JP4075066B2 - Fluid filled engine mount - Google Patents

Description

  The present invention relates to an engine mount for supporting a power unit on a vehicle body in a vibration-proof manner in an automobile, and in particular, using a flow action of an incompressible fluid sealed inside, a plurality of or shakes such as an engine shake and idling vibration. The present invention relates to a fluid-filled engine mount that can exhibit an effective vibration-proofing effect against vibrations in a wide frequency range.

  Conventionally, as a kind of automobile engine mount, a first attachment member and a second attachment member attached to one of a power unit and a vehicle body are connected by a main rubber elastic body, and the main rubber elastic body is used as a wall. Forming a pressure receiving chamber in which a part of the part is configured, and an equilibrium chamber in which a part of the wall is configured by a flexible membrane, enclosing the incompressible fluid in the pressure receiving chamber and the equilibrium chamber, and receiving the pressure 2. Description of the Related Art A fluid-filled engine mount having an orifice passage that communicates a chamber and an equilibrium chamber with each other is known. In such an engine mount, an excellent vibration isolation effect can be obtained based on the flow action of the incompressible fluid that is allowed to flow in the orifice passage.

  By the way, in the engine mount for automobiles, the frequency of vibrations to be vibrated differs depending on the running state of the automobile. However, the anti-vibration effect exhibited based on the resonance action of the fluid flowing through the orifice passage is limited to a relatively narrow frequency range in which the orifice passage is tuned in advance. In addition, in JP 2000-310274 A, etc., a valve body that provides first and second orifice passages tuned to different frequency ranges and opens and closes the second orifice passage tuned to a high frequency range. A semi-active type engine mount has been proposed in which the anti-vibration characteristics are actively switched by connecting / blocking the second orifice passage according to the running state of the vehicle. In such an engine mount, there is a problem that the structure is complicated and the manufacture is difficult and expensive because the valve body and the actuator must be assembled.

  Therefore, for example, in Patent Document 1 (Japanese Patent Laid-Open No. 2000-274480) and Patent Document 2 (Japanese Patent Laid-Open No. 5-280576), an intermediate is provided separately from the pressure receiving chamber and the equilibrium chamber communicated with each other by the first orifice passage. Forming a chamber, forming a second orifice passage for communicating any one of the pressure receiving chamber and the equilibrium chamber with the intermediate chamber, and setting the second orifice passage to a higher frequency region than the first orifice passage. In addition to tuning, a fluid-filled engine mount having a structure in which a partition wall that partitions the other of the pressure receiving chamber and the equilibrium chamber and the intermediate chamber is configured by a movable rubber film or a movable plate has been proposed. In such an engine mount, the amount of fluid flow through the second orifice passage is limited by the elasticity of the movable rubber film and the restraint of the movable plate.

  Therefore, in general, in a low frequency region such as an engine shake having a large amplitude, the fluid flow through the second orifice passage is limited, and the fluid flow through the first orifice passage is effectively generated. Anti-vibration performance can be obtained based on the high damping characteristics exhibited by the resonant action of the fluid flowing through the orifice passage. On the other hand, generally in the middle to high frequency range such as idling vibration having a small amplitude, the vibration isolation performance can be obtained based on the low dynamic spring characteristic exhibited by the resonance action of the fluid flowing through the second orifice passage. is there.

  However, in recent years, since a higher level of vibration isolation performance has been required, even with the engine mounts described in Patent Document 1 and Patent Document 2, the required vibration isolation performance cannot be realized sufficiently yet. There is a case. What is particularly required there is a problem as an engine shake during running while maintaining sufficient anti-vibration performance against medium to high frequency vibrations such as idling vibration, which is a problem when the vehicle is stopped. It is to realize an effective vibration-proofing performance for both low-frequency vibrations, such as low-frequency large-amplitude vibrations that are input when climbing over a level difference and low-frequency small-amplitude vibrations that are input during normal travel.

  That is, although it differs depending on the vehicle type, etc., in general, the idling vibration has a medium amplitude of about ± 0.1 to ± 0.25 mm in a medium to high frequency range of about 20 to 40 Hz, and a large amplitude exerted upon overcoming a step. The engine shake has a large amplitude of about ± 1 mm in the low frequency region around 10 Hz, and the small amplitude engine shake exerted during normal driving has a small amplitude of about ± 0.1 mm in the low frequency region around 10 Hz. In addition, in order to obtain an effective anti-vibration effect for medium to high frequency vibration such as idling vibration, low dynamic spring characteristics are required, while effective for low frequency vibration such as engine shake. In order to obtain an anti-vibration effect, high attenuation characteristics are required.

  However, in the engine mount having a structure in which the fluid flow amount through the second orifice passage is limited by the movable rubber film as described in Patent Document 1 described above, the second amount is equal to the elastic deformation amount of the movable rubber film. Although fluid flow through the orifice passage is generated, the movable rubber membrane requires pressure fluctuation according to Hook's law even when the amount of deformation is small. In idling vibration having a small amplitude, it is difficult to sufficiently deform the movable rubber film. Therefore, there is a problem that it is difficult to secure a fluid flow amount through the second orifice passage, and it is difficult to obtain a sufficient anti-vibration effect against idling vibration. In order to increase the fluid flow amount through the second orifice passage, it is conceivable to reduce the spring constant of the movable rubber film. However, in order to secure the fluid flow amount through the first orifice passage, the movable rubber membrane is movable. It is difficult to set the spring constant of the rubber film so small.

  Further, in the engine mount having a structure in which the fluid flow amount through the second orifice passage is limited by the movable plate as described in Patent Document 2 described above, since the resistance force hardly acts on the initial displacement of the movable plate, the amplitude Even when idling vibration is relatively small, the displacement of the movable plate is effectively generated and the amount of fluid flow through the second orifice passage is ensured, so that an effective vibration isolation effect can be obtained. it can. However, it is necessary to provide a gap for allowing displacement at the outer peripheral edge of the movable plate, and the pressure may escape from the pressure receiving chamber through this gap. In particular, in the case of small amplitude vibration such as an engine shake during normal running, the pressure fluctuation in the pressure receiving chamber and the fluid flow through the first orifice passage as the pressure escapes from the gap at the outer peripheral edge of the movable plate. As a result, there is a problem that it is difficult to effectively obtain a vibration isolation effect based on the fluid flow through the first orifice passage.

JP 2000-274480 A JP-A-5-280576

Here, the present invention has been made in the background as described above, and the problem to be solved is that for any of the following three types of vibration required in an engine mount of an automobile, It is an object of the present invention to provide a fluid-filled engine mount having a novel passive structure that can obtain a high level of vibration isolation performance and does not require an actuator or the like.
(1) Excellent anti-vibration performance based on high damping characteristics against large amplitude vibrations in the low frequency range corresponding to engine shake that occurs when stepping over a step, etc. (2) Low frequency range that corresponds to engine shake that occurs during normal driving Excellent anti-vibration performance based on high damping characteristics against small-amplitude vibration (3) Excellent anti-vibration performance based on low dynamic spring characteristics against medium-amplitude vibration corresponding to idling vibration generated when the vehicle is stopped

  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 features of the present invention are: (a) a first attachment member attached to one of the power unit side member and the vehicle body side member; and (b) the other of the power unit side member and the vehicle body side member. A second mounting member to be mounted; (c) a main rubber elastic body that elastically connects the first mounting member and the second mounting member; and (d) one of the wall portions by the main rubber elastic body. A pressure receiving chamber in which an incompressible fluid is enclosed, (e) an equilibrium chamber in which a part of the wall portion is formed of a flexible film and volume change is allowed, and (f) the pressure receiving chamber A first orifice passage that allows the equilibrium chamber to communicate with each other; (g) an intermediate chamber that is formed separately from the pressure receiving chamber and the equilibrium chamber and encloses an incompressible fluid; It is a rigid central movable plate and the outer periphery is changed. The outer peripheral movable rubber film part is an easy outer peripheral movable rubber film part, and is disposed so as to allow displacement or deformation in the central movable plate part and the outer peripheral movable rubber film part, so that the pressure receiving chamber and the equilibrium chamber are A movable partition member constituting a partition partitioning one of the intermediate chamber and the intermediate chamber; and (i) the first orifice passage that allows the other of the pressure receiving chamber and the equilibrium chamber and the intermediate chamber to communicate with each other. A second orifice passage tuned to a higher frequency range, and a hard restraint plate is disposed on the central movable plate portion of the movable partition member , with respect to the outer peripheral edge portion of the restraint plate. The outer peripheral movable rubber film part is bonded and protrudes on both sides in the plate thickness direction at a plurality of locations on the outer peripheral part of the central movable plate part where the restraint plate is disposed in the movable partition member. The elastic contact protrusion is formed so that the elastic contact protrusion is separated from and opposed to the displacement regulating member supported by the second attachment member or the second attachment member. Displacement amount limiting means for bufferingly limiting the displacement amount of the central movable plate portion by abutting the contact protrusion with the displacement restricting member is provided, and the elastic contact is provided at a plurality of locations on the outer peripheral portion of the central movable plate portion. A contact support portion that is formed integrally with the contact protrusion and protrudes on both sides in the plate thickness direction with a protrusion height larger than the elastic contact protrusion is provided, and the contact support portion with respect to the displacement regulating member is provided. In the fluid-filled engine mount, the restraint plate of the central movable plate portion is elastically supported by the corresponding contact support portion as a contact state .

In such a fluid-filled engine mount having a structure according to the present invention, the following anti-vibration characteristics are exhibited according to the difference in the frequency and amplitude of vibration to be inputted, which Therefore, an effective anti-vibration effect can be exhibited against these various different vibrations.
(1) With respect to low-frequency large-amplitude vibration corresponding to engine shake or the like that occurs when stepping over a step, fluid pressure absorption due to displacement or deformation of the movable partition member composed of the central movable plate portion and the outer peripheral movable rubber film portion follows. However, the amount of fluid flow through the second orifice passage is effectively limited, and pressure relief from the pressure receiving chamber to the equilibrium chamber through the second orifice passage is effective for the pressure receiving chamber. It is suppressed to such an extent that it does not cause a problem in order to cause pressure fluctuation. Thereby, a relative pressure variation is effectively generated between the pressure receiving chamber and the equilibrium chamber. Therefore, the amount of fluid flow through the first orifice passage can be advantageously ensured, a high damping effect based on the resonance action of the fluid flowing through the first orifice passage is exhibited, and excellent vibration-proof performance is achieved. Will be realized.
(2) For low-frequency, small-amplitude vibration corresponding to engine shake or the like that occurs during normal running, pressure escapes from the pressure receiving chamber to the equilibrium chamber through the second orifice passage with deformation or displacement of the movable partition member. Although there is a concern about the pressure absorbing action of the pressure receiving chamber by the movable partition member, fluid tightness on the outer peripheral side of the central movable plate portion is ensured by the outer peripheral movable rubber film portion, and the central movable plate portion is hard. As a result, the amount of deformation of the movable partition member can be suppressed, so that a sufficiently effective pressure fluctuation is still induced in the pressure receiving chamber. Therefore, as in the case of the low-frequency large-amplitude vibration described above, the relative pressure fluctuation between the pressure receiving chamber and the equilibrium chamber is effectively induced, and the amount of fluid flow through the first orifice passage is advantageously increased. As a result, a high damping effect based on the resonance action of the fluid that can flow through the first orifice passage is exhibited, thereby realizing excellent vibration isolation performance.
(3) For medium to high frequency range medium amplitude vibration corresponding to idling vibration or the like generated when the vehicle is stopped, the first orifice passage is substantially closed due to anti-resonance action. The low dynamic spring action exerted on the basis of the fluid flow through the second orifice passage tuned in the frequency range is excellent in suppressing a significant increase in the dynamic spring constant due to the anti-resonant action of the first orifice passage. It is expected to maintain anti-vibration performance. On the other hand, as in the case of the low-frequency small-amplitude vibration described above, the amount of fluid that can be caused to flow through the second orifice passage by the movable partition member disposed between the second orifice passage and the pressure-receiving chamber or the equilibrium chamber. There is concern that it will be significantly limited. However, in the vibration frequency region to be damped, the fluid flow through the second orifice passage is in a resonance state, so that the elastic displacement or deformation of the movable partition member is large due to the increase in flow energy based on the resonance magnification. Will be triggered. As a result, a fluid flow rate capable of flowing through the second orifice passage is positively secured, and an anti-vibration effect based on the resonance action of the fluid flowing through the second orifice passage can be effectively exhibited.

  In the present invention, more preferably, the natural frequency of the movable partition member, for example, the natural frequency of the central movable plate part or the natural frequency of the outer peripheral movable rubber film part is substantially equal to the tuning frequency of the second orifice passage. Tune to the same frequency range. As a result, the amount of fluid flow through the second orifice passage in the middle to high frequency range corresponding to idling vibration or the like is utilized not only for the resonance action of the fluid itself but also for the resonance action of the movable partition member. Therefore, it is possible to further increase the amount of fluid flow and further improve the vibration isolation effect.

In the present invention, by providing the displacement restricting means, the low-frequency, large-amplitude vibration at the input as well, also at low frequency, small amplitude when vibration is input prevent absorption by the movable partition member of the pressure fluctuations of the pressure receiving chamber Can do. Further, the amount of fluid flowing through the first orifice passage can be increased, so that the damping effect based on the resonance action of the fluid can be further improved, and the vibration-proof performance associated therewith can be further improved. The displacement restricting member with which the elastic contact protrusion is brought into contact can be advantageously configured, for example, by being fixedly supported by the second attachment member, specifically, by the second attachment member. It can be advantageously configured by using a partition member that is fixedly supported and forms a partition wall that partitions the pressure receiving chamber and the equilibrium chamber.

Furthermore, in the present invention, by adopting the constraint plate, at the time of vibration input of a low frequency range due to unnecessary deformation of the central movable plate portion, the absorption of pressure fluctuations in the pressure receiving chamber can be suppressed more reliably As a result, the vibration isolation effect based on the resonance action of the fluid flowing through the first orifice passage and the second orifice passage is more effectively and stably exhibited. As the restraining plate, a thin plate material made of a hard synthetic resin material or a metal is preferably used. In addition, the central movable plate portion can be constituted by only the restraining plate, and the movable partition member can be constituted by adhering the outer peripheral movable rubber film portion to the outer peripheral edge portion thereof.

  As is clear from the above description, in the fluid-filled engine mount structured according to the present invention, the first and second orifice passages function efficiently without using switching means such as an actuator ( 1) Excellent anti-vibration performance based on high damping characteristics against large-amplitude vibration in the low frequency range corresponding to engine shake that occurs when stepping over a step, and (2) Low frequency range that corresponds to engine shake that occurs during normal driving Excellent anti-vibration performance based on high damping characteristics against small-amplitude vibrations and (3) Excellent anti-vibration characteristics based on low dynamic spring characteristics against medium- to high-frequency medium-amplitude vibrations corresponding to idling vibrations generated when the vehicle is stopped Both of them can exhibit effective anti-vibration performance.

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

  First, FIG. 1 shows a vibration isolating mount 10 for an automobile as an embodiment of the present invention. This anti-vibration mount 10 has a structure in which a first mounting member 12 as a first mounting member and a second mounting member 14 as a second mounting member are elastically connected by a main rubber elastic body 16. The first mounting bracket 12 is mounted on the power unit side, while the second mounting bracket 14 is mounted on the body side of the automobile via the bracket 18 to support the power unit against vibration against the body. It is like that. In the following description, the vertical direction basically means the vertical direction in FIG.

  More specifically, the first mounting bracket 12 has a substantially inverted truncated cone block shape. A mounting bolt 20 is integrally formed on the end surface on the large diameter side so as to protrude upward in the axial direction.

  On the other hand, the second mounting bracket 14 has a substantially cylindrical shape with a large diameter as a whole. In addition, the second mounting bracket 14 includes a constricted portion 22 at the upper end in the axial direction. The constricted portion 22 is recessed inward in the radial direction and extends to the entire circumference in the circumferential direction, and by the constricted portion 22, the axially upper opening portion of the second mounting bracket 14 gradually expands upward. It has a reverse taper shape.

  In the second mounting bracket 14 having such a structure, the first mounting bracket 12 is disposed on substantially the same central axis so as to be separated from the upper opening side. A main rubber elastic body 16 is disposed between the first mounting bracket 12 and the second mounting bracket 14, and the first mounting bracket 12 and the second mounting bracket are arranged by the main rubber elastic body 16. 14 are elastically connected.

  The main rubber elastic body 16 has a truncated cone shape as a whole, and is vulcanized and bonded to the main rubber elastic body 16 so that the first mounting member 12 is inserted from the end surface on the small diameter side. Further, the opening portion on the upper side in the axial direction of the second mounting bracket 14 is overlapped and vulcanized and bonded to the outer peripheral surface of the large-diameter side end portion of the main rubber elastic body 16. As a result, the tapered outer peripheral surface of the first mounting bracket 12 and the reverse tapered inner peripheral surface of the constricted portion 22 of the second mounting bracket 14 are positioned to face each other, and the main rubber is interposed between the opposing surfaces. An elastic body 16 is interposed. In this embodiment, the main rubber elastic body 16 is an integrally vulcanized molded product including the first mounting bracket 12 and the second mounting bracket 14.

  Further, the opening of the second mounting bracket 14 is vulcanized and bonded to the outer peripheral surface of the main rubber elastic body 16 in this way, so that the opening on the upper side in the axial direction of the second mounting metal 14 is the main rubber elastic body. 16 is closed fluid-tightly. A mortar-shaped large-diameter recess 24 is formed on the large-diameter side end surface of the main rubber elastic body 16 and is opened in the second mounting bracket 14.

  Furthermore, a seal rubber layer 26 is formed on the inner peripheral surface of the second mounting bracket 14. The seal rubber layer 26 is integrally formed with the main rubber elastic body 16, and the inner peripheral surface of the second mounting member 14 is covered with the seal rubber layer 26 over substantially the entire surface.

  Furthermore, a partition member 28 and a rubber diaphragm 30 as a flexible film are sequentially fitted into the second mounting bracket 14 from an opening portion below the axial direction thereof. And fixed. A cylindrical fixed tube fitting 32 is vulcanized and bonded to the outer peripheral edge of the rubber diaphragm 30, and the fixed tube fitting 32 is fitted and fixed to the lower end opening of the second mounting bracket 14. Thus, the lower end opening of the second mounting member 14 is covered fluid-tightly.

  Accordingly, a pressure receiving chamber 34 in which a part of the wall portion is configured by the main rubber elastic body 16 is formed on the upper side in the axial direction of the partition member 28, while the wall on the lower side in the axial direction of the partition member 28 is formed. An equilibrium chamber 36 is formed, part of which is made of a rubber diaphragm 30. The pressure receiving chamber 34 and the equilibrium chamber 36 are fluid-tightly partitioned with respect to the external space, and incompressible fluids such as water, alkylene glycol, polyalkylene glycol, and silicone oil are sealed therein, respectively.

  In the pressure receiving chamber 34, a positive pressure fluctuation is generated based on the elastic deformation of the main rubber elastic body 16 at the time of vibration input. On the other hand, in the equilibrium chamber 36, the deformation of the rubber diaphragm 30 is easily allowed and the volume is variable, so that the pressure fluctuation is quickly absorbed.

  Here, the partition member 28 includes a partition block 38 having a thick, substantially disk shape. As shown in FIGS. 2 and 3, the partition block 38 is formed with a central recess 40 as an opening recess with a substantially circular recess shape at the center of the upper end surface.

  In addition, the partition block 38 is formed with a circumferential groove 42 that opens to the outer peripheral surface and extends in the circumferential direction, and both end portions of the circumferential groove 42 are formed on one surface in the axial direction. Opened.

  Furthermore, the central recess 40 of the partition block 38 is provided with a step surface 44 at the intermediate portion in the depth direction, and is a stepped circular recess comprising a small-diameter recess 46 on the bottom side and a large-diameter recess 48 on the opening side. ing. Further, the step surface 44 is formed with a groove-like annular recess 50 continuously extending over the entire circumference in the width direction at the intermediate portion in the width direction. Are connected to the small-diameter recess 46 by communication grooves 52 formed at appropriate locations.

  The movable partition member 54 is assembled to the large-diameter concave portion 48, and the lid plate metal fitting 56 is assembled on the upper surface of the partition block 38 from above the movable partition member 54.

  As shown in FIGS. 4 and 5, the movable partition member 54 has a circular rubber elastic plate 58 having a substantially thin plate shape, and a circular fitting 60 is added to the outer peripheral surface of the rubber elastic plate 58. Sulfur bonded. The fitting 60 is press-fitted into the large-diameter recess 48 of the partition block 38, so that the opening of the central recess 40 is fluid-tightly covered with the movable partition member 54. While the pressure receiving chamber 34 is formed above the member 54, a sealed intermediate chamber 61 is formed below the movable partition member 54.

  Further, the rubber elastic plate 58 has an elastic abutment protrusion 62 which is annularly extended continuously or discontinuously in the circumferential direction at a portion of the partition block 38 positioned substantially on the inner peripheral edge of the step surface 44. It is integrally formed as a part. Further, at appropriate locations (four locations in the present embodiment) on the circumference of the elastic protrusion 62, substantially plate-shaped contact support portions 64 that protrude larger on both the upper and lower surfaces are integrated as elastic contact protrusions. Is formed. In the present embodiment, the dimension between the projecting tip surfaces of the upper and lower elastic protrusions 62, 62 of the rubber elastic plate 58 is set slightly smaller than the axial dimension of the fitting 60, and The dimension between the projecting tip surfaces of both abutment support portions 64, 64 is set to be the same as or slightly larger than the axial dimension of the fitting 60.

  Furthermore, a hard restraint plate 66 made of metal or synthetic resin is fixed to the movable partition member 54 in an embedded state with respect to the central portion of the rubber elastic plate 58. In particular, in the present embodiment, as shown in FIG. 6, the restraint plate 66 has a substantially shallow dish shape with a slightly recessed central portion, and is improved in deformation rigidity despite being thin. The restraint plate 66 has an outer dimension larger than the inner diameter of the central recess 40 of the partition block 38, and the outer peripheral edge of the restraint plate 66 extends to the step surface 44.

  In the outer peripheral edge of the restraint plate 66, notches 68 are provided at a plurality of locations corresponding to the upper and lower contact support portions 64 and 64, respectively, so as to escape the formation portions of the contact support portions 64 and 64. Thus, the restraint plate 66 is attached to the rubber elastic plate 58. Further, a circular hole 70 is provided in the center of the restraining plate 66 and filled with a rubber elastic plate 58, so that the fixing strength to the rubber elastic plate 58 is improved.

  Further, the outer peripheral portion of the rubber elastic plate 58 is thin at the portion located between the elastic protrusion 62 and the fitting 60. Thereby, the outer periphery movable rubber film part 72 is formed with an annular plate shape extending in the circumferential direction with a predetermined width. The outer peripheral movable rubber film portion 72 is positioned on the opening of the annular recess 50 formed in the step surface 44 of the partition block 38.

  On the other hand, as shown in FIG. 7, the cover plate metal piece 56 has a thin and substantially disk shape as a whole, and a slight stepped portion 74 is formed in the radially intermediate portion, with respect to the outer peripheral edge portion. The central part protrudes downward. The lid plate metal 56 is superimposed on the upper surface of the partition block 38, and the stepped portion 74 is fitted into the opening of the central recess 40 of the partition block 38 so as to be positioned and assembled in the radial direction. .

  In addition, a circular central through hole 76 is provided in the central portion of the lid plate metal 56, and a plurality of outer peripheral through holes 78 extending in the circumferential direction with a predetermined width are provided around the central through hole 76. It is penetrating. When the cover plate metal piece 56 is assembled to the partition block 38, the central movable plate portion 80 of the rubber elastic plate 58 reinforced by the restraining plate 66 faces the pressure receiving chamber 34 through the central through hole 76. In addition, the outer peripheral movable rubber film portion 72 faces the pressure receiving chamber 34 through the outer peripheral through-hole 78.

  Furthermore, a cutout window 82 is provided at one place on the circumference on the outer peripheral edge of the cover plate metal piece 56, and this cutout window 82 is an upper opening of the circumferential groove 42 provided in the partition block 38. Are aligned. In addition, in order to align the upper opening of the notch window 82 and the circumferential groove 42 with each other, a positioning projection 84 projects from the upper end surface of the partition block 38 at an appropriate portion on the circumference, Positioning holes 86 are formed in corresponding portions of the cover plate metal piece 56, and circumferential positioning is realized by the engaging action of the positioning projections 84 and the positioning holes 86.

  Thus, under the state where the rubber elastic plate 58 and the lid plate metal piece 56 are assembled to the partition block 38 as described above, the contact support portions 64 of the rubber elastic plate 58 are as shown in FIG. Each front end surface is in contact with the stepped surface 44 of the partition block 38 as a displacement regulating member or the lower surface of the cover plate metal piece 56 and is appropriately compressed as necessary. Further, as shown in FIG. 9, the elastic protrusion 62 is positioned with a slight gap with respect to the step surface 44 of the partition block 38 or the lower surface of the cover plate metal piece 56. When the pressure variation of the pressure receiving chamber 34 is exerted on the rubber elastic plate 58, the rubber elastic plate is based on the pressure difference between the pressure receiving chamber 34 and the intermediate chamber 61 exerted on the upper and lower surfaces of the rubber elastic plate 58. 58 displacements or deformations are generated.

  Here, the deformation of the central movable plate portion 80 of the rubber elastic plate 58 is restricted by the restraining plate 66 that is embedded and fixed, and the displacement that is allowed mainly based on the elastic deformation of the contact support portions 64 and 64. Can be born. On the other hand, the outer peripheral movable rubber film portion 72 is thin and easily allowed to be elastically deformed, so that displacement due to the deformation is caused. Note that the space behind the central movable plate portion 80 and the space behind the outer peripheral movable rubber film portion 72 are stably maintained in a communication state by the communication groove 52, and substantially function as a single intermediate chamber 61. It is supposed to be.

  Further, the opening of the circumferential groove 42 formed on the outer peripheral surface of the partition block 38 is covered with a second mounting bracket 14 in a fluid-tight manner. Then, by covering the circumferential concave groove 42, a first orifice passage 88 that allows the pressure receiving chamber 34 and the equilibrium chamber 36 to communicate with each other is formed in a state in which the pressure receiving chamber 34 and the equilibrium chamber 36 are always in communication.

  Further, a communication hole 90 is formed in the center of the bottom surface of the small-diameter recess 46 formed on the upper surface of the partition block 38, thereby forming a second orifice passage 92 that communicates the intermediate chamber 61 and the equilibrium chamber 36. Yes.

  In particular, in the present embodiment, specifically, a high damping characteristic is exhibited with respect to vibration in a low frequency region around 10 Hz, such as an engine shake, based on the resonance action of the fluid flowing through the first orifice passage 88. The low dynamic spring effect is exerted on vibrations in the middle to high frequency range of about 20 to 40 Hz, such as idling vibration, based on the resonance action of the fluid flowing through the second orifice passage 92. Has been tuned to be.

  Further, in the present embodiment, at least one of the natural frequency of the central movable plate portion 80 and the natural frequency of the outer peripheral movable rubber film portion 72 in the movable partition member 54 is substantially equal to the tuning frequency of the second orifice passage 92. It is desirable to be tuned to the same frequency range.

  That is, with respect to low-frequency large-amplitude vibration that is input when climbing over a level difference during traveling, the hydraulic pressure due to displacement or deformation of the movable partition member 54 composed of the central movable plate portion 80 and the outer peripheral movable rubber film portion 72 Absorption cannot follow quantitatively, and the second orifice passage 92 is substantially closed, and pressure escape from the pressure receiving chamber 34 to the equilibrium chamber 36 through the second orifice passage 92 can be suppressed. . Thereby, a relative pressure variation is effectively generated between the pressure receiving chamber 34 and the equilibrium chamber 36. Therefore, the amount of fluid flow through the first orifice passage 88 can be advantageously ensured, and a high damping effect based on the resonance action of the fluid flowing through the first orifice passage 88 is exhibited, and excellent vibration-proof performance. Will be realized.

  In addition, for low-frequency small-amplitude vibration corresponding to engine shake or the like that occurs during normal travel, fluid tightness on the outer peripheral side of the central movable plate portion 80 is ensured by the outer peripheral movable rubber film portion 72. Even when a small amplitude vibration is input, the hydraulic pressure does not escape at the outer peripheral edge of the movable plate portion. Furthermore, since the central movable plate portion 80 is rigid and the amount of deformation of the movable partition member 54 can be suppressed, the hydraulic pressure absorption by the movable partition member 54 can be effectively suppressed. Therefore, a sufficiently effective pressure fluctuation is induced in the pressure receiving chamber 34, and a relative pressure fluctuation between the pressure receiving chamber 34 and the equilibrium chamber 36 is effectively induced, so that the first orifice passage 88. The fluid flow rate through the first orifice passage 88 can be advantageously ensured, and a high damping effect based on the resonance action of the fluid that is allowed to flow through the first orifice passage 88 is exhibited, thereby realizing excellent vibration isolation performance. .

  Furthermore, the first orifice passage 88 is substantially closed due to the anti-resonance action against the medium amplitude vibration corresponding to the idling vibration or the like generated when the vehicle is stopped. On the other hand, when the fluid flow through the second orifice passage 92 tuned to the middle to high frequency range is in a resonance state, the movable partition member 54 is elastically displaced or deformed by an increase in flow energy based on the resonance magnification. Will be greatly evoked. As a result, the fluid flow rate capable of flowing the second orifice passage 92 is positively secured, and the vibration isolation effect based on the resonance action of the fluid flowing the second orifice passage 92 can be effectively exhibited. .

  Further, the second orifice passage 92 is tuned by tuning the natural frequency of the central movable plate portion 80 and the natural frequency of the outer peripheral movable rubber film portion 72 to substantially the same frequency range as the tuning frequency of the second orifice passage 92. The amount of fluid flow through the fluid can be more advantageously secured by utilizing not only the resonance action of the fluid itself but also the resonance action of the movable partition member 54, thereby further increasing the amount of fluid flow and the accompanying prevention. Further improvement of the vibration effect can also be realized.

  Further, in the present embodiment, the amount of displacement of the movable partition member 54 is limited by forming the elastic projection 62 and the contact support portion 76 as the elastic contact projection on the movable partition member 54 so as to reduce the low frequency. Pressure absorption by the movable partition member 54 when inputting small amplitude vibration can be more effectively suppressed.

  Furthermore, in the present embodiment, the pressure of the pressure receiving chamber 34 at the time of vibration input in a low frequency range caused by unnecessary deformation of the central movable plate portion 80 is secured by fixing the hard restraint plate 66 to the central movable plate portion 80. The absorption of fluctuations can be suppressed more reliably. Therefore, the vibration isolation effect based on the resonance action of the fluid flowing through the first orifice passage 88 and the second orifice passage 92 is more effectively and stably exhibited.

  Incidentally, FIG. 10 shows the result of actual measurement of the frequency characteristics of the anti-vibration performance (dynamic absolute spring constant) of the anti-vibration mount having the structure according to the present embodiment as described above. Moreover, the measured value of the phase of the input vibration and transmission force in this vibration isolating mount is also shown in FIG. During measurement, an engine shake (small amplitude) or idling is applied between the first mounting bracket 12 and the second mounting bracket 14 by applying a static initial load of 1000 N corresponding to the shared support load of the power unit. A vibration having an amplitude (displacement) of 0.25 mm close to the vibration was applied.

  Also from the results shown in FIG. 10, in the vibration isolating mount of the present embodiment, there are a low frequency region corresponding to an engine shake close to 10 Hz and a medium to high frequency region corresponding to idling vibration slightly exceeding 30 Hz. It is recognized that the resonance phenomenon of the sealed fluid is effectively generated in both of the two frequency ranges, and that the effect of improving the vibration isolation performance based on the resonance action of the fluid can be sufficiently expected in each frequency range.

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

  For example, in the present embodiment, the intermediate chamber 61 is formed on the opposite side of the pressure receiving chamber 34 across the movable partition member 54, and the second orifice passage is formed so that the intermediate chamber 61 and the equilibrium chamber 36 are in communication with each other. Although 92 is formed, the arrangement of the intermediate chamber 61 and the liquid chamber with which the second orifice passage 92 communicates are not limited to those of this embodiment. Specifically, for example, the intermediate chamber 61 is formed on the opposite side of the equilibrium chamber 36 across the movable partition member 54, and the second orifice passage 92 is connected to the intermediate chamber 61 and the pressure receiving chamber 34. It may be formed. In short, for example, in the anti-vibration mount 10 of the above-described embodiment, the partition member 28 may be attached in the axial direction upside down.

In addition, in the said embodiment, although the specific example of what applied this invention to the engine mount for motor vehicles was shown, other than this, this invention can be applied advantageously also to engine mount apparatuses other than a motor vehicle. Of course.

It is a longitudinal cross-sectional view which shows the vibration proof mount as one Embodiment of this invention, Comprising: It is a figure corresponded in the II cross section in FIG. It is a top view which shows the partition block which comprises the vibration proof mount shown by FIG. It is a perspective view which shows the partition block shown by FIG. It is a top view which shows the movable partition member which comprises the vibration proof mount shown by FIG. FIG. 5 is a bottom view of the movable partition member shown in FIG. 4. It is a top view which shows the restraint plate which comprises the vibration proof mount shown by FIG. It is a top view which shows the cover plate metal fitting which comprises the vibration proof mount shown by FIG. It is a longitudinal cross-sectional view which expands and shows the contact | abutting support part in the vibration proof mount shown by FIG. It is a longitudinal cross-sectional view which expands and shows the elastic protrusion in the vibration isolating mount shown by FIG. It is a characteristic view which shows the dynamic characteristic in one Example of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Anti-vibration mount 12 1st mounting bracket 14 2nd mounting bracket 16 Main body rubber elastic body 28 Partition member 30 Rubber diaphragm 34 Pressure receiving chamber 36 Equilibrium chamber 54 Movable partition member 61 Intermediate chamber 72 Outer peripheral movable rubber film 80 Central movable plate part 88 First orifice passage 92 Second orifice passage

Claims (3)

A first attachment member attached to one of the power unit side member and the vehicle body side member;
A second attachment member attached to the other of the power unit side member and the vehicle body side member;
A main rubber elastic body for elastically connecting the first mounting member and the second mounting member;
A pressure receiving chamber in which a part of the wall is constituted by the main rubber elastic body and in which an incompressible fluid is enclosed;
An equilibrium chamber in which a part of the wall is made of a flexible membrane and volume change is allowed;
A first orifice passage that allows the pressure receiving chamber and the equilibrium chamber to communicate with each other;
An intermediate chamber formed separately from the pressure receiving chamber and the equilibrium chamber and enclosing an incompressible fluid;
The central part is a hard central movable plate part, and the outer peripheral part is an easily movable outer peripheral movable rubber film part, and displacement or deformation in the central movable plate part and the outer peripheral movable rubber film part is allowed. A movable partition member constituting a partition partitioning either the pressure receiving chamber or the equilibrium chamber and the intermediate chamber,
Allowed to communicate with each other and any other and the intermediate chamber of the pressure-receiving chamber and the equilibrium chamber, and a second orifice passage that is tuned to a higher frequency band than the first orifice passage, which has,
A hard restraint plate is disposed on the central movable plate portion of the movable partition member, and the outer peripheral movable rubber film portion is adhered to the outer peripheral edge portion of the restraint plate,
Elastic contact protrusions that protrude on both sides in the plate thickness direction are formed at a plurality of locations on the outer peripheral portion of the central movable plate portion on which the restraint plate is disposed in the movable partition member, and the second mounting member or the The elastic contact projection is spaced apart from the displacement regulating member supported by the second mounting member, and the central movable plate is brought into contact with the displacement regulation member by contacting the elastic contact projection. Displacement amount limiting means for buffering the amount of displacement of the part is provided, and
Contact support portions that are integrally formed with the elastic contact protrusions at a plurality of locations on the outer peripheral portion of the central movable plate portion and protrude to both sides in the plate thickness direction with a protrusion height larger than the elastic contact protrusions. A fluid-filled engine mount characterized in that the restraint plate of the central movable plate portion is elastically supported by the contact support portion with the contact support portion in contact with the displacement regulating member. .   2. The center movable plate portion of the movable partition member, wherein the elastic contact protrusion is formed on the restraint plate, and the contact support portion is formed at a portion off the restraint plate. Fluid-filled engine mount. The second mounting member has a substantially cylindrical shape, and the first mounting member is disposed on one opening side in the axial direction of the second mounting member, and the first mounting member is formed of the main rubber elastic body. And the second mounting member are elastically connected to cover one axial opening of the second mounting member in a fluid-tight manner, while the other axial opening of the second mounting member is flexible. The pressure-receiving chamber is formed between the partition member and the main rubber elastic body, by covering the fluid tightly with a conductive film and fitting and fixing the partition member to the second mounting member. The equilibrium chamber is formed between a member and the flexible membrane, and an opening recess is formed in the partition member on one side of the pressure receiving chamber and the equilibrium chamber so that the opening recess is fluid-tight. The movable partition member is fixedly attached to the partition member so as to cover the front. And forming an intermediate chamber, the fluid-filled engine mount according to claim 1 or 2 the intermediate chamber was allowed communicating with the other side of the receiving chamber and the equilibrium chamber by the second orifice passage.

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