JPH0811971B2 - Fluid-filled cylindrical mounting device - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a fluid-filled tubular mount device that suppresses transmission of vibrations based on the flow of a fluid enclosed therein, and particularly in a high frequency range. The present invention relates to a fluid-filled cylindrical mount device that can be advantageously achieved with improved vibration damping characteristics with a simple structure.

(Background Art) Conventionally, such a member is interposed between two members constituting a vibration transmission system, such as a suspension bush or an engine mount in an automobile, for vibration-proof connection of both members, or one member for the other member. As a type of mounting device for vibration-proof supporting a member, an inner cylindrical metal member and an outer cylindrical metal member, which are arranged concentrically or eccentrically with each other, are elastically elastic by a rubber elastic body interposed therebetween. Cylindrical mounting devices that are connected to each other have been used. Further, in this tubular mount device, a predetermined mounting shaft is inserted and fixed in the inner tubular metal fitting, and a support member to which the mounting shaft is connected is attached to the outer tubular metal fitting. The mounting device is interposed between the mounting shaft and the support member, and both members are vibration-proof connected based on the elastic deformation of the rubber elastic body.

However, in the cylindrical mount device having such a structure, since rubber alone is used as a vibration isolator, the mount of the mount caused by the resonance of the rubber elastic body at the time of vibration input in a high frequency range. The problem was that rigidification was induced.

For example, such a cylindrical mounting device is also used as an engine mount of an FF type automobile, but in a conventional engine mount, the resonance of the rubber elastic body is 300H.
To appear in the frequency range of z ~ 700Hz,
Prevention of muffled sounds such as engine transmission noise and high-frequency vibrations has been difficult to achieve sufficiently, and therefore, in particular, with the recent demand for higher levels of quietness and riding comfort of automobiles, such high noise has been required. There is an urgent need to improve the vibration isolation characteristics in the frequency range.

(Problem to be Solved) Here, the present invention has been made in view of the circumstances as described above, and the problem to be solved is to make the mount rigid when a vibration input in a high frequency range is effective. (EN) It is possible to provide a fluid-filled cylindrical mount device that can be avoided and that the improvement of the vibration isolation performance over a wide frequency range can be realized with a simple structure.

(Solution) In order to solve such a problem, in the present invention, an inner cylindrical metal member and an outer cylindrical metal member arranged concentrically or eccentrically with each other are provided with a rubber elastic member interposed therebetween. In a cylindrical mounting device elastically connected by a body, by covering the opening of the pocket portion formed in the rubber elastic body with the outer cylindrical metal fitting, the inner cylindrical metal fitting in the vibration input direction in the radial direction. And at least one fluid chamber, in which a low-viscosity non-compressible fluid is enclosed, into which vibration to be isolated is input, and the inner tubular metal fitting is sandwiched between the fluid and the outer tubular metal fitting. A bottom wall on both sides in the circumferential direction of the pocket portion that forms the fluid chamber is provided on the side opposite to the chamber by providing a thinned portion that extends axially through between the inner tubular metal member and the outer tubular metal member. Is an elastic wall that is easily elastically deformed, while The side walls on both sides in the axial direction made of the rubber elastic body are formed as thin portions that can be bulged and deformed, and further, inside the fluid chamber, substantially correspond to the inner surface shape of the pocket portion forming the fluid chamber. By providing an action projection having a surface shape that is formed, protruding from the outer tubular metal fitting side toward the inner tubular metal fitting side and spaced apart from the inner surface of the pocket portion, to the outer tubular metal fitting, Between the opposing surfaces of the action projection and the inner surface of the wall of the fluid chamber formed of the rubber elastic body in the vibration input direction,
The feature is that a vibration action gap is formed which spreads with a substantially constant gap under the mount mounted state.

Further, in the present invention, the acting projection fixes the housing member, which is housed and arranged in the fluid chamber, to the outer tubular metal fitting so that the outer tubular metal fitting side is moved to the inner tubular metal fitting side. The fluid-filled cylindrical mount device that is formed so as to project toward is also a feature thereof.

Furthermore, according to the present invention, in such a fluid-filled tubular mounting device, when the fluid chamber is input with vibration between the inner and outer tubular metal fittings, internal pressure fluctuation is caused by elastic deformation of the rubber elastic body. It is formed as a pressure receiving chamber that is generated, and the predetermined incompressible fluid is sealed between the inner tubular metal member and the outer tubular metal member, at least a part of which is defined by a flexible film. Therefore, at least one equilibrium chamber in which the input of vibration is avoided is formed independently of the pressure receiving chamber, and an orifice passage is provided to connect the pressure receiving chamber and the equilibrium chamber to each other. , Its characteristic.

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

First, FIGS. 1 and 2 show a specific example in which the present invention is applied to an engine mount of an FF type automobile as one embodiment of the present invention.

In this figure, reference numeral 10 denotes an inner cylindrical member, on the outer side of which an outer cylindrical member 12 is arranged eccentrically in one radial direction (vertical direction in FIG. 1) and spaced apart by a predetermined distance. A substantially cylindrical rubber elastic body 14 is interposed between the inner cylindrical fitting 10 and the outer cylindrical fitting 12.
Thus, the inner and outer tube fittings 10 and 12 are integrally and elastically connected.

Further, in the engine mount 16 in the present embodiment, a mounting rod provided on the vehicle body side is inserted and fixed to the inner tubular metal fitting 10, while the outer tubular metal fitting 12 is a mounting hole of a bracket provided on the engine unit side. By being press-fitted and fixed inside, the engine unit is interposed between the engine unit side and the vehicle body side, and the engine unit is vibration-isolatedly supported with respect to the vehicle body. Also, in such a mounted state, the weight of the engine unit
The inner and outer tube fittings 10, 12 are positioned substantially concentrically (third
Along with the eccentric directions of the metal fittings 10, 12, the main vibration is input.

Here, the rubber elastic body 14 has an inner cylindrical metal fitting 10 on the inner peripheral surface thereof and an inner cylindrical metal fitting 10 on the outer peripheral surface thereof.
A thin cylindrical mounting sleeve 18 eccentrically positioned with respect to a predetermined amount is formed as an integrally vulcanized molded product which is vulcanized and bonded.

Further, in the rubber elastic body 14, the vibration input direction is in the mount radial direction. In the eccentric direction of the inner cylindrical metal fitting 10 and the mounting sleeve 18, on the side where the separation distance is small, the inner cylindrical metal fitting 10 and the mounting sleeve 18 are axially penetrated, and extend in the circumferential direction over substantially a half circumference. A lightening portion 20 is formed. The lightening portion 20 can reduce the occurrence of tensile stress in the rubber elastic body 14 when the initial load of the engine unit weight portion as described above is exerted. .

Furthermore, the rubber elastic body 14 has the above-described lightening portion 20.
In contrast, a portion radially opposed across the inner cylinder fitting 10,
In other words, in the eccentric direction of the inner cylinder fitting 10 and the mounting sleeve 18, the mounting sleeve 18
The pocket portion 22 is formed in a recessed shape penetrating through the wall portion and opening on the outer peripheral surface. In short, the mounting sleeve 18 has a pocket 22 provided in the rubber elastic body 14.
The opening 26 is provided with a window 26, through which the pocket 22 is opened to the outside.

Note that, here, the rubber elastic body 14 that constitutes the mount axial direction side walls 24, 24 of the pocket portion 22 is:
As is clear from FIG. 2, it is relatively thin so that it can be bulged and deformed in the mount axis direction. Further, in the rubber elastic body 14, since the generation of the tensile stress when the vibration load is input between the inner and outer cylindrical metal fittings 10 and 12 is avoided by the lightening portion 20, the portion where the compressive stress is generated. Compressive deformation in the mount radial direction when a vibration load is input is more effectively induced in the pocket portion 22 formed in the above.

Then, the outer tubular metal fitting 12 is externally inserted to the integrally vulcanized molded product including the inner tubular metal fitting 10, the rubber elastic body 14 and the mounting sleeve 18, and the outer tubular metal fitting 12 is further reduced in diameter. And the end portions in the axial direction are subjected to roll crimping, and are engaged with the peripheral end portion of the mounting sleeve 18 as shown in the drawing, thereby forming the integrally vulcanized molded product and the outer tubular metal fitting 12. Are assembled together. Then, the opening of the pocket portion 22 is fluid-tightly closed by the outer insertion of the outer cylinder fitting 12, and the fluid chamber 30 having a predetermined volume is defined therein. A thin-walled seal rubber layer 28 is integrally provided on the inner peripheral surface of the outer tubular fitting 12 over substantially the entire surface thereof.

In addition, a predetermined low-viscosity incompressible fluid is sealed in the fluid chamber 30 by assembling the outer tube fitting 12 in a predetermined fluid. As the enclosed fluid, in order to achieve the object of the present invention, in order to ensure sufficient fluidity of the fluid, one having a kinematic viscosity of 500 centistokes or less, preferably 100 centistokes or less is desirable, For example, water, ethylene glycol, propylene glycol, other alkylene glycols, low-viscosity polyalkylene glycol, low-viscosity silicone oil, or a mixed solution thereof or the like is preferably used.

And in the fluid chamber 30, the inner and outer cylinder fittings
When the vibration is input between 10 and 12, the vibration to be isolated is input there, but at that time, the elasticity of the rubber elastic body 14 on the both side walls 24, 24 in the axial direction of the mount is outward in the axial direction of the mount. Due to the deformation or the bulging deformation into the lightening portion 20, a deformation in which the inner dimension opposed to the vibration input direction in the mount radial direction is changed can be generated.

Furthermore, in the fluid chamber 30, the protruding block 32
However, it is housed and arranged. This protruding block 32 has a surface shape that substantially corresponds to the inner surface shape of the fluid chamber 30,
Also, with the fixing bolt 33 inserted through the outer tubular metal fitting 12, the outer peripheral surface thereof is fixed to and supported by the outer tubular metal fitting 12 in a state of abutting against the inner peripheral surface of the outer tubular metal fitting 12. There is. That is, the protruding block 32 allows the fluid chamber 30
In the inside, there is formed an action protrusion that protrudes from the outer tubular metal fitting 12 side toward the inner tubular metal fitting 10 side at a predetermined height in the mount radial direction, which is the vibration input direction.

The mounting portion of the fixing bolt 33 in the outer cylinder fitting 12 is a recess 35 that is recessed radially inward, and the head of the fixing bolt 33 is housed in the recess 35 and By avoiding the outward protrusion in the direction, assembling is ensured by fitting the outer tubular metal fitting into the predetermined mounting hole when mounting on the vehicle body side or the engine unit side as described above. Has been done.

Further, as shown in FIG. 3, the protrusion block 32 is housed in the fluid chamber 30 to allow the mount 16 to be attached, that is, when the supported body (engine unit) is under heavy load. Between the projecting end surface (inner peripheral surface) of the block 32 and the inner surface of the fluid chamber 30 facing the projecting end surface in the mount radial direction of the vibration input direction, a substantially constant thickness ( A fluid action region 34 as a vibration action gap is formed, which has a predetermined area and extends in a mount circumferential direction substantially perpendicular to the vibration input direction. In the fluid action area 34, the thickness t is based on the fact that the inner dimension of the fluid chamber 30 in the vibration input direction changes (increases or decreases) due to the input of vibration between the inner and outer tubular fittings 10 and 12. The change in the amount of fluid due to the change in the gap (t) in the fluid action area 34 causes the bulging deformation of the rubber elastic body 14 (deformation of the side wall portion 24, to the lightening portion 20 side). The flow of the fluid is generated there by being compensated by the bulge.

That is, an engine mount with such a structure
In the case of 16, the thickness (t) of the fluid action region 34 formed inside the protruding block 32 in the radial direction inside the fluid chamber 30 increases or decreases due to the input of vibration between the inner and outer tubular metal fittings 10 and 12. By being urged, a driving force is applied to the fluid existing therein, and thus a repeated flow of the fluid in the fluid action region 34 (mainly a lateral flow in FIG. 2) is generated, Therefore, it is possible to effectively reduce the mount dynamic spring constant by utilizing the flow action or resonance action based on the flow of the fluid.

Note that, here, the fluid action area 34 is not only between the protruding block 32 and the inner cylindrical metal fitting 10, but also on the vibration input direction facing surface of the protruding block 32 and the rubber elastic body 14 forming the wall portion of the fluid chamber 30. The rubber elastic body 14 which is formed also in the space and forms the wall portion of the fluid chamber has a certain degree of freedom of deformation at the time of vibration input by the lightening portion 20. This causes a wavy deformation to the rubber elastic body 14 at the time of vibration input, and the fluid action area 34
The repetitive flow of the fluid in (1) is extremely advantageously induced, and therefore, the high dynamic spring due to the resonance of the rubber elastic body 14 or the like can be more effectively reduced or prevented.

By the way, the frequency region in which the effect of reducing the mount dynamic spring constant can be exhibited is the fluid action depending on the elastic modulus of the rubber elastic body 14 (mount spring constant), the elasticity of the side wall portion 24 thereof, the viscosity of the enclosed fluid, or the like. It is possible to set a desired frequency range by tuning the resonance frequency of the fluid that is made to flow in the fluid action region 34 by adjusting the thickness t of the region 34 and its size (width). Is possible,
Particularly, in such an engine mount 16, the resonance frequency of such fluid can be tuned to a high frequency region with advantage.

In such an engine mount, as described above, the gap (thickness) of the fluid action region 34 is set so that the desired low dynamic spring effect based on the fluid flow action or the resonance action can be sufficiently exerted. And area will be set,
Specific values thereof are set in a normal engine mount so that the thickness: t of the fluid action region 34 in FIG. 3 is 1 to 16 mm, preferably 2 to 10 mm, and The area of the action area 34, that is, the area where the radially inner peripheral surface of the protruding block 32 and the inner surface of the fluid chamber 30 face each other is set to 400 mm ² or more, preferably 800 mm ² or more.

Therefore, the engine mount 16 having the above-described structure is used.
In this case, based on the flow action or resonance action of the fluid existing in the fluid action region 34 inside the protruding block 32 in the fluid chamber 30 in which the gap (t) is increased or decreased by the vibration input, The low dynamic spring can be advantageously achieved even in a high frequency range, and as a result, as described above, the mount body rubber (rubber elastic body) is
The rigidification of the mount due to the resonance phenomenon of 14) at the time of vibration input in the high frequency region can be effectively eliminated.

Therefore, by using the engine mount 16, soft spring characteristics can be advantageously exerted against input vibration over a wide frequency range of middle to high frequencies, and the vibration transmissibility can be reduced. As a result, the quietness in the vehicle and the improvement of the riding comfort can be achieved very effectively.

Incidentally, the experimental results obtained by measuring the phase angle δ and the absolute spring constant K ^* with respect to the vibration frequency of the engine mount 16 having the structure according to the present embodiment are shown in FIGS. 4 (a) and 4 (b), respectively. ). In addition, in FIG. 4, the result of the engine mount made of a single rubber having a structure in which the fluid is not enclosed in the fluid chamber (30) and the protruding block (32) is not arranged is shown as Comparative Example 1. Further, the result of the engine mount having a structure in which only the fluid is enclosed without arranging the protruding block (32) in the fluid chamber (30) shows, as Comparative Example 2, the inside of the fluid chamber (30) in which the fluid is further enclosed. In Comparative Example 3, the results of an engine mount having a structure in which the protruding block (32) is arranged in a floating state without being fixed are also shown.

By the way, in such an experiment, while using tap water as the enclosed fluid, a vibration of ± 10 G was applied between the inner and outer cylindrical metal fittings 10 and 12 with an initial load of 105 kgf applied in the eccentric direction. By adding, each mount was evaluated.

As is clear from FIG. 4, in the engine mount of this embodiment, the high dynamic spring in the high frequency region due to the resonance phenomenon of the rubber of the mount body can be extremely advantageously eliminated. The lowering of the dynamic spring in the high frequency region and the accompanying reduction of the vibration transmissibility can be satisfactorily achieved. Furthermore, the projecting block (32) is placed in a floating state in the fluid chamber (30). By comparison, it is recognized that a better low dynamic spring effect can be exhibited. In this way, the engine mount 16 of the structure of the present embodiment can exert a low dynamic spring effect superior to that of the structure in which the protruding block 32 is not fixed is that the protruding block 32 is prevented from being tilted or shaken during vibration input. It is considered that the driving force is applied to the fluid existing in the fluid action region 34 (piston effect) more effectively.

Further, in such an engine mount 16, since it is only necessary to consider the protruding block 32 in the fluid chamber 30 when assembling the engine mount 16, it is possible to achieve a desired high frequency range without adding a complicated mechanism. It also has an advantage that the improvement of the vibration damping property can be advantageously achieved with a simple structure.

Next, FIGS. 5 and 6 show an engine mount 40 as another embodiment of the present invention. In addition, in the engine mount 40 of the present embodiment, members having the same structure as those of the first embodiment are designated by the same reference numerals, and detailed description thereof will be omitted. I will.

That is, in the engine mount 40 according to the present embodiment, the rubber elastic body 14 has a side opposed to the pocket portion 22 in the mount radial direction with the inner cylinder fitting 10 interposed therebetween,
In other words, on the side where the separation distance between the inner cylinder fitting 10 and the mounting sleeve 18 in the eccentric direction is small, it is located outside the lightening portion 20, penetrates the wall of the mounting sleeve 18, and opens on the outer peripheral surface. A recess 42 having a predetermined volume is provided. In short, in the mounting sleeve 18, at the site where the recess 42 is formed,
A window 44 through which the recess 42 is opened is provided, and the window 44 and the window 26 provided at a position corresponding to the pocket 22 are provided at the center in the axial direction. Are formed in the circumferential direction so as to extend in the circumferential direction so as to extend between them.

Then, the outer tubular metal fitting 12 is externally inserted into the mounting sleeve 18, and as in the previous example, by fluid-tightly assembling, the opening of the recess 42 is covered, and the inside thereof has the predetermined length as described above. Fluid chamber containing low viscosity incompressible fluid
48 are formed, and the openings of the circumferential grooves 46, 46 are covered, and orifice passages 50, 50 for interconnecting the fluid chamber 48 with the fluid chamber 30 are formed. It is.

Further, here, in the engine mount 40 according to the present embodiment, the axially opposite side wall portions 24, 24 of the rubber elastic body 14 constituting the wall portion of the fluid chamber 30 have their materials, wall thicknesses, etc. adjusted. Accordingly, at least when a vibration with a predetermined large amplitude is input, it is formed with a certain degree of rigidity so as not to absorb the internal pressure change in the fluid chamber 30. However, when a low-frequency, large-amplitude vibration is input, it is configured as a pressure receiving chamber that causes internal pressure fluctuations.

On the other hand, in the fluid chamber 48, the rubber elastic body 14 constituting the bottom wall portion is thinned by the lightening portion 20 to form a flexible film 52 that is easily elastically deformed. Accordingly, the fluid chamber 48 is configured as an equilibrium chamber in which a change in internal pressure at the time of vibration input to the mount is avoided due to a volume change due to the elastic deformation of the flexible film 52.

Then, in the engine mount 40 of the present embodiment having such a structure, when vibration is input between the inner and outer cylinder fittings 10 and 12, based on the internal pressure fluctuation in the fluid chamber 30,
The flow of fluid through the orifice passages 50, 50 is generated between the fluid chamber 48 and the resonance frequency of the fluid flowed through the orifice passage 50, and the cross-sectional area and length of the fluid are adjusted. Then, by performing appropriate tuning, a predetermined vibration damping effect against the input vibration in the predetermined frequency range can be exhibited by the flow action or resonance action of the fluid.

In particular, such an orifice passage 50 is tuned so that it can exhibit excellent damping performance against input vibration in a low frequency range of about 10 Hz corresponding to engine shake, bounce, etc. The anti-vibration performance of the mount in the low frequency range is improved.

And in such an engine mount 40,
At the time of vibration input in the high frequency range, there is a problem in that the mount has a high dynamic spring due to the orifice passage 50 being in a closed state, but the mount high dynamic spring is formed in the fluid chamber 30. This can be effectively eliminated by the effect of reducing the dynamic spring characteristic as described above, which is based on the flow action or resonance action of the fluid in the fluid action region 34.

Therefore, in the engine mount 40 of the present embodiment, high damping performance against input vibration in the low frequency range is formed in the fluid chamber 30 based on the flow action or resonance action of the fluid through the orifice passage 50. Based on the fluid flow action or resonance action of the fluid in the fluid action region 34, the effect of reducing the vibration transmissibility with respect to the input vibration over a wide frequency range of medium to high frequencies can be advantageously exhibited together. is there.

Further, FIG. 7 shows another embodiment of an engine mount for an FF type automobile having a structure according to the present invention.

That is, the engine mount 56 in this embodiment is
As compared with the engine mount 40 in the second embodiment, a fixing structure using rivets 58 is shown as another specific example of the fixing structure of the protruding block 32 to the outer tubular metal member 12.

In addition, in the present embodiment, except for the fixing structure of the protruding block 32, the structure is the same as that of the second embodiment. Therefore, in FIG. 7, the structure is the same as that of the second embodiment. By giving the same reference numerals to the respective members, detailed description thereof will be omitted.

Although some embodiments of the fluid-filled cylindrical mount device according to the present invention have been described above in detail, these are literal examples, and the present invention is construed as being limited to such specific examples. Not a thing.

For example, the forming material of the protruding block 32 is not limited in any way, and the shape thereof is appropriately set to various shapes such as a rectangular block shape and a columnar shape according to the shape of the fluid chamber 30. There is also a hollow shape.

Further, in the mounting device in the above-mentioned embodiment, the operating projections are both configured by separate projecting blocks, but, for example, by projecting the outer tubular metal fitting 12 into the fluid chamber 30, It is also possible to form a working projection.

Further, the lightening portion 20 formed in the rubber elastic body 14 at a position opposed to the fluid chamber 30 in the radial direction with the inner tubular metal member 10 interposed therebetween improves the durability of the mount, and Fluid action area 34 or orifice passage in
It is effective in securing the amount of fluid flowing through 50, but is not an essential requirement in the present invention.

In addition, it goes without saying that the present invention can be well applied to a mounting device in a device other than a suspension bush or an automobile, in addition to the engine mount as illustrated.

In addition, although not enumerated one by one, the present invention can be embodied in an aspect in 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 any of them is included in the scope of the present invention unless departing from the scope of the present invention.

(Effect of the Invention) As is apparent from the above description, in the fluid-filled cylindrical mount device having the structure according to the present invention, the vibration action gap formed in the fluid chamber, which is generated when the vibration is input. Based on the flow of the fluid in, the mount rigidity against the input vibration in the high frequency range can be effectively avoided, and the low dynamic spring can be achieved, whereby a wide frequency range of medium to high frequencies can be achieved. Therefore, the cylindrical mount device capable of exhibiting excellent vibration damping characteristics can be advantageously realized.

Further, in particular, in such a fluid-filled tubular mount, the vibration action gap is caused not only between the action protrusion and the inner tubular metal member but also between the action protrusion and the rubber elastic body forming the wall of the fluid chamber. The rubber elastic body, which is also formed between the facing surfaces in the input direction and which forms the wall of the fluid chamber, can be deformed relatively easily by the thinned-out portion. The corrugated deformation is generated in the body, and the repetitive flow of the fluid in the vibration action gap is extremely efficiently induced, whereby the low dynamic spring effect in the high frequency region as described above is more advantageous. Can be exerted to.

Further, in such a fluid-filled tubular mount, a housing member having a predetermined shape is fixed to and supported by an outer tubular metal member, and is placed in a fluid chamber, so that the action projection, and thus the vibration action. The formation of gaps can be tested easily and advantageously.

Further, in such a fluid-filled tubular mount, the fluid chamber is configured as a pressure receiving chamber, and the pressure receiving chamber is provided with an equilibrium chamber communicating with the orifice passage. As described above, while maintaining low dynamic spring characteristics against input vibrations in the middle to high frequency range, based on the fluid flow through the orifice passage, improvement of high damping characteristics with respect to input vibrations in the low frequency range is also achieved. This can be advantageously achieved.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a specific example in which the present invention is applied to an automobile engine mount, and FIG. 2 is a cross-sectional view taken along the line II-II in FIG. FIG. 3 is a transverse sectional view showing a mounted state of the engine mount shown in FIG. Further, FIG. 4 is a graph showing, together with a comparative example, experimental data on the vibration isolation performance of the engine mount having the structure shown in FIGS. 1 and 2, and FIG. Angle: The frequency characteristic of δ,
(B) shows the frequency characteristics of the absolute spring constant: K ^* , respectively. 5 is a cross-sectional view showing another specific example of the present invention applied to an automobile engine mount, and FIG. 6 is a VI-VI cross-sectional view in FIG. Furthermore, FIG. 7 is a cross-sectional view showing still another embodiment of the engine mount for an automobile having the structure according to the present invention. 10: Inner tube fitting, 12: Outer tube fitting 14: Rubber elastic body 16, 40, 56: Engine mount 24: Axial side wall parts (thin wall part) 30: Fluid chamber (pressure receiving chamber), 32: Projection block 34: Fluid action area (vibration action part) 48: Fluid chamber (equilibrium chamber), 50: Orifice passage 52: Flexible membrane

Claims (3)

[Claims] 1. A tubular mounting device in which an inner tubular metal member and an outer tubular metal member, which are arranged concentrically or eccentrically with each other, are elastically connected by a rubber elastic body interposed therebetween. By covering the opening of the pocket formed in the rubber elastic body with the outer tubular metal fitting, a low-viscosity non-compressible material is provided between the inner tubular metal fitting and the outer tubular metal fitting in the radial vibration input direction. Forming at least one fluid chamber in which a vibration-proof vibration is input, in which a permeable fluid is sealed, and the inner tubular metal member and the outer tubular member are provided on the side opposite to the fluid chamber across the inner tubular metal member. Providing a lightening portion extending axially through the metal fitting to make the bottom walls on both sides in the circumferential direction of the pocket portion forming the fluid chamber elastically deformable elastic wall portions, while the fluid chamber The side walls on both sides in the axial direction made of the rubber elastic body of The inner wall of the fluid chamber has a surface shape substantially corresponding to the inner surface of the pocket portion forming the fluid chamber. The fluid chamber formed by the action protrusion and the rubber elastic body is fixedly provided on the outer tubular metal member, and has an action protrusion that protrudes toward the side and is located away from the inner surface of the pocket. A fluid-filled cylindrical mount device, characterized in that a vibration action gap that spreads with a substantially constant gap in a mounted state is formed between the faces of the walls of the wall face facing the vibration input direction. 2. The operating projection projects from the outer tubular metal fitting side toward the inner tubular metal fitting side by fixing an accommodating member accommodated and arranged in the fluid chamber to the outer tubular metal fitting. The fluid-filled tubular mount device according to claim 1, wherein the fluid-filled cylindrical mount device is formed. 3. The fluid chamber is formed as a pressure receiving chamber in which an internal pressure fluctuation is caused by elastic deformation of the rubber elastic body when a vibration is input between the inner and outer cylindrical metal fittings, and the inner cylindrical metal fitting and the outer cylindrical metal fitting. An equilibrium chamber, in which the predetermined incompressible fluid is sealed between the tubular metal fitting and at least a part of which is defined by a flexible film and in which vibration input is avoided, is defined as the pressure receiving chamber. 3. The fluid-filled cylindrical mount device according to claim 1, wherein at least one is independently formed, and an orifice passage that connects the pressure receiving chamber and the equilibrium chamber to each other is provided.