each other. And the first compression rubber is interposed between the opposing surfaces, and the second inner inclined plate and the second outer inclined plate are separated from each other on substantially parallel opposing surfaces. And a second compression rubber interposed between the opposing surfaces. 2. An outer flange portion is integrally formed with one outer peripheral edge portion of the outer cylindrical member in the axial direction, and portions of the outer flange portion opposed to each other in one radial direction are obliquely outwardly extended. The anti-vibration bush according to claim 1, wherein the first and second outer inclined plates are formed. 3. The anti-vibration bush according to claim 1, wherein the projecting base ends of the first outer inclined plate and the second outer inclined plate are set at substantially the same position in the axial direction. 4. A separate plate fitting is welded to one end of the inner shaft member in the axial direction, and portions of the separate plate fitting which are opposed to each other in one radial direction extend obliquely outward. 4. The anti-vibration bush according to claim 1, wherein the first and second inner inclined plates are formed. 5. The protruding base end of the first inner inclined plate is set to be more axially outward of the inner shaft member than the protruding base end of the second inner inclined plate. 4. The vibration isolating bush according to any one of 4. 6. An anti-vibration bush according to claim 1, wherein said first and second compression rubbers are integrally formed by said main rubber elastic body. 7. In a radial direction in which the first and second inner inclined plates and the first and second outer inclined plates protrude, respectively, the inner shaft member and the outer cylindrical member are radially opposed to each other. The anti-vibration bush according to any one of claims 1 to 6, further comprising a pair of bore holes extending in the axial direction between the surfaces. 8. The straight hole has a cross-sectional shape perpendicular to the axis, the circumferential width of which gradually decreases from the outer cylinder member toward the inner shaft member, and a stopper is provided in the straight hole. When the inner shaft member and the outer cylinder member are brought closer to each other across the hole, the inner peripheral side of the stopper contacts the inner shaft member. The anti-vibration bush according to claim 7, wherein the bushing comes into contact with a peripheral side wall portion of the hole prior to the contact.