JP2010084780A - Fluid-filled engine mount - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid-filled engine mount of new structure, including an orifice passage exhibiting a high damping effect in a wide frequency range against the engine shake. <P>SOLUTION: Flexible films 38 and 80 are respectively arranged on a large diameter end surface side and a tapered outer peripheral surface side of a body rubber elastic body 16 to form a first balance chamber 88 and a second balance chamber 92 separately from each other. A first orifice passage 90 communicating a pressure receiver chamber 86 with the first balance chamber 88 and a second orifice passage 96 communicating the pressure receiver chamber 86 with the second balance chamber 92 are tuned to have a damping peak frequency different from each other in the frequency range of the engine shake. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a fluid-filled engine mount that obtains an anti-vibration effect based on the flow action of a fluid sealed inside.

  2. Description of the Related Art Conventionally, a fluid-filled engine mount in which a fluid is sealed is known as a kind of engine mount for supporting a power unit on a vehicle body in a vibration-proof manner. In such a fluid-filled engine mount, generally, a pressure receiving chamber and a balance chamber in which a fluid is sealed are formed, respectively, and an orifice passage that connects the pressure receiving chamber and the balance chamber to each other is provided. The vibration isolation effect is exhibited based on the fluid action such as the resonance action of the fluid that is caused to flow through the orifice passage when the vibration is input.

  By the way, there is an engine shake with a low frequency and a large amplitude as one of the vibrations which are problematic in automobiles. Therefore, conventionally, the orifice passage in the fluid-filled engine mount is tuned to a low frequency region corresponding to the engine shake, and a high damping effect is obtained by utilizing the resonance action of the fluid flowing through the orifice passage.

  In addition, with regard to engine shake, generally, the orifice passage is tuned for one specific frequency. This is because rigid body vibration in one vibration system in which a power unit including an engine is supported by an engine mount is considered as a target.

  However, with regard to such engine shake, it has been found that a more effective anti-vibration effect may be exhibited by setting the attenuation peak in a plurality of frequency ranges or a wide frequency range. There are various reasons for this, but according to the examination result of the present inventor, for example, it can be attributed to the amplitude dependency of the spring constant of the engine mount that supports the power unit. In particular, if the dynamic spring constant of the mount is reduced in order to improve ride comfort against idling vibration or the like, the change in the spring characteristics of the mount due to amplitude dependence tends to increase. As a result, regarding the engine shake, it is conceivable that the frequency of the engine shake in question changes depending on the magnitude of the input excitation force.

  For this reason, in order to obtain a more effective anti-vibration effect against the engine shake, it is effective to form an orifice passage that can exhibit a high damping effect in a wide frequency range with respect to the engine shake. That is why the present inventor thought.

  However, in a fluid-filled engine mount having a conventional structure, it has been difficult to tune the orifice passage so that a high damping effect can be exhibited in a wide frequency range with respect to the engine shake.

  That is, for example, as described in Patent Document 1, two orifice passages that are tuned to different frequency ranges by using a valve body with a flow rate restriction such as a movable plate function selectively according to input vibration. It is possible to make it. However, if both of the input vibrations to be tuned in the two orifice passages are engine shakes, there is almost no difference in amplitude, so that it is extremely difficult to selectively function the two orifice passages.

  In Patent Document 2, two equilibrium chambers are formed independently, and a first orifice passage connecting one equilibrium chamber to the pressure receiving chamber and a second orifice passage connecting the other equilibrium chamber to the pressure receiving chamber. Have been proposed in parallel. By adopting such a structure, it is conceivable to tune both the first orifice passage and the second orifice passage to the frequency ranges slightly different from each other by engine shake. However, since the engine shake has a large amplitude, it is difficult to secure a sufficient amount of volume change in each of the equilibrium chambers divided into a plurality of parts. In addition, it is difficult to secure two orifice passage formation spaces for tuning to a low frequency region such as an engine shake in the flat partition member, and it is difficult to put it to practical use.

JP 2005-233243 A JP-A-9-210117

  Here, the present invention has been made in the background as described above, and the problem to be solved is to provide an orifice passage that can exhibit a high damping effect in a wide frequency range with respect to the engine shake. Another object of the present invention is to provide a fluid-filled engine mount having a novel structure.

  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.

  In the fluid-filled engine mount according to the present invention, the inner shaft member is spaced apart from one opening side of the cylindrical outer tube member, and the inner shaft is disposed at the small-diameter side end of the substantially truncated cone-shaped main rubber elastic body. The outer cylindrical member is fixed to the outer peripheral surface of the large-diameter side of the main rubber elastic body so that the inner shaft member and the outer cylindrical member are elastically connected to each other, and is opposed to the large-diameter portion of the main rubber elastic body. By arranging the member and supporting the partition member with the outer cylinder member, a pressure receiving chamber is formed between the main rubber elastic body and the partition member so that vibration is input, and the pressure receiving chamber is sandwiched between the partition members. The first flexible membrane is disposed on the opposite side to form a first equilibrium chamber between which the volume change is allowed between the partition member and the first flexible membrane. A second flexible membrane covering the tapered outer peripheral surface of the body, A second equilibrium chamber in which volume change is allowed is formed between the elastic body and the second flexible membrane, and the pressure receiving chamber, the first equilibrium chamber, and the second equilibrium chamber are incompressible, respectively. A first orifice passage for enclosing a fluid and communicating the pressure receiving chamber with the first equilibrium chamber; and a second orifice passage for communicating the pressure receiving chamber with the second equilibrium chamber. The second orifice passage and the second orifice passage are tuned to have different attenuation peak frequencies in the frequency range of the engine shake.

  In the fluid-filled engine mount having the structure according to the present invention as described above, the flexible rubber is disposed on each of the large-diameter end face side and the tapered outer peripheral face side of the main rubber elastic body, and the first is independent from each other. Since the equilibrium chamber and the second equilibrium chamber are formed, a sufficient volume can be secured in any equilibrium chamber, and an effective area of the flexible membrane can be effectively secured. I can do it. Therefore, it is possible to secure a sufficient fluid flow amount, and it is possible to effectively exhibit a high damping effect based on the resonance action of the fluid that can flow through the orifice passage even for an engine shake with a large amplitude. Become.

  In addition, since the first equilibrium chamber and the second equilibrium chamber are formed with the main rubber elastic body interposed therebetween, it is possible to secure different formation regions for the first orifice passage and the second orifice passage. This makes it possible to form an orifice passage tuned to the engine shake with a sufficient passage length and passage cross-sectional area. As a result, the fluid flow amount can be ensured, and hence the vibration isolation effect (high damping effect) based on the resonance action of the fluid flowing through the orifice passage can be achieved.

  Further, since both the first orifice passage and the second orifice passage are tuned to a frequency range corresponding to the engine shake, fluid flow is generated through both orifice passages when vibration of the engine shake is input. It becomes like this. At that time, since the tuning of the first orifice passage and the second orifice is slightly different, the amount of fluid flow in the orifice passage adapted to the input vibration is relatively increased. As a result, as a whole, the high attenuation effect by the orifice passage can be exhibited in a wide frequency range.

  Further, in the present invention, based on the resonance frequency of the fluid that is caused to flow through the second orifice passage and the increase frequency region of the damping coefficient that is exhibited based on the resonance action of the fluid that is caused to flow through the first orifice passage. The first orifice passage and the first passage are arranged so that the increased frequency region of the attenuation coefficient to be exhibited overlaps the high frequency side portion of one of the increased frequency regions and the low frequency side portion of the other increased frequency region. It is desirable that the tuning frequencies of the two orifice passages are set. As a result, the frequency range in which the attenuation coefficient is increased can be widened. As a result, it is possible to exhibit a high attenuation effect by the orifice passage in a wide frequency range.

  Further, in the present invention, a thin rubber elastic film having a slack is assembled so as to cover the other opening of the outer cylinder member, and the first flexible film is constituted by the rubber elastic film. In addition, it is desirable that a partition member is disposed between the main rubber elastic body and the rubber elastic film in the axial direction. Thereby, the volume of the first equilibrium chamber can be secured more efficiently.

  Furthermore, in the present invention, it is desirable that the first orifice passage and the second orifice passage are formed so as to extend at least partially in the circumferential direction of the outer cylinder member. Thereby, each passage length of the first orifice passage and the second orifice passage can be efficiently secured in a small space.

  In the present invention, the movable member is disposed in the center of the partition member in a state where the amount of displacement is limited, and when the vibration in the frequency range higher than the frequency range of the engine shake is input, the movable member It is desirable that a fluid flow be generated between the pressure receiving chamber and the first equilibrium chamber based on the displacement of the first pressure chamber. As a result, an effective anti-vibration effect can be exhibited even for vibrations in a frequency range higher than the frequency range of the engine shake.

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

  FIG. 1 shows an automobile engine mount 10 as a first embodiment of a fluid-filled engine mount according to the present invention. The engine mount 10 has a structure in which an inner metal member 12 as an inner shaft member and an outer tube member 14 as an outer tube member are elastically connected by a main rubber elastic body 16, and the inner metal member 12 is not shown. On the other hand, the outer cylinder fitting 14 is attached to a vehicle body (not shown) so as to support the vibration of the power unit against the body. Further, under such a mounted state, the shared support load of the power unit and the main vibration to be damped are input between the inner fitting 12 and the outer cylinder fitting 14 in the direction of the central axis of the engine mount 10. It has become so. In the following description, the vertical direction means the vertical direction in FIG. 1 in principle.

  More specifically, the inner metal fitting 12 is made of a metal material such as steel or an aluminum alloy, and has an inverted truncated cone shape as a whole. A fitting portion 18 that protrudes upward in the axial direction is integrally formed at the large-diameter end of the inner metal fitting 12. Further, the fitting portion 18 is formed with a screw hole 20 that opens to the upper surface. And the inner metal fitting 12 is attached to a power unit with the volt | bolt (not shown) screwed by the screw hole 20 of the fitting part 18. As shown in FIG.

  The main rubber elastic body 16 is vulcanized and bonded to the inner metal fitting 12. The main rubber elastic body 16 has a substantially frustoconical shape, and has a tapered cylindrical outer peripheral surface that gradually decreases in diameter in the axial direction. And the inner metal fitting 12 is vulcanized and bonded in a state where it is inserted downward in the axial direction from the end surface on the small diameter side of the main rubber elastic body 16. In the present embodiment, the seal rubber layer 22 formed integrally with the main rubber elastic body 16 is attached to substantially the entire outer peripheral surface of the fitting portion 18 in the inner metal member 12. The main rubber elastic body 16 is formed with a large-diameter recess 24 that opens to the large-diameter side end face.

  A cylindrical outer cylindrical metal fitting 26 is vulcanized and bonded to the outer peripheral surface of the main rubber elastic body 16 on the large diameter end portion side. That is, the main rubber elastic body 16 is formed as an integrally vulcanized molded product including the inner metal fitting 12 and the outer cylindrical metal fitting 26. Then, the main rubber elastic body 16 and the outer cylindrical metal fitting 26 are vulcanized and bonded in this manner, so that the opening on the upper side in the axial direction of the outer cylindrical metal fitting 26 is fluid-tightly covered with the main rubber elastic body 16.

  Further, the main rubber elastic body 16 is integrally formed with a thick cylindrical rubber outer peripheral edge 28 extending downward in the axial direction along the inner peripheral surface of the outer peripheral cylindrical metal fitting 26. In particular, in the present embodiment, the rubber outer peripheral edge 28 protrudes downward in the axial direction from the lower end surface in the axial direction of the outer peripheral cylindrical metal fitting 26.

  Furthermore, a ring-shaped flange-shaped portion 30 that extends outward in the direction perpendicular to the axis is integrally formed on the peripheral edge of the upper opening of the outer cylindrical metal fitting 26. In addition, a notch-shaped opening window 31 is formed in the flange-shaped portion 30.

  On the other hand, the outer cylinder fitting 14 is formed of a metal material such as iron or aluminum alloy, and has a large-diameter cylindrical shape as a whole. Further, a stepped portion 32 is formed at the axially intermediate portion of the outer cylindrical metal fitting 14, and the axially upper side is a large-diameter portion 34 with the stepped portion 32 interposed therebetween, while the axially lower side is a small-diameter portion. 36. And the outer cylinder metal fitting 14 is attached to a vehicle body via the cylindrical bracket which is not shown in figure.

  In addition, a first flexible rubber film 38 as a first flexible film is disposed in the axially lower opening of the outer cylindrical metal member 14. The first flexible rubber film 38 is formed of a thin rubber elastic film having a substantially circular dome shape that is bent so as to be easily deformed, and an outer peripheral edge portion of the first flexible rubber film 38 has a small diameter of the outer cylinder fitting 14. Vulcanized and bonded to the inner peripheral surface of the portion 36. Thereby, the opening part of the axial direction lower side of the outer cylinder metal fitting 14 is covered with the 1st flexible rubber film 38 fluid-tightly. In the present embodiment, the seal rubber layer 40 formed integrally with the first flexible rubber film 38 is attached to substantially the entire inner peripheral surface of the outer tubular fitting 14.

  Such an outer tube fitting 14 is fitted and fixed to the outer tube fitting 26 by being extrapolated into an integrally vulcanized molded product of the main rubber elastic body 16 and subjected to diameter reduction processing such as eight-way drawing. . Thereby, the outer cylinder fitting 14 is fixed to the outer peripheral surface of the main rubber elastic body 16. As a result, the inner metal fitting 12 and the outer cylinder metal fitting 14 are elastically connected by the main rubber elastic body 16. In this state, the seal rubber layer 40 is sandwiched between the flange-shaped portion 30 of the outer cylindrical metal fitting 26 and the large-diameter portion 34 of the outer cylindrical metal fitting 14. Thus, a fluid chamber 42 is formed between the opposing surfaces of the main rubber elastic body 16 and the first flexible rubber film 38 so as to be blocked from the external space and filled with an incompressible fluid.

  As the fluid sealed in the fluid chamber 42, water, alkylene glycol, polyalkylene glycol, silicone oil, or the like can be used. In particular, in order to effectively obtain a vibration isolation effect based on the resonance action of the fluid described later, A low viscosity fluid having a viscosity of 0.1 Pa · s or less is preferably employed.

  A partition member 44 is disposed between the opposing surfaces of the main rubber elastic body 16 and the first flexible rubber film 38. Therefore, the partition member 44 of the present embodiment includes an upper partition member main body 46, a lower partition member main body 48, and a bottom metal fitting 50.

  The upper partition member body 46 is made of a metal material such as an aluminum alloy or a hard material such as a synthetic resin material, and has a large-diameter cylindrical shape as a whole. Therefore, in the present embodiment, an inner protrusion 52 that protrudes radially inward is formed on the lower end portion in the axial direction of the upper partition member main body 46 over the entire circumference. In particular, in this embodiment, the inward protrusion 52 is formed so as to continuously extend in a substantially constant rectangular cross-sectional shape over the entire circumference. Thus, the axially upper surface of the inward projection 52 is a flat annular seal contact surface.

  Further, the upper partition member main body 46 is formed with a circumferential groove 54 that opens to the outer peripheral surface and extends in the circumferential direction and has a substantially constant cross-sectional shape and a length of a little less than two rounds. One end of the circumferential groove 54 is opened to the upper end surface in the axial direction through a notch-shaped opening window 56, while the other end is inwardly projected through a notch-shaped communication hole 58. 52 is opened on the inner peripheral surface.

  Further, the upper partition member main body 46 is formed with a notch-like communication hole 60 extending in the radial direction at the lower end portion in the axial direction, except for the position where the circumferential groove 54 is formed.

  On the other hand, the lower partition member main body 48 is formed of the same hard material as the upper partition member main body 46, and has a thick disk shape as a whole. In the present embodiment, the outer diameter dimension of the lower partition member body 48 and the outer diameter dimension of the upper partition member body 46 are substantially the same. In addition, a circumferential groove 62 is formed in the outer peripheral portion of the lower partition member main body 48 and opens in the lower surface in the axial direction and has a substantially constant cross-sectional shape and extends a little less than one round in the circumferential direction. Here, one end in the circumferential direction of the circumferential groove 62 is opened on the upper surface of the lower partition member body 48 through a connection hole 64 formed in the upper bottom wall of the circumferential groove 62. Furthermore, an accommodation recess 66 is formed in the central portion of the lower partition member main body 48 and opens to the lower surface in the axial direction with a substantially constant circular cross section.

  The lower partition member main body 48 having such a structure is arranged on the same central axis as the upper partition member main body 46 so that the upper end surface thereof overlaps the lower end surface in the axial direction of the upper partition member main body 46. It has become. In this state, the connection hole 64 formed in the lower partition member main body 48 opens into the communication hole 60 formed in the upper partition member main body 46, and the connection hole 64 and the communication hole 60 are connected. Thus, the circumferential direction positions of the upper partition member main body 46 and the lower partition member main body 48 are matched.

  Although not clearly shown in the drawings, the upper partition member main body 46 and the lower partition member main body 48 are formed, for example, on one of the overlapping surfaces of the upper partition member main body 46 and the lower partition member main body 48. The engaging recess may be engaged with and fixed to the engaging recess by engaging the engaging protrusion formed on the other side, or may be bonded and fixed by an adhesive. You may come to be. Thereby, the upper partition member main body 46 and the lower partition member main body 48 are positioned in the circumferential direction.

  On the other hand, the bottom metal fitting 50 is formed of a metal material such as iron or an aluminum alloy, and has a thin disk shape as a whole. Further, a cutout connection window 68 is formed on the outer peripheral portion of the bottom metal fitting 50.

  Such a bottom metal fitting 50 is arranged on the same central axis as the lower partition member main body 48 and is superposed on the lower surface of the lower partition member main body 48. In this state, the lower partition is formed such that the connection window 68 formed in the bottom metal fitting 50 is located below the other circumferential end of the circumferential groove 62 formed in the lower partition member main body 48. The circumferential positions of the member main body 48 and the bottom metal fitting 50 are matched. .

  Although not clearly shown in the drawings, the lower partition member main body 48 and the bottom metal fitting 50 are, for example, engagement recesses formed on any one of the overlapping surfaces of the lower partition member main body 48 and the bottom metal fitting 50. On the other hand, the engaging projections formed on the other side may be fitted and engaged, so that they can be locked and fixed to each other, or they can be bonded and fixed by an adhesive. May be. Thereby, the alignment of the lower partition member main body 48 and the bottom metal fitting 50 in the circumferential direction is performed.

  Further, the lower partition member main body 48 and the bottom metal fitting 50 are overlapped as described above, whereby the opening of the accommodation recess 66 formed in the lower partition member main body 48 is covered with the bottom metal fitting 50. Thereby, the accommodation area | region 70 is formed between the opposing surfaces of the lower partition member main body 48 and the bottom metal fitting 50 using the accommodation recess 66. In the accommodation area 70, a movable rubber plate 72 as a movable member is disposed.

  The movable rubber plate 72 is formed of a rubber elastic body having a substantially disc shape, and an annular outer peripheral support portion 74 that protrudes on both sides in the axial direction is integrally formed at the outer peripheral edge portion, and at the central portion. Central support portions 76 projecting on both sides in the axial direction are integrally formed. That is, the movable rubber plate 72 is thicker at the outer peripheral edge portion and the central portion than the radially intermediate portion.

  In addition, a buffer abutting portion 77 that protrudes on both sides in the axial direction is integrally formed at a radially intermediate portion of the movable rubber plate 72. The buffer abutment portion 77 is a protrusion that continuously extends over the entire circumference, and has a protrusion height smaller than that of the outer periphery support portion 74 and the center support portion 76.

  Such a movable rubber plate 72 is fitted in a receiving recess 66 formed in the lower partition member main body 48, and the bottom metal fitting 50 is superimposed on the lower surface of the lower partition member main body 48. It is adapted to be accommodated in the accommodating area 70. In this state, the outer peripheral support portion 74 and the central support portion 76 of the movable rubber plate 72 are supported by pressing between the opposing surfaces of the lower partition member main body 48 and the bottom metal fitting 50, respectively. In addition, the radial intermediate portion of the movable rubber plate 72 including the formation position of the buffer contact portion 77 is entirely separated from both the lower partition member main body 48 and the bottom metal fitting 50.

  In addition, a plurality of through holes 78 are formed in the top wall portion and the bottom wall portion (upper and lower wall portions) of the accommodation region 70, respectively. As a result, a thin portion (radial intermediate portion) formed between the outer peripheral support portion 74 and the central support portion 76 of the movable rubber plate 72 is exposed to the outside through the through hole 78.

  The partition member 44 having such a structure is inserted from the upper opening portion of the outer tube metal member 14, and the outer peripheral tube metal member 26 constituting an integrally vulcanized molded product of the main rubber elastic body 16 is used as the partition member 44. By being inserted from the upper opening of the upper partition member main body 46 to be configured, it is assembled to the integrally vulcanized molded product of the main rubber elastic body 16 and the outer cylinder fitting 14.

  Then, as described above, with the partition member 44 assembled with the integrally vulcanized molded product of the main rubber elastic body 16 and the outer cylinder fitting 14, the outer cylinder fitting 14 is subjected to diameter reduction processing such as eight-way drawing. The partition member 44 is fixedly supported by the outer tubular fitting 14 and is disposed so as to spread in the direction perpendicular to the axis within the fluid chamber 42.

  Further, a second flexible rubber film 80 as a second flexible film is assembled to the outer cylindrical metal member 14 from the outside of the integrally vulcanized molded product of the main rubber elastic body 16. The second flexible rubber film 80 is formed of a thin rubber elastic film that can be easily deformed, and has an annular plate shape as a whole. Further, an inner peripheral fitting 82 having an annular shape or a cylindrical shape is vulcanized and bonded to the inner peripheral edge portion of the second flexible rubber film 80. Furthermore, an outer peripheral fitting 84 having a cylindrical shape is vulcanized and bonded to the outer peripheral edge of the second flexible rubber film 80. That is, in the present embodiment, the second flexible rubber film 80 is formed as an integrally vulcanized molded product including the inner peripheral fitting 82 and the outer fitting 84.

  Therefore, in the present embodiment, both end portions in the axial direction of the inner peripheral fitting 82 extend outward in the radial direction. Thereby, the inner peripheral fitting 82 is formed with a concave groove that opens to the outer peripheral surface. The inner peripheral edge of the second flexible rubber film 80 is vulcanized and bonded so as to fill the concave groove.

  In the present embodiment, the lower end portion in the axial direction of the inner peripheral fitting 82 is a tapered portion that gradually increases in diameter as it goes downward in the axial direction. Thereby, as will be described later, it is possible to easily insert the inner peripheral fitting 82 into the fitting portion 18 of the inner fitting 12.

  In the integrally vulcanized molded product of the second flexible rubber film 80 as described above, the inner peripheral fitting fitting 82 is press-fitted into the fitting portion 18 of the inner fitting 12, and the outer fitting fitting 84 is the outer cylinder fitting. 14 is inserted into the outer cylindrical metal member 14 from the outside of the integrally vulcanized molded product of the main rubber elastic body 16. That is, the second flexible rubber film 80 is disposed so as to cover the tapered cylindrical outer peripheral surface of the main rubber elastic body 16. In this state, the outer cylinder fitting 14 is subjected to drawing or caulking so that the large diameter portion 34 of the outer cylinder fitting 14 is fitted and fixed to the outer fitting fitting 84.

  In this state, the bottom fitting 50 constituting the partition member 44 is provided with a step difference in the outer tubular fitting 14 in a state where the integrally vulcanized molded product of the second flexible rubber film 80 is assembled to the outer tubular fitting 14 as described above. The flange-shaped portion 30 of the outer peripheral cylindrical metal fitting 26 that is superimposed on the portion 32 and that constitutes the integrally vulcanized molded product of the main rubber elastic body 16 is on the axial direction of the upper partition member main body 46 that constitutes the partition member 44. Further, an outer peripheral fitting 84 that constitutes an integrally vulcanized molded product of the second flexible rubber film 80 is superimposed on the upper surface of the flange-shaped portion 30 of the outer cylindrical fitting 26. ing. That is, the partition member 44 is pressed against the stepped portion 32 of the outer cylinder fitting 14 by the outer circumference fitting 84 that is fitted and fixed to the outer cylinder fitting 14, and is fixed in the axial direction.

  Further, in this state, between the overlapping surfaces of the bottom metal part 50 constituting the partition member 44 and the stepped portion 32 of the outer cylinder metal part 14, the upper partition member main body 46 and the lower partition member main body 48 constituting the partition member 44, A seal rubber layer 40 is sandwiched between the overlapping surfaces of the large-diameter portion 34 of the outer cylindrical metal member 14, and a rubber outer peripheral edge 28 is formed on the inward protrusion 52 of the upper partition member body 46. It is pressed against the contact surface. In addition, the outer peripheral cylindrical metal fitting 26 and the upper partition member main body 46 are superposed in a close contact state, and the upper partition member main body 46 and the lower partition member main body 48 are superposed in a close contact state. The partition member main body 48 and the bottom metal fitting 50 are superposed in a close contact state.

  As a result, the fluid chamber 42 is divided into two sides sandwiching the partition member 44, and on one side of the partition member 44, a part of the wall portion is constituted by the main rubber elastic body 16 and vibration is input. A pressure receiving chamber 86 is formed, and on the other side, a first equilibrium chamber 88 is formed in which a part of the wall portion is constituted by the first flexible rubber film 38 and volume change is allowed. Has been.

  Further, as described above, the partition member 44 is disposed in the fluid chamber 42, so that the opening of the circumferential groove 62 formed in the lower partition member main body 48 is fluid-tightly covered with the bottom metal fitting 50. A tunnel-like flow path is formed in the outer peripheral portion of the partition member 44 extending in the circumferential direction along the inner peripheral surface of the large-diameter portion 34 of the outer cylindrical metal member 14. The tunnel-shaped flow path is connected to the pressure receiving chamber 86 through the connection hole 64 formed in the lower partition member main body 48 and the communication hole 60 formed in the upper partition member main body 46 and is formed in the bottom metal fitting 50. The connection window 68 is connected to the first equilibrium chamber 88. That is, a first orifice passage 90 is formed which includes a tunnel-like flow path formed using the circumferential concave groove 62 and communicates the pressure receiving chamber 86 and the first equilibrium chamber 88 with each other.

  Further, in the state in which the integrally vulcanized molded product of the second flexible rubber film 80 is assembled to the outer tube fitting 14 as described above, the inner fitting fitting 82 and the fitting portion 18 of the inner fitting 12 are overlapped. A seal rubber layer 22 is sandwiched between the mating surfaces. As a result, the inner peripheral edge of the second flexible rubber film 80 is fixed fluid-tightly to the inner metal fitting 12.

  Furthermore, in the state in which the integrally vulcanized molded product of the second flexible rubber film 80 is assembled to the outer cylinder fitting 14 as described above, the outer fitting metal fitting 84 and the large diameter portion 34 of the outer cylinder fitting 14 are formed. A seal rubber layer 40 is sandwiched between lower ends in the axial direction between the overlapping surfaces. As a result, the outer peripheral edge of the second flexible rubber film 80 is fluid-tightly fixed to the outer cylinder fitting 14.

  Thus, the inner peripheral edge of the second flexible rubber film 80 is fluid-tightly fixed to the inner metal fitting 12, and the outer peripheral edge of the second flexible rubber film 80 is the outer cylindrical metal fitting. 14, a part of the wall portion is constituted by the main rubber elastic body 16 and the second flexible rubber film 80 on the outside of the main rubber elastic body 16. A second equilibrium chamber 92 that is allowed to change is formed. The second equilibrium chamber 92 is filled with the same incompressible fluid as the pressure receiving chamber 86 and the first equilibrium chamber 88.

  Further, as described above, the partition member 44 is disposed in the fluid chamber 42, so that the opening of the circumferential groove 54 formed in the upper partition member main body 46 is fluid-tightly covered with the large-diameter portion 34 of the outer cylinder fitting 14. Thus, a tunnel-like flow path extending in the circumferential direction is formed along the large-diameter portion 34 of the outer cylinder fitting 14. Such a tunnel-shaped flow path is connected to the pressure receiving chamber 86 through a communication hole 58 formed in the upper partition member main body 46, and is formed in the outer peripheral fitting 84 and the second flexible rubber film 80. It is connected to the second equilibrium chamber 92 through a notch-shaped connection hole 94, an opening window 31 formed in the flange-shaped portion 30 of the outer peripheral cylindrical metal fitting 26, and an opening window 56 formed in the upper partition member body 46. That is, a second orifice passage 96 that includes a tunnel-like flow path formed by using the circumferential groove 54 and that communicates the pressure receiving chamber 86 and the second equilibrium chamber 92 with each other is formed.

  Although not clearly shown in the drawings, for example, the locking projection formed on the upper end surface of the upper partition member main body 46 and the locking hole formed in the flange-shaped portion 30 of the outer cylindrical metal fitting 26 are locked. Then, the circumferential direction of the communication hole 58 formed in the opening window 31 formed in the flange-shaped portion 30 and the upper partition member main body 46 by aligning the outer peripheral cylindrical metal fitting 26 and the upper partition member main body 46 in the circumferential direction. The position is adjusted.

  As shown in FIG. 2, the first orifice passage 90 and the second orifice passage 96 are both tuned so that the peak frequency of the damping coefficient is located in the frequency range of the engine shake. Yes. In particular, in the present embodiment, the tuning frequency of the first orifice passage 90 is positioned higher than the tuning frequency of the second orifice passage 96.

  Further, in the present embodiment, the first orifice passage 90 is caused to flow and the high-frequency side portion A in the increased frequency region of the damping coefficient exhibited based on the resonance action of the fluid caused to flow through the second orifice passage 96. The first orifice passage 90 and the second orifice passage 90 are overlapped with at least a part of the low frequency side portion B of the increased frequency range of the damping coefficient exhibited based on the resonance action of the fluid to be generated. Orifice passage 96 is tuned. The high frequency side portion A is a portion on the right side of the peak point of the attenuation coefficient of the second orifice passage 96 in FIG. Further, the low frequency side portion B is a portion on the left side of the peak point of the attenuation coefficient of the first orifice passage 90 in FIG. As shown in FIG. 2, in the present embodiment, these two portions A and B intersect each other, and in a frequency range approximately ¼ to ３ of the frequency range X in which A and B are combined. They are overlapping.

  Particularly in the present embodiment, the fluid flow action through the first orifice passage 90 in the frequency range Y between the bottom and the peak of the dynamic spring constant exhibited based on the fluid flow action through the second orifice passage 96. The first orifice passage 90 and the second orifice passage 96 are tuned so that an increase region of the damping coefficient exerted based on In short, the start point P of the effect of increasing the attenuation coefficient by the first orifice passage 90 is set in the frequency range Y. Thereby, the attenuation coefficient increasing effect in both the first orifice passage 90 and the second orifice passage 96 is more effectively exhibited in a wide frequency range as a whole.

  In addition, since both the orifice passages 90 and 96 are tuned to the frequency range of the engine shake, when the engine shake is input, fluid flow is generated in both the orifice passages 90 and 96. ing. In this case, the first orifice passage 90 or the second orifice passage 96 that is more frequency-adapted to the input vibration is more than the other orifice passage (the second orifice passage 96 or the first orifice passage 90). However, the amount of fluid flow increases. Thereby, even when the frequency of the engine shake changes, a large damping coefficient is stabilized based on the resonance action of the fluid that can flow through the two orifice passages (the first orifice passage 90 and the second orifice passage 96). Can be demonstrated.

  The tuning of the first orifice passage 90 and the second orifice passage 96 can be performed, for example, by adjusting the ratio between the passage length and the passage sectional area. Since the tuning frequencies of the first and second orifice passages 90 and 96 also affect the wall spring rigidity of the pressure receiving chamber 86 and the equilibrium chambers 88 and 92, it is desirable to tune through repeated experiments. Here, the wall spring stiffness can be understood as the amount of change in pressure required to change the volume of the liquid chamber by a certain amount.

  By the way, when assuming a 4-6 cylinder engine, the frequency range where the engine shake is generated is generally about 5-25 Hz, but the attenuation peak by the second orifice passage 96 is set to 10 Hz, By setting the attenuation peak due to one orifice passage 90 to 15 Hz, a sufficiently large attenuation effect can be obtained in a wide frequency range of about 5 to 25 Hz.

  In the engine mount 10 having the above-described structure, a first equilibrium chamber 88 is formed below the main rubber elastic body 16 and a second equilibrium chamber is formed above the main rubber elastic body 16. Since 92 is formed, a sufficient volume can be secured in any of the equilibrium chambers 88 and 92.

  The first flexible rubber film 38 having a substantially circular dome shape constitutes a part of the wall portion of the first equilibrium chamber 88 in a state where the outer peripheral edge portion is supported. Therefore, it is possible to secure a large effective area.

  Further, the second flexible rubber film 80 having a substantially annular shape constitutes a part of the wall portion of the second equilibrium chamber 92 in a state where the inner peripheral edge portion and the outer peripheral edge portion are supported. Therefore, it is possible to ensure a large effective area.

  Furthermore, the first orifice passage 90 is formed by utilizing the circumferential groove 62 formed in the lower partition member main body 48 constituting the partition member 44, and the second orifice passage 96 is formed by the partition member. 44, the space for forming the first orifice passage 90 and the space for forming the second orifice passage 96 are efficiently secured. It becomes possible to do. As a result, it is possible to form the orifice passages 90 and 96 tuned in the frequency range of the engine shake with a sufficient passage length and passage sectional area.

  Therefore, in the engine mount 10 having the above-described structure, a sufficient amount of fluid flow is secured, and a high damping effect based on the resonance action of the fluid that can flow through the orifice passages 90 and 96 is effectively exhibited. It becomes possible to.

  Therefore, in the present embodiment, the flow is caused to flow through the first orifice passage 90 and the portion A on the high frequency side of the increased frequency region of the damping coefficient exhibited based on the resonance action of the fluid that is caused to flow through the second orifice passage 96. Since the portion B on the low frequency side of the increased frequency region of the damping coefficient exhibited based on the resonance action of the fluid to be squeezed partially overlaps, the frequency region where the damping coefficient is increased is widened. I can do it. As a result, a high attenuation effect can be exhibited in a wide frequency range.

  In the present embodiment, since the first equilibrium chamber 88 is formed on the opposite side of the pressure receiving chamber 86 with the partition member 44 interposed therebetween, it is easy to secure the volume of the first equilibrium chamber 88.

  Further, in the present embodiment, the first orifice passage 90 and the second orifice passage 96 are formed so as to extend along the large-diameter portion 34 of the outer tubular fitting 14, respectively. The lengths of the one orifice passage 90 and the second orifice passage 96 can be easily secured in a small space.

  Furthermore, in the present embodiment, since the movable rubber plate 72 is disposed in the partition member 44, when the input vibration is a high-frequency small-amplitude vibration corresponding to a running-over sound of an automobile, Due to the relative pressure difference between the pressure receiving chamber 86 and the first equilibrium chamber 88, the movable rubber plate 72 is slightly displaced in the axial direction, and the internal pressure fluctuation exerted on the pressure receiving chamber 86 is released to the first equilibrium chamber 88 side. It is supposed to be. Based on the low dynamic spring action exhibited by such a hydraulic pressure absorbing action, excellent vibration isolation performance due to the vibration insulation effect is realized even when vibration is input in a high frequency range.

  When the engine shake is input, the movable rubber plate 72 is pressed against one inner wall surface in the axial direction of the housing region 70 formed using the housing recess 66 so that the displacement is prevented. Yes. As a result, fluid pressure absorption due to minute displacement of the movable rubber plate 72 is prevented, and fluid flow through the first and second orifice passages 90 and 96 is effectively generated.

  Next, an engine mount 100 as a second embodiment of the fluid filled engine mount according to the present invention will be described with reference to FIG. In the following description, members and parts having the same structure as those of the first embodiment are denoted by the same reference numerals as those of the first embodiment, and detailed descriptions thereof are omitted. To do.

  In the engine mount 100 of the present embodiment, a lower flange portion 102 that extends radially outward is integrally formed with respect to the lower end portion in the axial direction of the outer cylindrical metal fitting 26. Thereby, the peripheral groove | channel metal fitting 26 is formed with the circumferential groove 104 extended over the perimeter.

  Further, in the present embodiment, the main rubber elastic body 16 extends into the circumferential groove 104 of the outer cylindrical metal fitting 26. As a result, in the circumferential groove 104, one side wall is constituted by the rubber wall 106, and the circumferential groove 108 that opens to the outer peripheral surface and extends in the circumferential direction has a substantially constant cross-sectional shape and is substantially spirally wound twice. It is formed with a weak length. The circumferential groove 108 has one end opened to the upper end surface in the axial direction of the outer cylindrical metal fitting 26 through a notch-shaped opening window 110, while the other end passes through the communication hole 112. Opened to the inner peripheral surface of the outer cylindrical metal fitting 26.

  Furthermore, in the present embodiment, instead of the rubber outer peripheral edge 28, the covering rubber layer 114 formed integrally with the main rubber elastic body 16 is substantially omitted from the inner peripheral surface of the outer cylindrical metal fitting 26 to the lower surface of the lower flange portion 102. It is applied over the entire surface.

  In the present embodiment, the seal rubber protrusion 116 integrally formed with the covering rubber layer 114 protrudes downward in the axial direction from the outer peripheral portion of the lower flange portion 102 so as to extend over the entire circumference with a substantially constant cross-sectional shape. Is provided.

  Furthermore, in this embodiment, the outer cylinder fitting 118 as the outer cylinder member is formed by the upper cylinder fitting 120 and the lower cylinder fitting 122, and has a large-diameter cylindrical shape as a whole.

  The upper cylindrical metal member 120 has a small diameter portion 126 on the upper side in the axial direction and a large diameter portion 128 on the lower side in the axial direction with a stepped portion 124 formed in the intermediate portion in the axial direction interposed therebetween. It has a cylindrical shape. Further, a caulking portion 130 is integrally formed at the opening edge of the upper cylindrical metal member 120 on the large diameter portion 128 side.

  Furthermore, the outer peripheral edge portion of the second flexible rubber film 80 is vulcanized and bonded to the end portion of the upper cylindrical fitting 120 on the small diameter portion 126 side. That is, in the present embodiment, the second flexible rubber film 80 is an integrally vulcanized molded product including the inner peripheral fitting fitting 82 and the upper cylindrical fitting 120. Further, a seal rubber 132 integrally formed with the second flexible rubber film 80 is applied over the entire inner peripheral surface of the small diameter portion 126.

  On the other hand, the lower cylindrical metal fitting 122 has a large diameter cylindrical portion 136 on the upper side in the axial direction and a small diameter cylindrical portion 138 on the lower side in the axial direction, with a stepped portion 134 formed in the intermediate portion in the axial direction. The overall shape is a stepped cylinder.

  Further, the outer peripheral edge of the first flexible rubber film 38 is vulcanized and bonded to the small-diameter cylindrical portion 138 of the lower cylindrical fitting 122. Therefore, in this embodiment, the seal rubber 140 integrally formed with the first flexible rubber film 38 is attached to substantially the entire inner peripheral surface and outer peripheral surface of the small-diameter cylindrical portion 138. In particular, in the present embodiment, a portion of the seal rubber 140 that is attached to the inner peripheral surface of the small-diameter cylindrical portion 138 extends to a radially intermediate portion on the upper surface of the stepped portion 134.

  The upper cylindrical fitting 120 and the lower cylindrical fitting 122 having the above-described structure are assembled to the integrally vulcanized molded product of the main rubber elastic body 16 as follows.

  First, the inner peripheral fitting fitting 82 is press-fitted into the fitting portion 18 of the inner fitting 12, and the small diameter portion 126 of the upper cylindrical fitting 120 is extrapolated to the outer cylindrical fitting 26, whereby the second flexible rubber. The integrally vulcanized molded product of the membrane 80 is assembled to the integrally vulcanized molded product of the main rubber elastic body 16. In this state, the outer peripheral edge portion of the flange-shaped portion 30 of the outer cylindrical metal fitting 26 is brought into contact with the step surface formed at the boundary portion between the second flexible rubber film 80 and the seal rubber 132. The step portion 124 of the upper cylindrical metal fitting 120 is overlapped with the outer peripheral portion of the lower flange portion 102 of the outer cylindrical metal fitting 26.

  Next, the large-diameter cylindrical portion 136 of the lower cylindrical metal fitting 122 is inserted into the large-diameter portion 128 of the upper cylindrical metal fitting 120, whereby the lower cylindrical metal fitting 122 is assembled to the large-diameter portion 128 side of the upper cylindrical metal fitting 120. . In this state, the large-diameter cylindrical portion 136 of the lower cylindrical fitting 122 is externally attached to the seal rubber protrusion 116, and the axial upper end surface of the lower cylindrical fitting 122 is the lower flange portion 102 of the outer cylindrical fitting 26. Is superimposed.

  Then, with the lower cylinder fitting 122 assembled to the upper cylinder fitting 120 as described above, the upper cylinder fitting 120 is subjected to drawing processing such as eight-way drawing. Thereby, the seal rubber 132 is clamped between the flange-shaped portion 30 of the outer cylindrical metal fitting 26 and the upper cylindrical metal fitting 120 and between the rubber wall 106 and the upper cylindrical metal fitting 120.

  Further, the caulking portion 130 of the upper cylindrical metal fitting 120 is caulked and fixed to the stepped portion 134 of the lower cylindrical metal fitting 122. Thereby, the upper cylinder fitting 120 and the lower cylinder fitting 122 are fixed, and the outer cylinder fitting 118 is configured. In this state, the seal rubber protrusion 116 is fluidly overlapped with the stepped portion 134 and the large-diameter cylindrical portion 136 of the lower cylindrical fitting 122. Note that the outer cylinder fitting 118 is attached to the vehicle body via a bracket (not shown).

  In this way, the outer cylinder fitting 118 is assembled to the integrally vulcanized molded product of the main rubber elastic body 16, so that the fluid formed between the opposing surfaces of the main rubber elastic body 16 and the first flexible rubber film 38. A partition member 142 is accommodated in the chamber 42.

  Therefore, the partition member 142 of the present embodiment includes a partition member main body 144 and a lid fitting 146.

  The partition member main body 144 is made of a hard material such as a metal material such as iron or aluminum alloy or a synthetic resin, and has a thick disk shape as a whole. In addition, an annular plate-like portion 147 that protrudes radially outward is integrally formed at the upper end portion of the partition member main body 144. Furthermore, a circular housing recess 148 that opens to the upper end surface is formed in the central portion in the radial direction of the partition member main body 144. Furthermore, the outer peripheral portion of the partition member main body 144 is formed with a concave groove 150 that opens to the upper end surface and extends with a substantially constant cross-sectional shape with a length of a little less than one round in the circumferential direction. Here, one end in the circumferential direction of the groove 150 is opened on the lower surface of the partition member main body 144 through a communication hole 152 formed in the bottom wall.

  On the other hand, the lid fitting 146 has a thin and substantially disk shape, and is formed of a metal material such as iron or an aluminum alloy. In addition, a communication hole 154 is formed in a radially intermediate portion of the lid fitting 146.

  The lid fitting 146 is overlaid on the upper end surface of the partition member main body 144. In this state, the communication hole 154 formed in the lid fitting 146 is positioned above the other circumferential end portion of the concave groove 150 formed in the partition member main body 144. Thereby, the concave groove 150 is opened on the upper surface of the lid fitting 146 through the communication hole 154.

  Although not clearly shown in the drawing, for example, by engaging a locking projection formed on the upper end surface of the partition member main body 144 and a locking hole formed in the lid fitting 146, the partition member main body 144 and The lid fitting 146 may be locked and fixed to each other. For example, the partition member main body 144 and the lid fitting 146 may be bonded and fixed using an adhesive or the like. Thereby, the lid fitting 146 and the partition member main body 144 are aligned in the circumferential direction.

  As described above, the partition member main body 144 and the lid fitting 146 are overlapped so that the opening of the accommodation recess 148 formed in the partition member main body 144 is covered with the lid fitting 146. Thereby, the accommodation area 70 is formed between the opposing surfaces of the partition member main body 144 and the lid fitting 146 using the accommodation recess 148.

  In the accommodation area 70, the movable rubber plate 72 is accommodated and disposed in a state where the outer peripheral support portion 74 and the center support portion 76 are supported by pressing between the opposing surfaces of the partition member main body 144 and the lid fitting 146, respectively. . Moreover, the thin part formed between the outer peripheral support part 74 of the movable rubber plate 72 and the center support part 76 in the radial direction in such a state becomes the top wall part and the bottom wall part (upper and lower wall parts) of the accommodation area 70. It is exposed to the outside through the formed through hole 78.

  The partition member having such a structure has an outer peripheral edge portion (an outer peripheral portion of the lid fitting 146 and an annular plate-like portion 147 of the partition member main body 144), and a lower flange-like portion 30 and a lower portion of the outer cylindrical fitting 26. By being caulked and fixed by the caulking portion 130 of the upper cylindrical fitting 120 together with the stepped portion 134 of the lower cylindrical fitting 122 while being sandwiched between the stepped portions 134 of the side cylindrical fitting 122, the direction perpendicular to the axis in the fluid chamber 42 is obtained. It is arrange | positioned so that it may spread. In this state, the covering rubber layer 114 is sandwiched between the outer peripheral edge portion of the partition member 142 and the lower flange portion 102, and the seal rubber 140 is interposed between the outer peripheral edge portion of the partition member 142 and the step portion 134. Is pinched.

  In this way, the partition member 142 is arranged so as to spread in the direction perpendicular to the axis in the fluid chamber 42, so that the fluid chamber 42 is divided into two sides with the partition member 142 interposed therebetween, and the partition member 142 is sandwiched between On the other hand, a pressure receiving chamber 86 is formed on one side, and a first equilibrium chamber 88 is formed on the other side.

  Further, as described above, the partition member 142 is disposed in the fluid chamber 42, so that the opening of the concave groove 150 formed in the partition member main body 144 is fluid-tightly covered with the lid fitting 146, and the partition member 142 A tunnel-like flow path is formed that extends in the circumferential direction along the outer cylinder 118 at the outer peripheral portion. The tunnel-shaped flow path is connected to the pressure receiving chamber 86 through a communication hole 154 formed in the lid fitting 146 and is connected to the first equilibrium chamber 88 through a communication hole 152 formed in the partition member main body 144. ing. That is, a first orifice passage 90 is formed which includes a tunnel-like flow path formed using the concave groove 150 and communicates the pressure receiving chamber 86 and the first equilibrium chamber 88 with each other.

  Further, as described above, the outer cylinder fitting 118 is assembled to the integrally vulcanized molded product of the main rubber elastic body 16 so that the second elastic rubber film 80 and the second flexible rubber film 80 have a second An equilibrium chamber 92 is formed.

  Furthermore, as described above, the outer cylinder fitting 118 is assembled to the integrally vulcanized molded product of the main rubber elastic body 16, so that the opening of the circumferential groove 108 is covered with the outer cylinder fitting 118, and the outer cylinder fitting 118. A tunnel-shaped flow path extending in the circumferential direction is formed. Such a tunnel-shaped flow path is connected to the pressure receiving chamber 86 through a communication hole 112 formed in the outer peripheral cylindrical metal fitting 26, and is connected to the second through an opening window 110 formed in the flange-shaped portion 30 of the outer peripheral cylindrical metal fitting 26. It is connected to the equilibrium chamber 92. That is, a second orifice passage 96 that includes the tunnel-shaped flow path formed by using the circumferential groove 108 and that communicates the pressure receiving chamber 86 and the second equilibrium chamber 92 with each other is formed.

  The first orifice passage 90 and the second orifice passage 96 are each tuned to a low frequency region corresponding to an engine shake and a slightly different frequency region.

  Also in the engine mount having such a structure, the first balance chamber 88 and the second balance chamber 92 are formed with the main rubber elastic body 16 sandwiched in the axial direction. Similar effects can be obtained.

  Further, in the present embodiment, the second orifice passage 96 is constituted by the outer peripheral cylindrical metal fitting 26 constituting the integral vulcanization molded product of the main rubber elastic body 16 and the rubber wall 106 integrally formed with the main rubber elastic body 16. Since the circumferential groove 108 is formed, it is not necessary to separately provide a special part for forming the second orifice passage 96. As a result, the number of necessary parts can be reduced.

  As mentioned above, although several embodiment of this invention has been explained in full detail, these are illustrations to the last, Comprising: This invention is not limited at all by the specific description in this embodiment. .

  For example, in the first and second embodiments, the movable rubber plate 72 is not necessarily required.

  In the first and second embodiments, the central portion of the movable rubber plate 72 is not necessarily supported by pressing.

  Furthermore, in the first and second embodiments, instead of the movable rubber plate 72 whose outer peripheral portion is supported by clamping, it is accommodated and arranged as a movable member in the accommodating region 70 so as to be minutely displaceable in the thickness direction. It is also possible to adopt a movable plate designed to prevent fluid flow on both sides of the movable member in the maximum displacement state while exhibiting the hydraulic pressure absorption effect due to minute displacement It is. When a movable plate is adopted as the movable member, the movable plate can be formed of a hard plate such as a synthetic resin in addition to a rubber elastic body. When the movable plate is formed of a hard plate such as a synthetic resin, it is desirable to form a buffer protrusion such as rubber on the contact surface between the movable plate and the inner surface of the accommodation area 70. Thereby, the hitting sound at the time of contact can be suppressed.

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

The longitudinal cross-sectional view which shows the engine mount as 1st embodiment of this invention. The graph for demonstrating the tuning frequency of the 1st orifice channel | path of the engine mount, and a 2nd orifice channel | path. The longitudinal cross-sectional view which shows the engine mount as 1st embodiment of this invention.

Explanation of symbols

10: engine mount, 12: inner metal fitting, 14: outer cylinder metal fitting, 16: main rubber elastic body, 38: first flexible rubber film, 44: partition member, 80: second flexible rubber film, 86: pressure receiving chamber, 88: first equilibrium chamber, 90: first orifice passage, 92: second equilibrium chamber, 96: second orifice passage, 100: engine mount, 118: outer cylinder fitting, 142: Partition member

Claims (5)

The inner shaft member is spaced apart from one opening side of the cylindrical outer tube member, and the inner shaft member is fixed to the small-diameter side end of the substantially truncated cone-shaped main rubber elastic body, and the main rubber elastic body The outer cylinder member is fixed to the outer peripheral surface of the large-diameter side, and the inner shaft member and the outer cylinder member are elastically connected,
By arranging a partition member facing the large-diameter portion side of the main rubber elastic body and supporting the partition member with the outer cylinder member, vibration is generated between the main rubber elastic body and the partition member. While forming the input pressure receiving chamber,
A first flexible membrane is disposed on the opposite side of the pressure receiving chamber across the partition member, and a volume change is allowed between the partition member and the first flexible membrane. While forming an equilibrium chamber of
A second flexible film covering the tapered outer peripheral surface of the main rubber elastic body is provided, and a second change in volume is allowed between the main rubber elastic body and the second flexible film. Forming an equilibrium chamber,
A first orifice passage for sealing the incompressible fluid in each of the pressure receiving chamber, the first equilibrium chamber, and the second equilibrium chamber, and communicating the pressure receiving chamber with the first equilibrium chamber; and the pressure receiving chamber A second orifice passage for communicating with the second equilibration chamber,
A fluid-filled engine mount, wherein the first orifice passage and the second orifice passage are tuned to have different attenuation peak frequencies in the engine shake frequency range.   An increasing frequency range of a damping coefficient exhibited based on the resonance action of the fluid flowing through the first orifice passage, and a damping coefficient exhibited based on the resonance action of the fluid flowing through the second orifice passage Of the first orifice passage and the second orifice passage so that the high frequency side portion of one of the increase frequency regions overlaps the low frequency side portion of the other increase frequency region. The fluid-filled engine mount according to claim 1, wherein each tuning frequency is set.   A thin rubber elastic film having a slack is assembled so as to cover the other opening of the outer cylinder member, and the first flexible film is constituted by the rubber elastic film. The fluid-filled engine mount according to claim 1, wherein the partition member is disposed between the main rubber elastic body and the rubber elastic film in the axial direction.   4. The fluid according to claim 1, wherein each of the first orifice passage and the second orifice passage is formed so as to extend at least partially in a circumferential direction of the outer cylinder member. 5. Enclosed engine mount.   At the center of the partition member, a movable member is disposed in a state where the amount of displacement is limited, and when a vibration in a frequency range higher than the frequency range of the engine shake is input, the movable member is displaced. The fluid-filled engine mount according to any one of claims 1 to 4, wherein a fluid flow is generated between the pressure receiving chamber and the first equilibrium chamber.

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