JP2011117512A - Vibration control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To suppress breakage or settling of one elastic body receiving a support load. <P>SOLUTION: The vibration control device 1 includes: a pair of vibration control members 2A, 2B having outer cylinders 20A, 20B formed with flange parts 23A, 23B, inner cylinders 21A, 21B disposed in their inner sides, and elastic bodies 22A, 22B connecting them, and disposed such that axial end faces face each other; a bracket member 3 held between the flange parts in both sides; a pair of holding members 4A, 4B holding the pair of vibration control members from axial both sides; and a fastening member 5 inserted into inner sides of the inner cylinders and connecting the pair of holding members. By fastening the fastening members and pushing the pair the holding members into axial inner sides, ends of the inner cylinders are butted together, and the elastic bodies are pre-compressed via the pair of holding members. Of elastic bodies of the pair of vibration control members, a spring constant of the one elastic body 22A receiving the support load of a vibration generating body is larger than a spring constant of the other elastic body 22B. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a vibration isolator used as a cabin mount, an engine mount, or the like for agricultural machines or construction machines.

  As this type of vibration isolator, there is conventionally a sandwich type vibration isolator having a structure in which a pair of vibration isolator members are sandwiched by plate-shaped clamping members from both sides as shown in Patent Document 1 below, for example. . The vibration isolating member includes a substantially cylindrical outer cylinder having a flange portion formed at an end on the outer side in the axial direction, a substantially cylindrical inner cylinder disposed inside the outer cylinder, and an outer cylinder and an inner cylinder. It is composed of an elastic body such as rubber interposed therebetween. The pair of vibration isolating members are arranged so that the end portions in the axial direction face each other, and are clamped from both sides in the axial direction by the pair of clamping members. A bracket member is sandwiched between the flange portions of the pair of vibration isolating members. Moreover, a pair of clamping member is connected through the fastening member. The fastening member has a configuration in which nuts that are fastened to a pair of clamping members are screwed to both ends of a bolt inserted inside the inner cylinder.

  In the sandwich-type vibration isolator having the above-described configuration, the end portions of the inner cylinder are brought into contact with each other by tightening the fastening member, and the elastic body is pre-compressed via the pair of clamping members. Then, by connecting one of the pair of clamping members and the bracket member to a vibration generator such as an engine, and connecting the other to a vibration receiver such as a vehicle body, the vibration generator and the vibration receiver It is inserted between.

Japanese Patent Laid-Open No. 2005-121161

  However, in the above-described conventional vibration isolator, the elastic bodies of the pair of prevention members are made of the same elastic material and are formed in substantially the same shape, and the spring constants of both elastic bodies are substantially the same. For this reason, when the fastening member is tightened and both elastic bodies are pre-compressed, the pre-compression amount of both elastic bodies becomes equal. When the vibration isolator is interposed between the vibration generator and the vibration receiver, the support load of the vibration generator acts on one of the elastic bodies of the pair of prevention members to be compressed. Therefore, the pre-compression amount of one elastic body described above increases, and the pre-compression amount of the other elastic body decreases accordingly. As a result, when the vibration isolator is interposed between the vibration generating body and the vibration receiving body (support load load state), the precompression amount of one elastic body (the side receiving the support load) is the elasticity of the other. Become bigger than the body.

  As described above, since the precompression amount of one elastic body is larger than that of the other elastic body, when a load is repeatedly input due to the vibration of the vibration generating body, the displacement of one elastic body is greater than the displacement of the other elastic body. There is a problem that one of the elastic bodies is easily damaged. Moreover, since one elastic body is easy to sag, the problem of the contact with the other structure by the fall of a precompression force and an increase in support displacement tends to arise.

  In addition, since the amount of pre-compression of the other elastic body in the state of supporting load is small, the flange portion of the outer cylinder on the other elastic body side is attached to the bracket when bouncing (at the time of load input on the supporting load side) due to vibration of the vibration generating body. Easily separated from the member. For this reason, the spring constant of the vibration isolator is reduced, or when rebounding, the flange portion of the outer cylinder once separated from the bracket member collides with the bracket member to generate abnormal noise (sounding sound), or the flange of the outer cylinder The flange part and the bracket member are likely to be damaged due to the collision between the part and the bracket member.

  In the present invention, the above-described conventional problems are taken into consideration, and it is possible to make it difficult to break one elastic body that receives a supporting load, and to make the one elastic body difficult to sag, and to reduce the precompression force. , While preventing contact with other structures due to increased support displacement, and further preventing the flange portion of the outer cylinder from being separated from the bracket member, reducing the spring constant of the vibration isolator, An object of the present invention is to provide a vibration isolator capable of preventing abnormal noise (sounding sound) due to collision between the flange portion and the bracket member and damage to the flange portion and the bracket member.

  The vibration isolator according to the present invention includes an outer cylinder in which a flange portion protruding outward in the radial direction is formed, an inner cylinder disposed on the inner side of the outer cylinder, and an elasticity that connects the outer cylinder and the inner cylinder. Each of which has a body and is connected to one of a vibration isolator and a vibration receiver and a pair of anti-vibration members arranged with axial end faces facing each other, and the pair of anti-vibration members A bracket member sandwiched between the flange portions of the member, and a pair of sandwiching members coupled to any one of the vibration generating body and the vibration receiving body and sandwiching the pair of vibration isolating members from both sides in the axial direction A fastening member that is inserted inside the inner cylinder and connects the pair of sandwiching members, and by tightening the fastening member and pushing the pair of sandwiching members inward in the axial direction, The ends of the inner cylinder meet In the vibration isolator in which the elastic body is pre-compressed via the pair of clamping members, of the elastic bodies of the pair of prevention members, one of the elastic bodies receiving the support load of the vibration generating body The spring constant is larger than the spring constant of the other elastic body.

With such a feature, when the vibration isolator is set by tightening the fastening member, each elastic body of the pair of vibration isolator members is pre-compressed. At this time, the spring constant of one elastic body that receives the support load of the vibration generating body is larger than the spring constant of the other elastic body, and one elastic body is harder than the other elastic body. However, the amount of pre-compression is smaller than that of the other elastic body.
Next, when a vibration isolator is interposed between the vibration generator and the vibration receiver, the support load of the vibration generator is applied to one of the elastic bodies of the pair of prevention members. As a result, one elastic body is compressed by the support load, the pre-compression amount of one elastic body is increased, and the pre-compression amount of the other elastic body is decreased accordingly.
As described above, the amount of pre-compression of one elastic body increases when the supporting load is applied. However, since the amount of pre-compression of one elastic body when the vibration isolator is set is small as described above, the elasticity of one of the elastic bodies when the supporting load is applied. The pre-compression amount of the body is kept small, and conversely, the pre-compression amount of the other elastic body becomes large.

In the vibration isolator according to the present invention, it is preferable that the one elastic body is made of an elastic material having a larger elastic modulus than the other elastic body.
As a result, even if both elastic bodies have the same shape, the spring constant of one elastic body that receives the support load of the vibration generating body is larger than the spring constant of the other elastic body. When the vibration isolator is set, the pre-compression amount of one elastic body is smaller than that of the other elastic body.

By the way, normally, at the time of bouncing, the input load is likely to be larger and more frequent than at the time of rebounding, so that one elastic body that receives the load at the time of bouncing is more fatigued than the other elastic body.
Therefore, in the vibration isolator according to the present invention, it is preferable that a precompression amount of the one elastic body in a state where a support load of the vibration generating body is applied is equal to or less than a precompression amount of the other elastic body.
As a result, when the vibration isolator is interposed between the vibration generating body and the vibration receiving body and the support load of the vibration generating body is loaded, the pre-compression amount of one elastic body that receives the support load is kept small. Thus, one of the elastic bodies is more durable than the other elastic body.

  According to the vibration isolator of the present invention, the amount of pre-compression of one elastic body that receives a supporting load can be suppressed to be small, so that one elastic body can be made difficult to break, and the one elastic body It is possible to prevent the pre-compression force from decreasing and prevent contact with other structures due to increased support displacement. Further, since the pre-compression amount of the other elastic body is increased, the separation between the flange portion of the outer cylinder and the bracket member is prevented, the spring constant of the vibration isolator is lowered, and the difference due to the collision between the flange portion and the bracket member is prevented. Sound and damage to the flange portion and the bracket member can be prevented.

It is sectional drawing of the vibration isolator before the set for demonstrating embodiment of this invention. It is sectional drawing of the vibration isolator of the set state for demonstrating embodiment of this invention. It is sectional drawing of the vibration isolator of the support load load state for demonstrating embodiment of this invention. It is sectional drawing of the vibration isolator for demonstrating the modification of this invention. It is sectional drawing of the vibration isolator for demonstrating the modification of this invention. It is sectional drawing of the vibration isolator for demonstrating the modification of this invention. It is sectional drawing of the vibration isolator for demonstrating the modification of this invention.

DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of a vibration isolator according to the present invention will be described with reference to the drawings.
In addition, the code | symbol O shown in FIG. 1 has shown the center axis | shaft of the vibration isolator 1, and let the direction along the center axis | shaft O be an "axial direction", and let the direction orthogonal to the center axis | shaft O be a "radial direction." A direction around the central axis O is defined as a “circumferential direction”. Further, the opposite surface side facing the other vibration isolating member 2B (2A) as viewed from one vibration isolating member 2A (2B) is defined as the axially inner side, and the opposite side is defined as the axially outer side.

  As shown in FIG. 1, the vibration isolator 1 is applied as an engine mount, for example, and is input from an engine (not shown) mounted on a construction machine or the like (corresponding to a vibration generator of the present invention). The vibration is attenuated and absorbed to suppress transmission of vibrations to a body (not shown) (corresponding to the vibration receiver of the present invention).

  As a schematic configuration of the vibration isolator 1, a pair of vibration isolating members 2A and 2B and a pair of vibration isolating members 2A and 2B arranged coaxially with the end surfaces on the inner sides in the axial direction facing each other are illustrated. Fastening that connects the bracket member 3 interposed between the machine body, the pair of clamping members 4A and 4B that clamp the pair of vibration isolating members 2A and 2B from both sides in the axial direction, and the pair of clamping members 4A and 4B. And a member 5. The anti-vibration members 2A and 2B having the above-described configuration are configured such that a pair of anti-vibration members 2A and 2B having the same shape are arranged symmetrically with the vertical plane of the central axis O as a symmetry plane. The members 2A and 2B are members having the same configuration, and have outer cylinders 20A and 20B, inner cylinders 21A and 21B, and elastic bodies 22A and 22B having the same shape.

  The vibration isolating member 2A (2B) is a substantially cylindrical outer cylinder 20A (20B) and a substantially cylindrical cylinder having a smaller diameter than the outer cylinder 20A (20B) and disposed inside the outer cylinder 20A (20B) with a space therebetween. The inner cylinder 21A (21B) having a shape, and an elastic body 22A (22B) interposed between the outer cylinder 20A (20B) and the inner cylinder 21A (21B) are configured.

  A flange portion 23 </ b> A (23 </ b> B) protruding outward in the radial direction is provided at an end portion on the outer side in the axial direction of the outer cylinder 20 </ b> A (20 </ b> B). The flange portion 23A (23B) is an annular portion extending over the entire circumference of the outer cylinder 20A (20B).

  The inner cylinder 21A (21B) is arranged coaxially with the outer cylinder 20A (20B) with the central axis O as a common axis, and has a longer overall length than the outer cylinder 20A (20B), and the outer cylinder 20A (20B). It is arranged in a state of protruding outward in the axial direction. In the state where no external force is applied, the end surface on the inner side in the axial direction of the inner cylinder 21A (21B) is located on the outer side in the axial direction with respect to the end surface on the inner side in the axial direction of the outer cylinder 20A (20B). , 21B end surfaces on the inner side in the axial direction are spaced apart from each other.

  The elastic body 22A (22B) is a rubber body that elastically connects the outer cylinder 20A (20B) and the inner cylinder 21A (21B), and the inner peripheral surface 20a of the outer cylinder 20A (20B) and the flange portion 23A (23B). ) Is vulcanized and bonded to the outer surface 23a on the axially outer side, and is vulcanized and bonded to the outer peripheral surface 21a of the inner cylinder 21A (21B). The elastic body 22A (22B) has a tapered shape that is gradually reduced in diameter toward the outer side in the axial direction, and the end surface 22a on the inner side in the axial direction of the elastic body 22A (22B) has a concave shape. It has become.

  In addition, a stopper portion 24A (24B) protruding outward in the axial direction is provided on the outer peripheral portion on the inner side in the axial direction of the elastic body 22A (22B). This stopper part 24A (24B) is a convex part which has the contact surface 24a which opposes the inner surface 4a of the axial direction inner side of clamping member 4A (4B) at intervals, and is formed in annular | circular shape over the perimeter. ing. As the elastic body 22A (22B), an elastic body such as a synthetic resin can be used in addition to rubber.

  Of the pair of elastic bodies 22A and 22B, one elastic body 22A that receives a supporting load of an engine (not shown) is made of an elastic material having a larger elastic modulus than the other elastic body 22B. The spring constant is larger than the spring constant of the other elastic body 22B. More specifically, as shown in FIG. 2, in a state where an unillustrated engine supporting load is applied, the precompression amount of both elastic bodies 22A and 22B is 0 or more, respectively, and one elastic body The elastic moduli of the elastic materials of both elastic bodies 22A and 22B are set so that the precompression amount of 22A is equal to or less than the precompression amount of the other elastic body 22B. Preferably, as shown in FIG. 3, both elastic bodies 22A and 22B are set so that the pre-compression amount of one elastic body 22A and the pre-compression amount of the other elastic body 22B are equal in the state of supporting load. The elastic modulus of each elastic material is set.

  The above-described elastic body 21A that receives the support load of the engine (not shown) means that when the engine (not shown) is mounted on the vibration isolator 1, the compression force is applied via the clamping member 4A by the engine load. In this embodiment, an engine (not shown) is connected to the upper clamping member 4A as will be described later, so that the upper elastic body 21A is configured to receive a supporting load.

  The bracket member 3 is a thick plate-like member that is fixed to an airframe (not shown). The bracket member 3 is formed with a substantially circular mounting hole 30 through which the outer cylinders 20A and 20B of the pair of anti-vibration rubbers 2A and 2B are inserted. A peripheral portion of the mounting hole 30 of the bracket member 3 is disposed between the upper and lower flange portions 23A and 23B of the pair of vibration isolating rubbers 2A and 2B, and is sandwiched between the upper and lower flange portions 23A and 23B.

  The pair of sandwiching members 4A and 4B are plate members that sandwich the pair of vibration isolating members 2A and 2B from both sides in the axial direction, and are respectively attached to the axially outer ends of the pair of vibration isolating members 2A and 2B. . One clamping member 4A of the pair of clamping members 4A and 4B is fixed to an engine (not shown) via an engine bracket (not shown). Further, bolt holes 40A and 40B communicating with the inner side of the inner cylinder 21A (21B) are formed in the pair of clamping members 4A and 4B, respectively.

  The fastening member 5 is a member that couples the pair of clamping members 4 </ b> A and 4 </ b> B, and specifically includes a bolt 50 and a nut 51. As shown in FIG. 1, the bolt 50 is inserted into the bolt hole 40A of the clamping member 4A from the outside in the axial direction of one clamping member 4A, and as shown in FIG. 2, the pair of upper and lower inner cylinders 21A, 21B The bolts 40B of the inner and the other clamping member 4B are inserted through the bolt holes 40B, respectively, and protrude to the axially outer side (the lower side in FIG. 1) of the other clamping member 4B. And the nut 51 is screwed by the front-end | tip of the volt | bolt 50 which protruded from the volt | bolt hole 40B of the other clamping member 4B.

  Next, a method for installing the vibration isolator 1 having the above configuration will be described.

  First, as shown in FIG. 1, a pair of vibration isolating members 2A and 2B, a bracket member 3, and a pair of clamping members 4A and 4B are assembled. More specifically, first, the outer cylinder 20A of one vibration isolation member 2A is inserted into the mounting hole 30 of the bracket member 3 from above the bracket member 3, and the outer cylinder 20B of the other vibration isolation member 2B is inserted into the bracket member. 3 is inserted into the mounting hole 30 of the bracket member 3 from below, and the bracket member 3 is sandwiched from above and below by the flange portions 23A and 23B of the pair of outer cylinders 20A and 20B. Subsequently, sandwiching members 4A and 4B are respectively arranged above and below the pair of vibration isolating members 2A and 2B, and the pair of vibration isolating members 2A and 2B are sandwiched from above and below by the pair of sandwiching members 4A and 4B.

Next, as shown in FIG. 2, the pair of clamping members 4A and 4B are connected by the fastening member 5, and the fastening member 5 is tightened to apply a precompression force to the elastic bodies 22A and 22B. Set.
More specifically, as shown in FIG. 1, first, a bolt 50 is inserted from a bolt hole 40A of one clamping member 4A, and the inside of the pair of inner cylinders 21A and 21B is inserted, and the tip of the bolt 50 is clamped by the other clamping pin. The bolt 4 is protruded from the bolt hole 40B of the member 4B, and the nut 51 is screwed to the tip of the protruding bolt 50.

  Subsequently, the bolt 50 or the nut 51 is axially rotated to tighten the fastening member 5. As the fastening member 5 is tightened, the pair of sandwiching members 4A and 4B are respectively pushed inward in the axial direction, the interval between the pair of sandwiching members 4A and 4B is narrowed, and the pair of vibration isolating members 2A and 2B is paired. The holding members 4A and 4B are pressed from both sides in the axial direction. Accordingly, the pair of inner cylinders 21A and 21B are pushed inward in the axial direction, and the end surfaces on the axially inner sides of the pair of inner cylinders 21A and 21B are brought into contact with each other.

  Further, as described above, when the pair of clamping members 4A and 4B are respectively pushed inward in the axial direction by the fastening member 5, the elastic bodies 22A and 22B are compressed in the axial direction via the pair of clamping members 4A and 4B. The elastic bodies 22A and 22B are elastically deformed so as to swell radially outward. Thereby, precompression force is given to elastic bodies 22A and 22B. At this time, since one elastic body 22A that receives a support load of an engine (not shown) has a larger spring constant than the other elastic body 22B and is harder, one elastic body 22A is pre-compressed than the other elastic body 22B. The amount becomes smaller.

  Further, as described above, the pair of clamping members 4A and 4B are pushed inward in the axial direction by the fastening member 5, so that the flange portions 23A and 23B of the pair of outer cylinders 20A and 20B are brought into close contact with the bracket member 3, respectively. The Thereby, the bracket member 3 is clamped between the upper and lower flange portions 23 </ b> A and 23 </ b> B, and the pair of vibration isolation members 2 </ b> A and 2 </ b> B are fixed to the bracket member 3.

  Next, the above-described vibration isolator 1 is fixed to an airframe (not shown) and an engine (not shown) is placed on the vibration isolator 1 so that the vibration isolator 1 is interposed between the airframe (not shown) and the engine. . More specifically, the above-described bracket member 3 is fixed to the airframe (not shown), and the vibration isolator 1 is installed on the airframe so that the central axis O is vertical. An engine (not shown) is fixed to one (upper) clamping member 4A via an engine bracket (not shown) to support the engine.

As a result, as shown in FIG. 3, the support load of the engine is applied to the one elastic body 22A via the one clamping member 4A, and the one elastic body 22A is compressed by the support load, and the one elastic body 22A. The amount of pre-compression increases, and the amount of pre-compression of the other elastic body 22B decreases accordingly. However, as described above, one elastic body 22A has a larger spring constant than the other elastic body 22B, and the pre-compression amount of one elastic body 22A when the vibration isolator 1 is set (shown in FIG. 2). Since it is small, the amount of pre-compression of one elastic body 22A at the time of supporting load loading is suppressed small. As a result, the pre-compression amount of one elastic body 22A at the time of supporting load is equal to or less than the pre-compression amount of the other elastic body 22B. Preferably, the pre-compression amount of one elastic body 22A and the other elastic body 22B is The distance L1 between the contact surface 24a of the stopper portion 24A of one elastic body 22A and the inner surface 4a of the holding member 4A, and the contact surface 24a of the stopper portion 24B of the other elastic body 22B and the inner surface of the holding member 4B are equal. The distance L2 from 4a becomes equal.
Thus, the engine (not shown) is mounted on the airframe (not shown) via the vibration isolator 1.

  According to the vibration isolator 1 described above, the pre-compression amount of the one elastic body 22A that receives the support load is suppressed to be small, so that the one elastic body 22A can be hardly damaged, and the one elastic body 22A can be made difficult to sag, and a decrease in the precompression force can be suppressed, and contact with other structures due to an increase in support displacement can be prevented.

  Further, since the amount of pre-compression of the other elastic body 22B that does not receive the support load becomes large, the flange portion 23B of the other outer cylinder 20B and the bracket member 3 are separated when the support load is applied or when vibration is input (bound). Can be prevented. Thereby, the fall of the spring constant of the vibration isolator 1 can be prevented, and the noise (sounding sound) due to the collision between the flange portion 23B and the bracket member 3 and the damage to the flange portion 23B and the bracket member 3 are prevented. be able to.

  Further, in the vibration isolator 1 described above, the elastic constant of one elastic body 22A is changed to the elastic constant of one elastic body 22A by using a material having a larger elastic modulus than the elastic material of the other elastic body 22B. Since the spring constant of the elastic body 22B is larger than the elastic body 22B, both the elastic bodies 22A and 22B can have the same shape. Thereby, the setting accuracy of the spring constant of the pair of elastic bodies 22A and 22B is increased, and the quality can be easily ensured. Further, the elastic bodies 22A and 22B can be formed with the same mold, and the cost can be reduced as compared with the case of manufacturing an elastic body having a different shape.

  Further, in the above-described vibration isolator 1, the elastic modulus of both elastic bodies 22A and 22B is set so that the precompression amount of one elastic body 22A in a support load load state is equal to or less than the precompression amount of the other elastic body 22B. Since (spring constant) is set, the durability of one elastic body 22A in the state of supporting load is improved compared to the other elastic body 22B. Thereby, the damage by fatigue of one elastic body 22A which receives the compressive force at the time of bound can be suppressed.

Further, in a state where a supporting load is applied, the distance L1 between the contact surface 24a of the stopper portion 24A of one elastic body 22A and the inner surface 4a of the clamping member 4A and the contact of the stopper portion 24B of the other elastic body 22B. Since the distance L2 between the surface 24a and the inner surface 4a of the clamping member 4B becomes equal, the contact frequency of both stoppers 24A and 24B can be set to be equal.
Further, as described above, since the one elastic body 22A can be prevented from being sag, the contact surface 24a of the stopper 24A of the one elastic body 22A is always in contact with the inner surface 4a of the holding member 4A in the state of supporting load. Can be prevented.

As mentioned above, although the embodiment of the vibration isolator according to the present invention has been described, the present invention is not limited to the above-described embodiment, and can be appropriately changed without departing from the gist thereof.
For example, as shown in FIG. 4, in the present invention, an elastic body 122A (122B) is added to an annular first elastic portion 122a vulcanized and bonded to an outer cylinder 120A (120B) and an inner cylinder 21A (21B). The anti-vibration member 102 </ b> A (102 </ b> B) may be divided into two parts. In this case, the spring of one elastic body 122A is formed by forming the second elastic portion 122b of one elastic body 122A with an elastic material having a larger elastic modulus than the second elastic portion 122b of the other elastic body 122B. The constant is made larger than the spring constant of the other elastic body 122B.

  Further, as shown in FIG. 4, the flange portion 123A (123B) of the outer cylinder 120A (120B) may have a curved shape in a longitudinal sectional view, and the axially inner side of the outer cylinder 120A (120B). An annular bottom wall portion 125 </ b> A (top wall portion 125 </ b> B) may be provided that protrudes from the end of the rim toward the radially inner side over the entire circumference.

  In addition, as shown in FIG. 5, the present invention may be configured such that curled 225A (225B) is formed in the elastic body 222A (222B). Further, a convex positioning portion 226A (226B) is projected from the end surface of the inner cylinder 21A (21B), and a concave notch 241A (at the edge of the bolt hole 40A (40B) of the clamping member 4A (4B) is provided. 241B). When the vibration isolation members 202A and 202B are sandwiched and set by the pair of sandwiching members 4A and 4B, the positioning portion 226A (226B) is fitted into the notch 241A (241B) so that the pair The structure which positions the vibration isolating members 202A and 202B may be used.

  Further, in the above-described embodiment, the vibration isolating members 2A and 2B provided with the stopper portions 24A and 24B made of an elastic material are provided. However, as shown in FIG. 302B may be provided with stopper portions (first stopper portions 325A, 325B) made of metal or the like. More specifically, a cylindrical first stopper portion 325A (325B) that protrudes outward in the axial direction from the outer edge of the flange portion 323A (323B) of the outer tube 320A (320B) is provided. In addition, a second stopper portion 324A (324B) protruding outward in the axial direction from the first stopper portion 325A (325B) is provided on the outer peripheral portion of the elastic body 322A (322B).

Further, as shown in FIG. 7, the present invention may have a configuration in which a stopper member 425A (425B) separate from the outer cylinder 420A (420B) and the elastic body 422A (422B) is mounted. The stopper member 425A (425B) described above includes an annular ring plate portion 425a sandwiched between the flange portion 423A (423B) of the outer cylinder 420A (420B) and the bracket member 403, and an outer edge of the ring plate portion 425a. And an extending portion 425b protruding outward in the axial direction.
Furthermore, the present invention can be configured without a stopper portion as shown in FIG. 5, for example.

  In the above-described embodiment, one elastic body 22A is formed of an elastic material having a larger elastic modulus than the other elastic body 22B, so that one elastic body 22A has a spring constant higher than that of the other elastic body 22B. However, according to the present invention, both elastic bodies can have different spring constants without using elastic materials having different elastic moduli. For example, by making both elastic bodies have different shapes, the spring constant of one elastic body can be made larger than the spring constant of the other elastic body.

  Further, in the above-described embodiment, the precompression amount of one elastic body 22A when a supporting load is applied is equal to or less than the precompression amount of the other elastic body 22B. If the pre-compression amount of the body 22A is smaller than the pre-compression amount of the other elastic body 22B, the one elastic body 22A can be prevented from being damaged or sag. Therefore, the pre-compression amount of the one elastic body 22A in the support load state May be larger than the pre-compression amount of the other elastic body 22B.

In the above-described embodiment, the clamping members 4A and 4B are plate-shaped members, but the present invention may be a clamping member other than a plate-like shape, for example, a truncated cone-shaped or box-shaped clamping member is used. It is also possible.
Further, in the above-described embodiment, the flange portions 23A and 23B are provided at the axially outer ends of the outer cylinders 20A and 20B. However, the present invention is provided at the intermediate portion in the axial direction of the outer cylinders 20A and 20B. A configuration in which the flange portions 23A and 23B are provided is also possible.

  In addition, in the range which does not deviate from the main point of this invention, it is possible to replace suitably the component in above-mentioned embodiment with a well-known component, and you may combine the above-mentioned modification suitably.

DESCRIPTION OF SYMBOLS 1 Anti-vibration apparatus 2A, 2B Anti-vibration member 3,403 Bracket member 4A, 4B Clamping member 5 Fastening member 20A, 20B Outer cylinder 21A, 21B Inner cylinder 22A, 22B Elastic body 23A, 23B Flange part 102A, 102B Anti-vibration member 120A , 120B Outer cylinder 122A, 122B Elastic body 123A, 123B Flange part 202A, 202B Anti-vibration member 222A, 222B Elastic body 302A, 302B Anti-vibration member 320A, 320B Outer cylinder 322A, 322B Elastic body 323A, 323B Flange part 420A, 420B Outside Tube 422A, 422B Elastic body 423A, 423B Flange

Claims (3)

An outer cylinder formed with a flange portion projecting radially outward, an inner cylinder disposed on the inner side of the outer cylinder, and an elastic body connecting the outer cylinder and the inner cylinder. A pair of vibration isolating members arranged with the end faces facing each other;
A bracket member connected to one of the vibration generator and the vibration receiver and sandwiched between the flange portions of the pair of vibration isolation members;
A pair of clamping members connected to either one of the vibration generator and the vibration receiver and clamping the pair of vibration isolating members from both sides in the axial direction;
A fastening member that is inserted into the inner cylinder and connects the pair of clamping members;
With
By tightening the fastening member and pushing the pair of clamping members inward in the axial direction, the end portions of the inner cylinder are brought into contact with each other and the elastic body is pre-compressed via the pair of clamping members. In the vibration isolator,
The anti-vibration device according to claim 1, wherein a spring constant of one elastic body that receives a supporting load of the vibration generating body is larger than a spring constant of the other elastic body among the elastic bodies of the pair of prevention members. The vibration isolator according to claim 1,
The one elastic body is made of an elastic material having an elastic modulus larger than that of the other elastic body. In the vibration isolator according to claim 1 or 2,
The anti-vibration device according to claim 1, wherein a pre-compression amount of the one elastic body in a state where a supporting load of the vibration generating body is applied is equal to or less than a pre-compression amount of the other elastic body.

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