JP2002005226A - Active vibration control equipment of fluid filled-system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize an active vibration control equipment of a fluid filled- system in which everyone active vibration effectiveness utilizing the resonant action of a fluid fluidizing an orifice path can be exerted effectively against the vibration of a plurality of frequent regions by a simple structure and a compact size. SOLUTION: This vibration control equipment is made to change a turning frequency of a first orifice path 46 (46') formed in a bore 34 for the orifice formation by approaching/separately isolating the controlling member 38 for the orifice against the bore 34 for the orifice formation by providing a bore 34 for the orifice formation astride the portion between a pressure receiving chamber 20 into which a vibration is inputted and a stimulative chamber 28 in which a pressure fluctuation is caused by the stimulative displacement of a stimulative member 26. Moreover, when the tuning frequency of such first orifice path 46 (46') is changed, the orifice controlling member 38 is made to drivingly displace by utilizing a stimulative means making the stimulative member 26 stimulatively displace.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an active-type fluid-filled vibration damping device that can reduce or positively reduce vibration by controlling the pressure of a pressure receiving chamber filled with an incompressible fluid. In particular, the present invention relates to an active fluid-filled type vibration damping device suitably used as a vibration damping mount or a vibration damper for an automobile.

[0002]

2. Description of the Related Art Vibration-proofing members, such as automobile bodies and various members, in which vibration (including noise caused by vibration) is a problem, have conventionally employed a vibration source to reduce the vibration. A vibration-damping connector such as an engine mount that is interposed between the vibration-damping target member and the vibration source to reduce the vibration from the vibration source to the vibration-damping target member, 2. Description of the Related Art Vibration damping devices such as a vibration damper such as a dynamic damper that absorbs and reduces vibration are used.

[0003] As one type of such a vibration isolator, Japanese Patent Laid-Open Publication No. 61-191543 and Japanese Patent Application Laid-Open No. 9-49541, etc. have been described in order to cope with the sophistication of the demand for the vibration isolating characteristics. As described above, a pressure receiving chamber in which a part of the wall is formed by a main rubber elastic body that is elastically deformed by the input of vibration, and a part of the wall which is formed by a displaceable vibration member. An orifice passage for providing a vibration chamber in which pressure fluctuations are generated by displacement of the vibration member, filling the pressure receiving chamber and the vibration chamber with an incompressible fluid, and interconnecting the pressure receiving chamber and the vibration chamber; On the other hand, a driving means for vibrating the vibrating member is provided, and the pressure fluctuation generated in the vibrating chamber by vibrating the vibrating member is transmitted to the pressure receiving chamber through the orifice passage. By controlling the internal pressure Vibration-proof object member offsetting or is so allowed to actively reduce the active fluid filled type vibration damping device the vibration of the have been proposed. In such a vibration isolator, the internal pressure fluctuation generated in the vibration chamber due to the vibration of the vibration member by the driving means is utilized in the pressure receiving chamber by utilizing the resonance action of the fluid caused to flow through the orifice passage. Therefore, the active vibration damping effect can be efficiently obtained.

In general, a plurality of types of vibrations having different frequencies and the like to be damped are input to a vibration isolator, and therefore, effective vibration damping effects are required for each of the plurality of types of vibrations. . For example, an automobile engine mount requires an anti-vibration effect against low-frequency vibrations such as shakes and high-frequency vibrations such as muffled sounds during traveling, and against middle-frequency vibrations such as idling vibrations when stopped. Therefore, an anti-vibration effect is required. However, in the conventional active-type fluid-filled type vibration damping device as described above, an efficient pressure transmitting function from the vibration chamber to the pressure receiving chamber, which is exhibited based on the resonance effect of the fluid flowing through the orifice passage, Means that effective active vibration damping effect can be exerted only in vibrations in a limited frequency range in which the orifice passage is tuned, so that sufficient vibration damping effect can be obtained for multiple types of input vibration Was difficult.

[0005] In order to deal with such a problem,
For example, a plurality of orifice passages, which are differently tuned, are formed in parallel between the pressure receiving chamber and the vibration chamber, and the orifice passages are selectively connected to each other by a valve body. It is conceivable that the resonance action of the fluid that is caused to flow through the passage is selectively exerted according to the type of vibration to be damped, but in such a vibration damping device, a plurality of orifice passages are formed,
In addition, the need to incorporate a valve body inevitably complicates the structure, increases the size, and complicates manufacture.

[0006]

The present invention has been made in view of the above-mentioned circumstances, and an object of the present invention is to provide a plurality of types based on a resonance action of a fluid which is caused to flow through an orifice passage. An object of the present invention is to provide a novel fluid-filled vibration damping device that can effectively obtain any active vibration damping effect with respect to input vibration.

[0007]

An embodiment of the present invention which has been made to solve such a problem will be described below. The components employed in each of the embodiments described below can be employed in any combination as possible. In addition, aspects or technical features of the present invention are not limited to those described below, but are described in the entire specification and drawings, or based on the invention ideas that can be understood by those skilled in the art from the descriptions. It should be understood that it is recognized on the basis of.

That is, in a first aspect of the present invention, a pressure receiving chamber in which a part of a wall is formed of a main rubber elastic body which is elastically deformed by the input of vibration and in which an incompressible fluid is sealed is provided. And a vibration chamber in which an incompressible fluid in which a pressure fluctuation is caused by displacement of the vibration member is formed, and the pressure receiving chamber is formed. And a first orifice passage for communicating the pressure receiving chamber and the vibration chamber with each other by an orifice forming hole formed so as to extend between the vibration chamber and the vibration chamber. By vibrating, the pressure fluctuation generated in the vibrating chamber is transmitted to the pressure receiving chamber through the first orifice passage, so that the vibration to be damped is actively reduced. An orifice forming hole. An orifice adjusting member for changing a length and / or a cross-sectional area of the first orifice passage by being squeezed to change the relative position with respect to the orifice forming hole; and providing the orifice forming member with the orifice forming member. The relative position with respect to the hole is changed using the driving force of the vibrating means for vibrating the vibrating member.

In the active-type fluid-filled type vibration damping device having the structure according to this aspect, the pressure fluctuation generated in the vibration chamber due to the vibration displacement of the vibration member causes the pressure fluctuation in the first orifice passage. In the case where the frequency corresponds to the tuning frequency, the fluid is efficiently transmitted to the pressure receiving chamber based on the resonance action of the fluid caused to flow through the first orifice passage. In this aspect, the tuning frequency of the first orifice passage can be appropriately changed by changing the relative position of the orifice adjusting member with respect to the orifice forming hole. By adjusting the position of the orifice adjusting member by means of the above, it is possible to obtain an effective anti-vibration effect using the resonance action of the fluid that is caused to flow through the first orifice passage against any of a plurality of types of vibrations. It becomes.

Further, in such an active type fluid filled type vibration damping device, a plurality of types of vibration damping devices are provided by appropriately changing the tuning frequency of one orifice passage formed using one orifice forming hole. Since the orifice passage for tuning corresponding to the vibration frequency to be realized can be realized, and the position of the orifice adjusting member is also changed using the driving means for exciting the exciting member, the structure is It can be simple and compact.

The active fluid filled type vibration damping device according to the present embodiment includes a vibration transmitting member (vibration generating member or the like) and a vibration transmitting member (vibration target member) such as an engine mount or a body mount for an automobile. ), The two members are connected to each other in a vibration-proof manner, or one of the members is supported by the other member in a vibration-proof manner. In addition, it can be configured as a vibration damper or the like that actively reduces the vibration of the vibration-proof member.
The specific structure of the vibration member is not particularly limited. For example, by forming the vibration member from an elastic material such as a rubber elastic body, the vibration member is displaced by its own deformation. It is possible to suitably adopt a structure having a structure in which a vibrating member having high rigidity is elastically supported or the like. In particular, if a rubber elastic body is employed as the elastic vibration member itself or an elastic support member that allows displacement of the vibration member made of a high-rigidity material, for example, a rectangular wave vibration such as a pneumatic driving means can be obtained. Even in the case where force is applied to the vibrating member, the displacement effect of the vibrating member and, consequently, the generated vibrating force can be more effectively brought close to a vibration waveform having a substantially sinusoidal waveform due to the damping effect when the rubber elastic body is deformed. It is possible to obtain a great anti-vibration effect.

As the driving means in the active type fluid filled type vibration damping device of the present embodiment, a driving means capable of controlling the generated vibration force by an electric signal is suitably employed, for example, a voice coil type or a moving magnet. Type, solenoid type and other electromagnetic drive means, drive means using a strain element such as an electrostrictive element or a magnetostrictive element, and fluid pressure such as air pressure or hydraulic pressure as a driving force is controlled by an electric signal using a servo valve or the like. It is also possible to adopt a fluid pressure driving means or the like that generates a driving force by applying an air pressure to the internal air chamber by using an electromagnetically driven switching valve or the like that is switched by an electric signal. Pneumatic driving means or the like that generates a driving force by alternately applying the driving force can be suitably employed.

According to a second aspect of the present invention, there is provided an active fluid-filled type vibration damping device having a structure according to the first aspect, wherein the vibration damping member is provided integrally with the vibration member. The orifice adjusting member is constituted by a constricted projection projecting from the central portion of the vibration member toward the orifice forming hole, and the orifice adjusting member is formed so as to approach / separate from the orifice forming hole. A cross-sectional area and / or a length of the first orifice passage formed inside the orifice forming hole is changed. In this aspect, the tuning frequency in the first orifice passage is changed and set by reducing the passage cross-sectional area of the first orifice passage formed by the orifice forming hole at the narrowing projection. Can be done.

According to a third aspect of the present invention, in the active fluid-filled type vibration damping device according to the second aspect, the narrowing projection extends from the vibration member toward the orifice forming hole. The orifice forming hole is formed by projecting a tapered constricting convex portion, and the orifice forming hole is narrowed by the constricting convex portion by approaching the constricting convex portion to the orifice forming hole. The first orifice passage whose passage cross-sectional area is narrowed is formed between the first orifice and the narrowing projection. In this embodiment, the first orifice passage is formed by moving the vibrating member closer to the orifice forming hole, and moving the stenosis convex portion closer to the orifice forming hole, and further entering as necessary. Thus, the tuning frequency of the first orifice passage can be changed by reducing the passage cross-sectional area of the orifice forming hole to be reduced by the constriction convex portion.
In particular, since the stenosis convex portion has a tapered outer peripheral surface shape, the passage cross-sectional area of the first orifice passage is extended by adjusting the amount of the stenosis convex portion entering the orifice forming hole. Can change and set the tuning frequency in a wide range.

In the second embodiment of the present invention,
Unlike the third aspect, for example, the stenosis protruding portion may be a stenosis protruding portion having an outer peripheral surface shape that protrudes with a substantially constant cross section. It is possible to stably secure the passage cross-sectional area of the first orifice passage, that is, the tuning frequency substantially constant, even if there is a slight variation in the amount of penetration of the first orifice passage.

According to a fourth aspect of the present invention, in the active-type fluid-filled vibration damping device according to the second aspect, the narrowing projection has a cylindrical shape protruding from the vibration member. The narrowed cylindrical portion is made to approach and enter the orifice forming hole, and the outer peripheral side of the narrowed cylindrical portion in the vibrating member is brought into contact with the opening of the orifice forming hole. By closing the orifice, the orifice forming hole is narrowed by the constricted cylindrical portion, and the first orifice passage having a constricted passage cross-sectional area is formed in the constricted cylindrical portion. I do. In this aspect, the vibrating member is moved closer to the orifice forming hole, and the constricted cylindrical portion is inserted into the orifice forming hole, whereby the passage of the orifice forming hole forming the first orifice passage is cut off. The tuning frequency of the first orifice passage can be changed by reducing the area in the constricted cylinder. In particular, since the outer peripheral side of the constricted cylindrical portion is closed in the orifice forming hole and the first orifice passage is formed in the constricted cylindrical portion, the length and cross-sectional area of the first orifice passage, and hence the tuning frequency Can be secured more stably.
In the present aspect, the inside of the stenotic cylinder is communicated with the pressure receiving chamber and the vibration chamber at both axial ends, and, for example, one opening of the stenotic cylinder is opened toward the pressure receiving chamber. At the same time, by closing the other opening with the vibration member, the first orifice passage and the vibration chamber can be formed inside the stenosis cylinder.

According to a fifth aspect of the present invention, in the active fluid-filled type vibration damping device according to the second aspect, the narrowing projection projects from the vibration member to the orifice forming hole. The orifice forming hole is formed between the fitting surface and the orifice forming hole. The narrowing fitting portion forms the first orifice passage, and the fitting amount of the narrowing fitting portion into the orifice forming hole is changed. Thus, the cross-sectional area and / or length of the first orifice passage is changed. In such an embodiment, the first orifice passage is formed by displacing the vibration member in the approach / separation direction with respect to the orifice forming hole and adjusting the amount of fitting of the stenosis fitting portion into the orifice forming hole. The tuning frequency of the first orifice passage can be changed by changing at least one of the cross-sectional area and the length of the first orifice. In particular, in this aspect, between the orifice forming hole and the fitting surface of the stenosis fitting portion, the first orifice passage is formed not only in the form extending in the axial direction, but also in the spiral shape, bending or bending shape extending in the circumferential direction. , Can be formed in various shapes, and the degree of freedom of tuning the first orifice passage can be more advantageously secured.

According to a sixth aspect of the present invention, there is provided an active fluid-filled type vibration damping device having a structure according to any one of the first to fifth aspects, wherein the vibrating member is sandwiched between the vibrating members. By forming a closed working air chamber on the opposite side of the chamber and exerting air pressure fluctuations on the working air chamber, the vibrating member is vibrated, and the air pressure of the working air chamber is adjusted. The relative position of the orifice adjusting member provided on the vibration member with respect to the orifice forming hole is changed and set. In this aspect, the air pressure applied to the working air chamber is used to vibrate the vibrating member and to change and set the relative position of the orifice adjusting member with respect to the orifice forming hole. The actuator (driving means)
It can be advantageously configured. By adopting such a pneumatic actuator, the structure of the vibration isolator becomes simpler and lighter and more compact than in the case of employing an electromagnetic actuator, for example. .

According to a seventh aspect of the present invention, there is provided an active-type fluid-filled type vibration damping device having a structure according to the sixth aspect, wherein the working air chamber is divided to vibrate the vibrating member. A vibrating air chamber to which air pressure fluctuations are applied, and a tuning air chamber to which air pressure for adjusting the position of the orifice adjusting member provided on the vibrating member is formed. I do. In this aspect, the excitation air chamber and the tuning air chamber are formed independently, so that the tuning frequency of the first orifice passage is prevented based on the air pressure applied to the tuning air chamber. It can be easily and stably changed according to the frequency of the vibration to be vibrated, and can prevent the pressure fluctuation generated in the vibration chamber based on the air pressure fluctuation applied to the vibration air chamber. It is possible to control with high accuracy according to the frequency of vibration to be vibrated and the like.

According to an eighth aspect of the present invention, in the active-type fluid-filled type vibration damping device having the structure according to the sixth or seventh aspect, the orifice adjusting member is provided with respect to the orifice forming hole. In the approaching direction, an urging means for constantly urging the vibrating member is provided, and a negative pressure is applied to the working air chamber to oppose the urging force of the urging member to the vibrating member. By applying a displacement force to the vibrating member, the vibrating member is vibrated, and the position of the orifice adjusting member in the approach / separation direction with respect to the orifice forming hole is changed. In this embodiment, by using the urging force exerted on the vibrating member by the urging means, the magnitude of the negative pressure exerted on the working air chamber is changed or adjusted, and the vibration member is Excitation, position change, and position setting can be performed easily and accurately. When the vibrating member or a part of the vibrating member is made of a rubber elastic body, a rubber elastic body constituting the vibrating member itself can be used as the urging means for applying the urging force to the vibrating member. Alternatively, an elastic material such as a coil spring separately provided may be used.

According to a ninth aspect of the present invention, in the active-type fluid-filled type vibration damping device having a structure according to any one of the sixth to eighth aspects, the working air chamber is pressured with respect to each other. By alternately connecting different air pressure sources,
An air line and valve means for exerting air pressure fluctuations on the working air chamber, and pressure regulating means for adjusting the average negative pressure applied to the working air chamber are provided. In such an embodiment, a vibration force corresponding to the air pressure fluctuation exerted on the working air chamber in response to the switching of the valve means is exerted on the vibration means, and an effective pressure fluctuation is generated in the vibration chamber. At the same time, the orifice adjusting member is positioned corresponding to the average negative pressure of the working air chamber set by the pressure adjusting means, and the tuning frequency of the first orifice passage can be set appropriately. As the air pressure sources having different pressures from each other, for example, it is sufficient to substantially prepare only one pressure source by using the atmospheric pressure as one air pressure source. Further, in order to advantageously obtain the structure and durability of the piping, it is preferable to employ a negative pressure rather than a positive pressure.For example, in a device including an internal combustion engine such as an automobile, in addition to a negative pressure pump, A negative pressure source utilizing a negative pressure generated in an intake system of an internal combustion engine can be suitably adopted as an air pressure source in combination with, for example, atmospheric pressure.

According to a tenth aspect of the present invention, there is provided an active-type fluid-filled type vibration damping device having a structure according to any one of the first to ninth aspects, wherein a part of the wall is easily deformable. An equilibrium chamber filled with an incompressible fluid is formed independently of the pressure receiving chamber and the vibration chamber. The equilibrium chamber is formed of a flexible membrane and allows a volume change based on deformation of the flexible membrane. Along with
A second orifice passage is formed to connect the equilibrium chamber to the pressure receiving chamber, and a resonance frequency of the fluid caused to flow through the second orifice passage is set to the resonance frequency of the fluid caused to flow through the first orifice passage. It is characterized in that it is set in a frequency range lower than the resonance frequency.
In such an embodiment, the vibration in the frequency range lower than the lowest tunable frequency of the first orifice passage is exerted based on the resonance action of the fluid caused to flow through the second orifice passage. By utilizing the low dynamic spring effect, a passive vibration isolating effect can be obtained. Further, even when an initial load such as the weight of a supported body is input in a mounted state of a vibration isolator such as an engine mount or the like, the pressure receiving chamber is changed by the volume changing action or the hydraulic pressure absorbing action of the equilibrium chamber. And the static internal pressure change of the vibration chamber is avoided, so that the pressure control of the pressure receiving chamber by the vibration of the vibration member can be efficiently performed, and the intended vibration damping effect can be stably obtained. Becomes possible. The second orifice passage may directly communicate the pressure receiving chamber and the equilibrium chamber,
In addition, a configuration in which the vibration chamber and the equilibrium chamber are communicated with each other, and the pressure receiving chamber and the equilibrium chamber are indirectly communicated with each other via the vibration chamber may be adopted. In addition, as a flexible film which can be easily deformed, a fluid-tight sheet or the like can be adopted in addition to a thin rubber elastic film.

According to an eleventh aspect of the present invention, there is provided an active-type fluid-filled type vibration damping device having a structure according to any one of the first to tenth aspects, which corresponds to the frequency of vibration to be damped. A control device for controlling the operation of the driving means is provided so that the vibration member is vibrated at the set frequency. In such an embodiment, the control device controls the vibration of the vibration member at a frequency corresponding to the vibration frequency to be damped, and the pressure of the vibration chamber and the pressure receiving chamber is controlled. An effective active vibration damping effect can be exerted against the vibration to be damped.

According to a twelfth aspect of the present invention, there is provided an active-type fluid-filled type vibration damping device having a structure according to any one of the first to eleventh aspects, wherein the elastic body is elastically provided by the main body rubber elastic body. A first mounting member and a second mounting member connected to the main liquid chamber on one side of the partition member supported by the second mounting member, and the main liquid chamber on the other side. A vibration chamber is formed, the orifice forming hole is formed through the partition member, and the vibration member forming a part of a wall portion of the vibration chamber is connected to the second mounting member. Characterized in that it is displaceably supported. In this embodiment, for example, the first mounting member is attached to one member that is connected to the vibration isolation, and the second mounting member is attached to the other member that is connected to the vibration isolation. Vibration-proof connection of both connected members,
For example, an engine mount, a differential mount, a body mount, a suspension mount, a bush, and the like for an automobile can be advantageously realized. Alternatively, one of the first mounting member and the second mounting member is attached to the vibration-proof member, and the other of the first mounting member and the second mounting member is attached to the vibration-proof member. By making the main rubber elastic body elastically supported via the main rubber elastic body, the main rubber elastic body is used as a spring system, and the other of the second mounting member of the first mounting member is used as a mass system, thereby forming a sub-vibration system. Is also possible, whereby a vibration damper for the member to be damped can be advantageously realized.

[0025]

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

First, as a first embodiment of the present invention, a specific configuration in which the present invention is applied to an automobile engine mount is schematically shown in FIG. The engine mount 10 includes a first mounting member 12 as a first mounting member and a second mounting member 1 as a second mounting member.
4, the first mounting member 12 and the second mounting member 14 are elastically connected by a main rubber elastic body 16. Then, the first mounting bracket 12 is mounted on a power unit of the vehicle (not shown), and the second mounting bracket 14 is mounted on the body of the vehicle (not shown) so that the power unit is supported on the body by vibration isolation. It has become. In the following description, the vertical direction refers to the vertical direction in FIG. 1 in principle.

More specifically, each of the first mounting bracket 12 and the second mounting bracket 14 is formed of a metal material such as an aluminum alloy or iron, and the first mounting bracket 12 has a substantially circular shape. While the second mounting bracket 1
4 has a substantially large diameter cylindrical shape. Then, the first mounting bracket 12 is substantially on the central axis of the second mounting bracket 14,
The main mounting rubber elastic body 16 is disposed between the first mounting bracket 12 and the second mounting bracket 14 so as to be spaced apart from each other on the axially upper opening side of the second mounting bracket 12. Have been. The main rubber elastic body 16 has a thick, substantially truncated conical shape, is fixed in a state where the first mounting bracket 12 is inserted into the small-diameter side end face, and has a large-diameter side. The upper opening peripheral edge of the second mounting member 14 is fixed to the outer peripheral surface of the end portion, whereby the upper opening portion of the second mounting member 14 is fluid-tightly closed.

A rigid partition member 18 extending in the direction perpendicular to the axis is provided at an intermediate portion of the second mounting member 12 in the axial direction, and the inside of the second mounting member 12 is separated by the partition member 18. By partitioning in a fluid-tight manner, a part of the wall is formed of the main rubber elastic body 16 on one axial side (the upper side in FIG. 1) of the partition member 18 and is filled with an incompressible fluid. The pressure receiving chamber 20 is formed. As the incompressible fluid to be enclosed, any of water, alkylene glycol, polyalkylene glycol, silicone oil and the like can be adopted. In particular, in order to effectively obtain a vibration damping effect based on the resonance action of the fluid described later. It is desirable to adopt a low-viscosity fluid of 0.1 Pa · s or less.

Further, a rigid partition member 22 is provided below the partition member 18, that is, on the opposite side of the partition member 18 from the pressure receiving chamber 20, and a rigid partition member 22 is provided.
The inside of the second mounting bracket 12 is partitioned by the active control region 24 which is partitioned fluid-tight with respect to the external space.
Are formed. The active control area 24 includes:
An elastic vibration plate 26 as a vibration member is accommodated and arranged.

The elastic vibration plate 26 is formed entirely of rubber elastic material and has a plate shape that can be elastically deformed. The outer peripheral edge portion is fixed to the inner peripheral surface of the active control region 24 in a fluid-tight manner.
As a result, the active control region 24 is fluid-tightly divided into two by the elastic vibrating plate 26, so that the working air chamber 30 is formed below the elastic vibrating plate 26. A compression coil spring 32 is disposed in the air chamber 30 as urging means.
, The central portion of the elastic vibration plate 26 is constantly urged upward, that is, in the direction approaching the partition member 18. Then, a pressure change is applied to the working air chamber 30 through a port 35 penetrating through the second mounting member 12, so that a pneumatic vibration force acts on substantially the entire elastic vibration plate 26. It is supposed to be. Particularly, in the present embodiment, when the engine mount 10 is mounted, the switching valve 42 is connected to the working air chamber 30 through the port 34 by the external air line 40, and the switching operation of the switching valve 42 is performed. , The working air chamber 30 is alternatively connected to the negative pressure source 44 as an air pressure source and the atmosphere, so that the working air chamber 30
Is subjected to pressure changes.

On the other hand, on the upper side of the elastic vibration plate 26, that is, on the side opposite to the working air chamber 30 across the elastic vibration plate 26, a vibration chamber in which a pressure change is generated by the displacement of the elastic vibration plate 26. 28 are formed, and in the vibration chamber 28,
An incompressible fluid is sealed as in the pressure receiving chamber 20. That is, the pressure receiving chamber 20 is formed on the upper side with the partition member 18 interposed therebetween, and the vibration chamber 28 is formed on the lower side. Further, the partition member 18 that partitions the pressure receiving chamber 20 and the vibration chamber 28 is provided with an orifice forming hole 34 extending substantially in parallel with the central axis of the second fitting 14.
The orifice forming hole 34 allows the pressure receiving chamber 2
0 and the vibration chamber 28 are connected to each other so that fluid flow between the two chambers 20 and 28 is allowed. In particular, in the present embodiment, the orifice forming hole 34 is formed linearly with a substantially constant cross section by a cylindrical tubular body 36, and the resonance action of the fluid caused to flow through the orifice forming hole 34 is achieved. The length and cross-sectional area of the orifice forming hole 34 are adjusted so as to be generated in a high frequency region such as a muffled sound.

Further, the elastic vibration plate 26 has a cylindrical stenosis tube fitting 3 as a stenosis tube portion with respect to the central portion thereof.
8 is fixed, and the constricted cylindrical metal fitting 38 is provided to protrude into the vibration chamber 28 from the elastic vibration plate 26 upward in the axial direction. Here, the stenosis tube fitting 38 is used.
Has a smaller inner and outer diameter than the orifice forming hole 34, and is disposed on substantially the same central axis as the orifice forming hole 34. The lower opening is fluid-tightly covered with an elastic vibration plate 26 as a vibration member, and is protruded upward in the axial direction to be opened. In short, when the elastic vibration plate 26 that closes the lower opening of the stenosis tube fitting 38 is vibrated and displaced by the air pressure fluctuation of the working air chamber 30 formed behind (lower), the stenosis is reduced. The fluid flow through the inside of the tube fitting 38 is generated. In particular, in the present embodiment, the stenosis tube fitting 38 is formed linearly with a substantially constant cross section, and the resonance effect of the fluid caused to flow through the stenosis tube fitting 38 occurs in a medium frequency region such as idling vibration. The length and the cross-sectional area of the stenosis tube fitting 38 are adjusted so as to be tightened.

When the working air chamber 30 is subjected to the atmospheric pressure or a negative pressure close to the atmospheric pressure, the elastic vibrating plate 26 is urged upward by the coil spring 32, and the elastic vibrating plate 26 is elastically vibrated. The plate 26 is held in contact with the lower opening of the cylindrical body 36, so that the lower opening of the orifice forming hole 34 is fluid-tightly closed. It has become. In this state, the elastic vibration plate 2
The stenosis tube fitting 38 protruding from 6 enters the orifice forming hole 34 and protrudes toward the pressure receiving chamber 20 in the orifice forming hole 34. Further, in a state where the elastic vibration plate 26 is in contact with the lower opening of the cylindrical body 36, a portion of the elastic vibration plate 26 located on the outer peripheral side of the constricted cylindrical metal fitting 38 is the cylindrical body 36. Stenosis tube fitting 3
The spring stiffness is made larger than that of the portion located on the inner peripheral side of 8. Therefore, in such a state, the working air chamber 30 is alternately connected to the negative pressure source 44 and the atmosphere to exert an air pressure fluctuation, whereby the inner peripheral side of the constricted cylindrical metal fitting 38 of the elastic vibration plate 26. Are effectively elastically vibrated, so that the pressure receiving chamber 20 and the vibrating chamber 28
The fluid flow through the stenosis barrel 38 is generated between the stenosis barrel 38 and the region formed in the stenosis barrel 38.

On the other hand, when a predetermined negative bias pressure is applied to the working air chamber 30, the elastic vibration plate 26 is attracted downward against the urging force of the coil spring 32. By being displaced, as shown in FIG. 2, the cylindrical body 36 is held in a non-contact state separated downward from the lower opening of the cylindrical body 36. 38 is held at a position where it comes out substantially downward from the cylindrical body 36. Therefore, in such a state, the working air chamber 30 is alternately connected to the negative pressure source 44 and the atmosphere to exert air pressure fluctuation, whereby the entire elastic vibration plate 26 can be effectively elastically vibrated. Becomes
As a result, a fluid flow is generated between the pressure receiving chamber 20 and the vibration chamber 28 through the orifice forming hole 34.

As is apparent from this, in the present embodiment, the working air chamber 30 is subjected to a bias negative pressure so that the elastic vibrating plate 26 is separated from the cylindrical body 36, and the working air By applying air pressure fluctuation to the chamber 30,
The entire elastic vibrating plate 26 is vibrated and displaced, so that a fluid flow is generated between the pressure receiving chamber 20 and the vibrating chamber 28 through the orifice forming hole 34. In such a state, , In the entire orifice forming hole 34,
A first orifice passage 46 having a large passage cross-sectional area is formed.

On the other hand, the atmospheric pressure is applied to the working air chamber 30 to bring the elastic vibration plate 26 into contact with the cylindrical body 36, and
When air pressure fluctuation is applied to the working air chamber 30 in a state where the stenosis tube fitting 38 is approached and inserted into the orifice forming hole 34, only the region of the elastic vibration plate 26 in the stenosis tube fitting 38 becomes effective. Vibration displacement causes pressure receiving chamber 2
Fluid flow through the stenosis tube fitting 38 occurs between the zero and the region of the vibration chamber 28 formed in the stenosis tube fitting 38. In such a state,
The cross-sectional area of the orifice forming hole 34 is changed by the stenosis tube fitting 38 so that a narrowed first orifice passage 46 ′ is formed in the hole of the stenosis tube fitting 38.

Further, a diaphragm 50 as a flexible film made of a thin rubber elastic film is provided at an opening on the lower side in the axial direction of the second mounting member 12. The lower axial opening of the second mounting member 12 is closed in a fluid-tight manner. Thus, on the opposite side of the partition member 18 from the pressure receiving chamber 20, a part of the wall is constituted by the diaphragm 50, and the equilibrium chamber 52 filled with the incompressible fluid is independent of the active control area 24. It is formed. The equilibrium chamber 52 includes the diaphragm 5
By easily permitting the deformation of 0, the change in volume is easily permitted, and the pressure fluctuation is quickly eliminated.

A second orifice passage 54 extending between the pressure receiving chamber 20 and the balancing chamber 52 is formed in the partition member 18 for partitioning the pressure receiving chamber 20 and the balancing chamber 52. The main rubber elastic body 16 at the time of vibration input
Based on the relative pressure fluctuations induced between the pressure receiving chamber 20 and the equilibrium chamber 52 due to the elastic deformation of
A fluid flow through the second orifice passage 54 is generated between the fluid and the balance chamber 52. In particular, in the present embodiment, the second orifice passage 54
Based on the resonance action of the fluid that is caused to flow, the vibration damping effect (damping effect) effective against low-frequency, large-amplitude vibration corresponding to a shake or the like lower than the tuning frequency of the first orifice passages 46, 46 '. So that
The passage length and cross-sectional area of the second orifice passage 54 are adjusted.

In the engine mount 10 having the above-described structure, as described above, the first mounting bracket 12 is mounted on the power unit of the vehicle, and the second mounting bracket 14 is mounted on the body of the vehicle. As a result, it is mounted between the power unit and the body. The control device 56 controls the switching of the switching valve 42 in accordance with the vibration for the purpose of preventing vibration, thereby controlling the air pressure applied to the working air chamber 30.
The first orifice passage 46 can obtain an active vibration damping effect with respect to a medium frequency vibration such as an idling vibration tuned to a high frequency vibration such as a muffled sound. The decrease in the volume of the pressure receiving chamber 20 due to the addition of the weight of the power unit is compensated for by the increase in the volume of the equilibrium chamber 52, so that an increase in the internal pressure in the pressure receiving chamber 20 and the vibration chamber 28 is avoided.

The control device 56 includes a bias pressure control means for changing and setting an average air pressure applied to the working air chamber 30, and a frequency corresponding to a vibration for which the air pressure applied to the working air chamber is to be damped. And frequency control means for controlling increase / decrease. Also, preferably, the control device 56 is operated by the frequency control means.
Phase adjustment means for controlling the phase of the air pressure fluctuation applied to the vibration-proof member in accordance with the vibration state, transfer function, and the like of the member. More preferably, such a controller 56
Includes gain adjustment means for controlling the amplitude of the air pressure fluctuation exerted on the working air chamber 30 by the frequency control means in accordance with the magnitude (amplitude or vibration level) of the vibration to be damped. .

More specifically, for example, the bias pressure control means can be constituted by using an electric control type variable pressure regulating valve or the like. Using a switching valve, a signal that directly detects the vibration of the body with an acceleration sensor or the like, or a crank angle signal or an ignition pulse signal that has a phase relationship with the vibration of the body is used as a reference signal to reduce the vibration to be damped. Using a control signal having a corresponding frequency component, for example, based on map data set based on an experiment or the like, the control is performed by a corresponding relationship with an appropriate reference factor such as an engine speed, an acceleration state, a shift position, and a temperature. And a feedback control device that detects and corrects an error signal and performs control correction.

In particular, in this embodiment, a pulse wave having a frequency corresponding to the vibration to be damped and a duty ratio of the pulse wave being adjusted, or a pulse width modulation being performed by PWM control, etc. By adopting the duty ratio control or the PWM control, the bias pressure control means and the frequency control means can be configured together.

Accordingly, in the engine mount 10 having the above-described structure, the switching valve 42 is switched by the control device 56 in the mounted state, and the vibration to be isolated from the working air chamber 30 is prevented. Is caused, and as a result, the elastic vibration plate 26 is vibrated and displaced, and a pressure change is generated in the vibration chamber 28. 28 is exerted on the pressure receiving chamber 20 by the fluid flow through the first orifice passage 46 (46 '), and the pressure change in the pressure receiving chamber 20 causes the first mounting member 12 and the second mounting member During the period 14, it acts as an exciting force. Therefore, the control device 56 controls the vibration drive of the elastic vibration plate 26, and changes the pressure applied to the pressure receiving chamber 20 or the vibration applied to the body in accordance with the vibration to be prevented in the body. By performing the adjustment, an active vibration damping effect can be obtained for the vibration to be damped.

Further, in the engine mount 10, the switching operation of the switching valve 42 by the control device 56 is changed according to the vibration frequency to be damped, specifically, according to the stopped state and the running state of the vehicle. As a result, the average, i.e., the bias pressure applied to the working air chamber 30 is changed. More specifically, when the vehicle stops, the biasing pressure value applied to the working air chamber 30 is set close to the atmospheric pressure, so that the elastic vibration plate 26 is turned on as shown in FIG. It will be made to contact the opening of the cylindrical body 36. Accordingly, when the air pressure fluctuation corresponding to the vibration to be damped as described above is applied to the working air chamber 30 in such a state, the pressure fluctuation generated in the vibration chamber 28 is constricted by the constriction cylinder 38. The pressure is transmitted to the pressure receiving chamber 20 through the first orifice passage 46 '.
6 'is tuned to the frequency range of the idling vibration, the efficiency of the pressure receiving chamber 20 is increased in the frequency range of the idling vibration or the like based on the resonance action of the fluid caused to flow through the first orifice passage 46'. As a result, the intended active vibration damping effect can be more effectively exerted against medium frequency vibration such as idling vibration.

On the other hand, when the vehicle is running, the biasing pressure value applied to the working air chamber 30 is set to a large value on the negative pressure side, so that the elastic vibration plate 26 is moved as shown in FIG. It will be located away from the opening of the cylindrical body 36. Therefore, when the air pressure fluctuation corresponding to the vibration to be damped as described above is applied to the working air chamber 30 in such a state, the pressure fluctuation generated in the vibration chamber 28 causes the pressure fluctuation in the orifice forming hole 34. Is transmitted to the pressure receiving chamber 20 through a first orifice passage 46 having a large passage cross-sectional area formed therein.
Since the first orifice passage 46 is tuned in the frequency range of the muffled sound, the first orifice passage 46 is tuned to the pressure receiving chamber 20 in the frequency range of the muffled sound based on the resonance action of the fluid caused to flow through the first orifice passage 46. As a result, more efficient pressure fluctuation is exerted, and the intended active vibration damping effect can be more effectively exerted against high-frequency vibrations such as muffled sounds.

In particular, in such an engine mount 10, the orifice tuning is changed by utilizing a substantially single orifice passage 46 formed by the orifice forming hole 34 and temporarily narrowing it. For this reason, the structure is simplified and the whole device is made compact as compared with the case where two orifice passages tuned differently from each other are formed. Further, the displacement of the elastic vibrating plate 26 in changing and controlling the passage cross-sectional area of the orifice passage 46 is performed by using a pneumatic actuator which is a driving means for vibrating the elastic vibrating plate 26. This eliminates the need for a special actuator for changing the setting of the orifice tuning, whereby the structure can be further simplified and the device can be made more compact.

Further, the engine mount 1 of the present embodiment
In FIG. 0, a variable-capacity equilibrium chamber 52 is formed independently of both the pressure receiving chamber 20 and the vibration chamber 28, and a second orifice passage 54 connecting the equilibrium chamber 52 to the pressure receiving chamber 20 is provided. Tuned to the low frequency range, the active vibration damping effect utilizing the fluid flow action through the first orifice passages 46, 46 'is hardly effectively exerted. The passive vibration damping effect based on the resonance action of the fluid that is caused to flow through the second orifice passage 54 can also be effectively exerted on the frequency vibration.

Next, FIGS. 3 and 4 schematically show a vehicle engine mount 60 according to a second embodiment of the present invention. In this embodiment, FIGS.
The members and parts having the same structure as the first embodiment shown in FIG. 3 are denoted by the same reference numerals as those in the first embodiment in the drawings, and the detailed description thereof is omitted. .

That is, the present embodiment exemplifies a structure different from that of the first embodiment as a specific example of the orifice adjusting member fixed to the elastic vibration plate. Specifically, in the engine mount 60 of the present embodiment, a stenosis projection 62 as a stenosis projection projecting upward in the axial direction is integrally formed with the central portion of the elastic vibration plate 26. The constriction convex portion 62 has an outer peripheral surface shape of a truncated cone that protrudes in a tapered shape, and the outer diameter of the large-diameter end portion is substantially the same as the inner diameter of the orifice forming hole 34. At the same time, the outer diameter of the small diameter end is smaller than the inner diameter of the orifice forming hole 34.

When the atmospheric pressure or a negative pressure close to the atmospheric pressure is applied to the working air chamber 30, the elastic vibration plate 26 is positioned close to the partition member 18, and as shown in FIG. As shown in FIG. 5, the small diameter side protruding tip portion of the constriction convex portion 62 enters the lower opening of the orifice forming hole 34 by a predetermined amount and is positioned. As a result, the orifice forming hole 34 is narrowed by the narrowing convex portion 62, and the narrowed first orifice passage 46 has an annular passage cross section extending around the narrowing convex portion 62 in the orifice forming hole 34. 'Is formed.

On the other hand, when a predetermined negative bias pressure is applied to the working air chamber 30, the elastic vibration plate 26 is displaced downward by suction against the urging force of the coil spring 32. As a result, as shown in FIG. 4, the stenosis convex portion 62 comes out downward from the cylindrical body 36 and is held at a separated position. As a result, the orifice forming hole 34 is brought into a communication state as a whole, and a first orifice passage 46 having a large passage cross section is formed.

The first orifice passage 46
And 46 ', the pressure fluctuation in the vibration chamber 28 is reduced by applying the air pressure fluctuation to the working air chamber 30 to vibrate the elastic vibration plate 26. The fluid can be efficiently transmitted to the pressure receiving chamber 20 by utilizing the resonance action of the fluid through 46 to 46 ', whereby the active vibration damping effect as effective as in the first embodiment can be obtained. It is demonstrated.

Therefore, in the engine mount 60 of this embodiment having such a structure, the same effects as those of the first embodiment can be effectively exhibited.

FIGS. 5 and 6 schematically show a vehicle engine mount 64 according to a third embodiment of the present invention. In this embodiment, FIGS.
The members and parts having the same structure as the second embodiment shown in FIG. 4 are denoted by the same reference numerals in the drawing as those in the second embodiment, and detailed description thereof is omitted. I do.

That is, the present embodiment exemplifies a structure different from that of the second embodiment as a specific example of the vibration structure of the elastic vibration plate 26 using air pressure. Specifically, in the engine mount 64 of the present embodiment, the working air chamber 30 formed behind the elastic vibration plate 26 is fluid-tightly divided into two by the elastic partition wall 66 formed integrally with the elastic vibration plate 26. Thus, the tuning air chamber 68 is located behind the stenosis convex portion 62 located at the center of the elastic vibration plate 26 and at the center of the working air chamber 30.
Is formed, and a vibration air chamber 70 is formed behind the outer peripheral portion of the elastic vibration plate 26 and at the outer peripheral portion of the working air chamber 30. In other words, in the outer peripheral portion of the elastic vibration plate 26 in the second embodiment, an independent vibration air chamber 70 is formed therein.

In the engine mount 64 of the present embodiment having such a structure, the tuning air chamber 6 is provided.
By adjusting the air pressure exerted on the diaphragm 8, the relative position of the elastic vibration plate 26 in the approaching / separating direction with respect to the partition member 18 is controlled, and the narrowing convex portion 62 enters the orifice forming hole 34 (FIG. 5). (See FIG. 6), and the position of exit from the orifice forming hole 34 (see FIG. 6).
The switching is controlled. On the other hand, by applying air pressure fluctuation to the vibration air chamber 70 to vibrate the elastic vibration plate 26 and adjusting the air pressure fluctuation, the pressure fluctuation of the vibration chamber 28 is reduced by the first orifice passage 4.
Utilizing the resonance action of the fluid through 6 to 46 ',
It can be transmitted to the pressure receiving chamber 20, so that the same active vibration damping effect as in the second embodiment is exerted.

Therefore, in the engine mount 64 of this embodiment having such a structure, the same effects as those of the second embodiment can be effectively exhibited.

In addition, in the engine mount 64 of this embodiment, the tuning air chamber 6 for controlling the position of the elastic vibration plate 26 with respect to the partition member is provided.
8, and a vibration air chamber 70 for vibrating the elastic vibration plate 26 to cause a pressure fluctuation in the vibration chamber 28 is formed independently, and the air pressure exerted on each of the air chambers 68, 70 is formed. Can be performed by each switching valve and control device, and therefore, there is an advantage that the control can be easily performed as compared with the second embodiment.

FIG. 7 schematically shows an automobile engine mount 74 according to a fourth embodiment of the present invention. In the present embodiment, members and parts having the same structure as the first embodiment shown in FIGS. 1 and 2 are denoted by the same reference numerals as those in the first embodiment. Thus, detailed description thereof will be omitted.

That is, the present embodiment exemplifies a structure different from that of the first embodiment as a specific example of the orifice adjusting member fixed to the elastic vibration plate. Specifically, in the engine mount 74 of the present embodiment, a stenosis fitting portion 76 as a stenosis projection projecting upward in the axial direction is formed integrally with the central portion of the elastic vibration plate 26. The constriction fitting portion 76 is provided with the orifice forming hole 3.
4 has a circular block shape having an outer peripheral surface shape corresponding to the inner peripheral surface shape, and is fitted into the orifice forming hole 34 so as to be slidable in the axial direction. The stenosis fitting portion 76 is desirably formed of a hard material such as a synthetic resin.

A peripheral groove 78 extending in the circumferential direction is formed on the outer peripheral surface of the stenosis fitting portion 76.
When is fitted into the orifice forming hole 34, the circumferential groove 78 is covered with the cylindrical body 36, so that the space between the stenotic fitting portion 76 and the fitting surface of the cylindrical body 36 spirals in the circumferential direction. A first orifice passage 46 extending to communicate the pressure receiving chamber 20 and the vibration chamber 28 with each other is formed.

In the engine mount 74 having such a structure, the position of the elastic vibration plate 26 for fixedly supporting the stenosis fitting portion 76 is adjusted by adjusting the air pressure applied to the working air chamber 30. By changing the direction of approach / separation with respect to the partition member 18 and adjusting the amount of fitting of the stenosis fitting portion 76 into the cylindrical body 36, the pressure receiving chamber 2 is adjusted.
The length of the first orifice passage 46 connecting the vibration chamber 28 to the vibration chamber 28 can be changed.

Accordingly, when the working air chamber 30 is subjected to the atmospheric pressure or a negative pressure close to the atmospheric pressure, the fitting amount of the stenotic fitting portion 76 into the cylindrical body 36 is increased, and the first fitting is performed. While the passage length of the orifice passage 46 is set to be long, under a state where a predetermined negative bias pressure is applied to the working air chamber 30, the stenosis fitting portion 76 fits into the cylindrical body 36. The amount is reduced, and the length of the first orifice passage 46 is set to be short. Thereby, the tuning frequency of the first orifice passage 46 can be changed and set, and, for example, the passage length expressed by increasing the fitting amount of the stenosis fitting portion 76 into the tubular body 36 is increased. Long first orifice passage 4
6 is tuned to a middle frequency range such as idling vibration, and the first orifice passage 46 having a short passage length that is developed by reducing the amount of fitting of the stenosis fitting portion 76 into the cylindrical body 36 is formed. By tuning to a high frequency region such as a muffled sound, the tuning frequency of one orifice passage is appropriately changed and adjusted, thereby exerting air pressure fluctuation on the working air chamber 30 to apply the elastic vibration plate 26 as described above. As in the first embodiment, the active vibration damping effect exerted by the vibration is applied to both the vibration in the middle frequency range such as the idling vibration and the vibration in the high frequency range such as the muffled sound. , It is possible to demonstrate it effectively.

Although the embodiments of the present invention have been described in detail above, these are merely examples, and the present invention
By the specific description in such an embodiment,
It is not to be construed as limiting.

For example, the balance chamber 52 having a variable volume and the second orifice passage 5 connecting the balance chamber 52 to the pressure receiving chamber 20 are provided.
4 and the like need not always be provided.

The tuning frequency of the first orifice passage is not limited at all, and it goes without saying that the tuning frequency is appropriately adjusted according to the required anti-vibration characteristics.

Further, the coil spring 32 for urging the elastic vibration plate 26 in an auxiliary manner is not always necessary. For example, the elastic vibration plate 26 It is also possible to configure so as to be elastically positioned at the position.

Further, in the engine mount 74 shown in the fourth embodiment, a peripheral groove 78 formed on the outer peripheral surface of the narrow fitting portion 76 is formed on the inner peripheral surface side of the orifice forming hole 34. Is also good.

In the engine mount 74 shown in the fourth embodiment, the sectional area of the circumferential groove 78 formed on the outer peripheral surface of the stenosis fitting portion 76 is changed, for example, as shown in FIG. As described above, by forming only the lower portion of the circumferential groove 78 with a small cross-sectional area, the tuning frequency of the first orifice passage 46 accompanying the change in the amount of fitting of the stenotic fitting portion 76 into the orifice forming hole 34 is changed. Can be set larger, and a greater degree of freedom in tuning characteristics can be ensured.

The specific structures and shapes of the elastic vibration plate 26 and the orifice adjusting members (38, 62, 76) are determined by the structure of the basic vibration isolator, required vibration isolating characteristics, It is appropriately changed and set according to the type, characteristics, and the like, and is not limitedly interpreted by the above-described embodiment. Specifically, for example, the elastic vibration plate 26
In the above-described embodiment, a substantially inverted dish-shaped rubber elastic member is employed. However, as a whole, a plate-shaped rubber elastic member or a dish-shaped rubber that expands toward the vibration chamber 28 is used. An elastic member or the like can also be appropriately adopted, and the spring characteristics may be partially changed and set by partially changing the wall pressure or the like of such a rubber elastic member.

Furthermore, the present invention relates to, for example,
As described in Japanese Patent No. 5739 or the like, an outer cylindrical metal fitting as a second mounting member is disposed radially outwardly of a shaft metal fitting as a first mounting member, and these shaft metal fittings are provided. And the outer cylinder fitting are elastically connected by a main rubber elastic body interposed between the two fittings, and a part of the wall portion is formed between the axial fitting and the outer cylinder fitting in a radial direction by a body rubber elastic body. And a part of the wall portion forms a vibration chamber formed of a vibration member, and the pressure reception chamber and the vibration chamber are connected to each other through a first orifice passage. The present invention is also applicable to a cylindrical active type fluid filled type vibration damping device. In addition, such a cylindrical active type fluid filled type vibration damping device is, for example,
It can be suitably used for an FF type automobile engine mount, an automobile body mount, a differential mount, a member mount, a suspension bush, and the like. Further, in such a cylindrical vibration isolator, when employing a pneumatic actuator, for example, by supporting the vibrating member with an outer cylinder, so as to be located behind the vibrating member,
A working air chamber can be formed inside or on the outer peripheral side of the outer tube fitting.

In addition, it goes without saying that the present invention is similarly applicable to vibration isolators such as mounts and vibration dampers in various devices other than the vibration isolators for automobiles.

In addition, although not enumerated one by one, the present invention
Based on the knowledge of those skilled in the art, various changes, modifications, improvements, and the like can be made, and unless such embodiments depart from the spirit of the present invention.
Both are included in the scope of the present invention,
Needless to say.

[0074]

As is apparent from the above description, in the active fluid-filled type vibration damping device having the structure according to the present invention, the first orifice passage formed using one orifice forming hole. By changing the tuning frequency, the active vibration isolating effect utilizing the resonance action of the fluid caused to flow through the first orifice passage is effectively exhibited for a plurality of vibrations having different frequencies. Therefore, an active vibration damping effect against vibrations in a wide frequency range can be obtained with a simple and compact structure.

[Brief description of the drawings]

FIG. 1 is a model diagram showing an automobile engine mount as a first embodiment of the present invention.

FIG. 2 is a model diagram showing another operation state of the engine mount shown in FIG. 1;

FIG. 3 is a model diagram showing an automobile engine mount as a second embodiment of the present invention.

FIG. 4 is a model diagram showing another operation state of the engine mount shown in FIG. 3;

FIG. 5 is a model diagram showing an automobile engine mount as a third embodiment of the present invention.

FIG. 6 is a model diagram showing another operation state of the engine mount shown in FIG. 5;

FIG. 7 is a model diagram showing an automobile engine mount as a fourth embodiment of the present invention.

FIG. 8 is a model diagram showing a vehicle engine mount as a fifth embodiment of the present invention.

[Explanation of symbols]

 10, 60, 64, 74, 80 Engine mount 12 First mounting bracket 14 Second mounting bracket 16 Main rubber elastic body 18 Partition member 20 Pressure receiving chamber 26 Elastic vibration plate 28 Vibration chamber 30 Working air chamber 34 Orifice formation Hole 38 stenosis tube fitting 46, 46 'first orifice passage 62 stenosis convex portion 76 stenosis fitting portion

Claims (12)

[Claims] 1. A pressure receiving chamber in which a part of a wall is formed of a main rubber elastic body which is elastically deformed by the input of vibration and in which an incompressible fluid is sealed, and a wall provided by a displaceable vibration member. A part of the portion is formed to form a vibration chamber in which an incompressible fluid in which a pressure fluctuation is generated by displacement of the vibration member is filled, and a straddle is formed between the pressure receiving chamber and the vibration chamber. By providing a first orifice passage that communicates the pressure receiving chamber and the vibration chamber with each other by the orifice forming hole formed in the way, by vibrating the vibration member by driving means,
An active-type fluid-filled type vibration damping device that transmits pressure fluctuations generated in the vibration chamber to the pressure receiving chamber through the first orifice passage to actively reduce vibration to be damped. An orifice adjusting member for changing a length and / or a cross-sectional area of the first orifice passage by changing a relative position with respect to the orifice forming hole by facing the orifice forming hole; An active fluid-filled type vibration damping device characterized in that the relative position of the adjusting member to the orifice forming hole is changed by using the driving force of the vibrating means for vibrating the vibrating member. . 2. The orifice adjusting member is constituted by a constricted projection provided integrally with the vibration member and protruding from a central portion of the vibration member toward the orifice forming hole. Wherein the constriction projection is moved toward or away from the orifice forming hole to change a cross-sectional area and / or a length of the first orifice passage formed inside the orifice forming hole. Item 2. An active fluid filled type vibration damping device according to item 1. 3. The stenosis protruding portion is formed of a tapered stenosis protruding from the vibrating member toward the orifice forming hole, and the constriction protruding portion approaches the orifice forming hole. The orifice forming hole is narrowed by the narrowing convex portion so that the first orifice passage having a narrowed passage cross-sectional area is formed between the orifice forming hole and the narrowing protrusion. The active fluid filled type vibration damping device according to claim 2. 4. The stenosis protruding portion is constituted by a cylindrical stenosis tube protruding from the vibrating member. The stenosis tube is made to approach the orifice forming hole and enter the stenosis tube. The orifice forming hole is narrowed by the stenosis tube by contacting the outer peripheral side of the stenosis tube in the vibration member with the opening of the orifice formation hole, thereby closing the orifice formation hole. 3. The active fluid-filled type vibration damping device according to claim 2, wherein said first orifice passage having a narrow passage cross-sectional area is formed. 5. The stenosis, wherein the stenosis projection projects from the vibrating member and is fitted into the orifice forming hole to form the first orifice passage between fitting surfaces with the orifice forming hole. 3. The cross-sectional area and / or length of the first orifice passage is changed by changing a fitting amount of the stenotic fitting portion into the orifice forming hole. 4. The active fluid-filled type vibration damping device according to item 1. 6. A closed working air chamber is formed on the opposite side of the vibrating chamber from the vibrating chamber, and the vibrating member is vibrated by exerting air pressure fluctuation on the working air chamber. 6. The method according to claim 1, wherein the relative position of the orifice adjusting member provided in the vibration member with respect to the orifice forming hole is changed and set by adjusting the air pressure of the working air chamber. An active-type fluid-filled vibration damping device according to any one of the above. 7. The vibrating air chamber to which air pressure fluctuation for vibrating the vibrating member is applied by dividing the working air chamber and the orifice adjusting member provided in the vibrating member are positioned. 7. The active fluid filled type vibration damping device according to claim 6, wherein a tuning air chamber to which air pressure for adjustment is applied is formed. 8. An urging means for constantly urging the vibrating member in a direction in which the orifice adjusting member approaches the orifice forming hole, and applies a negative pressure to the working air chamber. By applying a displacement force to the vibrating member in a direction opposite to the urging force of the urging means, the vibrating member is vibrated, and the orifice adjusting member approaches / closes to the orifice forming hole. 8. The active fluid-filled type vibration damping device according to claim 6, wherein the position in the separation direction is changed. 9. An air line and valve means for effecting air pressure fluctuations in the working air chamber by alternately connecting pneumatic pressure sources having different pressures to the working air chamber; The active fluid-filled type vibration damping device according to any one of claims 6 to 8, further comprising pressure adjusting means for adjusting the magnitude of the average negative pressure to be applied. 10. An equilibrium chamber filled with an incompressible fluid, wherein a part of a wall portion is formed of a flexible film which is easily deformable and a volume change is allowed based on deformation of the flexible film. A fluid which is formed independently of the pressure receiving chamber and the vibration chamber, forms a second orifice passage for connecting the equilibrium chamber to the pressure receiving chamber, and is caused to flow through the second orifice passage. The active fluid-filled type vibration damping device according to any one of claims 1 to 9, wherein the resonance frequency is set to a lower frequency range than the resonance frequency of the fluid caused to flow through the first orifice passage. 11. The control device according to claim 1, further comprising a control device that controls the operation of the driving unit so that the vibration member is vibrated at a frequency corresponding to the frequency of the vibration to be damped. A fluid-filled active vibration isolator according to the above description. 12. A first mounting member and a second mounting member elastically connected by the main rubber elastic body are provided,
The main liquid chamber is formed on one side of the partition member supported by the second mounting member, and the vibration chamber is formed on the other side, and the orifice forming hole penetrates the partition member. The active member according to any one of claims 1 to 11, wherein the vibration member, which forms a part of a wall portion of the vibration chamber, is displaceably supported by the second mounting member. Type fluid filled type vibration damping device.