JPH02129426A - Fluid enclosed type mount device - Google Patents

Abstract

PURPOSE:To make excellent vibrationproofing effect exhibit for input vibration of wide frequency range by arranging in a pressure receiving chamber a liquid- operated absorbing mechanism, in which elastic deformation of a flexible membrane accompanied with volume variation of an air chamber can be generated. CONSTITUTION:A closed air chamber 54 having a nearly disk-like shape and a prescribed volume, is formed in a cylinder part 44 and under a rubber elastic plate 48. A liquid-operated absorbing mechanism is constituted out of a partition member 38 consisted of the rubber elastic plate 48 and a metal cover 52, and the air chamber 54 formed between both members. Volume of the air chamber 54 is instituted by synthetically considering characteristic of input vibration, area of the rubber elastic plate 48, modulus of elasticity, volume of a pressure receiving chamber, etc. Thus, excellent vibrationproofing effect can be exhibited.

Description

Detailed Description of the Invention (Technical Field) The present invention relates to a fluid-filled mount device that reduces or prevents vibration transmission based on the flow of fluid sealed inside, and particularly relates to a fluid-filled mount device that reduces or prevents transmission of vibrations based on the flow of fluid sealed inside. The present invention relates to a fluid-filled mount device that can exhibit excellent vibration damping characteristics over a wide range of periods.

(Background Art) Conventionally, devices such as automobile engine mounts have been interposed between two members constituting a vibration transmission system to connect these members in a vibration-proof manner, or to connect one member to the other. As a type of mount device for anti-vibration support, Japanese Patent Laid-Open No. 55-107142 and Utility Model Laid-Open No. 58-114933
As disclosed in the above publication, a first support metal fitting and a second support metal fitting are arranged at a predetermined distance from each other,
They are elastically connected by a rubber elastic body interposed between them to form a connecting body, and inside the connecting body,
A pressure receiving chamber that forms a fluid storage chamber sealed with a predetermined incompressible fluid, and a partition member is disposed within the fluid storage chamber, and vibrations to be damped are input to both sides of the partition member. The so-called fluid-filled type has a structure in which a volume-variable equilibrium chamber is defined at least in part by an elastic thin film, and an orifice passage is provided to communicate the pressure-receiving chamber and the equilibrium chamber with each other. Mounting devices are known. In such a mounting device, a predetermined barrier set in the orifice passage is caused by a resonance effect based on the flow of fluid between the pressure receiving chamber and the equilibrium chamber through the orifice passage, which is generated when vibration is input. This means that a vibration effect can be exerted.

However, in a mounting device having such a structure, the vibration damping effect based on the resonance effect of the fluid in the orifice passage is not effective against input vibration in a relatively narrow frequency range near the resonance point of the fluid flowing in the orifice passage. However, when vibrations are input in a higher frequency range than that which can be effectively exerted, the orifice passage becomes substantially blocked, causing a significant increase in the mount dynamic spring constant, and rather preventing prevention. The problem was that the vibration function deteriorated.

Therefore, in Japanese Patent Application Laid-Open No. 57-9340, etc., a communication space is formed inside a partition wall that partitions the pressure receiving chamber and the equilibrium chamber, and communicates with the pressure receiving chamber and the equilibrium chamber, respectively. A hydraulic pressure absorption mechanism has been proposed in which a thin plate-like movable member is accommodated and arranged within the communication space. That is, when low-frequency, large-amplitude vibrations are input to a mount device equipped with such a hydraulic pressure absorption mechanism, the movable plate closes the communication hole that communicates the communication space with the pressure receiving chamber or the equilibrium chamber. As a result, the vibration damping effect due to the resonance effect of the fluid flowing in the orifice passage can be effectively ensured without the hydraulic pressure absorption mechanism substantially functioning. When input, substantial fluid flow is allowed between the pressure receiving chamber and the equilibrium chamber based on the displacement of the movable plate, thereby avoiding the mount from becoming a highly dynamic spring due to an increase in liquid pressure within the pressure receiving chamber. This means that it can be done.

However, in a hydraulic pressure absorption mechanism with such a structure,
The structure is extremely complex, which poses manufacturing and cost problems.Furthermore, when vibration is input, the movable plate comes into contact with the inner surface of the communication space, causing damage to the vibration. It also had the problem of generating noise.

On the other hand, JP-A-58-163842 and JP-A-61-
Publication No. 197836 discloses a hydraulic pressure absorption mechanism having a structure in which a part of a partition wall that partitions a pressure receiving chamber and an equilibrium chamber is made of a rubber elastic membrane. That is, in a mounting device equipped with a hydraulic pressure absorption mechanism having such a structure,
When vibration is input in a low frequency range, the amount of deformation of the rubber elastic membrane is limited by its own elastic force, so that the fluid flows through the orifice passage without the hydraulic pressure absorption mechanism substantially functioning. The vibration damping effect due to the resonance effect of the fluid can be effectively ensured, and on the other hand, when high frequency and small amplitude vibrations are input, the elastic deformation of the rubber elastic membrane effectively reduces the vibration between the pressure receiving chamber and the equilibrium chamber. As a result, the mount can be effectively prevented from becoming a highly dynamic spring due to an increase in the fluid pressure within the pressure receiving chamber.

However, in a hydraulic pressure absorption mechanism having such a structure, when a large load is applied to the mount, excessive stress is generated on the rubber elastic membrane, which reduces the durability of the rubber elastic membrane itself. The durability of the parts fixed to the walls and partition walls became a major problem, and it was difficult to obtain sufficient product durability and reliability. In addition, in order to improve the durability of the rubber elastic membrane and improve the effect of regulating the amount of deformation, a structure in which a reinforcing material such as canvas is embedded inside the membrane has been proposed. It is difficult to obtain sufficient durability, and conversely, problems arise in that the reinforcing material is embedded, making manufacturing difficult and disadvantageous in terms of cost.

(Problem to be solved) Here, the present invention has been made against the background of the above-mentioned circumstances, and the problem to be solved is:
While ensuring the vibration damping effect based on the resonance effect of the fluid flowing in the orifice passage, it eliminates the significant rise of the mount moving spring when vibration is input in a higher frequency range than the resonance frequency set in the orifice passage. obtain,
The object of the present invention is to clarify a hydraulic pressure absorption mechanism with a simple and novel structure, and thereby to provide a fluid-filled mount device that can exhibit an excellent vibration damping effect against input vibrations in a wide frequency range.

(Solution Means) In order to solve this problem, the present invention includes:
A first support metal fitting and a second support metal fitting that are arranged at a predetermined distance from each other are integrally connected by a rubber elastic body, while a gap between the first support metal fitting and the second support metal fitting is a pressure-receiving chamber filled with a predetermined incompressible fluid and into which vibrations to be damped are input; and a variable-volume equilibrium chamber at least partially defined by an elastic thin film. , a fluid-filled mounting device provided with an orifice passage that communicates the pressure receiving chamber and the equilibrium chamber with each other; A sealed air chamber with a predetermined volume is provided behind the flexible membrane, and when an internal pressure fluctuation occurs in the pressure receiving chamber, elastic deformation of the flexible membrane occurs accompanied by a change in the volume of the air chamber. The hydraulic pressure absorption mechanism
Its feature is that it is disposed within the pressure receiving chamber.

(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 an example of an engine mount for an automobile in which the present invention is applied.

In this figure, 1o and 12 are the first and second support fittings, respectively, and - vibration input direction (in FIG. 1,
They are arranged at a predetermined distance apart in the vertical direction. Also,
A rubber elastic body 30 is interposed between the first support metal fitting 10 and the second support metal fitting 12, and the rubber elastic body 30 allows the first support metal fitting lO and the second support metal fitting 10 to The support fittings 12 are integrally and elastically connected to each other. In the engine mount in this embodiment, the first support fitting 10 and the second support fitting 12 are attached to the engine unit side and the vehicle body side, respectively, so that the engine unit is attached to the vehicle body. It is designed to provide anti-vibration support.

When mounted in this manner, the weight of the engine unit is applied to the engine mount, so that the engine mount is placed under a state where an initial load of the extent shown in FIG. 4 is applied. That will happen.

More specifically, the first support fitting 10 has an approximately disk shape as a whole, and the outer circumferential edges facing each other in the radial direction each have a radial diameter at a portion extending over an approximately concave half circumference in the circumferential direction. The extending portion 13 extends outward in the direction by a predetermined width. Furthermore, a block-shaped support portion 14 fixed to the inner surface and a mounting bolt 16 protruding from the outer surface are each integrally provided at the center of the second support fitting 10. .

On the other hand, the second support fitting 12 has a substantially shallow cylindrical shape with a bottom, and has a bottom fitting 18 having an outer flange portion 20 at the opening periphery. The outer flange portion 2 of the bottom metal fitting 18 is composed of a cylindrical metal fitting 24 having a caulked portion 22 at the bottom.
0, the caulking portion 22 of the cylindrical metal fitting 24 is integrally assembled by caulking and fixing. Further, the bottom fitting 18 constituting the second support fitting 12 is integrally provided with mounting bolts 25, 25 that protrude from the outer surface of the bottom portion.

These first support fittings 10 and second support fittings 1
2 means that the second support fitting 12 is the first support fitting 10.
They are arranged concentrically facing each other with a predetermined distance apart, with openings on the sides.

In addition, at the opening peripheral portion of the cylindrical metal fitting 24 constituting the second support fitting 12 on the side of the first support metal fitting 10, located at approximately a quarter circumferential portion facing in one direction in the radial direction,
Each of the inner abutting portions 26 extending radially inward by a predetermined length is bent.
Outer abutting portions 28 are bent and extend diagonally outward by a predetermined length, respectively, at approximately quarter circumferential portions facing each other in a direction orthogonal to the opposing direction of the outer abutting portions 26 . Then, the outer contact portion 28.28 of the cylindrical metal fitting 24 has a relative positional relationship in which it is opposed to the extension portion 13.13 provided on the first support metal fitting 10 in the vibration input direction, It has been placed in place.

Furthermore, these first support metal fittings 10 and second support metal fittings 1
A rubber elastic body 30, which is interposed between the cylindrical fittings 10 and 2 and elastically connects the cylindrical fittings 10 and 12, has a substantially hollow truncated conical shape. Then, on the small diameter side end surface, on the inner surface of the first support fitting 10, and on the large diameter side end surface,
By being vulcanized and bonded to the opening-side peripheral edge of the cylindrical metal fitting 24 constituting the second support metal fitting 12, an integral vulcanized molded product having the first support metal fitting 10 and the cylindrical metal fitting 24 is formed. It is being done. Note that a reinforcing metal fitting 31 having a substantially Taber cylindrical shape is embedded in the axial center of the rubber elastic body 30, so that the rubber elastic body 3
The deformation of 0 can be regulated.

On the other hand, inside the mount having such a structure, there are a bottom metal fitting 18 and a cylindrical metal fitting 2 that constitute the second support metal fitting 12.
The outer peripheral edge of the diaphragm 3 is fluid-tightly sandwiched between the caulked portions of the diaphragm 3 and the elastic thin film.
2 are arranged.

The inside of the mount is formed by the diaphragm 32 into a sealed fluid chamber located on the first support fitting 10 side and a space 34 located on the bottom fitting 18 side that allows the diaphragm 32 to expand and deform. It is divided into two parts. In addition,
This space 34 is communicated with the atmosphere through a through hole 36, and the deformation of the diaphragm 32 is prevented from being inhibited by the internal pressure.

In the fluid chamber, a caulking portion 22 of the cylindrical metal fitting 24 is provided.
The bottom fitting 18 is caulked and fixed in a predetermined incompressible fluid such as water, alkylene glycol, polyalkylene glycol, silicone oil, etc., so that the predetermined incompressible fluid is enclosed. .

Furthermore, within the fluid chamber, a partition member 38 having an approximately disk shape as a whole is disposed in a direction perpendicular to the vibration input direction, so that the inside of the fluid chamber is separated by the partition member 38. Three days apart, a pressure receiving chamber 40 is located on the first support fitting 10 side, where internal pressure fluctuations are caused based on the elastic deformation of the rubber elastic body 30 upon vibration input, and a pressure receiving chamber 40 is located on the diaphragm 32 side. Based on the deformation of the diaphragm 32, it is partitioned into an equilibrium chamber 42 in which internal pressure fluctuations are avoided.

Here, the outer circumferential portion of the partition member 38 has a generally annular plate shape as a whole, and a support formed by integrally providing a cylindrical portion 44 rising at a predetermined height in the axial direction at the inner hole circumferential edge of the partition member 38. It is constituted by a metal fitting 46. A rubber elastic plate 48 as a flexible membrane having a substantially disk shape is integrally vulcanized and bonded to the opening on the protruding end side of the cylindrical portion 44 of the support fitting 46. The opening on the protruding end side of the cylindrical portion 44 is closed by the rubber elastic plate 48. Furthermore, on the support fitting 46, a hat-shaped lid fitting 52 having a circular convex portion 50 in the center is superimposed on the surface opposite to the side from which the cylindrical portion 44 protrudes. By fitting the convex portion 50 airtightly into the cylindrical portion 44 of the support fitting 46, a predetermined volume of a substantially disc-shaped sealed space is formed between the cylindrical portion 44 and the rubber elastic plate 48. An air chamber 54 is defined therein.

In addition, in such a partition member 38, in order to ensure the airtightness of the air chamber 54 formed inside the partition member 38, the rubber elastic plate 48 is attached to the support metal fitting 46 as shown in FIG.
A sealing rubber layer 57 of a predetermined thickness is integrally provided on the inner circumferential surface of the cylindrical portion 44 of the support fitting 46. The sealing performance between the lid fitting 52 and the circular convex portion 50 that is fitted into the lid fitting 52 is improved.

Further, a supporting metal fitting 4 is provided on the outer peripheral portion of the partition member 38.
By bending the distal end peripheral edge of the cylindrical portion 44 at 6 radially outward, a groove 56 that opens on the outer circumferential surface and extends in the circumferential direction is formed.

The partition member 38 having the above-mentioned structure has the bottom metal fitting 18 and the cylindrical metal fitting 24, which constitute the second support fitting 12, together with the diaphragm 32, at the outer peripheral edge of the support fitting 46 and the differential fitting 52. The rubber elastic plate 48 is assembled in a state where it is exposed in the pressure receiving chamber 40 by being held at the caulked portion. Furthermore, by assembling the partition member 38, the opening of the groove 56 is covered with the inner circumferential surface of the cylindrical metal fitting 24, so that a pressure receiving chamber 40 is formed therein which extends for a predetermined length in the circumferential direction.
An orifice passageway 58 is formed that interconnects the balance chamber 42 and the balance chamber 42 .

That is, in the partition member 38 having such a structure,
The liquid pressure in the pressure receiving chamber 40 will be directly applied to the front side of the rubber elastic plate 48, and the rubber elastic plate 48 will act as Since the deformation is permissible, the rise in hydraulic pressure within the pressure receiving chamber 40 can be reduced or eliminated by the elastic deformation of the rubber elastic body 48, and -
On the other hand, since the back side of the rubber elastic plate 48 receives air pressure due to the compression of the air in the air chamber 54 during such elastic deformation, the amount of elastic deformation is regulated by the applied air pressure. It becomes.

Therefore, when vibration is input between the first support metal fitting 10 and the second support metal fitting 12 to the engine mount including the partition member 38, the input vibration causes engine shake, bounce, etc. In the case of low-frequency, large-amplitude vibrations of around 10 Hz corresponding to the The amount of fluid flowing through the orifice passage 58 between the balance chamber 42 and the balance chamber 42 can be effectively ensured, and the high damping effect based on the resonance effect of the fluid can be effectively exhibited. .

On the other hand, if the input vibration is a high-frequency, small-amplitude vibration that substantially closes the orifice passage 58, the internal pressure fluctuations generated in the pressure receiving chamber 40 are small;
Since this can be absorbed by the elastic deformation of the rubber elastic plate 48, an increase in internal pressure within the pressure receiving chamber 40 is avoided, and the mount can advantageously have a low dynamic spring. In particular, since the air pressure acting on the rubber elastic plate 48 is inversely proportional to the volume inside the air chamber 54, when the amount of deformation is small, soft spring characteristics can be advantageously exhibited. This makes it possible to extremely effectively reduce the spring movement of the mount.

As is clear from the above description, in this embodiment, the hydraulic pressure absorption mechanism is created by the rubber elastic plate 48, the metal fitting 52, and the air chamber 54 defined between these members, which constitute the partition member 38. is configured.

In addition, as described above, the volume of the air chamber 54 is set to such an extent that it does not absorb internal pressure fluctuations generated within the pressure receiving chamber 54 when vibration is input in a frequency range that requires high damping characteristics.
While this can prevent deformation of the rubber elastic plate 48, when vibration is input in a frequency range that requires low dynamic spring characteristics, the rubber elastic plate 48 can sufficiently absorb the increase in internal pressure caused in the pressure receiving chamber 54. The setting is made by comprehensively considering the characteristics of the input vibration, the area of the rubber elastic plate 48, the elastic modulus, the volume inside the pressure receiving chamber 40, etc., so as to allow sufficient deformation.

Incidentally, in the engine mount according to the present embodiment, an umbrella fitting 60 having a substantially bottomed cylindrical shape is further accommodated in the pressure receiving chamber 40 . This umbrella fitting 60 has a stepped cylindrical shape consisting of a small diameter part 62 and a large diameter part 64, and is caulked and fixed to the support part 14 of the first support fitting 10 on the small diameter part 62 side. Particularly, it is disposed in such a manner that it opens toward the second support fitting 12 side. The inside of the pressure receiving chamber 40 is approximately divided into two chambers located on both sides in the vibration input direction with the full metal fittings 60 in between, and the large diameter portion 64 of the full metal fittings 60 is divided into two chambers located on both sides in the vibration input direction. Outer surface and pressure receiving chamber 4
An annular narrowed portion 66 is formed between the inner circumferential surface of 0 and the divided chambers to communicate with each other.

Further, in the opening of the large diameter portion 64 of the full fitting 60, an annular plate-shaped annular rubber 72 is integrally provided with a mounting ring 70 on the outer peripheral edge and a mass ring 6 day on the inner peripheral edge. is attached by press-fitting the mounting ring 70 into the large diameter portion 64, and the small diameter portion 62 of the entire metal fitting 60 is provided with a plurality of through holes 74, thereby, Inside the metal fittings 60,
A flow path is formed that communicates the two divided chambers partitioned by the metal fittings 60 with each other.

That is, by disposing all the metal fittings 60 in the pressure receiving chamber 40, the first and second supporting metal fittings 10
．． When vibration is input to the space between 12 and 12, all the metal fittings 60 are moved in the vibration input direction within the pressure receiving chamber 40, and between the divided chambers formed on both sides of the all metal fittings 60,
Fluid flow is caused through the constriction 66 and the interior of the fitting 60, respectively.

As a result, the resonance effect of the fluid flowing through the narrowed portion 66, the damper effect of the mass ring 68 disposed at the opening of the metal fitting 60, and the resonance effect of the fluid flowing inside the mass ring 68. Due to the synergistic effect of the above, a low dynamic spring effect can be exerted against input vibrations in a predetermined high frequency range.

In particular, in this embodiment, the low motion spring effect due to the resonance effect of the fluid within the narrowed portion 66, the damper effect of the mass ring 68, and the synergistic effect of the resonance effect of the fluid within 6 days of the mass ring reduce the low motion. The spring effects are respectively set in frequency ranges higher than the frequency range in which the low motion spring effect due to the hydraulic pressure absorption mechanism as described above can be exhibited, and in different frequency ranges from each other.

Furthermore, in the engine mount according to the present embodiment, the outer contact portion 28 of the cylindrical metal fitting 24 constituting the second support metal fitting 12 is able to resist vibrations with respect to the extending portion 13 of the first support metal fitting IO. They are arranged facing each other at a predetermined distance in the input direction, and by contacting the extension portion 13, excessive displacement in the bounding direction at the time of vibration input can be restricted, and all the metal fittings 60 The large diameter portion 64 is arranged to face the inner abutting portion 26 of the cylindrical metal fitting 24 at a predetermined distance in the vibration input direction, and by contacting the inner abutting portion 26, a rebound occurs when vibration is input. Excessive displacements in direction can be regulated.

Therefore, in the engine mount having the above-described structure, due to the resonance effect of the fluid flowing in the orifice passage 58, a high damping effect can be exhibited when vibration is input in a low frequency range, and the orifice passage 5
When vibration is input in a frequency range higher than the frequency to which 8 is tuned, a low dynamic spring effect can be exerted based on the elastic deformation of the rubber elastic plate 48 constituting the hydraulic pressure absorption mechanism, and thus a wide frequency range can be achieved. This means that good vibration damping characteristics can be exhibited over the entire period.

In particular, this liquid pressure absorption mechanism has an extremely simple structure in which an air chamber 54 is defined between the rubber elastic plate 48 and the lid fitting 52, so that , imparting the excellent anti-vibration properties as described above,
This can be advantageously realized with good manufacturability and low cost.

In addition, in such a hydraulic pressure absorption mechanism, the rubber elastic plate 48
Since the amount of deformation of the rubber elastic plate 48 is regulated by increasing the air pressure within the air chamber 54 on the back surface thereof, excessive deformation of the rubber elastic plate 48 can be completely prevented and sufficient durability can be achieved. At the same time, there is no occurrence of tapping sounds or the like when the deformation is restricted.

Furthermore, in the engine mount of this embodiment, since the hydraulic pressure absorption mechanism is configured as a partition wall member 38 that partitions the pressure receiving chamber 40 and the equilibrium chamber 42, an increase in the number of parts can be effectively suppressed. It also has the advantage of being able to be used.

Furthermore, the engine mount in this embodiment has a metal fitting 60 that partitions the inside of the pressure receiving chamber 40 into two divided chambers, and a narrow portion 6 created between the divided chambers.
The fluid flow through the mass ring 6 and the fluid flow through the inner hole of the mass ring 6 can also reduce the spring movement of the mount when vibration is input in a high frequency range, resulting in even better protection. This means that a vibration effect can be exerted.

Although one embodiment of the present invention has been described in detail above, this is a literal illustration, and the present invention is not to be construed as being limited only to this specific example.

For example, the specific structure of the hydraulic pressure absorption mechanism is by no means limited to that of the embodiment described above, and the pressure receiving chamber (40
) A structure comprising a flexible membrane on at least a part of the area exposed within the liquid pressure and to which the liquid pressure is applied, and a sealed air chamber with a predetermined volume behind the flexible membrane. Specifically, it is possible to arrange a hydraulic pressure absorption mechanism on the inner circumferential surface of the cylindrical metal fitting 24, and furthermore, it is possible to use a hollow member formed entirely of a rubber elastic body. It is also possible to configure a hydraulic pressure absorption mechanism by arranging the hollow member within the pressure receiving chamber (40).

Further, in the fluid-filled mount device according to the present invention, the pressure receiving chamber (40) and the equilibrium chamber (42) are separated from each other by the partition member (3).
It is not necessarily necessary that the pressure receiving chamber and the equilibrium chamber be located opposite each other with the space 8) in between, and it is also possible to install the pressure receiving chamber and the equilibrium chamber at separate positions.

Furthermore, the specific structure of the ori-free passageway (58) that communicates the pressure receiving chamber (40) and the equilibrium chamber (42) is not limited, and the vibration isolation required for the intended mounting device is not limited. The shape, including its length and cross-sectional area, should be changed as appropriate depending on the characteristics.

Further, in the present invention, all the metal fittings (60) arranged in the pressure receiving chamber (40) are not an essential requirement, and all the metal fittings (60) can be optionally provided depending on the required vibration-proofing characteristics. It is set.

In addition, although the embodiment described above shows an example in which the present invention is applied to an automobile engine mount, the present invention can also be advantageously applied to mounting devices for various other mechanical devices. Of course there is.

In addition, although not listed, the present invention can be implemented in embodiments with various changes, modifications, improvements, etc. added based on the knowledge of those skilled in the art, and such embodiments are not limited to the present invention. It goes without saying that any of these are included within the scope of the present invention as long as they do not depart from the spirit of the invention.

(Effects of the Invention) As is clear from the above description, in the fluid-filled mount device structured according to the present invention, when a low frequency and large amplitude vibration is input, the flexible As the deformation of the flexible membrane is regulated by the pressure within the air chamber applied to the back surface of the flexible membrane, the function of the hydraulic pressure absorption mechanism is substantially inhibited, and internal pressure fluctuations within the pressure chamber are prevented. can be effectively generated, so that the vibration damping effect due to the resonance effect of the fluid flowing in the orifice passage can be well exhibited.On the other hand, when high frequency and small amplitude vibration input is applied, Based on the elastic deformation of the flexible membrane allowed by the change, the hydraulic pressure absorption mechanism is activated, eliminating the increase in internal pressure in the pressure receiving chamber, and effectively reducing the dynamic spring characteristics of the mount. This is something that can be achieved.

In addition, such a liquid pressure absorption mechanism can be constructed with a simple structure in which an air chamber of a predetermined volume is formed behind a flexible membrane to which the liquid pressure in the pressure receiving chamber is applied. A mounting device having such excellent vibration damping properties can be advantageously provided with good manufacturability and low cost.

Furthermore, in such a hydraulic pressure absorption mechanism, since the deformation of the rubber elastic plate 48 is restricted by air pressure, excessive deformation thereof is advantageously prevented, and sufficient durability can be exhibited. , there is no occurrence of tapping sounds or the like when the deformation is restricted.

[Brief explanation of the drawing]

FIG. 1 is a vertical cross-sectional explanatory view showing an example of an integrated engine mount having a structure according to the present invention, and is a view corresponding to the I-1 cross section in FIG. FIG. Also, Figure 3 shows the first
FIG. 3 is an exploded explanatory view for explaining the structure of a partition member that constitutes the engine mount shown in the figure. Furthermore, the fourth
1 is a longitudinal sectional view corresponding to FIG. 1, showing the mounted state of the engine mount shown in FIG. 1. 52: Mold fitting 58 Niorifice passage: Air chamber

Claims (1)

[Scope of Claims] A first support metal fitting and a second support metal fitting arranged at a predetermined distance from each other are integrally connected by a rubber elastic body, while the first support metal fitting and the second support metal fitting are integrally connected by a rubber elastic body. A pressure-receiving chamber filled with a predetermined incompressible fluid and into which vibrations to be damped are input, and a variable-volume equilibrium at least partially defined by an elastic thin film are provided between the support fittings of the In the fluid-filled mounting device, the fluid-filled mount device is provided with an orifice passage that forms a chamber and communicates the pressure receiving chamber and the equilibrium chamber with each other, wherein at least a portion of the portion to which the liquid pressure is applied in the pressure receiving chamber is flexible. The flexible membrane has a membrane and a sealed air chamber of a predetermined volume behind the flexible membrane, and when an internal pressure fluctuation occurs in the pressure receiving chamber, the flexible membrane changes in volume of the air chamber. A fluid-filled mount device characterized in that a fluid pressure absorption mechanism that causes elastic deformation is disposed within the pressure receiving chamber.