JP4378249B2 - Liquid filled anti-vibration mount device - Google Patents

Description

  The present invention relates to a liquid-filled vibration-proof mount device in which vibration is damped by a flow resistance of a liquid flowing through a communication path (orifice path) between a plurality of liquid chambers formed inside, and in particular, a plurality of orifices. It belongs to the technical field of the structure of a switching type that obtains an effective anti-vibration action over a wide frequency band by switching the passage.

  Conventionally, an engine mount for automobiles is known as this type of vibration-proof mount device. The basic structure is that a rubber elastic body is interposed between the mounting member on the engine side and the support member on the vehicle body side, and the volume of the liquid chamber is changed between the two members so that the volume changes with the deformation of the rubber elastic body. In addition, the liquid chamber is partitioned into a pressure receiving chamber and an equilibrium chamber, and an orifice passage that communicates the pressure receiving chamber and the equilibrium chamber is provided. The liquid flows between the pressure receiving chamber and the equilibrium chamber via the orifice passage, so that vibration from the engine is absorbed and attenuated.

  By the way, since an automobile engine is generally used in a very wide driving state, an engine mount is required to have an anti-vibration effect for a plurality of types of vibration inputs having different frequencies and amplitudes. As described above, the frequency of vibration absorbed and damped by the flow of liquid in the orifice passage is largely determined by the cross-sectional area and length of the orifice passage. A sufficient anti-vibration effect cannot be obtained.

  In this regard, for example, in Patent Documents 1 and 2, a plurality of passages having different cross-sectional areas and lengths are provided so as to communicate with the pressure receiving chamber and the equilibrium chamber, respectively, and these passages are provided according to the operating state of the engine. What is switched is disclosed. For example, in the liquid-filled mount disclosed in Patent Document 1, the vibration at the start of the engine and the rattling vibration at the time of shifting with respect to the partition plate that partitions the first liquid chamber (pressure receiving chamber) and the second liquid chamber (equilibrium chamber). Or, an orifice passage with a large flow resistance tuned to a large amplitude vibration at a low frequency (about 5 to 15 Hz) such as a shake is provided in a spiral shape, and a through hole (through hole) with a smaller flow resistance is formed. Thus, the through hole is opened and closed by a valve portion formed integrally with the diaphragm of the equilibrium chamber.

  That is, for example, when the engine is idling, the valve portion is opened to open the through hole, and the liquid is allowed to flow between the pressure receiving chamber and the equilibrium chamber through the through hole, thereby lowering the dynamic spring of the mount and causing idle vibration. Can be effectively absorbed and insulated. On the other hand, the valve portion closes the through hole except during idle operation. When vibration with low frequency and large amplitude is input in this state, the through hole is closed, so that the liquid is received through the orifice passage. And flow between the equilibrium chambers, and effective vibration damping is achieved by the flow resistance.

  Furthermore, in the thing of the said patent document 1, the inner peripheral side of the said valve part functions as a sub-diaphragm, and with a through-hole closed as mentioned above by this valve part, it is a minute amplitude from an engine. When high-frequency vibration is input, a change in the hydraulic pressure in the pressure receiving chamber due to this is absorbed by repetitive elastic deformation of the sub-diaphragm, which can reduce a booming noise in the vehicle interior of the automobile.

  Similarly, in the liquid-sealed mount device disclosed in Patent Document 2, for example, a first orifice passage that is tuned to vibration having a relatively low frequency (about 20 to 40 Hz) and small amplitude such as engine idle vibration, and the like. And a second orifice passage tuned to a vibration having a lower frequency and a larger amplitude, and a part of the diaphragm partitioning the equilibrium chamber is pressed against the communication port of the first orifice passage to the equilibrium chamber. The door is opened and closed by separating them.

According to the document, in such a state that the passage of the first orifice passage is covered by a part of the diaphragm, the cover portion becomes a movable film constituting the wall portion on the equilibrium chamber side of the first orifice passage. When the movable film is elastically deformed, it is said that the frequency range in which the vibration isolating action is obtained is changed to the high frequency side by the flow of the liquid in the first orifice passage. In other words, by covering the equilibrium chamber side with a part of the diaphragm, the vibration isolation characteristics in the frequency range higher than the idle vibration are improved, thereby effectively preventing the high frequency vibration that causes the booming noise. It can be absorbed.
JP-A-8-277879 JP-A-10-89402

  However, each of the conventional engine mounts (Patent Documents 1 and 2) is a part of a diaphragm that partitions an equilibrium chamber as an elastic film (sub-diaphragm, movable film) for absorbing high-frequency vibrations from the engine. Therefore, the spring characteristics of the elastic film cannot be set freely, which is insufficient for reducing the booming noise.

  That is, when the passage (through hole) is closed by a portion of the diaphragm as described above and the portion is used as an elastic membrane, the elastic membrane is in contact with air on the surface opposite to the passage. When a large fluid pressure fluctuation of the pressure receiving chamber due to vibration input with a large frequency amplitude is applied, excessive deformation occurs, and the durability is greatly reduced and there is a possibility of premature breakage.

  Therefore, the elastic membrane is relatively thick and soft so that it can be elastically deformed in order to maintain durability even if it is subjected to such large fluid pressure fluctuations. However, since the natural frequency of such an elastic membrane does not become so high, in terms of automobile interior noise, the vibration corresponding to the so-called low and medium speed booming noise up to about 100 Hz is reduced. Although it is possible, vibrations in a higher frequency range cannot be effectively reduced.

  The present invention has been made in view of the above points, and an object of the present invention is to provide a vibration-sealing mount device suitable for an automobile engine mount or the like, vibration during shaking, shake, idle vibration. While being able to absorb and dampen relatively low-frequency vibrations as in the past, it is also possible to effectively absorb high-frequency vibrations, such as booming noise, up to a higher frequency range than before. There is.

  In order to achieve the above object, in the present invention, the elastic membrane member for closing the orifice passage is a member different from the diaphragm of the equilibrium chamber, and this is expanded from the partition plate to the equilibrium chamber side in the liquid chamber. In addition, the counter member formed with the concave portion corresponding to the bulging portion is disposed in the equilibrium chamber so that the elastic deformation of the elastic membrane member is restricted and the state is not restricted. I made it.

Specifically, the invention of claim 1 is characterized in that the mounting member attached to the supported body, the supporting member that supports the mounting member via the rubber elastic body, and the volume change with the deformation of the rubber elastic body. A liquid-filled vibration-proof mount device comprising a liquid chamber formed between both members, a partition plate that partitions the liquid chamber into a pressure receiving chamber and an equilibrium chamber, and an orifice passage that communicates the pressure receiving chamber and the equilibrium chamber as target, the partition plate, the pressure receiving chamber and the equilibrium chamber provided with a through hole so as to communicate, the elastic membrane member is disposed so as to try covering the through hole from the equilibrium chamber side, the elastic The membrane member has a conical bulge portion that bulges from the partition plate toward the equilibrium chamber side and divides the secondary liquid chamber therein.

  And an opposing member having a concave shape corresponding to the bulging portion of the elastic membrane member and disposed in the equilibrium chamber so as to advance and retreat against the bulging portion, and the opposing member, Advancing and retreating between a restricting position where the concave portion is brought into contact with the bulging portion so as to include the bulging portion and the elastic deformation is restricted and a non-regulating position where the concave portion is separated from the bulging portion. And a bulging portion of the elastic membrane member and a concave portion of the opposing member, wherein the concave portion is partially in contact with the bulging portion when the opposing member is in the restricting position. Thus, the elastic deformation of the part is allowed.

  With the above configuration, for example, when a large amplitude vibration is input at a low frequency from the supported body to the vibration-proof mount device, and the mounting member and the supporting member are relatively displaced relative to each other, the pressure is received along with the deformation of the rubber elastic body. The volume of the chamber changes, and the liquid flows through the orifice passage between the chamber and the equilibrium chamber due to the fluctuation of the hydraulic pressure. The vibration of the liquid is absorbed and damped by the flow of the liquid.

At that time, the fluid pressure fluctuation in the pressure receiving chamber also acts on the bulging portion of the elastic membrane member covering the partition plate through the through hole. By enveloping from the side of the equilibrium chamber by the concave portion of the inner wall and restricting the elastic deformation, it is possible to prevent a decrease in durability and early breakage due to excessive deformation of the elastic film member, and the deformation of the elastic film member It does not adversely affect vibration absorption and damping by the orifice passage.

  Further, even in a state where the elastic deformation of the bulging portion of the elastic film member is restricted as described above (restriction position), the concave portion of the opposing member is partially in non-contact with the bulging portion of the elastic film member. Therefore, when high-frequency vibration is input in this state and the volume of the pressure receiving chamber changes minutely in a very short period, this minute volume change, that is, high-frequency vibration is It is effectively absorbed by minute elastic deformation of the member.

  In addition, as described above, the bulging part of the elastic film member is encased by the concave part of the opposing member so as to restrict the deformation thereof, so that the durability of the elastic film member is not lowered and early damage is not caused. Its spring characteristics can be set relatively freely. For example, it can be tuned to vibrations in a higher frequency range by increasing the natural frequency by making it thinner and more rigid than the conventional example. it can.

  The elastic membrane member is disposed in the liquid chamber, and both surfaces thereof are in contact with the liquid in the liquid chamber. Even if a large fluid pressure fluctuation due to amplitude vibration acts from the pressure receiving chamber side, the liquid on the equilibrium chamber side becomes a buffer solution, and excessive deformation can be prevented.

On the other hand, if the opposing member is positioned at the non-restricted position by the advancing / retreating means, the bulging portion of the elastic film member is not restricted by the concave portion of the opposing member, and a large elastic deformation is possible. In this state, for example, when a vibration having a relatively low amplitude is input from the supported body and the volume of the pressure receiving chamber changes thereby, the fluid pressure fluctuation in the pressure receiving chamber is communicated through the through hole of the partition plate. The secondary liquid chamber acts on the secondary liquid chamber, that is, in the bulging portion of the elastic film member, and the secondary liquid chamber expands and contracts accordingly, thereby effectively absorbing vibration. Further, a vibration damping action is obtained by the liquid flowing between the sub liquid chamber and the pressure receiving chamber through the through hole of the partition plate.

  That is, according to the anti-vibration mount device having the above-described configuration, when this is applied to, for example, an engine mount, it is possible to absorb and attenuate relatively low-frequency vibrations such as vibrations during shakes, shakes, or idle vibrations as before. At the same time, high-frequency vibrations that cause a booming noise can be effectively absorbed up to a higher frequency range.

  In this case, that is, when the supported body is an automobile engine, the opposing member is provided integrally with a diaphragm that defines the equilibrium chamber, and the advancing / retreating means is configured such that the opposing member is an elastic membrane member. Preferably, a spring member that biases toward the bulging portion and an actuator that retracts the facing member from the bulging portion using intake negative pressure of the engine are provided (invention of claim 7).

  In this configuration, when the intake negative pressure increases during the idling operation of the engine, the facing member is retracted from the bulging portion by the actuator of the advancing / retreating means to be in the non-restricted position. Idle vibration with a small amplitude is effectively absorbed and damped.

  On the other hand, since the intake negative pressure is not so large except during idling, the concave portion of the opposing member is pressed against the bulging portion of the elastic film member by the spring member of the advance / retreat movement means, and the elastic deformation is restricted. This effectively absorbs and attenuates low-frequency large-amplitude vibrations such as vibrations during shakes and shakes as described above, and also effectively absorbs high-frequency vibrations generated by the engine. The muffled noise is sufficiently reduced.

  In the anti-vibration mount device having the above-described configuration, when the opposing member is in the restricting position, the inner periphery of the recessed portion is in contact with the outer periphery of the protruding portion when the opposing member is in the restriction position. On the other hand, the bottom surface of the concave portion is configured to be separated from the distal end side of the bulging portion, and a liquid pool is formed therebetween, and at least one of the outer periphery of the bulging portion and the inner periphery of the concave portion, It is preferable to provide a projecting portion or a recessed portion so that a communication path for communicating the liquid reservoir with the equilibrium chamber is formed between them.

  In this way, when the opposing member is in the restricting position, it is possible to restrict elastic deformation by bringing the inner periphery of the concave portion into contact with the outer periphery of the bulging portion of the elastic film member. Further, at this time, the bottom surface of the concave portion is separated from the distal end side of the bulging portion of the elastic membrane member and is in a non-contact state, and the liquid pool formed therebetween is communicated with the equilibrium chamber by the communication path. Therefore, elastic deformation on the tip side of the bulging portion is allowed.

  More specifically, in order to form a communication path between the inner periphery of the concave portion of the opposing member at the restricting position and the outer periphery of the bulging portion of the elastic film member as described above, for example, A groove extending from the vicinity of the bottom surface to the peripheral edge of the opening may be provided on the periphery (the invention of claim 3), or at least one of the outer periphery of the bulging portion of the elastic film member and the inner periphery of the concave portion of the opposing member In addition, a plurality of protrusions may be provided so that a gap is formed between both of them (invention of claim 4).

  Preferably, a folded portion that curves inward may be formed on the distal end side of the bulging portion of the elastic film member (invention of claim 5). In this way, elastic deformation is likely to occur in the vicinity of the folded portion, and the natural frequency can be easily tuned depending on the size and shape of the folded portion. Further, it is possible to reduce the influence of the dimensional error of the elastic film member, and to form a liquid pool having an appropriate volume between the front end side of the bulging portion and the bottom surface of the concave portion.

  Preferably, the partition plate may be provided with a cylindrical portion extending from the periphery of the through hole toward at least one of the pressure receiving chamber and the equilibrium chamber (invention of claim 6). In this way, when the opposing member is positioned at the non-restricted position and the bulging portion of the elastic membrane member is in a state where large elastic deformation is possible, the space between the bulging portion and the pressure receiving chamber is increased and reduced. The flowing liquid is subjected to a large flow resistance in the cylindrical portion, and thereby vibration is effectively damped.

  As described above, according to the liquid-filled vibration-proof mount device according to the present invention, the partition plate that partitions the liquid chamber into the pressure-receiving chamber and the equilibrium chamber is formed with a through-hole, and the elasticity is covered from the equilibrium chamber side. The membrane member is disposed so as to bulge to the equilibrium chamber side, and an opposing member having a concave portion corresponding to the bulging portion is disposed in the equilibrium chamber, thereby enclosing the bulging portion. By switching between the state in which the elastic deformation is controlled and the state in which the opposing member is separated from the elastic film member and the elastic deformation is not controlled, for example, when applied to an engine mount, the vibration at engine startup Can absorb and dampen relatively low-frequency vibrations such as vibrations, shakes, and idle vibrations as before, and can absorb high-frequency vibrations from the engine effectively up to a higher frequency range than before. By Les, it can and also be sufficiently reduced to high-speed booming noise in the passenger compartment.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. It should be noted that the following description of the preferred embodiment is merely illustrative in nature, and is not intended to limit the present invention, its application, or its use.

  FIG. 1 shows an embodiment in which a liquid-filled vibration-proof mount device of the present invention is applied to an automobile engine mount A. The engine mount A is interposed between an automobile power plant (not shown) and a vehicle body, While supporting the load of the power plant, the vibration from the power plant is absorbed or attenuated to suppress vibration transmission to the vehicle body.

  The engine mount A of this embodiment has a substantially cylindrical metal attachment member 1 attached to a power plant via a bracket or the like (not shown), and a cylindrical shape that supports this from the lower outer peripheral side via a rubber elastic body 2. A metal casing 3 (support member) is provided, and is fixed to the vehicle body frame by legs 33, 33,... Welded to the lower outer periphery of the casing 3.

  The attachment member 1 has a flange portion 11 projecting outward at an intermediate portion in the vertical direction, and has a tapered shape in which the lower side is recessed downward. On the other hand, a bracket on the power plant side is attached to the upper part of the attachment member 1, and a bolt hole 12 into which a fastening bolt for that purpose is screwed opens at the upper end surface. The collar portion 11 is covered with stopper rubbers 13 and 14 for regulating excessive displacement of the power plant in cooperation with a stopper fitting 8 and the like which will be described later.

  The rubber elastic body 2 is vulcanized and bonded at its upper portion to cover the lower tapered portion of the mounting member 1, and a thick-walled umbrella-shaped portion 21 extending obliquely downward while expanding radially therefrom. The cylindrical portion 22 includes a cylindrical portion 22 extending continuously downward from the lower end of the umbrella-shaped portion 21, and the cylindrical portion 22 is fixed to the inner periphery of the casing 3. That is, the casing 3 has a double structure comprising an inner cylinder member 31 on the inner circumference side and an outer cylinder member 32 on the outer circumference side, and the inner cylinder member 31 is embedded in the cylindrical portion 22 of the rubber elastic body 2. The cylindrical portion 22 is fitted on the inner peripheral side of the outer cylinder member 32.

  The cylindrical portion 22 of the rubber elastic body 2 has a lower inner diameter larger than that of the upper side, and an annular step portion 23 is formed at the boundary between them. Then, as the stepped portion 23, the resin partition plate 4 and the orifice plate 5 are sequentially stacked on the inner periphery of the cylindrical portion 22 of the rubber elastic body 2 from below, and the orifice plate 5 is further accommodated. A rubber diaphragm 6 is disposed so as to cover from below. The diaphragm 6 closes the lower end opening of the rubber elastic body 2 in a liquid-tight manner to form a cavity inside.

  The cavity thus formed is filled with a liquid such as ethylene glycol, and serves as a liquid chamber F for absorbing and mitigating vibrations of the power plant input to the rubber elastic body 2. The interior of the liquid chamber F is partitioned vertically by the partition plate 4, and the upper side thereof is a pressure receiving chamber f <b> 1 whose volume changes due to deformation of the rubber elastic body 2 due to vibration input and the fluid pressure fluctuates. . The lower side of the liquid chamber F is expanded or reduced in volume by deformation of the diaphragm 6 to become an equilibrium chamber f2 that absorbs the volume variation of the pressure receiving chamber f1. The vibration absorption and damping action caused by the flow of the liquid in the liquid chamber F will be described in detail later.

  A bottomed cylindrical metal cap 7 is attached to the lower end portion of the casing 3 in which the opening of the rubber elastic body 2 is closed by the diaphragm 6 as described above so as to cover the entire diaphragm 6 from below. ing. A flange projecting outward is formed on the peripheral edge of the opening at the upper end of the cap 7, and this flange is overlapped from below on the outer periphery of the diaphragm 6 in which the metal reinforcing plate 61 is embedded. The member 31 and the outer cylinder member 32 are caulked from below by flanges formed inwardly at the lower end edges thereof.

  On the other hand, a stopper fitting 8 having a slightly smaller diameter cylindrical shape is attached to the upper end portion of the casing 3. A flange projecting outward is formed on the peripheral edge of the opening at the lower end of the stopper fitting 8, and this flange is placed on the upper end of the cylindrical portion 22 of the rubber elastic body 2, so that the upper end edge of the outer cylinder member 32 of the casing 3 is It is caulked from above by a flange formed inward in the part.

  An annular wall portion 81 extending inwardly in a substantially horizontal direction so as to surround the attachment member 1 is formed at the opening peripheral edge portion of the upper end of the stopper fitting 8, and the lower surface of the annular wall portion 81 is the attachment member 1. By abutting against the stopper rubber 13 on the upper surface of the flange portion 11, the upward movement of the mounting member 1 is restricted. An annular stopper rubber 15 is vulcanized and bonded to the upper surface of the annular wall 81 so as to abut on a power plant side mounting bracket (not shown).

  1 shows a state where a static load of the power plant is not applied to the engine mount A, and the stopper rubber 13 on the upper surface of the flange portion 11 of the mounting member 1 is the lower surface of the annular wall portion 81 of the stopper fitting 8. In the 1G state where the engine mount A is attached to the car body of the automobile to support the power plant and the static load is applied, the rubber elastic body 2 is bent and the mounting member 1 is moved downward. Due to the displacement, a predetermined gap is formed between the stopper rubber 13 and the stopper fitting 8.

(Detailed structure of liquid chamber F)
Next, in the engine mount A, the structure of the liquid chamber F for absorbing and damping the vibration from the power plant by the flow of the liquid will be described in detail. In this embodiment, as described above, the partition plate 4 that divides the liquid chamber F into the pressure receiving chamber f1 and the equilibrium chamber f2 is formed in a disc shape as shown in FIG. 41 is formed. Further, a cylindrical portion 42 is formed so as to extend from the periphery of the through hole 41 toward the equilibrium chamber f2.

  Then, an inverted hat-shaped membrane 9 (elastic film member) is disposed so as to cover the through hole 41 and the cylindrical portion 42 from the equilibrium chamber f2 side and bulge toward the equilibrium chamber f2 side. Yes. The membrane 9 is a molded product of rubber, and a relatively thick collar portion 91 in which an annular metal reinforcing plate is embedded is superimposed on the lower surface of the partition plate 4. A relatively thin conical bulging portion 92 is provided so as to bulge from the end toward the equilibrium chamber f2 side (the lower side in the figure).

As a result, a small-volume sub liquid chamber is defined in the bulging portion 92 of the membrane 9, and this sub liquid chamber communicates with the pressure receiving chamber f <b> 1 by the through hole 41 of the partition plate 4 and the passage in the cylindrical portion 42. Has been. As shown in FIG. 3, when the elastic deformation is not restricted, the entire bulging portion 92 of the membrane 9 expands and contracts, so that the pressure receiving chamber f1 and the auxiliary liquid chamber are connected to each other through the through hole 41 and the like. A relatively large liquid flow is allowed between them.

  In other words, the bulging portion 92 of the membrane 9 has a function as a diaphragm that allows a change in volume of the sub liquid chamber, and the passages in the through hole 41 of the partition plate 4 and the tubular portion 42 are formed in the pressure receiving chamber f1. And has a function as an orifice passage communicating with the auxiliary liquid chamber. In this embodiment, the dimensions (diameter and length) of the orifice passage are set (tuned) so as to cause liquid column resonance in the vicinity of 20 to 40 Hz, for example, in accordance with idle vibration of the engine.

  The orifice plate 5 overlaid on the lower side of the partition plate 4 has a donut shape having a center hole 51 capable of accommodating the bulging portion 92 of the membrane 9 bulging downward from the partition plate 4 on the inner peripheral side as described above. A notch having a size corresponding to the outer peripheral side of the flange portion 91 of the membrane 9 is formed on the upper surface thereof so as to surround the upper end opening of the center hole 51. And the collar part 91 of the membrane 9 is inserted | pinched between the partition plates 4 in the part of the notch, and is hold | maintained.

  In addition, an opening groove 52 extending in the circumferential direction is provided on the outer periphery of the orifice plate 5 and is accommodated in the cylindrical portion 22 of the rubber elastic body 2 as shown in FIG. An annular orifice passage is formed by the inner peripheral surface and the opening groove 52 (hereinafter, the orifice passage is denoted by reference numeral 52). One end of the orifice passage 52 communicates with the pressure receiving chamber f1 through an opening 53 that opens to the upper surface of the orifice board 5 and an opening 43 that is formed in the partition plate 4 so as to communicate therewith. On the other hand, the other end of the orifice passage 52 communicates with the equilibrium chamber f2 in the same manner as the one end although not shown.

  The size (cross-sectional area and length) of the orifice passage 52 is larger in amplitude at a lower frequency (5 to 15 Hz) than idle vibration, such as vibration at engine start, rattling vibration generated at the time of shifting, or shake during running. It is tuned according to vibration (for example, about ± 0.5 mm), and liquid column resonance is generated by such low-frequency large-amplitude vibration.

  As described above, it faces the bulging portion 92 of the membrane 9 bulging downward from the lower surface of the partition plate 4 in the center hole 51 of the orifice plate 5, and the upper portion of the diaphragm 6 below the center portion A cylindrical protrusion 61 (opposing member) that protrudes toward the surface is formed. A substantially conical concave portion 62 corresponding to the adjacent bulging portion 92 is opened at the front end surface of the protruding portion 61, and the concave portion 62 includes the bulging portion 92 as shown in FIG. 1. By making contact in this manner, the elastic deformation of the bulging portion 92 can be regulated (hereinafter, this state is also referred to as the protruding portion 61 being in the regulating position).

  More specifically, regarding the relationship between the bulging portion 92 of the membrane 9 and the concave portion 62 of the diaphragm 6, the outer peripheral surface of the bulging portion 92 and the inner peripheral surface of the concave portion 62 have substantially the same size and shape. For this reason, as shown in the figure, when the protruding portion 61 is in the restricting position and includes the bulging portion 92 by the concave portion 62, the entire inner peripheral surface of the concave portion 62 comes into contact with the outer peripheral surface of the bulging portion 92. It comes to suppress so that it may not elastically deform.

  Further, the depth of the concave portion 62 is slightly deeper than the length of the bulging portion 92, and the tip side of the bulging portion 92 and the bottom surface of the concave portion 62 including the bulging portion 92 are not in contact with each other even in the regulation position. Thus, a liquid reservoir S having a predetermined volume or more is formed between the two. In addition, in order to maintain the shape of the concave portion 62 integrally formed with the rubber diaphragm 6 as described above, a horn-shaped metal reinforcement is provided in the protruding portion 61 near the concave portion 62. The board is buried.

  Further, as shown in FIG. 2 only, a plurality of radial grooves 62a, 62a,... Extending from the vicinity of the bottom surface to the peripheral edge of the opening are opened on the inner peripheral surface of the concave portion 62 at intervals in the circumferential direction. In this embodiment, there are four), so that the inner peripheral surface of the recess 62 and the outer peripheral surface of the bulging portion 92 are in contact with each other at the restricting position shown in FIG. A communication path for communicating the liquid reservoir S with the equilibrium chamber f2 is formed.

  In this way, a liquid pool S is formed between the bottom surface of the recess 62 at the restriction position and the tip of the bulging part of the membrane 9, and the liquid pool S communicates with the equilibrium chamber f2 so that the liquid can flow. In this state, the tip end side of the bulging portion 92 is in a state where minute elastic deformation is possible. In other words, the bulging portion 92 of the membrane 9 is restricted from large elastic deformation at the outer periphery at the restricting position, while minute elastic deformation at the distal end side is allowed.

  On the other hand, a bellows portion 64 extending downward toward the bottom of the cap 7 is integrally formed on the opposite side (lower side) of the projecting portion 61 at the center of the diaphragm 6. The bellows portion 64 has a hollow cylindrical shape whose peripheral wall can be expanded and contracted up and down, and a tip portion having a slightly small diameter protrudes outward through a round hole formed in the approximate center of the cap 7. In the state, it is locked in the round hole. Thus, a resin connector 65 is press-fitted into the tip of the bellows portion 64 protruding outward from the cap 7, and a vacuum hose (not shown) connected to this connector 65 causes the inside of the bellows portion 64 to be inside. The space communicates with the engine intake pipe.

  Further, the bellows portion 64 is pre-compressed up and down in a state where it is assembled to the mount as shown in FIG. 1, and the protruding portion 61 of the diaphragm 6 is made to be in contact with the membrane 9 by the compression reaction force, that is, the elasticity of rubber. The urging portion 92 is pressed and urged toward the restriction position. On the other hand, when a large suction negative pressure is applied via the vacuum hose during the engine idling operation, and the bellows portion 64 is contracted, the projecting portion 61 is retracted from the restriction position, and the concave portion 62 is It is positioned at a non-restricted position separated from the bulging portion 92.

  In other words, the bellows portion 64 of the diaphragm 6 uses the spring member that urges the protruding portion 61 toward the bulging portion 92 of the membrane 9 and the protruding portion 61 using the intake negative pressure of the engine. It also serves as a negative pressure type actuator that moves backward from 92, and, together with a vacuum hose that communicates with the intake pipe of the engine, constitutes a forward / backward moving means for moving the protruding portion 61 back and forth between a restricted position and a non-restricted position Yes.

(Function and effect)
Next, in the engine mount A configured as described above, the action of the liquid chamber F that absorbs and attenuates vibrations from the engine will be described separately for the idle operation and other states.

  First, when the engine is in an operating state other than idling and the intake negative pressure is not so high, the protruding portion 61 of the diaphragm 6 is biased toward the membrane 9 by the pressing force of the bellows portion 64 as shown in FIG. Then, the concave portion 62 opened at the tip end surface comes into contact with the bulging portion 92 of the membrane 9 so as to suppress the elastic deformation (restriction position). When a vibration with a low frequency and a large amplitude such as a shaking vibration at the time of shifting or a running shake is input to the engine mount A and the mounting member 1 and the casing 3 are relatively displaced relatively, a rubber elastic body With the deformation of 2, the volume of the pressure receiving chamber f <b> 1 changes relatively large, and due to the fluctuation of the liquid pressure caused thereby, the liquid flows through the orifice passage 52 between the pressure receiving chamber f <b> 1 and the equilibrium chamber f <b> 2.

  Here, the orifice passage 52 is tuned according to the vibration and shake at the time of the shift, and generates liquid column resonance in response to the vibration input. As shown, for example, with respect to a vibration input having a relatively large amplitude of about ± 0.5 mm, the engine mount A has a vibration damping characteristic having a low dynamic spring constant Kd with a peak around about 10 Hz and a large loss factor tanδ. Become. As a result, vibrations with relatively large amplitudes such as vibrations during shakes and shakes are satisfactorily absorbed and attenuated, thereby improving riding comfort.

  At that time, the fluid pressure fluctuation in the pressure receiving chamber f1 also acts on the sub liquid chamber through the through hole 41 of the partition plate 4 and the like, and acts on the bulging portion 92 of the membrane 9 that partitions the sub liquid chamber from the inside. However, the bulging portion 92 is in a state of being encased (from the outside) by the concave portion 62 of the protruding portion 61 at the restricting position from the balance chamber f2 side, and the entire outer peripheral surface of the bulging portion 92 is. Is in contact with the inner peripheral surface of the recess 62, the bulging portion 92 is hardly deformed. Therefore, the membrane 9 does not deteriorate in durability or cause premature breakage due to excessive deformation of the bulging portion 92, and the deformation of the membrane 9 adversely affects the vibration absorption and damping functions of the orifice passage 52. There is no effect.

  At this time, the distal end side of the bulging portion 92 of the membrane 9 is in a state in which a minute elastic deformation is possible without contact with the bottom surface of the concave portion 62 including the same. Since the liquid reservoir S is formed between the bottom surface of the recess 62 and both surfaces are in contact with the liquid, even if a large fluid pressure fluctuation acts from the inside as described above, The liquid on the side) serves as a buffer solution, and no excessive deformation occurs at that site.

  Further, as described above, the tip side of the bulging portion 92 of the membrane 9 is in a state in which the elastic deformation is possible without contact with the bottom surface of the concave portion 62. In this state, for example, high engine speed operation, etc. When the volume of the high-pressure micro-vibration is input and the volume of the pressure receiving chamber f1 changes minutely in an extremely short period, this small volume change, that is, the high-frequency vibration is transmitted to the auxiliary liquid chamber, and the tip of the bulging portion of the membrane 9 It is effectively absorbed by minute elastic deformation.

  Here, in this embodiment, as described above, the bulging portion 92 of the membrane 9 is encased by the concave portion 62 provided in the protruding portion 61 of the diaphragm 6 and the deformation thereof is restricted, whereby the durability of the membrane 9 is improved. Since it is possible to prevent lowering and early breakage, it is not necessary to make the membrane 9 thick and capable of large elastic deformation as in the conventional examples (Patent Documents 1 and 2). Can be set freely.

That is, for example, by making the tip of the bulging portion 92 of the membrane 9 particularly thin and rigid compared to the conventional example, the natural frequency is increased, thereby tuning to vibration in a higher frequency range. Can do. FIG. 5 shows a state in which the dynamic spring constant Kd of the engine mount A is lowered to a high frequency region of 100 Hz or more due to minute elastic deformation of the membrane 9 with respect to vibration input with a minute amplitude of about ± 0.05 mm, for example. FIG. 6 is an image diagram showing a case in which the membrane 9 is not elastically deformed at all (shown by phantom lines), and can absorb minute vibrations of the engine over a high frequency range in this way, so that high-speed bulking in the passenger compartment Even the sound can be reduced sufficiently.

  On the other hand, when the engine is idling, the intake negative pressure increases, and when this acts on the bellows portion 64 of the diaphragm 6 via the vacuum hose, the bellows portion 64 contracts as shown in FIG. Retreat from the restricted position. Thereby, the inner periphery of the recess 62 opened at the tip of the projecting portion 61 is separated from the outer periphery of the bulging portion 92 of the membrane 9 (non-regulatory position), and the entire bulging portion 92 is expanded and contracted, It will be in the state which accept | permits the volume change of the inside, ie, a subliquid chamber.

  In this state, when idle vibration of the engine is input and thereby the volume and the fluid pressure of the pressure receiving chamber f1 fluctuate in a predetermined cycle, the variation of the fluid pressure communicates through the through hole 41 of the partition plate 4 or the like. The vibration is absorbed by being transmitted to the liquid chamber and expanding and contracting the bulging portion 92 of the membrane 9 accordingly. Further, the liquid flows between the pressure receiving chamber f1 and the sub liquid chamber through the through hole 41 of the partition plate 4 and the passage in the cylindrical portion 42, and thereby the idle vibration is attenuated.

That is, the passages in the through hole 41 and the cylindrical portion 42 are tuned so as to cause liquid column resonance in response to idle vibration of the engine. For example, as shown in FIG. For an idling vibration input of about 1 mm, the engine mount A has a vibration damping characteristic with a low dynamic spring constant Kd with a peak at about 30 Hz and a large loss coefficient tanδ. For this reason, idle vibration can be satisfactorily absorbed and attenuated. Note that the phantom lines in the figure indicate the dynamic spring characteristics when the entire membrane 9 is formed flat. By providing the bulging portion 92 as in this embodiment, the dynamic spring at the peak is reduced. Can be bigger.

  Therefore, according to the engine mount A (liquid-filled vibration-proof mount device) according to this embodiment, for example, vibration at the start of the engine, rattling vibration at the time of shifting, vibration with low frequency and large amplitude such as a shake during traveling, It is possible to improve the ride comfort of the car by absorbing and attenuating both idle vibrations with a slightly higher frequency and smaller amplitude as before, as well as high-frequency vibrations generated by the engine. Can be effectively absorbed up to a higher frequency range than before, so that the muffled noise in the vehicle compartment can be sufficiently reduced to not only the so-called medium-low muffled noise but also the high-speed muffled noise.

(Other embodiments)
The configuration of the present invention is not limited to the above-described embodiment, but includes other various aspects. That is, in the above-described embodiment, the concave portion 62 is formed so as to open at the front end surface of the protruding portion 61 of the diaphragm 6, but not limited to this, a member (opposing member) separate from the diaphragm 6 is balanced. The recess 62 may be formed in the chamber f2.

  Moreover, in the said embodiment, you may form the folding | turning part 92a which curves inward at the front end side of the bulging part 92 of the membrane 9, as an example shows in FIG. In this way, it is advantageous to form a liquid reservoir S having an appropriate volume between the distal end side of the bulging portion 92 of the membrane 9 and the bottom surface of the recess 62, and elastic deformation is caused in the vicinity of the folded portion 92a. In addition to being easily generated, the natural frequency can be easily tuned depending on the size and shape of the folded portion 92a. In addition, the folding | turning part 92b which curves further outward may be provided in the folding | turning part 92a, and it can also be set as M cross-section as shown in FIG.

  Further, as shown in FIG. 7, the partition plate 4 may not be provided with the cylindrical portion 42, and although not shown, the cylindrical portion 42 may be provided so as to extend toward the pressure receiving chamber f <b> 1. .

  Furthermore, in the embodiment, a plurality of grooves 62a are formed so as to open to the inner peripheral surface of the concave portion 62, whereby the bottom surface of the concave portion 62 and the tip of the bulging portion 92 of the membrane 9 are formed at the restriction position. The liquid reservoir S formed therebetween communicates with the equilibrium chamber f2. However, the present invention is not limited to this. For example, as shown in FIG. 9, a plurality of protrusions 92c are formed on the entire outer peripheral surface of the bulging portion 92 of the membrane 9. , 92c,... May be integrally formed, so that a gap is formed between the outer peripheral surface of the bulging portion 92 and the inner peripheral surface of the recess 62. Such protrusions can also be formed on the inner peripheral surface of the recess 62.

  In addition, in the above-described embodiment, the vibration-proof mount device of the present invention is applied to the vertical engine mount A that receives a compressive load from above, but is not limited to this, for example, pulling downward Of course, the present invention can be applied to a horizontally mounted engine mount that receives a load, and it is needless to say that the present invention can also be applied to various anti-vibration mount devices other than the engine mount.

It is a longitudinal section showing the structure of the engine mount concerning an embodiment. It is a perspective view which decomposes | disassembles and shows the assembly | attachment states, such as a membrane, an orifice board, and a diaphragm, with respect to the partition plate of a liquid chamber. It is sectional drawing which shows the state of a liquid chamber when a protrusion part exists in a non-regulation position. It is a graph which shows the anti-vibration characteristic of the mount with respect to the low frequency large amplitude vibration input. FIG. 5 is a diagram corresponding to FIG. 4 corresponding to vibration input of high frequency and minute amplitude. FIG. 5 is a diagram corresponding to FIG. 4 corresponding to an input of idle vibration. It is the FIG. 3 equivalent view which concerns on other embodiment which provided the folding | returning part in the bulging part front-end | tip of a membrane. It is a longitudinal cross-sectional view of the membrane from which the shape of a folding | turning part differs. It is (a) longitudinal cross-sectional view and (b) bottom view of the membrane which provided the protrusion in the bulging part outer peripheral surface.

A Engine mount (liquid filled anti-vibration mount device)
F Liquid chamber f1 Pressure receiving chamber f2 Equilibrium chamber S Liquid reservoir 1 Mounting member 2 Rubber elastic body 3 Casing (supporting member)
4 Partition plate 41 Through hole 42 Cylindrical part 5 Orifice board 52 Opening groove (orifice passage)
6 Diaphragm 61 Protruding part (opposing member)
62 recess 62a groove 64 bellows (spring member, actuator)
9 Membrane (elastic membrane member)
92 bulging portion 92a folded portion 92c protrusion

Claims (7)

An attachment member attached to the supported body, a support member for supporting the attachment member via a rubber elastic body, and a liquid chamber formed between the two members so that the volume changes with deformation of the rubber elastic body; A liquid-filled vibration-proof mount device comprising: a partition plate that partitions the liquid chamber into a pressure receiving chamber and an equilibrium chamber; and an orifice passage that communicates the pressure receiving chamber and the equilibrium chamber.
Wherein the partition plate, a through-hole is provided so as to communicate the pressure receiving chamber and the equilibrium chamber, the elastic film member is disposed so as to try covering the through hole from the equilibrium chamber side, the elastic film member , Bulges toward the equilibrium chamber side from the partition plate, and has a conical bulge portion that divides the secondary liquid chamber inside ,
A counter member disposed in the equilibrium chamber so as to have a recess having a shape corresponding to the bulging portion of the elastic membrane member, and to advance and retreat against the bulging portion;
The opposing member is brought into contact with the bulging portion so that the concave portion includes the bulging portion, and a restriction position for restricting the elastic deformation, and a non-regulating position in which the concave portion is separated from the bulging portion. An advancing / retreating means for advancing / retreating between,
The bulging part of the elastic membrane member and the concave part of the opposing member are such that when the opposing member is in the restricting position, the concave part is not in contact with the bulging part and elastic deformation of the part is performed. A liquid-filled vibration-proof mount device characterized in that The vibration-proof mount device according to claim 1,
The bulging part of the elastic membrane member and the concave part of the opposing member are such that when the opposing member is in the restricting position, the inner periphery of the concave part comes into contact with the outer periphery of the bulging part, while the bottom surface of the concave part is swelled It is separated from the tip side of the part, and is configured so that a liquid pool is formed between them,
At least one of the outer periphery of the bulging portion and the inner periphery of the recess is provided with a protrusion or a recess so that a communication path is formed between the two to communicate the liquid reservoir with the equilibrium chamber. A liquid-sealed anti-vibration mount device. The anti-vibration mount device according to claim 2,
A liquid-filled vibration-proof mount device characterized in that a groove extending from the vicinity of the bottom surface of the recess to the peripheral edge of the opening is provided on the inner periphery of the recess of the facing member. The anti-vibration mount device according to claim 2,
A plurality of protrusions are provided on at least one of the outer periphery of the bulging portion of the elastic membrane member and the inner periphery of the concave portion of the opposing member so as to form a gap between the two. Type anti-vibration mounting device. In the vibration-proof mount apparatus as described in any one of Claims 2-4,
A liquid-filled vibration-proof mount device, wherein the elastic film member is formed with a folded portion that curves inwardly on the distal end side of the bulging portion. In the vibration-proof mount apparatus as described in any one of Claims 2-5,
A liquid-filled vibration-proof mount device, wherein the partition plate is provided with a cylindrical portion extending from the periphery of the through hole toward at least one of the pressure receiving chamber and the equilibrium chamber. In the vibration-proof mount apparatus as described in any one of Claims 2-6,
The supported body is an automobile engine,
The opposing member is provided integrally with a diaphragm that partitions the equilibrium chamber,
The advancing and retreating means includes a spring member that urges the opposing member toward the bulging portion of the elastic membrane member, an actuator that retracts the opposing member from the bulging portion using intake negative pressure of the engine, A liquid-filled vibration-proof mount device characterized by comprising:

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