JPH11344071A - Vibration control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To satisfactorily reduce vibrations of mutually different frequencies at three stages as a three-mode changeover structure. SOLUTION: An intermediate cylinder 22 and intermediate block 24 are installed inside an outer cylinder metal piece 16, and the space bounded by the intermediate block 24 and an elastic member constitutes a main liquid chamber 30, which is put in communication with the first aux. liquid chamber 32 via a shake orifice 64, low idle orifice, and high idle orifice. The main liquid chamber 30 is put in communication with the second aux. liquid chamber 96 via a filling orifice 62, and a rotor 36 opens and closes the low idle orifice, high idle orifice, and filling orifice 62.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration isolator for preventing transmission of vibration from a member that generates vibration, and is applicable to, for example, a case where transmission of vibration from an engine mounted on a vehicle is prevented. Things.

[0002]

2. Description of the Related Art For example, an anti-vibration device as an engine mount is disposed between an engine of a vehicle serving as a vibration generating portion and a vehicle body serving as a vibration receiving portion. There is known a structure that absorbs vibration and prevents vibration from being transmitted to the vehicle body.

That is, as an example of the vibration isolator, not only is an inner cylinder disposed inside a cylindrical outer cylinder, but also a main liquid chamber and a sub liquid chamber are provided inside the outer cylinder. There is a bush type in which these liquid chambers communicate with each other through a restriction passage serving as an orifice.

When the mounted engine operates and generates vibration, the vibration is absorbed or attenuated as a low dynamic spring due to the liquid column resonance of the liquid in the restriction passage communicating with these liquid chambers. To prevent the transmission of vibration.

[0005] On the other hand, the engine speed varies widely with changes in vehicle conditions, and the vibration frequency becomes wide with a wide operating state of the engine. Therefore, in order to maintain the vibration isolating characteristics even in such vibrations of a wide range of frequencies, recently, a vibration isolating device having an orifice which is a restriction passage having different lengths and inner diameters has been devised in recent years. Was.

Further, these conventional vibration damping devices are generally provided with one orifice each corresponding to each vehicle state, and are provided between an idling mode and a running mode in which a middle-to-low speed muffled sound is generated. The orifice can be switched by the rotor.

That is, the openings of the rotor serving as switching valves are arranged so as to be able to face one end of each orifice, and these orifices are opened and closed by rotating the rotor. At this time, considering each orifice, each orifice was a simple repetition of an open state and a closed state.

[0008]

On the other hand, as a recent trend in the design concept of vehicles such as automobiles, there is a tendency to set the engine speed at idling to a lower speed. For this reason, compared to the conventional idle vibration, a portion of the vibration frequency closer to a lower frequency during the idle vibration shifts to a lower frequency side.

As a result, the region of the anti-resonance where the dynamic spring constant is the highest overlaps with the region of the high idle vibration which is a high frequency component in the idle vibration, and it is difficult to sufficiently reduce the high idle vibration. Had become.

In other words, the conventional vibration damping device having a two-mode switching structure cannot sufficiently reduce vibrations in a wide range of frequencies.

The present invention has been made in view of the above-described circumstances, and has as its object to provide an anti-vibration device capable of sufficiently reducing vibrations of three different frequencies as a three-mode switching structure.

[0012]

According to a first aspect of the present invention, there is provided a vibration isolator which is connected to one of a vibration generator and a vibration receiver, and connected to the other of the vibration generator and the vibration receiver. A second mounting member, an elastic body disposed between the mounting members and elastically deformable, and a main liquid chamber in which a liquid is sealed with the elastic body as a part of the partition wall and the inner volume is changed by deformation of the elastic body. A sub-liquid chamber in which a liquid is sealed and at least a part of a partition wall is formed so as to be elastically deformable, and three orifices capable of reducing vibration by communicating between the main liquid chamber and the sub-liquid chamber, respectively; It is characterized by having a valve capable of reducing vibrations of three different frequencies by selectively opening and closing these three orifices, respectively, and an actuator connected to the valve to operate the valve. I do.

According to a second aspect of the present invention, there is provided a vibration isolator, wherein a first mounting member is connected to one of the engine and the vehicle body, a second mounting member is connected to the other of the engine and the vehicle body, and the first mounting member is disposed between the mounting members. An elastic body that can be elastically deformed by being deformed, a main liquid chamber in which the liquid is sealed with the elastic body as a part of the partition and the internal volume changes due to the deformation of the elastic body, and a liquid is sealed and at least a part of the partition is elastic. A sub-liquid chamber formed so as to be deformable, three orifices communicating with the main liquid chamber and the sub-liquid chamber respectively to reduce vibration, and selectively opening and closing these three orifices to each other. It is characterized by having a valve capable of reducing low idle vibration, high idle vibration, and vibration during traveling, each having a different frequency, and an actuator connected to the valve to operate the valve.

The operation of the vibration isolator according to the first aspect will be described below.

When vibration in a low frequency range is transmitted from the vibration generating portion connected to either the first mounting member or the second mounting member, the elastic body is deformed and the vibration is attenuated by the elastic body. You.

Further, the inner volume of the main liquid chamber changes due to the deformation of the elastic body. At this time, at least one of the three orifices connecting the main liquid chamber and the sub liquid chamber is closed by a valve. In this state, the liquid does not flow into the closed orifice, and the liquid actively flows toward the sub liquid chamber by the opened orifice. As a result, a pressure change occurs in the liquid in the opened orifice, and accordingly, the partition wall of the sub-liquid chamber formed so as to be elastically deformable.

That is, when the vibration in the low frequency range is transmitted from the vibration generating section side, the dynamic spring constant is established not only by the elastic body but also by the orifice opened between the main liquid chamber and the sub liquid chamber and opened by the valve. Is reduced, the vibration in the low frequency range is absorbed, and it becomes difficult to transmit the vibration to the vibration receiving portion side.

On the other hand, the frequency of vibration changes, and in the above-mentioned open orifice, vibration in a medium frequency range where vibration cannot be reduced is connected to either the first mounting member or the second mounting member. Even when the vibration is transmitted from the vibration generating unit side, the internal volume of the main liquid chamber changes due to the deformation of the elastic body as described above.

At this time, the actuator operates the valve in accordance with the frequency of the vibration to open another orifice connecting between the main liquid chamber and the sub liquid chamber, so that the internal volume of the main liquid chamber is reduced. The pressure in the liquid in the newly opened orifice changes due to the change in the pressure, and the partition of the sub-liquid chamber that is formed to be elastically deformable is deformed accordingly.

As a result, even when vibration in a medium frequency range is transmitted from the vibration generating section side, the dynamic spring constant is reduced by the orifice opened by the valve in the same manner as described above, and the dynamic spring constant is reduced. Vibration is absorbed, and it becomes difficult for the vibration to be transmitted to the vibration receiving unit side.

Further, even if the frequency of vibration changes, and vibration in a high frequency range that cannot be reduced by the above-mentioned open orifice is transmitted from the vibration generating section, the elastic body is deformed in the same manner as described above. When the actuator operates the valve to open another orifice, the orifice reduces the dynamic spring constant, absorbs the vibration in the high frequency range, and transmits the vibration to the vibration receiving part. It is hard to be done.

That is, by selectively opening and closing three orifices which can communicate with each other between the main liquid chamber and the sub liquid chamber to reduce vibration, the three orifices actuated by the actuator selectively form three orifices different from each other. The vibration of the frequency can be respectively reduced.

As a result, vibration is appropriately absorbed at any vibration frequency, and a wide range of vibration can be reduced.

The operation of the vibration isolator according to claim 2 will be described below.

The present invention has the same effect as the first embodiment. However, in the present invention, low idle vibration, high idle vibration, and vibration during traveling can be reduced by selectively opening and closing the three orifices by valves operated by the actuator. I did it.

That is, when the vibration generating section is the engine and the vibration receiving section is the vehicle body, the actuator operates the valve to selectively open and close the three orifices, thereby reducing the low frequency generated during idling. It is possible to reduce the low idle vibration that is the vibration in the frequency range and the high idle vibration that is the vibration in the medium frequency range.
Further, the actuator operates the valve to selectively open and close the three orifices, so that vibration during traveling, which is vibration in a high frequency range, can be reduced.

[0027]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of a vibration isolator according to the present invention is shown in FIGS. 1 to 5, and this embodiment will be described with reference to these drawings.

As shown in FIGS. 1 and 2, the so-called bush type vibration damping device 10 is provided with a mounting frame 12 formed in a ring shape for connection to a vehicle body (not shown). 12 has a cylindrical outer tube fitting 1
6 are fitted and arranged. The outer peripheral portion of the rubber-made thin first diaphragm 20 is vulcanized and bonded to the metal bracket 14, and this first diaphragm 20 is closer to the upper side in FIGS. 1 and 2 on the inner peripheral surface side of the outer cylinder fitting 16. Are located. As shown in FIGS. 1 and 2, an air chamber 31 is provided between the first diaphragm 20 and the outer cylindrical member 16.
And communicate with the outside if necessary.

An intermediate cylinder 22 and an intermediate block 24 are inserted into the outer cylinder fitting 16, and the intermediate cylinder 22 and the intermediate block 24 constitute a partition member.

The intermediate block 24 is formed in a substantially semicircular block shape when viewed from the axial direction of the outer cylinder 16, and the outer peripheral surface of the intermediate block 24 is formed inside the outer cylinder 16 as shown in FIG. It is in close contact with the peripheral surface. As shown in FIG. 2, flange portions 22 </ b> A are provided at both axial ends of the intermediate cylinder 22.
Are formed, and the intermediate block 24 is fitted between the pair of flange portions 22A. The outer peripheral surfaces of the pair of flange portions 22 </ b> A are in close contact with the inner peripheral surface of the outer cylinder fitting 16.

As shown in FIGS. 1 and 2, the portion of the intermediate cylinder 22 facing the flat portion 24B which is the upper surface of the intermediate block 24 is hollow, and the inside of this hollow is connected to an engine (not shown). The tube fitting 26 penetrates. This inner tube fitting 26 is arranged in parallel with the outer tube fitting 16,
An elastic body 28 made of a rubber material or the like is stretched between the first and second elastic members. As a result, the inner cylindrical member 26 can be moved relative to the outer cylindrical member 16.

That is, the inner cylinder fitting 26 connected to the engine, which is a vibration generating section, is a first mounting member, and the outer cylinder fitting 16 connected to the vehicle body, which is a vibration receiving section, via the mounting frame 12 is the first mounting member. 2 mounting member.

Further, the elastic body 28 also extends on the outer peripheral surface between the flange portions 22A of the intermediate cylinder 22, and protrudes from both ends of the intermediate block 24 on the inner peripheral side of the arc-shaped portion. A part of the elastic body 28 is in close contact with the inner circumferential arc surface 24A. A notch 28A is formed in the middle of the elastic body 28 and below the inner cylindrical fitting 26,
The space between the notch 28A and the intermediate block 24 is the main liquid chamber 30.

On the other hand, a pair of flange portions 22 of the intermediate cylinder 22
Between A, a first sub liquid chamber 32 surrounded by the intermediate cylinder 22 and the first diaphragm 20 is formed. Also,
As shown in FIG. 5, the outer peripheral surface of the intermediate block 24
A groove 46 is formed in a letter shape. One end of the groove 46 opens to the right end of the intermediate block 24 in FIG. 1 and is connected to the first auxiliary liquid chamber 32. This groove 46
The other end is communicated with the main liquid chamber 30 through a through hole 48 formed through the inside of the intermediate block 24. The groove 46 and the through hole 48 form a shake orifice 64 as a restriction passage for absorbing shake vibration.

A circular hole 34 is formed on the plane portion 24B side of the intermediate block 24, and a circular hole 3 is formed at the bottom of the circular hole 34.
A circular through hole 35 having a smaller diameter than that of the circular hole 4 and penetrating the outer peripheral surface of the intermediate block 24 is formed coaxially with the circular hole 34. A counterbore 39 is provided coaxially with the circular through-hole 35 on the side of the outer tube fitting 16 of the intermediate block 24, and an O-ring 41 for sealing is fitted outside the counterbore 39. I have.

In the circular hole 34 and the circular through hole 35,
A rotor 36 as a valve is rotatably inserted.
The main liquid chamber 30 side of the rotor 36 has a cylindrical cylindrical portion 36A.
On the opposite side of the cylindrical portion 36A, a thin shaft portion 36B as a rotating shaft is integrally provided. Further, a lid plate 40 also serving as a washer is fixed to the plane portion 24B side of the intermediate block 24 to prevent the rotor 36 from coming off.

A pair of O-rings 44 are fitted around the outer periphery of the thin shaft portion 36B. Therefore, this O
The liquid does not leak out of the intermediate block 24 through the circular through hole 35 by the ring 44.

Further, the cylindrical portion 36A of the rotor 36 has
A through-hole 38 communicating the inside and outside of the cylindrical portion 36A is formed. On the other hand, a passage 56 and a passage 66 are formed in the intermediate block 24 so that one end side is connected to the circular hole 34 and extends in a direction perpendicular to the plane of FIG. That is, these passages 56
One end of the passage 66 is opened at the inner periphery of the circular hole 34.

As shown in FIG. 4 and FIG.
Is connected to one end of a passage 58 which is a groove formed in the outer periphery of the intermediate block 24 along the circumferential direction. The other end of the passage 58 is connected to the first auxiliary liquid chamber 32. . Accordingly, when the rotor 36 rotates and the through hole 38 faces the passage 56 as shown in FIG. 3C, the passages 56 and 58 establish a connection between the main liquid chamber 30 and the first sub liquid chamber 32. Will be communicated.

In other words, the passages 56 and 58 communicate the main liquid chamber 30 and the first sub-liquid chamber 32 to form a restriction passage for absorbing low idle vibration, which is a low frequency side vibration among idle vibrations. A low idle orifice 60 is constructed.

As shown in FIG. 4 and FIG.
The other end of the passage 6 communicates with one end of a passage 68 which is a groove formed along the circumferential direction on the outer periphery of the intermediate block 24 in the same manner as described above. Has been communicated with. Accordingly, the rotor 36 rotates, and FIG.
As shown in (A), when the through hole 38 faces the passage 66, the passage 6 between the main liquid chamber 30 and the first sub liquid chamber 32 passes.
6, 68 will communicate.

That is, the main liquid chamber 30 and the first sub liquid chamber 32 communicate with each other through the passages 66 and 68 to form a restriction passage for absorbing a high idle vibration which is a vibration on the high frequency side among the idle vibrations. A high idle orifice 61 is constructed.

On the other hand, as shown in FIG.
4 further includes a passage 5 along the radial direction of the circular hole 34 and
A hole 92 is formed in the direction opposite to the direction 6 or 58. A second sub-liquid chamber 96 which is an arc-shaped space is formed in a portion of the intermediate block 24 corresponding to the opening end of the hole 92, and the end of the hole 92 is formed in a second shape. The second sub liquid chamber 96 is open. Therefore, when the rotor 36 rotates and the through-hole 38 faces the hole 92 for stagnation as shown in FIG. 1 and FIG.
The communication between the zero and the second sub liquid chamber 96 is established.

That is, the squeezing hole 92 connects the main liquid chamber 30 and the second sub-liquid chamber 96 to restrict passage for absorbing medium to low-speed muffled sound which is higher in frequency than idle vibration. The orifice 62 for retraction is formed.

A thin rubber-made second diaphragm 94 is provided on the outer peripheral side of the intermediate block 24 with respect to the second sub-liquid chamber 96, and the outer peripheral portion is formed between the outer cylinder fitting 16 and the intermediate block 24. The second diaphragm 94 is sandwiched between them, and serves as an elastically deformable partition wall of the second sub liquid chamber 96.

For this reason, the space between the second diaphragm 94 and the inner peripheral surface side of the outer tube fitting 16 is a second air chamber 98 which is built in the outer tube fitting 16 and in which gas is sealed. The second air chamber 98 allows the second diaphragm 94 to be deformed.

That is, the second diaphragm 94 constitutes a part of the partition wall of the second sub liquid chamber 96. As shown in FIG. 1, the area of the second diaphragm 94 is equal to the first sub liquid chamber. The first diaphragm 20 which constitutes a part of the partition wall 32
Is smaller than the area of the second diaphragm 9.
4 has higher rigidity than the first diaphragm 20.

The main liquid chamber 30, the first sub liquid chamber 32, and the second sub liquid chamber 96 are sealed so as to be filled with a liquid such as ethylene glycol.

On the other hand, a motor 70 as an actuator is provided outside the mounting frame 12. The tip of the rotating shaft 71 of the motor 70 is fitted to the tip of the thin shaft portion 36B of the rotor 36. The motor 70 is provided with a flange portion 70B, and the flange portion 70B is formed in an arc shape along the outer diameter of the mounting frame 12. Therefore, the motor 70 is fixed to the mounting frame 12 by screwing a screw (not shown) inserted through the flange portion 70B into a screw portion (not shown) provided on the mounting frame 12.

With the structure described above, when the rotor 36 is rotated and the through hole 38 of the cylindrical portion 36A opens the high idle orifice 61 as shown in FIG. The main liquid chamber 30 communicates with the first sub liquid chamber 32. Further, the rotor 36 is rotated 120 ° from this position, and as shown in FIG.
When the through-hole 38 of the cylindrical portion 36A opens the orifice 62, the main liquid chamber 3 is opened via the orifice 62.
0 and the second sub liquid chamber 96 are communicated. Further, when the rotor 36 is rotated 120 ° from this position and the through hole 38 of the cylindrical portion 36A opens the low idle orifice 60 as shown in FIG. 30 and the first sub liquid chamber 32 are communicated.

From this position, the rotor 36 is moved to 120
When rotated, the high idle orifice 61 is opened again as described above, and the orifices are sequentially opened in the same manner as described above.

Therefore, low idle vibration, which is vibration in a low frequency range, high idle vibration, which is vibration in a medium frequency range, and vibration during traveling, which is vibration in a high frequency range, can be reduced. The orifices are switched by the rotor 36 opening and closing the orifices 60, 61, 62.

As described above, the rotor 36 is connected to the main liquid chamber 30 and the first sub liquid chamber 32 through the high idle orifice 61 or the low idle orifice 60 as shown in FIGS. And the arrangement that communicates between
As shown in FIG.
It is rotated by the motor 70 so as to selectively adopt an arrangement for communicating between the zero and the second sub liquid chamber 96.

The motor 70 is connected to a controller 72 as control means, and the rotation of the motor 70 is controlled by the controller 72. Controller 7
2 is operated by a vehicle power supply and has at least a vehicle speed sensor 7
4 and the detection signal from the engine speed detection sensor 76, the vehicle speed and the engine speed are detected, and it is possible to determine whether the idle vibration or the shake vibration is generated, and the generated idle vibration is the low idle vibration. Or high idle vibration.

Next, the operation of the present embodiment will be described.

When the engine mounted on the inner cylinder 26 operates, the vibration of the engine is transmitted to the elastic body 28 via the inner cylinder 26. The elastic body 28 acts as a vibration absorbing main body, and can absorb vibration by a vibration damping function based on internal friction of the elastic body 28.

Further, the liquids in the main liquid chamber 30 and the first sub liquid chamber 32 whose inner volumes change with the deformation of the elastic body 28 and the first diaphragm 20 are displaced by the shake orifices 64,
The main liquid chamber 30 and the second sub liquid chamber 96 which flow mutually via the high idle orifice 61 or the low idle orifice 60 and whose inner volumes change with the deformation of the elastic body 28 and the second diaphragm 94. The liquid inside flows through the orifice 62 for stagnation, and the damping action based on the viscous resistance of the liquid flow generated in the orifice space and the resonance of the liquid column can improve the vibration isolation effect.

In addition to the normally open shake orifice 64, a low idle orifice 60, a high idle orifice 61 and an orifice 62 are provided. These low idle orifice 60, high idle orifice 61 and orifice 62 are provided. As a result of the provision of the rotor 36 for switching the passage between the first and second passages, the following operation is performed.

When the vehicle runs at a high speed of, for example, 70 to 80 km / h or more, shake vibration (about 10 Hz) occurs. The controller 72 determines whether or not a shake vibration has occurred based on a vehicle speed sensor 74 and an engine speed detection sensor 76. When the controller 72 determines that the shake vibration is occurring, the controller 72 operates the motor 70 to rotate the rotor 36, and as shown in FIG. 3B, associates the through hole 38 with the squeezing orifice 62, The low idle orifice 60 and the high idle orifice 61 are arranged so as not to correspond to each other.

Thus, the low idle orifice 60
Is closed and always open shake orifice 6
4 communicates between the main liquid chamber 30 and the first sub liquid chamber 32, and the orifice 62 for confining communicates between the main liquid chamber 30 and the second sub liquid chamber 96.

As a result, the pressure change based on the engine vibration generated in the main liquid chamber 30 is transmitted to the liquid in the shake orifice 64 and the orifice 62, and the vibration of the shake is absorbed by the resistance of the liquid.

Furthermore, a medium-to-low-speed muffled sound (80 m), which is a high-frequency, small-amplitude vibration that may occur together with shake vibration
(About Hz), the liquid column resonates in the muffled orifice 62 and the dynamic spring constant is reduced, and muffled sound is absorbed.

When the engine is idling or the vehicle speed is 5 km / h or less, low idle vibration (about 25 Hz) occurs. The controller 72 uses the vehicle speed sensor 74 and the engine speed detection sensor 76 to not only determine whether or not idle vibration occurs, but also determine whether the generated idle vibration is low idle vibration or high idle vibration.

When the controller 72 determines that idle vibration has occurred and determines that low idle vibration has occurred, the controller 72 causes the motor 70 to rotate, and FIG.
As shown in (C), the through hole 38 of the rotor 36 is made to correspond to the low idle orifice 60, and is arranged so as not to correspond to the high idle orifice 61 and the orifice 62 for stagnation.

As a result, the high idle orifice 61
The orifice 62 is closed, and the liquid having a small inner diameter moves back and forth between the main liquid chamber 30 and the first sub liquid chamber 32 through the low idle orifice 60 having a large passage resistance. The liquid column resonates and the dynamic spring constant decreases, and low idle vibration is absorbed.

On the other hand, if high idle vibration (about 45 Hz) occurs among idle vibrations, the controller 7
2 not only determines whether or not idle vibration has occurred by the vehicle speed sensor 74 and the engine speed detection sensor 76, but also
It is determined whether the generated idle vibration is low idle vibration or high idle vibration.

When the controller 72 determines that idle vibration has occurred and determines that high idle vibration has occurred, the controller 72 rotates the motor 70, and FIG.
As shown in (A), the through hole 38 of the rotor 36 is made to correspond to the high idle orifice 61, and is arranged so as not to correspond to the low idle orifice 60 and the orifice 62.

As a result, the low idle orifice 60
The orifice 62 is closed, and the liquid flows between the main liquid chamber 30 and the first sub liquid chamber 32 via the high idle orifice 61 having a large inner diameter and a small passage resistance. The dynamic spring constant decreases due to the liquid column resonance, and the high idle vibration is absorbed.

That is, the three orifices 60, 61, and 62, which can communicate with each other between the main liquid chamber 30 and the sub liquid chambers 32 and 96 to reduce vibration, are selectively provided by the rotor 36 operated by the motor 70. By opening and closing, vibrations at three different frequencies can be reduced.

As a result, vibration is appropriately absorbed at any vibration frequency, and a wide range of vibration can be reduced.

Next, a second embodiment of the vibration isolator according to the present invention is shown in FIGS. 6 to 8, and this embodiment will be described with reference to these drawings. The same members as those described in the first embodiment are denoted by the same reference numerals, and redundant description will be omitted.

As shown in FIGS. 6 to 8, this embodiment has a structure in which one orifice that is opened and closed by the through hole 38 of the rotor 36 is further added to the intermediate block 24. In other words, the low idle orifices 60 are disposed so as to face the orifice 62 and the rotor 36 with the rotor 36 interposed therebetween, and are located at a position orthogonal to the position where the orifice 62 is opened in the circular hole 34 and opposed to each other across the rotor 36. And a pair of high-idle orifices 61 are arranged.

The pair of high idle orifices 61 are also communicated with the first auxiliary liquid chamber 32, respectively.
The pair of high idle orifices 61 have the same inner diameter and length.

As a result, in the present embodiment, two high idle orifices 61 in the transient state are provided, and one high idle orifice 61 is arranged between the low idle orifice 60 and the orifice 62 for collecting. Becomes

As described above, the present embodiment can also obtain the same characteristics as the first embodiment. Further, in the present embodiment, (A), (B), and (B) of FIG.
By rotating the rotor 36 by 90 ° in the order of (C) and (D), each orifice is sequentially opened. At this time, the high idle orifice 61 is opened twice while the rotor 36 makes one rotation. Will be.

That is, when simply increasing the number of orifices and moving the rotor 36 in one-to-one correspondence with the frequency of vibration, it is also expected that the response speed will deteriorate when switching from one mode to another mode. But the rotor 3
The orifice can be switched at every 90 ° rotation of No. 6 to increase the response speed.

Next, a third embodiment of the vibration isolator according to the present invention is shown in FIG. 9, and this embodiment will be described with reference to these drawings. The same members as those described in the first embodiment are denoted by the same reference numerals, and redundant description will be omitted.

As shown in FIG. 9, in this embodiment, the number of orifices opened and closed by the through holes 38 of the rotor 36 is the same as that of the first embodiment. By increasing the inner diameter of the facing portion, the liquid reservoir 60 is provided at one end of the low idle orifice 60.
A was formed. Further, one end of the high idle orifice 61 and one end of the orifice 62 for refilling are respectively provided with circular holes 34.
And are formed so as to extend in parallel with each other. Then, a through hole 38 which is an opening of the rotor 36 is provided.
Are provided on the rotor 36, large and small.

Therefore, at the time of the low idle vibration, FIG.
As shown in FIG. 9 (B), a single orifice having only the low idle orifice 60 is provided,
As shown in (5), the high idle orifice 61 is further opened to form a double orifice while rotating the rotor 36 by 90 ° and keeping the low idle orifice 60 open.

Further, in the running state, as shown in FIG. 9C, the rotor 36 is rotated by 90 ° to close the two orifices, and the orifice 62 is opened.
Thereafter, as shown in FIG.
Rotate and arrange for high idle vibration.

That is, in this embodiment, since the liquid reservoir 60A is formed at one end of the low idle orifice 60, it is possible to use a double orifice.

In the above embodiment, the outer cylinder fitting 16 is attached to the vehicle body and the inner cylinder fitting 26 is attached to the engine. However, the reverse construction may be adopted. Although two sub liquid chambers and the second sub liquid chamber are provided, one sub liquid chamber may be used.

On the other hand, in the above-described embodiment, the purpose is to dampen the engine mounted on the vehicle. Needless to say, the damping device of the present invention can be used for other purposes.
Further, the shape and the like are not limited to those of the embodiment.

On the other hand, in the above embodiment, the rotor is rotated by the motor. However, the present invention is not limited to this, and the actuator for rotating the rotor may be other than the motor. Other valves or the like may be used.

[0085]

As described above, the anti-vibration device of the present invention has a configuration as described above, and as a three-mode switching structure, it is possible to sufficiently reduce vibrations at three different frequencies. .

[Brief description of the drawings]

FIG. 1 is a sectional view showing a first embodiment of a vibration isolator according to the present invention.

FIG. 2 is a view taken in the direction of arrow 2-2 in FIG. 1;

FIG. 3 is a diagram showing a relationship between a through hole of a rotor and an orifice of the first embodiment of the vibration isolator according to the present invention,
(A) shows a state in which the high idle orifice is opened, (B) shows a state in which the orifice for housekeeping is opened, and (C) shows a state in which the low idle orifice is opened.

FIG. 4 is a perspective view of an intermediate block applied to the first embodiment of the vibration isolator according to the present invention.

5A and 5B are diagrams showing an intermediate block applied to the first embodiment of the vibration isolator according to the present invention, wherein FIG. 5A is a left side view, FIG. 5B is a bottom view, (C) is a right side view.

FIG. 6 is a cross-sectional view showing a second embodiment of the vibration isolator according to the present invention.

FIG. 7 is a view taken in the direction of arrow 7-7 in FIG. 6;

FIG. 8 is a view showing a relationship between a through hole of a rotor and an orifice in a second embodiment of the vibration isolator according to the present invention,
(A) shows a state in which the low idle orifice is opened, (B) shows a state in which the high idle orifice is opened, (C) shows a state in which the orifice for confining is opened, and (D) shows a state in which the orifice for boom-in is opened. This shows a state where the idle orifice is opened.

FIG. 9 is a view showing a relationship between a through hole of a rotor and an orifice in a third embodiment of the vibration isolator according to the present invention,
(A) shows a state in which the low idle orifice is opened, (B) shows a state in which the low idle orifice and the high idle orifice are opened, (C) shows a state in which the orifice for the dead end is opened, D) shows a state where the high idle orifice and the low idle orifice are opened.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Vibration isolator 16 Outer cylinder fitting 26 Inner cylinder fitting 28 Elastic body 30 Main liquid chamber 32 First sub liquid chamber 36 Rotor 60 Low idle orifice 61 High idle orifice 62 Orifice for stagnation 70 Motor 96 Second sub liquid chamber

Claims (2)

[Claims] A first mounting member connected to one of the vibration generating section and the vibration receiving section; a second mounting member connected to the other of the vibration generating section and the vibration receiving section; An elastic body that is disposed and elastically deformable; a main liquid chamber in which the liquid is sealed using the elastic body as a part of the partition wall and whose internal volume changes due to the deformation of the elastic body; A sub-liquid chamber formed so as to be elastically deformable, three orifices communicating with the main liquid chamber and the sub-liquid chamber, respectively, to reduce vibration, and selectively opening and closing these three orifices. A vibration isolator comprising: a valve configured to reduce vibrations at three different frequencies; and an actuator connected to the valve to operate the valve. 2. A first mounting member connected to one of the engine and the vehicle body, a second mounting member connected to the other of the engine and the vehicle body, and an elastic member disposed between the mounting members and capable of elastic deformation. A main liquid chamber in which a liquid is sealed with the elastic body as a part of the partition and the internal volume is changed by deformation of the elastic body; The liquid chamber, three orifices that can communicate with each other between the main liquid chamber and the sub liquid chamber to reduce vibration, and selectively open and close these three orifices to produce low idle vibrations having different frequencies from each other. An anti-vibration device comprising: a valve configured to reduce high idle vibration and vibration during traveling; and an actuator connected to the valve to operate the valve.