JP2003232397A - Liquid sealing vibration controller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a liquid sealing vibration controller with a novel structure which can be externally inserted to an intermediate sleeve in the axial direction and easily assembled without making an orifice member in a nearly cylindrical shape extending in the circumference direction in semi-circumference length or more to be in a divided structure, and at the same time, in which a sealing property between the intermediate sleeve and an outer cylinder member can be advantageously secured and a high degree of fluid-tightness can be exerted. <P>SOLUTION: The cylindrical orifice member 94 is externally inserted from the end in the axial direction on the opposite side of a fitting cylindrical part 32 to the intermediate sleeve 26, in which the fitting cylindrical part 32 with large diameter is integrally formed to one end in the axial direction, clamped and fixed between the intermediate sleeve 26 and an outer cylinder member 14. A sealing protrusion 110 is formed at an opening edge of an opening window 36 in the intermediate sleeve 26, and the sealing protrusion 110 is brought into pressure contact with an inner peripheral face of the cylindrical orifice member 94 between the fitting faces of the intermediate sleeve 26 and the inner peripheral face of the cylindrical orifice member 94. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to a fluid filled type vibration damping device for obtaining a vibration damping effect based on a flow action of a fluid filled inside, for example, an engine mount for automobiles, a body mount, a differential mount, The present invention relates to a fluid filled type vibration damping device that can be suitably used as a suspension bush or the like.

[0002]

2. Description of the Related Art Conventionally, it has been described in, for example, Japanese Utility Model Publication No. 4-43636 as a type of a vibration isolator such as a vibration isolator or a vibration isolator which is interposed between members constituting a vibration transmission system. As described above, a main body rubber elastic body is provided in which outer cylinder fittings are arranged apart from each other on the outer peripheral side of the inner shaft member, and the inner shaft member and the outer cylinder fitting are arranged between the opposing surfaces of both members in the direction perpendicular to the axis. And a plurality of fluid chambers that are connected to each other by the orifice passage are formed between the inner shaft member and the outer tubular metal member, and are based on the flow action such as the resonance action of the fluid that causes the orifice passage to flow. BACKGROUND ART A fluid-filled type vibration damping device is known in which a vibration damping effect is obtained.

Further, in such a vibration isolator, in order to advantageously secure the degree of freedom in designing the length and cross-sectional area of the orifice passage when tuning the vibration isolating characteristics, as described in the above publication, A substantially annular orifice member extending in the circumferential direction along the inner peripheral surface of the outer tubular metal fitting so as to straddle the plurality of fluid chambers is preferably adopted, whereby the circumferential direction along the inner peripheral surface of the outer tubular metal fitting is adopted. It is possible to form an orifice passage extending in the vicinity of one round or a length of one round or more.

By the way, in the vibration isolator of the conventional structure, as described in the above publication, generally, the intermediate sleeve is vulcanized and adhered to the outer peripheral surface of the main rubber elastic body, and is provided on the intermediate sleeve. By forming a plurality of pockets each of which opens on the outer peripheral surface through the plurality of opening windows, and by fitting and fixing the outer tubular metal fitting to the intermediate sleeve to cover the opening windows, a plurality of fluid chambers are formed. ing. The central portion of the intermediate sleeve in the axial direction has a small diameter, and the tubular orifice member is accommodated and arranged in the small diameter portion, while the axial end portions of the intermediate sleeve have a large diameter, and the pair of large diameters are provided. The outer tubular metal fitting is externally fitted and fixed to the portion, and the liquid tightness of the enclosed fluid is highly achieved at the externally fitted fixing portion of the outer tubular metal fitting to the large diameter portion.

However, in such a vibration isolator, both axial end portions of the intermediate sleeve are larger in diameter than the inner diameter of the tubular orifice member assembled to the axial central portion of the intermediate sleeve. Therefore, when the orifice member is assembled to the intermediate sleeve, it is practically impossible to extrapolate it from the axial end portion of the intermediate sleeve. Therefore, as described in the above publication, it is necessary to divide and form the orifice member so as to be half or less in the circumferential direction, and to assemble the plurality of divided bodies separately in the radial direction. Yes, the number of parts of the orifice member increases, assembly is troublesome, the structure becomes complicated,
There is a problem in that it is difficult to manufacture the intended vibration damping device.

The large diameter portion of the intermediate sleeve is formed only at one end portion in the axial direction, and the cylindrical orifice member is externally inserted from the other end portion of the small diameter axial portion where the large diameter portion is not formed. It may be possible to externally fit and fix the outer tubular metal fitting to the intermediate sleeve via the orifice member, but it is difficult to reduce the diameter of the orifice member. There is a problem that it is difficult to stably secure the sealability between the surfaces. Further, particularly when the intermediate sleeve is subjected to a diameter reducing process to apply precompression after vulcanization molding of the main rubber elastic body, it is difficult to obtain a high degree of accuracy in the outer diameter dimension and shape of the intermediate sleeve. There is a problem in that it is difficult to effectively exhibit the required fluid tightness and manufacturability.

[0007]

The present invention has been made in view of the circumstances as described above, and a problem to be solved by the present invention is that a substantially cylindrical orifice member extending in a circumferential direction at a length of half a circumference or more. It is possible to easily attach the intermediate sleeve to the outer sleeve in the axial direction without using a split structure, and also to secure the sealability between the intermediate sleeve and the outer tubular metal fitting advantageously, thus achieving high fluid tightness. Can be exerted,
It is to provide a fluid filled type vibration damping device having a novel structure.

[0008]

Aspects of the present invention made to solve such problems will be described below. The constituent elements used in each of the following aspects can be used in any combination as much as possible. Further, the aspects and technical features of the present invention are not limited to those described below, but are described in the entire specification and the drawings, or the invention idea that can be understood by those skilled in the art from those descriptions. It should be understood that it is recognized based on this.

That is, the first aspect of the present invention is (a)
The inner shaft member and (b) a large-diameter fitting cylinder portion are integrally formed at one end portion in the axial direction, and an opening window extending in the circumferential direction at a predetermined length in the axially intermediate portion is separated in the circumferential direction. A plurality of intermediate sleeves that are formed on the outer peripheral side of the inner shaft member, and (c) are disposed between the inner shaft member and the intermediate sleeve, which face each other in the direction perpendicular to the axis. And the intermediate sleeve are elastically connected to each other, and a main body rubber elastic body having a plurality of pocket portions opened to the outer peripheral surface through the opening windows of the intermediate sleeve, and (d) one end portion in the axial direction are By being externally fitted and fixed to the fitting cylinder portion of the intermediate sleeve and assembled to the intermediate sleeve in an externally inserted state, the plurality of pocket portions in the main rubber elastic body are covered so that incompressible fluids are sealed therein. And (e) an outer tubular member forming a plurality of fluid chambers, and (e) a tubular shape having a circumferential length of not less than half the circumference and being externally fitted to the intermediate sleeve, so that one end portion in the axial direction has the opening window. And the other end in the axial direction is clamped and fixed over the entire circumference between the outer cylindrical member and the axial end of the intermediate sleeve opposite to the fitting cylindrical part. Assembled and assembled,
A tubular orifice member that forms an orifice passage that allows the plurality of fluid chambers to communicate with each other, and (f) the main body rubber elastic body at the opening edge portion of the opening window in the intermediate sleeve from the opening edge portion of the opening window. And a seal projection that is formed by projecting inward of the window and projecting outward in the radial direction from the outer peripheral surface of the intermediate sleeve, and is in pressure contact with the inner peripheral surface of the tubular orifice member. The present invention is characterized by the fluid filled type vibration damping device.

In the fluid filled type vibration damping device having the structure according to the present embodiment, the large diameter portion of the intermediate sleeve fitted and fixed directly to the outer tubular member is provided only at one end portion in the axial direction. Since it is formed, the cylindrical orifice member can be externally attached to the intermediate sleeve from the other end portion in the axial direction where the large diameter portion is not formed, and therefore, the length of a half circumference or more can be provided in the circumferential direction. It is possible to assemble the tubular orifice member extending in the vertical direction without forming a divided structure, the number of parts is suppressed, the structure is simplified, and the manufacturing is facilitated.

In addition, at the inner peripheral surface of the tubular orifice member and the fitting surface of the intermediate sleeve, the seal ridges projectingly formed at the opening edge of the opening window are pressed against the inner peripheral surface of the cylindrical orifice member. Good fluid tightness is exhibited by the presence of the fluid, leakage of incompressible fluid through such fitting surface,
Therefore, the problem such as a short circuit of the orifice passage resulting from this can be effectively suppressed.

The seal projection formed on the opening edge portion of the opening window of the intermediate sleeve has an opening edge of the opening window in consideration of the shape of the opening window, the shape of the fluid chamber, the tubular orifice member and the like. It can be provided at an appropriate position in the section with an appropriate circumferential length. Here, more preferably, even more excellent fluid tightness can be exhibited by forming the sealing ridge over substantially the entire length in the circumferential direction of the opening window in the intermediate sleeve. Further, the tubular orifice member may have a tubular shape that extends over the entire circumference in the circumferential direction, or may have a substantially C-shaped substantially tubular shape that does not fill one round in the circumferential direction. Further, the tubular orifice member may be formed with an axial length such that one end portion in the axial direction thereof reaches the axially intermediate portion of the opening window of the intermediate sleeve, or the opening window of the intermediate sleeve is arranged in the axial direction. It may be formed with an axial length extending across the intermediate sleeve to near the large diameter portion. In particular, one end of the tubular orifice member in the axial direction reaches only the axially intermediate portion of the opening window of the intermediate sleeve, and the tubular orifice member has only the other axial end of the intermediate sleeve and the outer tubular member. Even with a substantially cantilevered fixing structure in which the pressure is held between the seals, the seal ridge protruding outward in the radial direction is pressed against the tubular orifice member at the opening peripheral edge of the opening window of the intermediate sleeve. In addition, the outer cylindrical member is externally fitted and fixed to the outer peripheral surface of the cylindrical orifice member by reducing the diameter such as drawing, so that the sealing performance at the cantilever-fixed end of the cylindrical orifice member is also high. In addition, it can be stably exhibited.

In order to further improve the sealing effect of the enclosed incompressible fluid, for example, a seal rubber layer is formed on the inner peripheral surface of the outer tubular member over substantially the entire surface, and this seal rubber layer is used as an outer layer. It is desirable that the cylindrical member and the cylindrical orifice member or the fitting surface of the intermediate sleeve be pressed against each other.

Furthermore, the orifice passage for connecting the plurality of fluid chambers to each other can be advantageously formed, for example, by covering a concave groove that opens to the outer peripheral surface of the tubular orifice member and extends with the outer tubular member. In that case, since the concave groove can be set to have an appropriate shape such as meandering or bending in the circumferential direction or the axial direction, a large degree of freedom in design regarding the length and cross-sectional area of the orifice passage is realized. It can be done.

According to a second aspect of the present invention, in the fluid filled type vibration damping device according to the first aspect, the outer tubular member has a substantially bottomed cylindrical shape, and the inner shaft member is the outer tubular member. Is arranged so as to enter the opening from the axial direction, and the opening end edge portion of the outer tubular member is externally fitted and fixed to the fitting tubular portion of the intermediate sleeve, and with respect to the bottom wall portion of the outer tubular member. While axially abutting the other end portion of the tubular orifice member in the axial direction to position and support the tubular orifice member, an incompressible fluid is provided between the main rubber elastic body and the facing surface of the bottom wall portion of the outer tubular member. Is formed independently of the plurality of fluid chambers, and axial end portion fluid chambers in which the relative pressure fluctuations are generated between the fluid chambers when the vibration is input. The fluid chamber of the plurality of fluid chambers That the formation of the second orifice passage occupied passed, with the one, characterized.

In the fluid filled type vibration damping device having the structure according to the present embodiment as described above, at the time of inputting the vibration in the direction perpendicular to the axis, the effective vibration damping is based on the fluid flow through the orifice passage between the plurality of fluid chambers. In addition to the effect being exerted, it becomes possible to effectively obtain the vibration damping effect based on the fluid flow through the second orifice passage between the fluid chamber and the axial end fluid chamber when the vibration in the axial direction is input. Further, in the fluid filled type vibration damping device of the present aspect, as described above, the short circuit of the second orifice passage due to the leakage between the fitting surfaces of the tubular orifice member and the intermediate sleeve causes the short circuit of the opening window of the intermediate sleeve. Since it is highly prevented by the sealing ridges protruding from the opening edge, the vibration isolation effect based on the flow action of the fluid flowing in the second orifice passage is effectively prevented without being obstructed by the passage short circuit. And it can be demonstrated stably. Furthermore, in this aspect, since the other axial end of the tubular orifice member is abutted and positioned by the bottom wall of the outer tubular member, the position of the assembled tubular orifice member is stabilized. As described above, the fluid tightness between the tubular orifice member and the outer tubular member and between the tubular orifice member and the intermediate sleeve can be more stably exhibited. The second orifice passage can be formed by using a tubular orifice member, and thus the second orifice passage can be advantageously realized with a small number of parts and a simple structure.

According to a third aspect of the present invention, in the fluid filled type vibration damping device according to the first aspect, the outer tubular member has a substantially bottomed cylindrical shape, and the inner shaft member is the outer tubular member. Of the outer cylinder member, the opening end edge of the outer cylinder member is externally fitted and fixed to the fitting cylinder part of the intermediate sleeve, and the cylinder is fitted to the bottom wall part of the outer cylinder member. The other end of the axial orifice member is brought into contact with the other end in the axial direction for positioning and support, while at least a part of the bottom wall of the outer tubular member is formed of a flexible film, and the main body rubber elastic member is provided. A partition member is arranged between the body and the opposing surface of the bottom wall portion of the outer tubular member, and a pressure receiving chamber in which a part of the wall portion is formed of the main rubber elastic body is formed on one side of the partition member. In addition, a part of the wall is flexible on the other side of the partition member. In forming a configured equilibrium chamber, the encapsulating an incompressible fluid to the equilibrium chamber with pressure receiving chamber, that the formation of the fluid flow paths allowed to communicate with each other the equilibrium chamber with pressure receiving chamber, characterized.

In the fluid filled type vibration damping device having the structure according to the present embodiment as described above, at the time of inputting the vibration in the direction perpendicular to the axis, the effective vibration damping is performed based on the fluid flow through the orifice passage between the plurality of fluid chambers. In addition to the effect being exerted, it becomes possible to effectively obtain the vibration damping effect based on the fluid flow through the fluid flow path between the pressure receiving chamber and the equilibrium chamber when the vibration in the axial direction is input. Further, in such a fluid filled type vibration damping device, an increase in the internal pressure of the pressure receiving chamber when a static load is applied between the inner shaft member and the outer tubular member can be eliminated by the volume change of the equilibrium chamber, For example, even under a condition where a static supporting load is applied in a mounted state such as an automobile engine mount, desired vibration damping characteristics can be stably exhibited.

In the fluid filled type vibration damping device according to any one of the first to third aspects of the present invention as described above, the seal ridges protruding from the opening edge portion of the opening window of the intermediate sleeve are: For example, it is formed in an integrally vulcanized molded product obtained by setting an intermediate sleeve in a predetermined molding cavity and vulcanizing and molding a main rubber elastic body, and forming a seal ridge as a molded body shape of the main rubber elastic body. This can be achieved by projecting the intermediate sleeve radially outward of the outer peripheral surface, but it is also possible to form the seal ridge after vulcanization molding of the main rubber elastic body.

Specifically, for example, in the integrally vulcanization molded article of the main rubber elastic body as described above, the seal ridge is
The intermediate sleeve is formed so as not to project from the outer peripheral surface of the intermediate sleeve or slightly projected, and the intermediate sleeve is subjected to a diameter reduction process such as a drawing process after the integral vulcanization molded product is molded to reduce the diameter. The protrusion of the seal on the outer peripheral surface relative to the formed intermediate sleeve,
It is also possible to increase the protruding height.

Particularly, in the integrally vulcanization molded product of the main rubber elastic body, the outer peripheral surface of the seal ridge is formed to be substantially flush with the outer peripheral surface of the intermediate sleeve, and the intermediate sleeve is vulcanized and molded. It is desirable to apply a pre-compression in the radial direction to the rubber elastic body of the main body by performing a drawing process, and to make the sealing ridge project outward in the radial direction of the intermediate sleeve. It is possible to reliably cut off the end of the intermediate sleeve at the opening window during vulcanization molding, and the rubber elastic body of the main body unnecessarily rotates from the opening window of the intermediate sleeve to the outer peripheral surface of the intermediate sleeve. In addition, it is possible to more advantageously prevent a defect that adversely deteriorates the fluid tightness of the fluid chamber.

[0022]

Embodiments of the present invention will now be described in detail with reference to the drawings in order to more specifically clarify the present invention.

First, FIGS. 1 and 2 show an automobile engine mount 10 as a first embodiment of the present invention. In this engine mount 10, an inner shaft metal member 12 as an inner shaft member and an outer cylinder metal member 14 as an outer cylinder member are arranged apart from each other, and the inner shaft metal member 12 and the outer cylinder metal member 14 are made of a main rubber elastic body 16. The inner shaft metal fitting 12 is attached to a power unit of an automobile,
The outer cylinder fitting 14 is attached to the body of the automobile so that the power unit can be supported in a vibration-proof manner with respect to the body. Note that the engine mount 10 of the present embodiment is mounted in a state where the vertical direction in FIG. 1 is a substantially vertical vertical direction, and in the following description, the vertical direction means, in principle, the vertical direction in FIG. It means the direction.

More specifically, the inner shaft fitting 12 has a solid, small-diameter circular rod shape, and an attachment fixing portion 18 is integrally formed with an axial upper end portion extending straight in the vertical direction. . Further, a tapered stepped portion 20 is provided at an axially intermediate portion of the inner shaft metal fitting 12,
A small diameter portion 22 is formed on the lower side in the axial direction, and a large diameter portion 24 is formed on the upper side in the axial direction, with the tapered portion 20 with steps interposed therebetween.

Further, on the outer peripheral side of the inner shaft fitting 12, an intermediate tubular fitting 26 having a thin, large-diameter cylindrical shape as an intermediate sleeve is arranged on the same central axis at a predetermined distance in the radial direction. ing. The intermediate tubular metal member 26 has a stepped portion 30 that extends radially outward with respect to one axial end (upper axial end) of a small-diameter tubular portion 28 that extends straight in the axial direction over substantially the entire length. A large-diameter cylindrical portion 32 having a large-diameter cylindrical shape as a fitting cylindrical portion is integrally provided to form a stepped cylindrical shape. In addition, a pair of window portions 36, 36 as opening windows are formed in the axially intermediate portion of the intermediate tubular metal piece 26 at portions facing each other in one radial direction, and each window portion 36 is formed.
However, each of them is opened with a length of a little less than half a circumference in the circumferential direction. It should be noted that each window portion 36 has an axial opening width that extends between each of the small-diameter tubular portion 28 and the large-diameter tubular portion 32.

The inner shaft metal fitting 12 is arranged so as to be inserted from the axially upper opening of the intermediate tubular metal fitting 26, and the entire small diameter portion 22 of the inner shaft metal fitting 12 is radially outward. The intermediate tubular metal fitting 26 is positioned in a state of being spaced apart and enclosed. The mounting fixing portion 18 of the inner shaft metal fitting 12 is located so as to project axially upward from the intermediate tubular metal fitting 26, while the axial lower end of the small diameter portion 22 is the axial lower end of the intermediate tubular metal fitting 26. It is located in the middle part in the axial direction, which is not reached.

Further, a rubber elastic body 16 is disposed between the inner shaft fittings 12 and the intermediate tubular fittings 26 which face each other in the radial direction, and the inner shaft fittings 12 and the intermediate tubular fittings 26 are elastically connected. Has been done. This rubber elastic body 16
As shown in FIGS. 3 to 4, each has a circular block shape as a whole, and the small diameter portion 22 of the inner shaft metal fitting 12 is arranged so as to extend from the center of the upper end surface thereof onto the central axis.
The stepped tapered portion 20 is inserted, and the outer peripheral surfaces of the small diameter portion 22 and the stepped tapered portion 20 are vulcanized and bonded to the main rubber elastic body 16. Further, the main rubber elastic body 16
An intermediate cylindrical metal fitting 26 is superposed and vulcanized and bonded to the outer peripheral surface of the. In short, the main rubber elastic body 16 is formed as an integrally vulcanized molded product 38 including the inner shaft fitting 12 and the intermediate tubular fitting 26.

Further, in the main rubber elastic body 16, a circular recess 40 having a large diameter inverted mortar shape that opens downward is formed at the center of the lower end surface in the axial direction, and opens in the outer peripheral surface. The pair of pockets 42, 42
The inner shaft fitting 12 is formed on both sides of the inner shaft fitting 12 in one radial direction. Each of the pair of pocket portions 42, 42 is formed in the intermediate cylindrical metal fitting 26 with a length of a little less than half a circumference in an expanding shape in which the axial opening width gradually increases as it approaches the opening. The outer peripheral surface is opened through the pair of windows 34, 34 formed. In addition, the pair of pockets 42, 42 are both formed so as to be displaced from the center of the main body rubber elastic body 16 in the axial direction by a predetermined amount, and are thereby positioned so that the main body rubber elastic body 16 is formed. The wall thickness dimensions of the axial upper wall portion 44 and the axial lower wall portion 46 of each pocket portion 42 formed by are different from each other, so that the axial lower wall portion 46 is formed as a whole more than the axial upper wall portion 44. It is thick throughout.

Further, particularly in the present embodiment, as shown in FIG. 3, the main rubber elastic body 16 is formed so as to project inward of the window by a predetermined length: 1 from the opening edge of the window 36. As a result, as shown also in FIG. 5, a projecting ridge which is integrally formed with the main rubber elastic body 16 and has a substantially constant height: 1 at the opening edge of the window 36. Part 5
0 is formed so as to extend with a predetermined width over substantially the entire length in the circumferential direction.

On the other hand, the outer tubular metal piece 14 has a large-diameter, substantially bottomed cylindrical shape having a bottom wall portion 52 and a peripheral wall portion 54. The peripheral wall portion 54 has a cylindrical shape having a diameter larger than that of the intermediate tubular fitting 26 and extends substantially straight in the axial direction, and the axial length thereof is substantially the same as that of the intermediate tubular fitting 26.

On the other hand, the bottom wall portion 52 of the outer tubular fitting 14
A large-diameter through hole 56 is formed in the central portion of the. Further, a cylindrical holding cylinder portion 58 that projects downward in the axial direction is integrally formed at the opening peripheral edge portion of the through hole 56 in the bottom wall portion 52. A diaphragm 60 as a flexible film is arranged in the through hole 56. The diaphragm 60 has a substantially disc shape made of a thin rubber elastic film, and an outer peripheral edge portion of the diaphragm 60 is vulcanized and adhered to the holding cylinder portion 58. As a result, the through hole 56 formed in the bottom wall portion 52 of the outer tubular fitting 14 becomes
The diaphragm 60 is fluid-tightly closed. The diaphragm 60 is arranged with a slack so that deformation is easily allowed. A thin seal rubber layer 62 integrally formed with the diaphragm 60 is attached to the inner peripheral surface of the peripheral wall portion 54 over substantially the entire surface thereof.

The outer tubular metal piece 14 is formed by integrally vulcanizing and molding the main rubber elastic body 16 from one axial end thereof.
8, which is externally inserted and has one axial end (opening end edge)
Is externally inserted into the large-diameter tubular portion 32 of the intermediate tubular metal fitting 26 and is reduced in diameter by an eight-way drawing process or the like, so that it is fitted and fixed to the large-diameter tubular portion 32. Further, as a result, the inner shaft fitting 12 is arranged on the same central axis so as to enter from the opening of the outer tubular fitting 14. The axial lower end surface of the intermediate tubular metal fitting 26 is in contact with the bottom wall portion 52 of the outer tubular metal fitting 14, whereby the intermediate tubular metal fitting 26 is axially positioned with respect to the outer tubular metal fitting 14. . A seal rubber layer 62 is sandwiched and sealed between the fitting surfaces of the intermediate tubular metal fitting 26 and the outer tubular metal fitting 14.

Thus, the outer tubular metal fitting 14 is the intermediate tubular metal fitting 2
By being externally fitted and fixed to 6, the opening portion of the outer tubular metal fitting 14 on the side of the peripheral wall portion 54 is fluid-tightly covered by the main rubber elastic body 16, so that the bottom portion of the outer tubular metal fitting 14 is A liquid chamber 64 containing an incompressible fluid is formed between the opposing surfaces of the main rubber elastic body 16 and the diaphragm 60. As the sealed fluid, for example, water, alkylene glycol, polyalkylene glycol, silicone oil, or a mixture thereof can be adopted.
Particularly, in order to effectively obtain the vibration damping effect based on the resonance action of the fluid through the orifice passage, which will be described later, the viscosity is 0.1
It is desirable to use a low-viscosity fluid of Pa · s or less.

A partition member 66 having a substantially disk shape as a whole is arranged in the liquid chamber 64 so as to spread in a direction perpendicular to the axis. The partition member 66 is formed by stacking a thin disk-shaped lid fitting 70 on the upper surface of a thick disk-shaped partition fitting 68, and the outer peripheral edge portions of the partition fitting 68 and the lid fitting 70. Are closely stacked and sandwiched between the bottom wall portion 52 of the outer tubular metal member 14 and the axial lower end surface of the outer peripheral edge portion of the main body rubber elastic body 16, whereby the diaphragm 60 and the main body rubber elastic body. It is accommodated and arranged between the facing surfaces of the body 16. As a result, the liquid chamber 64 is fluid-tightly divided into upper and lower halves by the partition member 66, so that the main liquid chamber 72 as a pressure receiving chamber is formed on the upper side of the partition member 66, while the partition member is formed. A sub-liquid chamber 74 as a balance chamber is formed below 66. In the main liquid chamber 72, a part of the wall portion is composed of the main body rubber elastic body 16, and pressure fluctuation is generated based on elastic deformation of the main body rubber elastic body 16 at the time of vibration input. A part of the wall of the sub liquid chamber 74 is composed of the diaphragm 60, and the volume change is easily allowed based on the deformation of the diaphragm 60.

Furthermore, the partition fitting 68 is formed with a recess groove 76 having a length of less than one circumference, which is open to the outer peripheral surface and extends in the outer peripheral portion in the circumferential direction. The opening of the recess groove 76 is the outer tubular fitting. A fluid-tight cover is provided at 14. As a result, the outer peripheral portion of the partition member 66 extends in the circumferential direction, one end in the circumferential direction is connected to the main liquid chamber 72 through the communication hole 78, and the other end in the circumferential direction passes through the communication hole 80 and the auxiliary liquid chamber 74. A fluid flow path 82 connected to the fluid flow path 82 is formed.
Through, the fluid flow between the main liquid chamber 72 and the sub liquid chamber 74 is allowed. In this embodiment,
The length, the cross-sectional area, etc. of the fluid flow passage 82 are adjusted so that a high damping effect is exhibited in a low frequency range corresponding to the engine shake based on the resonance action of the fluid flowing in the fluid flow passage 82. .

Further, a circular central recess 84 that opens upward is formed in the central portion of the partition fitting 68, and a movable rubber plate 86 having a disc shape with a predetermined thickness is formed in the central recess 84. It is accommodated and arranged, and the opening of the central recess 84 is covered with the lid fitting 70. The movable rubber plate 86 is
An annular supporting portion 88, which is thicker than the central portion, is provided at the outer peripheral edge portion, and the annular supporting portion 88 is provided with the partition fitting 68 and the lid fitting 7.
By being sandwiched by 0, it is disposed in the central recess 84 in a state where a predetermined amount of axial elastic deformation is allowed in the central portion. A plurality of through holes 9 are formed in both upper and lower walls of the central recess 84 formed by the partition metal fitting 68 and the lid metal fitting 70.
0 are provided so that the hydraulic pressures of the main liquid chamber 72 and the sub liquid chamber 74 are exerted on the upper surface and the lower surface of the movable rubber plate 86 arranged in the central recess 84 through these through holes 90. It has become. Then, the movable rubber plate 86 is elastically deformed on the basis of the pressure difference between the main liquid chamber 72 and the auxiliary liquid chamber 74 exerted on the upper and lower surfaces of the movable rubber plate 86, thereby responding to the elastic deformation amount of the movable rubber plate 86. Through hole 90 and central recess 84 formed in partition metal fitting 68 and lid metal fitting 70, respectively, by the amount.
A fluid flow between the main liquid chamber 72 and the sub liquid chamber 74 is substantially generated, so that the pressure fluctuation of the main liquid chamber 72 is reduced or absorbed. . In particular, in the present embodiment, the elastic deformation amount of the movable rubber plate 86 is limited by the elasticity of the movable rubber plate 86 and the contact of the movable rubber plate 86 with the inner surface of the central recess 84, so that high frequencies such as muffled sound are generated. When inputting a small amplitude vibration, the main liquid chamber 72
While the pressure fluctuation of the movable rubber plate 86 can be advantageously absorbed or reduced based on the elastic deformation of the movable rubber plate 86, the elastic deformation amount of the movable rubber plate 86 is limited at the time of vibration input of low frequency large amplitude such as engine shake. As a result, effective pressure fluctuation is induced in the main liquid chamber 72.

Further, the outer tubular metal fitting 14 is externally fitted and fixed to the intermediate tubular metal fitting 26, so that the windows 36 and 36 of the intermediate tubular metal fitting 26 are fluid-tightly covered by the outer tubular metal fitting 14. The openings of the pair of pocket portions 42, 42 are covered to form a pair of working fluid chambers 92, 92 as fluid chambers in which incompressible fluid is enclosed. Further, in each of the pair of working liquid chambers 92, 92, an incompressible fluid similar to that in the main liquid chamber 72 is sealed.

Further, the outer tubular fitting 14 and the intermediate tubular fitting 26
A cylindrical orifice member 94 is disposed in a housed state between the surfaces facing each other in the direction orthogonal to the axis. Cylindrical orifice member 94
As shown in FIGS. 6 to 9, each has a substantially cylindrical shape having a circumferential length of at least a half circumference (in the present embodiment, a circumferential length of approximately 3/4 circumference), and is composed of It is made of a hard material such as resin or metal. In addition, the tubular orifice member 9
The inner diameter of 4 is slightly larger than the outer diameter of the small-diameter tubular portion 28 of the intermediate tubular metal fitting 26, while the outer diameter of the tubular orifice member 94 is the outside of the large-diameter tubular portion 32 of the intermediate tubular metal fitting 26. It is almost the same as the diameter. Furthermore, the tubular orifice member 94 is externally mounted from the axial end of the intermediate tubular fitting 26 opposite to the large-diameter tubular portion 32 toward the axial upper side, and the tubular orifice member 94 is attached. An upper end portion 96 as one end portion in the axial direction extends to the window portion 36 and is positioned at an intermediate portion in the axial direction of the window portion 36, while a lower end portion 98 as the other end portion in the axial direction is an outer portion. While being brought into contact with and positioned by the bottom wall portion 52 of the tubular metal fitting 14, the intermediate tubular metal fitting 26 is clamped over the entire circumference between the opening side edge of the small diameter tubular portion 28 and the peripheral wall portion 54 of the outer tubular metal fitting 14. It is fixed and assembled.

Further, the cylindrical orifice member 94 is formed with a concave groove 100 extending in a reciprocating or meandering manner in the circumferential direction with an opening on the outer peripheral surface. One end of the concave groove 100 is formed. Is connected to one working fluid chamber 92 through a through hole 102 penetrating the bottom wall of the groove 100, and the other end of the groove 100 in the circumferential direction is connected to the bottom wall of the groove 100. It is connected to the other working fluid chamber 92 through a through hole 104 formed therethrough. The recessed groove 100 is fluid-tightly covered by the peripheral wall portion 54 of the outer tubular metal member 14 to form an orifice passage 106 that communicates the pair of working fluid chambers 92, 92 with each other. In the present embodiment, the pair of working fluid chambers 92, 92 is passed through the orifice passage 106.
The length, cross-sectional area, etc. of the orifice passage 106 are adjusted so that a high damping effect can be exerted against low-frequency vibrations such as engine shake based on the resonance action of the fluid flowing between them. Further, in the present embodiment, the cylindrical orifice member 94 is provided with a lightening hole 108 having an appropriate shape and size as needed.

Further, in this embodiment, the tubular orifice member 94 is provided with rectangular positioning notches 107, 107 which are open at the upper end surface in the axial direction, while the tubular orifice member 94 is externally fitted. Intermediate tube fitting 26
On the outer peripheral surface of the pair of window portions 36,
Engaging projections 109, 109 projecting axially from the large-diameter cylindrical portion 32 between 36 are fixed by a rubber elastic body.
Then, the positioning notches 107, 107 of the tubular orifice member 94 are fitted to the engaging convex portions 109, 109, so that the tubular orifice member 94 is surrounded by the integral vulcanization molded product 38. It is designed to be positioned in the direction.

Further, particularly in the present embodiment, when the tubular orifice member 94 is externally fitted to the intermediate tubular metal fitting 26, the intermediate tubular metal fitting 26 is previously subjected to a diameter reduction process such as an eight-way drawing.
By pre-compressing the main rubber elastic body 16, the diameter of the intermediate tubular fitting 26 is reduced. That is, by pre-compressing the main rubber elastic body 16, the tensile stress induced in the main rubber elastic body 16 during vulcanization molding of the main rubber elastic body 16 is reduced or eliminated, and the load bearing performance and durability are improved. Is being improved.

Furthermore, by reducing the diameter of the intermediate tubular metal member 26, a reducing force is exerted on the outer peripheral surface of the main rubber elastic body 16 to elastically deform the main rubber elastic body 16.
The projected ridge portion 50 integrally formed with the main rubber elastic body 16 and formed by being adhered and formed over substantially the entire circumference of the opening edge portion of the window portion 36,
As shown in FIG. 10, the intermediate tubular metal fitting 26 is made to project radially outward relative to the intermediate tubular metal fitting 26.
As a result, at the opening edge portion of the window portion 36, a seal having a substantially semicircular cross section that is projected to the inside of the window from the opening edge portion and is projected radially outward from the outer peripheral surface of the intermediate tubular metal fitting 26. The ridge 110 is formed. And such seal ridge 1
10 is pressed against the inner peripheral surface of the tubular orifice member 94 by externally inserting the tubular orifice member 94 into the intermediate tubular fitting 26, whereby the opening edge portion of the window portion 36 and the tubular orifice member. The fluid tightness between the fitting surfaces of 94 is ensured to a high degree.

Further, in the present embodiment, the seal projection 110 is formed so as to project also on the opening edge portion located on the axially upper side of the window portion 36, and the intermediate tubular metal fitting 26 of the outer tubular metal fitting 14 is formed.
At the time of external fitting and fixing to the outer cylindrical metal fitting 14, the seal ridge 110 is pressed against the inner peripheral surface of the outer cylindrical metal fitting 14 so that the opening side edge of the peripheral wall portion 54 of the outer cylindrical metal fitting 14 and the large diameter cylinder of the intermediate cylindrical metal fitting 26. The sealability between the fitting surfaces of the portions 32 is also improved. In addition, as apparent from the above description, in the present embodiment, the seal protrusion 110 is formed over substantially the entire length of the window portion 36 in the circumferential direction.

In the engine mount 10 having such a structure, the inner shaft fitting 12 has a mounting and fixing portion 18 attached thereto.
Is fixed to a power unit (not shown) by a bolt (not shown) inserted through the mounting hole 111, while the outer tubular metal fitting 14 is externally fitted and fixed to the tubular bracket 112.
It is fixed to the body of the automobile through the, thereby making it possible to support the power unit in a vibration-proof manner with respect to the body. The inner shaft fitting 12 is covered with a reverse cup-shaped dustproof cover 114 and fitted in the large-diameter portion 24. The dustproof cover 114 covers the entire upper opening of the tubular bracket 112. It is being appreciated.

In the vehicle engine mount 10 having the above-mentioned structure, when mounted on the vehicle,
When a substantially vertical vibration load is input between the inner shaft fitting 12 and the outer tubular fitting 14, a relative pressure difference is generated between the main liquid chamber 72 and the sub liquid chamber 74. When the input vibration is a low-frequency large-amplitude vibration such as an engine shake, a high damping effect is exhibited based on the resonance action of the fluid flowing through the fluid flow path 82, and the input vibration is a high-frequency wave such as a muffled sound. In the case of small-amplitude vibration, the pressure fluctuation of the main liquid chamber 72 is absorbed or reduced based on the elastic deformation of the movable rubber plate 86, and the vibration isolation effect by the low dynamic spring action is exhibited.

On the other hand, when a vibration load in a substantially horizontal direction is input between the inner shaft fitting 12 and the outer tubular fitting 14 when the vehicle is mounted, a relative pressure difference between the pair of working fluid chambers 98, 98. Is generated, and the orifice passage 1
Based on the resonance effect of the fluid flowing through 06, an effective vibration damping effect against such vibration is exhibited.

There, such engine mount 1
In No. 0, the tubular orifice member 94 integrally formed with a shape that extends in the circumferential direction for a length of more than half the circumference is simply externally inserted from the axial lower end of the intermediate tubular metal fitting 26, and the integrally vulcanized molded product is obtained. Since the tubular orifice member 94 can be easily assembled to the engine mount 10 without forming the divided structure in the manufacturing of the engine mount 10, the number of members is suppressed and the structure is reduced. In addition to being simplified, the assembling workability can be advantageously improved.

Moreover, in this embodiment, since the upper end portion 96 of the tubular orifice member 94 is positioned so as to extend to the axially intermediate portion of the window portion 36, the orifice passage 106 in the tubular orifice member 94 is positioned. Can be set with a sufficient length, and the degree of freedom in tuning the orifice passage 106 can be more advantageously ensured.

Further, the intermediate tubular metal fitting 26 to which the tubular orifice member 94 is fitted is provided with a sealing ridge 110 protruding from each opening edge of the windows 36, 36. Since it is pressed against the inner peripheral surface of the tubular orifice member 94, the fitting surface between the intermediate tubular metal fitting 26 and the tubular orifice member 94 does not have to be specially processed such as an eight-way drawing. It is possible to secure a high degree of fluid tightness between them. Therefore, the tubular orifice member 94
The short circuit of the orifice passage 106 and the leakage of the enclosed fluid between the fitting surfaces of the intermediate tubular metal fitting 26 and the intermediate cylinder fitting 26 can be effectively prevented, and the desired vibration damping effect can be stably obtained, and Reliability can also be ensured to a high degree.

In particular, in this embodiment, the seal projection 110
Is the projected ridge portion 5 integrally formed with the main rubber elastic body 16.
0 is formed by subjecting the intermediate tubular metal fitting 26 to a drawing process so as to bulge and deform outward from the intermediate tubular metal fitting 26 in the radial direction. On the other hand, it is not necessary to perform fine processing for molding the seal ridge 110, and the structure and manufacturing of the vulcanization mold are facilitated. Further, since it is not necessary to perform fine processing for molding the seal ridge 110 on the vulcanization molding die of the main rubber elastic body 16, the intermediate tubular metal fitting 26 of the intermediate tubular metal fitting 26 at the time of molding the main rubber elastic body 16 is not required. It is possible to reliably cut off the end portion of the rubber material in the window portion 36, and the main rubber elastic body 16 unnecessarily wraps around the outer peripheral surface of the intermediate tubular metal fitting 26 from the window portion 36 of the intermediate tubular metal fitting 26. Also, a problem that deteriorates the fluid tightness of the working fluid chamber 92 can be advantageously suppressed.

Furthermore, in the engine mount 10 of the present embodiment, the main liquid chamber 72 and the sub liquid chamber 74, in which relative pressure fluctuations are generated at the time of axial vibration input, are formed. The fluid tightness of the pair of working liquid chambers 92, 92 in 72 and the sub liquid chamber 74 also means that the seal projection 110 protruding from the opening edge portion of the window portion 36 is brought into contact with the tubular orifice member 94. Can be advantageously secured by.

Next, FIGS. 11 to 12 show an automobile engine mount 140 as a second embodiment of the present invention. In the present embodiment, members and parts having the same structure as in the first embodiment will be described in detail by assigning the same reference numerals to those in the first embodiment in the drawings. The description is omitted.

In the engine mount 140 of this embodiment, the movable rubber plate 148 is arranged in a stretched state in the through hole 56 formed in the central portion of the bottom wall portion 52 of the outer tubular metal fitting 14. The movable rubber plate 148 has a disk shape with a predetermined thickness, and the outer peripheral edge portion is vulcanized and adhered to the peripheral edge portion of the through hole 56, whereby the through hole 56 is covered in a fluid-tight manner.
Under such an arrangement, the internal pressure and the atmospheric pressure of the axial end fluid chamber 144 are exerted on the upper surface and the lower surface of the movable rubber plate 148, and the axial vibration load is applied to input the axial load. When the pressure fluctuation is generated in the directional end fluid chamber 144, the movable rubber plate 148 is elastically deformed to absorb and reduce the pressure fluctuation of the axial end fluid chamber 144. The movable rubber plate 148
Since the elastic deformation amount is limited based on its own elasticity, the axial end fluid chamber 144 of the axial direction end fluid chamber 144 is input at the time of input of high-frequency small-amplitude vibration, similarly to the movable rubber plate (86) of the first embodiment. Although pressure fluctuations can be effectively absorbed and reduced, effective pressure fluctuations are generated in the axial end fluid chamber 144 when low-frequency large-amplitude vibrations are input.

Further, an annular protrusion 150 as shown in FIGS. 13 to 14 is integrally formed on the lower end portion of the tubular orifice member 94 of the present embodiment in the axial direction. The annular protrusion 150 has an inner flange shape that protrudes radially inward from the opening peripheral edge of the tubular orifice member 94 on the lower side in the axial direction by a predetermined length, and the inner peripheral edge is It reaches near the through hole 56 formed in the bottom wall portion 52 of the outer tubular metal member 14. The annular protrusion 150 is superposed in close contact with the bottom wall 52 of the outer tubular fitting 14, and the outer peripheral edge portion of the annular protrusion 150 has an intermediate tubular fitting 26.
Also, it is sandwiched in the axial direction between the lower end portion of the main body rubber elastic body 16 in the axial direction and the bottom wall portion 52 of the outer tubular metal member 14 to be fixed to the outer tubular metal member 14, and the annular protrusion 1
The inner peripheral edge of 50 extends to and is positioned inside the axial end fluid chamber 144.

Further, the cylindrical orifice member 94 is formed with a recessed groove 152 formed so as to extend in the circumferential direction by a length of a little less than one circumference in the axial direction, and the recessed groove 152 is formed.
Communication holes 154, 1 with both circumferential ends of which extend through the bottom wall
The working fluid chambers 92, 92 communicate with each other through 54. Further, at a position separated axially downward of the concave groove 152,
A pair of divided concave grooves 156, 156 extending in the circumferential direction with a length of less than a half circumference are formed. Each of the pair of divided concave grooves 156, 156 extends axially downward at one end in the circumferential direction, and is opened at the inner peripheral edge of the annular protrusion 150 through the radial groove 158 formed in the annular protrusion 150. The cylindrical orifice member 94 is open to the inner peripheral surface of the tubular orifice member 94 through a communication hole 160 penetrating the bottom wall at the other end in the circumferential direction.

Then, the peripheral wall portion 54 and the bottom wall portion 52 of the outer cylindrical metal fitting 14 are superposed in close contact with the outer peripheral surface of the cylindrical wall portion of the cylindrical orifice member 94 and the lower end surface of the annular protrusion 150, By covering the concave groove 152 in a fluid-tight manner, the orifice passage 106 of the present embodiment for communicating the pair of working liquid chambers 92, 92 with each other is formed, and
The second concave orifices 156, 156 and the radial grooves 158, 158 are fluid-tightly covered so that the working fluid chambers 92, 92 can independently communicate with the axial end fluid chamber 144. The passages 162 and 162 are formed independently of each other.

Although not clearly shown in the drawing, the sealing ridge 110 similar to that of the first embodiment is adhered to the opening edge portion of the window portion 36 of the present embodiment to form a tubular shape. As the orifice member 94 is externally inserted from the lower side in the axial direction of the intermediate tubular member 26, the seal ridge 110 is formed on the inner peripheral surface of the tubular orifice member 94 and the fitting surface of the intermediate tubular member 26. By contacting the inner peripheral surface of 94, good sealing performance is exhibited.

Incidentally, the engine mount 14 of this embodiment.
At 0, the inner shaft fitting 12 is sandwiched in the radial direction in which the pair of working fluid chambers 92, 92 are opposed to the wall portion of the axial end fluid chamber 144 formed by the main rubber elastic body 16. Located in a pair of pocket-shaped recesses 164,1
64 is formed, and the recesses 164 and 164 partially reduce the axial lower wall portions of the working fluid chambers 92 and 92, thereby setting a large spring ratio in the radial directions orthogonal to each other. In addition, the spring constant in the axial direction is adjusted.

In the engine mount 140 of the present embodiment having such a structure, when a vibration load in the direction perpendicular to the axis is input, the engine mount 140 through the orifice passage 106 is used as in the engine mount of the first embodiment. While the vibration damping effect based on the fluid flow action is effectively exhibited, when the axial vibration load is input, the axial end fluid chamber 1
The second orifice passage 162, based on the relative pressure fluctuation generated between the hydraulic fluid chamber 44 and the working fluid chambers 92, 92.
A fluid flow is generated through 162, and a vibration damping effect (high damping effect) based on a resonance action or the like of the fluid flowing in the second orifice passages 162 and 162 is exhibited. When the axial vibration in the frequency range higher than the tuning frequency of the second orifice passage 162 is input, the effect of absorbing and reducing the pressure fluctuation of the axial end fluid chamber 144 due to the elastic deformation of the movable rubber plate 148 is exerted. It will be.

Here, also in the engine mount 140 of the present embodiment, as in the engine mount (10) of the first embodiment, the window portion 3 of the intermediate tubular metal fitting 26.
At the peripheral edges of the openings of 6, 36, there are formed seal ridges 110 that extend into the window and are made to project radially outward from the outer peripheral surface of the intermediate tubular metal fitting 26 by the diameter reduction processing of the intermediate tubular metal fitting 26. ing.

As described above, the seal projection 110, which is provided so as to project over the entire circumference of the opening edge portion of the window portion 36, is provided on the inner peripheral surface of the tubular orifice member 94 and the fitting portion of the intermediate tubular metal fitting 26. It is in contact with the inner peripheral surface of the tubular orifice member 94, so that, like the first embodiment,
A pair of working fluid chambers 92, 92 and axial end fluid chamber 14
In 4, good fluid tightness can be advantageously exerted.

Although the embodiments of the present invention have been described in detail above, these are merely examples, and the present invention is
Depending on the specific description in these embodiments,
It should not be construed as limiting.

For example, in the above-described embodiment, the seal projection is formed on the opening edge of the window by drawing the intermediate tubular metal member. However, the invention is not limited to this. The elastic body may be formed so as to protrude during vulcanization molding. Alternatively, it is also possible to cause the seal projection, which is formed to slightly project at the time of vulcanization molding of the main rubber elastic body, to project further to the outside by reducing the diameter of the intermediate tubular metal fitting.

Further, the specific structure of the fluid passage, the orifice passage, etc., the passage length, the passage cross-sectional area, etc. are appropriately determined in accordance with the required vibration damping characteristics, and are not limited in any way. Not something. There, it is also possible to tune the fluid passages, the orifice passages, etc. so as to exhibit an effective vibration damping effect against idling vibration, depending on the required characteristics.

Further, in the above embodiment, a part of the walls of the main liquid chamber and the axial end fluid chamber is made of a movable rubber plate that absorbs pressure fluctuations in a high frequency range. The plate is appropriately arranged according to the required vibration damping characteristics, manufacturability, etc., and is not always necessary in the present invention.

Furthermore, in the above-described embodiment, the invention is applied to the engine mount for automobiles. However, the invention is, for example, a fluid-filled type bush as described in Japanese Utility Model Publication No. 4-43636 or a bush. Or engine mount of various structures, body mount, differential mount,
Further, it goes without saying that any of them can be applied to a vibration isolation device for various vibrators other than automobiles.

Although not listed one by one, the present invention
The present invention can be carried out in a mode in which various changes, modifications, improvements, etc. are added based on the knowledge of those skilled in the art, and such a mode does not depart from the gist of the present invention.
Both are included within the scope of the present invention,
Needless to say.

[0068]

As is apparent from the above description, in the fluid filled type vibration damping device having the structure according to the present invention, when the tubular orifice member is assembled to the intermediate sleeve, the opening edge portion of the opening window of the intermediate sleeve. Since the seal ridge projecting on the inner surface of the cylindrical orifice member is brought into contact with the inner peripheral surface of the cylindrical orifice member, the sealing property between the cylindrical orifice member and the fitting surface of the intermediate sleeve is ensured at a high level, and the circumferential direction is increased. A cylindrical orifice member extending over a half circumference or more can be easily externally attached to the intermediate sleeve in the axial direction, and easily assembled.
The simplification of the structure and the improvement of the manufacturability can be effectively achieved.

[Brief description of drawings]

1 is a longitudinal cross-sectional explanatory view showing an automobile engine mount according to a first embodiment of the present invention, and is a view corresponding to a cross-section taken along line I-I in FIG. 2;

FIG. 2 is a sectional view taken along line II-II in FIG.

FIG. 3 is a vertical cross-sectional explanatory view showing an integrally vulcanized molded product which constitutes a part of the automobile engine mount shown in FIG. 1, and is a III-III cross-sectional view in FIG. 4.

4 is a sectional view taken along line IV-IV in FIG.

5 is an explanatory plan view showing the integrally vulcanized molded product in FIG. 3. FIG.

6 is an explanatory plan view showing a tubular orifice member that constitutes a part of the automobile engine mount shown in FIG. 1. FIG.

7 is a front explanatory view showing the tubular orifice member in FIG.

8 is a right side explanatory view showing the tubular orifice member in FIG.

9 is a left side view showing the tubular orifice member in FIG.

10 is an explanatory longitudinal cross-sectional view showing an enlarged main part of the automobile engine mount shown in FIG.

11 is a vertical cross-sectional explanatory view showing an automobile engine mount according to a second embodiment of the present invention, and is a view corresponding to a cross-section taken along line XI-XI in FIG. 12;

12 is a sectional view taken along line XII-XII in FIG.

13 is a front explanatory view of a tubular orifice member forming a part of the automobile engine mount shown in FIG. 11. FIG.

14 is a sectional view taken along line XIV-XIV in FIG.

[Explanation of symbols]

10 engine mount 12 Inner shaft bracket 14 Outer tube fittings 16 Rubber elastic body 26 Intermediate tube fitting 32 Large diameter tube 36 Window 42 Pocket 92 Working fluid chamber 94 Cylindrical orifice member 96 upper end 98 Lower end 106 Orifice passage 110 seal ridges

Claims (7)

[Claims] 1. An inner shaft member and a large-diameter fitting cylinder portion are integrally formed at one end portion in the axial direction, and an opening window extending in the axial direction at a predetermined length in the circumferential direction is circumferentially formed. A plurality of intermediate sleeves that are spaced apart from each other and are spaced apart from each other on the outer peripheral side of the inner shaft member, and the inner shaft member that is disposed between the inner shaft member and the intermediate sleeves in the axially-opposing faces. A main body rubber elastic body that elastically connects the intermediate sleeve and has a plurality of pockets that open to the outer peripheral surface through the respective opening windows of the intermediate sleeve; and one end portion in the axial direction of the intermediate sleeve. By being externally fitted and fixed to the fitting cylinder part and assembled to the intermediate sleeve in an externally inserted state, the incompressible fluid is enclosed by covering the plurality of pocket parts in the main rubber elastic body. An outer tubular member that forms a plurality of fluid chambers, and an outer tubular member that has a circumferential length of at least half the circumference and is externally inserted into the intermediate sleeve so that one end in the axial direction extends to the opening window. It is taken out and arranged,
The other end in the axial direction is assembled by being clamped and fixed over the entire circumference between the outer end of the intermediate sleeve and the end in the axial direction on the side opposite to the fitting cylinder portion, and the plurality of fluid chambers are attached. A tubular orifice member that forms an orifice passage that communicates with each other; and the main body rubber elastic body that protrudes inward from the opening edge of the opening window at the opening edge of the opening window in the intermediate sleeve. A seal projection that is formed by projecting radially outward from the outer peripheral surface of the intermediate sleeve, and is in pressure contact with the inner peripheral surface of the tubular orifice member.
A fluid-filled type vibration damping device having. 2. The fluid filled type vibration damping device according to claim 1, wherein the seal projection is formed over substantially the entire length in the circumferential direction of the opening window in the intermediate sleeve. 3. The fluid filled type vibration damping device according to claim 1, wherein one end of the tubular orifice member in the axial direction is located at an axially intermediate portion of the opening window. 4. The outer cylinder member has a substantially bottomed cylindrical shape, and the inner shaft member is disposed so as to enter the opening part of the outer cylinder member in the axial direction, and the opening end edge part of the outer cylinder member is formed. The intermediate sleeve is externally fitted and fixed to the fitting tubular portion, and the other end of the tubular orifice member in the axial direction is brought into contact with the bottom wall portion of the outer tubular member in the axial direction for positioning support. On the other hand, a non-compressible fluid is enclosed between the main rubber elastic body and the opposing surface of the bottom wall of the outer tubular member, so that relative pressure fluctuation is generated between the plurality of fluid chambers when vibration is input. An axial end fluid chamber formed independently of the plurality of fluid chambers, and further forming a second orifice passage communicating the axial end fluid chamber with at least one of the plurality of fluid chambers. Item 1 to 3 Fluid filled type anti-vibration device. 5. The outer cylinder member is formed into a substantially bottomed cylinder shape, the inner shaft member is arranged so as to enter from the opening of the outer cylinder member, and the opening end edge of the outer cylinder member is formed into the intermediate sleeve. While being externally fitted and fixed to the fitting cylinder portion, the other end of the tubular orifice member in the axial direction is brought into contact with the bottom wall portion of the outer tubular member in the axial direction to position and support the same. At least a part of the bottom wall portion of the outer tubular member is formed of a flexible film, and a partition member is provided between the main rubber elastic body and the opposing surface of the bottom wall portion of the outer tubular member, A part of the wall portion forms a pressure receiving chamber composed of the main rubber elastic body on one side of the partition member,
On the other side of the partition member, a part of the wall portion forms an equilibrium chamber composed of the flexible film, and an incompressible fluid is enclosed in the pressure-receiving chamber and the equilibrium chamber and equilibrium with the pressure-receiving chamber. The fluid filled type vibration damping device according to any one of claims 1 to 3, wherein a fluid flow path is formed to connect the chambers to each other. 6. The main body rubber elastic body is formed as an integrally vulcanization molded product including the inner shaft member and the intermediate sleeve, and in the integrally vulcanization molded product, the intermediate vulcanization product is formed to have the outer peripheral surface of the intermediate sleeve. 6. The fluid filled type vibration damping device according to claim 1, wherein the seal ridge is formed by vulcanization so as to project radially outward. 7. The main body rubber elastic body is formed as an integrally vulcanization molded product including the inner shaft member and the intermediate sleeve, and the intermediate sleeve is reduced in diameter so that the main body rubber elastic body has a radial direction. By pre-compressing the outer peripheral surface of the intermediate sleeve so that the outer peripheral surface of the intermediate sleeve is deformed radially inward with respect to the seal ridge, so that the seal ridge is radially outward relative to the intermediate sleeve. The fluid filled type vibration damping device according to any one of claims 1 to 6, wherein the vibration damping device is made to protrude.