JP2010159861A - Vibration absorbing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibration absorbing device having higher durability while achieving a greater spring ratio in the cross/longitudinal direction of a vehicle. <P>SOLUTION: A pair of side face portions 20 opposing each other in a cross direction Y of a shaft member 12 are formed in planar shape perpendicular to the cross direction Y, and a pair of sidewalls 24 of an outer cylinder 14 opposed to the first side face portions are formed in planar shape parallel to the first side face portions. A vibration absorbing base 16 connecting the shaft member 12 to the outer cylinder 14 consists of a pair of elastic connection portions 32 located across the shaft member 12 in the cross direction Y and connecting the first side face portions 20 to the first sidewalls 24. In a peripheral area excluding the first side face portions and the first sidewalls, a cavity portion 34 is provided passing between the axial member 12 and the outer cylinder 14 in an axial direction Z for establishing a non-connecting condition. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention has a cylindrical shape including a shaft member, an outer cylinder surrounding the shaft member, and a vibration-proof base made of a rubber-like elastic body that is interposed between the shaft member and the outer cylinder and couples the two cylinders. The present invention relates to a vibration isolator.

  Conventionally, as this type of vibration isolator, there is a body mount interposed between a body of an automobile and a suspension member (see, for example, Patent Document 1 below). In the body mount, the shaft member is attached to a member on the body side such as a frame with the axial direction being the vertical direction, and the outer cylinder is fixed to the member member of the suspension by press-fitting means or the like. Thereby, durability and riding comfort are improved by causing the vibration-proof base to undergo shear deformation with respect to vibration input in the vehicle vertical direction.

  In the body mount, in order to improve the ride comfort by reducing the spring constant in the vehicle front-rear direction, relative to the vehicle anti-vibration base in the vehicle front-rear direction in order to increase the spring constant in the vehicle left-right direction and improve steering stability. There is a case where an axial cavity portion called “Suraku” is provided at a position where the spring is formed to give the spring characteristics different directions (see, for example, Patent Document 2 below).

Japanese Utility Model Publication No. 7-41090 JP 2007-132386 A

  By providing an anti-vibration base as in the conventional case, the spring constant in the vehicle left-right direction can be made larger than the spring constant in the front-rear direction to improve steering stability and ride comfort. There is a need for further improvement in performance. For this reason, it is desired to further increase the spring ratio in the left-right direction and the front-rear direction (that is, the spring constant in the left-right direction / the spring constant in the front-rear direction).

  However, in the conventional vibration isolator, the inner peripheral surface of the shaft member and the inner peripheral surface of the outer cylinder facing the shaft member are both circular, and the anti-vibration base that connects between them is also arc-shaped. Since the vibration-proof substrate is subjected not only to shear deformation but also compressive deformation in response to vibration input in the direction, there is a limit to increasing the left / right / front / rear spring ratio. In addition, since combined deformation of shear deformation and compression deformation is generated with respect to vibration in the vehicle longitudinal direction, it is disadvantageous from the viewpoint of durability.

  The present invention has been made in view of these points, and can increase the ratio of the spring constant in two directions in the direction perpendicular to the axis, such as the vehicle lateral direction and the front-rear direction, and improve durability. An object of the present invention is to provide an anti-vibration device that can be used.

  An anti-vibration device according to the present invention includes a shaft member that is arranged with its axial direction facing the vehicle vertical direction, an outer cylinder that surrounds the shaft member in an axially parallel manner, and an interposition between the shaft member and the outer cylinder. And a vibration isolating base comprising a rubber-like elastic body that couples the two, wherein the shaft member is a pair of first side surfaces that are located across the shaft core in the first axis perpendicular direction. The portion is formed in a planar shape perpendicular to the first axis-perpendicular direction, and the outer cylinder includes a pair of first side walls located between the axis members in the first axis-perpendicular direction, and the shaft member An inner side surface of the first side wall facing the first side surface portion is formed in a planar shape parallel to the first side surface portion, and the anti-vibration base sandwiches the shaft member in the direction perpendicular to the first axis. A pair of elastic members that are located and connect the first side surface portion of the shaft member and the inner side surface of the first side wall of the outer cylinder. Consists of a connecting portion, and in a circumferential portion excluding the first side surface portion and the first side wall, a hollow portion penetrating in the axial direction is provided between the shaft member and the outer cylinder so as not to be connected. It is.

  With this configuration, the vibration isolating substrate is only compressed and deformed with respect to the vibration input in the direction perpendicular to the first axis, and the vibration input in the direction perpendicular to the second axis is perpendicular to this. In the anti-vibration base, only shear deformation occurs. Therefore, the spring ratio in the direction perpendicular to the first axis / the direction perpendicular to the second axis can be made larger than before. For example, the direction perpendicular to the first axis is the vehicle left-right direction and the second axis perpendicular direction is the vehicle front-rear direction. By setting the direction, the spring ratio in the left / right / front / rear direction can be increased to improve steering stability and ride comfort.

  In addition, since the vibration-proof base can be used only by shear deformation with respect to vibration input in the vehicle vertical direction and the second axis perpendicular direction (front-rear direction), durability in these directions can be improved. In addition, since the durability can be improved in this way, the vibration isolator can be reduced in size, and the weight can be reduced.

  In the vibration isolator, the outer cylinder may be made of resin. Thus, further weight reduction can be achieved by making an outer cylinder resin.

  In the vibration isolator, the outer cylinder includes a flange portion projecting outward in a direction perpendicular to the axis at one end portion in the axial direction, and the flange portion has an inner peripheral edge portion that is built up on the outer side in the axial direction. A stopper rubber portion made of a rubber-like elastic body may be provided on the outer side surface in the axial direction of the flange portion.

  When pressing the stopper rubber part to press-fit the vibration isolator into the holder, if the flange part is not built up and is bent outward with a constant thickness, the flange part is pressed. It is easy to add bending input that falls in the direction. On the other hand, by embedding the inner peripheral edge portion of the flange portion as described above, the pressing force is easily transmitted to the outer cylinder main body, the bending input is hardly applied to the flange portion, and the press-fitting property can be improved.

  In the above-described vibration isolator, the outer cylinder has an arcuate cross section that is located between the pair of first side walls and a second axis perpendicular direction perpendicular to the first axis orthogonal direction with the shaft member interposed therebetween. It consists of a pair of formed second side walls, the outer peripheral surface is formed in a circular shape so as to be press-fitted and held in a cylindrical holder, and the first side wall is a flat plate having the planar inner side surface The inner wall portion and the outer side surface of the inner wall portion are integrally projected from the outer side of the first axis in the direction perpendicular to the first axis to support the inner wall portion against the inner peripheral surface of the holder. It is good also as a structure which consists of the supporting wall part to which the outer edge of the said supporting wall part is located on the same periphery of the circular arc which prescribes | regulates the outer surface of the said 2nd side wall.

  By comprising in this way, in the resin-made outer cylinder, the 1st side wall with a planar inner surface becomes a thick part, improving the press fit property in the cylindrical holder by making the external shape circular. The occurrence of sink marks can be prevented.

  In the above-described vibration isolator, the outer cylinder includes a flange portion that protrudes outward in a direction perpendicular to the axis at one axial end portion, and the flange portion has a circular outer shape so that the flange on the first side wall The portion has an arcuate shape, the overhang width is set larger than the flange portion on the second side wall, and a stopper rubber portion made of a rubber-like elastic body is provided on the outer surface in the axial direction of the flange portion. The portion is assembled in a state of being compressed in the axial direction between the stopper member fixed to the shaft member, and the first stopper rubber portion provided in the flange portion on the first side wall, The flange portion at the second side wall is assembled in a state in which the stopper clearance is held between the stopper member by forming the axial height lower than the first stopper rubber portion. It may be composed of a second stopper rubber portion provided.

  Since the first stopper rubber portion is assembled in a compressed state with the stopper member on the shaft member side, it has a role of increasing the static spring constant in the vehicle vertical direction in the assembled state. On the other hand, the second stopper rubber portion has a role of restricting the displacement by contacting the stopper member when the vehicle is excessively displaced in the vertical direction of the vehicle. About each stopper rubber part which has such a different role, by providing the first stopper rubber part on the flange portion on the first side wall having a large overhanging width, the first stopper rubber is enlarged, and a static spring in the vertical direction is provided. The constant can be further increased, and the static ratio (ie, static spring constant / dynamic spring constant) with respect to the dynamic spring constant mainly determined by the shear deformation of the vibration-proof base can be increased.

  In the above-described vibration isolator, the outer cylinder may be configured such that the elastic coupling portion is pre-compressed by a tightening margin when the outer cylinder is press-fitted into a cylindrical holder. Thereby, although it is a resin-made outer cylinder, pre-compression can be provided to a vibration isolator base | substrate and durability can be improved.

  According to the present invention, it is possible to increase the ratio of the spring constants in the two directions in the direction perpendicular to the axis such as the vehicle left-right direction and the front-rear direction, improve durability, and contribute to weight reduction. .

The top view of the vibration isolator which concerns on 1st Embodiment. The bottom view of the vibration isolator of 1st Embodiment. The side view of the vibration isolator of 1st Embodiment. IV-IV sectional view taken on the line of FIG. The longitudinal cross-sectional view which shows the vehicle assembly state of the vibration isolator of 1st Embodiment. The top view of the vibration isolator which concerns on 2nd Embodiment. The bottom view of the vibration isolator of 2nd Embodiment. The side view of the vibration isolator of 2nd Embodiment. IX-IX sectional view taken on the line of FIG. The longitudinal cross-sectional view which shows the vehicle assembly state of the vibration isolator of 2nd Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[First Embodiment]
A vibration isolator 10 according to a first embodiment will be described with reference to FIGS. This anti-vibration device 10 is a body mount for supporting an underbody member such as a suspension of an automobile in a vibration-proof manner with respect to a body such as a frame, and more specifically, is assembled on the front side of a rear suspension of an automobile. Body mount.

  The vibration isolator 10 includes a shaft member 12 made of a rigid material such as metal, an outer cylinder 14 that surrounds the shaft member 12 in parallel and concentric with the shaft member 12, and a vulcanization adhesive unit interposed between the shaft member 12 and the outer cylinder 14. And an anti-vibration base 16 made of a rubber elastic body that couples the two together.

  The shaft member 12 is a member that is attached to the body 1 with its axial direction Z facing the vehicle vertical direction, and has a columnar shape having a hollow portion 18 that penetrates in the axial direction Z. As shown in FIGS. 1 and 2, the shaft member 12 includes a pair of first side surface portions 20 and 20 that are positioned with the axis O interposed therebetween in the vehicle left-right direction Y that is a first axis perpendicular direction, and a first shaft. It has a quadrangular prism shape including a pair of second side surface portions 22 and 22 positioned with the axis O in the vehicle longitudinal direction X, which is a second axis perpendicular direction perpendicular to the perpendicular direction.

  The first side surface portion 20 is formed in a planar shape perpendicular to the vehicle left-right direction Y. That is, the pair of first side surface portions 20, 20 facing the vehicle left-right direction Y extends along the vehicle front-rear direction X. The plane parts are parallel to each other. On the other hand, as shown in FIGS. 1 and 2, the second side surface portion 22 is formed in a curved surface with a horizontal cross section forming an arc shape as shown in FIGS. 1 and 2, and the arc of the outer cylinder 14 facing the vehicle longitudinal direction X. It is formed with the same radius of curvature as the inner peripheral surface. The width of the first side surface portion 20 is set to about twice the width of the second side surface portion 22, whereby the shaft member 12 has a substantially rectangular shape elongated in the vehicle longitudinal direction X in the horizontal cross section shown in FIG. There is no.

  As shown in FIGS. 1 and 2, the hollow portion 18 of the shaft member 12 is provided in a circular shape centering on the shaft core O, and in the front-rear direction in order to reduce the weight at a position opposite to the front-rear direction X. It is configured to have meat stealing portions 18A, 18A extending to X.

  The outer cylinder 14 is a member attached to a member member of the suspension connected to the suspension member, and is press-fitted and fitted into the cylindrical holder 2 of the member member. The outer cylinder 14 is formed of, for example, a synthetic resin such as a polyamide resin blended with glass fiber, and the vibration-proof base 16 (that is, the elastic connecting portion 32 described below) is preliminarily provided by tightening when being pressed into the holder 2. It is configured to be compressed. That is, the outer cylinder 14 is formed so that its outer diameter D1 (see FIG. 4) is slightly larger than the inner diameter D2 (see FIG. 5) of the holder 2, and is compressed by press-fitting into the holder 2, thereby being elastic. The connecting portion 32 is compressed in the vehicle left-right direction Y so that residual distortion due to shrinkage after vulcanization of the vibration-proof base 16 is removed.

  As shown in FIGS. 1 and 2, the outer cylinder 14 is positioned with the pair of first side walls 24 and 24 positioned with the shaft member 12 in the vehicle left-right direction Y and the shaft member 12 in the vehicle longitudinal direction X. A pair of second side walls 26, 26 is configured.

  In the first side wall 24, an inner side surface 24 </ b> A facing the first side surface part 20 of the shaft member 12 is formed in a planar shape parallel to the first side surface part 20. That is, the inner side surface 24A of the first side wall 24 is a plane portion perpendicular to the vehicle left-right direction Y so as to be opposed to the first side surface portion 20 of the shaft member 12 at a certain interval in the vehicle left-right direction Y. Is formed. On the other hand, the second side wall 26 is formed in a circular arc shape with the axis O of the shaft member 12 as the center.

  As described above, the outer cylinder 14 is formed in a non-circular shape having a straight portion (planar portion) on the first side wall 24 in the cross-sectional shape of the inner peripheral surface, whereas the cross-sectional shape of the outer peripheral surface is a cylindrical shape. It is formed in a circular shape so as to be press-fitted and held in the holder 2 (see FIG. 2). Since the outer peripheral surface has a circular cross section, the first side wall 24 includes a flat plate-like inner wall portion 28 having the planar inner side surface 24A, and an outer side surface of the inner wall portion 28 toward the vehicle laterally outward Yo side. And a support wall portion 30 that projects integrally with the inner wall portion 28 and abuts and supports the inner wall portion 28 against the inner peripheral surface of the holder 2. As shown in FIGS. 2 and 3, the support wall portion 30 includes a plurality (three in this case) of vertical walls 30 </ b> A extending in the axial direction Z, and a plurality (in the circumferential direction orthogonal to the vertical walls 30 </ b> A ( Here, four horizontal walls 30B are formed in a lattice shape. And each outer edge of these support wall parts 30 is the same circular arc which prescribes | regulates the outer surface 26A of the 2nd side wall 26 so that the cross-sectional shape of the outer peripheral surface of the outer cylinder 14 may become circular shape as mentioned above. It is provided so as to be located on the circumference P (see FIG. 2).

  In addition, in order to improve the support effect by the support wall part 30 while ensuring the moldability of the outer cylinder 14, the inner wall part 28 and the support wall part 30 which are each wall part which comprises the 1st side wall 24, and a 2nd side wall The thickness of 26 is set to be the same.

  As shown in FIG. 1, the anti-vibration base 16 includes the pair of first side surfaces 20 and 20 of the shaft member 12 and the inner surfaces 24A of the pair of first side walls 24 and 24 of the outer cylinder 14 opposed thereto. 24A is constituted by a pair of left and right elastic connecting portions 32 and 32 positioned with the shaft member 12 in between in the vehicle left-right direction Y so as to be connected to each other. Specifically, between the first side surface portion 20 and the first side wall 24 that are both planar and parallel to each other, an elastic connection portion 32 is interposed within the range within the planar shape. . In the circumferential direction portion excluding the first side surface portion 20 and the first side wall 24, a hollow portion 34 penetrating in the axial direction Z is provided between the shaft member 12 and the outer cylinder 14, and the shaft member 12 and the outer side wall A space between the cylinder 14 and the cylinder 14 is not connected.

  As shown in FIGS. 1 and 4, between the pair of second side walls 26, 26 and the second side surface portions 22, 22 of the shaft member 12 opposed thereto, the shaft member 12 in the vehicle longitudinal direction X is provided. In order to limit excessive displacement, stopper convex portions 36 and 38 made of a rubber elastic body are provided. Specifically, the second side surface portion 22 of the shaft member 12 is provided with a stopper convex portion 36 that continues from the elastic connection portion 32 via the rubber film 40, and the second side wall 26 of the outer cylinder 14 has an elastic connection portion. A stopper protrusion 38 is provided from 32 through a rubber film 42, and a constant stopper clearance 44 is secured between them in the circumferential direction.

  As shown in FIGS. 1 and 4, a flange portion 46 that projects outward in a direction perpendicular to the axis is provided at one end portion (upper end portion in this example) of the outer cylinder 14 in the axial direction Z over the entire circumference. The flange portion 46 has a circular outer shape. On the other hand, the side wall of the outer cylinder 14 provided with the flange portion 46 has a flat surface on the inner side surface 24A of the first side wall 24 as described above. As shown in FIG. 1, it has an arcuate shape in plan view, and the overhang width is larger than the flange portion 46 </ b> B on the second side wall 26.

  As shown in FIG. 4 in an enlarged manner, the flange portion 46 has an inner peripheral edge portion 46i that is built up on the axially outward Zo side (in this example, upward), and accordingly, the wall thickness at the inner peripheral edge portion 46i. T1 is formed larger than the wall thickness T2 at the outer peripheral edge portion 46o. The axially outer side surface 46C of the flange portion 46 is formed in an inclined surface shape that is inclined so as to gradually become lower from the built-up inner peripheral edge portion 46i toward the outer peripheral edge portion 46o.

  A stopper rubber portion 48 made of a rubber elastic body continuous from the vibration isolation base 16 is provided on the axially outer side surface 46 </ b> C of the flange portion 46. As shown in FIG. 1, the stopper rubber portion 48 includes a pair of left and right first stopper rubber portions 48A and 48A provided on the flange portions 46A and 46A of the pair of first side walls 24 and 24, respectively, and the pair of first rubber portions 48A and 48A. 2 comprises a pair of front and rear second stopper rubber portions 48B and 46B provided on the flange portions 46B and 46B of the side walls 26 and 26, respectively.

  As shown in FIG. 5, the first stopper rubber portion 48 </ b> A is a rubber portion that is assembled in a state compressed in the axial direction Z with the stopper member 3 on the body 1 side fixed to the shaft member 12. In the state, it has a role of increasing the static spring constant in the vehicle vertical direction Z. The second stopper rubber portion 48B is formed with a height in the axial direction Z lower than that of the first stopper rubber portion 46A. Thus, the second stopper rubber portion 48B is assembled in a state where the stopper clearance 50 is held between the second stopper rubber portion 48B and the stopper member 3. It is a rubber part, and has a role of regulating the displacement by contacting the stopper member 3 at the time of excessive displacement in the vehicle vertical direction Z. 48 A of 1st stopper rubber parts are provided in the flange part 46A in the 1st side wall 24 with a large overhang | projection width | variety, and, thereby, the width | variety in an axis perpendicular direction is set larger than the 2nd stopper rubber part 48B, and it enlarges. Has been.

  When manufacturing the vibration isolator 10, the extruded metal shaft member 12 and the injection-molded resin outer cylinder 14 are set in a vulcanization mold, and the inside of the vulcanization mold cavity. By injecting the rubber material into the vibration isolator base 16, the stopper convex portions 36 and 38 and the stopper rubber portion 48 are formed.

  As shown in FIG. 5, the vibration isolator 10 thus obtained fixes the outer cylinder 14 by being press-fitted into the holder 2 of the member member from above and is connected to the hollow portion 18 of the shaft member 12. The shaft member 12 is fixed to the body 1 and used by inserting and fastening the bolt 4.

  At that time, when the outer cylinder 14 is press-fitted, as shown in FIG. 4, the outer cylinder 14 is pressed by pressing the upper surface of the stopper rubber portion 48 provided on the upper surface of the flange portion 46 downward with the press-fitting jig 9. By being pushed into the holder 2, pre-compression is applied to the elastic connecting portion 32, and durability can be improved.

  When the outer cylinder 14 is press-fitted in this way, if the flange portion 46 is not built up and is bent outwardly with a constant thickness, the bending input is such that the flange portion bows downward. However, by building up the inner peripheral edge 46i of the flange portion 46 as in this embodiment (T1> T2), the pressing force is easily transmitted to the main body 14 and bending input is applied to the flange portion 46. It becomes difficult to improve the press fit.

  On the other hand, when the shaft member 12 is fixed to the body 1 with the connecting bolt 4, the first stopper rubber portion 48A provided on the upper surface of the flange portion 46 is pressed against the lower surface of the stopper member 3 of the body 1, The flange portion 46 and the stopper member 3 are assembled in a state compressed in the axial direction Z. Further, a flat plate-like second stopper member 5 is fastened and fixed to the lower end of the shaft member 12 by a connecting bolt 4, and the lower end of the outer cylinder 14 extends between the second stopper member 5 and the lower end of the holder 2. A ring-shaped rubber member 6 for limiting excessive displacement is clamped and fixed.

  In the vibration isolator 10 of the present embodiment configured as described above, the vibration isolating base 16 is deformed by pure compression with respect to vibration input in the vehicle left-right direction Y, and against vibration input in the vehicle front-rear direction X. As a result, pure shear deformation occurs in the vibration-proof substrate 16. Therefore, the spring ratio in the vehicle left / right direction / up / down direction can be set larger than before, and steering stability and ride comfort can be improved.

  In addition, since the vibration-proof base 16 can be used with pure shear deformation with respect to vibration input in the vehicle vertical direction Z and the front-rear direction X, durability in these directions can be improved. Therefore, in combination with the weight reduction of the outer cylinder 14 by the resin, further weight reduction can be achieved by directing the improvement in the durability to the size reduction of the vibration isolator 10.

  Further, in the vibration isolator 10, the spring constant in the vehicle vertical direction Z is a composite spring of the elastic connecting portion 32, the first stopper rubber portion 48A, and the rubber member 6, and the first stopper rubber portion 48A. When the rubber member 6 is compressed in the vertical direction Z in the assembled state, the static spring constant is increased. On the other hand, the dynamic spring constant is set small by using the pure shear deformation of the elastic connecting portion 32. In such a configuration, since the first stopper rubber portion 48A for increasing the static spring constant is provided in the flange portion 46A of the first side wall 24 having a large overhang width in the present embodiment, the size is increased. The static spring constant in the vertical direction Z can be further increased to increase the static ratio.

  Further, in the vibration isolator 10, since the first side wall 24 of the outer cylinder 14 is configured by the inner wall portion 28 and the support wall portion 30, the outer cylinder 14 has a circular outer shape. While improving the press fit into the holder 2, it is possible to prevent the first side wall 24 having the planar inner side surface 24 </ b> A from becoming a thick portion and causing sink marks or the like.

[Second Embodiment]
6 to 10 show a vibration isolator 10A according to the second embodiment. This vibration isolator 10A is a body mount that is assembled to the rear side of a rear suspension of an automobile, and has a point that an intermediate plate 52 is embedded in an elastic connecting portion 32 and a flange portion 46 provided at an end portion on the upside down side. This is different from the first embodiment.

  That is, in this example, as shown in FIGS. 6, 7, and 9, flat intermediate plates 52 are interposed at intermediate positions in the left-right direction Y of the pair of left and right elastic coupling portions 32, 32. Thereby, in this example, the spring constant in the vehicle left-right direction Y is higher than that in the first embodiment, and therefore the spring ratio in the left-right direction / up-down direction is set to be larger.

  Moreover, in this example, the flange part 46 is provided in the lower end of the axial direction Z of the outer cylinder 14, and the outer cylinder 14 is press-fitted in the holder 2 of a member member from below, and is fixed. Therefore, as shown in FIG. 10, a disc-shaped stopper member 7 for receiving the stopper rubber portion 48 in the vertical direction Z is sandwiched and fixed by the connecting bolt 4 at the lower end of the shaft member 12, and the stopper member 7 and the flange portion are fixed. 46, the first stopper rubber portion 48 </ b> A is assembled in a state compressed in the axial direction Z. A ring-shaped rubber member 8 that restricts the upward displacement of the outer cylinder 14 is disposed between the holder 2 of the member member and the body 1.

  In addition, since the shared load is larger on the rear side of the rear suspension than on the front side, the width of the first stopper rubber portion 48A in the direction perpendicular to the axis is set to be larger than the width in the first embodiment. It is planned.

  Other configurations are the same as those of the first embodiment, and the same operational effects are achieved.

  In the above-described embodiment, the second side wall 26 of the outer cylinder 14 is formed in an arc shape. However, the outer cylinder 14 may not be necessarily formed in an arc shape. For example, the outer cylinder 14 may be formed in a square cylinder shape. Further, the present invention can be applied to various vibration isolation devices other than the body mount. Although not enumerated one by one, various modifications can be made without departing from the spirit of the present invention.

DESCRIPTION OF SYMBOLS 10,10A ... Vibration isolator, 12 ... Shaft member, 14 ... Outer cylinder, 16 ... Anti-vibration base | substrate 20 ... 1st side part, 22 ... 2nd side part 24 ... 1st side wall, 24A ... Inner side surface of 1st side wall 26 ... 2nd side wall, 26A ... Outer surface 28 of 2nd side wall ... Inner side wall part, 30 ... Support wall part 32 ... Elastic connection part, 34 ... Hollow part 46 ... Flange part, 46A ... Flange part in 1st side wall, 46B ... Flange portion on the second side wall, 46C ... Axial outer surface, 46i ... Inner peripheral edge portion, 46o ... Outer peripheral edge portion 48 ... Stopper rubber portion, 48A ... First stopper rubber portion, 48B ... Second stopper rubber portion 50 ... stopper clearance O ... shaft core, P ... circular circumference Z that defines the outer surface of the second side wall ... axial direction (vehicle vertical direction)
Y: first axis perpendicular direction (vehicle left-right direction), X: second axis perpendicular direction (vehicle longitudinal direction)

Claims (7)

A shaft member disposed with its axial direction facing the vehicle vertical direction, an outer cylinder surrounding the shaft member in parallel with the shaft, and a rubber-like elasticity that is interposed between the shaft member and the outer cylinder to couple them together An anti-vibration device comprising an anti-vibration base comprising a body,
In the shaft member, a pair of first side surface portions positioned with the shaft core sandwiched in the first axis perpendicular direction is formed in a planar shape perpendicular to the first axis orthogonal direction,
The outer cylinder includes a pair of first side walls positioned with the shaft member interposed therebetween in a direction perpendicular to the first axis, and an inner side surface of the first side wall facing the first side surface portion of the shaft member is the first side wall. 1 is formed in a plane parallel to the side surface,
The vibration isolating base is positioned between the shaft member in the direction perpendicular to the first axis, and couples between the first side surface portion of the shaft member and the inner side surface of the first side wall of the outer cylinder. It is made of an elastic connecting portion, and a hollow portion penetrating in the axial direction is provided between the shaft member and the outer cylinder in a circumferential portion excluding the first side surface portion and the first side wall, and is in a non-connected state. An anti-vibration device characterized by that. The outer cylinder is made of resin;
The vibration isolator according to claim 1. The outer cylinder includes a flange portion projecting outward in a direction perpendicular to the axis at one axial end portion, and the flange portion is thicker than the outer peripheral edge portion with the inner peripheral edge portion being built up on the outer side in the axial direction. Formed, and provided with a stopper rubber portion made of a rubber-like elastic body on the outer surface in the axial direction of the flange portion,
The vibration isolator according to claim 2. The outer cylinder is positioned between the pair of first side walls and a second axis perpendicular direction perpendicular to the first axis perpendicular direction, with the shaft member interposed therebetween, and a pair of first tubes It consists of two side walls, the outer peripheral surface is formed in a circular cross section so as to be press-fitted and held in a cylindrical holder,
The first side wall protrudes integrally from the outer side surface of the inner side wall part toward the outer side in the first axis perpendicular direction with the flat inner side wall part having the planar inner side surface. A support wall portion that abuts and supports the inner wall portion against the inner peripheral surface of the holder, and the outer edge of the support wall portion is on the same circumference of an arc that defines the outer surface of the second side wall. The vibration isolator according to claim 2 or 3. The outer cylinder includes a flange portion projecting outward in a direction perpendicular to the axis at one axial end portion, and the flange portion has a circular outer shape so that the flange portion on the first side wall has a bow shape. The overhang width is set larger than the flange portion on the second side wall,
A stopper rubber portion made of a rubber-like elastic body is provided on the outer surface in the axial direction of the flange portion,
The stopper rubber portion is assembled in a state of being compressed in the axial direction between the stopper member fixed to the shaft member, and is provided at a flange portion on the first side wall. And an axial height lower than that of the first stopper rubber portion so that the stopper clearance is maintained between the stopper member and the flange portion on the second side wall. A second stopper rubber portion provided;
The vibration isolator according to claim 4. The outer cylinder is configured such that the elastic coupling part is pre-compressed by a tightening margin when press-fitted into a cylindrical holder,
The vibration isolator according to claim 4 or 5. The first axis perpendicular direction is the vehicle left-right direction, and the second axis perpendicular direction perpendicular to the first axis perpendicular direction is the vehicle front-rear direction.
The vibration isolator of any one of Claims 1-6.

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