JP3603653B2 - Fluid-filled anti-vibration device - Google Patents

Description

[0001]
【Technical field】
The present invention relates to a fluid-filled type vibration damping device in which a vibration damping effect is obtained by utilizing a flow action of a fluid sealed therein, and in particular, by making a plurality of orifice passages selectively function, a plurality of orifice passages are provided. The present invention relates to a fluid filled type vibration damping device capable of exhibiting an effective vibration damping effect against different vibrations.
[0002]
[Background Art]
Description of the Related Art Conventionally, as a kind of a vibration-proof connecting body or a vibration-proof support interposed between members constituting a vibration transmission system, it is described in Japanese Patent Publication No. 2-6934 and Japanese Patent Application Laid-Open No. 6-264958. As described above, a part of the wall is formed by a main rubber elastic body that is elastically deformed by input vibration, and a pressure receiving chamber into which vibration is input and a part of the wall is formed by a flexible film that is easily deformed. To form an equilibrium chamber whose volume is allowed to change, fill the pressure receiving chamber and the equilibrium chamber with an incompressible fluid, and connect the pressure receiving chamber and the equilibrium chamber with each other. 2. Description of the Related Art There is known a fluid-filled type vibration damping device provided with one orifice passage and further provided with first valve means for switching the high-frequency first orifice passage between a communicating state and a blocking state. In such a vibration isolator, in a state where the first orifice passage for high frequency is blocked, the vibration isolating effect based on the resonance action of the fluid that is caused to flow through the orifice passage for low frequency is exhibited, and the first orifice for high frequency is exhibited. In a state where the orifice passages are communicated with each other, a vibration damping effect based on the resonance action of the fluid caused to flow through the first high-frequency orifice passage is exhibited, so that the low-frequency orifice passage and the first high-frequency orifice passage are respectively provided. Any effective vibration damping effect can be obtained with respect to a plurality of different tuned vibrations. Therefore, for example, the present invention is applied to an automobile engine mount or the like, and a low frequency orifice passage such as a shake is used. Tuning at the time of vibration and tuning the first orifice passage for high frequency to vibration at stop such as idling vibration And by, for different vibration input when the vehicle is stopped and during travel of the vehicle, both it becomes possible to obtain an effective vibration damping effect.
[0003]
By the way, the vibration damping device may be required to have higher vibration damping performance. For example, a vibration damping effect that is effective against vibrations in a plurality of different frequency ranges and vibrations in a wide frequency range is required at the same time. There are cases. More specifically, for example, in an engine mount for an automobile, while maintaining a vibration-proof effect against a shake or the like due to a low-frequency orifice passage when the vehicle is running, when the vehicle is stopped, a vibration-proof effect against idling low-order vibration, An anti-vibration effect against idling higher-order vibration may be required at the same time.
[0004]
However, in the vibration isolator having the conventional structure as described above, the orifice passage for low frequency and the first orifice passage for high frequency which are selectively operated are effective only for vibration in any one narrow frequency range. Since only a vibration effect is exhibited, it has been extremely difficult to obtain an effective vibration damping effect against vibrations in a plurality of or wide frequency ranges at the same time.
[0005]
In addition to the low-frequency orifice passage and the high-frequency first orifice passage, an additional orifice tuned to a frequency range different from that of the high-frequency first orifice passage so as to function simultaneously with the high-frequency first orifice passage. It is also conceivable to separately form the passage so as to extend between the pressure receiving chamber and the balancing chamber. However, when such an additional orifice passage is formed, not only does the vibration isolator increase in size to secure a space for forming the additional orifice passage, but also both the first high-frequency orifice passage for high frequency and the additional orifice passage are communicated simultaneously. It is necessary to shut off the fluid, and it is necessary to simultaneously secure the fluid flow rates of the first orifice passage for high frequency and the additional orifice passage. There was a problem that it could not be done.
[0006]
[Solution]
Here, the present invention has been made in view of the above-described circumstances, and a problem to be solved is to provide a low-frequency orifice passage and a high-frequency orifice passage that can be selectively operated. In the fluid filled type vibration damping device, when the high frequency orifice passage is made to function, not only the input vibration in the tuning frequency range of the high frequency orifice passage but also the input vibration in another or wide frequency range. An object of the present invention is to realize a novel structure capable of exhibiting an effective vibration damping effect with a simple and compact structure.
[0007]
[Solution]
Hereinafter, embodiments of the present invention made to solve such problems will be described. In addition, each aspect described below can be adopted in any combination. In addition, it should be understood that aspects or technical features of the present invention are not limited to the following description, but are recognized based on the inventive concept described in the entire specification and the drawings. It is.
[0008]
According to 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 input vibration and vibration is input, and a wall which is easily deformable by a flexible film. A low-frequency orifice that is partially configured to form an equilibrium chamber whose volume change is allowed, fills an incompressible fluid in the pressure receiving chamber and the equilibrium chamber, and communicates the pressure receiving chamber and the equilibrium chamber with each other. A high-frequency first orifice passage, and a first valve means for switching the high-frequency first orifice passage between a communicating state and a shut-off state; First flow rate limiting means for limiting the amount of fluid flowing through the passage is provided closer to the equilibrium chamber than the first valve means, and the first valve in the high frequency first orifice passage is provided. That the area between the stage and said first flow restriction means to form a small communication hole that allowed to directly communicate with the equilibrium chamber, characterized.
[0009]
In the fluid-filled type vibration damping device according to the first aspect, by communicating / blocking the first high-frequency orifice passage by the first valve means, the high-frequency first orifice passage is shut off under the closed state. Fluid flow through the low-frequency orifice passage is positively generated, preventing vibration in the tuning frequency range of the low-frequency orifice passage based on the resonance action of the fluid caused to flow through the low-frequency orifice passage. While the vibration effect is effectively exhibited, the fluid flow through the first high-frequency orifice passage having a smaller flow resistance than the low-frequency orifice passage is actively generated under the communication state of the first high-frequency orifice passage. The fluid that is caused to flow through the high-frequency first orifice passage in response to vibration in the tuning frequency range of the high-frequency first orifice passage. The vibration damping effect based on the resonance action is effectively exhibited, and the amount of fluid flowing through the high frequency first orifice passage is restricted by the first flow rate restricting means, so that the fluid flowing through the low frequency orifice passage is restricted. The flow rate is also advantageously secured. In this case, under the communication state of the first orifice passage for high frequency, the fluid flow through the communication small hole is allowed at the same time as the low frequency orifice passage, and the fluid flow through the communication small hole is restricted by the first flow rate restriction. Since the flow rate is not limited by the means and is permitted in the same manner as the low-frequency orifice passage, the tuning frequency range of the low-frequency orifice passage is adjusted by adjusting the flow path cross-sectional area and length of the communication small hole. Can be changed and adjusted.
[0010]
Therefore, in such a fluid filled type vibration damping device, the input vibration in the original frequency range in which the low frequency orifice passage is tuned by the low frequency orifice passage while the first high frequency orifice passage is shut off. While the effective vibration damping effect is exerted on the high frequency first orifice passage, the vibration damping effect against the high frequency vibration by the high frequency first orifice passage is exhibited and the low frequency The fluid flow through the orifice passage for air is also generated, and the vibration damping effect of the orifice passage for low frequency is also exhibited. Moreover, in the communication state of the first high-frequency orifice passage, the communication small hole is in the communication state, so that the tuning frequency range of the low-frequency orifice passage is originally lower than that of the high-frequency first orifice passage in the cut-off state. Is different from the tuning frequency range described above, the tuning frequency range is set according to the size of the communication small hole. As a result, under the communication state of the first high-frequency orifice passage, the low-frequency orifice passage functions as an orifice passage tuned differently from the original characteristics, and the low-frequency orifice passage prevents the low-frequency orifice passage. The vibration effect and the vibration-proof effect of the first high-frequency orifice passage are effectively exhibited in different tuned frequency ranges.
[0011]
Therefore, for example, while tuning the single orifice passage for low frequency to low frequency vibration such as shake, the first orifice passage for high frequency is tuned to high frequency vibration such as idling higher order vibration, and the communication small hole is tuned for high frequency vibration. Under the communication state of the first orifice passage, it is possible to tune the tuning frequency range of the low-frequency orifice passage so as to shift to a middle frequency region such as idling low-order vibration. With the first orifice passage closed, an effective vibration damping effect against shake can be obtained based on the resonance action of the fluid that is caused to flow through the low frequency orifice passage, and when the vehicle stops, the high frequency first orifice passage is closed. In the communicating state, resonance of the fluid caused to flow through the first high-frequency orifice passage In addition to obtaining an effective vibration damping effect against idling high-order vibration based on the application, the idling low-order vibration is performed based on the flow action such as the resonance action of the fluid that is made to flow through the low-frequency orifice passage adjusted by the communication small hole. Therefore, an effective anti-vibration effect can be obtained.
[0012]
In particular, in this aspect, the orifice passage capable of exhibiting a vibration-proof effect against vibrations in a frequency range different from that of the first high-frequency orifice passage under the communication state of the first high-frequency orifice passage is formed by the low-frequency orifice. Since it is formed using a passage, a fluid-filled type vibration damping device that can exhibit an effective vibration damping effect simultaneously with respect to a plurality of vibrations or a wide frequency range with a simple and compact structure is advantageous. It can be achieved.
[0013]
In the first embodiment as described above, the first valve means may be any as long as it can communicate / block the first orifice passage for high frequency. For example, various types of valves such as a gate valve, a butterfly valve, and a rotary valve may be used. A valve mechanism having a structure can be suitably employed. Further, as the first flow rate limiting means, for example, the high frequency first orifice is disposed in a state where a small displacement in the fluid flow direction of the high frequency first orifice passage is allowed, and the high frequency first orifice is provided at the displacement limiting position. A movable plate body that closes the passage, a rubber elastic plate that is disposed with the outer peripheral edge fixedly supported, and that allows fluid flow through the first high-frequency orifice passage by elastic deformation, or the like can be suitably used. . Furthermore, the communication ostium need not itself be connected / disconnected, but can be advantageously formed with a simple structure that is always connected.
[0014]
In a second aspect of the present invention, in the fluid-filled type vibration damping device having the structure according to the first aspect, the communication small hole is formed between the low-frequency orifice passage and the high-frequency first orifice passage. It is characterized by being formed with a smaller flow path cross-sectional area and a smaller flow path length than any of them. In this embodiment, the tuning frequency of the low-frequency orifice passage can be advantageously changed and adjusted by the communication small hole while avoiding the adverse effect on the characteristics of the first high-frequency orifice passage.
[0015]
According to a third aspect of the present invention, in the fluid filled type vibration damping device having the structure according to the first or second aspect, a hard partition member for partitioning the pressure receiving chamber and the equilibrium chamber is provided. The member has an internal passage extending linearly in a direction substantially perpendicular to the direction in which the pressure receiving chamber and the equilibrium chamber are opposed to each other, and one end of the internal passage is bent toward the pressure receiving chamber and opened. The other end is bent toward the equilibrium chamber side to open, thereby forming the first high-frequency orifice passage, and disposing the first valve means on the internal passage, and An end of the passage closer to the equilibrium chamber than the first valve means is further linearly extended beyond a bending point toward the equilibrium chamber, and the extended portion and the equilibrium chamber are connected to each other by the communication small. The feature is that they are connected directly by holes. To. In such an embodiment, the communication small hole can be formed simply and compactly while ensuring sufficient design flexibility such as the flow path length and the cross-sectional area of the first orifice passage for high frequency. .
[0016]
According to a fourth aspect of the present invention, in the fluid-filled type vibration damping device having a structure according to any one of the first to third aspects, a high-frequency second vibration communicating the pressure receiving chamber and the equilibrium chamber with each other is provided. A second orifice passage is provided to tune the second high-frequency orifice passage to a higher frequency range than the first high-frequency orifice passage, and to restrict a fluid flow amount through the second high-frequency orifice passage. And a second valve means for switching the high-frequency second orifice passage between a communicating state and a shut-off state, and selecting between the high-frequency second orifice passage and the high-frequency first orifice passage. It is characterized in that it is made to communicate with each other. In this aspect, the fluid flow through the second high-frequency orifice passage is generated under the cutoff state of the first high-frequency orifice passage, and the vibration isolation effect in the high frequency range based on the resonance action of the fluid is generated. At the same time, the amount of fluid flowing through the second high-frequency orifice passage is limited by the second flow rate restricting means, so that the fluid flowing through the low-frequency orifice passage also exerts a vibration damping effect. At this time, the first orifice passage for high frequency is blocked, and the communication small hole is also in a blocked state, so that the vibration isolation effect of the low frequency orifice passage is not affected by the communication small hole, and the original tuning is performed. Demonstrated based on characteristics.
[0017]
Therefore, for example, as described in the first aspect, the single orifice passage for low frequency is tuned to low frequency vibration such as shake, and the first orifice passage for high frequency is tuned to high frequency vibration such as idling higher order vibration. A fluid-filled vibration isolator tuned so that the tuning frequency range of the low-frequency orifice passage shifts to medium-frequency vibration such as idling low-order vibration under the communication state of the high-frequency first orifice passage. In the device, by forming a high-frequency second orifice passage according to the fourth aspect, by tuning the high-frequency wave second orifice passage to high-frequency vibrations such as run-up muffled even higher than idling higher-order vibration, When the vehicle is stopped, idling low-order vibration due to the low-frequency orifice passage adjusted by the communication small hole It is possible to simultaneously obtain the vibration damping effect against the high-order vibration of idling by the first orifice passage for high frequency and the vibration damping effect for the shake by the orifice passage for low frequency and the high frequency second orifice when the vehicle is running. The vibration damping effect against the muffled noise caused by the passage can be obtained at the same time. In addition, as the second flow rate restricting means, similarly to the first flow rate restricting means, for example, the high frequency second orifice passage is disposed in a state where a small displacement in the fluid flow direction is allowed, and the displacement amount is A movable plate that closes the high-frequency second orifice passage at the restricted position, and a rubber elastic member that is fixedly supported at an outer peripheral edge thereof and that allows fluid flow through the second high-frequency orifice passage by elastic deformation. A plate or the like can be suitably adopted.
[0018]
According to a fifth aspect of the present invention, in the fluid-filled type vibration damping device having the structure according to the fourth aspect, the second flow rate restricting unit is provided on the high-frequency second orifice passage. It is characterized by being located closer to the pressure receiving chamber than the second valve means. In this aspect, since the second flow restricting means is disposed on the opposite side of the first flow restricting means with respect to the valve means, the first flow restricting means and the second flow restricting means are disposed. It is possible to advantageously and efficiently secure a space for disposing the second flow rate restricting means.
[0019]
In a sixth aspect of the present invention, in the fluid-filled type vibration damping device having the structure according to the fourth or fifth aspect, the first flow rate restricting means is provided in the first orifice passage for high frequency. A movable member is disposed at the opening toward the equilibrium chamber so as to be displaceable, and the amount of displacement is limited so that the amount of fluid flowing through the first orifice passage for high frequency is restricted. Extending to the opening of the high-frequency second orifice passage toward the equilibrium chamber and integrally covering both openings of the high-frequency first orifice passage and the high-frequency second orifice passage. It is characterized by having been provided. In this embodiment, the space for forming each opening on the equilibrium chamber side in the first orifice passage for high frequency and the second orifice passage for high frequency and the space for disposing the first flow restricting means are both efficiently used. And the vibration isolator can be made compact as a whole.
[0020]
According to a seventh aspect of the present invention, there is provided a fluid filled type vibration damping device having a structure according to any of the fourth to sixth aspects, wherein the first mounting member is spaced apart in a vibration input direction. And the second mounting member are connected by the main rubber elastic body, the pressure receiving chamber is formed on one side with the partition member supported by the second mounting member interposed therebetween, and the equilibrium chamber is formed on the other side. On the other hand, in the partition member, the low-frequency orifice passage is formed so as to extend in a circumferential direction at an outer peripheral portion of the partition member, and the high-frequency first orifice passage is formed in the balance with the pressure receiving chamber. The high-frequency second orifice passage is formed in a direction substantially perpendicular to the facing direction of the chamber, and further penetrates the second high-frequency orifice passage linearly in the direction opposite to the pressure receiving chamber and the equilibrium chamber. While forming in the direction The first orifice passage for high frequency and the second orifice passage for high frequency are disposed at the intersection of the first orifice passage for high frequency and the second orifice passage for high frequency. And a second valve means.
[0021]
In this embodiment, the high-frequency first orifice passage tuned to a high frequency range and the high-frequency second orifice passage tuned to a higher frequency range can be formed with excellent space efficiency. The valve means for selectively connecting the high-frequency first orifice passage and the high-frequency second orifice passage can be assembled with excellent space efficiency. In particular, in the present embodiment, a rotary valve such as a rotary valve is suitably adopted as the valve means, whereby the space for disposing the valve means can be made more efficient. Further, in this aspect, the third aspect is suitably used in combination, whereby the communication small holes can also be formed with excellent space efficiency, and the entire fluid flow path is formed more compactly. It becomes possible.
[0022]
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.
[0023]
First, FIGS. 1 to 4 show an automobile engine mount 10 as one embodiment of the present invention. In the engine mount 10, a first mounting member 12 as a first mounting member and a second mounting member 14 as a second mounting member are arranged so as to be separated from each other and opposed to each other, and between the opposed surfaces. It is elastically connected by an interposed main body rubber elastic body 16. The engine mount 10 is configured such that the power unit is fixedly mounted on the first mounting bracket 12 and the second mounting bracket 14, one of which is fixedly mounted on the power unit side and the other is fixedly mounted on the body side. On the other hand, it is designed to support vibration isolation. In such a mounted state, the power unit weight is exerted on the engine mount 10 in a substantially vertical direction in FIG. 1 which is a direction substantially opposite to the first mounting bracket 12 and the second mounting bracket 14, The main rubber elastic body 16 is elastically deformed in a direction in which the first mounting bracket 12 and the second mounting bracket 14 approach each other, and in a direction substantially opposite to the first mounting bracket 12 and the second mounting bracket 14. The main vibration to be damped is input. In the following description, the vertical direction refers to the vertical direction in FIG. 1 in principle.
[0024]
More specifically, the first mounting bracket 12 has a substantially disc shape, and has a second mounting bracket 14 that protrudes radially outward at one location on the outer peripheral edge thereof. A stopper protruding portion 18 that bends and extends toward the side and has a tip portion bent in a hook shape is integrally formed. At the center of the lower surface of the first mounting bracket 12, a substantially cup-shaped support bracket 20 is overlapped and welded at the opening. Furthermore, a mounting bolt 22 protruding upward is fixed at the center of the first mounting bracket 12, and the first mounting bracket 12 is connected to a power unit (not shown) of the vehicle by the mounting bolt 22. It can be attached.
[0025]
On the other hand, the second mounting fitting 14 is formed by a cylindrical fitting 24 having a large-diameter, substantially cylindrical shape, and a bottom fitting 26 having a large-diameter, shallow, substantially bottomed cylindrical shape. The cylindrical metal fitting 24 has a tapered portion 28 whose upper end in the axial direction increases in diameter upward, while a step portion 30 that expands radially outward is formed at the lower end in the axial direction. A large-diameter cylindrical caulking portion 32 extending axially downward from the outer peripheral edge of the step portion 30 is integrally formed. Further, an abutment projecting portion 36 which protrudes radially outward and is reinforced by a reinforcing metal member 34 is integrally formed at a peripheral portion of the opening of the tapered portion 28 of the cylindrical metal member 24. On the other hand, a flange-like portion 38 that extends radially outward is formed integrally with the peripheral edge of the opening of the bottom fitting 26. Then, the bottom fitting 26 is superimposed on the lower opening of the tubular fitting 24, and the swaged portion 32 of the tubular fitting 24 is swaged and fixed to the flange-shaped portion 38 of the bottom fitting 26. Is formed in a generally deep-bottomed, substantially bottomed cylindrical shape. At the center of the bottom of the bottom fitting 26, a mounting bolt 40 protruding downward is fixedly provided. With this mounting bolt 40, the second mounting fitting 14 is attached to a vehicle body (not shown). It has become.
[0026]
The second mounting member 14 is disposed so as to open upward in the axial direction, and is separated from the opening side of the second mounting member 14 so that the first mounting member 12 is opened. , And the second mounting bracket 14 are disposed on substantially the same central axis. Thus, a main rubber elastic body 16 is disposed between the first mounting metal 12 and the second mounting metal 14, and the first mounting metal 12 and the second Are elastically connected. The main rubber elastic body 16 has a substantially truncated conical shape as a whole, the first mounting bracket 12 is superimposed on the small-diameter side end face, and the support bracket 20 is inserted in the axial direction from the small-diameter side end face and embedded. In the inserted state, the first mounting member 12 and the supporting member 20 are vulcanized and bonded to the rubber elastic body 16. The inner peripheral surface of the tapered portion 28 of the cylindrical metal fitting 24 constituting the second fitting 14 is superposed and vulcanized and bonded to the outer peripheral surface of the large-diameter end of the main rubber elastic body 16. In short, in the present embodiment, the main rubber elastic body 16 is formed as an integrally vulcanized molded product including the first mounting bracket 12, the support bracket 20, and the cylindrical metal fitting 24, and is formed on the upper side in the axial direction of the cylindrical metal fitting 24. The opening is closed by the main rubber elastic body 16 in a fluid-tight manner.
[0027]
In such an integrally vulcanized molded product, the tapered outer peripheral surface of the support bracket 20 on the first mounting bracket 12 side and the tapered portion 28 of the cylindrical bracket 24 on the second mounting bracket 14 side are opposed to each other. The main rubber elastic body 16 is interposed between the opposing surfaces so that a load such as a power unit weight can be effectively applied to the main rubber elastic body 16 as a compressive force. Have been. In such an integrally vulcanized molded product, a large-diameter recess 42 is formed on the large-diameter side end surface of the main rubber elastic body 16, and is opened in the cylindrical metal fitting 24. On the peripheral surface, a thin seal rubber layer 43 extending over substantially the entire surface is formed integrally with the main rubber elastic body 16. Furthermore, a cushioning rubber 44 is formed on the surface of the contact protrusion 36 of the second mounting member 14, and the stopper protrusion of the first mounting member 12 is covered so as to cover the contact protrusion 36. Section 18 is aligned. When the first mounting member 12 and the second mounting member 14 are relatively displaced by an input vibration load or the like, the stopper projection 18 is brought into contact with the contact projection 36 via the buffer rubber 44. A stopper function for limiting the relative displacement amount of the first mounting member 12 and the second mounting member 14, and furthermore, the elastic deformation amount of the main rubber elastic body 16 is exerted. I have.
[0028]
Further, a partition member 46 and a diaphragm 48 as a flexible film are sequentially inserted and fitted into the integrally vulcanized molded product from the lower opening in the axial direction of the cylindrical metal fitting 24, and the second mounting metal fitting is formed. 14 is fixedly assembled. The partition member 46 is formed of a hard material such as a metal or a synthetic resin, and has a substantially circular block shape slightly smaller in diameter than the tubular metal fitting 24. Further, the outer peripheral edge of the lower end in the axial direction of the partition member 46 extends cylindrically downward in the axial direction, and the protruding tip portion is bent radially outward, so that the flange-shaped portion 50 is integrally formed. Is formed. The partition member 46 is inserted into the cylindrical metal fitting 24, the outer peripheral surface of the partition member 46 is in close contact with the cylindrical metal fitting 24 via the sealing rubber layer 42, and the flange 50 is overlapped with the step 30 of the cylindrical metal fitting 24. Then, it is fixed to the second mounting member 14 by being caulked and fixed by the caulking portion 32 together with the flange-shaped portion 38 of the bottom metal member 26. The diaphragm 48 is formed of a thin rubber film that can be easily deformed. The diaphragm 48 has a slack at a central portion so as to be easily deformed, and a substantially annular plate-shaped fixing portion at an outer peripheral edge portion. The metal fitting 52 is bonded by vulcanization. Then, the diaphragm 48 is inserted into the cylindrical metal fitting 24, the fixing metal fitting 52 is overlapped on the stepped portion 30 of the cylindrical metal fitting 24, and is caulked and fixed together with the flange-shaped part 38 of the bottom metal fitting 26, so that the second fitting is performed. It is attached in a state where the lower opening of the attachment fitting 14 is covered in a fluid-tight manner. A seal rubber layer 53 is formed on the surface of the fixing bracket 52 to seal a portion fixed by caulking by the second mounting bracket 14 in a fluid-tight manner.
[0029]
As a result, both side openings of the cylindrical metal fitting 24 are covered with the main rubber elastic body 16 and the diaphragm 48 in a fluid-tight manner, and a fluid chamber 54 in which an incompressible fluid is sealed is formed. As the incompressible fluid to be enclosed, for example, water, alkylene glycol, polyalkylene glycol, silicone oil, or the like can be adopted. A low viscosity fluid of 0.1 Pa · s or less is preferably used. Further, the injection of the incompressible fluid can be performed simultaneously with the formation of the fluid chamber 54, for example, by assembling the partition member 46 and the diaphragm 48 to the integrally vulcanized molded product in the fluid. In the present embodiment, after the partition member 46 and the diaphragm 48 are assembled to the integrally vulcanized molded product in the atmosphere, the partition member 46 and the diaphragm 48 are incompressible through an injection hole 56 formed in a fixing bracket 52 vulcanized and bonded to the diaphragm 48. The fluid is injected into the fluid chamber 54, and then the injection hole 56 is sealed with a blind rivet 58 so that the incompressible fluid is filled.
[0030]
Further, the fluid chamber 54 is fluid-tightly divided into two parts by a partition member 46 disposed at an axially intermediate portion of the cylindrical metal fitting 24. Therefore, a part of the wall portion is provided above the partition member 46 in the body. While a pressure receiving chamber 60 formed of the rubber elastic body 16 is formed, an equilibrium chamber 62 whose wall is partially formed of the diaphragm 48 is formed below the partition member 46. That is, when pressure is applied to the pressure receiving chamber 60 between the first mounting member 12 and the second mounting member 14, vibration is input based on the elastic deformation of the main rubber elastic body 16 and a pressure change is generated. On the other hand, the equilibrium chamber 62 absorbs and avoids a pressure change by easily permitting a volume change by deformation of the diaphragm 48. On the opposite side of the diaphragm 48 from the equilibrium chamber 62, an air chamber 64 is formed between the diaphragm 48 and the bottom fitting 26 to allow the deformation of the diaphragm 48.
[0031]
Further, a partition member 46 for partitioning the pressure receiving chamber 60 and the equilibrium chamber 62 has a low-frequency orifice passage through which the pressure receiving chamber 60 and the equilibrium chamber 62 communicate with each other to allow fluid flow between the two chambers 60 and 62. 66, a first high-frequency orifice passage 68 and a second high-frequency orifice passage 70 are formed substantially independently of each other. Then, based on the pressure difference generated between the pressure receiving chamber 60 and the equilibrium chamber 62 at the time of vibration input, a fluid flow is generated through each of the orifice passages 66, 68, 70, so that each of the orifice passages 66, 68, 70 is formed. With respect to the input vibration in the frequency range according to the tuning of 70, an anti-vibration effect based on the resonance action of the fluid is exhibited.
[0032]
More specifically, first, the partition member 46 is provided with a concave groove 112 which is opened on the upper surface and extends in the outer peripheral portion by a length slightly less than one circumference in the circumferential direction, and the upper surface of the partition member 46 has a thin wall. A disk-shaped lid 78 is overlaid so as to cover the entire surface, and the concave groove 112 is covered with the lid 78. One end of the groove 112 in the circumferential direction is opened to the pressure receiving chamber 60 through a communication hole 114 formed through the cover fitting 78, while the other end of the groove 112 in the circumferential direction is connected to the partition member 46. Is opened to the equilibrium chamber 62 through a connection hole 116 penetrating in the axial direction. Accordingly, the low-frequency portion including the concave groove 112, the communication hole 114, and the connection hole 116 extends across the space between the pressure receiving chamber 60 and the equilibrium chamber 62 and allows the fluid flow between the two chambers 60, 62. An orifice passage 66 is formed. In the present embodiment, the low-frequency orifice passage 66 is always formed in a communicating state.
[0033]
In particular, in the present embodiment, such a low-frequency orifice passage 66 can exhibit, for example, a vibration-proof effect (attenuation effect) that is effective against shake vibration, for example, based on the resonance effect of the fluid that flows inside the low-frequency orifice passage 66. Has been tuned to. In this tuning, for example, in consideration of the wall spring stiffness of the pressure receiving chamber 60 and the equilibrium chamber 62 and the density of the sealed fluid, the cross-sectional area of the concave groove 112, the communication hole 114, and the connection hole 116 is A1 and the length. : L1 ratio: A1 / L1.
[0034]
An upper recess 72 and a lower recess 74 are formed at the center of the upper surface and the lower surface of the partition member 46. In the lower recess 74, a first rubber film 82 as a first flow rate restricting means is provided. The first rubber film 82 has a substantially annular fixing plate 84 bonded to the outer peripheral edge thereof by vulcanization, and the fixing plate 84 is overlapped on the bottom surface of the lower recess 74 and fixed by fixing bolts 85. As a result, the first rubber film 82 is supported by the fixing metal plate 84 in a state where the first rubber film 82 is separated from the bottom surface of the lower recess 74 by a predetermined distance and covers the opening of the lower recess 74 in a fluid-tight manner. In this arrangement state, the first rubber film 82 is allowed to be elastically deformed, and its lower surface is directly exposed to the equilibrium chamber 62.
[0035]
On the other hand, the upper recess 72 is covered by a cover fitting 78, and opening windows 80, 80 for opening the upper recess 72 to the pressure receiving chamber 60 are formed in the cover fitting 78. In the upper recess 72, a second rubber film 76 as a second flow rate restricting means is provided, and a thick outer peripheral edge is formed between the bottom surface of the recess 72 and the cover fitting 78. By being sandwiched, the central portion of the second rubber film 76 is disposed in the upper recess 72 so as to be elastically deformable. Accordingly, the inside of the upper recess 72 is fluid-tightly divided into a bottom side and an opening side by the second rubber film 76, and the pressure receiving chamber is placed on the upper surface of the second rubber film 76. An internal pressure of 60 is exerted through the opening windows 80, 80.
[0036]
Here, in the present embodiment, the central portion of the second rubber film 76 is thickened, and is substantially in contact with the bottom surface of the upper recess 72 of the partition member 46 and the cover fitting 78 to regulate the displacement. At the same time, the first rubber film 82 has a smaller wall thickness and a larger free length than the second rubber film 76. Thus, the first rubber film 82 has a smaller spring constant than the second rubber film 76, and elastic deformation is easily allowed. In addition, the first rubber film 82 and the second rubber film 76 are configured such that the displacement amount due to deformation is limited mainly by their own spring stiffness, and when the same pressure acts, A larger displacement is generated for the first rubber film 82 than for the second rubber film 76.
[0037]
Further, the partition member 46 is formed with a radial hole 90 as an internal passage extending straight through the intermediate portion in the axial direction with a substantially rectangular cross section in the radial direction. That is, the radial hole 90 is formed so that the inside of the partition member 46 is linearly formed in a direction substantially orthogonal to the direction in which the pressure receiving chamber 60 and the equilibrium chamber 62 face each other. It is covered with a metal fitting 24 in a fluid-tight manner. In addition, connection holes 92 and 94 are formed near both ends in the radial direction of the radial hole 90 so as to branch off from the radial hole 90 and extend in opposite axial directions. One end of the radial hole 90 is opened to the pressure receiving chamber 60 through a connection hole 92 from a window 96 formed in the lid 78, and the other end of the radial hole 90 is connected to the other end of the radial hole 90. , Through the connection hole 94, the lower recess 74 is opened. Thus, the first rubber film 82 extends over the pressure receiving chamber 60 and the equilibrium chamber 62, including the radial holes 90, the connection holes 92 and 94, and the lower recess 74, based on the elastic deformation of the first rubber film 82. A high frequency first orifice passage 68 is formed to allow fluid flow between the two chambers 60 and 62. In particular, in the present embodiment, the first high-frequency orifice passage 68 has an effective vibration damping effect against idling high-order vibrations such as tertiary idling based on the resonance action of the fluid caused to flow through the inside. It is tuned to be able to demonstrate. Note that, like the low-frequency orifice passage 66, such tuning takes into consideration, for example, the wall spring rigidity of the pressure receiving chamber 60 and the equilibrium chamber 62, the spring rigidity of the first rubber film 82, the density of the sealed fluid, and the like. This can be achieved by adjusting the ratio of the cross-sectional area of the radial hole 90 and the connection holes 92 and 94: A2 to the length: L2: A2 / L2. The amount of fluid flowing through the first high-frequency orifice passage 68 is restricted by the elasticity of the first rubber film 82. In the present embodiment, the value of A2 / L2 in the first orifice passage 68 for high frequency is such that A1 / L1 <A2 / L2 with respect to the value of A1 / L1 in the orifice passage 66 for low frequency. , Whereby the tuning characteristics as described above are advantageously realized.
[0038]
Furthermore, the partition member 46 is formed with an axial hole 86 that extends linearly with a substantially rectangular cross section on the central axis, and both sides of the axial hole 86 are formed by the upper recess 72 and the lower recess 74. Each center is opened. Accordingly, the first and second rubber films 76 and 82 extend over the pressure receiving chamber 60 and the equilibrium chamber 62, including the axial hole 86 and the upper and lower recesses 72 and 74. Thus, a high-frequency second orifice passage 70 is formed to allow fluid flow between the two chambers 60 and 62. In particular, in the present embodiment, the high-frequency second orifice passage 70 can exhibit an effective vibration-proofing effect against high-frequency vibrations such as running noises, based on the resonance action of the fluid caused to flow inside. Has been tuned as such. The tuning is performed in the same manner as the low-frequency orifice passage 66, for example, the wall spring stiffness of the pressure receiving chamber 60 and the equilibrium chamber 62, the spring stiffness of the first and second rubber films 82 and 76, the density of the sealed fluid, and the like. In consideration of the above, the adjustment can be performed by adjusting the ratio of the sectional area: A3 of the axial hole 86 to the length: L3: A3 / L3. The amount of fluid flowing through the high frequency second orifice passage 70 is limited by the elasticity of the first and second rubber films 82 and 76, particularly the elasticity of the second rubber film 76 having a large spring constant. It has become. In the present embodiment, the value of A3 / L3 in the second orifice passage 70 for high frequency is such that A1 / L1 <A3 / L3 with respect to the value of A1 / L1 in the orifice passage 66 for low frequency. , Whereby the tuning characteristics as described above are advantageously realized.
[0039]
Further, in the partition member 46, the first high-frequency orifice passage 68 and the second high-frequency orifice passage 70 intersect each other orthogonally at a substantially central portion in the length direction of each passage. A valve mounting hole 100 that extends linearly through the partition member 46 is formed in the radial direction orthogonal to both the first and second orifice passages 68 and 70 for high frequency. A rotary valve body 102 as a valve means is inserted into the valve mounting hole 100 and assembled. The rotary valve main body 102 has a hollow cylindrical shape, is fitted into the valve mounting hole 100, cannot be pulled out by the valve pressing plate 103 pressed into the valve mounting hole 100, and is rotatable around the central axis. Has been assembled. In the cylindrical wall portion of the rotary valve body 102, communication holes 104, 104 having a substantially rectangular shape are formed to penetrate inside and outside a portion opposed to each other in one direction in the radial direction. The communication holes 104 are selectively aligned with either the opening of the radial hole 90 or the opening of the axial hole 86 in the inner peripheral surface of the valve mounting hole 100. To communicate with each other.
[0040]
Further, a drive shaft 105 extending to one side in the axial direction is formed integrally with the rotary valve body 102, and the drive shaft 105 penetrates the partition member 46 and protrudes from the outer peripheral surface. Further, a stepping motor 106 is provided outside the second mounting member 14 and is fixed to the cylindrical member 24 via a bracket 108. An output shaft 110 of the stepping motor 106 is connected to the cylindrical member 24. It is inserted through an insertion window 111 provided and connected to the drive shaft 105 of the rotary valve body 102. As a result, the rotary valve body 102 is rotated by the stepping motor 106 so as to communicate with the first high-frequency orifice passage 68 and block the second high-frequency orifice passage 70. The position is alternatively selected to be a rotation position that communicates with the passage 70 and blocks the first orifice passage 68 for high frequency. The operation of the stepping motor 106 is controlled in accordance with the input state of the vibration to be damped, for example, based on a signal (for example, a speed signal, a shift position signal, or the like) corresponding to the running state of the vehicle. Become.
[0041]
In addition, the partition member 46 branches off from the portion located on the equilibrium chamber 62 side of the rotary valve body 102 at the radial hole 90 constituting the first high-frequency orifice passage 68, and is opened to the equilibrium chamber 62. The communication small hole 120 is formed. In particular, in the present embodiment, the radial hole 90 is formed to extend further in the radial direction beyond the opening of the connection hole 94 as a bending point, and a straddle is formed between the extended portion and the equilibrium chamber 62. Thus, the communication small hole 120 is formed so as to extend linearly in the axial direction. Further, the communication small hole 120 is opened from the lower recess 74 to the equilibrium chamber 62, so that the amount of fluid flowing through the communication small hole 120 causes the first recessed portion covering the lower recess 74. Without being limited by the rubber film 82. The communication small hole 120 allows a portion of the high-frequency first orifice passage 68 closer to the equilibrium chamber 62 than the rotary valve main body 102 to always communicate with the equilibrium chamber 62.
[0042]
Thus, when the high-frequency first orifice passage 68 is blocked by the rotary valve body 102 and the high-frequency second orifice passage 70 is communicated, the communication between the pressure receiving chamber 60 and the equilibrium chamber 62 through the small communication hole 120 is established. Is also shut off by the rotary valve body 102 disposed on the high frequency first orifice passage 68. On the other hand, when the high-frequency second orifice passage 70 is blocked by the rotary valve body 102 and the high-frequency first orifice passage 68 is communicated with the high-frequency first orifice passage 68, the communication small hole 120 is also in a communicating state. The fluid flow between the pressure receiving chamber 60 and the equilibrium chamber 62 is allowed. The fluid flow through the communication small hole 120 is allowed in the same manner as the low frequency orifice passage 66 without being restricted by the flow rate of the first rubber film 82. The tuning characteristics set in the low-frequency orifice passage 66 are affected and change according to the conditions.
[0043]
In other words, when the high-frequency first orifice passage 68 is blocked by the rotary valve body 102 and the high-frequency second orifice passage 70 is communicated, the low-frequency orifice passage 66 is affected by the communication small hole 120. Without receiving the vibration, the vibration isolating effect based on the resonance action of the fluid that is caused to flow through the low-frequency orifice passage 66 in accordance with the tuning of the low-frequency orifice passage 66 alone, that is, in the present embodiment, against the low-frequency vibration such as a shake. An anti-vibration effect (attenuation effect) can be effectively exhibited. On the other hand, when the high-frequency second orifice passage 70 is blocked by the rotary valve body 102 and the high-frequency first orifice passage 68 is communicated with the high-frequency The tuning characteristic of the orifice passage 66 is changed, and in the present embodiment, in particular, based on the fluid flow action through the low-frequency orifice passage 66 affected by the communication small hole 120, the idling primary and the like are controlled. Considering the size of the low frequency orifice passage 66, the rigidity of the wall springs of the pressure receiving chamber 60 and the equilibrium chamber 62, the density of the sealed fluid, etc., so that the vibration isolating effect (insulating effect) against idling low-order vibration can be effectively exerted. Tuning is performed by appropriately adjusting the passage length and passage cross-sectional area of the communication small hole 120. As described above, the influence of the communication small hole 120 is generally generated in a direction in which the tuning frequency of the low frequency orifice passage 66 is shifted to the high frequency side. Also, it has been confirmed that the influence exerted on the low-frequency orifice passage 66 by the communication small hole 120 can be adjusted by changing the size of the communication small hole 120, for example, the passage length or the passage sectional area, Generally, as the passage length of the communication small hole 120 is shortened or the passage cross-sectional area is increased, the tuning frequency of the low-frequency orifice passage 66 is shifted to a higher frequency side by connecting the communication small hole 120. Can be done. In the present embodiment, the value of A4 / L4 in the communication small hole 120 is different from the value of A1 / L1 in the low frequency orifice passage 66 and the value of A2 / L2 in the high frequency first orifice passage 68. Thus, A1 / L1 <A4 / L4 and A4 / L4 <A2 / L2 are set, whereby the tuning characteristics as described above are advantageously realized.
[0044]
Therefore, in the engine mount 10 having the above-described structure, the mount anti-vibration characteristics can be changed by switching the rotational position of the rotary valve main body 102. When the vehicle is running, the rotary valve main body 102 can be changed. As shown in the drawing, the rotary valve 102 is held at a rotational position that communicates with the high-frequency second orifice passage 70 and shuts off the high-frequency first orifice passage 68, while the rotary valve 102 is stopped when the vehicle is stopped (idling). 102 is rotated about the central axis by 90 degrees from the position shown in the drawing, and is held at a rotation position where the high-frequency first orifice passage 68 is communicated and the high-frequency second orifice passage 70 is shut off.
[0045]
Thus, under the running condition of the vehicle, an effective vibration damping effect (vibration insulation effect) against high-frequency vibrations such as running muffled sound is exhibited based on the resonance action of the fluid that is caused to flow through the second high-frequency orifice passage 70. At the same time, based on the resonance action of the fluid that is caused to flow through the low-frequency orifice passage 66, an effective vibration damping effect (attenuation) against low-frequency vibrations such as shakes follows the original tuning of the low-frequency orifice passage 66. Effect) is exhibited. The low-frequency orifice passage 66 has a higher fluid flow resistance than the high-frequency second orifice passage 70, but the second rubber film 76 limits the fluid flow rate of the high-frequency second orifice passage 70. The fluid flow rate through the low frequency orifice passage 66 can also be advantageously secured.
[0046]
On the other hand, when the vehicle is stopped, fluid flow through the high-frequency first orifice passage 68 and the low-frequency orifice passage 66 is allowed between the pressure receiving chamber 60 and the equilibrium chamber 62, and the fluid flows through the communication small hole 120. Fluid flow is also allowed. Further, the fluid flow rate through the high-frequency first orifice passage 68, which has a smaller fluid flow resistance than the low-frequency orifice passage 66, is restricted by the first rubber film 76. The fluid flow rate through the first frequency orifice passage 68 and the communication small hole 120 can both be advantageously ensured. As a result, an effective vibration damping effect against idling high-frequency vibration such as idling tertiary vibration is exerted on the basis of the resonance action of the fluid caused to flow through the first orifice passage 68 for high frequency, and the communication small holes 120 Based on the resonance effect of the fluid flowing through the orifice passage 66 for low frequency whose tuning has been changed under the influence, an effective vibration damping effect is exhibited against idling low frequency vibration such as idling primary vibration. It is.
[0047]
In short, in the engine mount 10 having the above-described structure, the addition of the extremely small communication hole 120 merely causes the low-frequency orifice passage 66, the high-frequency first orifice passage 68, and the high-frequency second orifice passage 70. The three orifice passages provide effective vibration isolation against vibrations in a plurality or a wide frequency range by the two orifice passages tuned differently from each other in both the vehicle running state and the vehicle stopped state. The effect is exhibited, and thus, the improvement of the vibration isolation characteristics can be achieved with a simple and compact structure.
[0048]
In particular, in the engine mount 10, the single low-frequency orifice passage 66 can be used by giving different tuning characteristics under various conditions when the vehicle is running and when the vehicle is stopped. With respect to the low-frequency orifice passage 66, the characteristic exhibited when the vehicle is running and the characteristic exhibited when the vehicle is stopped can be independently adjusted and set, so that a large degree of freedom in tuning is ensured. Thus, there is an advantage that the required anti-vibration characteristics can be easily and effectively realized.
[0049]
In addition, in the engine mount 10 of the present embodiment, the area where the first rubber film 82 is provided can be reduced by making good use of the high-frequency first orifice passage 68 formed by extending the inside of the partition member 46 in the diameter direction. At the outer peripheral portion of the separated partition member 46, a communication small hole 120 for directly connecting the high-frequency first orifice passage 68 to the balancing chamber 62 is formed in a simple linear hole shape extending in the axial direction. The high-frequency first orifice passage 68 and the high-frequency second orifice passage 70 are formed to intersect with each other, and the low-frequency orifice passage 66 and the low-frequency orifice passage 66 Since the first and second orifice passages 68 and 70 and the communication small hole 120 for high frequency are advantageously formed with a compact and simple structure. That.
[0050]
Further, in the engine mount 10, the first rubber film 76 is provided on the lower surface side of the partition member 46, and the second rubber film 82 is provided on the upper surface side of the partition member 46. Therefore, the thickness and the area (free length) of the first and second rubber films 76 and 82 can be advantageously secured without increasing the size of the partition member 46, etc. Compatibility of compactness can be advantageously achieved.
[0051]
The embodiments of the present invention have been described in detail above, but these are merely examples, and the present invention is not to be construed as being limited by specific descriptions in the embodiments.
[0052]
For example, the orifice passage 66 for low frequency, the first and second orifice passages 68 and 70 for high frequency, and the communication small hole 120 have a shape including a length, a cross-sectional area, and the like according to required vibration isolation characteristics. The structure and the structure are changed as appropriate, and the present invention is not limited to the above embodiment.
[0053]
Further, the high frequency second orifice passage 70, the second rubber film 76, and the like are all adopted according to the anti-vibration characteristics required for the mount, and are not necessarily provided.
[0054]
Furthermore, even when the high-frequency second orifice passage 70 is provided, the high-frequency first orifice passage 68 and the high-frequency second orifice passage 70 do not necessarily need to be selectively communicated with each other. Of the second rubber film 76 to such an extent that the fluid flow rate through the first orifice passage 68 for high frequency or the small hole 120 does not adversely affect the fluidity under the communication state of the first orifice passage 68 for high frequency. In the case where it is sufficiently limited, the high-frequency second orifice passage 70 can be always in a communicating state.
[0055]
Further, in the above-described embodiment, the first mounting member 12 and the second mounting member 14 are separated from each other in one direction of the vibration input direction to be opposed to each other, and the main rubber elastic body 16 is interposed between the opposed surfaces. A specific example of the present invention applied to a vibration isolator having a mounted structure has been described. A fluid-filled cylindrical mount suitable for use in engine mounts for FF-type automobiles, having a structure in which the outer cylindrical members are elastically connected by a main rubber elastic body interposed between their radially opposed surfaces. Is also applicable.
[0056]
In addition, in the above-described embodiment, a specific example in which the present invention is applied to an engine mount for a vehicle has been described.In addition, the present invention relates to a body mount or a differential mount for a vehicle, or various devices other than a vehicle. Of course, any of them can be similarly applied to the vibration isolator.
[0057]
In addition, although not enumerated one by one, the present invention can be embodied in modes in which various changes, modifications, improvements, and the like are made based on the knowledge of those skilled in the art. It goes without saying that any of them is included in the scope of the present invention unless departing from the spirit of the present invention.
[0058]
【The invention's effect】
As is clear from the above description, in the fluid filled type vibration damping device having the structure according to the present invention, the high frequency first orifice passage is bypassed to the equilibrium chamber under the communication state of the high frequency first orifice passage. The communication state of the high-frequency first orifice passage is adjusted by the low-frequency orifice passage tuned so as to exhibit a specific vibration-proof effect when the high-frequency first orifice passage is shut off. In addition, different vibration damping effects can be obtained below, and by adjusting the size of the communication small holes, the vibration damping exerted by the low frequency orifice passage under the communication state of the high frequency first orifice passage. The tuning is performed independently of the vibration isolation characteristics exhibited by the low-frequency orifice passage when the first high-frequency orifice passage is shut off. Rukoto is possible.
[0059]
In other words, in such a fluid-filled type vibration damping device, one low-frequency orifice passage can be used as substantially two orifice passages that are differently tuned and function alternatively. Therefore, a fluid-filled type vibration damping device capable of switching vibration damping characteristics according to a change in input vibration or the like can be advantageously realized with a simple and compact structure.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view showing an automobile engine mount as one embodiment of the present invention, and is a view corresponding to a II section in FIG.
FIG. 2 is a sectional view taken along line II-II in FIG.
FIG. 3 is a sectional view taken along line III-III in FIG.
FIG. 4 is a sectional view taken along line IV-IV in FIG. 1;
[Explanation of symbols]
10 Engine mount
12 First mounting bracket
14 Second mounting bracket
16 Rubber elastic body
46 Partition member
48 Diaphragm
60 pressure receiving chamber
62 Equilibrium chamber
66 Low frequency orifice passage
68 High frequency first orifice passage
70 High frequency second orifice passage
76 Second rubber film
82 First rubber film
102 Rotary valve body
120 communication hole

Claims (6)

Part of the wall is composed of the main rubber elastic body that is elastically deformed by the input vibration, and the pressure receiving chamber to which the vibration is input and part of the wall is composed of the easily deformable flexible film, and the volume change is made. An allowable equilibrium chamber is formed, an incompressible fluid is sealed in the pressure receiving chamber and the equilibrium chamber, and a low-frequency orifice passage and a high-frequency first orifice passage that mutually communicate the pressure-receiving chamber and the equilibrium chamber, respectively. A fluid-filled vibration isolator provided with first valve means for switching the high-frequency first orifice passage between a communicating state and a blocking state.
First flow rate limiting means for limiting the amount of fluid flowing through the high frequency first orifice passage is provided at a position closer to the equilibrium chamber than the first valve means. A communication hole is provided for directly connecting the region between the first valve means and the first flow rate restricting means to the equilibrium chamber, and a hard partition member for dividing the pressure receiving chamber and the equilibrium chamber is provided. Forming, on the partition member, an internal passage extending linearly in a direction substantially perpendicular to the direction in which the pressure receiving chamber and the equilibrium chamber face each other, and bending one end of the internal passage toward the pressure receiving chamber. Along with opening, the other end is bent toward the equilibrium chamber side to open, thereby forming the first high-frequency orifice passage, and disposing the first valve means on the internal passage. , The internal passage The end on the equilibrium chamber side of the first valve means is further linearly extended beyond the bending point toward the equilibrium chamber, and the extended portion and the equilibrium chamber are connected to the communication small hole. A fluid-filled type vibration damping device, characterized in that the fluid communication is directly performed by the fluid. The fluid filled type vibration damping device according to claim 1, wherein the communication small hole is formed with a smaller flow path cross-sectional area and a smaller flow path length than any of the low-frequency orifice passage and the high-frequency first orifice passage. . A high-frequency second orifice passage communicating the pressure receiving chamber and the equilibrium chamber with each other is provided, and the high-frequency second orifice passage is tuned to a higher frequency range than the high-frequency first orifice passage. A second flow rate restricting means for restricting a fluid flow amount through the second orifice passage, and a second valve means for switching the high frequency second orifice passage between a communicating state and a cutoff state, and fluid-filled vibration damping device according to claim 1 or 2 as alternatively allowed to communicate with the second orifice passage with the first orifice passage for the high frequency. 4. The fluid filled type vibration damping device according to claim 3 , wherein the second flow rate restricting means is located on the high pressure second orifice passage closer to the pressure receiving chamber than the second valve means. The first flow rate restricting means is displaceably disposed at an opening of the high frequency first orifice passage toward the equilibrium chamber, and the amount of displacement is limited, whereby the high frequency first orifice passage is restricted. And a movable member that restricts the amount of fluid flowing through the high-frequency second orifice passage to the opening of the high-frequency second orifice passage toward the equilibrium chamber. The fluid filled type vibration damping device according to claim 3 or 4 , wherein the two orifices for the high frequency second orifice passage are disposed so as to integrally cover both openings. The first mounting member and the second mounting member which are arranged apart from each other in the vibration input direction are connected by the main rubber elastic body, and the first mounting member and the second mounting member are arranged on one side with the partition member supported by the second mounting member interposed therebetween. While forming the pressure receiving chamber, while forming the equilibrium chamber on the other side, in the partition member, the low-frequency orifice passage is formed so that the outer peripheral portion of the partition member extends in the circumferential direction, The high-frequency first orifice passage is formed in a direction substantially orthogonal to the direction in which the pressure receiving chamber and the balancing chamber face each other, and the high-frequency second orifice passage is linearly formed in the direction in which the pressure receiving chamber and the balancing chamber face each other. The first orifice passage for high frequency is formed at a crossing point between the first orifice passage for high frequency and the second orifice passage for high frequency. Fluid-filled vibration damping device according to any one of claims 3 to 5 constitute a office passage and said first and second valve means by alternatively communicating allowed to valve means of the second orifice passage for high frequency.

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