JP2009243511A - Fluid-filled engine mount for automobile - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid-filled engine mount for an automobile having a novel structure, improving vibration isolation performance by avoiding significantly high dynamic spring motion caused by the antiresonance action of an orifice passage when large amplitude vibration is inputted on a high-frequency side rather than a tuning frequency of the orifice passage while sufficiently securing the vibration isolation performance by fluid flowing action through the orifice passage and fluid pressure absorption performance by a movable plate. <P>SOLUTION: A pressure release hole 94 is formed at the wall 38 of a movable plate arrangement area 62 on the side of an equilibration chamber 90, and a valve element 96 is provided in such a manner as to abut on an opening of the pressure release hole 94 on the side of the equilibration chamber 90 and to be displaced in a separating direction. Furthermore, a urging means 96 is provided for urging the valve element 96 to elastically close the pressure release hole 94 by the valve element 96. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an engine mount for vibration-proofing and supporting a power unit of an automobile on a vehicle body, and more particularly to a fluid-filled engine mount capable of exhibiting a vibration-proofing effect based on the flow action of a fluid sealed inside.

  2. Description of the Related Art Conventionally, a fluid-filled engine mount is known as a kind of automobile engine mount that is interposed between an automobile power unit and a vehicle body and supports the power unit against vibration against the vehicle body. In this fluid-filled engine mount, the first mounting member and the second mounting member that are attached to each of the power unit and the vehicle body are connected by the main rubber elastic body, and a part of the wall portion is main rubber elastic. A pressure receiving chamber constituted by a body and an equilibrium chamber in which a part of the wall portion is constituted by a flexible film are formed, and an incompressible fluid is sealed in the pressure receiving chamber and the equilibrium chamber. The pressure receiving chamber and the equilibrium chamber are communicated with each other through the orifice passage, and an anti-vibration effect that is an orifice effect is exhibited based on a fluid action such as a resonance action of the fluid through the orifice passage.

  By the way, in the engine mount for automobiles, vibrations having different frequency ranges and amplitudes are input depending on the running state of the automobile and the like, and therefore, anti-vibration performance is required for a plurality of different vibrations. For example, there may be a demand for vibration-proof performance against low-frequency large-amplitude vibrations such as engine shakes, and vibration-proof performance against medium to high-frequency small-amplitude vibrations such as idling vibrations and traveling noises. However, since the effective vibration isolation effect by the orifice passage is exhibited in a specific tuning frequency range, when vibration on the higher frequency side than the tuning frequency is input, the flow resistance becomes remarkably due to the anti-resonant action of the fluid through the orifice passage. There is a problem that the vibration-proof performance is deteriorated due to the increase in mount characteristics and the fact that the mount characteristics are greatly increased and the mount rigidity is increased.

  In order to deal with this problem, for example, Patent Document 1 (Japanese Patent Laid-Open No. 57-9340), Patent Document 2 (Japanese Patent Laid-Open No. 61-55429), etc. In addition to tuning the orifice passage so that an effective orifice effect can be obtained, a movable plate is disposed within the partition member that partitions the pressure receiving chamber and the equilibrium chamber so that the movable plate can be displaced by a predetermined amount, and is passed through the partition member. A liquid that forms a hole and applies pressure in the pressure receiving chamber and the equilibrium chamber to one side of the movable plate through the through hole and absorbs pressure fluctuations in the pressure receiving chamber due to a small displacement of the movable plate due to a pressure difference between the two chambers. A structure provided with a pressure absorbing mechanism has been proposed. As a result, when a vibration is input at a frequency higher than the tuning frequency of the orifice passage, the fluctuation of the pressure in the pressure receiving chamber is absorbed by a small displacement of the movable plate, thereby avoiding a high dynamic spring caused by the anti-resonance action of the orifice passage. Can be done.

  In particular, in the hydraulic pressure absorption mechanism using the displacement of the movable plate described above, the through hole can be reliably covered by the contact of the movable plate with the partition member when the low frequency large amplitude vibration is input. Compared to a movable membrane type hydraulic pressure absorption mechanism, a movable membrane that can be deformed only by a fixed amount is arranged between the pressure receiving chamber and the equilibrium chamber to absorb pressure fluctuations in the pressure receiving chamber based on elastic deformation of the movable membrane. Thus, it is possible to suppress the pressure fluctuation of the pressure receiving chamber when the low frequency large amplitude vibration is input from being unnecessarily absorbed by the hydraulic pressure absorbing mechanism. Therefore, there is an advantage that the fluid flow amount in the orifice passage is sufficiently secured, and an excellent vibration-proofing effect due to the orifice effect can be exhibited against low-frequency large-amplitude vibration.

  However, as a result of investigations by the present inventors, even in a fluid-filled engine mount that combines such an orifice passage and a hydraulic pressure absorption mechanism, the required vibration isolation effect may still not be sufficiently achieved. But I found out anew. This is because it has been found that vibration with a large amplitude may be input in a frequency range higher than the tuning frequency of the orifice passage. For example, in an engine mount for automobiles, in the idling state, unlike the basic idling vibration that accompanies the explosion of the engine, the shock vibration may occur irregularly. The amplitude is often larger than the fundamental vibration. Further, due to the interaction with the external impact load or the like, a large amplitude vibration may be input in a frequency range higher than the tuning frequency of the orifice passage. In this way, when large amplitude vibration is input in a frequency range higher than the tuning frequency of the orifice passage, since the hydraulic pressure absorption mechanism cannot function effectively anymore, the anti-vibration performance of the mount decreases and the vehicle There was a problem that the ride comfort deteriorated.

  Although it is conceivable to increase the displacement allowance of the movable plate so that the function of the hydraulic pressure absorption mechanism is exerted for such a large amplitude vibration in the frequency range exceeding the tuning frequency of the orifice passage, As a result, the fluid pressure absorption action is not desirable, and the pressure fluctuation in the pressure receiving chamber is absorbed even at the time of input of tuning vibration of the orifice passage, and the vibration damping performance due to the orifice effect exerted against the low frequency large amplitude vibration is reduced. It is not an effective measure because it leads to a decline.

Japanese Unexamined Patent Publication No. 57-9340 JP 61-55429 A

  Here, the present invention has been made in the background as described above, and the problem to be solved is to prevent the fluid flow through the orifice passage that is exerted against the low-frequency large-amplitude vibration. Large amplitude vibration in the higher frequency range than the tuning frequency of the orifice passage, while ensuring sufficient vibration performance and hydraulic pressure absorption performance by the movable plate that is exhibited for small amplitude vibration in the middle to high frequency range In the case of an input, a fluid-filled engine for automobiles with a novel structure that can prevent a significant decrease in vibration-proof performance due to the anti-resonant action of the orifice passage, etc., and can exhibit good vibration-proof performance To provide a mount.

  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, the feature of the present invention is that the main rubber elastic body includes a first attachment member attached to one of a power unit of an automobile and a vehicle body, and a second attachment member attached to the other of the power unit and the vehicle body. Connected to form a pressure receiving chamber with a part of the wall made of rubber elastic body and an equilibrium chamber with a part of the wall made of flexible membrane, and uncompressed into the pressure receiving chamber and the equilibrium chamber In addition to enclosing a fluid, an orifice passage that connects the pressure receiving chamber and the equilibrium chamber to each other is provided, and a movable plate arrangement region is formed in a partition member that partitions the pressure reception chamber and the equilibrium chamber, and the movable plate arrangement region is movable. Fluid sealing for automobiles with a hydraulic pressure absorption mechanism that absorbs fluctuations in pressure in the pressure receiving chamber by displacement by placing and arranging plates and providing through holes that allow each side of the movable plate to face the pressure receiving chamber or the equilibrium chamber formula A pressure relief hole that penetrates the wall of the movable plate arrangement area on the side of the equilibrium chamber and communicates the movable plate arrangement area with the equilibrium chamber, at least part of which is a contact surface of the movable plate And a valve body that is displaceable in a contact and separation direction with respect to the opening portion of the pressure relief hole on the equilibrium chamber side, and further biases the valve body. Thus, there is a fluid-filled engine mount for an automobile provided with an urging means for elastically closing the pressure relief hole with a valve body.

  In such a fluid-filled engine mount for automobiles structured in accordance with the present invention, it is movable when a small amplitude vibration is input on the high frequency side rather than the low frequency large amplitude vibration that is the tuning vibration of the orifice passage. Since the plate is displaced in the movable plate disposition region and the pressure fluctuation in the pressure receiving chamber is absorbed, the high dynamic spring due to the anti-resonant action of the orifice passage can be avoided. In particular, in the hydraulic pressure absorption mechanism having such a movable plate structure, the movable plate is brought into contact with the wall portion of the movable plate arrangement region due to a large pressure difference between the pressure receiving chamber and the equilibrium chamber at the input of the low frequency large amplitude vibration. In addition to being restrained and displaced, the through hole can be covered with a movable plate to prevent pressure leakage in the pressure receiving chamber through the through hole. As a result, when the vibration in the tuning frequency range of the orifice passage is input, the fluid pressure absorption (escape) of the pressure receiving chamber by the fluid pressure absorbing mechanism is suppressed, and the fluid flow amount in the orifice passage can be sufficiently secured. A target vibration-proof effect (for example, a high damping effect against engine shake) can be stably obtained.

  Here, a pressure relief hole is formed through the wall on the equilibrium chamber side of the movable plate arrangement region. A valve element is attached to the opening portion of the pressure relief hole on the equilibrium chamber side. By being brought into contact with each other based on the urging force of the urging means, the communication through the pressure relief hole between the movable plate arrangement region and the pressure receiving chamber and the equilibrium chamber is blocked. Therefore, when a large amplitude vibration is input in the tuning frequency range of the orifice passage, or when a small amplitude vibration is input in a higher frequency range, the pressure relief hole is maintained in a shut-off state, Ensuring fluid flow in the orifice passage when low-frequency large-amplitude vibration is input, such as engine shake, and exhibiting fluid resonance, and movable when medium to high-frequency small-amplitude vibration is input Based on the fact that the pressure absorbing function accompanying the displacement of the plate is exhibited, the intended vibration-proof performance is exhibited.

  On the other hand, when a vibration with a large amplitude is input at a frequency higher than the tuning frequency of the orifice passage, the orifice passage is substantially closed and the hydraulic pressure absorption mechanism based on the small displacement of the movable plate is sufficient to absorb the pressure. Cannot be achieved. Under this circumstance, the pressure fluctuation in the pressure receiving chamber becomes large, so that a large pressure induced in the pressure receiving chamber passes through the pressure relief hole to the valve body that covers the pressure relief hole from the outside (equilibrium chamber side). Therefore, the valve element is separated from the opening portion of the pressure relief hole on the equilibrium chamber side against the urging force by the pressure action. As a result, communication through the pressure relief hole between the movable plate arrangement region and the equilibrium chamber is allowed, and the pressure relief hole as a separate passage in which the pressure receiving chamber and the equilibrium chamber pass through the orifice passage and the movable plate. Through a short circuit. Thus, when the pressure in the pressure receiving chamber is released to the equilibrium chamber through this pressure relief hole, large pressure fluctuations in the pressure receiving chamber caused by large amplitude vibrations higher than the tuning frequency of the orifice passage are reduced. Thus, the rigid body of the mount and the avoidance thereof can be avoided, and the vibration isolation performance of the mount can be effectively exhibited.

  In particular, the pressure relief hole is formed in a state in which at least a part thereof is maintained in a communication state by removing the contact surface of the movable plate in the wall portion of the movable plate arrangement region. The movable plate disposing region in FIG. 1, and thus the entire opening portion on the pressure receiving chamber side is prevented from being covered with the movable plate. In other words, the pressure relief hole is always opened with respect to the pressure receiving chamber side, so that the pressure in the pressure receiving chamber is surely exerted on the valve body when large amplitude vibration is input in a high frequency range which is a problem. Thus, a short circuit between the pressure receiving chamber and the equilibrium chamber through the pressure relief hole can be reliably performed. In addition, since the valve body is provided in the opening portion on the equilibrium chamber side of the pressure relief hole, the space for disposing the valve body can be efficiently secured without being limited by the movable plate or the like. Become. In addition, since the fluid flow passage through the pressure relief hole can be secured by using the movable plate arrangement area, the mounting structure becomes complicated and the mount size becomes large when forming the pressure relief hole. Problems such as conversion can be effectively avoided.

  When low-frequency large-amplitude vibration, which is tuning vibration of the orifice passage, a fluid flow action occurs through the orifice passage, and when the vibration is smaller than the tuning frequency on the high-frequency side, the displacement of the movable plate As a result of the function of absorbing the hydraulic pressure by the above-described function, a large pressure is not exerted on the valve body in any vibration input as in the case of the large amplitude vibration input in the above-described high frequency range. As a result, when low-frequency large-amplitude vibration or high-frequency small-amplitude vibration is input, the pressure receiving chamber and the equilibrium chamber are kept disconnected from each other by contact with the opening of the pressure relief hole in the valve body. In addition, an adverse effect on the anti-vibration effect due to the intended orifice effect and the function of the hydraulic pressure absorption mechanism due to the short circuit between the pressure receiving chamber and the equilibrium chamber can be avoided.

  In addition, when a large amplitude vibration in the middle to high frequency range, which is a problem in terms of vibration isolation, is input, the fluid flow resistance in the orifice passage is remarkably increased, and the hydraulic pressure absorbing function accompanying the displacement of the movable plate is also provided. Since it cannot be expected, a large pressure fluctuation is induced in the pressure receiving chamber. The abutting biasing force of the valve body that is brought into contact with the pressure relief hole is adjusted so that the valve body is opened by the action of the large pressure fluctuation. That is, when receiving low-frequency large-amplitude vibration or medium-to-high-frequency small-amplitude vibration, the pressure receiving chamber at the time of vibration is applied to such an extent that the contact state with the opening of the pressure relief hole of the valve body is stably maintained. On the other hand, when a large amplitude vibration in the high frequency range (high frequency large amplitude vibration) is input from the tuning frequency of the orifice passage, the separation from the opening of the pressure relief hole of the valve body is quickly manifested. Thus, the urging force is set to be smaller than the pressure in the pressure receiving chamber during the vibration. Thereby, the shut-off state and the communication state of the pressure relief hole are surely made based on the pressure difference between the target pressure receiving chamber and the equilibrium chamber.

  Therefore, according to the fluid-filled engine mount for automobiles of the present invention, a large-amplitude vibration is generated on the higher frequency side than the tuning frequency of the orifice passage while sufficiently obtaining the vibration-proofing effect by the orifice effect and the hydraulic pressure absorption mechanism. Even when the pressure is input, due to the short circuit between the pressure receiving chamber and the equilibrium chamber through the pressure relief hole, the rigid mounting due to the increase in pressure in the pressure receiving chamber is avoided, and the vibration isolation performance can be improved.

  Further, in the fluid-filled engine mount for automobiles according to the present invention, the elastic protruding member that is supported by the second mounting member and protrudes from the equilibrium chamber side toward the partition member is formed of a rubber elastic body, Both the valve body and the urging means are constituted by the elastic protruding member by elastically abutting the protruding tip portion of the elastic protruding member against the opening on the equilibrium chamber side of the pressure relief hole in the partition member. A structure may be adopted. According to such a structure, the valve body and the urging means can be made into an integral structure, and the working efficiency in manufacturing can be improved.

  Further, in the fluid-filled engine mount for automobiles according to the present invention, the second mounting member has a cylindrical portion, and the first mounting member is arranged apart from one opening side of the cylindrical portion. And is connected by a rubber elastic body, and an annular fixing member is fixed to the outer peripheral edge of the flexible membrane so that the fixing member is on the other opening side of the cylindrical portion of the second mounting member. By fixing, the other opening part of the cylindrical part is covered with a flexible film, and the partition member is assembled inside the cylindrical part of the second mounting member so that the partition member and the main rubber elastic body A structure in which a pressure receiving chamber is formed therebetween and an equilibrium chamber is formed between the partition member and the flexible membrane, while the valve body is disposed on the fixed member may be employed. According to such a structure, the fixing member for fixing the flexible membrane to the second mounting member is also used as the fixing member for the valve body. Therefore, it is possible to reduce the size and the manufacturing cost.

  Further, in the fluid-filled engine mount for automobiles according to the present invention, the wall portion on the equilibrium chamber side of the movable plate disposition region has a larger shape on the outer peripheral side than the movable plate disposed in the movable plate disposition region. In addition, a structure in which a plurality of pressure relief holes are formed in the circumferential direction in the outer peripheral portion of the wall portion on the equilibrium chamber side of the movable plate arrangement region may be employed. According to such a structure, an aspect in which the pressure relief hole is formed in a state in which at least a part thereof is maintained in a communication state by removing the contact surface of the movable plate in the wall portion of the movable plate arrangement region. It can be suitably realized. More preferably, a structure in which a plurality of pressure relief holes are formed in a region deviated to the outer peripheral side so as to be opposed to each other in the radial direction across the movable plate can be adopted, and more preferably, A structure in which the pressure relief holes are formed so as to face each other in a plurality of different radial directions may be employed.

  Further, in the fluid-filled engine mount for automobiles according to the present invention, the displacement of the movable plate within the plane perpendicular to the plate thickness direction is limited in the movable plate disposition region, and the movable plate of the pressure relief hole is used. A structure in which a displacement amount limiting means for the movable plate for preventing the blockage may be employed. According to such a structure, it is possible to more reliably prevent the entire opening portion of the pressure relief hole from being covered with the movable plate. In addition, the desired displacement amount limitation of the movable plate in the hydraulic pressure absorbing mechanism can be realized, and the target orifice effect or the vibration isolation effect based on the hydraulic pressure absorbing action can be obtained more stably.

  Further, in the fluid-filled engine mount for automobiles according to the present invention, the orifice passage for shaking tuned to a low frequency region corresponding to the engine shake is adopted as the orifice passage, and the main component of the engine explosion in the idling state is adopted. A structure may be adopted in which the valve body is opened against the urging force by the urging means when inputting large amplitude vibration generated in a lower frequency range than the steady idling fundamental vibration caused by .

  That is, when the present inventor diligently examined the vibration isolation characteristics of the engine mount for automobiles, when idling, a large amplitude vibration is generated in a lower frequency range than the idling basic vibration (steady vibration generated due to the engine explosion). It has been found that this may occur irregularly, and this is a major problem in vehicle comfort. Thus, in the fluid-filled engine mount for automobiles of the present invention, the vibration-proofing effect against the low-frequency large-amplitude vibration caused by the orifice passage, and the small-to-high-frequency vibration in the middle to high frequency accompanying the displacement of the movable plate. The anti-vibration effect is exhibited effectively, and the stiffness of the mount spring that accompanies a large increase in pressure in the pressure-receiving chamber due to the opening of the valve element against large-amplitude vibration exerted under idling conditions. Can be avoided and a good ride can be achieved.

  Hereinafter, in order to clarify the present invention more specifically, an embodiment of the present invention will be described in detail with reference to the drawings. First, FIG. 1 shows an automobile engine mount 10 as an embodiment of the fluid-filled engine mount for automobiles of the present invention. In this automobile engine mount 10, a first mounting bracket 12 as a first mounting member and a second mounting bracket 14 as a second mounting member are elastically connected to each other by a main rubber elastic body 16. The first mounting bracket 12 is attached to a vehicle power unit (not shown), and the second mounting bracket 14 is attached to a vehicle body (not shown) of the vehicle, so that the power unit is protected from the vehicle body via the vehicle engine mount 10. It is designed to be supported.

  In FIG. 1, the state of the vehicle engine mount 10 alone before being mounted on the vehicle is shown, but in the mounted state on the vehicle, the shared support load of the power unit is in the mount axis direction (in FIG. 1), the first mounting bracket 12 and the second mounting bracket 14 are displaced toward each other in the mount axis direction, and the main rubber elastic body 16 is elastically deformed. In addition, under such a mounted state, main vibrations to be vibrated are input substantially in the mount axis direction. In the following description, unless otherwise specified, the vertical direction refers to the vertical direction in FIG.

  More specifically, the first mounting member 12 has a substantially truncated truncated cone shape or a cylindrical shape with a small diameter. A screw hole 18 that opens to the upper end surface is formed in the central portion in the direction perpendicular to the axis of the first mounting bracket 12, and a member on the power unit side (not shown) is screwed and fixed to the screw hole 18 via a fixing bolt. Thus, the first mounting member 12 is attached to the power unit.

  Further, the second mounting bracket 14 has a large-diameter, generally cylindrical shape, and the substantially entire structure forms a cylindrical portion. An annular step 20 is formed at the lower end of the second mounting bracket 14 and extends outward in the direction perpendicular to the axis. A large-diameter ring is formed on the outer peripheral edge of the step 20 downward. A cylindrical caulking tube portion 22 is projected. The second mounting bracket 14 is attached to a vehicle body side member via a bracket member (not shown). The first mounting bracket 12 and the second mounting bracket 14 are disposed on the same central axis, and the first mounting bracket 12 is located above the upper opening of the second mounting bracket 14. It is positioned at a predetermined distance. A main rubber elastic body 16 is interposed between the first mounting bracket 12 and the second mounting bracket 14.

  The main rubber elastic body 16 is a thick rubber elastic body having a substantially truncated truncated cone shape as a whole, and the substantially entire portion excluding the upper end portion of the first mounting member 12 is embedded in the upper end portion thereof. The entire inner peripheral surface of the second mounting bracket 14 excluding the step portion 20 and the caulking tube portion 22 is vulcanized and bonded to the outer peripheral surface of the main rubber elastic body 16. Yes. In short, the main rubber elastic body 16 is formed as an integrally vulcanized molded product including the first mounting bracket 12 and the second mounting bracket 14, whereby the first mounting bracket 12 and the second mounting bracket are formed. 14 is connected by a main rubber elastic body 16, and one opening (in FIG. 1) of the second mounting bracket 14 is fluid-tightly closed by the main rubber elastic body 16. In addition, a substantially inverted mortar-shaped large-diameter recess 24 that opens downward is formed on the lower end surface of the main rubber elastic body 16. Further, the main rubber elastic body 16 is integrally formed with a thin seal rubber layer 26 extending downward from the opening edge of the large-diameter recess 24, and the lower end portion or the step portion 20 of the second mounting bracket 14. It is deposited on the inner peripheral surface.

  A partition member 28 is assembled to such an integrally vulcanized molded product of the main rubber elastic body 16. 2 to 4, the partition member 28 has a substantially circular block shape as a whole, and is formed using a hard member made of a metal material, a synthetic resin material, or the like. The partition member 28 includes a partition member main body 30 and a lid member 32.

  The partition member main body 30 has a substantially circular block shape, and has a circular concave upper recess 34 that opens from the middle portion in the axial direction (up and down in FIGS. 1 and 3) in the thickness direction to the upper end surface and the lower end surface. And a lower recess 36 is formed. In the present embodiment, the upper recess 34 and the lower recess 36 are formed in the central portion in the direction perpendicular to the axis of the partition member main body 30, and the shapes and sizes of the two recesses 34, 36 are substantially the same. ing. As a result, a substantially central portion in the axial direction of the partition member main body 30 between the bottom portions of the two recesses 34 and 36 is a disc-shaped central bottom portion 38. In other words, the outer peripheral portion of the partition member main body 30 is the outer cylindrical portion 40 having a thin and large-diameter substantially cylindrical shape, and the central bottom portion 38 extends in the direction perpendicular to the axis inside the axial central portion of the outer cylindrical portion 40. The upper inner peripheral surface of the outer cylindrical portion 40 sandwiching the central bottom portion 38 and the upper end surface of the central bottom portion 38 cooperate to form the upper recess 34 and the outer cylindrical portion. The lower inner peripheral surface of the central bottom portion 38 and the lower end surface of the central bottom portion 38 cooperate with each other to form a lower recess 36. In the present embodiment, the outer peripheral surface of the outer cylindrical portion 40 has a tapered shape in which the diameter dimension gradually decreases downward.

  A communication window 42 is formed in a lower portion of the outer cylinder portion 40 of the partition member body 30 with the central bottom portion 38 interposed therebetween. The communication window 42 is formed so as to penetrate in a direction perpendicular to the axis (left and right in FIGS. 1 and 3), which is the thickness direction of the outer cylindrical portion 40, and has a notch shape that opens at the lower end surface of the outer cylindrical portion 40. It extends in the circumferential direction with a predetermined length (in this embodiment, a little less than a quarter of the outer cylindrical portion 40). Further, in the outer cylindrical portion 40, the outer peripheral surface adjacent to one end portion (downward in FIG. 4) of the communication window 42 in the circumferential direction protrudes slightly outward in the direction perpendicular to the axis and has a slight length in the circumferential direction. An extending substantially arc-shaped partitioning protrusion 44 is integrally formed. The protruding front end surface of the partition projection 44 has an arc shape that is inclined with respect to the axial direction and extends in the circumferential direction, like the tapered outer peripheral surface of the outer cylindrical portion 40. Further, the outer cylinder portion 40 is provided with a plurality of fixing holes 46 for fixing bolts, rivets and the like at an upper end surface with an appropriate interval in the circumferential direction.

  A plurality of first through holes 48 and second through holes 50 as through holes are formed through the central bottom 38 of the partition member main body 30. The first through holes 48 have a substantially semicircular shape, and a plurality (eight in the present embodiment) are provided at equal intervals around the central portion in the direction perpendicular to the axis of the central bottom 38. The linear edges of the first through holes 48 are spaced apart from each other on one side in the circumferential direction, and the arc-shaped edges of the first through holes 48 are arranged on the other side in the circumferential direction. They are spaced apart so that they face each other. Further, a plurality (eight in the present embodiment) of second through holes 50 are provided at equal intervals in the circumferential direction outside the first through holes 48 in the direction perpendicular to the axis. The 2nd through-hole 50 is exhibiting the substantially fan shape from which a circumferential direction dimension becomes large gradually toward an axial perpendicular direction outward.

  On the other hand, the lid member 32 has a thin and substantially disk shape, and its outer diameter dimension is larger than the outer diameter dimension of the upper end portion of the outer cylindrical portion 40 which is the maximum outer diameter dimension of the partition member body 30. It is big enough. In addition, a circular positioning hole 52 is provided in the center portion of the lid member 32 in the direction perpendicular to the axis. Further, a communication hole 54 extending in an arc shape in the circumferential direction is provided through the outer peripheral side in the vicinity of the outer peripheral edge portion of the lid member 32. Furthermore, a circular insertion hole 56 is provided at a position corresponding to each fixing hole 46 in the outer cylindrical portion 40 of the partition member body 30 on the outer peripheral side avoiding the communication hole 54 of the lid member 32. .

  Further, a plurality of first through-holes 58 and second through-holes 60 as through-holes are provided in the axially perpendicular middle portion of the lid member 32 on the outer peripheral side of the positioning hole 52 and on the inner peripheral side of the insertion hole 56. It is formed through. The first through-holes 58 have a substantially arc shape, and a plurality (four in the present embodiment) are provided around the positioning holes 52 of the lid member 32 at equal intervals. Further, a plurality (eight in this embodiment) of second through holes 60 are provided at equal intervals in the circumferential direction outside the first through holes 58 in the direction perpendicular to the axis. Similar to the second through hole 50 of the partition member main body 30, the second through hole 60 has a substantially fan shape whose circumferential dimension gradually increases outward in the direction perpendicular to the axis.

  The partition member body 30 and the lid member 32 are aligned in the circumferential direction so that all the insertion holes 56 of the lid member 32 are positioned on all the fixing holes 46 in the outer cylindrical portion 40 of the partition member body 30. In addition, the upper end portion of the outer cylindrical portion 40 and the circumferential portion in which each insertion hole 56 in the lid member 32 is arranged to pass through are overlapped in the axial direction, and a fixing member such as a bolt or a rivet is passed through each insertion hole 56 to each fixing hole. 46 is fixed. Thereby, the partition member main body 30 and the lid member 32 are fixed in a form in which they are positioned substantially concentrically with each other, and the partition member 28 is configured.

  In such a partition member 28, the partition projection 44 of the partition member main body 30 is positioned inward in the direction perpendicular to the axis from the outer peripheral edge of the lid member 32, and one side in the circumferential direction sandwiching the partition projection 44 The communication window 42 of the partition member main body 30 is positioned on the upper side (in FIG. 4), and the communication hole 54 of the lid member 32 is positioned on the other circumferential side (the lower side in FIG. 4) across the partition member 28. It has been. Further, the communication hole 54 is covered with the upper end portion of the outer cylindrical portion 40 of the partition member main body 30 from the inner peripheral edge portion to the middle portion in the axis-perpendicular direction, so that the opening portion of the communication hole 54 to the lower end surface of the lid member 32 Is a portion extending from the intermediate portion in the direction perpendicular to the axis of the communication hole 54 to the outer peripheral edge. Further, circumferential end portions of the first through holes 48 of the partition member body 30 and the first through holes 58 of the lid member 32, and the second through holes 50 of the partition member body 30 and the second through holes of the lid member 32. The holes 60 are positioned so as to project in the axial direction.

  Further, the opening portion of the upper recess 34 of the partition member main body 30 is covered and covered inside the portion of the lid member 32 that is overlapped with the outer cylindrical portion 40 of the partition member main body 30, so that the inside of the partition member 28 is formed. Is an accommodation space as a movable plate disposing region extending in a substantially constant circular cross section in the axial direction in cooperation with the upper end surface of the central bottom portion 38, the inner peripheral surface of the outer cylindrical portion 40, and the lower end surface of the lid member 32. 62 is formed. That is, the top wall portion of the housing space 62 is formed by the cover portion of the upper recess 34 in the lid member 32, and the bottom wall portion of the housing space 62 is formed by the central bottom portion 38 of the partition member body 30. In addition, the peripheral wall portion of the accommodation space 62 is constituted by the peripheral wall portion of the upper recess 34 of the partition member main body 30. Here, before the opening portion of the upper recess 34 of the partition member main body 30 is covered with the lid member 32 to form the accommodation cavity 62, the elastic rubber plate 64 as a movable plate is placed in the upper recess 34. The elastic rubber plate 64 is accommodated in the accommodating space 62 by configuring the accommodating space 62 as described above.

  The elastic rubber plate 64 is made of a rubber elastic material, and has a thick and substantially disk shape as a whole. In particular, in the present embodiment, the elastic rubber plate 64 is formed as a central disc portion 66 from the central portion in the direction perpendicular to the axis to the outer peripheral portion or the vicinity of the outer peripheral portion. It has a thick and thick disk shape. Further, in the outer peripheral annular portion 68 that is positioned away from the central disc portion 66 in the direction perpendicular to the axis and constitutes the outer peripheral edge and the outer peripheral portion of the elastic rubber plate 64, the thickness dimension is the outer direction perpendicular to the axis. It is gradually getting smaller toward. A groove-like portion that is open at both axial end surfaces and extends continuously in the circumferential direction is formed in the middle portion of the outer circumferential annular portion 68 in the direction perpendicular to the axis. The peripheral portion has a rib shape that protrudes on both sides in the axial direction from the intermediate portion in the direction perpendicular to the axis of the outer peripheral annular portion 68 and extends continuously in the circumferential direction. In addition, the outer peripheral annular portion 68 may have a shape that spreads flatly on the outer peripheral circle of the elastic rubber plate 64, but in the present embodiment, the outer peripheral circle of the elastic rubber plate 64 rises to one side in the thickness direction. The undulation (undulation) is provided in the circumferential direction so that the portion and the portion that swells on the other side in the thickness direction are alternately expressed in the circumferential direction. In addition, the annular portion of the elastic rubber plate 64 between the central disc portion 66 and the outer peripheral annular portion 68 is sufficiently thicker than the central disc portion 66 and the outer peripheral annular portion 68. The thin plate-like portion 70 is reduced, and the central disc portion 66 and the outer peripheral annular portion 68 are connected via the thin plate-like portion 70. Note that the thin plate-like portion 70 may have a flat shape as a whole like the central disc portion 66, or may have a curved shape that undulates in the circumferential direction like the outer peripheral annular portion 68.

  Further, a substantially cylindrical positioning protrusion 72 integrally formed with the elastic rubber plate 64 is projected from the upper end surface of the central portion in the direction perpendicular to the axis of the central disk portion 66 of the elastic rubber plate 64. Further, an elastic protrusion 74 integrally formed with the elastic rubber plate 64 is projected from the lower end surface of the central disc portion 66 of the elastic rubber plate 64. The elastic protrusion 74 of the present embodiment is constituted by a protrusion that extends in the circumferential direction in an axial cross section such as a semicircular shape or a mountain shape, and a plurality of elastic protrusions 74 that are concentrically spaced from the central disk portion 66 in the direction perpendicular to the axis. Although it is provided, for example, it may be constituted by a protruding portion formed of a small protrusion having a tapered shape such as a hemispherical shape or a mountain shape, and a plurality of the protruding portions may be provided on the central disk portion 66 at a distance. Moreover, it is also possible to provide an elastic protrusion on the upper end surface of the central disk portion as necessary.

  In particular, in the present embodiment, the thickness dimension of the elastic rubber plate 64 extending in the axial direction of the central disk portion 66 is represented by the distance between the opposed surfaces in the axial direction of the central bottom portion 38 of the partition member main body 30 and the lid member 32. The inner cavity 62 is slightly smaller than the inner dimension in the axial direction. Further, the outer diameter dimension of the elastic rubber plate 64 is made smaller by a predetermined amount than the inner dimension in the direction perpendicular to the axis of the accommodation cavity 62 represented by the inner diameter dimension of the upper recess 34 of the partition member body 30. Yes.

  The elastic rubber plate 64 is accommodated in the accommodation space 62, and the positioning protrusion 72 of the elastic rubber plate 64 is inserted into the positioning hole 52 of the lid member 32. Are positioned in a direction perpendicular to the axis in a form positioned substantially concentrically with respect to the axis. Further, the upper end surface of the central disc portion 66 of the elastic rubber plate 64 is in contact with the lid member 32 constituting the top wall portion of the accommodation space 62, and protrudes from the lower end surface of the central disc portion 66. The elastic protrusion 74 is in contact with the central bottom 38 while being pre-compressed between the central bottom 38 and the top wall (lid member 32) of the partition member main body 30 constituting the bottom wall of the housing space 62. As a result, the displacement of the elastic rubber plate 64 in the direction perpendicular to the axis is limited by the abutting action of the elastic protrusion 74 against the central bottom 38, and the elastic protrusion 74 is elastic based on the axial deformation displacement of the elastic protrusion 74. The rubber plate 64 is allowed to move in the axial direction. In short, in the present embodiment, the displacement amount limiting means in the direction perpendicular to the axis of the elastic rubber plate 64 is engaged in the direction perpendicular to the axis by inserting the positioning projection 72 of the elastic rubber plate 64 into the positioning hole 52 of the lid member 32. It includes a stop mechanism and an abutment mechanism in which an elastic protrusion 74 protruding from the elastic rubber plate 64 abuts against the wall portion (central bottom portion 38) of the accommodation space 62 with pre-compression.

  Under such a state that the elastic rubber plate 64 is accommodated in the accommodation space 62, the outer diameter of the elastic rubber plate 64 is made smaller than the internal dimension in the direction perpendicular to the axis of the accommodation space 62. Between the axially perpendicular facing surfaces of the peripheral wall portion of the upper recess 34 of the partition member main body 30 constituting the peripheral wall portion of the housing space 62 and the outer peripheral edge portion of the elastic rubber plate 64 (outer annular portion 68), A gap is provided over the entire area. As is clear from this, a disk in which the central bottom portion 38 of the partition member main body 30 constituting the bottom wall portion of the housing space 62 is slightly larger than the elastic rubber plate 64 disposed in the housing space 62. It is made into a shape. The upper and lower end surfaces of the central disc portion 66 of the elastic rubber plate 64 are opposed to the first through hole 58 of the lid member 32 and the first through hole 48 of the partition member body 30 in the axial direction, and are elastic. The upper and lower end surfaces of the thin plate portion 70 of the rubber plate 64 are opposed to the second through hole 60 of the lid member 32 and the second through hole 50 of the partition member main body 30 in the axial direction. Further, the axially perpendicular inner portion of the outer annular portion 68 of the elastic rubber plate 64 is axially opposed to the axially perpendicular outer portions of the second through holes 50 and 60 of the partition member main body 30 and the lid member 32. ing. Further, in the circumferential annular portion 68 having a shape that undulates in the circumferential direction, the tip of the portion that rises upward in the axial direction is in contact with the lid member 32, while the tip of the portion that rises downward in the axial direction is the partition member main body 30. Is brought into contact with the central bottom 38 of the main body.

  The partition member 28 in which the elastic rubber plate 64 is accommodated is inserted in the axial direction from the lower opening of the second mounting bracket 14 in the integrally vulcanized molded product of the main rubber elastic body 16, and the lid member in the partition member 28. The outer peripheral portion of 32 is fitted into the caulking tube portion 22 of the second mounting bracket 14 and overlapped with the step portion 20 of the second mounting bracket 14 in the axial direction. In addition, a diaphragm 76 as a flexible film is assembled to the lower opening of the second mounting bracket 14.

  The diaphragm 76 is formed of a thin circular rubber film having sufficient slackness. A fixing bracket 78 as a fixing member is vulcanized and bonded to the outer peripheral edge of the diaphragm 76. The fixing bracket 78 is made of a press-molded product having a large-diameter, generally annular shape as a whole, and has a cylindrical wall portion 80 having a large-diameter substantially cylindrical shape and a radial direction (a direction perpendicular to the axis) from the upper end portion of the cylindrical wall portion 80. An outer flange-like portion 82 that extends outward and an inner flange-like portion 84 that extends radially inward from the lower end portion of the cylindrical wall portion 80 are configured. In particular, the cylindrical wall portion 80 has a larger diameter than the outer diameter dimension of the partition member main body 30 and has a tapered cylindrical shape in which the diameter dimension gradually decreases downward. By being inclined with respect to the mount axis direction at substantially the same taper angle as the surface, the shape corresponds to the outer peripheral surface of the partition member main body 30. Further, the outer diameter of the outer flange-shaped portion 82 of the fixing bracket 78 is substantially the same as the outer diameter of the lid member 32. Further, the inner diameter dimension of the inner flange-shaped portion 84 of the fixing bracket 78 is made smaller than the outer diameter dimension of the central bottom portion 38 of the partition member main body 30.

  The outer peripheral edge portion of the diaphragm 76 is vulcanized and bonded to the inner peripheral edge portion of the inner flange-shaped portion 84 of the fixing bracket 78. Further, a thin seal rubber layer 86 integrally formed with the diaphragm 76 is coated on the inner peripheral surface of the outer flange-shaped portion 82, the inner and outer peripheral surfaces of the cylindrical wall portion 80, and the upper and lower end surfaces of the inner flange-shaped portion 84 by vulcanization molding. It is worn. That is, the diaphragm 76 and the seal rubber layer 86 are formed as an integrally vulcanized molded product including the fixing bracket 78.

  The fixing bracket 78 of the diaphragm 76 is inserted in the axial direction from the lower opening of the second mounting bracket 14, and the outer flange-shaped portion 82 of the fixing bracket 78 is fitted into the caulking tube portion 22 of the second mounting bracket 14. And overlapped with the outer peripheral portion of the lid member 32 in the axial direction. In addition, the intermediate portion in the direction perpendicular to the axis of the inner flange-shaped portion 84 of the fixing bracket 78 is connected to the lower end portion of the outer cylindrical portion 40 of the partition member body 32 via a seal rubber layer 86 attached to the upper end surface of the inner flange-shaped portion 84. And are superposed in the axial direction.

  Thus, the caulking tube portion 22 of the second mounting bracket 14 is caulked, and the outer peripheral portion of the lid member 32 and the outer flange-shaped portion 82 of the fixing bracket 78 are caulked and fixed to the second mounting bracket 14. Accordingly, the partition member 28 and the diaphragm 76 are fixedly assembled to the second mounting bracket 14 so as to cover the lower opening of the second mounting bracket 14.

  In addition, as the partition member 28 and the fixing bracket 78 are caulked and fixed to the second mounting bracket 14, the seal rubber layer 26 attached to the second mounting bracket 14 is connected to the second mounting bracket 14 and the lid. While being compressed and deformed between the members 32, the opening portion of the large-diameter recess 24 of the main rubber elastic body 16 is fluid-tightly sealed by the partition member 28 by being superimposed on the outer peripheral portion of the lid member 32. Yes. Further, the seal rubber layer 86 attached to the upper end surface of the inner flange-shaped portion 84 of the fixing bracket 78 is compressed and deformed between the outer tubular portion 40 and the inner flange-shaped portion 84 of the partition member main body 30, and the outer tubular portion. By overlapping the lower end portion of 40, the region defined by the lower recess 36, the diaphragm 76, and the inner flange-shaped portion 84 of the partition member main body 30 is fluid-tightly sealed.

  Thereby, on one side in the axial direction (upward in FIG. 1) sandwiching the partition member 28, there is a wall portion in the region where the large-diameter recess 24 of the main rubber elastic body 16 is closed by the partition member 28. A pressure receiving chamber 88 is formed, the portion of which is constituted by the main rubber elastic body 16 and in which a pressure fluctuation is generated based on elastic deformation of the main rubber elastic body 16 when vibration is input. In addition, on the other side in the axial direction on the other side of the partition member 28 (downward in FIG. 1), a region defined by the lower recess 36, the diaphragm 76, and the inner flange-shaped portion 84 of the partition member main body 30 includes a wall. A part of the portion is constituted by a diaphragm 76, and an equilibrium chamber 90 is formed in which volume change is easily allowed based on elastic deformation of the diaphragm 76. The pressure receiving chamber 88 and the equilibrium chamber 90 are filled with an incompressible fluid. For example, water, alkylene glycol, polyalkylene glycol, silicone oil, or the like is employed as the incompressible fluid to be enclosed. In order to effectively obtain a vibration isolation effect based on a fluid action such as a resonance action of the fluid. It is desirable to employ a low viscosity fluid of 0.1 Pa · s or less. Further, the incompressible fluid is sealed in the pressure receiving chamber 88 or the equilibrium chamber 90, for example, the partition member 28 for the integrally vulcanized molded product of the main rubber elastic body 16 including the first and second mounting brackets 12 and 14. And the diaphragm 76 are preferably realized by performing the assembly in an incompressible fluid.

  Further, between the cover member 32 and the axially facing surface of the inner flange-shaped portion 84 of the fixing bracket 78, the outer cylindrical portion 40 of the partition member main body 30 and the cylindrical wall portion 80 of the fixing bracket 78 are separated by a predetermined distance in the direction perpendicular to the axis. Are opposed to each other. In addition, the outer peripheral surface of the partition projection 44 projecting from the outer cylindrical portion 40 is superimposed on the surface of the seal rubber layer 86 that is attached to the inner peripheral surface of the cylindrical wall portion 80 of the fixing bracket 78. As the partition member 28 and the fixing bracket 78 are caulked and fixed to the second mounting bracket 14, the seal rubber layer 86 attached to the upper end surface of the inner flange-shaped portion 84 of the fixing bracket 78 as described above, While being compressed and deformed between the outer cylindrical portion 40 and the inner flange-shaped portion 84 of the partition member main body 30, it is superimposed on the lower end portion of the outer cylindrical portion 40, and the inner peripheral edge portion of the outer flange-shaped portion 82 in the fixing bracket 78. Or the seal rubber layer 86 attached to the upper end portion of the cylindrical wall portion 80 is overlapped with the outer peripheral portion of the lid member 32 while being compressed and deformed between the second mounting bracket 14 and the outer peripheral portion of the lid member 32. Yes. Further, a part of the circumference of the seal rubber layer 86 attached to the inner peripheral surface of the cylindrical wall portion 80 of the fixing bracket 78 is between the partition projection 44 and the fixing bracket 78 protruding from the outer cylindrical portion 40. It is superimposed on the partition projection 44 while being compressed and deformed. Note that, in the cutout communication window 42 formed in the outer cylindrical portion 40 of the partition member main body 30, the lower end opening is covered with the inner flange-shaped portion 84 of the fixing bracket 78 through the seal rubber layer 86. However, the form in which the communication window 42 penetrates the outer cylindrical portion 40 in the direction perpendicular to the axis is maintained.

  Thereby, between the outer side cylinder part 40 of the partition member main body 30 and the axially perpendicular direction opposing surface of the cylindrical wall part 80 of the fixing metal 78 between the axial direction opposing surfaces of the lid member 32 and the inner flange-shaped part 84 of the fixing metal 78, An annular region extending in the circumferential direction is closed fluid-tightly, and a part of the circumference of the annular region is partitioned fluid-tightly by a partition projection 44. The annular region constitutes an orifice passage 92 that extends the outer peripheral portion of the partition member 28 in the circumferential direction with a length of a little less than one round. One end portion of the orifice passage 92 is connected to the pressure receiving chamber 88 through the communication hole 54 formed in the lid member 32, and the other end portion of the orifice passage 92 is connected to the outer cylinder of the partition member main body 30. By being connected to the equilibrium chamber 90 through the communication window 42 formed in the section 40, fluid flow through the orifice passage 92 between the pressure receiving chamber 88 and the equilibrium chamber 90 is allowed.

  In particular, in the present embodiment, the anti-vibration effective for the low frequency region vibration of about 10 Hz corresponding to the engine shake or the like based on the resonance action of the fluid flowing through the orifice passage 92, for example. It is tuned so that the effect (high attenuation effect) is exhibited. The tuning of the orifice passage 92 is performed by, for example, the body rubber elastic body corresponding to the rigidity of the wall springs of the pressure receiving chamber 88 and the equilibrium chamber 90, that is, the amount of pressure change required to change the chambers 88 and 90 by a unit volume. 16 and the diaphragm 76 can be performed by adjusting the passage length and passage cross-sectional area of the orifice passage 92 while taking into account the characteristic values based on the respective elastic deformation amounts, such as the diaphragm 76 and the diaphragm 76, and are generally transmitted through the orifice passage 92. The frequency at which the phase of the pressure fluctuation changes and becomes substantially resonant can be grasped as the tuning frequency of the orifice passage 92.

  Further, in the elastic rubber plate 64 accommodated and disposed in the accommodation space 62 of the partition member 28, the first and second through holes 58, 60 in the lid member 32 with respect to one surface (upper in FIG. 1). The pressure of the pressure receiving chamber 88 is exerted through the first and second through holes 48 and 50 in the central bottom 38 of the partition member main body 30 with respect to the other surface (lower side in FIG. 1). The pressure of the equilibrium chamber 90 is exerted through. Thereby, based on the pressure difference between the pressure receiving chamber 88 and the equilibrium chamber 90, the central disc portion 66 is displaced in the axial direction by the deformation displacement of the elastic protrusion 74 of the elastic rubber plate 64, or the elastic rubber plate 64 has a thin plate shape. The part 70 and the outer annular part 68 are deformed and displaced. Thereby, the axial deformation of the elastic rubber plate 64 in the accommodation space 62 can be realized, and the pressure fluctuation of the pressure receiving chamber 88 is absorbed based on the deformation. As is clear from this, the hydraulic pressure absorbing mechanism that absorbs the pressure fluctuation of the pressure receiving chamber 88 by the displacement is formed in the elastic rubber plate 64, the accommodation space 62, the lid member 32, and the partition member main body 30. The first and second through holes 48, 50, 58, 60 are included.

  The resonance frequency of the fluid that flows between the pressure receiving chamber 88 and the equilibrium chamber 90 through the first and second through holes 48, 50, 58, 60 in accordance with the displacement of the elastic rubber plate 64 is higher than the idling fundamental vibration. It is designed so as to be in a high frequency range, and more preferably designed to be in a higher frequency range such as traveling noise. As a result, the anti-resonance action of the fluid flow caused by the displacement of the elastic rubber plate 64 is avoided, and the hydraulic pressure absorbing function is exhibited against small amplitude vibrations in a sufficiently wide frequency range. However, the resonance frequency of the fluid that is caused to flow between the pressure receiving chamber 88 and the equilibrium chamber 90 through the first and second through holes 48, 50, 58, 60 in accordance with the displacement of the elastic rubber plate 64 is specifically damped. You may tune to power vibration frequency (for example, idling vibration frequency etc.). As a result, it is possible to obtain a more effective anti-vibration effect against the vibration in the tuning frequency range by using the resonance action of the fluid.

  Note that the upper end surface of the central disc portion 66 of the elastic rubber plate 64 is brought into contact with the lower end surface of the lid member 32 around the first through hole 58 under the accommodation state of the elastic rubber plate 64 in the accommodation space 62. In addition, the lower end surface of the central disc portion 66 is brought into contact with the upper end surface around the first through hole 48 of the central bottom portion 38 of the partition member body 30 through the elastic protrusion 74, or a slight gap is formed. The first through holes 48 and 58 of the lid member 32 and the partition member main body 30 are substantially covered with the central disk portion 66 by being opposed to each other. On the other hand, the thin plate-like portion 70 of the elastic rubber plate 64 positioned between the second through-hole 60 of the lid member 32 and the second through-hole 50 of the center bottom portion 38 is located in the intermediate portion in the axial direction of the accommodation space 62. By being positioned, neither the lid member 32 nor the central bottom portion 38 is in contact with each other, and is positioned between the second through hole 60 of the lid member 32 and the second through hole 50 of the central bottom portion 38 in the axial direction. The outer annular portion 68 of the elastic rubber plate 64 to be fastened has a wavy shape in the circumferential direction, so that the portion that contacts the lower end surface around the second through hole 60 of the lid member 32 and the second of the center bottom portion 38. The portions in contact with the upper end surface around the through hole 50 are alternately positioned in the circumferential direction. Thereby, reduction of the contact sound of the elastic rubber plate 64 is achieved.

  Therefore, in the central bottom portion 38 of the partition member main body 30 constituting the wall portion on the balance chamber 90 side of the accommodation space 62, there is a pressure relief on the outer peripheral portion positioned outward in the direction perpendicular to the axis from the elastic rubber plate 64. A short-circuit hole 94 is formed as a through hole. The short-circuiting hole 94 of the present embodiment has a substantially circular shape with a small cross section in the direction perpendicular to the axis, and is substantially constant in the thickness direction (up and down in FIGS. 1 and 3) of the central bottom portion 38 parallel to the mount axis direction. It extends continuously in the circular cross section, and is opened at the upper end surface facing the accommodation space 62 and the lower end surface facing the equilibrium chamber 90 in the central bottom 38. In addition, a plurality (eight in this embodiment) of short-circuit holes 94 are formed at equal intervals in the circumferential direction in the outer peripheral portion of the central bottom portion 38 that is axially perpendicular to the second through-hole 50. ing.

  In particular, in the present embodiment, the short-circuit holes 94 are positioned outward in the direction perpendicular to the axis from the elastic rubber plate 64 accommodated and disposed in the accommodation space 62, and the positioning protrusion 72 of the elastic rubber plate 64. The displacement of the elastic rubber plate 64 in the direction perpendicular to the axis is restricted by the displacement amount limiting means in the direction perpendicular to the axis of the elastic rubber plate 64 as described above, such as by inserting the lid member 32 into the positioning hole 52. Accordingly, the opening portion of the short-circuit hole 94 to the accommodation space 62 is prevented from being covered with the elastic rubber plate 64, and the short-circuit hole 94 is always opened to the accommodation space 62. . In short, the plurality of short-circuit holes 94 are formed in a state in which the contact state of the elastic rubber plate 64 at the center bottom portion 38 is removed and the communication state with the accommodation space 62 is maintained.

  Further, a rubber valve body 96 as an elastic projecting member is provided on the inner flange portion 84 of the fixing metal fitting 78 of the diaphragm 76. The rubber valve body 96 of the present embodiment is made of a rubber elastic material integrally formed with the diaphragm 76 and the seal rubber layer 86, and each short-circuiting hole in the center bottom portion 38 of the partition member body 30 from the inner peripheral edge portion of the inner flange-shaped portion 84. It protrudes toward 94 and has a substantially cylindrical shape with a small diameter extending in the balance chamber 90 in the vertical direction. That is, the number of the rubber valve bodies 96 projecting from the inner flange-shaped portion 84 of the fixing bracket 78 corresponding to the short-circuit holes 94 of the partition member body 30 (eight in the present embodiment). Since they are provided at positions corresponding to the respective short-circuit holes 94 of the main body 30, they are arranged at equal intervals in the circumferential direction. Further, as shown in FIG. 4, the protruding tip surface of the rubber valve body 96 has a substantially circular shape, and the outer diameter size of the protruding tip surface is larger than the outer diameter size of the short-circuit hole 94. Has also been enlarged.

  In such a rubber valve body 96, as the partition member 28 and the fixing bracket 78 are caulked and fixed to the second mounting bracket 14, the protruding front end surface of the rubber valve body 96 is located at the center bottom of the partition member body 30. 38 is in contact with the lower end surface of the central bottom portion 38 around the opening portion so as to cover the opening surface on the equilibrium chamber 90 side of the short-circuiting hole 94 that opens to the lower end surface of 38. Further, the rubber valve body 96 is compressed and deformed between the inner flange-shaped portion 84 of the fixing bracket 78 and the central bottom portion 38 of the partition member body 30, so that the protruding front end surface of the rubber valve body 96 is centered with a precompression force. The bottom portion 38 is brought into contact with the opening portion of the short-circuit hole 94 on the equilibrium chamber 90 side. In particular, under such a contact state, the rubber valve body 96 is mounted in the mount axial direction from the base end portion vulcanized and bonded to the inner flange-shaped portion 84 of the fixing bracket 78 toward the projecting distal end portion that contacts the center bottom portion 38. Are gradually inclined outward in the direction perpendicular to the axis. The inclined shape of the rubber valve body 96 may be provided from the state before the fixing bracket 78 is attached to the second mounting bracket 14, or the fixing bracket 78 may be attached to the second mounting bracket 14. The rubber valve element 96 extending in the axial direction may be elastically deformed in contact with the central bottom portion 38 in a state before being attached.

  That is, the protruding tip portion of the rubber valve body 96 has the elasticity of the rubber valve body 96 deformed by pre-compression between the central bottom portion 38 of the partition member main body 30 and the axially opposed surface of the inner flange-shaped portion 84 of the fixing bracket 78. Utilizing it, it is urged from the inner flange-shaped portion 84 toward the central bottom portion 38 and is brought into contact with the opening portion of the short-circuit hole 94 in the central bottom portion 38. As a result, the opening portion on the equilibrium chamber 90 side of each short-circuit hole 94 in the central bottom portion 38 is elastically closed by the rubber valve body 96, and passes through the short-circuit hole 94 between the accommodation space 62 and the equilibrium chamber 90. Communication is blocked. As apparent from the above description, in this embodiment, the valve body provided at the opening portion of the short-circuiting hole 94 on the equilibrium chamber 90 side, and the valve body is energized to make the short-circuiting hole 94 a valve body. The urging means for elastically closing each is constituted by a rubber valve body 96.

  Here, the pressure exerted on the rubber valve body 96 from the pressure receiving chamber 88 through the accommodation space 62 and the short-circuit hole 94 urges the protruding tip portion of the rubber valve body 96 from the fixing fitting 78 toward the partition member main body 30. When the urging force (in this embodiment, the elastic restoring force of the rubber valve body 96 compressed and deformed) becomes larger, the rubber valve body 96 is deformed and displaced in a direction away from the opening portion of the short-circuit hole 94 in the central bottom portion 38. As a result, the communication state through the short-circuit hole 94 between the accommodation region 62 and the equilibrium chamber 90 is allowed. In particular, in the present embodiment, the biasing force exerted on the rubber valve body 96 is applied to the pressure receiving chamber 88 at the time of low-frequency large-amplitude vibration input corresponding to engine shake or the like, or at the middle to high-frequency small-amplitude vibration input corresponding to idling vibration or the like. The frequency range is about 11 to 15 Hz, which is lower than the idling basic vibration, which is a periodic main vibration corresponding to the engine explosion component, at the time of idling vibration. Thus, when an irregular vibration having an amplitude larger than usual of idling vibration is input, the pressure is made smaller than the pressure generated in the pressure receiving chamber 88.

  In the engine mount 10 for automobiles having the above-described structure, when a low-frequency large-amplitude vibration such as an engine shake is input, the amplitude is large. Therefore, an elastic rubber intended for vibration isolation by a low dynamic spring Due to the displacement of the plate 64 in the accommodation space 62, the pressure fluctuation in the pressure receiving chamber 88 cannot be absorbed effectively. On the other hand, the magnitude of the pressure in the pressure receiving chamber 88 generated during the amplitude vibration such as engine shake is larger than the pressure in the pressure receiving chamber 88 at the time of idling when a large amplitude vibration is input in a lower frequency range than the idling basic vibration. In addition to being made smaller, the protruding tip portion of the rubber valve body 96 is urged so as to abut on the equilibrium chamber 90 side opening portion of the short-circuit hole 94 in the central bottom portion 38 of the partition member body 30. Since the force is larger than the pressure of the pressure receiving chamber 88 during the engine shake, the rubber valve body 96 is brought into contact with the opening portion of the short circuit hole 94 on the equilibrium chamber 90 side in the center bottom portion 38. Thus, a state in which the communication through the short-circuit hole 94 between the accommodation space 62 and the equilibrium chamber 90 is blocked is maintained. As a result, the pressure in the pressure receiving chamber 88 and the equilibrium chamber 90 can be prevented from being absorbed by the deformation displacement of the elastic rubber plate 64 or leaking from the accommodation space 62 through the short-circuit hole 94. During this time, a pressure difference is effectively induced, and a sufficient amount of fluid can be secured through the orifice passage 92. As a result, an anti-vibration effect (high damping effect) based on a fluid action such as a resonance action of the fluid can be stably obtained.

  When a small amplitude vibration in a medium to high frequency range such as idling vibration is input, the orifice passage 92 is substantially closed due to a remarkably large fluid flow resistance due to an anti-resonant action. . Here, the pressure fluctuation of the pressure receiving chamber 88 is effectively absorbed based on the small displacement in the accommodation space 62 in the elastic rubber plate 64 designed for the purpose of vibration isolation by the low dynamic spring.

  However, since the magnitude of the pressure fluctuation of the pressure receiving chamber 88 generated during idling is relatively small in idling basic vibrations (generally, primary and secondary periodic vibrations associated with engine explosion), the short-circuiting hole 94 Is maintained in the shut-off state by the rubber valve body 96. However, since the amplitude of the basic idling vibration is small, the fluid pressure absorbing action of the pressure receiving chamber 88 is exerted by the deformation or displacement of the elastic rubber plate 64 without requiring fluid flow through the short-circuit hole 94, and idling. Anti-vibration effect (vibration insulation effect based on low dynamic spring characteristics) effective for basic vibration is exhibited.

  At this time, the flow length and the cross-sectional area of the fluid flow allowed between the pressure receiving chamber 88 and the equilibrium chamber 90 are appropriately set in accordance with the displacement of the elastic rubber plate 64, and resonance of the fluid flow is performed. By the action, it is possible to obtain a low dynamic spring effect with respect to idling fundamental vibration. In this case, since the short-circuit hole 94 is maintained in the shut-off state by the rubber valve body 96, the anti-vibration effect on the idling basic vibration based on the resonance action of the fluid flow is inhibited by the short-circuit hole 94. Nor.

  By the way, as a result of investigation by the present inventor, it has been found that in the automobile engine mount 10, a large amplitude vibration may be input aperiodically at a lower frequency side than the idling basic vibration during idling. In such a case, the orifice passage 92 is substantially closed due to the anti-resonance action, and the pressure absorbing function of the pressure receiving chamber 88 due to the deformation displacement of the elastic rubber plate 64 is the pressure that can be accommodated. It cannot function effectively because it exceeds the amount of change.

  Therefore, in the engine mount 10 for an automobile according to the present embodiment, when the large amplitude vibration in the high frequency range (idling large amplitude vibration) that is the large amplitude idling vibration as described above is input, the pressure receiving chamber 88 is large. The pressure is exerted on the rubber valve body 96 from the accommodation space 64 through the short-circuit hole 94, so that the rubber valve body 96 is deformed and displaced against the urging force, and the short-circuit hole in the central bottom portion 38 of the partition member body 30. The pressure receiving chamber 88 and the equilibrium chamber 90 are short-circuited through the accommodation space 62 and the short-circuit hole 94 by being separated from the periphery of the opening portion of the 94 in the equilibrium chamber 90 side. In short, in the present embodiment, in the rubber valve body 96, the biasing force that closes the short-circuit hole 94 based on its own elasticity is the generated pressure (positive pressure) of the pressure receiving chamber 88 when the idling large amplitude vibration is input. It is made smaller than the size.

  As a result, it is possible to avoid a significant decrease in the vibration proof performance due to the significant rigid body of the engine mount 10 when inputting idling large amplitude vibration, which has been a problem in the past, and it is also good for idling large amplitude vibration. Anti-vibration performance is demonstrated. By setting the flow path cross-sectional area and flow path length of the fluid flow path through the short-circuit hole 94 by opening the short-circuit hole 94, idling is performed based on the resonance action of the fluid. It is also possible to obtain a more effective vibration isolation effect against large amplitude vibrations. In that case, it is generally effective to tune so that a high damping effect is exhibited in a frequency range corresponding to idling large amplitude vibration.

  In particular, the elastic rubber plate 64 is positioned and held in the center of the accommodation space 62 by the engagement positioning action of the positioning protrusion 72 with respect to the lid member 32, while the short-circuit hole 94 is formed in the central bottom 38 of the accommodation space 62. Since the elastic rubber plate 64 is formed at a position away from the contact surface, the communication state of the short-circuit hole 94 to the accommodation space 62 is stably secured without being obstructed by the elastic rubber plate 64. Yes. In addition, a plurality of short-circuiting holes 94 are formed in the outer peripheral portion of the center bottom portion 38, and the plurality of short-circuiting holes 94 having the outer diameter dimension of the elastic rubber plate 64 formed in the center bottom portion 38 are elastic rubber plates. It is formed on a circumference larger than the outer diameter dimension of 64. As a result, even if the elastic rubber plate 64 can be displaced in the radial direction in the accommodation space 62, at least one short-circuiting hole at any displacement position in the accommodation space 62 in the elastic rubber plate 64. At least a part of 94 can be kept open. Thereby, the short circuit between the pressure receiving chamber 88 and the equilibrium chamber 90 through the short circuit hole 94 at the time of input of the idling large amplitude vibration in question can be surely performed, and high reliability is exhibited. It is.

  Therefore, according to the engine mount 10 for automobiles of the present embodiment, the anti-shake effect against engine shake and idling basic vibration can be stably exhibited, and even when idling large amplitude vibration as illustrated is input, a short-circuiting hole is provided. By virtue of a short circuit between the pressure receiving chamber 88 and the equilibrium chamber 90 through 94, an excellent vibration isolation effect can be obtained.

  Incidentally, the concrete vibration-proof characteristic in the engine mount 10 for motor vehicles of this embodiment is illustrated. The anti-vibration characteristics shown below are such that the static load corresponding to the shared support load of the power unit is applied to the first mounting bracket 12 and the second mounting on the central axis with respect to the automobile engine mount 10 structured according to the above-described embodiment. It was performed under the condition exerted between the mounting brackets 14.

  In the first specific example, the orifice passage 92 is tuned to a low frequency large amplitude vibration (frequency: about f1 = 10 Hz, amplitude: ± 1.0 mm) corresponding to an engine shake, and an elastic rubber as a movable plate. High-frequency small-amplitude vibration (frequency: f2 = about 20 to 30 Hz, amplitude: ±±) corresponding to idling fundamental vibration in the fluid flow path in which fluid flows through the through holes 48, 50, 58, 60, etc. based on the displacement of the plate 64 Of the elastic rubber plate 64 so that a hydraulic pressure absorption function (low dynamic spring effect) based on the resonance action of the fluid is exhibited at the time of input of 0.1 mm) and low frequency large amplitude vibration corresponding to an engine shake. Tuned not to function with displacement limit. By performing such tuning, as shown in FIG. 5, the high damping effect by the orifice passage 92 is excellent in the frequency range corresponding to the engine shake with respect to the low frequency large amplitude vibration. Anti-vibration effect is realized. On the other hand, for high-frequency small-amplitude vibration, as shown in FIG. Anti-vibration effect is demonstrated. Further, at the time of vibration input such as a running-over sound having a higher frequency: f3, the hydraulic pressure absorbing function by the elastic rubber plate 64 cannot be sufficiently exhibited, but the rubber valve body 96 is increased with the pressure increase in the pressure receiving chamber 88. By releasing the pressure, the significant pressure increase in the pressure receiving chamber 88 is released to the equilibrium chamber 90 through the short-circuit hole 94, so that the rigid mounting property is avoided and excellent vibration isolation performance can be exhibited. . Incidentally, FIG. 6 shows a measurement result when a similar experiment is performed on a conventional engine mount having no short-circuit hole 94 as a comparative example.

  In the second specific example, similarly to the first specific example, the low-frequency large-amplitude vibration (frequency: about f1 = 10 Hz, amplitude: ± 1.0 mm) corresponding to the engine shake in the orifice passage 92. In addition, the fluid flow path in which the fluid flows through the through holes 48, 50, 58, 60, etc. based on the displacement of the elastic rubber plate 64 as a movable plate is adjusted to a high frequency small amplitude vibration (frequency : F2 = about 20 to 30 Hz, amplitude: ± 0.1 mm), so that the fluid pressure absorption function (low dynamic spring effect) based on the resonance action of the fluid is exhibited, and the low frequency corresponding to the engine shake The amplitude vibration was tuned so as not to function by limiting the amount of displacement of the elastic rubber plate 64. On the other hand, the fluid flow path through the short-circuit hole 94 which is brought into a communication state by opening the elastic rubber plate 64 has a medium frequency large amplitude vibration corresponding to idling large amplitude vibration (frequency is about 11 to 15 Hz, amplitude is ± 0. Tuning was performed so that a high damping effect based on the resonance action of the fluid was exhibited when the input was about 5 mm. By performing such tuning, the high damping effect by the orifice passage 92 with respect to the engine shake and the low dynamic spring effect (vibration insulation effect) based on the displacement of the elastic rubber plate 64 with respect to the idling basic vibration are the first specifics. In the same way as in the case of a typical example, all of them could be effectively exhibited, and in addition to the large amplitude vibration of the idling, the rubber valve body 96 is opened as the pressure in the pressure receiving chamber 88 increases. The high damping effect based on the fluid flow through the short-circuiting hole 94 to be tightened was exhibited, and an excellent anti-vibration effect could be exhibited.

  In short, in the engine mount 10 configured according to the present invention, it is possible to easily and effectively cope with various anti-vibration characteristics respectively required in three or more frequency ranges by tuning. It is.

  The embodiments of the present invention have been described in detail above. However, the present invention is not limited to the specific descriptions in the embodiments, and various changes, modifications, and improvements based on the knowledge of those skilled in the art. Needless to say, any of these embodiments can be included in the scope of the present invention without departing from the spirit of the present invention.

  For example, as one embodiment of the present invention different from the above embodiment, a donut disk-shaped elastic rubber plate provided with a through hole in the center is adopted, and the partition member body corresponding to the formation position of this through hole is adopted. It is also possible to form a short-circuiting hole in the central portion in the direction perpendicular to the axis at the center bottom. In this case, as a valve body structure for covering the short-circuit hole, for example, a metal leaf spring as an urging means is supported by a partition member, a diaphragm fixing bracket or the like, and formed separately from the diaphragm. A valve body made of rubber elastic material or the like is provided at the free end of the metal leaf spring so that the valve body is superposed from the equilibrium chamber side on the equilibrium chamber side opening of the short-circuit hole in the central portion of the center bottom. For example, it is possible to adopt a mode in which the short-circuiting hole is elastically closed by the valve body by the urging force of the metal plate spring.

  In the embodiment, the means for restricting the displacement amount of the elastic rubber plate 64 in the direction perpendicular to the axis perpendicular to the plate thickness direction in the accommodation space 62 positions the protrusion 72 for positioning the elastic rubber plate 64 on the lid member 32. A locking mechanism in a direction perpendicular to the axis inserted through the hole 52 and an elastic protrusion 74 protruding from the elastic rubber plate 64 are brought into contact with the wall portion (central bottom portion 38) of the accommodation space 62 with pre-compression. The contact mechanism is included, but the invention is not limited to this. For example, the restriction protrusion is positioned on the inner peripheral side of the short-circuit hole on the outer peripheral side of the elastic rubber plate, and the inner surface of the central bottom portion. The inner dimension in the thickness direction of the area where the opening of the short-circuiting hole is arranged is smaller than the thickness of the elastic rubber plate. It is also possible to configure the elastic rubber plate displacement amount limiting means A.

  In the above-described embodiment, the orifice passage 92 is tuned to engine shake and the elastic rubber plate 64 and the rubber valve body 96 are designed to prevent idling vibration. The design of the tuning vibration of the orifice passage, the elastic rubber plate, and the rubber valve body can be changed in accordance with the vibration, the high-speed boom and other vibrations that cause problems. Therefore, for example, the flow path length is set to be large by forming the short-circuit hole with an internal flow path shape extending in the circumferential direction, the radial direction, or the like inside the partition member or a cylindrical shape protruding toward the equilibrium chamber. It is also possible to do so.

  Further, for example, a plurality of short-circuiting holes may be closed with a rubber valve element extending in an arc shape in the circumferential direction, or the elastic rubber plate may be formed in a disk shape with a constant thickness dimension throughout.

  In addition, the shape and size of the rubber valve body 96, the short-circuit hole 94, the elastic rubber plate 64, the partition member 28, the accommodation space 62, the first through holes 48 and 58, the second through holes 50 and 60, the orifice passage 92, and the like. The form of the structure, number, arrangement, etc. can be appropriately changed in design according to the required anti-vibration effect, manufacturability, etc., and is not limited to the above embodiment.

It is a longitudinal cross-sectional view of the engine mount for motor vehicles as one Embodiment of this invention, Comprising: The figure equivalent to the II cross section of FIG. The top view of the partition member which is one structural member of the engine mount for the motor vehicles. III-III sectional drawing of FIG. Bottom view of the partition member The graph showing the anti-vibration characteristic of the low frequency range equivalent to an engine shake in the engine mount for the said cars. The graph showing the anti-vibration characteristic of the high frequency region equivalent to idling vibration in the engine mount for the automobile.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10: Engine mount for motor vehicles, 12: 1st mounting bracket, 14: 2nd mounting bracket, 16: Main body rubber elastic body, 28: Partition member, 38: Center bottom part, 48: 1st through-hole, 50: 1st Two through holes, 58: First through hole, 60: Second through hole, 62: Storage space, 64: Elastic rubber plate, 76: Diaphragm, 88: Pressure receiving chamber, 90: Equilibrium chamber, 92: Orifice passage, 94 : Short circuit hole, 96: Rubber disc

Claims (6)

A first attachment member attached to one of the power unit of the automobile and the vehicle body and a second attachment member attached to the other of the power unit and the vehicle body are connected by a main rubber elastic body, and the wall portion is formed by the main rubber elastic body. Forming a pressure receiving chamber in which a part of the wall is formed and an equilibrium chamber in which a part of the wall portion is formed of a flexible membrane, and incompressible fluid is enclosed in the pressure receiving chamber and the equilibrium chamber, and the pressure receiving chambers And an orifice passage that communicates the equilibrium chamber with each other, a movable plate arrangement region is formed in a partition member that partitions the pressure receiving chamber and the equilibrium chamber, and the movable plate is accommodated in the movable plate arrangement region. A fluid-filled engine mount for an automobile having a fluid pressure absorption mechanism that absorbs a pressure variation in the pressure receiving chamber by displacement by providing a through hole for allowing one surface of the movable plate to face the pressure receiving chamber or the equilibrium chamber. So ,
A pressure relief hole that penetrates the wall of the movable plate arrangement region on the side of the equilibrium chamber and communicates the movable plate arrangement region with the equilibrium chamber, at least a part of which is a contact surface of the movable plate. A valve body that is formed so as to be disconnected and maintained in communication and that can be displaced in a contact and separation direction with respect to the opening portion of the pressure relief hole on the side of the equilibrium chamber is provided. A fluid-filled engine mount for an automobile, comprising urging means for resiliently closing the pressure relief hole with the valve body.   An elastic projecting member supported by the second mounting member and projecting from the equilibrium chamber side toward the partition member is formed of a rubber elastic body, and a projecting tip portion of the elastic projecting member is in the partition member The valve body and the urging means are both constituted by the elastic projecting member by elastically abutting against the opening on the equilibrium chamber side of the pressure relief hole. The fluid-filled engine mount for automobiles described.   The second mounting member includes a cylindrical portion, and the first mounting member is disposed so as to be spaced apart from one opening side of the cylindrical portion and connected by the main rubber elastic body. In addition, an annular fixing member is fixed to the outer peripheral edge portion of the flexible film, and the fixing member is fixed to the other opening side of the cylindrical portion of the second mounting member. The other opening of the part is covered with the flexible film, and the partition member is assembled inside the cylindrical part of the second mounting member, so that the partition member and the main rubber elastic body The pressure receiving chamber is formed therebetween, and the equilibrium chamber is formed between the partition member and the flexible membrane, while the valve body is disposed on the fixing member. 2. A fluid-filled engine mount for automobiles according to 2.   A wall portion on the equilibrium chamber side of the movable plate arrangement area is formed to have a larger shape on the outer peripheral side than the movable plate arranged in the movable plate arrangement area. The fluid-filled engine mount for an automobile according to any one of claims 1 to 3, wherein a plurality of the pressure relief holes are formed in a circumferential direction in an outer peripheral portion of the wall portion on the equilibrium chamber side.   Displacement amount limiting means for the movable plate for limiting the displacement amount of the movable plate in a plane orthogonal to the plate thickness direction to prevent the pressure relief hole from being blocked by the movable plate in the movable plate arrangement region. The fluid-filled engine mount for automobiles according to any one of claims 1 to 4, wherein the engine mount is provided.   As the orifice passage, a shake orifice passage tuned to a low frequency range corresponding to an engine shake is adopted, and a large amplitude vibration generated in a low frequency range than an idling fundamental vibration caused by an engine explosion main component in an idling state. The fluid-filled engine mount for an automobile according to any one of claims 1 to 5, wherein the valve body is opened against an urging force of the urging means when inputting the pressure.

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