JP2010025219A - Fluid-filled vibration isolator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid-filled vibration isolator which can obtain a vibration-proof effect effective for the vibration of a wide frequency, and is novel in structure, by making the isolator light in weight and compact in size. <P>SOLUTION: In the vibration isolator, a valve-body side connecting part 130 and a needle-side connecting part 132 are arranged which are oppositely positioned in one axial direction at a valve body 72 and a needle 84, a connecting permanent magnet 134 is arranged which can displace the valve body 72 by displacing the needle-side connecting part 132 in a state that the valve-body side connecting part 130 and the needle-side connecting part 132 are made to abut on each other by a magnetic absorption force, and the valve body 72 can be displaced to and held in the communicative state of an orifice passage 70 by displacing the valve-body side connecting part 130 by utilizing the restoration displacement of the needle 84 by stopping electricity application to a coil 86 after adsorbing the needle-side connecting part 132 to the valve-body side connecting part 130. Furthermore, a shaker 78 can function as an active vibration damper by the effect that the needle 84 including the needle-side connecting part 132 is shaken independently from the valve body 72. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an anti-vibration device that is interposed between members constituting a vibration transmission system and supports the anti-vibration connection or anti-vibration of these members. The present invention relates to a fluid filled type vibration isolator using a vibration effect.

  Conventionally, an anti-vibration device is known as an anti-vibration coupling body or anti-vibration support body that is interposed between members constituting a vibration transmission system and interconnects these members. This anti-vibration device has a structure in which a first attachment fitting attached to one member to be anti-vibration connected and a second attachment fitting attached to the other member are mutually connected by a rubber elastic body. ing. Furthermore, as one type of vibration isolator, a fluid-filled vibration isolator has been proposed in which a pressure receiving chamber and an equilibrium chamber filled with an incompressible fluid are provided, and the pressure receiving chamber and the equilibrium chamber communicate with each other through an orifice passage. For example, application to an engine mount for automobiles is being studied.

  By the way, in the fluid filled type vibration damping device, the vibration damping effect based on the fluid flow action is exhibited against the vibration of the frequency of the orifice passage tuned in advance, while the vibration of the orifice passage is out of the tuning frequency. On the other hand, there is a problem that an effective anti-vibration effect is hardly exhibited. In particular, when vibration having a higher frequency than the tuning of the orifice passage is input, the orifice passage is substantially blocked by an anti-resonant action, and the vibration-proof performance may be significantly reduced.

  Therefore, as one of the means for solving such a problem, an effective anti-vibration effect is exhibited against vibrations of different frequencies by switching the opening of the orifice passage between a communication state and a cutoff state by a valve body. A switching type fluid-filled vibration isolator as described above has also been proposed. As such a switching type fluid-filled vibration isolator, there are generally one that employs a negative pressure type actuator as means for driving a valve body and one that employs an electromagnetic actuator. Patent Document 1 discloses a switching type fluid-filled vibration isolator equipped with a negative pressure actuator, and Patent Document 2 discloses a switching type fluid-filled vibration isolation device equipped with an electromagnetic actuator. The device is shown.

  However, the switching type fluid-filled vibration isolator having the actuator as described above has a problem to be solved. First, when a fluid-filled vibration isolator equipped with a negative pressure actuator is applied to an automobile engine mount, the intake system of the engine is used as a negative pressure source. As a result, it has become difficult to obtain a sufficient negative pressure when the vehicle is stopped. In particular, in an automobile or the like that employs a hybrid system that uses an electric motor and an engine together, it is more difficult to obtain a negative pressure from the intake system of the engine when the vehicle is stopped. As a result, it is difficult to obtain an effective anti-vibration effect against idling vibration, which is a problem when the vehicle is stopped, by switching the orifice passage to a communication state.

  A structure is also conceivable in which the negative pressure is applied to the air chamber during traveling to block the orifice passage, and the atmospheric pressure is applied to the air chamber when the vehicle is stopped to connect the orifice passage. However, in this case, since a negative pressure is exerted on the air chamber in a traveling state having a long use time, stress is exerted on the rubber film constituting the wall portion of the air chamber for a long time, and durability is improved. There is a risk of lowering.

  On the other hand, electromagnetic actuators have a more complicated structure and a larger number of parts than negative pressure actuators. Therefore, there is a problem that a fluid-filled vibration isolator equipped with an electromagnetic actuator is difficult to avoid becoming larger than a fluid-filled vibration isolator equipped with a negative pressure actuator. In particular, in a fluid-filled vibration isolator that does not have a vibration isolating mechanism such as a movable plate against high-frequency vibrations, an active vibration control device may be provided separately in order to obtain a vibration isolating effect against high-frequency vibrations. There is also a possibility that a larger installation space may be required. Moreover, in the electromagnetic actuator, the mass of the actuator is likely to be larger than the negative pressure actuator that uses air pressure due to the structure that obtains the driving force by the electromagnetic force, which may adversely affect the running performance and fuel consumption of the automobile. . Furthermore, in order to maintain the switching state, it is necessary to continue energization of the coil even after the switching operation, and increase in power consumption and heat generation of the coil are likely to be problems.

Japanese Patent No. 3663841 Japanese Patent Laid-Open No. 10-267072

  Here, the present invention has been made in the background as described above, and the problem to be solved is a novel anti-vibration effect that can obtain an effective anti-vibration effect against vibrations of a wider frequency. An object of the present invention is to provide a fluid-filled vibration isolator having a structure that is lightweight and compact.

  Hereinafter, the aspect of this invention made | formed in order to solve such a subject is described. In addition, the component employ | adopted in each aspect as described below is employable by arbitrary combinations as much as possible. Further, aspects or technical features of the present invention are not limited to those described below, but are described in the entire specification and drawings, or an invention that can be understood by those skilled in the art from those descriptions. It should be understood that it is recognized based on thought.

  That is, according to the present invention, the first mounting member and the second mounting member are connected by the rubber elastic body of the main body, and each of the main liquids in which an incompressible fluid is sealed and relative pressure fluctuations are exerted upon vibration input. A valve for switching the orifice passage between a communication state and a shut-off state in a fluid-filled vibration isolator provided with a chamber and a sub-liquid chamber and an orifice passage communicating the main liquid chamber and the sub-liquid chamber with each other And a biasing means for applying a biasing force to the valve body to hold the orifice passage in a shut-off state by the valve body, while having a stator and a mover assembled so as to be relatively displaceable in one axial direction. A coil is provided on one of the stator and the mover, and a permanent magnet for driving is provided on the other, and an elastic connecting member for elastically positioning the stator and the mover in a uniaxial direction is provided. Switching of the valve element that employs a vibration device in which the mover is driven uniaxially by energizing the cylinder, and the uniaxial direction in which the mover in the vibration device is displaced switches the orifice passage between the communication state and the cutoff state A valve in which the stator of the vibration exciter is fixedly arranged with respect to the second mounting member in a state matching the operating direction, and is opposed to each other at a predetermined distance in the uniaxial direction between the valve element and the mover. The body-side connecting part and the mover-side connecting part are provided, and the valve-body-side connecting part and the mover-side connecting part are adsorbed in a contact state by exerting a magnetic attractive force on the valve-body-side connecting part and the mover-side connecting part. Displacement of the mover side connecting part until the valve element is displaced against the urging force of the urging means is provided, and a permanent magnet for connection is provided to energize the coil of the vibration exciter to After adsorbing to the body side connecting part By discontinuing energization of the actuator, the valve body side coupling portion adsorbed on the movable element side coupling portion is displaced using the restoring displacement of the movable element by the elastic positioning force of the elastic coupling member in the vibration device. The valve element can be displaced and held in the communication state of the orifice passage, and the movable element side is excited and displaced in a uniaxial direction with respect to the stator by energizing the coil of the vibration exciter. The mover including the connecting portion is vibrated independently from the valve body so as to function as an active vibration control device.

  In such a fluid-filled vibration isolator having the structure according to the present invention, the orifice passage that allows the main liquid chamber and the sub liquid chamber to communicate with each other can be switched between a communication state and a blocking state by the valve body. Therefore, an effective anti-vibration effect can be obtained with respect to a plurality of types of vibrations having different frequencies, and a more excellent anti-vibration performance can be realized. In addition, the valve body is switched and operated using a vibration exciter that exhibits a damping effect that counteracts the input vibration. Therefore, an effective anti-vibration effect can be obtained for vibrations of a wider frequency by virtue of the anti-vibration effect of the orifice passage and the anti-vibration effect of the vibration exciting device.

  Further, by utilizing the vibration device as the valve body driving means, there is no need to provide a special electromagnetic actuator that is used only for driving the valve body, and a switching type fluid-filled vibration damping device and vibration device. As compared with the case where both are provided, the weight can be reduced and the installation space can be reduced.

  Further, the driving of the valve body for switching the orifice passage to the communication state is realized by using the magnetic attraction force of the connecting permanent magnet and the restoring force of the elastic connecting member. In particular, since the valve element is displaced and held by the magnetic attraction force of the connecting permanent magnet, it is necessary to maintain energization to the coil even when the orifice passage is kept in communication for a long time. Therefore, it is possible to prevent deterioration of durability due to heat generation and deterioration of fuel consumption due to power consumption.

  Further, in the fluid-filled vibration isolator according to the present invention, the second mounting member has a cylindrical shape, and the first mounting member is disposed separately on one opening side of the second mounting member. While connected by a rubber elastic body, the other opening side of the second mounting member is closed with a flexible membrane, and the main liquid is placed on one side of the partition member supported by the second mounting member. The chamber is formed as a pressure receiving chamber in which a part of the wall part is constituted by a main rubber elastic body, and on the other side, a secondary liquid chamber is provided on the other side of the equilibrium part in which a part of the wall part is constituted by a flexible film. And a valve body side projection that extends through the flexible membrane to the outside is provided in the valve body that switches the orifice passage that communicates between the pressure receiving chamber and the equilibrium chamber between the communication state and the cutoff state. On the other hand, in the vibration exciter, the stator is supported in the accommodated state with respect to the cylindrical outer sleeve. In addition, a mover is attached to an inner member that is disposed so as to be relatively displaceable in the central axis direction with respect to the outer sleeve, and the outer sleeve is an opening on the flexible membrane side of the second attachment member The inner member is provided with a movable element side protrusion that extends to one side of the outer sleeve in the axial direction, and the movable element side protrusion is the valve element side protrusion. The movable element side connecting portion and the valve body side connecting portion may be configured to be opposed to each other.

  With such a structure, it is possible to realize a fluid-filled vibration isolator equipped with a vibration exciter, and by switching the orifice passage by driving a valve body using the vibration exciter, vibration at a wider frequency can be achieved. An effective anti-vibration effect can be obtained.

  Further, in the fluid filled type vibration damping device according to the present invention, a stopper mechanism for limiting the displacement amount of the valve body is provided, and the coil side connection portion is adsorbed to the valve body side connection portion, and the coil is energized. When the mover is displaced away from the valve body in the direction of separation, the mover is displaced beyond the displacement of the valve body allowed by the stopper mechanism, so that the valve body side connection portion is moved from the mover side connection portion. You may be forced to leave.

  According to this, separation of the valve body side connecting portion and the mover side connecting portion is realized with higher reliability, and the switching of the orifice passage to the shut-off state can be performed stably. Therefore, it is possible to efficiently obtain an anti-vibration effect corresponding to the input vibration, and to improve the anti-vibration performance.

  Further, in the fluid filled type vibration isolator according to the present invention, a DC drive power is supplied to the coil, and the mover is driven and displaced in the uniaxial direction toward the valve body, thereby moving the mover side connection. Power supply means for adsorbing the contact portion to the valve body side coupling portion, and excitation power supply for supplying alternating drive power to the coil to reciprocally drive the mover in a uniaxial direction independently of the valve body And a control device that controls the energization state of the coil.

  According to this, by supplying direct-current power to the coil by the attracting power feeding means, the valve body can be displaced in one direction and the orifice passage can be switched to the communication state. On the other hand, by supplying AC power to the coil by the excitation power supply means, the mover is excited and displaced, and the orifice passage is switched to a cut-off state, or based on an offset action by the excitation force. The vibration control effect can be demonstrated.

  Further, in the fluid filled type vibration damping device according to the present invention, the main liquid chamber is a pressure receiving chamber in which a part of the wall portion is formed of a main rubber elastic body, and the pressure of the pressure receiving chamber is exerted on the valve body. In addition, a pressure relief mechanism for the pressure receiving chamber may be configured by allowing the displacement of the valve body in accordance with the pressure of the pressure receiving chamber acting on the valve body in the biasing means.

  Thus, when a shocking large load is input, the pressure relief mechanism is configured to displace the valve body against the urging force of the urging means and switch the orifice passage to the communication state. In the pressure receiving chamber, it is possible to prevent an excessive pressure fluctuation from being abruptly induced. Therefore, it is possible to effectively prevent the deterioration of the vibration-proof performance due to the remarkably high dynamic spring and the generation of abnormal noise and vibration due to cavitation.

  Further, in the fluid filled type vibration damping device according to the present invention, preferably, a fluid flow path for communicating the main liquid chamber and the sub liquid chamber is formed, and the fluid flow path has a lower frequency than the orifice passage. It has been tuned.

  According to this, it is possible to obtain an anti-vibration effect against vibration at a lower frequency based on the flow action of the fluid that is caused to flow through the fluid flow path. In particular, since the communication state and shut-off state of the orifice passage tuned to a higher frequency than the fluid flow path can be switched by the valve body, the fluid flow through the fluid flow path can be prevented by shutting off the orifice passage. It can be produced efficiently and an effective anti-vibration effect can be obtained.

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

  FIG. 1 shows an automotive engine mount 10 as an embodiment of an active fluid-filled vibration isolator according to the present invention. The engine mount 10 includes a mount main body 12, and the mount main body 12 includes a first mounting bracket 16 as a first mounting member and a second mounting bracket 18 as a second mounting member. The main rubber elastic bodies 20 are connected to each other. The first mounting bracket 16 is attached to a power unit (not shown), and the second mounting bracket 18 is attached to a vehicle body (not shown), so that the power unit is supported by the vehicle body in a vibration-proof manner. In the following description, in principle, the vertical direction refers to the vertical direction in FIG. 1 that is the axial direction. In addition, when the engine mount 10 is mounted on the vehicle, the shared load of the power unit is exerted in the axial direction, so that the first mounting bracket 16 and the second mounting bracket 18 are brought close to each other in the axial direction.

  More specifically, the first mounting bracket 16 has a substantially hemispherical fixing portion 22, a flange portion 24 that spreads on the outer peripheral side at the upper end portion of the fixing portion 22, and extends upward from the upper end surface of the fixing portion 22. It has a structure that is integrally provided with a mounting portion 26 to be taken out. Furthermore, the attachment portion 26 is formed with a screw hole 28 that opens in the upper surface and extends in the axial direction. The first mounting bracket 16 is attached to the power unit by a fixing bolt that is screwed into the screw hole 28.

  On the other hand, the second mounting bracket 18 has a thin-walled, large-diameter, generally cylindrical shape, and has a step portion 30 at an axially intermediate portion. Further, a cylindrical caulking portion 32 extending downward is integrally formed at the outer peripheral edge portion of the step portion 30. A cylindrical bracket 34 is fitted to the second mounting bracket 18. In the present embodiment, an inner flange-shaped stopper portion 36 integrally formed at the upper end edge of the bracket 34 is opposed to the flange portion 24 of the first mounting bracket 16 in the axial direction, so that the first mounting A rebound stopper for limiting the relative displacement in the axial direction between the metal fitting 16 and the second mounting metal 18 is configured.

  Further, the first mounting bracket 16 is spaced apart on the same center axis on the upper opening side of the second mounting bracket 18, and the first mounting bracket 16 and the second mounting bracket 18 are elastic in the main body. Connected by the body 20. The main rubber elastic body 20 has a substantially frustoconical shape, and is vulcanized and bonded to the end portion of the small diameter side with the first mounting bracket 16 buried at a predetermined depth. The mounting bracket 18 is vulcanized and bonded to the outer peripheral surface of the large-diameter end of the main rubber elastic body 20. In addition, a substantially mortar-like or hemispherical large-diameter recess 38 is formed on the large-diameter side end face of the main rubber elastic body 20. Further, a thin-walled cylindrical seal rubber layer 40 extending downward is integrally formed on the outer peripheral edge of the main rubber elastic body 20. The flange portion 24 of the first mounting bracket 16 is overlapped and fixed to the end surface on the small diameter side of the main rubber elastic body 20 and is integrally formed with the main rubber elastic body 20 on the upper surface of the flange portion 24. Further, a buffer rubber 42 is formed to adhere.

  Further, a diaphragm 44 as a flexible film is assembled to the second mounting bracket 18. The diaphragm 44 is a thin rubber elastic film having a substantially disk shape, and has a slack in the axial direction. The diaphragm 44 is assembled so as to cover the lower opening of the second mounting bracket 18. Accordingly, a fluid sealing region 46 is formed on the inner peripheral side of the second mounting bracket 18 so as to be sealed with respect to the external space and sealed with an incompressible fluid. As the sealed fluid, a low-viscosity fluid such as water or alkylene glycol is preferably employed.

  A partition member 48 is disposed in the fluid sealing area 46. The partition member 48 includes a partition member main body 50 and a lid plate 52. The partition member main body 50 is a hard member having a thick, substantially disk shape. Further, a circular central recess 54 that opens to the upper end surface is formed in the central portion of the partition member body 50 in the radial direction, and a central hole 56 that penetrates the bottom wall portion of the central recess 54 is provided. Yes. Further, an annular stopper protrusion 57 that protrudes upward from the bottom wall portion of the central recess 54 is integrally formed at the inner peripheral edge of the central hole 56. In addition, a spiral circumferential groove 58 is formed in the outer peripheral edge of the partition member main body 50 so as to open to the outer peripheral surface and extend in the circumferential direction with a predetermined length of less than two rounds. Further, the partition member main body 50 is formed with a plurality of communication holes 60 penetrating in the axial direction through the outer peripheral edge of the bottom wall of the central recess 54. In the partition member main body 50, between the radial direction of the central recess 54 and the circumferential groove 58, a hollowing groove extending in the circumferential direction is formed at both upper and lower ends in the axial direction.

  On the other hand, the lid plate 52 has a thin disk shape, and is overlapped and fixed on the upper surface of the partition member main body 50. Thereby, the opening of the central recess 54 formed in the partition member main body 50 is covered with the cover plate 52. A plurality of through holes 62 are formed in the lid plate 52 so as to penetrate the opening portion of the central recess 54 in the plate thickness direction.

  The partition member 48 including the partition member main body 50 and the cover plate 52 is disposed so as to spread in the direction perpendicular to the axis in the fluid sealing region 46 and supported by the second mounting bracket 18. As a result, the fluid sealing region 46 is vertically divided into two by the partition member 48. On the upper side across the partition member 48, a part of the wall portion is constituted by the main rubber elastic body 20, and the internal pressure fluctuations when vibration is input. A pressure receiving chamber 64 as a main liquid chamber is formed, and on the lower side across the partition member 48, a part of the wall portion is constituted by the diaphragm 44, and the secondary liquid is allowed to change in volume. An equilibrium chamber 66 is formed as a chamber.

  Further, the circumferential groove 58 formed in the partition member main body 50 is covered with the second mounting bracket 18 via the seal rubber layer 40. Further, both end portions of the circumferential groove 58 are communicated with the pressure receiving chamber 64 and the equilibrium chamber 66. Thus, a fluid flow path 68 is formed which extends the outer peripheral edge of the partition member 48 in the circumferential direction by a predetermined length and communicates the pressure receiving chamber 64 and the equilibrium chamber 66 with each other. The fluid flow path 68 is tuned to a low frequency corresponding to the engine shake. In the present embodiment, the fluid flow path 68 is always in communication.

  Further, the communication hole 60 formed in the partition member main body 50 and the communication hole 62 formed in the lid plate 52 communicate with each other via the central recess 54, thereby communicating the pressure receiving chamber 64 and the equilibrium chamber 66. An orifice passage 70 is formed. The orifice passage 70 is tuned to a frequency higher than that of the fluid flow path 68. In the present embodiment, the orifice passage 70 is tuned to a medium frequency corresponding to idling vibration. The tuning frequency of the fluid flow path 68 and the orifice passage 70 is set by appropriately adjusting the ratio value (A / L) of the passage cross-sectional area (A) and the passage length (L).

  In this case, a valve fitting 72 as a valve body is disposed in the central recess 54. The valve fitting 72 is a substantially cup-shaped member that opens upward, and a lower end portion is inserted into the central hole 56. A flange-shaped valve portion 74 is provided at the upper end portion of the valve fitting 72. The valve portion 74 is provided so as to block the through hole 62 of the lid plate 52 by being superimposed on the lid plate 52 from below. Further, a coil spring 76 as an urging means is interposed between the opposed surfaces of the valve portion 74 and the bottom wall portion of the central recess 54. The coil spring 76 is disposed in a compressed state in the axial direction, and is always urged in a direction (upward) in which the valve fitting 72 approaches the cover plate 52 by the elastic force of the coil spring 76. The valve portion 74 of the valve fitting 72 is pressed against the opening peripheral edge of the through hole 62 by the urging force of the coil spring 76, so that the through hole 62 and the orifice passage 70 are blocked by the valve portion 74. The pressure of the pressure receiving chamber 64 is exerted on the upper surface of the valve portion 74 through the through-hole 62 and the lower surface of the valve portion 74 is communicated through the communication hole 60 with the through-hole 62 blocked. The pressure in the equilibrium chamber 66 is exerted

  Below the mount body 12 having such a structure, an electromagnetic vibration damper 78 serving as a vibration exciter is disposed. The electromagnetic vibration damper 78 includes a stator 82 supported by a vehicle body as a vibration suppression object, and a mover 84 that is allowed to be displaced in the axial direction with respect to the stator 82.

  The stator 82 includes a coil 86. The coil 86 is wound around a non-magnetic bobbin and has a substantially cylindrical shape. The coil 86 is connected to an external power supply device 88, and a magnetic field is formed by energization of the coil 86 from the power supply device 88. Furthermore, in this embodiment, the control device 90 is disposed on a circuit that connects the coil 86 to the power supply device 88. The control device 90 supplies direct-current power having a constant current direction to the coil 86 to generate a strong magnetic field having a constant polarity, and a power supply means 92 for attracting power to the coil 86. It is configured to include an excitation power supply means 94 that supplies alternating-current power whose direction changes and generates a magnetic field whose polarity changes. Then, the control device 90 selects any one of the non-energized state of the coil 86, the DC power supply state, and the AC power supply state, and the power supply state to the coil 86 is controlled. Yes.

  A yoke fitting 96 is attached to the coil 86. The yoke fitting 96 is formed of a ferromagnetic material having a substantially cylindrical shape. The yoke fitting 96 is externally inserted into the coil 86, and the lower end portion is protruded to the inner peripheral side and overlapped with the lower surface of the coil 86.

  The stator 82 including the coil 86 and the yoke fitting 96 is accommodated in a housing 98 as an outer sleeve. The housing 98 has a substantially cylindrical shape and is integrally provided with a cylindrical mounting portion 100 having a yoke fitting 96 fixed to the inner peripheral surface thereof and a mounting leg portion 102 that extends to the outer peripheral side at the lower end portion of the cylindrical mounting portion 100. It has become.

  A mover 84 is disposed on the inner peripheral side of the coil 86. The mover 84 includes a vibration magnet 104 as a driving permanent magnet. The exciting magnet 104 has a substantially annular plate shape and is magnetized in the axial direction.

  Further, an upper mass metal fitting 106 and a lower mass metal fitting 108 as mass members are fixed to the upper and lower surfaces of the vibration magnet 104. The upper and lower mass fittings 106 and 108 are substantially circular plate-shaped members made of a ferromagnetic material, and are superimposed on the exciting magnet 104 from both sides in the axial direction.

  The vibration magnet 104 provided with the upper and lower mass fittings 106 and 108 is attached to a rod member 110 as an inner member. The rod member 110 has a substantially cylindrical shape, and both axial end portions have a smaller diameter than the central portion. The vibrating magnet 104 and the mass metal fittings 106 and 108 are externally fitted and fixed to the large-diameter portion at the center in the axial direction. The rod member 110 may be formed of a ferromagnetic material or a nonmagnetic material such as a synthetic resin.

  The rod member 110 to which the excitation magnet 104 is attached in this manner is inserted and arranged on the inner peripheral side of the coil 86 fixed to the housing 98, and the first leaf spring 112 and the second leaf spring 112 serving as an elastic connecting member. The plate spring 114 is elastically connected to the stator 82. Each of the first and second leaf springs 112 and 114 has a structure in which a plurality of substantially annular plate-shaped metal springs extending in the direction perpendicular to the axis are laminated. Further, it is desirable that a slit as shown in FIG. 2 of Japanese Patent No. 3873618 is formed in the first and second leaf springs 112 and 114 so as to penetrate in the plate thickness direction. The first leaf spring 112 has an inner peripheral edge that is fitted and fixed to the upper end small diameter portion of the rod member 110, and an outer peripheral edge that is overlapped and fixed to the upper end surface of the yoke fitting 96. On the other hand, the second leaf spring 114 has an inner peripheral edge portion that is externally fixed to the small diameter portion of the lower end of the rod member 110, and an outer peripheral edge portion that is inserted and fixed to the housing 98.

  Note that the inner peripheral edge and the outer peripheral edge of the first plate spring 112 are attached to the rod member 110 and the housing 98 by a suction metal fitting 132 described later and a holding metal fitting 116 that is press-fitted into the housing 98 in a substantially annular plate shape. It is fixed against. On the other hand, the inner peripheral edge and the outer peripheral edge of the second leaf spring 114 are inserted into the housing 98 with a small-diameter ring-shaped inner peripheral support bracket 118 fixed to the small-diameter portion of the lower end of the rod member 110 in an extrapolated state. It is fixed to the rod member 110 and the housing 98 by a large-diameter ring-shaped outer peripheral support member 120 that is fixed in the above.

  Furthermore, the rod member 110 to which the mover 84 is attached is connected to the housing 98 by a support rubber elastic body 122 at the lower end in the axial direction. The support rubber elastic body 122 has a substantially annular plate shape extending in a direction perpendicular to the axis, and a ring-shaped fixing bracket 124 is vulcanized and bonded to the outer peripheral edge portion, and a substantially cup-like shape is attached to the inner peripheral edge portion. The fitting fitting 126 is vulcanized and bonded. The fixing metal 124 is inserted into the lower end portion of the housing 98 and supported by a cover metal 128 that is fitted to the housing 98 from below. On the other hand, the fitting 126 is covered and fixed to the lower end of the rod member 110 from below. Thus, the lower end portion of the rod member 110 is elastically connected to the housing 98 by the support rubber elastic body 122.

  Thus, the upper and lower ends of the rod member 110 are connected to the stator 82 by the first and second leaf springs 112 and 114 and the support rubber elastic body 122. Accordingly, the movable element 84 including the rod member 110 is fixedly supported in the direction perpendicular to the axis with respect to the stator 82 and is elastically positioned in the axial direction, whereby the first and second leaf springs 112, 114 and the elastic support body 122 are allowed to be displaced in the axial direction by elastic deformation. In addition, under the positioning arrangement of the stator 82 and the mover 84, the inner peripheral surface of the stator 82 and the outer peripheral surface of the mover 84 are opposed to each other in the radial direction with a predetermined gap. Further, in the coupled state of the stator 82 and the mover 84, in this embodiment, the axial center of the exciting magnet 104 and the upper and lower mass fittings 106, 108 of the mover 84 is the axis of the coil 86 of the stator 82. It is biased downward with respect to the direction center.

  In the electromagnetic vibration damper 78 having such a structure, when the coil 86 is energized from the external power supply device 88, the movable element 84 is fixed to the stator by the action of the magnetic field by the coil 86 and the magnetic field by the exciting magnet 104. 82 can be driven in the axial direction.

  More specifically, when DC driving power is supplied to the coil 86 by the attracting power feeding means 92 of the control device 90, the mover 84 is largely displaced in the axial direction upward with respect to the stator 82. It can be driven. The energization of the coil 86 stops the energization in a state where the movable element 84 is driven and displaced in the axial direction with respect to the stator 82, so that the elastic force of the leaf springs 112, 114 and the support rubber elastic body 122 is stopped. Thus, the movable element 84 is returned to the original position in the axial direction.

  On the other hand, when alternating drive power is supplied to the coil 86 by the excitation power supply means 94 of the control device 90, the mover 84 moves to the stator 82 in accordance with a change in the energization direction of the coil 86. Thus, it can be displaced in the axial direction up and down. Then, the exciting force exerted by the mover 84 to which the upper and lower mass fittings 106 and 108 are attached is transmitted to the vehicle body via the housing 98, so that an offset damping effect against the input vibration is exhibited. It has come to be. In the present embodiment, the vibration damping effect by the electromagnetic vibration damper 78 is set so as to be effectively exhibited against high-frequency vibration corresponding to traveling noise.

  The AC driving power mentioned here includes sine wave AC whose energization direction is reversed at a short time interval, as well as pulsating power whose power changes at a short time interval. When pulsating power is supplied to the coil 86, an upward driving force due to the action of a magnetic field and a downward driving force due to the elastic force of the leaf springs 112 and 114 are alternately applied to the mover 84. As a result, the movable element 84 is driven to vibrate in the axial direction.

  The electromagnetic vibration damper 78 having such a structure is disposed below the mount body 12 and is fixed to the mount body 12 by fixing the housing 98 to the second mounting bracket 18. That is, the housing 98 has the upper end portion of the cylindrical mounting portion 100 protruding to the outer peripheral side fixed by the caulking portion 32 of the second mounting bracket 18 and overlapped with the second mounting bracket 18 in the axial direction. Has been attached. As a result, the electromagnetic vibration damper 78 is attached to the mount body 12, and the stator 82 is fixed to the second mounting bracket 18 via the housing 98. On the other hand, the housing 98 is mounted on the vehicle body by mounting bolts that are inserted through bolt holes formed in the mounting legs 102. Thereby, the second mounting bracket 18 is fixed to the vehicle body via the housing 98. Note that, when the mount body 12 and the electromagnetic damper 78 are assembled, the center axis of the mount body 12 and the center axis of the electromagnetic damper 78 are aligned, and the operating direction of the valve fitting 72 of the mount body 12 is adjusted. And the drive direction of the movable element 84 are matched.

  Here, a magnet support member 130 as a valve body side protrusion is attached to the valve fitting 72 of the mount body 12, and a mover side protrusion to the rod member 110 of the electromagnetic vibration damper 78. A suction metal fitting 132 is attached.

  The magnet support member 130 has a substantially bottomed cylindrical shape in the reverse direction, and the upper bottom wall portion is overlapped and fixed to the bottom wall portion of the valve fitting 72. Furthermore, the magnet support member 130 is made of a nonmagnetic material. The magnet support member 130 is disposed so as to penetrate the radial central portion of the diaphragm 44 in the axial direction, and the diaphragm 44 is vulcanized and bonded to the outer peripheral surface of the magnet support member 130 over the entire circumference. Has been.

  On the other hand, the suction fitting 132 has a substantially cup shape in the reverse direction, and is formed of a ferromagnetic material such as iron. The suction metal fitting 132 is fitted so as to cover the upper end portion of the rod member 110 after the first leaf spring 112 is extrapolated to the upper end portion of the rod member 110. As described above, by attaching the suction metal fitting 132 to the rod member 110, a portion having ferromagnetism is provided at the upper end portion of the rod member 110. In the present embodiment, the suction metal fitting 132 prevents the first leaf spring 112 from being pulled upward.

  The magnet support member 130 and the attracting metal fitting 132 are opposed to each other with a predetermined distance in the axial direction on the central axis of the engine mount 10. As a result, the lower opening of the magnet support member 130 is opposed to the upper bottom wall surface of the suction fitting 132. In the present embodiment, the valve body side coupling portion is configured by the magnet support member 130, and the mover side coupling portion is configured by the suction metal fitting 132.

  Here, an attracting magnet 134 as a permanent magnet for connection is disposed between the magnet support member 130 and the attracting metal fitting 132. The attracting magnet 134 has a substantially circular block shape and is magnetized in the axial direction. Then, the magnet support member 130 is fitted into the lower opening and fixed to the inner peripheral side of the magnet support member 130.

  In the engine mount 10 having the mount body 12 and the electromagnetic damper 78 as described above, the valve fitting 72 of the mount body 12 is driven and displaced in the axial direction by the electromagnetic damper 78, so that the orifice passage 70 communicates. It can be switched between a state and a shut-off state. Below, the operation | movement which switches the orifice channel | path 70 from the interruption | blocking state to a communication state is demonstrated.

  First, as shown in FIG. 1, when the coil 86 of the electromagnetic vibration damper 78 is not energized, the valve fitting 72 is urged upward by the urging force of the coil spring 76, and the lid plate 52 is It is pressed against. As a result, the valve portion 74 of the valve fitting 72 is pressed so as to close the through hole 62, and the orifice passage 70 is held in a shut-off state. Note that, when the coil 86 is not energized, the axial distance between the magnet support member 130 and the suction fitting 132 is set appropriately, and the magnet support member 130 and the suction fitting due to the magnetic attractive force of the suction magnet 134 are set. Adsorption of 132 is prevented.

  Next, DC power is supplied to the coil 86 from the attracting power feeding means 92 of the control device 90, and as shown in FIG. 2, the mover 84 is greatly displaced upward in the axial direction. The attracting metal fitting 132 attached to the upper end of the rod member 110 is brought close to the attracting magnet 134 attached to the valve metal fitting 72. As a result, the magnet support member 130 provided with the attracting magnet 134 is attracted to the attracting metal fitting 132 formed of a ferromagnetic material by the magnetic attraction force of the attracting magnet 134, and the magnet support member 130. And the suction fitting 132 are connected to each other.

  In particular, in this embodiment, when the coil 86 is not energized, the arrangement position of the excitation magnet 104 that constitutes the mover 84 is in the axial direction with respect to the arrangement position of the coil 86 that constitutes the stator 82. It is shifted downward. Therefore, it is possible to displace the mover 84 to the suction position shown in FIG. 2 by efficiently applying an axially upward driving force to the mover 84 by energizing the coil 86. .

  Next, after the magnet support member 130 and the attracting metal fitting 132 are attracted, the energization to the coil 86 is stopped, whereby the restoring force of the first and second leaf springs 112 and 114 and the support rubber elastic body 122 is restored. Thus, the mover 84 is returned to the initial position. At that time, as shown in FIG. 3, the magnet support member 130 attached to the valve fitting 72 and the adsorption fitting 132 attached to the mover 84 are brought into an attracting state in which they are brought into contact with each other by the action of magnetic force. It is supposed to be retained. As a result, the valve fitting 72 provided with the attracting magnet 134 is pulled downward by the displacement of the mover 84, and the valve portion 74 provided at the upper end of the valve fitting 72 is separated downward from the cover plate 52. . As a result, the through hole 62 formed in the lid plate 52 is communicated, and the orifice passage 70 is switched to the communication state.

  Although a gap is formed between the outer peripheral surface of the valve fitting 72 and the inner peripheral surface of the central hole 56, it is compressed and deformed in the axial direction under the communication state of the orifice passage 70 shown in FIG. The coil spring 76 substantially blocks between the opposing surfaces of the valve portion 74 and the bottom wall portion of the central recess 54. Therefore, communication between the pressure receiving chamber 64 and the equilibrium chamber 66 by the gap is prevented, and fluid flow through the orifice passage 70 is efficiently induced.

  Further, the first and second plates in which the urging force of the coil spring 76 that urges the valve fitting 72 in the direction in which the valve fitting 72 is pressed against the lid plate 52 is exhibited under the displacement state of the mover 84 shown in FIG. It is set smaller than the sum of the restoring forces of the springs 112 and 114 and the support rubber elastic body 122. Thus, by stopping energization of the coil 86, the valve fitting 72 resists the urging force of the coil spring 76 by the restoring force of the first and second leaf springs 112, 114 and the support rubber elastic body 122. Can be displaced downward.

  On the other hand, the switching of the orifice passage 70 from the communication state to the cutoff state is performed by, for example, supplying AC power to the coil 86 from the excitation power feeding means 94 of the control device 90 in the axial direction. This is realized by applying an excitation force and pulling the attracting magnet 134 away from the attracting metal fitting 132. That is, by releasing the adsorption of the adsorption magnet 134 and the adsorption fitting 132, the valve fitting 72 is pressed against the cover plate 52 by the biasing force of the coil spring 76, and the through hole 62 is blocked by the valve fitting 72. As a result, the orifice passage 70 is switched to the shut-off state.

  Further, the switching of the orifice passage 70 to the shut-off state is performed by, for example, supplying the DC power to the coil 86 from the attracting power feeding means 92 of the control device 90 so that the movable element 84 is greatly lowered in the axial direction. This can also be realized by forcibly separating the attracting bracket 132 from the attracting magnet 134 by pulling the movable element 84 downward beyond the allowable amount of downward displacement of the valve bracket 72. In the present embodiment, a stopper mechanism that restricts the displacement of the valve fitting 72 by the contact between the stopper projection 57 and the valve portion 74 is configured, and the adsorption fitting 132 and the adsorption magnet 134 are separated by the stopper mechanism. It has come to be realized. That is, in the state of FIG. 3 in which the attracting metal fitting 132 and the attracting magnet 134 are attracted while the coil 86 is not energized, the distance between the projecting tip surface of the stopper projecting portion 57 and the axially facing surface of the valve portion 74 is The distance is smaller than the distance between the axially opposed surfaces of the lower surface of the inner peripheral edge of the support rubber elastic body 122 fixed to the fitting fitting 126 and the cover fitting 128. Therefore, when the movable element 84 is displaced downward, the stopper projection 57 is brought into contact with the valve portion 74 of the valve fitting 72, and the adsorption fitting 132 and the adsorption magnet 134 are forcibly separated. It has come to be. On the other hand, as the stopper mechanism, for example, a structure that limits the amount of downward displacement of the valve fitting 72 using the limit of the compressive deformation in the axial direction of the coil spring 76 can be employed.

  Then, by driving the movable element 84 in a state of being separated and independent from the valve fitting 72, an excitation force can be exerted on the vehicle body to exert an active damping action against the input vibration. . In short, the electromagnetic vibration damper 78 functions as an active vibration damping device in a state where the magnet support member 130 and the suction metal fitting 132 are separated.

  When the automobile engine mount 10 having such a structure according to the present embodiment is mounted on a vehicle and the automobile is running, the orifice passage 70 is held in a cut-off state, so that a low frequency large amplitude corresponding to an engine shake is obtained. Both vibrations and high-frequency small-amplitude vibrations equivalent to running-over noise are effectively reduced.

  That is, when low frequency vibration corresponding to engine shake is input, fluid flow through the fluid flow path 68 is positively generated based on the relative pressure difference between the pressure receiving chamber 64 and the equilibrium chamber 66. As a result, an anti-vibration effect based on the fluid action of the fluid flowing between the two chambers 64 and 66 through the fluid flow path 68 is exhibited. At this time, since the orifice passage 70 is blocked, the fluid flow through the fluid flow path 68 can be efficiently generated, and the vibration isolation effect obtained by the fluid flow path 68 can be advantageously obtained. .

  In addition, when inputting high-frequency vibration equivalent to traveling noise, AC power is supplied to the coil 86 by the excitation power supply means 94 of the control device 90, and the mover having the mass fittings 106 and 108 attached thereto. 84 is displaced by excitation. As a result, a vibration damping effect is exerted by applying an exciting force to the vehicle body and canceling the input high-frequency vibration.

  On the other hand, when the automobile stops, DC power is supplied to the coil 86 by the attracting power feeding means 92 of the control device 90, and the orifice passage 70 is switched to the communication state. As a result, an anti-vibration effect based on the fluid flow action is exhibited against medium-frequency vibration corresponding to idling vibration.

  As described above, the engine mount 10 has an effective anti-vibration effect with respect to a plurality of types of vibrations having different frequencies, and can achieve excellent anti-vibration performance. is there.

  Furthermore, in the present embodiment, when an impact heavy load is input between the first mounting bracket 16 and the second mounting bracket 18 due to, for example, the automobile getting over the protrusion while the orifice passage 70 is blocked. In addition, a pressure relief mechanism for reducing the positive pressure exerted on the pressure receiving chamber 64 is provided. That is, when excessive pressure fluctuation is applied to the pressure receiving chamber 64, the pressure in the pressure receiving chamber 64 is applied to the valve fitting 72 through the through hole 62, and the valve fitting 72 is displaced downward against the urging force of the coil spring 76. I'm damned. Thereby, the orifice passage 70 is passively switched to the communication state, and the pressure in the pressure receiving chamber 64 is released to the equilibrium chamber 66 through the orifice passage 70, so that the pressure fluctuation in the pressure receiving chamber 64 is reduced or eliminated. It has become. Therefore, the high dynamic spring caused by the excessive pressure fluctuation in the pressure receiving chamber 64 can be prevented, and the deterioration of the vibration isolation performance can be prevented.

  Further, in the present embodiment, the driving of the valve fitting 72 is realized by using the driving force of the electromagnetic vibration damper 78 that exhibits a vibration-proofing effect against high-frequency vibration. Therefore, it is not necessary to provide a special actuator for switching between communication and blocking of the orifice passage 70, and switching of the orifice passage 70 can be realized with a small number of parts. In other words, the structure that allows the actuator that drives the valve fitting 72 to be used as an active vibration damping device reduces vibrations against high-frequency vibrations without specially providing a hydraulic pressure absorbing mechanism such as a movable plate. An effect can be obtained. In this way, the structure provided with the electromagnetic vibration damper 78 can reduce the installation space compared to providing a vibration device separately from the engine mount, and can reduce the size and weight of the automobile. Can be realized in an advantageous manner.

  In addition, the valve fitting 72 has a displacement of the mover 84 due to energization of the coil 86, adsorption of the magnet support member 130 and the adsorption fitting 132 by the magnetic attractive force of the adsorption magnet 134, and first and second leaf springs. 112 and 114 and the restoring force against deformation of the support rubber elastic body 122 are used to switch to the communication state. In addition, the orifice passage 70 is held in a communicating state in a state where energization to the coil 86 is stopped. Therefore, when the orifice passage 70 is switched to the communication state, the energization time to the coil 86 can be extremely shortened, and it is possible to suppress the heat generation due to the energization and reduce the power consumption. As a result, the durability of the engine mount 10 and the fuel efficiency of the automobile can be advantageously improved.

  As mentioned above, although one Embodiment of this invention has been described, this is an illustration to the last, Comprising: This invention is not limited at all by the specific description in this Embodiment.

  For example, although the structure in which the attracting magnet 134 is attached to the valve fitting 72 side is shown in the embodiment, the coupling permanent magnet may be attached to the mover side. In this case, the valve body side is attracted by the magnetic force of the coupling permanent magnet. Moreover, the permanent magnet for a connection may be provided in both the valve body side and the needle | mover side, and these permanent magnets for a connection may mutually adsorb | suck with the mutual magnetic force.

  Further, in the above-described embodiment, the magnet support member 130 is disposed so as to penetrate the diaphragm 44 in the axial direction, and the attracting magnet 134 supported by the magnet support member 130 is attached to the mover 84. It is adsorbed in a state of being in direct contact with the metal fitting 132. However, for example, the attracting magnet 134 may be disposed with the rubber layer such as the diaphragm 44 and other members sandwiched between the attracting metal fitting 132. In particular, by interposing a rubber layer such as the diaphragm 44 between the attracting magnet 134 and the attracting metal fitting 132, abnormal noise due to contact can be suppressed when the attracting magnet 134 and the attracting metal fitting 132 are attracted. Made

  Further, the structure of the vibration exciter applied to the present invention is not limitedly interpreted by the specific structure of the electromagnetic vibration damper 78 shown in the above embodiment. For example, a vibration device having a structure in which a driving permanent magnet is disposed on the stator side and a coil is disposed on the mover side may be applied.

  In the above-described embodiment, the pressure release mechanism is configured to release the pressure in the pressure receiving chamber 64 to the equilibrium chamber 66 when an excessive positive pressure is applied to the pressure receiving chamber 64. However, a pressure relief mechanism may be provided so that the pressure in the pressure receiving chamber 64 is released to the equilibrium chamber 66 when an excessive negative pressure is applied. According to this, cavitation caused by an excessive negative pressure in the pressure receiving chamber 64 can be prevented, and generation of abnormal noise or vibration can be reduced or avoided.

  In the above-described embodiment, the fluid flow path 68 is always in a communication state. For example, the communication state and the cutoff state of the fluid flow path 68 are switched by a negative pressure actuator or an electromagnetic actuator. Also good. Further, a hydraulic pressure absorbing member such as a movable plate or a movable film that exhibits an anti-vibration effect based on the hydraulic pressure absorbing action against vibration having a higher frequency than the orifice passage 70 may be provided.

  Moreover, in the said embodiment, although the example which applied the fluid filled type vibration isolator which concerns on this invention to the engine mount for motor vehicles is shown, this invention is not necessarily limited to motor vehicles, The present invention can also be suitably applied to fluid-filled vibration damping devices for various vehicles such as trains and bicycles, and other uses. Furthermore, the present invention is not necessarily applied only to the engine mount, but can also be applied to a body mount, a suspension member mount, and the like.

  In addition, although not enumerated one by one, the present invention can be carried out in a mode to which various changes, modifications, improvements and the like are added based on the knowledge of those skilled in the art. It goes without saying that all are included in the scope of the present invention without departing from the spirit of the present invention.

The longitudinal cross-sectional view which shows the engine mount as one Embodiment of this invention. The longitudinal cross-sectional view which shows the electricity supply state to the coil of the engine mount. The longitudinal cross-sectional view which shows the electricity supply stop state to the coil of the engine mount.

Explanation of symbols

10: Engine mount for automobile, 12: Mount body, 16: First mounting bracket, 18: Second mounting bracket, 20: Rubber elastic body, 44: Diaphragm, 48: Partition member, 64: Pressure receiving chamber, 66 : Equilibrium chamber, 68: Fluid flow path, 70: Orifice passage, 72: Valve fitting, 76: Coil spring, 78: Electromagnetic damper, 82: Stator, 84: Mover, 86: Coil, 88: Power supply Device: 90: Control device, 92: Adsorption power supply means, 94: Excitation power supply means, 98: Housing, 104: Excitation magnet, 110: Rod member, 112: First leaf spring, 114: Second Leaf spring, 122: elastic elastic body of support, 130: magnet support member, 132: metal fitting for adsorption, 134: magnet for connection

Claims (6)

The first mounting member and the second mounting member are connected by a rubber elastic body of the main body, and a main liquid chamber and a sub liquid chamber in which an incompressible fluid is sealed and relative pressure fluctuation is exerted at the time of vibration input are provided. In the fluid-filled vibration isolator provided with an orifice passage that communicates with the main liquid chamber and the sub liquid chamber,
A valve body for switching the orifice passage between the communication state and the shut-off state is provided, and biasing means for applying a biasing force to the valve body to hold the orifice passage in a shut-off state by the valve body is provided. Each of the stator and the mover is provided with a coil and a driving permanent magnet is provided on the other, and the stator and the mover are attached to the stator and the mover. An elastic coupling member that is elastically positioned in a uniaxial direction is provided, and an exciter that drives the movable element in the uniaxial direction by energizing the coil is employed. The stator of the vibration device is moved with respect to the second mounting member in a state where the uniaxial direction to be displaced coincides with the switching operation direction of the valve body that switches the orifice passage between the communication state and the cutoff state. The valve body and the mover are provided with a valve body side connecting portion and a mover side connecting portion that are opposed to each other at a predetermined distance in the uniaxial direction, and are movable with the valve body side connecting portion. By attaching a magnetic attraction force to the child side connecting portion, the valve body side connecting portion and the mover side connecting portion are adsorbed in a contact state, and the movable body side connecting portion is displaced to displace the valve body. A permanent magnet for connection that can be displaced against the biasing force of the biasing means is provided, and the coil of the vibration exciter is energized to attract the movable element side connecting part to the valve body side connecting part, and then to the coil. The valve body side coupling portion adsorbed on the movable element side coupling portion by using the restoring displacement of the movable element by the elastic positioning force of the elastic coupling member in the vibration device Displace the valve body to communicate with the orifice passage The movable element side coupling portion is included by energizing the coil of the vibration exciter and oscillating and moving the movable element in the uniaxial direction with respect to the stator. A fluid-filled vibration damping device, wherein the movable element is vibrated independently from the valve body so as to function as an active vibration damping device.   While the second mounting member is cylindrical, the first mounting member is spaced apart and connected by the main rubber elastic body on one opening side of the second mounting member, The other opening side of the second mounting member is closed with a flexible membrane, and the main liquid chamber is part of the wall on one side of the partition member supported by the second mounting member. Is formed as a pressure receiving chamber composed of the main rubber elastic body, and the secondary liquid chamber is formed on the other side as an equilibrium chamber composed of a part of the wall portion of the flexible film. In addition, the valve body that switches the orifice passage that communicates between the pressure receiving chamber and the equilibrium chamber between a communication state and a shut-off state is provided with a valve body-side protrusion that extends through the flexible membrane to the outside. On the other hand, in the vibration exciter, the stator is supported in the accommodated state with respect to the cylindrical outer sleeve. And the mover is attached to an inner member that is inserted and arranged relative to the outer sleeve so as to be relatively displaceable in the central axis direction, and the outer sleeve is attached to the second attachment member. The movable member side protrusion is provided to be overlapped and fixed in the axial direction with respect to the opening on the flexible membrane side, and extends to one side in the axial direction of the outer sleeve in the inner member, The fluid-filled vibration isolator according to claim 1, wherein the movable element side protrusion is positioned opposite to the valve element side protrusion to constitute the movable element side connecting part and the valve element side connecting part.   A stopper mechanism for limiting the amount of displacement of the valve element is provided, and the movable element is separated from the valve element by energizing the coil while the movable element side connecting part is adsorbed to the valve element side connecting part. Is displaced toward the valve body, and the movable element is displaced beyond the displacement amount of the valve body allowed by the stopper mechanism, so that the movable body side coupling section is forced to move from the movable body side coupling section. The fluid-filled type vibration damping device according to claim 1 or 2, wherein the vibration-proof type vibration damping device is separated. DC driving power is supplied to the coil, and the mover is driven and displaced toward the valve body in the uniaxial direction, thereby moving the mover side connecting portion to the valve body side connecting portion. Adsorption power feeding means for adsorption,
Including excitation power feeding means for supplying alternating drive power to the coil and reciprocatingly driving the movable element in the uniaxial direction independently of the valve body, The fluid filled type vibration damping device according to any one of claims 1 to 3, wherein a control device for control is configured.   The main liquid chamber is a pressure receiving chamber in which a part of the wall is made of the main rubber elastic body, and the pressure of the pressure receiving chamber is applied to the valve body. 5. The pressure relief mechanism of the pressure receiving chamber is configured by allowing the displacement of the valve body in accordance with the pressure of the pressure receiving chamber acting on the valve body in the biasing means. The fluid-filled vibration isolator described in 1.   6. A fluid flow path that connects the main liquid chamber and the sub liquid chamber to each other is formed, and the fluid flow path is tuned to a frequency lower than that of the orifice passage. The fluid-filled vibration isolator described in 1.

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