JPH0349316Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Technical Field) The present invention relates to a fluid-filled cylindrical mount that can exhibit a vibration-proofing effect based on the flow of an enclosed fluid.
In particular, the present invention relates to a structure of a fluid-filled cylindrical mount that can advantageously improve durability.

(Prior art) As a type of mounting device for engine mounts, etc. for FF (front engine/front drive) vehicles, as disclosed in Japanese Patent Publication No. 48-36151, Japanese Patent Publication No. 52-16544, etc. , for a connecting body constructed by connecting an inner cylindrical metal fitting and an outer cylindrical metal fitting arranged concentrically or eccentrically to each other with a cylindrical rubber elastic body interposed between them. , by forming inside the connecting body a plurality of fluid chambers and an orifice passage that allows the plurality of fluid chambers to communicate with each other, and by sealing a predetermined incompressible fluid in the fluid chambers, When vibration is input in the radial direction of the mount, a fluid flow is generated through the orifice passage based on the relative internal pressure change of the fluid space, and this causes a fluid flow action or a liquid column resonance action within the orifice passage. Therefore, a so-called fluid-filled cylindrical mount is known that is designed to dampen such input vibrations.

However, in such a fluid-filled cylindrical mount, all of the plurality of fluid chambers are formed within the cylindrical rubber elastic body, and due to the relative displacement of the inner and outer cylindrical fittings upon vibration input, all of the fluid chambers are Since the structure is such that a forced change in volume (internal pressure) is generated in the fluid chamber, it is unavoidable that tensile stress will be generated in a part of the cylindrical rubber elastic body when a load is input. Therefore, especially when placed under a condition where a large initial load is applied, such as an automobile engine mount, the mount The problem was that the durability of the material itself was significantly reduced.

Therefore, in recent years, for the cylindrical rubber elastic body,
A space is provided that extends through the axial direction and has a predetermined width in the circumferential direction, and at a position of the cylindrical rubber elastic body that faces the space with the inner cylindrical fitting interposed therebetween, when vibration is input. As the internal pressure changes with the relative displacement of the inner and outer cylindrical fittings, a pressure receiving chamber is formed into which vibrations to be damped are input, and the pressure receiving chamber is communicated with each other through an orifice passage. an equilibrium chamber of variable volume, defined at least in part by a flexible membrane, in which internal pressure changes can be absorbed by elastic deformation of the flexible membrane; The plurality of fluid chambers are configured by the chamber and the equilibrium chamber, and fluid flow is caused between the chamber and the equilibrium chamber through the orifice passage based on the internal pressure change in the pressure receiving chamber upon vibration input. A fluid-filled cylindrical mount structure has been proposed.

In other words, in the case of such a passage mount, by setting a space at the position where tensile force is applied when the initial load is applied, the generation of tensile stress at that position can be effectively made. Therefore, even when placed under the action of such an initial load, the durability of the rubber elastic body and, by extension, the durability of the mount itself may be significantly reduced. There isn't.

(Problem) However, in a fluid-filled cylindrical mount having the structure described above, when it is mounted under the action of an initial load, the inner cylindrical metal fitting deforms due to the elastic deformation of the cylindrical rubber elastic body. Since the metal fittings are displaced in the radial direction where the pressure receiving chamber is formed, the distance between the inner and outer cylindrical metal fittings in the space,
In other words, the amount of displacement of the inner cylindrical fitting relative to the outer cylindrical fitting toward the space (rebound direction) tends to become too large.

In addition, in the case of such a cylindrical mount, the equilibrium chamber is usually located radially outward of the air chamber, and the flexible membrane can be expanded into the air chamber. Therefore, since the structure is such that a change in volume is allowed, it is extremely difficult to restrict the displacement of the inner cylinder fitting in the rebound direction.

In other words, in such a fluid-filled cylindrical mount, if a large vibration load is input in the rebound direction, it is difficult to set the displacement regulating mechanism of the inner cylinder metal fitting, and the cylindrical rubber elastic body may be excessively deformed and Because of the accompanying excessive tensile stress, there is still a problem in that it is difficult to obtain sufficient durability.

(Solution) The present invention was developed against the background of the above-mentioned circumstances, and its features are (a) an inner cylindrical metal fitting, and (b) an outer side of the inner cylindrical metal fitting. (c) a cylindrical rubber elastic body interposed between the inner and outer cylinder fittings to elastically connect them; (d) ) a hollow space formed in the cylindrical rubber elastic body in the axial direction and extending with a predetermined width in the circumferential direction; Vibration to be damped is input to opening pocket portions formed on the outer circumferential surface, which are formed at opposing positions with the cylindrical metal fitting in between, and which are formed by closing the openings with the outer cylindrical metal fitting. (f) a pocket portion that opens on the outer peripheral surface and is formed at a predetermined distance in the circumferential direction from the pocket portion forming the pressure receiving chamber, the opening of which is closed by the outer cylindrical fitting; (g) an orifice passageway that allows the pressure receiving chamber and the equilibrium chamber to communicate with each other; (h) In a fluid-filled cylindrical mount having a predetermined incompressible fluid sealed in the pressure receiving chamber and the equilibrium chamber, the inner cylindrical fitting is brought into pressure contact with the inner cylindrical fitting through a rubber layer of a predetermined thickness. A stopper member that generates a radial compressive force against the rubber elastic body on the side where the pressure receiving chamber is formed is located in the cavity of the rubber elastic body, and the inner cylinder metal fitting and the outer cylinder metal fitting This is due to the fact that an interposition was placed between the two.

(Examples) Hereinafter, in order to clarify the present invention more specifically, examples of the present invention will be described in detail with reference to the drawings.

First, FIGS. 1 and 2 show a specific example in which the present invention is applied to an engine mount for a front-wheel drive vehicle. In these figures, reference numerals 10 and 12 denote an inner cylinder metal fitting and an outer cylinder metal fitting, respectively, which are arranged eccentrically by a predetermined distance in the radial direction of the mount, and which are interposed between them.
They are elastically connected by a rubber elastic body 14 that has a generally cylindrical shape as a whole.

As for such engine mounts,
The inner cylindrical metal fitting 10 and the outer cylindrical metal fitting 12 are attached to either the vehicle body side or the power unit side including the engine, so as to provide vibration-proof support for the power unit to the vehicle body. The load weight of the power unit is applied to the eccentric direction of the metal fittings 10, 12, and the rubber elastic body 14 is elastically deformed, so that the metal fittings 10, 12 are positioned approximately concentrically. becomes. In addition, in the case of such an engine mount, an inner cylinder fitting 10 and an outer cylinder fitting 1 are provided.
The rubber elastic body 14 is mainly used to dampen vibrations that are input in the eccentric direction (vertical direction in FIG. 1) with respect to the rubber elastic body 14.
is deformed exclusively in the eccentric direction of both metal fittings 10 and 12.

Here, the inner cylindrical fitting 10 is formed to have a relatively thick cylindrical shape, and a metal sealing sleeve 16 having a substantially thin cylindrical shape is provided on the outside in the radial direction at a predetermined distance. , are positioned eccentrically by a predetermined amount. As shown in FIGS. 3 and 4, these inner cylinder fittings 10
The rubber elastic body 14 is interposed between the inner cylinder fitting 10 and the seal sleeve 16, and is integrally vulcanized and bonded to the outer peripheral surface of the inner cylinder fitting 10 and the inner peripheral surface of the seal sleeve 16, respectively. It is formed as a product.

In addition, the rubber elastic body 14 includes an inner cylinder fitting 1.
0 and the seal sleeve 16 on the side where the separation distance in the eccentric direction is smaller.
A cavity 18 having a generally arcuate cross section is formed to extend approximately half the circumference in the circumferential direction along the inner circumferential surface of the housing, and to penetrate in the axial direction. Then, the rubber elastic body 14 substantially elastically connects the inner cylinder fitting 10 and the outer cylinder fitting 12 only on the side where the separation distance between the two metal fittings 10 and 12 in the eccentric direction is large. As described above, the generation of tensile stress during elastic deformation of the rubber elastic body 14 due to the load weight (initial load) of the power unit applied in the installed state is minimized. It is now possible to reduce the

Further, in the rubber elastic body 14, the space 1 is
At a position radially opposite to 8 with the inner cylindrical fitting 10 interposed therebetween, in other words, on the side where the distance between the inner cylindrical fitting 10 and the seal sleeve 16 in the eccentric direction is greater, the inner cylindrical fitting 10 and the seal Eccentric direction with respect to the sleeve 16 and the rubber elastic body 14
A through hole 20 is formed so as to penetrate in a direction substantially perpendicular to both directions of the axial center. In this embodiment, the through hole 20 constitutes a pocket portion for forming a pressure receiving chamber that opens on the outer peripheral surface.

Further, in the through hole 20, an umbrella plate 22 having a substantially rectangular flat plate shape is supported by the inner cylinder fitting 10, so that an umbrella plate 22 is provided on both sides in the axial direction of the rubber elastic body 14 that defines the through hole 20. The umbrella plate 22 is arranged so as to face the inner wall surface of the umbrella plate 22 with a gap 24 of a predetermined distance therebetween.
The inside of the through hole 20 is approximately divided into two in the eccentric direction of the inner cylinder fitting 10 and the seal sleeve 16. The outer surface of the umbrella plate 22 is integrally covered with a rubber elastic layer having a predetermined thickness.

Furthermore, in the engine mount of the present embodiment, a hard regulation pipe 26 having a small diameter hollow cylindrical shape is axially penetrated and buried in the radially outer portion of the through hole 20 in the rubber elastic body 14. The seal sleeve 16 is disposed under the condition and is integrally fixed to the rubber elastic body 14, and further radially outward from the buried position of the regulating pipe 26 along the inner circumferential surface of the seal sleeve 16. A slit 28 is formed which has an arcuate cross section, extends in the circumferential direction with a predetermined width, and penetrates in the axial direction.

Due to the effect of suppressing the deformation of the rubber elastic body 14 by the regulating pipe 26 and the effect of absorbing the deformation of the rubber elastic body 14 by the slit 28, the wall of the through hole 20 due to the initial load under the above-mentioned mounting condition is In particular, bulging deformation in the axial direction of the side wall portion in the axial direction of the mount can be effectively suppressed. Gap 2
4 can be effectively reduced.

On the other hand, in the case of the seal sleeve 16, the diameter of the central part in the axial direction is reduced in the shape of a concave groove over the entire circumferential direction to form a small diameter part 30, thereby forming an opening on the outer circumferential surface. A circumferential groove 3 extending in the circumferential direction
2 is formed.

In addition, window portions 34 are provided in the small diameter portion 30 at the locations where the openings on both sides of the through hole 20 formed in the rubber elastic body 14 are located. The through hole 20 is opened to the outside through the space 18 formed in the rubber elastic body 14.
A window portion 36 is provided at a portion corresponding to the outer peripheral side portion of
The hollow space 18 is formed to have a length of a little less than half a circumference in the circumferential direction, and the space 18 is opened on the outer circumferential surface at the center in the axial direction through the window portion 36 .

In the case of such an integrally vulcanized product consisting of the inner cylinder fitting 10, the seal sleeve 16, and the rubber elastic body 14, the circumferential groove of the seal sleeve 16 is as shown in FIGS. 1 and 2. A stopper fitting 38 is assembled into the inside of the stopper fitting 32 at a portion where the window portion 36 is formed.

As shown in FIGS. 5 and 6, the stopper fitting 38 is formed in a substantially thin-walled semi-cylindrical shape, and has a radial center portion in the axial center portion excluding both circumferential end edges. An inwardly recessed portion 42 is provided, thereby forming a recess 44 opening on the outer circumferential surface.

Further, on the radially outer side of the stopper fitting 38, as shown in FIGS. 1 and 2, a diaphragm assembly fitting 46 is arranged so as to be overlapped on the outer peripheral surface thereof. .

As shown in FIGS. 7 and 8, the diaphragm assembly fitting 46 is formed in a substantially thin semi-cylindrical shape so as to cover the entire outer peripheral surface of the stopper fitting 38. The diaphragm assembly fitting 46 also has a rectangular window portion 48 in a portion corresponding to the recess 44 of the stopper fitting 38.
is provided, and a peripheral wall 50 that enters into the recess 44 of the stopper fitting 38 is erected at the peripheral edge of the window 48.
0, the diaphragm 52 as a flexible membrane is arranged and integrally attached so as to close the window 48 from the inside by fixing and supporting the peripheral edge. .

These stopper fittings 38 and diaphragm assembly fittings 46 are attached to the inner cylindrical fitting 10 and seal sleeve 16, as shown in FIGS. 1 and 2, for the integrally vulcanized product. The seal sleeve 16 is arranged in order from the side with the smaller eccentric distance.
It is assembled so as to fit into the circumferential groove 32 in. As is clear from these figures, in this embodiment, the diaphragm assembly fitting 46 and the diaphragm 52 form a pocket portion 6 for forming an equilibrium chamber that opens on the outer peripheral surface.
0 is formed.

Incidentally, during such assembly, the fitting portion 42 of the stopper fitting 38 is inserted into the space 18 through the window portion 36 of the seal sleeve 16. Then, the fitting portion 42
Since the depth of the recess is set to be larger than the gap of the cavity 18, the bottom of the fitting portion 42 is placed against the inner cylindrical fitting 10 during such assembly. Rubber layer 5 present on the outer peripheral surface of 10
4, and in this abutting state, the stopper fitting 38 is further pushed radially inward and positioned approximately on the same axis as the rubber elastic body 14. -ing

That is, by assembling the stopper fitting 38, the inner cylindrical fitting 10 is displaced in the radial direction with a larger eccentric distance with respect to the seal sleeve 16, whereby the rubber elastic body 14, pre-compression is applied in the radial direction to the radial portion where the through-hole 20 is formed, in other words, pre-compression is applied in the direction in which the initial load is applied in the mounted state.

Furthermore, after the stopper fitting 38 and the diaphragm fitting 46 are assembled to the integrally vulcanized molded product, the inner cylindrical fitting 1 is attached to the outer peripheral surface of the integrally vulcanized product.
0 and the seal sleeve 16 from both sides in the eccentric direction,
Orifice forming metal fittings 5 each having a substantially semi-cylindrical shape
6 and 58 are assembled so as to fit into the circumferential groove 32 of the seal sleeve 16, and furthermore, by fitting the outer cylindrical fitting 12 onto the outer circumferential surface of the seal sleeve 16, , are integrally assembled. Note that a thin sealing rubber layer 6 is provided on the inner circumferential surface of the outer cylindrical fitting 12 over almost the entire surface.
8 is formed.

That is, by assembling the orifice fittings 56, 58 and the outer cylinder fitting 12, the through hole 20
The openings through the windows 34 and 34 and the opening of the pocket section 60 are respectively closed, so that the first fluid chamber 62 is opened in the through hole 20 and the first fluid chamber 62 is closed inside the pocket section 60. , and a second fluid chamber 64 are respectively formed. Here, the first fluid chamber 62 is configured as a pressure receiving chamber in which a change in volume (change in internal pressure) occurs due to relative displacement of the inner and outer cylindrical fittings 10 and 12 based on the above-mentioned vibration input. The interior thereof is divided into an inner portion and an outer portion in the radial direction by the umbrella plate 22, and both side portions are formed between the umbrella plate 22 and the wall surface of the fluid chamber. They communicate with each other through an annular constriction 66 formed therebetween. On the other hand, the second fluid chamber 64 has a variable volume based on the elastic change of the diaphragm 52 forming its bottom wall, and is configured as an equilibrium chamber in which changes in its internal pressure can be avoided. Note that a space 55 located radially inside the second fluid chamber 64 and formed between the stopper fitting 38 and the diaphragm 52 is
It is configured as a space that allows for bulging deformation of 2.

Although not clearly shown in the drawings, each of the orifice forming metal fittings 56 and 58 has a concave opening on the outer circumferential surface and extending in the circumferential direction for approximately one and a half circumferences in a generally spiral shape. A groove 70 is formed, and both end portions of the groove 70 are communicated with the first fluid chamber 62 and the second fluid chamber 64 through communication holes 71, respectively. and,
By closing the opening of the groove 70 with the outer cylindrical fitting 12, the first fluid chamber 6
2 and the second fluid chamber 64 with a predetermined length and cross-sectional area.
is being formed.

Further, the operation of fitting the orifice forming fittings 56, 58 and the outer cylindrical fitting 12 onto the integrally vulcanized product is performed in a predetermined incompressible fluid such as water or polyalkylene glycol. A predetermined incompressible fluid is sealed in the first and second fluid chambers 62, 64 and the orifice passage 72 by performing diameter reduction processing such as eight-way drawing on the cylindrical fitting 12. You will be forced to do so.

Therefore, in the engine mount having the above-described structure, when the vibration is input, the first fluid chamber 62 and Based on the fluid flow between the second fluid chamber 64 or the displacement of the umbrella plate 22 within the first fluid chamber 62, a fluid flow is induced through the narrowed portion 66, and When vibrations are input to the orifice passage 72 and the narrowed portion 66 in respective predetermined frequency ranges, a predetermined vibration damping effect based on fluid flow action or liquid column resonance action can be exerted. It is.

More specifically, for example, when inputting vibrations in a low frequency range such as engine shake, the orifice passage 7
Based on the flow of fluid through the orifice passage 72, excellent vibration damping force can be exerted, and vibrations in the medium to high frequency range such as muffled sounds and engine transmitted sounds, etc., where the orifice passage 72 is substantially blocked, are At the time of input, the flow cross-sectional area, length, etc. of the orifice passage 72 and the narrowed part 66 are tuned so that a low dynamic spring effect can be exerted based on the fluid flow through the narrowed part 66. .

For such engine mounts,
A stopper fitting 38 is installed in the space 18 of the rubber elastic body 14.
is arranged, and by the contact of the inner cylindrical fitting 10 with the stopper fitting 38, the amount of displacement of the inner cylindrical fitting 10 toward the space 18 when a vibration load is input can be effectively regulated. . A rubber layer 54 is interposed between the abutting surfaces of the inner cylinder fitting 10 and the stopper fitting 38 to reduce the impact caused by such abutting.

Moreover, there, such a stopper fitting 38
Since the rubber elastic body 14 is assembled under pressure contact with the inner cylindrical fitting 10 so that preliminary compression is applied to the rubber elastic body 14, the inner cylindrical member 14 is assembled under pressure contact with the inner cylindrical fitting 10. A desired displacement amount can be advantageously set without the amount of displacement of the cylindrical fitting 10 toward the cavity 18 side (rebound direction) becoming excessive.

Therefore, due to the effect of regulating the displacement of the inner cylinder fitting 10 by the stopper fitting 38, that is, the effect of regulating the amount of deformation in the rubber elastic body 14, excessive deformation of the rubber elastic body 14 and The generation of large stress accompanying this can be effectively avoided, and the rubber elastic body 14,
As a result, the durability of the mount itself can be advantageously improved.

In addition, in the case of an engine mount having such a structure, fluid is sealed into the first and second fluid chambers 62 and 64 under a certain degree of preliminary compression in the initial load input direction. Therefore, the generation of hydraulic pressure in the fluid chamber due to the initial load applied at the time of installation and the amount of expansion deformation of the diaphragm 52 caused by this can be effectively reduced, and thereby the initial The volume change amount of the second fluid chamber 64 is advantageously ensured, and an excellent effect can be achieved such that a sufficient amount of fluid flow between the fluid chambers can be stably obtained when a large vibration load is input. It is.

Regarding the mount in this example,
The amount of displacement of the inner cylinder fitting 10 when the inner cylinder fitting 10 is displaced toward the first fluid chamber 62 side, that is, when a vibration load in the bounce direction is input, is also regulated by the contact of the umbrella plate 22 with the rubber elastic body 14. This makes it possible to effectively avoid excessive displacement of the rubber elastic body 14 and generation of stress when vibration is input in the bounding direction.

In addition, in the mount according to this embodiment, the diaphragm 52 defining the second fluid chamber 64 is housed in the recess 44 of the stopper fitting 38, and the amount of deformation thereof is reduced. Since the diaphragm 52 can be regulated by the stopper fitting 38, excessive bulging deformation of the diaphragm 52 and the generation of large stress accompanying it can be effectively prevented, and its durability can be improved. It also has some advantages.

Although one embodiment of the present invention has been described in detail above, this is a literal illustration, and the present invention is based on the following:
It is not intended to be interpreted as being limited to such specific examples.

For example, none of the umbrella plate 22, regulation pipe 26, slit 28, etc. in the embodiment described above are essential requirements for the present invention.

In addition, the first fluid chamber 62, the second fluid chamber 64,
Further, the specific structure of the orifice passage 72 is not limited in any way; for example, the first fluid chamber may be configured with a pocket portion formed simply in the shape of a recess; In the above embodiment, the diaphragm 52 that compensates for the change in volume of the second fluid chamber 64 is located in the space 18 (the space 5
5) It was placed in a state where it could be expanded and deformed,
A window closed by a diaphragm is provided in the peripheral wall of the outer cylindrical metal fitting, so that the volume change can be compensated for by the diaphragm expanding outward in the radial direction. It is also possible.

Furthermore, the specific structure of the stopper member is by no means limited to that of the embodiment described above; for example, the stopper metal fitting 38 in the embodiment described above is formed with an abutment surface extending in the radial direction of the mount. However, it is also possible to set a contact surface that extends in the axial direction so that the inner cylinder fitting 10 comes into contact with it over almost the entire length, and it is also possible to set a contact surface that extends in the axial direction so as to contact the inner cylinder fitting 10 over almost the entire length. It is also possible to form layers.

In addition, in the embodiment described above, an example was shown in which the present invention was applied to an automobile engine mount, but the present invention can be advantageously applied as a mount for various other devices. Of course there is.

Although not listed in detail, the present invention can be implemented with various changes, modifications, improvements, etc. based on the knowledge of those skilled in the art, and such embodiments do not go beyond the spirit of the present invention. It goes without saying that all of these are included within the scope of the present invention as long as they do not deviate from the above.

(Effect of the invention) As is clear from the above explanation, according to the present invention, even in a fluid-filled cylindrical mount that is installed under the application of an initial load, it is possible to reduce the internal damage when a load is applied in the rebound direction. A stopper member that can effectively restrict the displacement of the cylindrical metal fitting toward the cavity side can be easily and advantageously set.

The displacement regulating function of the inner cylindrical metal fitting by such a stopper member can effectively avoid excessive deformation of the rubber elastic body and the generation of large stress associated with it when an excessive vibration load is input. The durability of the elastic body and, by extension, the mount itself can be effectively improved.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view showing an engine mount which is an embodiment of a fluid-filled cylindrical mount structured according to the present invention, FIG. 2 is a cross-sectional view taken from FIG. 1, and FIG. FIG. 4 is a cross-sectional view corresponding to FIG. 1, showing an integrally vulcanized molded product constituting such an engine mount, FIG. 4 is a cross-sectional view taken from FIG. 3, and FIG. FIG. 6 is a sectional view showing the stopper fitting, FIG. 6 is a cross-sectional view taken from FIG. 5, and FIG. FIG. 8 is a cross-sectional view taken from FIG. 7. 10: Inner cylinder metal fitting, 12: Outer cylinder metal fitting, 14: Rubber elastic body, 18: Hole, 20: Through hole (pocket part), 38: Stopper metal fitting, 52: Diaphragm,
54: Rubber layer, 60: Pocket portion, 62: First fluid chamber (pressure receiving chamber), 64: Second fluid chamber (equilibrium chamber), 72: Orifice passage.

Claims (1)

[Scope of Claim for Utility Model Registration] (a) An inner cylindrical metal fitting, (b) an outer cylindrical metal fitting arranged at a predetermined distance on the outside of the inner cylindrical metal fitting, and (c) the inner cylindrical metal fitting and the outer cylindrical metal fitting. (d) a cylindrical rubber elastic body interposed between the cylindrical rubber elastic body and elastically connecting them; and (e) a pocket portion of the cylindrical rubber elastic body that opens on the outer circumferential surface and is formed at a position opposite to the void with the inner cylindrical fitting interposed therebetween. a pressure receiving chamber which is formed by being closed by the outer cylindrical metal fitting and into which vibrations to be damped are input, and (f) a predetermined distance in the circumferential direction from the pocket portion forming the pressure receiving chamber. a pocket portion that is formed at a position that is open to the outer circumferential surface, and is formed by closing the opening with the outer cylindrical metal fitting, and at least a part of the pocket portion is defined by a flexible membrane. It has an equilibrium chamber with a variable volume, (g) an orifice passage that allows the pressure receiving chamber and the equilibrium chamber to communicate with each other, and (h) a predetermined incompressible fluid sealed in the pressure receiving chamber and the equilibrium chamber, respectively. In the fluid-filled cylindrical mount, the inner cylindrical metal fitting is pressed against the inner cylindrical fitting via a rubber layer of a predetermined thickness, and applies a radial compressive force to the rubber elastic body on the side where the pressure receiving chamber is formed. a stopper member that generates the force is located in the cavity of the rubber elastic body and is interposed between the inner cylindrical metal fitting and the outer cylindrical metal fitting;
Fluid filled cylindrical mount.