JPH01193425A - Liquid-in type mounting device - Google Patents

Abstract

PURPOSE:To display excellent vibration isolating effect to input vibration included within a wide frequency range by tuning a movable part held by the first and the second throttling passage and a backlash keeping mechanism to low, medium and high frequencies respectively, and a movable means in the frequency higher than the second throttling passage. CONSTITUTION:Movable parts of the first partitioning member 34 held between the first and the second throttling passage 56, 74, and inner peripheral edges of ring-shaped fittings 44, 46 are tuned to low, medium and high frequencies respectively, and a movable means 70 is tuned in the frequency higher than the second throttling passage 74. Input vibrations having the low frequency and large amplitude, and the medium frequency and small amplitude respectively can therefore be excellently damped and cut off on the basis of the liquid resonating action of incompressible fluid flowing through the first and the second throttling passage 55, 74, and the input vibration having the high frequency and minute amplitude can be excellently cut off on the basis of the displacement of the movable part of the first partitioning member 34. Thus excellent vibration isolating effect can be displayed to the input vibration included within a wide frequency range.

Description

DETAILED DESCRIPTION OF THE INVENTION (Technical Field) The present invention relates to a fluid-filled mount device such as an automobile engine mount, and particularly to a fluid-filled mount device for an automobile engine mount, etc. The present invention relates to a fluid-filling mount device that can exhibit a blocking effect.

(Prior Art) Mounting devices such as automobile engine mounts are generally required to exhibit a good damping effect against input vibrations of low frequency and large amplitude, and are also required to exhibit a good damping effect against input vibrations of medium frequency and small amplitude and high frequency minute vibrations. It is required to exhibit a good blocking effect against high-amplitude input vibrations, and in particular, a good damping effect is required against low-frequency, large-amplitude input vibrations. Therefore, in recent years, as such a mounting device, a first support body and a second support body are arranged at a predetermined distance from each other in the vibration input direction; a rubber elastic body that is elastically connected;
A partition member, at least a part of which is formed of a predetermined flexible membrane, is disposed on the second support side and forms a fluid accommodation space which is partially defined by the rubber elastic body. ; a predetermined incompressible fluid sealed within the fluid storage space;
a partition member disposed on the second support body side and partitioning the fluid accommodation space into a pressure receiving chamber on the rubber elastic body side and an equilibrium chamber on the partition wall member side; and communicating the pressure receiving chamber and the equilibrium chamber with each other. A so-called fluid-filled mounting device has been proposed, which is equipped with a constriction passageway that restricts the flow of air.

According to the fluid-filled mounting device having such a structure, input vibrations in a frequency range set for the throttle passage can be effectively damped based on the liquid column resonance effect of the incompressible fluid flowing through the throttle passage. By tuning the throttle passage to a low frequency, it is possible to satisfactorily attenuate low frequency, large amplitude input vibrations.

However, in a fluid-filled mounting device with such a structure, as mentioned above, although low-frequency large-amplitude input vibrations can be well damped by tuning the throttle passage to a low frequency, medium-frequency In response to input vibrations of small amplitude and high frequency minute amplitude, there is a problem in that the incompressible fluid becomes difficult to flow through the throttle passage, and the vibration damping function (blocking function) is rather deteriorated.

On the other hand, in a fluid-filled mounting device having the structure described above, the partition member is deformed or displaced by a predetermined dimension in the vibration input direction so as to absorb the fluid pressure difference between the pressure receiving chamber and the equilibrium chamber. A fluid-filled mounting device has been proposed that may include a movable means. According to the fluid-filled mount device having such a structure, based on the fact that the movable means is deformed or displaced in the vibration input direction, it is possible to effectively block input vibration in a frequency range set for the movable means. By tuning the movable means to a medium frequency or high frequency, small amplitude vibrations in the medium frequency range or minute amplitude vibrations in the high frequency range corresponding to the tuning frequency of the movable means can be effectively blocked. It is possible.

(Problem) However, even in a fluid-filled mounting device with such a structure, large amplitude vibrations in the low frequency range set for the throttle passage, and small amplitude vibrations in the medium frequency range set for the movable means. Although it can exhibit a good vibration isolation effect (damping or blocking effect) for either small amplitude vibrations in the high frequency range, small amplitude vibrations in the medium frequency range or small amplitude vibrations in the high frequency range. Regarding the other one, there was a problem that a good blocking effect could not be exhibited.

(Solution Means) Against this background, the present invention provides a fluid-filled mount device that can satisfactorily attenuate or block input vibrations of low frequency large amplitude, medium frequency small amplitude, and high frequency minute amplitude. The purpose of this project is to provide a fluid-filled mounting device with (a)
first and second supports disposed at a predetermined distance from each other in the vibration input direction; and (b) a rubber elastic body elastically connecting the first support and the second support. and (c
) A partition member, at least a part of which is formed of a predetermined flexible membrane, is disposed on the second support side and forms a fluid accommodation space which is partially defined by the rubber elastic body. and (d
) a predetermined incompressible fluid sealed in the fluid accommodation space; (e) a predetermined incompressible fluid sealed in the fluid accommodation space; (f) a second partition member disposed on the first partition member and forming an intermediate chamber between the first partition member; (g) a first throttle passage provided to allow the pressure receiving chamber and the equilibrium chamber to communicate with each other; and (h) a first restricting passage provided to allow the first partition member to absorb a fluid pressure difference between the chambers on both sides thereof. (i) a movable means provided to be capable of deforming or displacing a predetermined dimension in the vibration input direction; and (i) a movable means provided to allow chambers on both sides of the second partition member to communicate with each other. (j) at least a portion of the first partition member where the second partition member is disposed so as to absorb a fluid pressure difference between the pressure receiving chamber and the equilibrium chamber; The present invention is configured to include a backlash holding mechanism that holds the second support body such that it can be displaced by a predetermined dimension in the vibration input direction.

(Function/Effect) According to the fluid-filled mount device having such a structure, like the conventional fluid-filled mount device, by tuning the first throttle passage to a low frequency, the first throttle passage Based on the liquid column resonance effect of the flowing incompressible fluid, large amplitude vibrations in the low frequency range can be well damped.

Further, according to such a fluid-filled mounting device, the incompressible fluid is caused to flow through the second throttle passage based on the deformation or displacement of the movable means, so that the second throttle passage is tuned to a medium frequency. At the same time, by tuning the movable means to a higher frequency, it is possible to induce liquid column resonance in the incompressible fluid flowing through the second throttle passage when vibrations in the medium frequency range are input. Based on the liquid column resonance effect, small amplitude vibrations in the medium frequency range can be effectively blocked.

Further, in such a fluid-filled mounting device, the portion of the first partition member where at least the second partition member is disposed is held by the backlash holding mechanism so as to be able to be displaced by a predetermined dimension in the vibration input direction. Since the incompressible fluid is substantially caused to flow between the pressure receiving chamber and the equilibrium chamber based on the displacement of the movable part of the first partition member that moves, the movement of the first partition member By tuning the part to a high frequency higher than the tuning frequency of the second throttle passage, an incompressible part that flows with the displacement of the movable part of the second partition member when vibrations in a high frequency range are input. It is possible to induce liquid column resonance in the fluid, and based on the liquid column resonance effect, minute amplitude vibrations in a high frequency range can be effectively blocked.

That is, according to the fluid-filled mounting device according to the present invention, the first throttle passage, the second throttle passage, and the movable portion of the first partition member held by the backlash retaining mechanism are controlled at low frequency and medium frequency, respectively. by tuning the movable means to a higher frequency than the tuning frequency of the second throttle passage;
Based on the liquid column resonance effect of the incompressible fluid flowing through the first throttle passage and the second throttle passage, input vibrations of low frequency, large amplitude, and medium frequency, small amplitude can be well damped and blocked, respectively. In addition, based on the displacement of the movable part of the first partition member, input vibrations with high frequency and minute amplitude can be effectively blocked, and input vibrations with a wider frequency range can be blocked than with conventional fluid-filled mounting devices. In contrast, it is possible to exhibit a good vibration isolation effect (damping or blocking effect).

(Example) Hereinafter, in order to clarify the present invention more specifically,
One embodiment thereof will be described in detail based on the drawings.

First, FIG. 1 shows an example of an engine mount for an automobile, which is an embodiment of a fluid-filled mount device according to the present invention. Here, reference numerals 10 and 12 denote first and second support fittings as first and second supports, respectively, which are arranged at a predetermined distance apart in the vibration input direction (vertical direction in the figure). has been done.

The first support fitting 10 has a thick disk shape with a relatively small diameter, and is arranged so that its center line is in the vibration input direction. On the other hand, the second support fitting 12 has a relatively large diameter bag-like structure in which an opening fitting 16 is integrally caulked and fixed to the opening of the bottom fitting 14, and the inner space thereof is the first support fitting 12. The first support metal fitting 1 is opened on the support metal fitting 10 side of the first support metal fitting 1.
It is placed concentrically with 0. Here, the annular rubber elastic body 18 fluid-tightly closes the opening of the second support fitting 12, and the outer circumference of the first support fitting 10 and the second supporting metal fittings 12
It is integrally vulcanized and bonded to the inner circumferential surface of the opening.
As a result, the first support metal lO and the second support metal fitting 12
and are elastically connected by a rubber elastic body 18.

In addition, in FIG. 1, 20 is a mounting bolt erected on the first support metal fitting 10, and 22, 22 is a mounting bolt erected on the bottom metal fitting 14 of the second support metal fitting 12. . The engine mount of this embodiment is attached to the vehicle body side or the engine side by the mounting bolts 20 of the first support metal fittings 10, while the second support metal fittings 1
It is attached to the engine side or the vehicle body side by two mounting bolts 22 and 22, so that the engine or the power unit including the engine is supported against the vehicle body in a vibration-proof manner.

Further, in FIG. 1, reference numeral 24 denotes an annular reinforcing metal fitting embedded in the rubber elastic body 18 concentrically with the rubber elastic body 18.

The second support fitting 12 has a diaphragm 26 as a partition member made of a rubber elastic membrane (flexible membrane), the outer peripheral edge of which is fluid-tightly held between the bottom metal fitting 14 and the opening metal fitting 16. is installed.

As a result, a portion of the rubber elastic body 1 is disposed between the diaphragm 26 and the first support fitting 10.
A sealed space as a fluid storage space defined by 8 is formed, and a predetermined incompressible fluid such as water or polyalkylene glycol is sealed in this sealed space. Note that the space between the diaphragm 26 and the bottom metal fitting 14 is
An air chamber 28 is provided to allow the diaphragm 26 to deform.

Similarly to the diaphragm 26, the second support fitting 12 has an annular outer portion 30 and an annular outer portion 30, the outer peripheral edge of which is fluid-tightly held between the bottom fitting 14 and the opening fitting 16. A first partition member 34 consisting of an inner portion 32 surrounded by It is partitioned into an equilibrium chamber 38 on the 26 side. And here, such a first partition member 3
A second partition member 40 is disposed on the surface of the inner portion 32 of 4 on the equilibrium chamber 38 side, and this second partition member 40
and the inner portion 32 of the first partition member 34.
2 is formed.

The outer portion 30 of the first partition member 34 includes two annular metal fittings 44. which are overlapped with their outer peripheral edges in close contact with each other.
46, and the overlapping portion of the outer peripheral edges of these annular fittings 44 and 46 is connected to the bottom fitting 14 and the opening fitting 16.
The second support fitting 12 is fluid-tightly sandwiched between the second support fitting 12 and the second support fitting 12 in a fixed position. Further, the annular metal fittings 44 and 46 constituting the outer portion 30 are brought into close contact with each other at a radially intermediate portion that is a predetermined distance from the contact portion of the outer peripheral edge. As a result, an annular space 48 extending in two circumferential directions is formed between the close contact portions of the annular metal fittings 44 and 46.
An annular groove 50 having a predetermined width and opening radially inward is formed between the inner circumferential edges of 4.46 mm.

Here, the annular space 48 is connected to each annular metal fitting 4.
The pressure receiving chamber 36 and the equilibrium chamber 38 are communicated with each other through communication holes 52.54 formed in 4.46. A passage 56 is formed.

When vibration is input between the first support fitting 10 and the second support fitting 12 and a fluid pressure difference is induced between the pressure receiving chamber 36 and the equilibrium chamber 38, the pressure receiving chamber 36 and the equilibrium chamber 38
The incompressible fluid within the first constriction passage 56 can be caused to flow into each other through the first constriction passage 56.
Based on the liquid column resonance effect of the incompressible fluid flowing through the first throttle passage 56, input vibrations in the frequency range set for the first throttle passage 56 can be effectively damped. -ing

Note that, here, the first throttle passage 56 is 5 to 1
The engine is tuned to a low frequency corresponding to a low frequency range of about 5 Hz, and based on the liquid column resonance effect of the incompressible fluid flowing through the first throttle passage 56, the engine frequency of about 5 to 15 Hz is tuned. Input vibrations in the low frequency range, such as shakes, are effectively damped.

On the other hand, the inner portion 32 of the first partition member 34 has an outwardly facing flange portion 58 at the opening, and a bottomed cylindrical fitting 60 arranged to open toward the equilibrium chamber 38 side, and a cylindrical fitting 60 with a bottom at the peripheral edge. It consists of a circular metal fitting 64 that is fixed to the inner peripheral surface of the bottomed cylindrical part of the bottomed cylindrical metal fitting 60 and forms a disc-shaped space 62 with a predetermined gap between it and the bottom wall of the bottomed cylindrical metal fitting 60. There is. As shown in the figure, this inner portion 32 is arranged such that the flange portion 58 of the bottomed cylindrical fitting 60 is inserted into the annular groove 50 of the outer portion 30.
It is configured to be able to move (displace) relative to the outer portion 30 by a predetermined distance α in the vibration input direction. Pressure receiving chamber 3
When a fluid pressure difference is induced between 6 and the equilibrium chamber 38, the inner portion 32 is moved in the direction of absorbing the fluid pressure difference.
The inner portion 32 can be displaced by a distance α, and as the inner portion 32 is displaced, the incompressible fluid is substantially caused to flow between the pressure receiving chamber 36 and the equilibrium chamber 38. There is. Note that on both sides of the flange portion 58 of the bottomed cylindrical metal fitting 60, annular metal fittings 44.
An annular cushioning rubber layer 65, 65 is provided to cushion the impact upon contact with 46.

Further, the second partition member 40 is fixed to the inner circumferential surface of the bottomed cylindrical portion of the bottomed cylindrical fitting 60 at a further fixed distance from the circular fitting 64, thereby making it circular. The intermediate chamber 42 is formed between the metal fitting 64 and the metal fitting 64 .

Here, the bottom wall of the bottomed cylindrical fitting 60 and the circular fitting 64 defining the disk-shaped space 62 of the inner portion 32 are in a state in which the disk-shaped space 62 is communicated with the pressure receiving chamber 36 and the intermediate chamber 42, respectively. , each of the plurality of communication holes 66.6
8 is formed.

In addition, in the disc-shaped space 62, the pressure receiving chamber 36 and the intermediate chamber 42 are cut off, and the inner portion 32 is moved in the vibration input direction by a distance β greater than the movable distance α. A disc-shaped movable plate 70 is disposed as a movable means made of a rubber material or the like in a movable state. As a result, when a fluid pressure difference is generated between the pressure receiving chamber 36 and the intermediate chamber 42, the movable plate 70 can move by a distance β in the direction of absorbing the fluid pressure difference. There is.

Further, the second partition member 40 that forms the intermediate chamber 42 with the circular metal fitting 64 is integrally provided with a cylindrical portion 72 extending toward the equilibrium chamber 38 at its center.
The equilibrium chamber 38 and the intermediate chamber 42 are communicated with each other through the inner hole. Here, the inner hole of the cylindrical portion 72 is used as the second throttle passage 74, and when a fluid pressure difference is caused between the equilibrium chamber 38 and the intermediate chamber 42, the inner hole of the cylindrical portion 72 is The incompressible fluids within 42 are allowed to flow into each other through the second constriction passage 74.

Here, the tuning frequency of the second throttle passage 74 is set to a lower frequency than the tuning frequency of the movable plate 70, and the tuning frequency of the inner portion 32 of the first partition member 34 is set to a lower frequency. The frequency is set to be higher than the tuning frequency of the second throttle passage 74, so that the input vibration in the frequency range corresponding to the tuning frequency of the second throttle passage 74 and the inner portion 32 of the first partition member 34 are Input vibrations in a frequency range corresponding to the tuning frequency of the tuning frequency are both effectively blocked.

If the tuning frequency of the second throttle passage 74 is set to a lower frequency than the tuning frequency of the movable plate 70, even when vibration is input in the frequency range corresponding to the tuning frequency of the second throttle passage 74, the movable plate 7
0 is smoothly moved in the vibration input direction, and based on the movement of the movable plate 70, the incompressible fluid is effectively caused to flow into the second throttle passage 74. Therefore, when vibration is input in a frequency range corresponding to the tuning frequency of the second throttle passage 74, liquid column resonance is induced in the incompressible fluid flowing through the second throttle passage 74, and the liquid column resonates. Based on the resonance effect, input vibrations in a frequency range corresponding to the tuning frequency of the second throttle passage 74 are effectively blocked.

Furthermore, if the tuning frequency of the inner portion 32 of the first partition member 34 is set to a higher frequency than the tuning frequency of the second throttle passage 74, when vibration is input in a frequency range corresponding to the tuning frequency of the inner portion 32, Since the incompressible fluid becomes difficult to flow through the second throttle passage 74, the inner portion 32 is effectively moved in response to the vibration input, and the movement of the inner portion 32 causes the pressure receiving chamber to A substantially incompressible fluid is caused to flow between 36 and balance chamber 38.

Therefore, when vibration is input in a frequency range corresponding to the tuning frequency of the inner part 32, liquid column resonance is induced in the incompressible fluid caused to flow by the movement of the inner part 32, and this liquid column resonance Based on this action, input vibrations in a frequency range corresponding to the tuning frequency of the inner portion 32 are effectively blocked.

Note that here, the second throttle passage 74 has a width of 20 to 50
The inner portion 32 of the first partition member 34 is tuned to correspond to a medium frequency range of about Hz, and the inner portion 32 of the first partition member 34 is
It is tuned to correspond to a high frequency range of about 00 to 300 Hz, and based on the liquid column resonance effect of the incompressible fluid flowing through the second throttle passage 74,
Small amplitude vibrations in the medium frequency range, such as idle vibrations of about 50H2, can be effectively blocked, and
Based on the movement of the inner portion 32 of the first partition member 34 in the vibration input direction, input vibration in a high frequency range such as engine transmitted sound of about 100 to 300 H2 is effectively blocked.

Further, the movable distance of the inner portion 32 of the first partition member 34: α and the movable distance of the movable plate 70: β are respectively set for the inner portion 32 (
It is set in accordance with the magnitude of the vibration amplitude in the tuned frequency range (tuned) and the magnitude of the vibration amplitude in the frequency range set for the second throttle passage 74,
Generally, within the range of 0.1 to 0.5 and 0.3
They will each be set within a range of about 1.2 cranes.

Furthermore, as is clear from the above description, in this embodiment, the inner peripheral edge portions of the annular metal fittings 44 and 46 that hold the flange portion 58 of the bottomed cylindrical metal fitting 60 constitute a backlash holding mechanism.

As explained above, according to the engine mount of this embodiment, based on the liquid column resonance effect of the incompressible fluid flowing through the first throttle passage 56, large low-frequency waves such as engine shake of about 5 to 15 Hz can be suppressed. The amplitude vibration can be well damped, and it is based on the liquid column resonance effect of the incompressible fluid flowing through the second throttle passage 74 and the movement (displacement) of the first partition member 34 in the vibration input direction. , respectively, 20 to 5
Medium frequency small amplitude vibration around 0Hz and 100~300H
It can effectively block high-frequency, minute amplitude vibrations of about 2.2 degrees, and it can exhibit good vibration isolation effects against input vibrations in a wider frequency range than conventional fluid-filled engine mounts. be.

Next, another example of the automobile engine mount according to the present invention will be explained based on FIG. 2. Note that the engine mount of this example is different from the engine mount of the previous example.
The only difference is the structure of the first partition member, and the other structures are substantially the same as those in the previous embodiment. Therefore, only the structure of the first partition member will be described in detail, and the other structures will not be described in detail. The explanation will be omitted.

That is, in the engine mount shown in FIG. 2, the two annular metal fittings are fluid-tightly sandwiched between the bottom metal fitting 14 and the opening metal fitting 16 of the second support metal fitting 12 at their overlapping outer peripheral edges. An annular groove 50 having a predetermined width and opening radially inward is formed between the inner peripheral edges of these annular fittings 76 and 78. The first partition member 82 is disposed with its outer peripheral edge protruding into and housed in the annular groove 50.
As a result, when a fluid pressure difference is generated between the pressure receiving chamber 36 and the equilibrium chamber 38, the first partition member 82 is moved between the position where it abuts the annular metal fitting 76 and the position where it abuts the annular metal fitting 78. It is configured to be able to move by a distance α in the vibration input direction. Here, the inner circumferential edges of the annular fittings 76 and 78 constitute a backlash holding mechanism, and this backlash holding mechanism holds the entire first partition member 82 movably in the vibration input direction. Because there is, there is.

In addition, on both sides of the outer peripheral edge of the first partition member 82 held between the annular fittings 76 and 78, cushioning rubber layers 65° 65 similar to those in the previous embodiment are provided. .

By the way, the first partition member 82 has two partition fittings 84.
．． It has a structure in which 86 are overlapped, and on its outer periphery, with partition fittings 84 and 86 defined,
An annular space 48 similar to the previous embodiment is formed. Here, the annular space 48 is divided into each partition fitting 84.
．． Pressure receiving chamber 3 through communication hole 88.90 formed in 86
6 and the equilibrium chamber 38, thereby forming a first throttle passage 56 similar to that of the previous embodiment.

Further, in the center of the first partition member 82, similar to the annular space 48, partition fittings 84 and 86 are defined.
A disk-shaped space 62 similar to that of the previous embodiment is formed,
In this disc-shaped space 62, a movable plate 7o similar to that of the previous embodiment is housed so as to be movable by a distance β in the vibration input direction.

This disk-shaped space 62 is connected to the pressure receiving chamber 36 and the intermediate chamber 4 formed on both sides of the disk-shaped space 62 through a plurality of communication holes 92, 94 formed in the partition fittings 84 and 86.
2 is communicated with.

Here, the intermediate chamber 42 is connected to the partition fitting 86.
and a second partition member 40 similar to the embodiment described above, which is fixed to this partition fitting 86, and is formed as an inner hole of the cylindrical portion 72 of this second partition member 40. The balance chamber 38 is communicated with the balance chamber 38 through a second throttle passage 74 .

Also in the engine mount having such a structure, the first throttle passage 56. The tuning frequencies of the second throttle passage 74 and the movable plate 70 are tuned to frequencies similar to those in the embodiment described above, and the tuning frequency of the first partition member 82 is adjusted to the inside of the first partition member 34 in the embodiment described above. By tuning to the same frequency as the portion 32, it is possible to obtain the same vibration-proofing function as the engine mount of the previous embodiment.

Although a few embodiments of the present invention have been described in detail above, these are literal illustrations, and it goes without saying that the present invention should not be interpreted as being limited to these specific examples.

For example, in the embodiment described above, the second partition members 40 were arranged on the surface of the first partition member 34, 82 on the equilibrium chamber 38 side; It is also possible to arrange it on the surface of one partition member 34.82 on the pressure receiving chamber 36 side.

Further, in the embodiment, a movable plate 70 disposed so as to be displaceable by a predetermined dimension in the vibration input direction with respect to the inner portion 32 of the first partition member 34 and the first partition member 82 is employed as the movable means. However, those first partition members 3
It is also possible to employ, as the movable means, a membrane member that is disposed so as to be deformable by a predetermined dimension in the vibration input direction with respect to the inner portion 32 of 4 and the first partition member 82.

Further, in the embodiment described above, an example was described in which the present invention was applied to an automobile engine mount, but the present invention can also be applied to mounting devices other than such automobile engine mounts.

In addition, although it is omitted to list specific examples one by one, the present invention can be implemented with various changes, modifications, improvements, etc. without departing from the spirit thereof.
It goes without saying.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal cross-sectional view showing one embodiment of the present invention, and FIG. 2 is a cross-sectional view of essential parts showing another embodiment of the present invention. 10: First support fitting (first support body) 12: Second support fitting (second support body) 18: Rubber elastic body 26; Diaphragm (flexible membrane; partition member) 30: Outer portion ( (of the first partition member) 32: Inner portion (of the first partition member) 34.82: First partition member 36: Pressure receiving chamber 38: Equilibrium chamber 40: Second partition member 42: Intermediate chamber 56: No. First throttle passage 70: Movable plate (movable means) 74: Second throttle passage 76.78: Annular metal fitting

Claims (1)

[Claims] First and second supports arranged at a predetermined distance from each other in the vibration input direction, and the first support and the second support are elastically connected. a rubber elastic body; and at least a portion of a predetermined flexible membrane, which is disposed on the second support side and forms a fluid accommodation space partially defined by the rubber elastic body. a predetermined incompressible fluid sealed in the fluid accommodation space; and a partition member disposed on the second support body side to connect the fluid accommodation space to the pressure receiving chamber on the rubber elastic body side. a first partition member that partitions into an equilibrium chamber on the partition wall member side; a second partition member that is disposed on the first partition member and forms an intermediate chamber between the first partition member; a first throttle passage provided so as to allow the pressure receiving chamber and the equilibrium chamber to communicate with each other; a movable means provided to be capable of deforming or displacing a predetermined dimension in the direction; a second throttle passage provided to the second partition member so as to allow chambers on both sides of the second partition member to communicate with each other; At least a portion of one partition member where the second partition member is disposed is arranged in the vibration input direction with respect to the second support so as to absorb a fluid pressure difference between the pressure receiving chamber and the equilibrium chamber. A fluid-filled mount device comprising: a backlash holding mechanism that holds the mount so that it can be displaced by a predetermined dimension.