JPH10196708A - Fluid-filled vibration isolator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a light and compact fluid-filled vibration damping device capable of advantageously realizing active control of vibration damping characteristics with a small number of parts and a simple structure. SOLUTION: A movable member 30, 49 constituting a part of a wall portion of a fluid chamber 60, 66 is formed by a rubber elastic plate 32, 50 having a mass member, and a movable member 30, 49 having a mass member is provided. A vibration system having a vibration frequency is formed, and working air chambers 62 and 68 are formed on the opposite side of the fluid chambers 60 and 66 with the movable members 30 and 49 interposed therebetween.
By vibrating the movable members 30 and 49 based on a change in air pressure exerted externally on the fluid chambers 68 and 68,
To control the internal pressure.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention comprises a fluid chamber in which an incompressible fluid is sealed, and a fluid-filled type in which the vibration damping characteristics can be appropriately adjusted by controlling the internal pressure and fluid flow in the fluid chamber. The present invention relates to a vibration isolator.

[0002]

2. Description of the Related Art Japanese Patent Application Laid-Open Nos. 60-8540 and 61-61 discloses a type of vibration isolating device as a vibration isolating connection member or a vibration isolating support member interposed between members constituting a vibration transmission system. 293
As described in Japanese Patent Application Publication No. 9-205, etc., a first mounting member and a second mounting member which are separated from each other are connected by a main rubber elastic body, while the first mounting member and the second mounting member are connected to each other. A main liquid chamber in which an incompressible fluid is sealed is generated, in which an internal pressure change is caused by deformation of the main rubber elastic body at the time of vibration input during, and a part of the wall of the main liquid chamber is formed by a movable member. A fluid-filled anti-vibration device that is configured to vibrate the movable member at an appropriate frequency corresponding to the vibration to be anti-vibrated and control the internal pressure of the main liquid chamber so that the anti-vibration characteristics can be adjusted appropriately. It has been known.

However, in the conventional fluid-filled type vibration damping device, as described in the above-mentioned publication, an electromagnetic drive means for vibrating a movable member must be incorporated in the device. In addition, many expensive parts such as coils and coils are required, and there is a problem that it is difficult to reduce the cost because it is difficult to manufacture, and there is a problem that an increase in size and weight is inevitable. In addition, the electromagnetic drive means requires permanent magnets and coils with high dimensional accuracy in order to stably obtain the desired drive force. Was also inferior. Furthermore, when it is necessary to control the internal pressure of the pressure receiving chamber continuously for a long time,
When a larger driving force is required, for example, there is a possibility that a rise in temperature due to heat generation when the coil is energized, a problem of securing power consumption, and the like may become problems.

Further, in the above-described fluid-filled type vibration damping device, it is necessary to directly control the internal pressure of the main liquid chamber by vibrating a movable member forming a part of the wall of the main liquid chamber. Since a large excitation force and a large amount of displacement are required for the movable member, there are problems such as an increase in the size of the electromagnetic drive means and an increase in power consumption when trying to achieve the required vibration isolation characteristics. There is also a problem that it is easy to occur, and it is difficult to achieve the required vibration isolation characteristics.

In order to further improve the vibration isolation characteristics, Japanese Utility Model Laid-Open Publication No. 61-191543 and the like disclose a sub liquid chamber which is connected to a main liquid chamber through an orifice passage. The chamber and the sub-liquid chamber communicate with each other through the orifice passage, and a part of the wall of the sub-liquid chamber is constituted by a movable member. By vibrating the movable member, a pressure change is generated in the sub-liquid chamber. A fluid filled type vibration damping device having such a configuration has been proposed.

In such an anti-vibration device, the internal pressure fluctuation generated in the sub liquid chamber by the vibration of the movable member is adjusted in consideration of the internal pressure fluctuation caused in the main liquid chamber at the time of vibration input. It is possible to control the flow of the fluid through the orifice passage. Therefore, it is possible to utilize the flow action such as the resonance action of the fluid caused to flow through the orifice passage, or to apply the internal pressure of the sub liquid chamber through the orifice passage. By controlling the internal pressure of the main liquid chamber, a more excellent vibration-proof effect can be obtained effectively.

However, even in such a fluid-filled type vibration damping device having such an orifice passage and a sub liquid chamber, the electromagnetic driving means for vibrating the movable member is still required. In addition, there is a problem similar to that of the fluid filled type vibration damping device having no orifice passage as described above, and there is still room for improvement.

[0008]

The inventions described in claims 1 to 6 are all made on the background of the above-mentioned circumstances, and the problem to be solved is that the pressure or flow of the sealed fluid is It has a simple structure while ensuring sufficient control of the mount's anti-vibration characteristics by controlling the size of the mount, which can advantageously reduce the size and weight, improve the manufacturability, etc., and reduce the problems of heat generation and power consumption. Can be effectively resolved,
An object of the present invention is to provide a fluid-filled type vibration damping device provided with a novel movable member vibration mechanism capable of stably controlling vibration damping characteristics for a long time.

[0009]

In order to solve such a problem, a feature of the invention according to claim 1 is that a first mounting member and a second mounting member which are separated from each other are separated from each other by a rubber elastic body. While connecting with a body, a fluid chamber in which an incompressible fluid is sealed is formed, and a part of the wall of the fluid chamber is formed of a movable member, and the fluid is excited by vibrating the movable member. In a fluid filled type vibration damping device in which the internal pressure of the chamber is controlled to adjust the vibration damping characteristics, the movable member is formed by an elastic plate to which a mass member is fixed, and vibration is to be damped by the movable member. While forming a vibration system having a natural frequency corresponding to vibration, a working air chamber sealed on the opposite side of the fluid chamber with respect to the movable member is formed, and the working air chamber is externally applied to the working air chamber. The movable member based on the air pressure change Lies in the so exciting force is exerted.

In the fluid filled type vibration damping device having the structure according to the first aspect of the present invention, by applying air pressure to the working air chamber, the movable member is displaced by the action of the air pressure. , Thereby exerting pressure on the fluid chamber. In other words, the air pressure of the working air chamber is exerted on the fluid chamber via the movable member, and by controlling the air pressure of the working air chamber,
It is possible to control the internal pressure and fluid flow of the fluid chamber.

Further, in the fluid filled type vibration damping device having the structure according to the first aspect of the present invention, one vibration system is constituted by the elastic plate and the mass member constituting the movable member, and the natural vibration At the time of excitation in several regions, a large excitation force is generated by a small change in air pressure based on the resonance action of the vibration system, so that the internal pressure of the fluid chamber and the control of the fluid flow are efficiently and effectively performed. You get.

Therefore, in such a fluid-filled type vibration damping device, the internal pressure of the pressure receiving chamber can be advantageously controlled without incorporating an actuator such as an electromagnetic driving means inside the device, thereby reducing the number of parts and the structure. Can be simplified, productivity and cost can be improved, and the device can be advantageously made compact and lightweight.

In such a fluid-filled type vibration damping device, since the internal pressure of the fluid chamber is controlled using an appropriate external air pressure source, continuous operation for a long period of time is only required if an appropriate air pressure source is secured. In a typical use, the desired vibration damping performance can be stably obtained without causing a problem such as high temperature due to heat generation and an increase in power consumption. In such a case, since a negative pressure can be easily obtained in the internal combustion engine, there is no need to newly provide a special air pressure source, and the internal pressure of the fluid chamber can be advantageously controlled. ,
It is possible to stably obtain the desired vibration isolation performance.

In addition, in such a fluid-filled type vibration damping device, problems such as an increase in size of the device and an increase in energy consumption are caused by utilizing a resonance action of a vibration system constituted by an elastic plate and a mass member. Without this, a dramatic improvement in vibration isolation performance can be achieved. In addition, as the material of the elastic plate forming the movable member, various elastic materials such as a rubber elastic body, a synthetic resin, and a metal can be adopted according to a vibration frequency to be damped.

The invention described in claim 2 is the first invention.
In the fluid filled type vibration damping device having a structure according to the invention described in the above, the fluid chamber is a main liquid chamber in which a part of a wall is formed by the main rubber elastic body and an internal pressure change is generated at the time of vibration input. The main liquid chamber is configured so as to include another part of the wall portion of the main liquid chamber, and the internal liquid pressure is directly applied to the main liquid chamber by the vibration of the movable member. The feature is that it is.

In the fluid filled type vibration damping device having the structure according to the second aspect of the present invention, the internal pressure of the main liquid chamber is directly controlled by vibrating the movable member, so that the vibration damping characteristics are improved. You can control it. At this time, the movable member can be efficiently vibrated without using an apparatus having a large size or an increase in energy consumption by utilizing the resonance action of the vibration system constituted by the elastic plate and the mass member. Therefore, the internal pressure of the main liquid chamber and, consequently, the vibration isolation characteristics can be advantageously controlled.

The invention described in claim 3 is the first invention.
Or a fluid-filled type vibration damping device having a structure according to the invention described in 2, wherein the fluid chamber has a main liquid chamber in which a wall portion is formed by the main rubber elastic body and an internal pressure change is generated at the time of vibration input. The movable member forms a part of a wall portion and includes a sub liquid chamber which is communicated with the main liquid chamber through an orifice passage. Is characterized in that it can be generated.

In the fluid filled type vibration damping device having the structure according to the third aspect of the present invention, the movable member is vibrated by applying air pressure fluctuation to the working air chamber, and the pressure is applied to the auxiliary liquid chamber. Since the change is exerted, the internal pressure of the sub liquid chamber is controlled by vibrating the movable member with an appropriate phase difference with respect to the input vibration, taking into account the pressure fluctuation of the main liquid chamber due to the vibration input. The desired vibration damping characteristics can be advantageously obtained based on the flow action of the fluid to be caused to flow and the internal pressure control of the main liquid chamber through the orifice passage. At this time, the movable member can be efficiently vibrated without using an apparatus having a large size or an increase in energy consumption by utilizing the resonance action of the vibration system constituted by the elastic plate and the mass member. Therefore, the internal pressure of the auxiliary liquid chamber and, consequently, the vibration isolation characteristics can be more advantageously controlled.

The invention described in claim 4 is the same as the invention described in claim 2.
Or a fluid-filled type vibration damping device having a structure according to the invention described in 3 above, wherein an equilibrium chamber in which a part of a wall portion is formed of a flexible film and volume change is allowed is provided, and the equilibrium chamber is provided with the equilibrium chamber. It is characterized in that an incompressible fluid is sealed, and a fluid communication path is provided for communicating the equilibrium chamber with the main liquid chamber.

In the fluid filled type vibration damping device having the structure according to the fourth aspect of the present invention, a pressure change is generated in the main liquid chamber at the time of vibration input, so that the main liquid chamber and the equilibrium chamber are separated. A pressure difference occurs between the two chambers, and a fluid flow is generated between the two chambers through the fluid communication passage, and based on a fluid action such as a resonance action of the fluid caused to flow through the fluid communication passage, An effective anti-vibration effect is exhibited.

Therefore, if the fluid communication passage is tuned differently from the orifice passage formed between the main liquid chamber and the sub liquid chamber, the input vibration at which the orifice passage exerts the vibration damping effect will not be obtained. An effective vibration damping effect can be obtained for different vibrations, and the vibration damping performance can be further improved.

The invention described in claim 5 is the first invention.
The fluid-filled type vibration damping device having a structure according to any one of claims 1 to 4, wherein the elastic plate constituting the movable member has a restoring force to a constant shape based on elasticity. Features.

In the fluid filled type vibration damping device having the structure according to the fifth aspect of the present invention, the movable member returns to a substantially constant position under a state where the air pressure applied to the working air chamber is released. Because it is held, the internal pressure of the fluid chamber can be easily controlled. Further, when the air pressure exerted on the working air chamber is released, the movable member is returned to a predetermined position, so that, for example, only one of the negative pressure and the positive pressure is used as the air pressure exerted on the working air chamber. The movable member can be vibrated advantageously by employing a fluctuating air pressure, or a fluctuating air pressure by alternately switching between one of a certain level of negative pressure or positive pressure and atmospheric pressure. .

In order to assist the restoring force to a constant shape based on the elasticity of the elastic plate, it is possible to provide an urging means for constantly applying an urging force in a specific direction to the elastic plate.
For example, if a coil spring or the like is employed as the urging means, it is possible to obtain the resilience of the elastic plate to a constant shape extremely advantageously and stably for a long period of time.

The invention described in claim 6 is the first invention.
6. A fluid-filled vibration damping device having a structure according to any one of the above-described inventions, wherein a pneumatic pressure control device is provided for changing an air pressure applied to the working air chamber in synchronization with a frequency of vibration to be damped. Is characterized.

In the fluid filled type vibration damping device having the structure according to the sixth aspect, the internal pressure of the fluid chamber is controlled in accordance with the input vibration to be damped, thereby being effective against the input vibration. A very effective anti-vibration effect can be achieved, for example, the anti-vibration effect by controlling the internal pressure of the main liquid chamber and the anti-vibration effect based on the flow action such as the resonance action of the fluid flowing through the orifice passage. It can be done. In order to change the air pressure of the working air chamber in synchronization with the frequency of the vibration to be damped, for example, the working air chamber is moved between the air pressure source such as a negative pressure and the atmosphere by switching the switching valve. It can be advantageously made by connecting alternatively. At this time, for example, an electromagnetic switching valve or the like can be suitably used as the switching valve so that control can be easily performed and switching can be performed at high speed. For example, based on a vibration signal detected by an acceleration sensor or the like, By controlling the switching valve for controlling the air pressure to the working air chambers by known adaptive control or map control, the air pressure control of each working air chamber can be advantageously performed.

[0027]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 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.

FIG. 1 shows an engine mount 10 for a vehicle according to a first embodiment of the present invention. The engine mount 10 has a first mounting member 12 and a second mounting member 14 as a first mounting member and a second mounting member which are arranged opposite to each other at a predetermined distance from each other. The two mounting brackets 12 and 14 are connected by a main rubber elastic body 16, and one of the first mounting bracket 12 and the second mounting bracket 14 is mounted on one of the power unit side and the body side.
The power unit is designed to support the body against vibration. In the engine mount 10, a main unit rubber elastic body 16 is compressed and deformed when a power unit load is applied when the engine mount 10 is mounted on an automobile. Further, in such a mounted state, vibration to be damped is input in a direction substantially opposite to the first mounting member 12 and the second mounting member 14 (vertical direction in FIG. 1).
In the following description, the terms “upper” and “lower” mean, in principle, “upper” and “lower” in FIG.

More specifically, the first mounting member 12 includes an inverted cup-shaped upper metal member 18 and a tapered cylindrical lower metal member 20.
Are overlapped with each other in a fluid-tight manner in the axial direction, and a flange portion 22 formed on an opening peripheral portion of the upper fitting 18 and a flange portion 24 formed on a large-diameter opening peripheral portion of the lower fitting 20 are bolt-connected. And is formed with a hollow structure. The hollow inside of the first mounting member 12 is opened downward through an opening 26 on the small diameter side of the lower metal member 20. A mounting bolt 28 protruding outward is fixed to the bottom wall of the upper bracket 18 so that the first mounting bracket 12 can be mounted on the power unit side or the body side by the mounting bolt 28. Has become.

A first movable member 30 is housed and arranged inside the hollow of the first mounting member 12. The first movable member 30 has a first rubber elastic plate 32 having a disk shape with a predetermined thickness.
2, a disk-shaped first mass metal fitting 34
A constraining ring 36 is concentrically disposed at a predetermined distance around the outer periphery of the first mass metal fitting 34 and is vulcanized and adhered to the first rubber elastic plate 32. Further, a press-fit ring 3 is provided on the outer peripheral surface of the first rubber elastic plate 32.
When the press-fit ring 38 is press-fitted and fixed to the large-diameter opening of the lower fitting 20, the first movable member 30 covers the large-diameter opening in a fluid-tight manner. It is assembled in a state where it does. As a result, the hollow interior of the first mounting member 12 is partitioned by the first movable member 30 and is divided into the upper metal member 18 and the lower metal member 20 in a fluid-tight manner.

Here, the first movable member 30 is formed by fixing the outer peripheral edge of the first rubber elastic plate 32 to the first mounting member 12 so that the first rubber elastic plate 32 Based on the spring rigidity of the first rubber elastic plate 32 as a whole, even if the first rubber elastic plate 32 is deformed by a large external force, by removing the external force, One rubber elastic plate 32
Based on the restoring force due to the elasticity of the plate, the plate is restored and held in an initial state having a flat plate shape as a whole.

Further, by attaching the first movable member 30 to the first mounting member 12, a first vibration system having the first rubber elastic plate 32 as a spring and the first mass metal member 34 as a mass is formed. It is configured. The first rubber elastic plate 3
2, the spring constant is adjusted by the restraining ring 36, and irregular deformation is prevented, so that stable spring characteristics are exhibited. By adjusting the spring constant of the first rubber elastic plate 32 constituting the first vibration system and the mass of the first mass metal fitting 34, the natural frequency in the first vibration system is reduced. The tuning is set in accordance with the power frequency to be tuned.

On the other hand, the second mounting member 14 includes an annular block-shaped peripheral wall metal member 40 and a disk-shaped bottom wall metal member 42.
Are formed by being overlapped with each other in the axial direction and connected by bolts, and as a whole, have a thick bottomed cylindrical shape having a concave portion 44 that opens upward in a central portion. . The bottom wall fitting 42 is provided with a mounting bolt 45 protruding above the bottom surface, and the second mounting fitting 14 is mounted on the body side or the power unit side by the mounting bolt 45. .

The second mounting member 14 is opposed to the first mounting member 12 at a predetermined distance axially below the first mounting member 12 with a predetermined distance therebetween. The body 16 elastically connects the two mounting brackets 12 and 14. The main rubber elastic body 16 is
It has a thick tapered cylindrical shape, and its small-diameter side opening is vulcanized and adhered to the outer peripheral surface of the lower fitting 20 constituting the first mounting fitting 12, while its large-diameter side is A connection ring 46 is vulcanized and adhered to the opening, and the connection ring 46 is used to form the second mounting member 14.
It is superimposed on the top of
The large-diameter opening is fixed to the second mounting member 14.
A substantially annular restraining member 48 is vulcanized and bonded to an axially intermediate portion of the main rubber elastic body 16 in order to stabilize elastic deformation and prevent buckling or the like.

The recess 4 in the second mounting member 14
4, the second movable member 49 and the partition member 52
Are arranged so as to be overlapped with each other in the axial direction, and the outer peripheral edges overlapped with each other are clamped by the attachment portion of the connection ring 46 to the peripheral wall metal fitting 40,
It is assembled to the second mounting bracket 14.

The second movable member 49 has a second rubber elastic plate 50 having a disc shape having a predetermined thickness.
A substantially disk-shaped second mass fitting 53 is vulcanized and bonded to the center of the second rubber elastic plate 50. Then, by being fixed to the second mounting member 14 at the outer peripheral edge of the second rubber elastic plate 50, the second movable member 4
9 is provided to cover the opening of the recess 44 in the second mounting member 14 in a fluid-tight manner. Although the second rubber elastic plate 50 is thinner than the first rubber elastic plate 32, even when the second rubber elastic plate 50 is subjected to tensile deformation by an external force, by removing the external force, based on the restoring force due to its elasticity, It is restored and kept in the initial state.

Further, by attaching the second movable member 49 to the second mounting member 14, the second vibration system having the second rubber elastic plate 50 as a spring and the second mass metal member 53 as a mass is formed. It is configured. Then, by adjusting the spring constant of the second rubber elastic plate 50 and the mass of the second mass metal fitting 53 constituting the second vibration system, the natural frequency of the second vibration system is reduced. The tuning is set in accordance with the power frequency to be tuned.

On the other hand, the partitioning member 52 is constituted by an upper partitioning plate 54 and a lower partitioning plate 56 each having a substantially disc shape, which are superposed in the axial direction, and is superposed on the second rubber elastic plate 50. And the second mounting bracket 1
4, the large-diameter opening of the main rubber elastic body 16 is fluid-tightly covered. In the partition member 52, an orifice passage 58 extending around the outer peripheral portion by a predetermined length in the circumferential direction is formed between the overlapping surfaces of the upper and lower partition plates 54 and 56.

Thus, on one side (upper side) with respect to the partition member 52, a part of the wall is constituted by the main rubber elastic body 16, and the portion between the first mounting bracket 12 and the second mounting bracket 14 is formed. A main liquid chamber 60 is formed in which an internal pressure change is caused based on the elastic deformation of the main rubber elastic body 16 when vibration is input to the main rubber elastic body 16. The main liquid chamber 60 is filled with an incompressible fluid such as water, alkylene glycol, polyalkylene glycol, and silicone oil. It is preferable that a low-viscosity fluid having a viscosity of 0.1 Pa · s or less be used as the sealed fluid in order to effectively obtain the resonance action of the fluid.

Here, the main liquid chamber 60 includes the hollow inside of the lower fitting 20 which is partitioned by the first movable member 30 in the first mounting fitting 12, and a part of the wall portion. Are constituted by the first movable member 30. Further, in the first mounting bracket 12, the first movable member 30
A first working air chamber 62 positioned opposite to the main liquid chamber 60 with the first movable member 30 interposed therebetween is formed in the hollow inside of the upper fitting 18 which is partitioned by. In addition, a first port portion 64 communicated with the first working air chamber 62 is provided on a peripheral wall portion of the upper fitting 18.

On the other side (lower side) of the partition member 52, a part of the wall is constituted by the second movable member 49, and the same incompressible fluid as the main liquid chamber 60 is sealed therein. The formed sub liquid chamber 66 is formed. The auxiliary liquid chamber 66 is provided in the orifice passage 5 provided in the partition member 52.
8, the main fluid chamber 60 communicates with the main fluid chamber 60, and between the main fluid chamber 60 and the sub-fluid chamber 66, fluid flow through the orifice passage 58 based on the internal pressure difference between the two chambers 60, 66 is allowed. It has become.

In the present embodiment, the orifice passage 58 is formed by the second rubber elastic plate 50 and the second mass metal fitting 5.
The tuning is performed in accordance with the natural frequency of the second vibration system constituted by 3. Thereby, the length of the orifice passage 58 and the length of the orifice passage 58 are so set that the vibration damping effect based on the resonance action of the fluid caused to flow through the orifice passage 58 is effectively exhibited in the frequency range substantially equal to the natural frequency of the second vibration system. The cross-sectional area is set.

Further, on the side opposite to the auxiliary liquid chamber 66 with the second rubber elastic plate 50 interposed therebetween, the recess 4 of the second mounting member 14 is provided.
The second working air chamber 68 is formed by covering the 4 with the second movable member 49. An air supply / discharge passage 69 communicated with the second working air chamber 68 is provided in the second mounting member 14 so as to penetrate through the bottom wall fitting 42. A second port portion 70 is fixed to the outside opening of the second port.

In the engine mount 10 having the above-described structure, the first pneumatic line 72 is connected to the first port portion 64 when mounted on the automobile. Through the first working air chamber 62
Is connected to the first switching valve 74 and the negative pressure tank 76. Then, in accordance with the switching operation of the first switching valve 74, the first working air chamber 62 is selectively connected to the negative pressure tank 76 and the atmosphere.

A second pneumatic line 78 is connected to the second port portion 70. Through this second pneumatic line 78, a second working air chamber 68 is connected to a second switching valve. 80 and a negative pressure tank 82. Then, in accordance with the switching operation of the second switching valve 80, the second working air chamber 68 is selectively connected to the negative pressure tank 82 and the atmosphere. The negative pressure tank 82 to which the second working air chamber 68 communicates may be the same as the negative pressure tank 76 to which the first working air chamber 62 communicates.

That is, in the engine mount 10 mounted as described above, the switching operation of the first switching valve 74 allows the negative pressure and the atmospheric pressure to be selectively applied to the first working air chamber 62. And the switching operation of the second switching valve 80 causes the second working air chamber 68
, The negative pressure and the atmospheric pressure are applied alternatively. Therefore, by switching the first switching valve 74 and the second switching valve 80 at an appropriate cycle,
Periodic air pressure fluctuations can be generated in the first working air chamber 62 and the second working air chamber 68, and this air pressure fluctuation causes the first movable member 30 and the second movable member 49. , The first movable member 30 and the second movable member 49 are vibrated.

Here, the first movable member 30 has a structure in which a restoring force to a constant shape is exhibited based on the elasticity of the first rubber elastic plate 32. When the first working air chamber 62 is connected to the atmosphere, it is held in a substantially flat plate shape based on the restoring force due to the elasticity of the first rubber elastic plate 32. The first rubber elastic plate 32 is deformed and displaced upward (to the first working air chamber 62 side) against the elasticity of the first rubber elastic plate 32. When the negative pressure is released from that state, the first rubber elastic plate 32 is released. By the restoring force based on the elasticity of the elastic member 32, the restoring deformation is displaced downward (toward the main liquid chamber 60). As a result, the first movable member 30 is moved to the first switching valve 74.
Is reciprocated up and down (vibration) in accordance with the operation of the valve. Thus, the internal pressure of the main liquid chamber 60 fluctuates.

Accordingly, the first switching valve 74 is switched at a cycle corresponding to the frequency of the input vibration to be damped, and the main liquid chamber 6 is switched.
By causing the internal pressure fluctuation to be zero, an active vibration damping effect based on the internal pressure control of the main liquid chamber 60 can be effectively obtained. In particular, since the first movable member 30 constitutes a first vibration system including the first rubber elastic plate 32 and the first mass metal fitting 34, the first movable member 30 has a first vibration frequency in the region of the natural frequency. Based on the resonance phenomenon of the movable member 30 itself, a large internal pressure fluctuation can be efficiently generated in the main liquid chamber 60 by an exciting force caused by a small air pressure fluctuation. It can be used effectively.

The natural frequency of the first vibration system constituted by the first movable member 30 is not limited at all, and is set appropriately according to the vibration-proof characteristics required for the mount. However, in particular, the first movable member 30 forms a part of the wall of the main liquid chamber 60, and the vibration thereof causes a direct internal pressure fluctuation in the main liquid chamber 60. Therefore, tuning can be easily performed even in a high frequency region such as a muffled sound, and an anti-vibration effect against high-frequency vibration can be effectively obtained.

Similarly, the second movable member 49 has a structure in which a restoring force to a constant shape is exerted on the basis of the elasticity of the second rubber elastic plate 50. By alternately applying a negative pressure and an atmospheric pressure to the second working air chamber 68 by the switching operation of 80, the reciprocating displacement (vibration) is caused up and down, so that the internal pressure fluctuation occurs in the sub liquid chamber 66. Will be done. Therefore, at the time of vibration input, the second movable member 4 has a period corresponding to the vibration frequency.
9 is vibrated to generate a positive internal pressure change in the sub liquid chamber 66, thereby generating a large internal pressure difference between the main liquid chamber 60 and the sub liquid chamber 66, and causing the fluid flow through the orifice passage 58 to flow. As a result, the vibration damping effect based on the flow action such as the resonance action of the fluid caused to flow through the orifice passage 58 can be more advantageously exerted.

In particular, since the second movable member 49 constitutes a second vibration system including the second rubber elastic plate 50 and the second mass metal fitting 53, the second movable member 49 has a characteristic frequency in the range of its natural frequency. Based on the resonance phenomenon of the second movable member 49 itself, a large internal pressure fluctuation can be efficiently generated in the sub liquid chamber 66 by an exciting force due to a small air pressure fluctuation. Therefore, in the orifice passage 58 tuned in accordance with the natural frequency of the second movable member 49, the fluid flow rate in the tuning frequency range can be more advantageously ensured. The vibration damping effect based on the resonance action of the fluid caused to flow through the passage 58 is more advantageously exerted.

The natural frequency of the second vibration system constituted by the second movable member 49 and the tuning range of the resonance frequency of the orifice passage 58 are not limited at all, and are required for the mount. Although it is appropriately set according to the vibration isolation characteristics, preferably, the natural frequency of the second vibration system and the resonance frequency of the orifice passage 58 are the same as those defined by the first movable member 30. It is set lower than the natural frequency of the first vibration system. Thereby,
For input vibration in a low frequency range, the orifice passage 5
In addition to obtaining an anti-vibration effect based on the resonance action of the fluid flowed through 8, the internal pressure of the main liquid chamber 60 by vibrating the first movable member 30 is controlled against input vibration in a high frequency range. It is possible to obtain an anti-vibration effect based on the above. Specifically, for example, while the natural frequency of the second vibration system and the resonance frequency of the orifice passage 58 are tuned to a medium frequency vibration range such as idling vibration, the natural vibration of the first movable member 30 The number is tuned for a high frequency vibration region such as a muffled sound.

In order to obtain an anti-vibration effect based on the resonance action of the fluid caused to flow through the orifice passage 58, the first movable member 30 is applied with a phase substantially opposite to that of the second movable member 49. By vibrating, the internal pressure difference between the main liquid chamber 60 and the sub liquid chamber 66 is increased, and the amount of fluid flowing through the orifice passage 58 is increased, thereby further improving the vibration damping effect based on the resonance action of the fluid. It is also possible to plan.

Further, for example, when a vibration is input in a frequency range lower than the tuning frequency of the orifice passage 58, the first movable member 30 and the second movable member 49 are vibrated in substantially the same phase to cause the main liquid chamber 60 to vibrate. And the sub-fluid chamber 66 generate an internal pressure fluctuation in substantially the same phase as the internal pressure fluctuation caused in the main liquid chamber 60 based on the elastic deformation of the main rubber elastic body 16 due to the input vibration, thereby providing effective vibration damping. The effect can also be obtained.

In the vibration control of the rubber elastic plate 32 and the rubber elastic film 50, feedback control such as adaptive control using a reference signal corresponding to an input vibration detected by an acceleration sensor or the like, map control, and the like are performed. Any of them can be adopted, and the period, the phase difference, the excitation force, and the like are determined so that the required vibration isolation performance is advantageously achieved.

Further, in this engine mount 10, since it is not necessary to incorporate an actuator member such as an electromagnetic drive means into the engine mount 10 itself, the structure is extremely simple and easy to manufacture, and the engine mount 10 is lightweight, compact and inexpensive. There is a big advantage that there is. Moreover, since the structure is simple, it has excellent durability and reliability,
There is also an advantage that it is easy to cope with a failure.

In short, according to the structure of the present embodiment as described above, it is possible to obtain an effective vibration damping effect against various input vibrations by actively controlling the internal pressures of the main liquid chamber 60 and the sub liquid chamber 66. A possible engine mount 10 can be advantageously realized with a compact size and a simple structure. In addition, the first movable member 30 and the second movable member 49 are configured to include a vibration system, and the first working air chamber 62 and the second working air chamber 68 The first movable member 30 and the second movable member 49
Is exerted on the main liquid chamber 60 and the sub liquid chamber 66, whereby a large internal pressure can be adjusted. Therefore, the internal pressure of the main liquid chamber 60 and the orifice passage 58 can be controlled.
The vibration-proofing effect based on the fluid flow and the like can be extremely efficiently and effectively exerted.

In the engine mount 10,
Since the main liquid chamber 60 and the sub liquid chamber 66 can be pressure-controlled by using the negative pressure, it is necessary to effectively use the negative pressure generated in the intake system and the like, particularly in an automobile using an internal combustion engine. This has the advantage that no special drive energy generating means is required.

Further, in such an engine mount 10, even during continuous operation, there is no problem of energized heat generation and power consumption, and stable performance is exhibited for a long time.

When the compressed air can be easily obtained, the first movable member 3 is formed by using the positive pressure instead of the negative pressure.
0 or the second movable member 49 may be displaced, and the rubber elastic plate 32 and the rubber elastic film 50 may be deformed and displaced by increasing or decreasing the pressure within the range of negative pressure or positive pressure. It is possible.

Further, in order to assist the restoring force due to the elasticity of the first rubber elastic plate 32 and to exhibit stable characteristics over a long period of time, the first rubber elastic plate 32 and the upper bracket 18 are provided between the first rubber elastic plate 32 and the upper bracket 18. It is also effective to dispose a biasing means such as a coil spring to constantly bias the first rubber elastic plate 32 in the direction opposite to the direction of deformation due to negative pressure.

Further, if the natural frequencies of the first movable member 30 and the second movable member 49 are set to substantially the same frequency range, the two movable members 30 and 49 are mutually operated at a frequency corresponding to the input vibration and mutually. By vibrating in substantially the opposite phase, it is possible to further increase the amount of fluid flowing through the orifice passage 58 by utilizing the resonance action of the movable members 30 and 49 in the vibration system. Further, the vibration damping effect based on the resonance action of the fluid with respect to the input vibration in the tuning frequency range of the orifice passage 58 can be further improved.

In the engine mount 10 according to the first embodiment, it is possible to employ only one of the first movable member 30 and the second movable member 49. The effect of improving the vibration isolation characteristics can be effectively exhibited. Specifically, for example, the main liquid chamber 60 is formed between the bottom wall of the lower fitting 20 and the opposing surface of the partition member 52 without providing the opening 26 in the lower fitting 20 constituting the first mounting fitting 12. Accordingly, even when a mount structure having no first movable member or first working air chamber is employed, the fluid flow action through the orifice passage 58 based on the vibration of the second rubber elastic plate 50 can be achieved. The vibration damping effect based on the above can be effectively exhibited. Also, for example, when the partition member 52 is not provided with an orifice passage and adopts a mount structure having no second movable member and no second working air chamber or auxiliary liquid chamber, the first rubber elastic plate 32 may be used. Based on the vibration, the vibration damping effect based on the internal pressure control of the main liquid chamber 60 can be effectively exhibited.

Next, FIG. 2 shows an engine mount 84 according to a second embodiment of the present invention. In the present embodiment, members and parts having the same structure as the engine mount 10 according to the first embodiment are the same as those in the engine mount 10 according to the first embodiment in the drawings. The detailed description thereof is omitted by attaching the reference numerals.

That is, in the engine mount 84 according to the present embodiment, the opening 26 is not provided in the lower fitting 20 constituting the first mounting fitting 12, and the lower fitting 2 is not provided.
The main liquid chamber 60 is formed between the bottom wall portion of the O and the opposing surface of the partition member 52. A thin elastic disk-like rubber elastic film 85 as a flexible film is accommodated and arranged in the hollow inside of the first mounting member 12.
The first mounting member 12 is disposed so as to be fluid-tightly partitioned between the upper fitting 84 and the lower fitting 86 by being sandwiched between the first and second fittings 8 and 20. This allows
One side (lower fitting 20 side) of the rubber elastic film 85 is filled with the same incompressible fluid as that of the main liquid chamber 39 so that a volume change based on the deformation of the rubber elastic film 85 is easily allowed. An air chamber 87 is formed on the other side (upper bracket 18 side) of the rubber elastic film 85 so as to communicate with the external space and allow the rubber elastic film 85 to be deformed. .

Further, on the bottom wall of the lower fitting 20 constituting the first mounting fitting 12, a disc-shaped passage forming fitting 88 is overlapped and fixed by bolts.
A fluid communication passage 89 is formed between the superimposed surface of the passage 0 and the passage forming metal member 88 and extends a little less than one circumference in the circumferential direction and communicates the main liquid chamber 60 and the equilibrium chamber 86 with each other.

In the engine mount 84 having such a structure, the fluid flow through the orifice passage 58 is caused by the vibration of the second movable member 49, similarly to the engine mount (10) according to the first embodiment. The vibration-proofing effect based on the action is effectively exerted. In addition, when the internal pressure fluctuation is generated in the main liquid chamber 60 based on the elastic deformation of the main rubber elastic body 16 at the time of vibration input,
Since the fluid flow through the fluid communication passage 89 is generated based on the internal pressure difference between the main liquid chamber 60 and the equilibrium chamber 86,
A predetermined vibration damping effect can also be obtained by such a fluid action as the resonance action of the fluid.

As in the case of the orifice passage 58, the fluid communication passage 89 has an input vibration in a frequency range in which a vibration damping effect based on the fluid flow action is intended by adjusting the flow passage cross-sectional area and length. It is possible to tune so that it is exhibited against, the tuning frequency is appropriately determined according to the required anti-vibration characteristics and the like, and is not limited, but preferably, In a frequency range lower than the tuning frequency of the orifice passage 58,
The fluid communication passage 89 is tuned. Specifically, for example, the fluid communication passage 89 is tuned corresponding to low frequency vibration such as shake, the orifice passage 58 is tuned corresponding to medium frequency vibration such as idling vibration, or the fluid communication passage 89 is tuned to idle vibration. And the orifice passage 58 is tuned to high frequency vibration such as muffled sound. As a result, both the vibration damping effect of the orifice passage 58 and the vibration damping effect of the fluid communication passage 89 are effectively exerted for input vibrations in different frequency ranges. In addition, also when obtaining the vibration-proof effect by the fluid communication passage 89, the second movable member 49 is vibrated in synchronization with the input vibration, and
6 through the orifice passage 58.
By positively causing the internal pressure fluctuation of the main liquid chamber 60, it is possible to further improve the vibration isolation effect by increasing the amount of fluid flowing through the fluid communication passage 89.

Further, FIGS. 3 to 5 show a cylindrical engine mount 90 as a third embodiment of the present invention.

In this engine mount 90, an inner cylindrical fitting 92 as a first mounting member and an outer cylindrical fitting 94 as a second mounting member are arranged at a predetermined distance in the radial direction. Rubber elastic body 96 interposed between
And an inner cylinder fitting 92 and an outer cylinder fitting 94.
Is attached to either the power unit side or the body side, so that the power unit is supported on the body by vibration isolation. In the engine mount 90, the inner and outer cylinder fittings 92, 9 are provided.
4 are eccentrically positioned by a predetermined amount, and the inner and outer cylindrical metal fittings 9 are compressed and deformed by the load of the power unit at the time of mounting on the automobile.
2, 94 are positioned substantially coaxially. Further, the vibration to be damped is input in a substantially eccentric direction (up and down direction in FIG. 3) of the inner and outer cylindrical fittings 92 and 94.

More specifically, the inner cylindrical fitting 92 has a thick small-diameter cylindrical shape, and is radially outwardly eccentric at a predetermined distance and a predetermined amount to form a metal sleeve 98.
Are arranged. The metal sleeve 98 has a thin-walled large-diameter cylindrical shape, and stepped portions 100 each having a slightly smaller diameter are formed continuously in the circumferential direction near both ends in the axial direction. Also, such a metal sleeve 98
The window 102 is provided on the side where the separation distance is large in the eccentric direction, while the pocket-shaped concave part that opens to the outer peripheral side at the center portion is provided on the side where the separation distance is small in the eccentric direction. 104 are formed.

The main rubber elastic body 96 is interposed between the inner cylindrical metal fitting 92 and the metal sleeve 98, and the outer peripheral surface of the inner cylindrical metal fitting 92 and the inside of the metal sleeve 98 with respect to the main rubber elastic body 96. The peripheral surfaces are respectively vulcanized and adhered.
Further, a slit 106 is provided between the inner cylinder fitting 92 and the metal sleeve 98 on the side where the separation distance in the eccentric direction is small, extends over substantially half a circumference in the circumferential direction, and penetrates in the axial direction.
The slit 106 allows the main rubber elastic body 96 to be substantially interposed only between the radially opposed surfaces of the inner cylindrical fitting 92 and the metal sleeve 98, on the side where the separation distance is large in the eccentric direction. Is equipped. Thus, the tensile stress of the main rubber elastic body 96 when the power unit load is input is reduced. A buffer rubber 108 is provided on the surface of the inner cylinder fitting 92 on the side of the slit 106, and the inner cylinder fitting 92 comes into contact with the concave portion 104 of the metal sleeve 98 via the cushion rubber 108, so that the main body is formed. Excessive tensile deformation of the rubber elastic body 96 is prevented.

The main rubber elastic body 96 is formed with a pocket portion 110 which opens on the side where the separation distance between the inner cylinder fitting 92 and the metal sleeve 98 in the eccentric direction is large, and the window portion 102 of the metal sleeve 98 is formed. Through the outer peripheral surface. Furthermore, a thin seal rubber layer 112 is formed integrally with the main rubber elastic body 96 on the outer peripheral surface of the metal sleeve 98.

As described above, the integrally vulcanized molded product of the inner cylindrical metal member 92 and the main rubber elastic body 96 having the metal sleeve 98 includes the orifice member 114 and the mounting metal member 116 each having a substantially semi-cylindrical shape as a whole. The metal sleeve 9 is fitted from both sides in the radial direction so as to have a cylindrical shape.
An outer cylindrical fitting 94 having a large-diameter cylindrical shape is externally inserted so as to be assembled on the outer peripheral surface of the central portion in the axial direction of 8 and to cover and support the outer peripheral surfaces of the orifice member 114 and the mounting bracket 116. And is externally fixed to the metal sleeve 98.

The orifice member 114 has a thick semi-cylindrical shape, and includes the inner cylindrical fitting 92 and the metal sleeve 9.
8 is disposed on the outer peripheral surface of the metal sleeve 98 on the side where the separation distance in the eccentric direction is large, and has both ends in the axial direction and both ends in the circumferential direction at the window 10 in the metal sleeve 98.
2 and the outer peripheral surface of the outer cylindrical fitting 94 is supported.
Are fixedly disposed so as to cover the window 102 of the metal sleeve 98 which is the opening of the pocket 110. The opening of the pocket portion 110 is covered in a fluid-tight manner as described above, so that water, alkylene glycol, polyalkylene glycol,
An incompressible fluid such as silicone oil is sealed therein, and a main liquid chamber 118 is formed in which an internal pressure change is caused by elastic deformation of the main rubber elastic body 96 at the time of vibration input.

Further, the orifice member 114 is provided with a through hole 120 located at a central portion facing the main liquid chamber 118, and the through hole 120 is fluid-tightly covered to form a first movable member. 122 are provided. The first movable member 122 has a substantially cylindrical bottomed first mass metal fitting 124 vulcanized and bonded to a central portion of a first rubber elastic plate 126 having a substantially disk shape with a predetermined thickness. The outer peripheral edge of the first rubber elastic plate 126 is
4, the first rubber elastic plate 1
Based on the spring stiffness of 26, the first orifice member 114 is held in a shape to enter the pocket portion 110 from the through hole 120 of the orifice member 114, and even if a large external force is applied and deformed, the first external force is removed. The initial state shown in the figure is restored and held based on the restoring force due to the elasticity of the rubber elastic plate 126. As a result, a part of the wall of the main liquid chamber 118 is
22 and the first movable member 122
The first movable member 1 is located on the side opposite to the main liquid chamber 118 with the first movable member 1 therebetween.
A sealed first working air chamber 128 is formed between the outer casing 22 and the outer tube fitting 94.

Further, a coil spring 132 is accommodated in the first working air chamber 128, and is disposed between the outer tube fitting 94 and the first mass fitting 124. And
The urging force of the coil spring 132 is the first mass metal fitting 1
The first rubber elastic plate 126 is always extended in a direction to separate the first movable member 122 from the outer cylinder fitting 94, that is, a direction to displace the first movable member 122 toward the main liquid chamber 118.
Is assisted by the urging force of the coil spring 132, and is advantageously secured for a long period of time.

In short, in this embodiment, in the first movable member 122, the first mass metal fitting 124 is used as a mass, the first rubber elastic plate 126 and the coil spring 13 are used.
A first vibration system having a spring as a restoring force due to the elasticity of the second member is formed. Then, the natural frequency in the first vibration system is set corresponding to the vibration frequency to be damped.

The outer cylinder fitting 94 is provided with a first port portion 130 which is in communication with the first working air chamber 128. When the first port portion 130 is mounted on an automobile, the first port portion 130 is provided. A pneumatic line 134 is connected to 130, through which a first working air chamber 128 is switched via a first switching valve 136 between a negative pressure tank 138 and the atmosphere. I am being squeezed. As a result, like the first working air chamber (62) in the first embodiment, a periodic air pressure fluctuation is generated in the first working air chamber 128 according to the switching operation of the first switching valve 136. , The first movable member 122 is vibrated.

On the other hand, the mounting member 116 has a thin semi-cylindrical shape, and the inner cylindrical member 92 and the metal sleeve 98 are provided.
Is disposed on the outer peripheral surface of the metal sleeve 98 on the side where the separation distance in the eccentric direction is small, and both edges in the axial direction are supported by the steps 100, 100 of the metal sleeve 98, and the outer peripheral surface is By being supported by the metal fitting 94, the metal sleeve 98 is fixedly disposed so as to cover the opening of the concave portion 104 in the metal sleeve 98. Further, a partition wall 140 that protrudes radially inward at the center in the circumferential direction is fixed to the mounting bracket 116.
Enters the recess 104 of the metal sleeve 98 and the recess 1
04 is closely contacted with the inner peripheral surface of the
4 is fluid-tightly divided into two parts on both sides in the circumferential direction with the partition wall 140 interposed therebetween. The contact surface of the partition wall 140 with the concave portion 104 is covered with a seal rubber 142 to ensure fluid tightness.

Further, a first opening 144 and a second opening 146 are formed in the mounting bracket 116 on both sides in the circumferential direction independently of each other, and the first opening 144 and the second opening 146 are formed separately. The flexible membrane 148 and the second movable member 150 are provided, respectively, so as to cover the opening 146 in a fluid-tight manner.

The flexible film 148 is formed of an easily deformable thin rubber elastic film having a substantially disk shape swelling on one surface side, and has an outer peripheral edge formed by the first metal member of the mounting bracket 116. The first opening 144 is fluid-tightly covered by being vulcanized and bonded to the inner peripheral edge of the opening 144. As a result, the opening on one side in the circumferential direction of the recess 104 is covered with the flexible film 148 in a fluid-tight manner, and the equilibrium chamber 152 in which the same incompressible fluid as the main liquid chamber 118 is sealed is formed. Have been.

On the other hand, the second movable member 150 is substantially disc-shaped with respect to the central portion of the second rubber elastic plate 153 having a substantially disc shape having a predetermined thickness swelling on one surface side. The second mass metal fitting 155 is vulcanized and bonded, and the outer peripheral edge of the second rubber elastic plate 153 is vulcanized and bonded to the inner peripheral edge of the first opening 144 in the mounting bracket 116. The first opening 144 is fluid-tightly covered.
Thus, the opening on the other side in the circumferential direction of the recess 104 is covered with the second movable member 150 in a fluid-tight manner, and the sub-liquid chamber 154 in which the same incompressible fluid as the main liquid chamber 118 is sealed. Are formed.

Further, the second movable member 150 is held in such a shape as to enter the concave portion 104 from the second opening 146 in the mounting bracket 116 based on the spring rigidity of the second rubber elastic plate 153, and temporarily. Even when a large external force is applied and deformed, by removing the external force, the initial state shown in the figure is restored and held based on the restoring force due to the elasticity of the second rubber elastic plate 153. ing. And such a second movable member 150
A part of the wall portion of the sub liquid chamber 154 is formed by the sub liquid chamber 154, and the sub liquid chamber 154 is sandwiched by the second movable member 150.
On the opposite side, a sealed second working air chamber 156 is formed between the second movable member 150 and the outer cylinder fitting 94.

Also, there, the second movable member 15
At 0, a second vibration system is configured in which the second mass metal fitting 155 is used as a mass and the restoring force due to the elasticity of the second rubber elastic plate 153 is used as a spring. Then, the natural frequency of the second vibration system is set corresponding to the vibration frequency to be damped.

Further, the outer cylinder fitting 94 is provided with a second port portion 158 which is communicated with the second working air chamber 156. When the second port portion 158 is mounted on a vehicle, the second port portion 158 is provided. A pneumatic line 160 is connected to 158 through which a second working air chamber 156 is connected via a second switching valve 162.
The connection between the negative pressure tank 164 and the atmosphere is switched. Thereby, similarly to the second working air chamber (68) in the first embodiment, the second working air chamber 156 is operated according to the switching operation of the second switching valve 162.
The second movable member 150 is caused to reciprocate (vibrate) due to periodic air pressure fluctuations.

Further, the orifice member 114 includes
A first groove 166 and a second groove 168 are formed on the outer peripheral surface and extend at a predetermined length in the circumferential direction, respectively.
By covering these concave grooves 166 and 168 with the outer cylinder fitting 94, a fluid communication passage 170 that connects the main liquid chamber 118 to the equilibrium chamber 152 and a main liquid chamber 118 that connects the sub liquid chamber 154 are formed.
Orifice passages 172 are formed independently of each other. At the time of vibration input, the main liquid chamber 1 passes through the fluid communication passage 170 and the orifice passage 172.
A predetermined vibration damping effect is exerted on the basis of a fluid action such as a resonance action of the fluid which is caused to flow between the fluid chamber 18 and the equilibrium chamber 152 or the auxiliary liquid chamber 154.

The fluid communication passage 170 and the orifice passage 172 are tuned according to the vibration frequency to be damped, for example, like the fluid communication passage (89) and the orifice passage (58) in the second embodiment. Is done.

Accordingly, in the engine mount 90 having such a structure, similarly to the first embodiment,
At the time of vibration input, air pressure fluctuation is applied to the first working air chamber 128 and the second working air chamber 156 at a cycle corresponding to the vibration frequency, and the first movable member 122 and the second movable member 15 are changed.
By vibrating 0 and adjusting the internal pressure of the main liquid chamber 118 and the sub liquid chamber 154, the vibration control effect based on the internal pressure control of the main liquid chamber 118, the fluid flow action through the orifice passage 172, and the like can be effectively obtained. You can do it. Then, there, the first and second movable members 122, 150
Constitute a vibration system in which the natural vibration frequency is set in accordance with the vibration frequency to be damped, and are based on the resonance action of the first and second movable members 122 and 150. In addition, the vibration control effect based on the internal pressure control of the main liquid chamber 118 and the fluid flow action through the orifice passage 172 can be more effectively exerted.

In the engine mount 90 according to the present embodiment, the fluid communication passage 17 is
Since the equilibrium chamber 152 having a variable volume communicated through the fluid communication passage 170 is provided, an effective vibration damping effect is obtained also by the flow action of the fluid made to flow through the fluid communication passage 170 as in the second embodiment. You can do it.

In addition, the engine mount 9 of this embodiment
0, as in the first embodiment, there is no need to incorporate an actuator member such as an electromagnetic driving means into itself, so that the structure is extremely simple and easy to manufacture,
The effects such as light weight, compactness, and low cost are all effectively achieved.

Note that the engine mount 90 of the present embodiment is
In the same manner as in the first embodiment, the positive pressure may be used instead of the negative pressure, and the vibration of the movable members 122 and 150 may be controlled using only one of the negative pressure and the positive pressure. It is possible.

The coil spring 132 disposed in the first working air chamber 128 is not always necessary.
A configuration using only the restoring force based on the elasticity of the first rubber elastic plate 126 can be adopted.

Further, the engine mount 9 of the present embodiment
0, the first movable member 122 and the second movable member 1 are similar to the engine mount according to the first embodiment.
It is also possible to employ only one of the 50, and thereby, the effect of improving the mount anti-vibration characteristics can be effectively exhibited. Further, the equilibrium chamber 152, the fluid communication path 170, and the like are also adopted according to the required characteristics of the mount, and need not necessarily be provided.

Although the embodiments of the present invention have been described in detail above, these are literal examples, and the present invention
The description of these specific embodiments should not be construed as limiting in any way.

For example, in the first and third embodiments, only one first working air chamber for controlling the pressure of the main liquid chamber via the first movable member is formed. A plurality can be provided. Then, by providing a plurality of first working air chambers and a first movable member so as to apply a synchronous air pressure change to each working chamber, the amount of air supply / discharge to each first working air chamber, and hence the first working air chamber Even if the amount of displacement of the first movable member is small, it is possible to exert an effective pressure change on the main liquid chamber, and the responsiveness of pressure control of the main liquid chamber and, consequently, control of the mount anti-vibration characteristics is improved. .

Further, the auxiliary liquid chamber which is communicated with the main liquid chamber through the orifice passage and whose internal pressure is controlled by the second working air chamber via the second movable member also has required vibration-proof characteristics and the like. Can be provided in plurality. In addition, the plurality of sub-liquid chambers are communicated with the main liquid chamber through independent orifice passages, respectively, and the respective orifice passages are tuned differently from each other, so that the action of air pressure on each second working air chamber is achieved. By appropriately controlling the vibration, it is possible to selectively exhibit the anti-vibration effect of each orifice passage according to the input vibration, and to obtain an effective anti-vibration effect for input vibration in a wider frequency range. Become. In this case, for example, by applying air pressure fluctuation of a cycle corresponding to the input vibration frequency to any one of the second working air chambers, one of the sub-liquid chambers and the main By causing a fluid flow through one orifice passage, while applying a constant air pressure to the other second working air chamber to prevent the fluid flow through the other orifice passage, the plurality of orifice passages Can be used selectively.

Further, in the above-described embodiment, the engine mount for the vehicle has been exemplified. However, the present invention is not limited to the vehicle mount, the differential mount, the suspension bush, or the vibration isolator for various devices other than the vehicle. Needless to say, the present invention is applicable.

In addition, although not enumerated one by one, the present invention
Based on the knowledge of those skilled in the art, the present invention can be implemented in a form in which various changes, modifications, improvements, and the like are made.
It goes without saying that all such embodiments are included within the scope of the present invention, without departing from the spirit of the present invention.

[0100]

As is apparent from the above description, in the fluid filled type vibration damping device having the structure according to the first to sixth aspects of the present invention, all of the movable members are vibrated by pneumatic action. As a result, it is possible to obtain an active vibration damping effect based on the internal pressure control of the fluid chamber and the fluid flow through the orifice passage. In particular, since the vibration system is constituted by the movable member, the resonance effect is utilized. By doing so, a large vibration force can be exerted on the movable member with a small air pressure effect, and the vibration control effect based on the internal pressure control of the fluid chamber and the fluid flow through the orifice passage is more advantageously exhibited. .

Further, in such a fluid-filled type vibration damping device, active control of the vibration damping characteristics by controlling the internal pressure of the fluid chamber is realized without incorporating an actuator such as an electromagnetic driving means inside the device. Therefore, the number of parts is reduced and the structure is simplified, so that the manufacturability and cost are improved, and the device can be advantageously made compact and lightweight.

[Brief description of the drawings]

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

FIG. 2 is an explanatory longitudinal sectional view showing an engine mount according to a second embodiment of the present invention.

FIG. 3 is an explanatory cross-sectional view showing an engine mount as a third embodiment of the present invention.

FIG. 4 is a sectional view taken along line IV-IV in FIG.

FIG. 5 is a sectional view taken along line VV in FIG. 3;

[Explanation of symbols]

 10, 84, 90 Engine mount 12 First mounting bracket 14 Second mounting bracket 16, 96 Main rubber elastic body 30, 122 First movable member 32, 126 First rubber elastic plate 34, 124 First mass Metal fittings 49, 150 Second movable member 50, 153 Second rubber elastic plate 53, 155 Second mass metal fittings 60, 118 Main liquid chamber 62, 128 First working air chamber 66, 154 Secondary liquid chamber 68, 156 Second working air chamber 92 Inner tube fitting 94 Outer tube fitting

Claims (6)

[Claims] A first mounting member and a second mounting member which are spaced apart from each other are connected by a main rubber elastic body, and a fluid chamber in which an incompressible fluid is sealed is formed. In a fluid-filled type vibration damping device in which a part of the wall portion is formed of a movable member and the movable member is vibrated to control the internal pressure of the fluid chamber and adjust the vibration damping characteristics, The movable member is formed by an elastic plate to which a mass member is fixed to form a vibration system having a natural frequency corresponding to vibration to be damped by the movable member, while the fluid chamber is sandwiched by the movable member. A fluid which is characterized in that a closed working air chamber is formed on the opposite side of the movable air chamber so that an exciting force is applied to the movable member based on a change in air pressure applied to the working air chamber from outside. Enclosed vibration damping device. 2. The fluid chamber includes a main liquid chamber, a part of a wall of which is formed by the main rubber elastic body, and a main liquid chamber in which an internal pressure change is generated at the time of vibration input. Another part of the wall portion is constituted by the movable member,
2. The fluid filled type vibration damping device according to claim 1, wherein an internal pressure change is directly applied to the main liquid chamber by the vibration of the movable member. 3. A main liquid chamber in which the fluid chamber has a wall portion formed of the main rubber elastic body and a change in internal pressure is generated when a vibration is input, and an orifice in which a part of the wall portion is formed by the movable member. 3. The liquid storage device according to claim 1, further comprising a sub-liquid chamber communicated with said main liquid chamber through a passage, wherein an internal pressure change is generated in said sub-liquid chamber by vibrating said movable member. 4. The fluid filled type vibration damping device according to claim 1. 4. An equilibrium chamber, part of a wall of which is formed of a flexible membrane, and whose volume is allowed to change, is provided. The equilibrium chamber is filled with the incompressible fluid. The fluid filled type vibration damping device according to claim 2 or 3, wherein a fluid communication passage communicating with the main liquid chamber is provided. 5. The elastic plate constituting the movable member,
2. A resilience to a constant shape based on elasticity.
5. The fluid filled type vibration damping device according to any one of items 1 to 4. 6. An air pressure applied to the working air chamber,
6. The fluid filled type vibration damping device according to claim 1, further comprising an air pressure control device that changes the frequency in synchronization with the frequency of vibration to be damped.