JP2015052351A - Fluid filled type vibration control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fluid filled type vibration control device of a new structure, capable of achieving effective vibration control effect with respect to vibration having different input directions or frequencies without adversely affecting durability or spring characteristics of a body rubber elastic body.SOLUTION: In a fluid filled type vibration control device 10, a first attachment member 12 and a second attachment member 14 are elastically connected by a body rubber elastic body 16, and fluid chambers 40 and 42 in which a part of a wall is constituted by the body rubber elastic body 16 and incompressible fluid 44 is filled inside are formed. Functional fluid 50 is filled in the fluid chamber 40, and holding means 52 is provided for holding the functional fluid 50 in a prescribed position by always applying a voltage or a magnetic field to the functional fluid 50.

Description

  The present invention relates to a fluid-filled vibration isolator used for an engine mount of an automobile.

  Conventionally, an anti-vibration device is known as a type of anti-vibration coupling body or anti-vibration support body that is interposed between members constituting a vibration transmission system and anti-vibration-couples the members to each other. The vibration isolator has a structure in which a first mounting member and a second mounting member are elastically connected by a main rubber elastic body, and vibration energy is generated by a damping action caused by internal friction of the main rubber elastic body. It comes to reduce.

  By the way, since there is a limit to the damping action obtained by the deformation of the rubber elastic body, in order to realize a higher level of damping performance, a fluid chamber in which an incompressible fluid is enclosed is formed, and the fluid flow A fluid-filled vibration isolator that utilizes a vibration isolating effect based on the action and the like has also been proposed. In this fluid-filled vibration isolator, generally, a structure is adopted in which a fluid chamber is divided into a pressure receiving chamber and an equilibrium chamber, and an orifice passage is formed to communicate the two chambers with each other, and fluid flows through the orifice passage. By doing so, an anti-vibration effect based on the resonance action of the fluid is exhibited. For example, it is shown in Japanese Patent Laid-Open No. 10-132015 (Patent Document 1) and Japanese Patent Laid-Open No. 8-28623 (Patent Document 2).

  However, such a fluid-filled vibration isolator is effective for vibration input at a specific frequency with the orifice passage tuned, while effective for vibration input at other frequencies. It was difficult to obtain a good anti-vibration effect. In addition, effective anti-vibration effect is exerted against vibration input in a specific direction that causes a relative internal pressure fluctuation between the main liquid chamber and the sub liquid chamber, while the internal pressure fluctuation of the pressure receiving chamber is reduced. There is a problem that it is difficult to effectively exhibit the vibration-proofing effect due to the fluid flow action against the vibration input in the direction.

Japanese Patent Laid-Open No. 10-132015 JP-A-8-28623

  The present invention has been made in the background of the above-mentioned circumstances, and the problem to be solved is against vibrations with different input directions and frequencies without adversely affecting the durability and spring characteristics of the main rubber elastic body. An object of the present invention is to provide a fluid-filled vibration isolator having a novel structure capable of obtaining an effective vibration isolating effect.

  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.

  That is, according to the first aspect of the present invention, the first mounting member and the second mounting member are elastically connected by the main rubber elastic body, and a part of the wall portion is configured by the main rubber elastic body. In a fluid-filled vibration isolator in which a fluid chamber in which an incompressible fluid is sealed is formed, a functional fluid is sealed in the fluid chamber, and a voltage or a magnetic field is constantly applied to the functional fluid. Thus, a holding means for holding the functional fluid in a predetermined position is provided.

  According to the fluid-filled vibration isolator configured as described above according to the first aspect, the fluid mounting type vibration isolator is held at a predetermined position in the fluid chamber by the relative displacement of the first mounting member and the second mounting member due to vibration input. By flowing the functional fluid, the desired anti-vibration effect is exhibited based on the energy damping action due to the viscous resistance of the functional fluid and the frictional resistance at the interface between the functional fluid and the incompressible fluid. .

  In addition, since the functional fluid is always held, there is no need for control according to the input vibration, and a stable vibration-proofing effect can be obtained with a simple structure.

  According to a second aspect of the present invention, in the fluid-filled vibration isolator described in the first aspect, the fluid chamber includes a main liquid chamber and a sub liquid chamber. An orifice passage that communicates the liquid chambers is formed, and the functional fluid is sealed in at least one of the main liquid chamber and the sub liquid chamber and held by the holding means.

  According to the second aspect, both the vibration isolation effect based on the resonance action of the fluid flowing through the orifice passage and the vibration isolation effect exhibited based on the viscosity of the functional fluid can be obtained. Even if the vibration frequency and the input direction are difficult to exhibit the vibration isolation effect due to the orifice passage, an effective vibration isolation effect can be obtained.

  According to a third aspect of the present invention, in the fluid-filled vibration isolator described in the second aspect, the main liquid chamber is a pressure receiving chamber in which a part of the wall portion is formed of the main rubber elastic body. In addition, the secondary liquid chamber is an equilibrium chamber in which a part of the wall portion is formed of a flexible film, and the functional fluid is sealed in the pressure receiving chamber and held by the holding means. It is.

  According to the third aspect, since the functional fluid is held in the pressure receiving chamber where the fluid flow is efficiently generated at the time of vibration input, the vibration isolation effect based on the viscosity of the functional fluid is effectively exhibited. Is done.

  According to a fourth aspect of the present invention, in the fluid-filled vibration isolator described in the second or third aspect, the functional fluid is held at a position off the opening of the orifice passage by the holding means. It is what.

  According to the fourth aspect, by preventing the functional fluid from being held so as to block the opening of the orifice passage, the flow of the incompressible fluid efficiently occurs through the orifice passage. The anti-vibration effect due to the action can be obtained effectively.

  According to a fifth aspect of the present invention, in the fluid-filled vibration isolator described in any one of the first to fourth aspects, the functional fluid is a magnetic fluid, and the holding means is The magnetic fluid application means applies a magnetic field to the functional fluid.

  According to the fifth aspect, when the functional fluid is a magnetic fluid, the viscosity of the magnetic fluid increases in a state where the functional fluid is held by the magnetic force of the magnetic field applying means, and the energy is exhibited based on the viscous resistance or the like. Since the damping action is improved, more excellent vibration isolation performance is realized. As the magnetic field applying means, an electromagnet or the like can be adopted, but the structure of the following sixth aspect is preferably adopted.

  According to a sixth aspect of the present invention, in the fluid-filled vibration isolator described in the fifth aspect, the magnetic field applying means is a permanent magnet.

  According to the sixth aspect, since the magnetic field applying means is a permanent magnet, a magnetic field can be applied to the magnetic fluid with a simple structure. In addition, it is not necessary to energize constantly to form a magnetic field, and energy saving is also realized.

  According to a seventh aspect of the present invention, in the fluid-filled vibration isolator described in any one of the first to sixth aspects, the fluid chamber includes the first mounting member and the second mounting member. A stenosis region that is deformed by the relative displacement is provided, and the functional fluid is held in the stenosis region by the holding means.

  According to the seventh aspect, the flow of the functional fluid is likely to occur due to the relative displacement between the first mounting member and the second mounting member due to vibration input, and the vibration isolation effect based on the viscosity of the functional fluid is obtained. It is beneficial. In particular, even when the amplitude of the input vibration is small, the flow of the functional fluid is effectively generated, so that the intended vibration isolation effect can be obtained.

  According to an eighth aspect of the present invention, in the fluid-filled vibration isolator described in the first to seventh aspects, the viscosity of the functional fluid to which a voltage or a magnetic field is applied by the holding means is the incompressibility. It is made larger than the viscosity of the fluid.

  According to the eighth aspect, for example, an incompressible fluid having a relatively low viscosity flows in the orifice passage with a small flow resistance, thereby effectively exhibiting a vibration isolation effect based on the fluid flow action. Also, the vibration isolation effect due to the viscosity of the functional fluid can be effectively obtained.

  According to the present invention, since the incompressible fluid and the functional fluid are sealed in the fluid chamber, and the functional fluid is held at a predetermined position by the holding means, the fluid flow is generated in the fluid chamber by the vibration input. In addition, the desired vibration damping effect is exhibited by the energy damping action based on the flow resistance due to the viscosity of the functional fluid and the frictional resistance at the interface.

It is an engine mount as 1st embodiment of this invention, Comprising: II sectional drawing of FIG. II-II sectional drawing of FIG. It is an engine mount as 2nd embodiment of this invention, Comprising: III-III sectional drawing of FIG. IV-IV sectional drawing of FIG. FIG. 8 is an engine mount as a third embodiment of the present invention, taken along the line VV in FIG. 6. VI-VI sectional drawing of FIG. FIG. 10 is a cross-sectional view of the engine mount as a fourth embodiment of the present invention, taken along the line VII-VII in FIG. 8. VIII-VIII sectional drawing of FIG. FIG. 11 is an IX-IX cross-sectional view of FIG. 10 showing an engine mount as a fifth embodiment of the present invention. XX sectional drawing of FIG. FIG. 13 is an XI-XI cross-sectional view of FIG. 12 showing an engine mount as a sixth embodiment of the present invention. XII-XII sectional drawing of FIG. FIG. 15 is an XIII-XIII cross-sectional view of FIG. 14, which is an engine mount as a seventh embodiment of the present invention. XIV-XIV sectional drawing of FIG. FIG. 17 is an XV-XV sectional view of FIG. 16 showing an engine mount as an eighth embodiment of the present invention. XVI-XVI sectional drawing of FIG.

  Embodiments of the present invention will be described below with reference to the drawings.

  1 and 2 show an engine mount 10 for an automobile as a first embodiment of a fluid filled type vibration damping device having a structure according to the present invention. The engine mount 10 has a structure in which a first mounting member 12 and a second mounting member 14 are elastically connected by a main rubber elastic body 16. In the following description, the vertical direction refers to the vertical direction in FIG. 1, the horizontal direction refers to the horizontal direction in FIG. 1, and the front-rear direction refers to the horizontal direction in FIG.

  More specifically, the first mounting member 12 is a highly rigid member made of iron, aluminum alloy, or the like, and has a substantially cylindrical shape with a thick and small diameter. Further, a stopper member 18 is attached to the first attachment member 12. The stopper member 18 has a structure in which a bound stopper portion 22 protrudes on one side in the radial direction from an annular fixing portion 20 that is fitted and fixed to the first mounting member 12 and a rebound stopper portion 24 protrudes on the other side in the radial direction. It is said that. Note that the rebound stopper portion 24 protrudes from the fixing portion 20 on both sides in the axial direction, and has a larger axial dimension than the bound stopper portion 22.

  An intermediate sleeve 26 is extrapolated to the first mounting member 12. The intermediate sleeve 26 is a high-rigidity member similar to the first attachment member 12 and has a thin cylindrical shape with a large diameter. Further, the intermediate sleeve 26 is formed with a pair of window portions 28a and 28b. The window portion 28 passes through the substantially central portion in the axial direction of the intermediate sleeve 26 and extends in the circumferential direction with a predetermined length that is less than a half circumference. A circumferential groove 30 that opens to the outer periphery and extends in the circumferential direction is formed between the pair of windows 28a and 28b in the intermediate sleeve 26, and both circumferential ends of the circumferential groove 30 are a pair of windows. The portions 28a and 28b communicate with each other.

  The first mounting member 12 and the intermediate sleeve 26 are elastically connected by the main rubber elastic body 16. The main rubber elastic body 16 has a thick, large-diameter, generally cylindrical shape. The inner peripheral surface is vulcanized and bonded to the first mounting member 12 and the stopper member 18, and the outer peripheral end is an intermediate sleeve 26. Is vulcanized and bonded. The main rubber elastic body 16 is formed as an integrally vulcanized molded product including the first mounting member 12 and the intermediate sleeve 26.

  Further, the main rubber elastic body 16 is formed with a pair of pocket portions 32a and 32b that open to the outer peripheral surface. The pocket portion 32a has a concave shape that opens on the outer peripheral surface of the main rubber elastic body 16 in the radial direction from which the bound stopper portion 22 protrudes, and opens to the outer peripheral side through the window portion 28a. On the other hand, the pocket portion 32b is formed in a concave shape that opens to the outer peripheral surface of the main rubber elastic body 16 on the other radial direction from which the rebound stopper portion 24 protrudes, and opens to the outer peripheral side through the window portion 28b.

  Furthermore, a slit 34 is formed in the main rubber elastic body 16. The slit 34 penetrates the main rubber elastic body 16 in the axial direction, and extends in the circumferential direction on the outer peripheral side of the first mounting member 12 with a length of about a half circumference. Further, the slit 34 has both end portions in the circumferential direction approaching the inner peripheral surface of the intermediate sleeve 26. Thereby, the part which comprises the wall part of the window part 28b in the main rubber elastic body 16 is thinned by the slit 34, and is substantially independent, and the flexible film | membrane 36 is comprised by the said part. As is clear from the above, the flexible film 36 in this embodiment is formed integrally with the main rubber elastic body 16.

  Further, a seal rubber layer 38 integrally formed with the main rubber elastic body 16 is vulcanized and bonded to the outer peripheral surface of the intermediate sleeve 26. In the present embodiment, the inner surface of the circumferential groove 30 in the intermediate sleeve 26 is exposed, but the inner surface of the circumferential groove 30 may be covered with a rubber layer.

  The second mounting member 14 is fitted on the intermediate sleeve 26. The second mounting member 14 is a highly rigid member similar to the first mounting member 12 and has a thin cylindrical shape with a large diameter. The second attachment member 14 is externally fitted and fixed to the intermediate sleeve 26 by being subjected to diameter reduction processing such as an eight-way drawing in a state of being extrapolated to the intermediate sleeve 26. A space between the overlapping surfaces of the intermediate sleeve 26 and the second mounting member 14 is fluid-tightly sealed with a seal rubber layer 38.

  Further, the second mounting member 14 is externally fitted to the intermediate sleeve 26, so that the pair of window portions 28 a and 28 b of the intermediate sleeve 26 are covered with the second mounting member 14. As a result, a pressure receiving chamber 40 as a main liquid chamber in which a part of the wall part is constituted by the main rubber elastic body 16 is formed using the pocket part 32a, and a part of the wall part is flexible. An equilibrium chamber 42 as a secondary liquid chamber constituted by the film 36 is formed using the pocket portion 32b. In the present embodiment, the pressure chamber 40 and the equilibrium chamber 42 constitute a fluid chamber.

  An incompressible fluid 44 is enclosed in the pressure receiving chamber 40 and the equilibrium chamber 42. The incompressible fluid 44 is not particularly limited, and for example, water, ethylene glycol, alkylene glycol, polyalkylene glycol, silicone oil, or a mixed solution thereof is preferably employed. Further, in order to advantageously obtain an anti-vibration effect based on the fluid flow action described later, the incompressible fluid 44 is desirably a low-viscosity fluid of 0.1 Pa · s or less.

  Further, the outer peripheral opening of the circumferential groove 30 of the intermediate sleeve 26 is covered with the second mounting member 14, thereby forming a tunnel-like flow path extending in the circumferential direction. An orifice passage 46 that connects the pressure receiving chamber 40 and the equilibrium chamber 42 to each other is formed using one circumferential groove 30. In the other circumferential groove 30, a partition rubber 48 formed integrally with the main rubber elastic body 16 is formed on a part of the circumference, and the tunnel-like flow path is interrupted in the middle. The orifice passage 46 adjusts the ratio (A / L) of the passage cross-sectional area (A) and the passage length (L) while taking into account the wall spring rigidity of the pressure receiving chamber 40 and the equilibrium chamber 42, thereby allowing the fluid fluid to flow. The resonance frequency (tuning frequency) is set, and in this embodiment, it is set to a low frequency of about 10 Hz corresponding to engine shake.

Here, a magnetic fluid 50 as a functional fluid is sealed in the pressure receiving chamber 40. The magnetic fluid 50 is, for example, a surface of a ferromagnetic material such as magnetite (Fe ₃ O ₄ ) made into a powder (fine particles) of about 100 A with a hydrophobic surfactant and a liquid phase such as silicone oil. It is stably dispersed inside, and the fluid itself behaves magnetically without causing aggregation or precipitation in the liquid phase of the ferromagnetic material against the action of magnetic force or centrifugal force. Has properties. In short, as the functional fluid, for example, a fluid in which a holding force based on a magnetic force or Lorentz force is exerted on dispersed particles or molecules is employed. The liquid phase of the magnetic fluid 50 is preferably a fluid that is incompatible with the incompressible fluid 44, and for example, a combination of a hydrophilic fluid and a non-hydrophilic fluid can be suitably employed. Further, as the surfactant used for the surface treatment of the dispersed particles, those having an affinity for the liquid phase of the magnetic fluid 50 are used. However, the magnetic fluid 50 described above is merely an example, and various known fluids can be adopted.

  The magnetic fluid 50 is enclosed in the pressure receiving chamber 40 as an enclosed fluid together with the incompressible fluid 44. The magnetic fluid 50 is held by a permanent magnet 52 as a holding means fixed to the stopper member 18. The permanent magnet 52 is embedded in the protruding tip portion of the rebound stopper portion 24 and is magnetized in the protruding direction of the rebound stopper portion 24. As a result, the magnetic fluid 50 is increased in viscosity by being constantly applied with the magnetic field of the permanent magnet 52 and is exerted with a magnetic attraction force. Is retained. Note that the holding means of this embodiment is a magnetic field applying means for constantly applying a magnetic field to the magnetic fluid 50, as is apparent from the configuration of the permanent magnet 52.

  Furthermore, the viscosity of the magnetic fluid 50 held by applying the magnetic field of the permanent magnet 52 is larger than that of the incompressible fluid 44. The magnetic field of the permanent magnet 52 is set to a strength that can always hold the magnetic fluid 50 in a predetermined position, and is set appropriately according to the required viscosity of the magnetic fluid 50 and the like.

  In the present embodiment, the rebound stopper portion 24 protrudes into the pressure receiving chamber 40, so that the width is narrower than other portions between the protruding front end of the rebound stopper portion 24 and the second mounting member 14. A constricted region 54 is formed, and the magnetic fluid 50 is held in the constricted region 54. The narrowed region 54 is deformed by the relative displacement of the first attachment member 12 and the second attachment member 14 and is enclosed when the first attachment member 12 and the second attachment member 14 are relatively displaced. The fluid flows. Further, the constriction region 54 is provided off the opening of the orifice passage 46 on the pressure receiving chamber 40 side, and the magnetic fluid 50 is held at a position away from the opening of the orifice passage 46. In FIGS. 1 and 2, the magnetic fluid 50 is modeled by hatching and boundary lines different from the incompressible fluid 44 for easy understanding.

  The engine mount 10 having the structure according to the present embodiment has a first mounting member 12 attached to a power unit (not shown) and a second mounting member 14 attached to a vehicle body (not shown). Installed.

  When a low-frequency large-amplitude vibration corresponding to an engine shake is input in the vertical direction, a pressure fluctuation relative to the equilibrium chamber 42 is caused in the pressure receiving chamber 40. As a result, a fluid flow is generated between the pressure receiving chamber 40 and the equilibrium chamber 42 through the orifice passage 46, and the vibration isolation effect based on the fluid flow action is effectively exhibited.

  In the present embodiment, the magnetic fluid 50 is held by the permanent magnet 52 at a position outside the opening of the orifice passage 46 on the pressure receiving chamber 40 side, and the flow of the incompressible fluid 44 through the orifice passage 46 is caused by the magnetic fluid 50. Therefore, the vibration isolation effect by the orifice passage 46 is effectively exhibited.

  In the engine mount 10, when excessive vibration is input in the vertical direction, the stopper member 18 comes into contact with the second mounting member 14, so that the first mounting member 12 and the second mounting member 14 are relative to each other. The amount of displacement is limited. In short, in this embodiment, the bounce stopper means is configured by the abutment of the bound stopper portion 22 and the second mounting member 14, and the rebound stopper means is the abutment of the rebound stopper portion 24 and the second mounting member 14. It is configured.

  Further, when a downward load is input to the first mounting member 12, the damping action by the magnetic fluid 50 is also exerted. That is, the rebound stopper portion 24 of the stopper member 18 fixed to the first mounting member 12 is moved closer to the second mounting member 14, and the magnetic fluid 50 is allowed to move between the rebound stopper portion 24 and the second mounting member. When compressed between 14, the magnetic fluid 50 flows in the pressure receiving chamber 40, thereby exhibiting an energy damping action based on the viscous resistance of the magnetic fluid 50 and the like. As a result, it is possible to advantageously obtain a vibration isolation effect against the downward load input.

  In particular, since the magnetic fluid 50 is always held by the magnetic field of the permanent magnet 52 and there is no need for control according to the input vibration, the target vibration-proof effect can be stably obtained with a simple structure.

  In the present embodiment, the magnetic fluid 50 is held in the constricted region 54 formed between the second mounting member 14 and the tip of the rebound stopper portion 24, and the magnetic fluid 50 is compressed with respect to the downward input. It is easy. Therefore, the anti-vibration effect due to the viscosity of the magnetic fluid 50 is advantageously exhibited, and an effective anti-vibration effect can be obtained even when the amplitude of the input vibration is particularly small.

  Furthermore, since the magnetic fluid 50 is held on the contact surface of the rebound stopper means, the damping action of the magnetic fluid 50 can also be expected to reduce the impact at the time of stopper contact. In particular, since the magnetic fluid 50 can flow, it does not hinder the direct contact of the rebound stopper portion 24 with the second mounting member 14, but the first mounting member 12 and the second mounting member 14. It is possible to improve the stopper cushioning action and improve the durability of the rubber layer covering the front end surface of the rebound stopper portion 24 while securing the allowable relative displacement amount.

  Such a damping action based on the viscosity of the magnetic fluid 50 can be exerted even when the frequency of the input vibration is out of the tuning frequency of the orifice passage 46. Therefore, the anti-vibration effect effective in a wider frequency range. Can be obtained. Further, according to the structure of the present invention that encloses and holds the magnetic fluid 50, the static spring characteristics of the engine mount 10 and the anti-vibration characteristics against high-frequency small-amplitude vibration are compared with the case where the characteristics of the main rubber elastic body 16 are changed. It is possible to provide a high attenuation characteristic while avoiding an excessive adverse effect on.

  On the other hand, for input in the front-rear direction and the left-right direction, the internal pressure fluctuation of the pressure receiving chamber 40 hardly occurs, but fluid flow in the pressure receiving chamber 40 occurs, so that a damping action based on the viscosity of the magnetic fluid 50 is exhibited. Is done. As a result, the engine mount 10 can obtain an effective anti-vibration effect for not only the vertical vibration input but also the multi-directional vibration input.

  In the present embodiment, since the magnetic fluid 50 is sealed and held in the pressure receiving chamber 40 in which a part of the wall portion is constituted by the main rubber elastic body 16, the fluid flow is effectively generated at the time of vibration input, and the magnetic fluid 50 is generated. The vibration isolation effect due to the viscosity of the fluid 50 can be effectively obtained.

  In addition, the magnetic fluid 50 is used as the functional fluid, and the viscosity of the magnetic fluid 50 is increased by constantly applying the magnetic field of the permanent magnet 52. Therefore, the vibration isolation effect due to flow resistance and the like is more efficient. Can be obtained.

  Furthermore, since the permanent magnet 52 is used as the holding means, a magnetic field that holds the magnetic fluid 50 in a predetermined position can be formed with a simple structure. Moreover, by employing the permanent magnet 52, a magnetic field can be formed without requiring energy consumption such as energization, and energy saving can be achieved.

  3 and 4 show an engine mount 60 as a second embodiment of the present invention. The engine mount 60 includes permanent magnets 62 that are different in the number and position of the engine mount 10 from the first embodiment. In the following description, members and portions that are substantially the same as those in the first embodiment are denoted by the same reference numerals in the drawings, and the description thereof is omitted.

  More specifically, the permanent magnets 62 are respectively disposed at the front and rear end portions at the protruding tip of the rebound stopper portion 24, and both are magnetized in the front-rear direction (left-right direction in FIG. 4).

  By arranging the pair of permanent magnets 62 and 62 in this way, the magnetic field of the pair of permanent magnets 62 and 62 is applied to the magnetic fluid 50 sealed in the pressure receiving chamber 40, and the magnetic fluid 50 is magnetically applied. While the attractive force is exerted, the viscosity of the magnetic fluid 50 is increased. Thereby, the magnetic fluid 50 is always held on both the front and rear sides of the rebound stopper portion 24 as shown in FIG. In the present embodiment, the magnetic fluid 50 is held in a constricted region 64 formed between the front and rear wall portions of the pressure receiving chamber 40 and the rebound stopper portion 24.

  In the engine mount 60 having such a structure according to the present embodiment, an anti-vibration effect based on the viscous resistance of the magnetic fluid 50 and the like is advantageously exhibited particularly with respect to vibration input in the front-rear direction. Therefore, in combination with the anti-vibration effect by the orifice passage 46 exhibited against the vibration input in the vertical direction, the anti-vibration in multiple directions is effectively realized.

  5 and 6 show an engine mount 70 as a third embodiment of the present invention. The engine mount 70 of this embodiment includes a pair of permanent magnets 72 and 72.

  More specifically, the pair of permanent magnets 72, 72 are both fixed to the main rubber elastic body 16 and are held in an exposed state on the inner surfaces of the front and rear walls of the pressure receiving chamber 40. The pair of permanent magnets 72 and 72 are both magnetized in the front-rear direction (left-right direction in FIG. 6).

  As shown in FIG. 6, the pair of permanent magnets 72, 72 are arranged and a magnetic field is constantly applied to the magnetic fluid 50, so that the magnetic fluid 50 has increased viscosity before and after the pressure receiving chamber 40 as shown in FIG. It is always held on the inner wall surface. In the present embodiment, similarly to the second embodiment, the magnetic fluid 50 is held in a constricted region 74 formed between the front and rear wall portions of the pressure receiving chamber 40 and the rebound stopper portion 24.

  In the engine mount 70 having the structure according to the present embodiment as described above, an anti-vibration effect based on the viscous resistance of the magnetic fluid 50 is advantageously exhibited particularly with respect to vibration input in the front-rear direction. Therefore, in combination with the anti-vibration effect by the orifice passage 46 exhibited against the vibration input in the vertical direction, the anti-vibration in multiple directions is effectively realized.

  7 and 8 show an engine mount 80 as a fourth embodiment of the present invention. The engine mount 80 of the present embodiment includes a permanent magnet 82.

  More specifically, the permanent magnet 82 is fixed to the main rubber elastic body 16 and is held in a state of being exposed on the inner surface of the upper wall of the pressure receiving chamber 40. Further, the permanent magnet 82 is disposed on the opposite side of the circumferential direction with the rebound stopper portion 24 between the opening of the orifice passage 46. The permanent magnet 82 is magnetized in the vertical direction (the vertical direction in FIG. 7).

  By arranging the permanent magnet 82 in this way, as shown in FIG. 7, the magnetic fluid 50 is always held on the inner surface of the upper wall of the pressure receiving chamber 40 in a state where the viscosity is increased. The magnetic fluid 50 is held at a position outside the opening of the orifice passage 46 by the holding force of the permanent magnet 82 due to the magnetic field. In the present embodiment, the magnetic fluid 50 is held in the constricted region 84 formed between the left wall portion of the pressure receiving chamber 40 and the rebound stopper portion 24.

  In the engine mount 80 having the structure according to the present embodiment as described above, an anti-vibration effect based on the viscous resistance of the magnetic fluid 50 is advantageously exhibited particularly with respect to vibration input in the left-right direction. Therefore, in combination with the anti-vibration effect by the orifice passage 46 exhibited against the vibration input in the vertical direction, the anti-vibration in multiple directions is effectively realized.

  9 and 10 show an engine mount 90 as a fifth embodiment of the present invention. The engine mount 90 has a structure in which a first mounting member 92 and a second mounting member 94 are elastically connected by a main rubber elastic body 96. In the following description, the vertical direction means the vertical direction in FIG. 9 in principle.

  More specifically, the first mounting member 92 is a high-rigidity member having a substantially circular block shape formed of iron, aluminum alloy, or the like, and has a screw hole 98 extending on the central axis and opening on the upper surface. Has been. A caulking piece 100 is integrally provided at the lower end of the first mounting member 92.

  The second mounting member 94 is a highly rigid member like the first mounting member 92, has a thin cylindrical shape with a large diameter, and has a step portion provided in the middle in the axial direction. The upper part is larger in diameter than the lower part.

  The first mounting member 92 and the second mounting member 94 are arranged on substantially the same central axis, and the first mounting member 92 and the second mounting member 94 are elastically connected by the main rubber elastic body 96. ing. The main rubber elastic body 96 has a thick, large-diameter, generally frustoconical shape. The end on the small diameter side is vulcanized and bonded to the first mounting member 92, and the end on the large diameter side is the first. The second mounting member 94 is vulcanized and bonded.

  Further, a large diameter recess 102 is formed in the main rubber elastic body 96. The large-diameter recess 102 is a recess that has a substantially mortar shape in the opposite direction, and is open to the lower surface of the main rubber elastic body 96. Furthermore, a cylindrical sealing rubber layer 104 integrally formed with the main rubber elastic body 96 extends downward, and the inner peripheral surface of the small diameter portion of the second mounting member 94 is covered with the sealing rubber layer 104. Yes. In the present embodiment, the first attachment member 92 is disposed vertically through the center in the radial direction of the main rubber elastic body 96, and the caulking piece 100 of the first attachment member 92 is a large-diameter recess. Projecting into 102.

  A flexible film 106 is attached to the second attachment member 94. The flexible film 106 is a thin circular rubber film, and has a slack in the vertical direction. In the flexible membrane 106, an annular fixing member 108 fixed to the outer peripheral end is fluid-tightly fitted to the lower end portion of the second mounting member 94. The flexible film 106 of this embodiment is a separate body from the main rubber elastic body 96.

  By attaching the flexible membrane 106, a fluid chamber 110 is formed between the main rubber elastic body 96 and the flexible membrane 106, and the incompressible fluid 44 is sealed in the fluid chamber 110. .

  A partition member 112 is disposed in the fluid chamber 110. The partition member 112 has a structure in which the partition member main body 114 and the bottom metal fitting 116 are overlapped, and the movable film 118 is sandwiched between the partition member main body 114 and the bottom metal fitting 116.

  The partition member main body 114 is a hard member formed of metal or synthetic resin, and has a thick, substantially disk shape. In addition, the partition member main body 114 is formed with a circumferential groove 120 that opens to the outer peripheral surface and extends in a length less than one circumference in the circumferential direction. In addition, while the inner peripheral part of the partition member main body 114 is made thinner than an outer peripheral part, the circular center hole penetrated up and down is formed in the center part.

  The bottom metal fitting 116 has a thin, substantially annular plate shape, and has a stepped shape in which the inner peripheral portion is located above the outer peripheral portion. And the bottom metal fitting 116 is fixed by overlapping the outer peripheral portion with the outer peripheral portion of the partition member main body 114 from below.

  Further, a movable film 118 is disposed between the overlapping surfaces of the partition member main body 114 and the inner peripheral portion of the bottom metal fitting 116. The movable film 118 has a substantially disk shape, and a thick outer peripheral end is sandwiched between the partition member main body 114 and the bottom metal fitting 116, and a central portion is formed between the partition member main body 114 and the bottom. Elastic deformation in the vertical direction is allowed by the central hole of the metal fitting 116.

  The partition member 112 having such a structure is disposed so as to extend in the direction perpendicular to the axis in the fluid chamber 110, and has an outer peripheral surface superimposed and held on the second mounting member 94. The end portion is sandwiched between the lower surface of the main rubber elastic body 96 and the fixing member 108 in the axial direction.

  Thereby, the fluid chamber 110 is divided into two parts up and down across the partition member 112, and a pressure receiving chamber 122 in which a part of the wall portion is configured by the main rubber elastic body 96 is formed above the partition member 112. On the other hand, an equilibration chamber 124 in which a part of the wall portion is formed of the flexible film 106 is formed below the partition member 112.

  Further, both end portions of the circumferential groove 120 covered with the second mounting member 94 and having a tunnel shape are communicated with one of the pressure receiving chamber 122 and the equilibrium chamber 124, and the pressure receiving chamber 122 and the equilibrium chamber 124 are mutually connected. A communicating orifice passage 126 is formed.

  Furthermore, the hydraulic pressure of the pressure receiving chamber 122 is exerted on the upper surface of the movable film 118, and the hydraulic pressure of the equilibrium chamber 124 is exerted on the lower surface, and due to the relative pressure fluctuation between the pressure receiving chamber 122 and the equilibrium chamber 124. The movable film 118 is elastically deformed up and down so that the hydraulic pressure is transmitted.

  Here, a magnetic fluid 50 is sealed in the pressure receiving chamber 122, and the magnetic fluid 50 is held at a predetermined position by permanent magnets 128, 128, 128, 128 disposed in the pressure receiving chamber 122. . As shown in FIG. 10, the permanent magnets 128 extend in a circumferential direction with a predetermined length, and four permanent magnets 128 are arranged at a predetermined distance from each other on the same circumference.

  Further, the permanent magnets 128, 128, 128, 128 are supported by the first mounting member 92 and are disposed in the pressure receiving chamber 122. Specifically, as shown in FIG. 9, the permanent magnet 128 is fixed to the support member 130, and the support member 130 is caulked and fixed to the caulking piece 100 of the first mounting member 92. The mounting member 92 is supported. The support member 130 has a substantially bottomed cylindrical shape in the opposite direction, and has a tapered shape in which the outer peripheral end portion of the upper bottom wall portion is inclined downward toward the outer periphery. The four permanent magnets 128, 128, 128, 128 are fixed to the outer peripheral end of the upper bottom wall portion of the support member 130. Each permanent magnet 128 is magnetized in the overlapping direction with respect to the support member 130.

  The magnetic fluid 50 sealed in the pressure receiving chamber 122 is increased in viscosity by applying the magnetic field of the permanent magnets 128, 128, 128, 128 at all times, and exerts a magnetic attraction force. ing. Thereby, the magnetic fluid 50 is always held in the constricted region 132 formed between the main rubber elastic body 96 and the upper bottom wall portion of the support member 130.

  The engine mount 90 having such a structure is attached to the vehicle by attaching the first attachment member 92 to a power unit (not shown) and attaching the second attachment member 94 to a vehicle body (not shown).

  When a low-frequency large-amplitude vibration corresponding to an engine shake is input in the vertical direction with the vehicle mounted, a target vibration-proof effect is exhibited based on the resonance action of the fluid flowing through the orifice passage 126 and the like. .

  Further, when medium to high frequency small amplitude vibration corresponding to idling vibration or traveling noise is input, the orifice passage 126 is substantially blocked by anti-resonance, and the hydraulic pressure absorbing action due to elastic deformation of the movable film 118 is effective. Based on this, the intended anti-vibration effect is exhibited.

  In addition, an anti-vibration effect based on the viscous resistance of the magnetic fluid 50 and the like is exerted against axial and perpendicular vibration inputs. That is, when the first attachment member 92 is relatively displaced with respect to the second attachment member 94, the narrowed region 132 formed between the main rubber elastic body 96 and the support member 130 is deformed, and the fluid in the narrowed region 132 is fluidized. Flow is produced. Therefore, based on the viscosity of the magnetic fluid 50 held by the permanent magnet 128, a damping effect on the vibration energy can be obtained.

  As described above, the bowl-shaped engine mount 90 can also be applied to a plurality of types of input vibrations having different input directions and frequencies with a simple structure, similar to the cylindrical fluid-filled vibration isolator, by applying the present invention. On the other hand, an effective anti-vibration effect can be obtained.

  11 and 12 show an engine mount 140 as a sixth embodiment of the present invention. In the engine mount 140, the permanent magnet 142 is fixed to the outer peripheral surface of the first mounting member 92, and the magnetic fluid 50 is held in the holding recess 144 formed in the main rubber elastic body 96.

  More specifically, the permanent magnet 142 is disposed in each of the four recesses 146, 146, 146, and 146 that open to the outer peripheral surface of the first mounting member 92.

  The holding recess 144 is a recess extending substantially vertically with a predetermined length in the circumferential direction, and is open to the upper bottom surface of the large-diameter recess 102. Further, four holding recesses 144 are formed on the inner peripheral portion of the main rubber elastic body 96 at a predetermined distance on the circumference. Furthermore, the holding recess 144 is formed to a depth that reaches the outer peripheral side of the permanent magnet 142, and the magnetic field of each permanent magnet 142 acts on each holding recess 144. In the present embodiment, the region in the holding recess 144 constitutes a part of the pressure receiving chamber 122, and the constriction region is provided in the holding recess 144.

  As shown in FIG. 11, the magnetic fluid 50 sealed in the pressure receiving chamber 122 is applied with the magnetic field of the permanent magnet 142, increases in viscosity, and exerts a magnetic attraction force, so In place 144. When vibration is input between the first mounting member 92 and the second mounting member 94, the holding recess 144 is deformed by the elastic deformation of the main rubber elastic body 96, and the fluid enters the holding recess 144. The flow comes to occur. As a result, the intended vibration isolation effect is effectively exhibited by the energy damping action based on the viscosity of the magnetic fluid 50 and the like.

  In addition, since the permanent magnet 142 is directly supported by the first mounting member 92 and the constricted region is constituted by the holding recess 144 formed in the main rubber elastic body 96, the fifth embodiment is provided. A member such as the support member 130 is not required, and a simple structure with a small number of parts can be achieved.

  13 and 14 show an engine mount 150 as a seventh embodiment of the present invention. In the engine mount 150, the permanent magnet 152 is fixed to a support member 154 provided on the partition member 112 and supported on the second mounting member 94 side.

  More specifically, the support member 154 integrally includes a fixing portion 156 that is continuously fixed to the upper surface of the partition member 112 in the circumferential direction, and a plurality of column portions 158 that protrude upward from the fixing portion 156. The permanent magnet 152 is superimposed and fixed to the tip portion of the support column 158. Note that the tip portion of the column portion 158 to which the permanent magnet 152 is fixed has a tapered shape that inclines inward toward the tip side, and the inner surface of the wall of the large-diameter recess 102 and the tip portion of the column portion 158. A narrowed region 160 is formed between the two. The permanent magnet 152 is magnetized in the overlapping direction with respect to the column portion 158.

  As shown in FIG. 13, the magnetic fluid 50 sealed in the pressure receiving chamber 122 is held in the constricted region 160 when the magnetic field of the permanent magnet 152 is applied. Then, vibration is input between the first mounting member 92 and the second mounting member 94, and the first mounting member 92 and the second mounting member 94 are relatively displaced, whereby the constriction region 160 is deformed. Fluid flow. As a result, an energy attenuating action based on the viscosity of the magnetic fluid 50 is exhibited, and the intended vibration isolation effect can be obtained effectively.

  15 and 16 show an engine mount 170 as an eighth embodiment of the present invention. In the engine mount 170, permanent magnets 172 are fixed to a plurality of support columns 174 protruding from the partition member main body 114, supported on the second mounting member 94 side, and formed to protrude from the main rubber elastic body 96. It is made to oppose the constricted convex part 176.

  In more detail, the support | pillar part 174 protrudes upwards from the inner peripheral edge part of the partition member main body 114, and four are arrange | positioned at predetermined intervals in the circumferential direction. In addition, a concave groove 175 that opens to the inner peripheral surface is formed in the column portion 174, and a permanent magnet 172 is fitted into and fixed to the concave groove 175. The permanent magnet 172 is magnetized in the overlapping direction with the support column 174 (in the direction perpendicular to the mount axis).

  The main rubber elastic body 96 is formed with four constricted convex portions 176, 176, 176, and 176 that protrude downward from the upper bottom wall portion of the large-diameter recess 102. The narrowing convex portion 176 extends to a position where the tip portion faces the permanent magnet 172 in the direction perpendicular to the axis, and a narrowing region 178 is formed between the permanent magnet 172 and the narrowing convex portion 176.

  As shown in FIG. 16, the magnetic fluid 50 sealed in the pressure receiving chamber 122 is held in the constriction region 178 when the magnetic field of the permanent magnet 172 is applied. When the first mounting member 92 and the second mounting member 94 are relatively displaced by vibration input, fluid flow is generated between the opposing surfaces of the support column 174, the permanent magnet 172, and the constriction convex portion 176, and the viscous resistance The anti-vibration effect based on the above has been effectively demonstrated.

  Further, even if the support column 174 and the permanent magnet 172 and the constricted convex portion 176 come close to each other and come into contact with each other in the direction perpendicular to the axis, the constricted convex portion 176 elastically deforms to reduce the impact force due to the contact. The hitting sound is reduced.

  As mentioned above, although embodiment of this invention was explained in full detail, this invention is not limited by the specific description. For example, the functional fluid may be sealed and held in two or more chambers constituting the fluid chamber, and is not limited to a mode in which the functional fluid is sealed and held only in the pressure receiving chamber as in the above embodiment.

  Moreover, in the said embodiment, although the structure provided with two chambers, a pressure receiving chamber and an equilibrium chamber, is illustrated as a fluid chamber, A fluid chamber is not necessarily limited to the structure provided with only two chambers, It comprises only one chamber. It may be provided, and may be provided with three or more rooms.

  Further, the orifice passage is not essential, and the orifice passage is not provided particularly when the fluid chamber is composed of only one chamber.

  Further, when the fluid chamber is composed of two chambers, it is not always necessary to be a combination of a pressure receiving chamber and an equilibrium chamber. For example, both of the two chambers are composed of a body rubber elastic body partly. It may be a pressure receiving chamber.

  Moreover, in the said embodiment, although the combination of a magnetic fluid and a permanent magnet is illustrated as a functional fluid and a holding means, a functional fluid and a holding means are not limited to them. Specifically, for example, a magnetic fluid is used as the functional fluid, and an electromagnet is used as the holding means, and the electromagnet is always energized to obtain a magnetic field for holding the magnetic fluid. Further, for example, an electrorheological fluid is used as the functional fluid, and an energizing unit including an electrode is used as the holding unit, and a voltage (electric field) is constantly applied to the electrorheological fluid by the energizing unit. The viscosity of the fluid can be increased and held in place.

10, 60, 70, 80, 90, 140, 150, 170: engine mount (fluid-filled vibration isolator), 12, 92: first mounting member, 14, 94: second mounting member, 16, 96 : Body rubber elastic body, 36, 106: flexible membrane, 40, 122: pressure receiving chamber (main liquid chamber), 42, 124: equilibrium chamber (sub liquid chamber), 44: incompressible fluid, 46, 126: Orifice passage, 50: magnetic fluid (functional fluid), 52, 62, 72, 82, 128, 142, 152, 172: permanent magnet (holding means, magnetic field applying means), 54, 64, 74, 84, 132, 160, 178: Stenosis region, 110: Fluid chamber

Claims (8)

A fluid in which the first mounting member and the second mounting member are elastically connected by the main rubber elastic body, and a part of the wall portion is configured by the main rubber elastic body, and an incompressible fluid is sealed inside. In the fluid-filled vibration isolator in which the chamber is formed,
A fluid characterized in that a functional fluid is sealed in the fluid chamber, and holding means for constantly applying a voltage or a magnetic field to the functional fluid to hold the functional fluid in a predetermined position is provided. Enclosed vibration isolator.   The fluid chamber is configured to include a main liquid chamber and a sub liquid chamber, an orifice passage is formed to communicate the main liquid chamber and the sub liquid chamber with each other, and the main liquid chamber and the sub liquid chamber are connected to each other. The fluid-filled vibration isolator according to claim 1, wherein at least one of the functional fluids is sealed and held by the holding means.   The main liquid chamber is a pressure receiving chamber in which a part of the wall portion is configured by the main rubber elastic body, and the secondary liquid chamber is an equilibrium chamber in which a part of the wall portion is configured by a flexible film; The fluid-filled vibration isolator according to claim 2, wherein the functional fluid is sealed in the pressure receiving chamber and held by the holding means.   The fluid-filled vibration isolator according to claim 2 or 3, wherein the functional fluid is held by the holding means at a position off the opening of the orifice passage.   The fluid-filled type prevention according to any one of claims 1 to 4, wherein the functional fluid is a magnetic fluid, and the holding means is a magnetic field applying means for applying a magnetic field to the functional fluid. Shaker.   The fluid-filled vibration isolator according to claim 5, wherein the magnetic field applying means is a permanent magnet.   The said fluid chamber is provided with the constriction area | region deform | transformed by the relative displacement of said 1st attachment member and said 2nd attachment member, The said functional fluid is hold | maintained in this constriction area | region by the said holding means. Item 7. The fluid-filled vibration isolator according to any one of Items 1 to 6.   The fluid-filled vibration isolator according to any one of claims 1 to 7, wherein a viscosity of the functional fluid to which a voltage or a magnetic field is applied by the holding unit is larger than a viscosity of the incompressible fluid. .

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