JPH0540638U - Fluid-filled mounting device - Google Patents

Abstract

(57) [Abstract] [Purpose] To provide a fluid-filled mount device capable of switching control of vibration damping characteristics exerted on the basis of fluid flow action over a wide frequency range. [Structure] A pressure receiving chamber 44 and an equilibrium chamber 4 formed inside a mount and communicating with each other through a first orifice passage 50.
6, a second orifice passage 56 having a larger cross-sectional area / length ratio than the first orifice passage 50 and a larger cross-sectional area / length ratio than the second orifice passage 56. The third orifice passage 58 and the third orifice passage 58 are provided in parallel, and the openings of the second orifice passage 56 and the third orifice passage 58 are opened and closed at the confluence of the third orifice passage 58 and selectively opened. And a switching valve 64 for adjusting the opening amount of at least the opening portion of the third orifice passage 58.
Was arranged.

Description

[Detailed description of the device]

[0001]

【Technical field】

 The present invention relates to a fluid-filled mount device that obtains a vibration damping effect based on a fluid flow action, and in particular, can control switching of a vibration damping characteristic exhibited based on a fluid flow action. The present invention relates to a fluid-filled mount device.

[0002]

[Background technology]

 Conventionally, as a type of vibration-proof coupling or supporting device, a first elastic member and a second elastic member, which are arranged at a predetermined distance from each other, are connected by a rubber elastic body, and at the same time, both of the elastic members are connected. A pressure receiving chamber, into which a predetermined incompressible fluid is filled, to which vibration is input, and a volume-equilibrium chamber are formed between the pressure receiving chamber and an orifice passage that connects the pressure receiving chamber and the equilibrium chamber to each other. A so-called fluid-filled mount device having a structure provided is known. Further, in such a fluid-filled mount device, it is possible to easily obtain a vibration damping effect, which cannot be obtained with a rubber elastic body, based on the resonance action of the fluid flowing in the orifice passage. Therefore, it has come to be favorably used as an anti-vibration device for automobiles.

By the way, in a vehicle vibration damping device or the like in which such a fluid-filled mount device is preferably used, a plurality of types of vibrations are input depending on the running state of the vehicle, etc. Various anti-vibration effects are required for input vibration over a wide range. For example, in an automobile engine mount, in addition to a high damping effect for low-frequency vibrations such as shakes at around 10Hz, a low dynamic spring effect for medium-frequency vibrations equivalent to idling vibrations around 25Hz, engine vibrations, etc. Therefore, a low dynamic spring effect is required for higher high frequency vibrations caused by the above, and the high frequency vibrations change in frequency depending on the engine speed, etc. Therefore, a low dynamic spring effect is required.

However, in the fluid-filled mount device as described above, the vibration isolation effect due to the resonance action of the fluid can be effectively exerted only in the limited frequency range set in the orifice passage, and At the time of inputting vibration in a frequency range higher than the set frequency, the flow resistance of the orifice passage remarkably increases, 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 made variable by adjusting the opening (cross-sectional area) of one orifice passage (Actual Publication No. 63- No. 24004), and (2) a structure in which two orifice passages having different cross-sectional areas / lengths are provided in parallel, and they are selectively opened by switching them with valve means (Japanese Patent Laid-Open Publication No. Sho. 58-54247, etc.) has been proposed.

However, as described in (1) above, it was extremely difficult to obtain a sufficient tuning range by simply 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 thereof is L, the resonance frequency F of the fluid that is caused to flow inside is expressed by F ∝ (A / L) ^1/2 . Even if the cross-sectional area A of the orifice passage is changed to 4 times (or 1/4 times), the tuning frequency of the orifice passage can be changed only twice, and it is difficult to obtain an effective amount of change. Moreover, in order to be able to tune up to the high frequency range, it is necessary to set the length L of the orifice passage to be short. Then, when tuning to the low frequency region, the cross-sectional area of the orifice passage: A Must be made extremely small, and it becomes difficult to secure the fluid flow rate, so it is difficult to obtain sufficient vibration damping effect.

Further, as described in (2) above, by selectively operating the two orifice passages, two vibration damping characteristics pre-tuned to each orifice passage can be selectively exerted. Therefore, as described above, when the vibration isolation effect is required for the input vibrations in the three or more frequency ranges, satisfactory vibration isolation is achieved for the input vibrations in all the frequency ranges. It was extremely difficult to get the effect.

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

[0009]

[Solution]

 Here, the present invention has been made against the background of the above circumstances, and the problem to be solved is that it is possible to switch the anti-vibration characteristics and to handle a plurality of input vibrations over a wide frequency range. On the other hand, it is an object of the present invention to provide a fluid-filled mount device having an improved structure, in which the vibration damping effect exerted based on the flow action of the fluid caused to flow through the orifice passage can be advantageously exerted. ..

[0010]

[Solution]

 Then, in order to solve such a problem, in the present invention, a first mounting metal fitting, which is arranged at a predetermined distance in the vibration input direction and is to be respectively attached to members to be vibration-isolated and connected. And the second mounting member are connected by a rubber elastic body interposed between them, and a part of the wall portion is constituted by the rubber elastic body so that the internal pressure fluctuation is caused at the time of vibration input. A pressure chamber and a balance chamber, at least a part of the wall of which is made of a flexible film and in which the volume change is easily allowed. In a fluid-filled mount device which is provided with a first orifice passage that seals a fluid and connects the pressure-receiving chamber and the equilibrium chamber to each other, a cross-sectional area / length ratio of the first orifice passage is larger than that of the first orifice passage. A large second orifice passage, A third orifice passage having a larger cross-sectional area / length ratio than that of the liffith passage is provided in parallel with each other across the pressure receiving chamber and the equilibrium chamber, and Of the second orifice and the third orifice passage are slid on the wall surface where the second orifice passage and the third orifice passage are opened at the confluence point where the second orifice passage and the third orifice passage are opened, respectively, and the second orifice is opened. A switching valve for opening and closing the opening of the passage and the opening of the third orifice passage to selectively open the opening and at least adjusting the opening amount of the opening of the third orifice passage is provided. Is its characteristic.

[0011]

【Example】

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

First, FIGS. 1 and 2 show an automobile engine mount as an embodiment of the present invention. In these drawings, 10 and 12 are a first mounting member and a second mounting member, respectively, which are arranged to face each other with a predetermined distance therebetween. The first mounting member 10 and the second mounting member 12 are elastically connected by a main body rubber 14 as a rubber elastic body interposed between them. In such an engine mount, the first mounting member 10 and the second mounting member 12 are mounted on one of the vehicle body side and the power unit side, respectively, and are mounted between the vehicle body and the power unit. The power unit is supported by the vehicle body in a vibration-proof manner. Under such an installed condition, in such an engine mount, the weight of the power unit is exerted in a direction substantially opposite to the first and second mounting brackets 10 and 12 (generally vertical direction in FIG. 1). By elastically deforming the body rubber 14, both the 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 The vibration damping effect is exerted against the vibration input in the substantially opposite direction.

More specifically, the first mounting member 10 is formed in a disc shape. In addition, a support metal fitting 18 having a substantially bottomed cylindrical shape is welded at the opening to the first mounting metal fitting 10 so as to project and be fixed to one surface. Furthermore, a mounting bolt 20 is fixed to the first mounting member 10 so as to project to the side opposite to the supporting member 18. Then, the mounting bolts 20 are mounted on a power unit (not shown).

On the other hand, the second mounting member 12 is composed of a tubular member 22 having a substantially cylindrical shape and a bottom member 24 having a substantially bottomed cylindrical shape. The tubular metal member 22 has a tapered portion 26 that expands outward in the axial direction on one side in the axial direction, while a caulking portion 28 is integrally provided on the other end portion in the axial direction. Further, an abutting piece 29 protruding outward in the radial direction is fixed to an opening of the tubular metal fitting 22 on the side of the taper portion 26. An outward flange portion 30 is integrally formed in the opening of the bottom metal fitting 24.

Then, the caulking portion 28 of the tubular metal fitting 22 is caulked and fixed to the flange portion 30 of the bottom metal fitting 24, so that the second mounting metal fitting 12 as a whole has a bottomed cylindrical shape with a substantially deep bottom. , Formed. The second mounting member 12 has a mounting bolt 32 fixed to the bottom of the bottom metal fitting 24 so as to project outward. The mounting bolt 32 mounts the mounting bolt 32 to the vehicle body (not shown). It is designed to be used.

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

Further, a diaphragm 34 as a flexible film is housed and arranged inside the second mounting member 12 in the connected body. As shown in the drawing, the diaphragm 34 is vulcanized so as to cover a cylindrical metal fitting 38 having an outwardly facing flange portion 36 at one end in the axial direction so as to cover the opening at the other end in the axial direction. It is adhered, and the flange portion 36 of the tubular metal member 38 is attached to the second mounting metal member 12 by being sandwiched between the tubular metal member 22 and the bottom metal member 24 by caulking. That is, as a result, the inside of the second mounting member 12 covered with the main body rubber 14 is fluid-tightly partitioned by the diaphragm 34 between the first mounting member 10 side and the bottom mounting member 24 side. It is being done.

A fluid chamber, in which a predetermined incompressible fluid is sealed, is formed on the side of the diaphragm 34 that is closer to the first mounting member 10. On the other hand, an air chamber 40 that allows the deformation of the diaphragm 34 is formed on the side opposite to the fluid chamber across the diaphragm 34.

As the fluid sealed in the fluid chamber, for example, water, alkylene glycol, polyalkylene glycol, silicone oil, a mixed solution thereof, or the like is preferably used. Further, such filling of the fluid is advantageously performed, for example, by caulking and fixing the tubular metal fitting 22 constituting the integrally vulcanized molded product to the flange portion 30 of the bottom metal fitting 24 in the fluid. obtain.

Furthermore, a partition member 42 is accommodated in the fluid chamber. The partition member 42 has a generally thick disk shape as a whole, and an upper recess 52 opening to the pressure receiving chamber 44 side and a lower recess opening to the equilibrium chamber 46 side are provided in a substantially central portion thereof. And 54 are provided respectively. Further, a thin disk-shaped lid fitting 48 is superposed on the surface where the upper recess 52 is opened. The partition member 42 has the annular support portion 55, which is formed on the outer peripheral edge of the partition member 42, and is clamped together with the lid fitting 48 at the caulking portion between the tubular fitting 22 and the bottom fitting 24. It is fixed to the mounting bracket 12.

As a result, the fluid chamber is divided into two parts 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 constituted by the main body rubber 14 to form a pressure receiving chamber 44 in which fluctuation of internal pressure is caused at the time of vibration input. ing. On the other hand, on the side opposite to the pressure receiving chamber 44 with the partition member 42 sandwiched between them, a part of the wall portion is constituted by the diaphragm 34, and a balance chamber 46 in which the volume change is easily allowed is formed.

The partition member 42 has a first orifice passage 50 that linearly penetrates the partition member 42 in the thickness direction at the outer peripheral edge thereof and connects the pressure receiving chamber 44 and the equilibrium chamber 46 to each other. Is provided. The opening of the first orifice passage 50 to the pressure receiving chamber 44 is communicated with the pressure receiving chamber 44 through a through hole 51 provided in the lid fitting 48. Further, in the present embodiment, the first orifice passage 50 is formed with a relatively small flow passage cross-sectional area and a long flow passage length, so that the resonance action of the fluid flowing through the inside thereof Based on the above, it is tuned so that a high damping effect can be exhibited against low-frequency vibration around 10 Hz, which is equivalent to shaking.

Further, the outer peripheral edge portion of the partition member 42, independently of the first orifice passage 50, extends through the inside thereof in a bent form to extend the pressure receiving chamber 44 and the equilibrium chamber 46 from each other. A second orifice passage 56 that communicates is provided. The opening of the second orifice passage 56 to the pressure receiving chamber 44 is communicated with the pressure receiving chamber 44 through the through hole 57 provided in the lid fitting 48, while the opening to the equilibrium chamber 46 is formed. Are located on the peripheral wall surface of the lower recess 54. Further, the cross section area and length of the second orifice passage 56 are set so that the cross section area / length ratio is larger than that of the first orifice passage 50. Based on the resonance action of the fluid that flows through the inside, it is tuned so that a low dynamic spring effect can be exerted against the mid-frequency vibration around 25 Hz, which is equivalent to idling vibration.

Furthermore, the partition member 42 penetrates the partition between the upper recess 52 and the lower recess 54, independently of the first and second orifice passages 50 and 56. A third orifice passage 58 is provided which extends and extends to connect the pressure receiving chamber 44 and the equilibrium chamber 46 to each other. The opening of the third orifice passage 58 into the equilibrium 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 of the fluid that is made to flow therethrough is resonated. Based on the action, it is tuned so that a low dynamic spring effect can be exerted against a high frequency vibration of about 150 Hz which corresponds to an engine vibration at a relatively high speed.

In addition, the third orifice passage 58 in the present embodiment is based on the resonance action of the fluid that is made to flow through the inside by limiting the opening amount, that is, the cross-sectional area to approximately 1/2. It is tuned so that a low dynamic spring effect can be exerted against high-frequency vibrations around 100 Hz, which corresponds to engine vibrations at relatively low speeds.

A substantially disk-shaped rubber elastic plate 60 is provided inside the upper recess 52 in which the third orifice passage 58 opens, and the outer peripheral edge portion of the rubber elastic plate 60 is divided into the partition member 42 and the lid fitting 48. It is arranged by being sandwiched between them. The rubber elastic plate 60 divides the upper recess 52 into an opening portion side and a bottom portion side, and the opening portion side is passed through the communication hole 62 provided in the lid fitting 48 to the pressure receiving chamber. One of them is connected to the equilibrium chamber 46 through the third orifice passage 58 provided in the partition member 42. Then, based on the elastic deformation of the rubber elastic plate 60, 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, inside the lower recess 54 of the partition member 42, in which the openings to the equilibrium chamber 46 side in the second orifice passage 56 and the third orifice passage 58 are located, The rotary valve 64 is disposed so as to be rotatable about one axis that is substantially orthogonal to the vibration input direction. In this rotary valve 64, the opening of the second orifice passage 56 and the opening of the third orifice passage 58 are rotatably moved on one circumference in which they are positioned at a predetermined distance in the circumferential direction. A valve element 66 having a substantially arc shape is provided.

A stepping motor 68 is provided outside the mount and is fixedly attached to the tubular metal member 22. The stepping motor 68 drives the valve body 66 of the rotary valve 64 to rotate under the control of the controller 70.

Then, depending on the rotational position of the rotary valve 64, 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 is closed. The opening amount of the opening portion of the orifice passage 58 of the mount can be adjusted. Based on the switching of the orifice passages 56 and 58 and the adjustment of the opening amount, the vibration damping characteristic of the mount is switched. That will be the case.

Specifically, when the valve body 66 is positioned at the rotating 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 received. Only the flow of fluid through the second orifice passage 56 will effectively be generated due to the pressure difference created between the and the equilibrium chamber 46. As a result, based on the resonance action of the fluid that is made to flow through the second orifice passage 56, a low dynamic spring effect is exhibited for input vibration (idling vibration, etc.) in the medium frequency range around 25 Hz, Excellent vibration damping characteristics can be exhibited.

Further, the valve body 66 is positioned at the rotational position as shown in FIG. 4 to close the second orifice passage 56 and open the third orifice passage 58 by about half. Under the condition, when the vibration is input, only the flow of the fluid through the third orifice passage 58 having the restricted opening is effective based on the pressure difference generated between the pressure receiving chamber 44 and the equilibrium chamber 46. It will be born. As a result, based on the resonance action of the fluid that is made to flow through the third orifice passage 58 whose opening is restricted, the input vibration (engine vibration at low speed etc.) in the high frequency range around 100 Hz is As a result, the low dynamic spring effect is exerted, and excellent vibration damping performance can be exerted.

Furthermore, the valve body 66 is positioned at the rotational position as shown in FIG. 5 to close the second orifice passage 56 and open the third orifice passage 58 entirely. Under this condition, only the fluid flow through the third orifice passage 58 is effectively generated based on the pressure difference generated between the pressure receiving chamber 44 and the equilibrium chamber 46 at the time of vibration input. .. As a result, based on the resonance action of the fluid that is made to flow through the third orifice passage 58, the low dynamic spring effect is applied to the input vibration in a high frequency range around 150 Hz (engine vibration at high speed, etc.). Is exhibited, and excellent anti-vibration performance can be exhibited.

By the way, as shown in FIGS. 3 to 5, in any of the states, the first orifice passage 50 is in an open state, but the first orifice passage 50 has a sectional area / length. Ratio of the second orifice passage 56 and the third orifice passage 58 is sufficiently smaller than that of both the second orifice passage 56 and the third orifice passage 58, and the flow resistance is large. When a small-amplitude vibration in the middle to high frequency range is input, which requires a low dynamic spring effect by the fluid flow of the fluid through the first orifice passage 50, the flow of the fluid hardly occurs. The vibration damping effect of the second orifice passage 56 and the third orifice passage 58 can be effectively exhibited.

On the other hand, at the time of inputting a low-frequency large-amplitude vibration (shake, bounce, etc.) around 10 Hz, which requires the vibration damping effect of the first orifice passage 50, at least as shown in FIG. 4 or FIG. The valve body 66 is positioned so that the second orifice passage 56 is closed. Then, the amount of fluid flowing through the inside of the third orifice passage 58 is limited by the rubber elastic plate 60, so that the third orifice passage 58 is induced in the pressure receiving chamber 44 when the low-frequency large-amplitude vibration is input. Since the internal pressure fluctuation cannot be absorbed only by the flow of the fluid through the third orifice passage 58, the internal orifice fluctuates through the first orifice passage 50 regardless of the opening state of the third orifice passage 58. The fluid flow can be effectively generated. As a result, based on the resonance action of the fluid that is made to flow through the first orifice passage 50, a high damping effect is exerted on the input vibration in the low frequency range around 10 Hz, and excellent vibration isolation is achieved. The performance can be demonstrated.

Therefore, in the engine mount having the above-described structure, the mount anti-vibration characteristic can be appropriately changed by switching the rotational position of the valve body 66 of the rotary valve 64. Therefore, for example, by controlling the operation of the stepping motor 68 in accordance with the engine speed of the vehicle and switching the rotational position of the valve element 66, effective vibration damping characteristics can be obtained according to the type of input vibration. It is possible to obtain the advantage.

In addition, in such an engine mount, the cross-sectional area A of the orifice passage is changed by adjusting the opening amount of the third orifice passage 58 according to the frequency of the input vibration to be isolated. In addition to changing the second and third orifice passages, it is possible to change the length L of the orifice passage as well. Therefore, only the cross-sectional area A can be changed as in the prior art. Compared with the one that only allows or the two orifice passages are simply switched, the anti-vibration characteristics can be effectively tuned to the input vibration in an extremely wide frequency range.

Further, in the engine mount according to the present embodiment, the rubber elastic plate 60 that limits the amount of fluid that is made to flow through the third orifice passage 58 is provided, so that the third orifice passage 58 is opened. Regardless, the high damping effect of the first orifice passage 50 can be effectively exerted on the low-frequency, large-amplitude vibrations, which can simplify the control of the rotational position of the valve element 66. It also has advantages.

In the above embodiment, the case where the opening amount of the third orifice passage 58 is controlled to be switched in two steps has been described. However, the opening amount is changed in multiple steps or continuously according to the input vibration. It is also possible to change it, which makes it possible to obtain a better anti-vibration effect against input vibration in a wide frequency range. By the way, in the engine mount having the above-described structure, the mount vibration isolation characteristic (spring ratio) obtained by continuously changing the opening amount of the third orifice passage 58 according to the input vibration frequency was tested. The results of measurement by are shown in FIG.

Although the embodiments of the present invention have been described in detail above, this is a literal example, and the present invention should not be construed as being limited to such specific examples.

For example, in the above-described embodiment, the rubber elastic plate 60 that limits the amount of fluid that is made to flow through the third orifice passage 58 is provided, but such a rubber elastic plate is, for example, the second orifice passage. It is not always necessary to provide the valve element which can block 56 and the third orifice passage 58 at the same time.

Further, the specific shapes of the first orifice passage, the second orifice passage, and the third orifice passage, and their cross-sectional areas and lengths, all depend on the vibration damping characteristics required for the mount. It should be decided accordingly and is not limited.

Further, in the above-mentioned embodiment, the case where only the sectional area (opening amount) of the third orifice passage is adjusted by the valve element has been described. The area (aperture amount) may also be adjusted, whereby effective vibration damping performance can be exhibited against input vibration in a wider frequency range.

Further, in the above-described embodiment, the switching control of the orifice passage by the valve element 66 and the adjustment of the opening amount thereof are performed according to the engine speed. It is also possible to perform such switching control of the valve element 66 and adjustment of the opening amount thereof according to the deceleration state and the like, and the control conditions are vibration isolation characteristics required for the mount, tuning of each orifice passage, etc. It will be decided accordingly.

Furthermore, although the rotary valve is used as the switching valve in the above-described embodiment, a slide valve or the like may be used depending on the positional relationship of the openings of the orifice passages and the like.

Furthermore, it is possible to provide a confluence point between the second orifice passage and the third orifice passage on the pressure receiving chamber side, and dispose the switching valve there.

In addition, in the above embodiment, a concrete example of the present invention applied to an automobile engine mount is shown. However, the present invention is applied to an automobile or various other vibration-proof mounts. Of course, it can be applied to advantage.

Although not listed one by one, the present invention can be carried out in a mode in which various changes, modifications, improvements, etc. are added based on the knowledge of those skilled in the art, and such an embodiment is also possible. However, it goes without saying that all of them are included in the scope of the present invention without departing from the spirit of the present invention.

[0048]

[Effect of the device]

 As is apparent from the above description, in the fluid-filled mount device having the structure according to the present invention, the first orifice passage, the second orifice passage, and the third orifice passage formed independently of each other are provided. However, it is possible to exert effective anti-vibration effects on input vibrations in three different frequency bands by making them selectively operate, and furthermore, the third orifice passage By adjusting the opening amount, effective anti-vibration effect can be obtained even for input vibration in the intermediate frequency range between the tuning frequency range of the second orifice passage and the tuning frequency range of the third orifice passage. Since it can be exhibited, it is possible to obtain good vibration damping characteristics against input vibration in an extremely wide frequency range.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional explanatory view showing an engine mount as one embodiment of the present invention.

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

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

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

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

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

[Explanation of symbols]

 10 First Mounting Metal Fitting 12 Second Mounting Metal Fitting 14 Main Body Rubber 22 Cylindrical Metal Fitting 24 Bottom Metal Fitting 34 Diaphragm 42 Partition Member 44 Pressure Receiving Chamber 46 Equilibrium Chamber 48 Lid Metal Fitting 50 First Orifice Passage 56 Second Orifice Passage 58 58 Third Orifice passage 60 Rubber elastic plate 64 Rotary valve 66 Valve body 68 Stepping motor

Claims (1)

[Scope of utility model registration request] 1. A first mounting metal fitting and a second mounting metal fitting, which are arranged at a predetermined distance in a vibration input direction and are respectively mounted on members to be vibration-proof connected, are interposed between them. And a flexible membrane in which at least a part of the wall is connected to the pressure receiving chamber in which a part of the wall is formed by the rubber elastic and the internal pressure fluctuates when vibration is input. And an equilibrium chamber in which the volume change is easily allowed, and a predetermined incompressible fluid is sealed in the pressure-receiving chamber and the equilibrium chamber, while the pressure-receiving chamber and the equilibrium chamber are mutually A fluid-filled mount device having a first orifice passage communicating with the first orifice passage, the second orifice passage having a larger cross-sectional area / length ratio than the first orifice passage, and the second orifice passage. The cross-sectional area / length ratio is even greater And a third orifice passage, straddling between the equilibrium chamber and the pressure receiving chamber,
They are provided in parallel with each other and slide on the wall surface where the second orifice passage and the third orifice passage are open at the confluence point 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 selectively to open the opening, and at least the opening amount of the opening of the third orifice passage is adjusted. A fluid-filled mount device characterized in that a switching valve is provided.