JP2523237Y2 - Fluid-filled mounting device - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid-filled mounting device that obtains an anti-vibration effect based on a fluid flow action.
In particular, the present invention relates to a fluid-filled mounting device capable of switching and controlling vibration isolation characteristics exerted on the basis of a fluid flow action.

[0002]

2. Description of the Related Art Conventionally, as one type of vibration-proof connection or support device, a first mounting bracket and a second mounting bracket which are arranged at a predetermined distance from each other are connected by a rubber elastic body. A pressure receiving chamber in which a predetermined incompressible fluid is sealed and a vibration is input, and a balance chamber with a variable volume are formed between the two mounting brackets, and the pressure receiving chamber and the balance chamber are communicated with each other. With a structure that has an orifice passage,
A so-called fluid-filled mounting device is known. And
In such a fluid-filled mounting device, a vibration damping effect that cannot be obtained with a rubber elastic body can be easily obtained based on the resonance action of the fluid that is caused to flow in the orifice passage. It has come to be suitably used as a vibration isolator for automobiles and the like.

[0003] In an anti-vibration device for an automobile or the like in which such a fluid-filled mounting device is preferably used, a plurality of types of vibrations are input according to the running state of the vehicle and the like. For input vibration over
Various anti-vibration effects are required. For example, in the case of an engine mount for automobiles, in addition to the high damping effect for low frequency vibration such as a shake of about 10 Hz, and the low dynamic spring effect for medium frequency vibration corresponding to idling vibration of about 25 Hz, it is caused by engine vibration and the like. Therefore, a low dynamic spring effect is required for the high-frequency vibrations, and the high-frequency vibrations vary in frequency depending on the engine speed and the like. An effect is required.

However, in the fluid-filled mounting device as described above, the vibration damping effect due to the resonance action of the fluid can be effectively exerted only in a limited frequency range set in the orifice passage, and the setting thereof is also required. At the time of vibration input in a higher frequency range than the frequency, the flow resistance of the orifice passage is remarkably increased, so that a high dynamic spring is caused and the vibration damping effect is significantly reduced.

Therefore, in order to deal with such a problem,
Conventionally, (1) a structure in which the tuning frequency is variable by adjusting the opening degree (cross-sectional area) of one orifice passage (see Japanese Utility Model Publication No. 63-24004, etc.), and (2) cross-sectional area / length There has been proposed a structure in which two orifice passages having different sizes are provided in parallel, and these are switched by a valve means to be selectively opened (see Japanese Patent Application Laid-Open No. 58-54247).

However, as described in the above (1), it is extremely difficult to obtain a sufficient tuning width by merely changing the cross-sectional area of one orifice passage. That is, assuming that the cross-sectional area of the orifice passage is A and the length is L, the resonance frequency F of the fluid flowing inside the orifice passage is represented by F に て (A / L) ^1/2 , Even if the cross-sectional area of the passage: A is changed by a factor of four (or １ ／), the tuning frequency of the orifice passage can only be changed by a factor of two, and it is difficult to obtain an effective amount of change. Moreover, in order to enable tuning to a high frequency range, the length of the orifice passage: L needs to be set short. However, when tuning to a low frequency range, the cross-sectional area of the orifice passage: A is reduced. It must be extremely small, and it is difficult to secure a sufficient fluid flow amount, so that it is difficult to obtain a sufficient vibration damping effect.

[0007] As described in the above (2), by selectively operating the two orifice passages, only the two vibration-proof characteristics pre-tuned to each orifice passage are selectively exhibited. Therefore, as described above, if vibration isolation effects are required for input vibrations in three or more frequency ranges, satisfactory vibration isolation effects can be obtained for input vibrations in all of these frequency ranges. Was extremely difficult to obtain.

In short, conventionally, when a vibration damping effect is required for a plurality of input vibrations over a wide frequency range, such as in an engine mount for an automobile, the vibration damping effect based on the fluid flow action is effectively performed. It was difficult to obtain, and a fluid-filled mounting device that satisfies such anti-vibration characteristics has not yet been realized.

[0009]

Here, the present invention has been made in view of the above-mentioned circumstances, and a problem to be solved is that a plurality of vibration-suppressing characteristics can be switched over a wide frequency range. Provided is a fluid-filled mounting device having an improved structure, which can advantageously exert an anti-vibration effect based on the flow action of a fluid caused to flow through an orifice passage against input vibration. It is in.

[0010]

According to the present invention, in order to solve such a problem, first attached to members to be vibration-isolated and connected at a predetermined distance in a vibration input direction. The mounting bracket and the second mounting bracket are connected by a rubber elastic body interposed therebetween, and a part of a wall is formed by the rubber elastic body, so that an internal pressure fluctuation is caused at the time of vibration input. A pressure receiving chamber and an equilibrium chamber in which at least a part of the wall portion is formed of a flexible film and a volume change is easily allowed. A fluid-filled mounting device comprising a first orifice passage for communicating the pressure receiving chamber and the equilibrium chamber with each other while enclosing the fluid, and having a sectional area / length ratio greater than that of the first orifice passage. A second orifice passage having a larger A third orifice passage having a larger cross-sectional area / length ratio than the two orifice passages is provided in parallel with each other over the pressure receiving chamber and the equilibrium chamber. At the junction where the second orifice passage and the third orifice passage are respectively opened, the second orifice passage and the third orifice passage are slid on the opening wall surface to form the second orifice passage. Opening and closing the opening of the third orifice passage and selectively opening it, and providing a switching valve for adjusting the opening amount of at least the opening of the third orifice passage, This is the feature.

[0011]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, in order to clarify the present invention more specifically, embodiments of the present invention will be described with reference to the drawings.
It will be described in detail.

1 and 2 show an automobile engine mount as one embodiment of the present invention.
In these figures, reference numerals 10 and 12 denote a first mounting bracket and a second mounting bracket, respectively, which are opposed to each other with a predetermined distance therebetween. Further, the first mounting member 10 and the second mounting member 12 are formed by a main rubber 14 as a rubber elastic body interposed therebetween.
It is elastically connected. In such an engine mount, the first mounting bracket 10 and the second mounting bracket 12 are mounted on one of the vehicle body side and the power unit side, and are interposed between the vehicle body and the power unit. As a result, the power unit is supported on the vehicle body with vibration isolation. In such an engine mount in such a mounted state, the power unit weight is exerted on the engine mount in a substantially opposing direction (substantially up and down direction in FIG. 1) of the first and second mounting brackets 10 and 12, and the body rubber By elastically deforming 14, the two mounting brackets 10 and 12 are positioned close to each other by a predetermined distance, and mainly the first and second mounting brackets 10 and 12 are substantially opposed to each other. An anti-vibration effect is exerted against vibration input in the direction.

More specifically, the first mounting member 10 is formed in a disk shape. The first mounting member 10 has a support member 18 having a substantially bottomed cylindrical shape.
Are welded at the opening to protrude and fix on one surface. Furthermore, the first mounting bracket 10 projects to the opposite side from the supporting bracket 18,
A mounting bolt 20 is fixedly provided. The mounting bolt 20 allows the power unit to be mounted to a power unit (not shown).

On the other hand, the second mounting member 12 includes a cylindrical metal member 22 having a substantially cylindrical shape and a bottom metal member 24 having a substantially bottomed cylindrical shape. The cylindrical metal fitting 22 has a tapered portion 2 whose one side in the axial direction expands in diameter toward the outside in the axial direction.
6, and a caulking portion 28 is integrally provided at the other end in the axial direction. Further, a contact piece 29 protruding radially outward is fixed to an opening of the cylindrical metal fitting 22 on the side of the tapered portion 26. An outward flange 30 is formed integrally with the opening of the bottom fitting 24.

The caulking portion 28 of the cylindrical metal fitting 22 is caulked and fixed to the flange portion 30 of the bottom metal fitting 24, so that the second mounting fitting 12 has a substantially deep bottomed cylindrical shape as a whole. , Is formed. A mounting bolt 32 is fixed to the second mounting bracket 12 at the bottom of the bottom bracket 24 so as to protrude outward. The mounting bolt 32 allows the second mounting bracket 12 to be attached to a vehicle body (not shown). It has become.

Further, the first mounting member 10 and the second mounting member 12 are elastically connected to each other by a main rubber 14 in a state where they are opposed to each other with a predetermined distance therebetween. That is, the main rubber 14 is formed in a substantially truncated conical shape as a whole, and the first mounting bracket 10 is provided on the small-diameter side end surface, and the second mounting bracket 12 is provided on the large-diameter side end outer peripheral surface. It is formed as an integrally vulcanized molded product that is vulcanized and bonded. The opening of the second mounting member 12 is fluid-tightly covered by connecting the first mounting member 10 and the second mounting member 12 with the main rubber 14.

Further, a diaphragm 34 as a flexible film is provided inside the second mounting member 12 in this connection body.
Are accommodated. Such a diaphragm 34 is
As shown in the figure, a cylindrical metal fitting 38 provided with an outward flange portion 36 at one axial end is vulcanized and bonded so as to cover an opening at the other axial end. The flange portion 36 is attached to the second mounting member 12 by being clamped at a caulking portion between the tubular metal member 22 and the bottom metal member 24. That is, thereby, the inside of the second mounting bracket 12 covered with the main rubber 14 is
The diaphragm 34 is fluid-tightly partitioned between the first fitting 10 and the bottom fitting 24.

On the first mounting member 10 side of the diaphragm 34, a fluid chamber in which a predetermined incompressible fluid is sealed is formed. On the other hand, the diaphragm 34
An air chamber 40 that allows the diaphragm 34 to deform is formed on the opposite side of the fluid chamber with respect to the fluid chamber.

The fluid sealed in the fluid chamber includes, for example, water, alkylene glycol, polyalkylene glycol, silicone oil, and a mixture thereof.
It is preferably used. Further, such filling of the fluid is advantageously performed, for example, by caulking and fixing the cylindrical fitting 22 constituting the integrally vulcanized molded product to the flange portion 30 of the bottom fitting 24 in the fluid. obtain.

Further, a partition member 42 is provided in the fluid chamber.
Are accommodated. The partition member 42 has a substantially thick disk shape as a whole, and has an upper recess 52 opening toward the pressure receiving chamber 44 and a balancing chamber 4 in a substantially central portion thereof.
A lower recess 54 opening to the sixth side is provided. Also, on the surface where the upper recess 52 opens,
A thin disk-shaped lid fitting 48 is overlapped. In addition, the partition member 42 includes an annular supporting portion 55 protrudingly formed on an outer peripheral edge thereof, together with the lid fitting 48, and the cylindrical fitting 2.
The second fitting 12 is fixed to the second fitting 12 by being clamped between the caulking portions of the second fitting 2 and the bottom fitting 24.

Thus, the fluid chamber is divided into two on both sides of the partition member 42. Thus, on the side of the first mounting member 10 with respect to the partition member 42, a part of the wall portion is formed of the main body rubber 14, and the pressure receiving chamber 44 in which the internal pressure fluctuation is caused at the time of vibration input is formed. ing. On the other hand, on the side opposite to the pressure receiving chamber 44 with the partition member 42 therebetween, an equilibrium chamber 46 in which a part of the wall is constituted by the diaphragm 34 and whose volume change is easily allowed is formed.

The partitioning member 42 has a first orifice passage 50 at its outer peripheral edge, which extends linearly in the thickness direction and communicates the pressure receiving chamber 44 and the balancing chamber 46 with each other. Is provided. The opening of the first orifice passage 50 to the pressure receiving chamber 44 communicates with the inside of the pressure receiving chamber 44 through a through hole 51 provided in the cover fitting 48. Further, in the present embodiment, the first orifice passage 50 is formed with a relatively small passage cross-sectional area and a long passage length, so that the first orifice passage 50 has a resonance action of a fluid flowing through the inside thereof. On the basis of the tuning, tuning is performed so that a high damping effect against low frequency vibration of about 10 Hz corresponding to a shake or the like can be exerted.

The outer peripheral edge of the partition member 42 extends through the inside of the first orifice passage 50 in a bent form independently of the first orifice passage 50, and the pressure receiving chamber 44 and the equilibrium chamber 46 are provided.
And a second orifice passage 56 that communicates with the other. The opening of the second orifice passage 56 to the pressure receiving chamber 44 is communicated with the inside of the pressure receiving chamber 44 through a through hole 57 provided in the cover fitting 48, while the opening to the balance chamber 46 is provided. Are located on the peripheral wall surface of the lower recess 54. Further, the second orifice passage 56 is set such that its cross-sectional area and length are larger in cross-sectional area / length ratio than that of the first orifice passage 50. It is tuned so that a low dynamic spring effect against a medium frequency vibration of about 25 Hz corresponding to an idling vibration can be exerted based on a resonance action of a fluid flowing through the inside.

Further, in the center of the partition member 42, independently of the first and second orifice passages 50 and 56, a partition wall of the upper recess 52 and the lower recess 54 penetrates. And a third orifice passage 58 that extends between the pressure receiving chamber 44 and the balancing chamber 46 is provided. The opening of the third orifice passage 58 into the balancing chamber 46 is located on the bottom wall surface of the lower recess 54. Further, the third orifice passage 58 is set so that its cross-sectional area and length are larger than those of the second orifice passage 56, so that the resonance action of the fluid flowing through the inside thereof can be achieved. Is tuned such that a low dynamic spring effect can be exerted against high-frequency vibrations of about 150 Hz corresponding to engine vibrations at a relatively high speed.

In addition, the third orifice passage 58 in the present embodiment restricts the opening amount, that is, the cross-sectional area of the third orifice passage 58 to approximately １ ／, so that the third orifice passage 58 is formed based on the resonance action of the fluid flowing through the inside. The tuning is performed so that a low dynamic spring effect can be exhibited with respect to high-frequency vibration of about 100 Hz corresponding to engine vibration or the like at a relatively low speed.

A substantially disc-shaped rubber elastic plate 60 is provided inside the upper recess 52 where the third orifice passage 58 opens, and its outer peripheral edge is formed between the partition member 42 and the cover fitting 48. They are arranged by being sandwiched between them. The rubber elastic plate 60 separates the upper recess 52 into an opening side and a bottom side, and the opening side has
Through the communication hole 62 provided in the cover fitting 48, the pressure receiving chamber 4
4 while the bottom side thereof is connected to a partition member 42.
Is connected to the equilibrium chamber 46 through a third orifice passage 58 provided at the bottom. And the rubber elastic plate 6
Based on the elastic deformation of zero, the flow of the fluid through the third orifice passage 58 can be allowed between the pressure receiving chamber 44 and the equilibrium chamber 46.

Further, a rotary valve is provided inside the lower recess 54 of the partition member 42 in which the openings of the second orifice passage 56 and the third orifice passage 58 toward the equilibrium chamber 46 are located. 64 is provided so as to be rotatable around one axis substantially orthogonal to the vibration input direction. The rotary valve 64 is configured such that the opening of the second orifice passage 56 and the opening of the third orifice passage 58 are pivotally moved on one circumference which is positioned at a predetermined distance in the circumferential direction. An arcuate valve element 66 is provided.

Further, a stepping motor 68 is provided outside the mount, and is fixedly attached to the tube fitting 22. The valve 66 of the rotary valve 64 is rotated by the stepping motor 68 under the control of the controller 70.

The opening of the second orifice passage 56 and the opening of the third orifice passage 58 are selectively closed or the third orifice passage 58 depending on the rotational position of the rotary valve 64. The opening amount of the opening of the orifice passage 58 can be adjusted. The anti-vibration characteristics of the mount can be switched based on the switching of the orifice passages 56 and 58 and the adjustment of the opening amount. It becomes.

More specifically, when the valve body 66 is positioned at the rotation position as shown in FIG. 3 and the third orifice passage 58 is closed, when the vibration is input, the pressure receiving chamber 44 is closed. Due to the pressure difference created between the pressure chamber and the balance chamber 46, only the flow of fluid through the second orifice passage 56 will be effectively produced. As a result, based on the resonance action of the fluid caused to flow through the second orifice passage 56, a low dynamic spring effect is exhibited with respect to an input vibration (idling vibration, etc.) in a medium frequency range of about 25 Hz, and excellent. That is, the vibration-proof characteristics can be exhibited.

The valve orifice 66 is positioned at a pivot position as shown in FIG.
Is closed and the third orifice passage 58 is opened substantially halfway, and when the vibration is input, the pressure receiving chamber 44 is closed.
Due to the pressure difference created between the pressure chamber and the balancing chamber 46, only the flow of fluid through the third orifice passage 58 having a restricted opening is effectively produced.
As a result, on the basis of the resonance action of the fluid caused to flow through the third orifice passage 58 whose opening is restricted, input vibrations in a high frequency range around 100 Hz (engine vibrations at low rotation, etc.) A low dynamic spring effect is exhibited, and excellent vibration isolation performance can be exhibited.

Further, the valve body 66 is positioned at the pivot position as shown in FIG. 5, and the second orifice passage 56 is closed and the third orifice passage 58 is fully opened. Under the vibration input, only the flow of the fluid through the third orifice passage 58 is effectively generated based on the pressure difference generated between the pressure receiving chamber 44 and the balance chamber 46 at the time of vibration input. As a result, based on the resonance action of the fluid caused to flow through the third orifice passage 58, a low dynamic spring effect is exhibited with respect to input vibration in a high frequency range of about 150 Hz (engine vibration during high rotation, etc.). Thus, excellent vibration isolation performance can be exhibited.

As shown in FIGS. 3 to 5, the first orifice passage 50 is in an open state in any state, but the first orifice passage 50 has a sectional area / length. Since the ratio is sufficiently smaller than that of any one of the second orifice passage 56 and the third orifice passage 58 and the flow resistance is large, the low motion due to the second orifice passage 56 and the third orifice passage 58 is low. When a small amplitude vibration in the middle to high frequency range where a spring effect is required, almost no fluid flows through the first orifice passage 50, and therefore the second orifice Both the passage 56 and the third orifice passage 58 can effectively exhibit the vibration damping effect.

On the other hand, at the time of inputting low-frequency large-amplitude vibration (shake, bounce, etc.) of about 10 Hz, for which the first orifice passage 50 is required to have an anti-vibration effect, at least as shown in FIG. 4 or FIG. Second orifice passage 56
The valve body 66 is positioned so that is closed. Then, since the amount of fluid flowing through the third orifice passage 58 is limited by the rubber elastic plate 60, the internal pressure fluctuation induced in the pressure receiving chamber 44 when a low-frequency large-amplitude vibration is input. Cannot be absorbed solely by the flow of fluid through the third orifice passage 58, so that the third orifice passage 5
Regardless of the open state of 8, the flow of the fluid through the first orifice passage 50 can be effectively generated. As a result, the first orifice passage 50
On the basis of the resonance action of the fluid flowing through
With respect to input vibration in a low frequency range of about 10 Hz, a high damping effect is exhibited, and excellent vibration isolation performance can be exhibited.

Therefore, in the engine mount having the above-described structure, the mount anti-vibration characteristics can be appropriately changed by switching the rotational position of the valve element 66 of the rotary valve 64. Therefore, for example, by controlling the operation of the stepping motor 68 according to the engine speed of the vehicle and the like, and switching the rotational position of the valve body 66, an effective anti-vibration characteristic can be obtained according to the type of input vibration. Can be obtained advantageously.

Moreover, in such an engine mount, the sectional area A of the orifice passage is changed by adjusting the opening amount of the third orifice passage 58 in accordance with the frequency of the input vibration to be damped. At the same time, by switching the second and third orifice passages, it is possible to change the length: L of the orifice passage, so that only the cross-sectional area: A is changed as in the prior art. Compared to a conventional device or a device that simply switches between two orifice passages, its vibration isolation characteristics can be effectively tuned for input vibration in an extremely wide frequency range.

Further, in the engine mount according to the present embodiment, the rubber elastic plate 60 for limiting the amount of fluid flowing through the third orifice passage 58 is provided, regardless of the open state of the third orifice passage 58. ,
For low frequency large amplitude vibration, the first orifice passage 50
Therefore, the high damping effect of the valve body 66 can be effectively exerted, and thereby, there is an advantage that the control of the rotational position of the valve body 66 can be simplified.

In the above embodiment, the case where the opening amount of the third orifice passage 58 is controlled to be switched in two stages has been described. However, the opening amount is changed in multiple stages or continuously according to the input vibration. It is also possible to change it, so that a better vibration damping effect can be obtained for input vibration in a wide frequency range. Incidentally, in the engine mount having the above-described structure, the mount anti-vibration characteristics (spring ratio) obtained by continuously changing the opening amount of the third orifice passage 58 in accordance with the input vibration frequency are experimentally determined. The measurement result is shown in FIG.

Although the embodiment of the present invention has been described in detail, this is a literal example, and the present invention should not be interpreted as being limited to such a specific example.

For example, in the above-described embodiment, the rubber elastic plate 60 for limiting the amount of the fluid which is made to flow through the third orifice passage 58 is provided. In the case where a valve body capable of simultaneously closing the and the third orifice passage 58 is adopted, it is not always necessary to provide the valve body.

Further, the specific shapes of the first orifice passage, the second orifice passage, and the third orifice passage, and the cross-sectional areas and lengths thereof are all different depending on the anti-vibration characteristics required for the mount. It is to be determined in accordance with, and is not limited to.

Further, in the above-described embodiment, the description has been given of the case where only the sectional area (opening amount) of the third orifice passage is adjusted by the valve body.
The cross-sectional area (opening amount) of the second orifice passage may also be adjusted, so that effective vibration damping performance can be exhibited for input vibration in a wider frequency range.

In the above-described embodiment, the switching control of the orifice passage and the opening amount thereof are controlled by the valve element 66 in accordance with the engine speed. It is also possible to control the switching of the valve element 66 and adjust the opening amount thereof in accordance with the deceleration state or the like, and the control conditions include the vibration isolation characteristics required for the mount and the tuning of each orifice passage. Depending on,
It will be determined appropriately.

Furthermore, in the above-described embodiment, a rotary valve is employed as the switching valve. However, a slide valve or the like may be employed depending on the positional relationship of the opening of the orifice passage.

Further, it is also possible to provide a junction of the second orifice passage and the third orifice passage on the pressure receiving chamber side, and to arrange a switching valve there.

In addition, in the above-described embodiment, a specific example in which the present invention is applied to an engine mount for an automobile is shown. However, the present invention is advantageous for various kinds of anti-vibration mounts for automobiles and other types. Of course, it can be applied to

In addition, although not enumerated one by one, the present invention
Based on the knowledge of those skilled in the art, various changes, modifications, improvements and the like can be implemented in an embodiment,
It goes without saying that all such embodiments are included in the scope of the present invention unless they depart from the spirit of the present invention.

[0048]

As is apparent from the above description, in the fluid-filled mounting device structured according to the present invention, the first orifice passages formed independently of each other,
The second orifice passage and the third orifice passage are
By selectively functioning, any effective vibration damping effect can be exhibited for input vibrations in three different frequency ranges, and the opening amount of the third orifice passage is adjusted. By doing so, an effective vibration damping effect can be exhibited even for input vibration in an intermediate frequency range between the tuning frequency range of the second orifice passage and the tuning frequency range of the third orifice passage, Good vibration damping characteristics can be obtained for input vibrations in an extremely wide frequency range.

[Brief description of the drawings]

FIG. 1 is an explanatory longitudinal sectional view showing an engine mount as one embodiment of the present invention.

FIG. 2 is an explanatory diagram corresponding to a II-II cross section in FIG.

FIG. 3 is an explanatory diagram showing an operation state of a main part of the engine mount shown in FIG. 1;

FIG. 4 is an explanatory diagram showing another operation state of a main part of the engine mount shown in FIG. 1;

FIG. 5 is an explanatory view showing still another operation state of a main part of the engine mount shown in FIG. 1;

FIG. 6 is a graph showing vibration isolation characteristics of the engine mount shown in FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 First mounting bracket 12 Second mounting bracket 14 Body rubber 22 Cylindrical bracket 24 Bottom bracket 34 Diaphragm 42 Partition member 44 Pressure receiving chamber 46 Equilibrium chamber 48 Cover metal fitting 50 First orifice passage 56 Second orifice passage 58 Third Orifice passage 60 rubber elastic plate 64 rotary valve 66 valve element 68 stepping motor

Claims (1)

(57) [Scope of request for utility model registration] 1. A first mounting bracket and a second mounting bracket which are respectively disposed at a predetermined distance in a vibration input direction and which are mounted on members to be vibration-isolated and connected therebetween. And a pressure receiving chamber in which a part of a wall is formed by the rubber elastic body and an internal pressure fluctuation is caused at the time of vibration input, and at least a part of the wall is a flexible film. Are formed, and a predetermined incompressible fluid is sealed in the pressure receiving chamber and the equilibrium chamber, and the pressure receiving chamber and the equilibrium chamber are mutually connected. A first orifice passage communicating with the first orifice passage, a second orifice passage having a larger sectional area / length ratio than the first orifice passage, and a second orifice passage. Larger cross-sectional area / length ratio And a third orifice passage, straddling between the equilibrium chamber and the pressure receiving chamber,
At the junction where the second orifice passage and the third orifice passage are respectively opened, they slide on the wall surface where the second orifice passage and the third orifice passage are opened. The opening of the second orifice passage and the opening of the third orifice passage are opened and closed to selectively open, and at least the opening amount of the opening of the third orifice passage is adjusted. A fluid-filled mounting device, characterized in that a switching valve is provided.