JPH01320344A - Fluid sealed cylinder type mount device - Google Patents

Abstract

PURPOSE:To contrive the improvement of vibro-isolating performance over a wide frequency region by forming a vibration acting clearance of predetermined size between an action protruding part protruding in a vibration input direction and an internal surface of a fluid chamber. CONSTITUTION:At least one fluid chamber 30 is formed sealing non-compressive fluid of low viscosity between an inner cylinder metal fixture 10 and an outer cylinder metal fixture 12 in a vibration input direction in the diametric direction and inputting a vibration to be isolated. A fluid action region 34, serving as the vibration action clearance having a predetermined thickness further spreading with a predetermined area in a mount peripheral direction almost at a right angle with the vibration input direction, is formed between a protruding end surface of a protruding block 32 and an internal surface of the fluid chamber 30 opposed facing to a mount diametric direction in the vibration input direction.

Description

Detailed Description of the Invention (Technical Field) The present invention relates to a fluid-filled cylindrical mount device that suppresses vibration transmission based on the flow of a fluid sealed inside, and particularly relates to a fluid-filled cylindrical mount device that suppresses vibration transmission based on the flow of a fluid sealed inside. Improved anti-vibration properties
The present invention relates to a fluid-filled cylindrical mount device that can be advantageously achieved with a simple structure.

(Background Art) Conventionally, vibration damping devices have been interposed between two members constituting a vibration transmission system, such as suspension bushes and engine mounts in automobiles, to connect these two members in a vibration-proof manner.
Alternatively, as a type of mount device that provides vibration-proof support for one member with respect to another member, an inner cylindrical metal fitting and an outer cylindrical metal fitting that are arranged concentrically or eccentrically with respect to each other, and a rubber interposed between them. A cylindrical mount device that is elastically connected using an elastic body has been used. In this cylindrical mount device, a predetermined mounting shaft is inserted and fixed into the inner cylindrical fitting, while a support member to which the mounting shaft is to be connected is attached to the outer cylindrical fitting. A mount device is interposed between the mounting shaft and the support member, and the two members are connected in a vibration-proof manner based on the elastic deformation of the rubber elastic body.

However, in the case of a cylindrical mount device with such a structure, since a single piece of rubber is used as the vibration isolator, when vibrations in a high frequency range are input, the mount may be damaged due to resonance of the rubber elastic body. This had the inherent problem of causing rigidity.

For example, such a cylindrical mount device is also used as an engine mount for front-wheel drive cars, but in conventional engine mounts, the resonance of the rubber elastic body is 30
Because it appears in the frequency range of about 0Hz to 700Hz, it has been difficult to sufficiently prevent muffled sounds such as engine transmitted sound and high-frequency vibrations.
In particular, with the recent demand for higher levels of quietness and ride comfort for automobiles, there is a strong desire to improve vibration isolation characteristics in such a high frequency range.

(Problem to be solved) Here, the present invention has been made against the background of the above-mentioned circumstances, and the problem to be solved is:
A fluid-filled cylindrical mount device that can effectively prevent the mount from becoming rigid when vibration is input in a high frequency range, and can improve vibration isolation performance over a wide frequency range with a simple structure. Our goal is to provide the following.

(Solution Means) In order to solve this problem, the present invention includes:
In a cylindrical mount device in which an inner cylindrical metal fitting and an outer cylindrical metal fitting arranged concentrically or eccentrically with each other are elastically connected by a rubber elastic body interposed between them, radial vibration can be avoided. At least one fluid chamber is formed between the inner cylindrical metal fitting and the outer cylindrical metal fitting in the input direction, and the fluid chamber is filled with a low-viscosity incompressible fluid and into which vibrations to be damped are input. A predetermined portion of the peripheral wall made of the rubber elastic body, which defines at least a portion of the chamber, is formed into a thin wall portion that can be bulged and deformed, while the inner cylindrical fitting and the outer tube are provided inside the fluid chamber. A working protrusion projecting at a predetermined height in the direction of the vibration force is fixedly provided from one side of the cylindrical metal fitting toward the other side, and vibration input between the working protrusion and the inner surface of the fluid chamber is provided. Its feature is that a vibration action gap of a predetermined size is formed between the directionally opposing surfaces.

Further, in the present invention, the working protrusion fixes the housing member housed in the fluid chamber to the outer cylindrical metal fitting, thereby moving the housing member from the outer cylindrical metal side to the inner cylindrical metal fitting side. Another feature of the device is the fluid-filled cylindrical mount device that is formed to protrude toward the vehicle.

Furthermore, in the present invention, in such a fluid-filled cylindrical mount device, when vibration is input to the fluid chamber between the inner and outer cylindrical fittings, internal pressure fluctuations are caused by elastic deformation of the rubber elastic body. The predetermined incompressible fluid is sealed between the inner cylindrical metal fitting and the outer cylindrical metal fitting, and at least a portion thereof is defined by a flexible membrane. At least one equilibrium chamber in which vibration input is avoided is formed independently of the pressure receiving chamber, and an orifice passage is provided to communicate the pressure receiving chamber and the equilibrium chamber with each other. , is its characteristic.

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

First, FIGS. 1 and 2 show, as an embodiment of the present invention, an example in which the present invention is applied to an engine mount for a front-wheel drive vehicle.

In this figure, reference numeral 10 denotes an inner cylindrical metal fitting, and an outer cylindrical metal fitting 12 is arranged on the outside of the inner cylindrical metal fitting 10, eccentrically in one direction in the radial direction (in the vertical direction in FIG. 1) and spaced apart by a predetermined distance. Furthermore, a substantially cylindrical rubber elastic body 14 is interposed between the inner cylindrical metal fitting 10 and the outer cylindrical metal fitting 12, and the rubber elastic body 14 allows the inner and outer cylindrical metal fittings 10, 12 to The engine mount 1 in this embodiment is integrated and integrated.
6, the mounting iron provided on the vehicle body side is inserted into and fixed to the inner cylinder metal fitting 10, while the outer cylinder metal fitting 12 is fixed in the mounting hole of the bracket provided on the engine unit side. , are interposed between the engine unit side and the vehicle body side, so that the engine unit is supported against the vehicle body in a vibration-proof manner.

In addition, in such a mounted state, the weight of the engine unit causes the inner and outer cylindrical metal fittings 1O112 to be positioned approximately concentrically (see FIG. 3), and both these metal fittings 10
．． The main vibration will be input in the eccentric direction of 12.

Here, the rubber elastic body 14 has an inner cylindrical fitting 10 on its inner circumferential surface, and a thin cylindrical mounting sleeve 18 positioned eccentrically by a predetermined amount with respect to the inner cylindrical fitting 10 on its outer circumferential surface. , are each formed as an integrally vulcanized molded product that is vulcanized and bonded.

Further, the rubber elastic body 14 includes an inner cylinder fitting 10 and a mounting sleeve 1 which are in the radial direction of the mount in the vibration input direction.
A hollowed-out portion 20 that penetrates between the inner cylinder fitting 10 and the mounting sleeve 18 in the axial direction and extends approximately half a circumference in the circumferential direction on the side where the separation distance is smaller in the eccentric direction with respect to the inner cylinder fitting 10 and the mounting sleeve 18.
is formed. And, by this lightening part 20,
This makes it possible to reduce as much as possible the generation of tensile stress in the rubber elastic body 14 when an initial load such as the weight of the engine unit as described above is applied.

Furthermore, the rubber elastic body 14 has the above-mentioned hollow portion 2.
With respect to 0, the wall portion of the mounting sleeve 18 is located at a portion facing radially across the inner cylinder fitting 10, in other words, on the side where the separation distance between the inner cylinder fitting 10 and the mounting sleeve 18 is larger in the eccentric direction. A pocket portion 22 is formed with a recess-like shape that penetrates through and opens on the outer peripheral surface. In short, the mounting sleeve 18 is provided with a window 26 at the opening of the pocket 22 provided in the rubber elastic body 14, and the pocket 22 is opened through the window 26.
However, it is opened to the outside.

Here, as is clear from FIG. 2, the rubber elastic body 14 portions constituting both side walls 24.24 in the mount axis direction of the pocket portion 22 are made relatively thin, and the mount axis direction The bulging deformation is allowed. In addition, in the rubber elastic body 14, since the hollowed out portion 20 prevents the generation of tensile stress when a vibration load is input between the inner and outer cylindrical fittings 10 and 12, compressive stress is generated at the location where compressive stress is generated. Compressive deformation in the radial direction of the mount is more advantageously induced in the square pocket portion 22 when a vibration load is input.

Then, the outer cylindrical metal fitting 12 is fitted onto the integrally vulcanized product made of the inner cylindrical metal fitting 10, the rubber elastic body 14, and the mounting sleeve 18, and the outer cylindrical metal fitting 12 is further subjected to diameter reduction processing. At the same time, both ends in the axial direction are roll caulked and engaged with the peripheral end of the mounting sleeve 18 as shown in the figure, thereby connecting the integrally vulcanized molded product and the outer cylindrical fitting 12. are integrally assembled. By inserting the outer cylindrical fitting 12, the opening of the pocket portion 22 is fluid-tightly closed, and a fluid chamber 30 with a predetermined volume is defined therein. A thin sealing rubber layer 28 is integrally provided on the inner circumferential surface of the outer cylindrical fitting 12 over substantially the entire surface thereof.

Furthermore, a predetermined low-viscosity incompressible fluid is sealed in the fluid chamber 30 by assembling the outer cylindrical fitting 12 in a predetermined fluid. In order to achieve the object of the present invention, the enclosed fluid preferably has a kinematic viscosity of 500 centistokes or less, preferably 100 centistokes or less, such as , water, ethylene glycol, propylene glycol, other alkylene glycols, low viscosity polyalkylene glycols,
Low viscosity silicone oil or a mixture thereof is preferably used.

In the fluid chamber 30, when vibrations are input between the inner and outer cylindrical fittings 10 and 12, vibrations that should be damped are input there.
Due to the elastic deformation of the axial side wall portions 24.24 outward in the mount axial direction or the bulging deformation into the hollowed out portion 20, the inner dimension facing the mount radial direction, which is the vibration input direction, changes. Such deformations are now possible.

Furthermore, within the fluid chamber 30, a protruding block 32 is provided.
is accommodated and arranged. This protruding block 32 is
It has a surface shape that approximately corresponds to the inner surface shape of the fluid chamber 30, and its outer circumferential surface abuts the inner circumferential surface of the outer tube fitting 12 by the fixing bolt 33 inserted through the outer tube fitting 12. In this state, it is fixed to and supported by the outer cylinder metal fitting 12. That is, the protruding block 32 forms an operating protrusion that protrudes within the fluid chamber 30 from the outer cylindrical fitting 12 side toward the inner cylindrical fitting 10 side at a predetermined height in the mount radial direction, which is the vibration input direction. There is.

The mounting portion of the fixing bolt 33 in the outer cylinder fitting 12 is a recess 35 that is recessed inward in the radial direction, and the head of the fixing bolt 33 is accommodated in the recess 35, and the diametrically By avoiding outward protrusion,
As described above, when the outer cylindrical metal fitting is installed on the vehicle body side or the engine unit side, assemblability is ensured by fitting it into a predetermined mounting hole.

Also, by housing the protruding block 32 in the fluid chamber 30, the mounting (mount) 1 as shown in FIG.
6, that is, under the weight load state of the supported body (engine unit), the protruding end surface (inner peripheral surface) of the protruding block 32 faces the protruding end surface in the radial direction of the mount in the vibration input direction. A fluid action area 34 is formed between the fluid chamber 30 and the inner surface of the fluid chamber 30 as a vibration action gap, which has a predetermined thickness (gap) and extends over a predetermined area in the mount circumferential direction substantially perpendicular to the vibration input direction. -ing In addition, in this fluid action region 34, the thickness L is determined based on the fact that the inner dimensions of the fluid chamber 30 in the direction of vibration input change (increase or decrease) due to the input of vibration between the inner and outer cylindrical fittings 10 and 12. will be forced to change,
Then, the change in the amount of fluid due to the change in the gap (L) in the fluid action region 34 is compensated for by the bulging deformation of the rubber elastic body 14 (deformation of the side wall portion 24, bulging toward the hollowed out portion 20 side, etc.). As a result, fluid flow is generated there.

That is, the engine mount 1 having such a structure
6, the thickness (1
) is increased or decreased, a driving force is applied to the fluid present therein, thereby causing a repeated flow of the fluid in the fluid action area 34 (mainly a flow in the left-right direction in FIG. 2). Therefore, by utilizing the flow effect or resonance effect based on the flow of the fluid, the mount dynamic spring constant can be effectively reduced.

By the way, the frequency range in which this effect of reducing the mount dynamic spring constant can be exhibited depends on the elastic modulus of the rubber elastic body 14 (mount spring constant), the elasticity of the side wall portion 24, the viscosity of the enclosed fluid, etc. Thickness of the region 34: Adjust the size (width) of the mist to make the fluid action region 34
By tuning the resonant frequency of the fluid flowing through the engine mount 16, the resonant frequency of the fluid can be set to a desired frequency range. It is possible to tune it to your advantage.

In addition, in such an engine mount, the gap (thickness) of the fluid action area 34 is adjusted so that the desired low motion spring effect based on the fluid flow action or resonance action as described above can be sufficiently exhibited. Although the area and area will be set,
The specific values of these values are as shown in FIG. 3 for a normal engine mount, where the thickness of the fluid action area 34: t is 1 to 16 mm.
, preferably 3 to 10 mm, and the area of the fluid action area 34, that is, the protruding block 3
The opposing area between the radial inner circumferential surface of No. 2 and the inner surface of the fluid chamber 30 is set to be 400 mm" or more, preferably 1000 mm" or more.

Therefore, the engine mount (16) having the structure as described above is
In this case, the mount characteristics are reduced based on the flow effect or resonance effect of the fluid existing in the fluid action area 34 inside the protrusion block 32 in the fluid chamber 30, where the gap (1) is increased or decreased by vibration input. Dynamic springs can be advantageously achieved even in the high frequency range,
As a result, it is possible to effectively eliminate the rigidity of the mount caused by the resonance phenomenon of the mount body rubber (rubber elastic body 14) when vibration is input in a high frequency range, as described above.

Therefore, by using such an engine mount 16, soft spring characteristics can be advantageously exhibited against input vibrations over a wide frequency range from medium to high frequencies, and the vibration transmission rate can be reduced. Therefore, the quietness inside the vehicle and the improvement of ride comfort can be extremely effectively achieved.

Incidentally, the experimental results of measuring the phase angle δ and the absolute spring constant 9 with respect to the vibration frequency using the engine mount 16 having the structure according to this embodiment are as follows.
This is shown in FIGS. 4(a) and (b). In addition, in FIG. 4, the results for an engine mount made of only rubber and having a structure in which no fluid is sealed in the fluid chamber (30) and no protruding block (32) are arranged are shown as Comparative Example 1. In addition, a protruding block (32) is provided in the fluid chamber (30).
) The result of an engine mount having a structure in which only fluid is sealed is shown as Comparative Example 2, in which a protruding block (3
Comparative Example 3 shows the results for an engine mount with a structure in which 2) is placed in a floating state without being fixed.
They are shown together.

Incidentally, in such an experiment, while tap water was used as the enclosed fluid, vibration of ±10G was applied to the space between the inner and outer cylindrical fittings 10 and 12 with an initial load of 105 kgf applied in the eccentric direction thereof. Each mount was evaluated based on this.

As is clear from FIG. 4, in the engine mount of this embodiment, the high dynamic spring in the high frequency range due to the resonance phenomenon of the mount body rubber can be extremely advantageously eliminated, and Furthermore, it is possible to satisfactorily achieve a low dynamic spring in a high frequency region and a corresponding reduction in vibration transmissibility.
It is recognized that a more excellent low dynamic spring effect can be exhibited even when compared with the case where 32) is placed in a floating state. The reason why the engine mount 16 having the structure of this embodiment is able to achieve a low motion spring effect superior to that of a structure in which the protruding block 32 is not fixed is that the protruding block 32 is prevented from tilting or wobbling when vibration is input. Being done,
This is thought to be because the application of driving force (piston effect) to the fluid existing in the fluid action area 34 is more effectively achieved.

In addition, with such an engine mount 16, since it is only necessary to place the protruding block 32 in the fluid chamber 30 when assembling the engine mount 16, it is possible to achieve the desired high frequency range without adding a complicated mechanism. It also has the advantage that improved vibration damping properties 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 the engine mount 40 of this embodiment, members having the same structure as those of the first embodiment are designated by the same reference numerals, and a detailed description thereof will be omitted. shall be.

That is, in the engine mount 40 in this embodiment, the pocket portion 22 in the rubber elastic body 14 is
The hollowed out portion 2 is located on the side opposite to the inner cylinder fitting 10 in the radial direction of the mount, in other words, on the side where the distance between the inner cylinder fitting 10 and the mounting sleeve in the eccentric direction is smaller.
A recess 42 having a predetermined volume is provided at the outside of the mounting sleeve 18, penetrating the wall of the mounting sleeve 18 and opening to the outer peripheral surface. In short, the mounting sleeve 18 has such a recess 42
A window portion 44 through which the recess 42 is opened is provided at the forming portion of the window portion 44 and the pocket portion 2 at the central portion in the axial direction.
A circumferential groove 46.2 that opens on the outer circumferential surface and extends in the circumferential direction across the window portion 26 provided at a position corresponding to 46.2.
46 is formed.

Then, the outer cylinder metal fitting 12 is attached to the mounting sleeve 18.
is inserted and assembled in a fluid-tight manner as in the previous example, thereby covering the opening of the recess 42 and forming a fluid chamber 48 in which a predetermined low-viscosity incompressible fluid as described above is sealed. is formed, and the circumferential groove 46
．． The opening of 46 is covered to form an orifice passage 50.50 which interconnects the fluid chamber 48 with the fluid chamber 30.

In addition, in the engine mount 40 of this embodiment, the axial side wall portions 24, 24 of the rubber elastic body 14 constituting the wall portion of the fluid chamber 30 are adjusted in material, wall thickness, etc. By doing so, the fluid chamber 30 is formed with a certain degree of rigidity so as not to absorb changes in the internal pressure within the fluid chamber 30 at least when vibrations of a predetermined large amplitude are input.
0 is configured as a pressure receiving chamber in which internal pressure fluctuations are caused when low frequency, large amplitude vibrations are input.

On the other hand, in the fluid chamber 48, the rubber elastic body 14 constituting the bottom wall thereof is thinned by the hollowed out portion 20, so that the flexible membrane 52 is easily elastically deformed. Therefore, the fluid chamber 48 is configured as an equilibrium chamber in which internal pressure fluctuations when vibrations are input to the mount are avoided by volume changes based on the elastic deformation of the flexible membrane 52.

In the engine mount 40 of this embodiment having such a structure, when vibration is input between the inner and outer cylindrical fittings 10 and 12, the fluid chamber 48 between the orifice passage 50.50
Therefore, the resonant frequency of the fluid flowing through the orifice passage 50 is tuned as appropriate by adjusting its cross-sectional area, length, etc. Through the flow action or resonance action, a predetermined vibration damping effect against input vibration in a predetermined frequency range can be exhibited.

In particular, the orifice passage 50 is tuned so that it can exhibit excellent damping performance against input vibrations in the low frequency range of around 10 Hz, which corresponds to engine shake, bounce, etc. This will improve the vibration isolation performance of the mount in the low frequency range.

And, in such an engine mount 40,
When inputting vibrations in a high frequency range, the formation of a linear motion spring in the mount due to the blockage of the orifice passage 50 poses a problem. This problem can be effectively eliminated by the effect of reducing the dynamic spring characteristics as described above, which is based on the flow effect or resonance effect of the fluid in the fluid action region 34.

Therefore, in the engine mount 40 of this embodiment, high damping performance against input vibrations in the low frequency range is achieved based on the flow action or resonance action of the fluid through the orifice passage 50. Based on the flow action or resonance action of the fluid in the fluid action region 34, the vibration transmissibility reduction effect for input vibration over a wide frequency range from medium to high frequencies can be advantageously exhibited. be.

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
Compared to the engine mount 40 in the second embodiment, a fixing structure using rivets 58 is shown as another example of a fixing structure of the protruding block 32 to the outer cylinder metal fitting 12.

Note that this embodiment has the same structure as the second embodiment except for the fixing structure of the protruding block 32, so in FIG. By assigning the same reference numerals to the members, detailed explanation thereof will be omitted.

Although several embodiments of the fluid-filled cylindrical mount device according to the present invention have been described in detail above, these are literal illustrations, and the present invention is to be construed as being limited only to such specific examples. It's not a thing.

For example, the material for forming the protruding block 32 is not limited to the same, and its shape may be appropriately set to various shapes such as a rectangular block shape or a cylindrical shape depending on the shape of the fluid chamber 30, etc. Furthermore, it is also possible to form it in a hollow shape.

Furthermore, in the mount device in the embodiment described above, all of the working protrusions were constituted by separate protruding blocks. It is also possible to form working projections.

Furthermore, the hollowed out portion 20 formed in the rubber elastic body 14 at a position radially opposite to the fluid chamber 30 across the inner cylinder fitting IO improves the durability of the mount, and also improves the durability of the mount. Although this is effective in securing the amount of fluid flowing through the fluid action region 34 or orifice passage 50 in the present invention, it is not an essential requirement in the present invention.

Furthermore, in each of the above embodiments, the working protrusion forming the vibration action gap extends radially inward in the fluid chamber 30 from the outer cylinder fitting 12 side toward the inner cylinder fitting IO side. However, on the contrary, such a working protrusion,
By fixing and supporting the inner cylinder fitting 10, the projecting end surface of the operating protrusion and the fluid It is also possible to form a vibration gap with the inner surface of the chamber 30.

In addition, the present invention provides an engine mount as illustrated, as well as an engine mount.
Of course, the present invention can also be effectively applied to suspension bushings and mounting devices for devices other than automobiles.

In addition, although not listed, the present invention can be implemented in embodiments with various changes, modifications, improvements, etc. added based on the knowledge of those skilled in the art, and such embodiments may be incorporated into the present invention. It goes without saying that any of these are included within the scope of the present invention as long as they do not deviate from the spirit.

(Effects of the Invention) As is clear from the above description, in the fluid-filled cylindrical mount device structured according to the present invention, the vibration action gap formed in the fluid chamber is generated when vibration is input. Based on the fluid flow in the input vibrations in the high frequency range, marant stiffness can be effectively avoided and a low dynamic spring can be achieved, thereby allowing the input vibration to be applied over a wide frequency range from medium to high frequencies. A cylindrical mount device that can exhibit excellent vibration damping properties can be advantageously realized.

In addition, in such a fluid-filled cylindrical mount, a housing member having a predetermined shape is fixed and supported by the outer cylindrical metal fitting and placed in the fluid chamber, so that the acting protrusion and, by extension, the vibration effect The formation of the gap can be done easily and advantageously.

Furthermore, in such a fluid-filled cylindrical mount, the fluid chamber is configured as a pressure receiving chamber, and an equilibrium chamber is provided which is communicated with the pressure receiving chamber through an orifice passage. While ensuring low dynamic spring characteristics against human vibrations in the medium to high frequency range, it is also advantageous to improve high damping characteristics against input vibrations in the low frequency range based on the fluid flow through the orifice passage. It can be achieved.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view showing a specific example of an automobile engine mount to which the present invention is applied, and FIG. 2 is a cross-sectional view taken along the line -■ in FIG. Moreover, FIG. 3 is a cross-sectional view showing the mounted state of the engine mount shown in FIG. 1. Furthermore, Figure 4 shows that
2 is a graph showing experimental data on vibration isolation performance of engine mounts structured as shown in FIGS. 1 and 2 together with comparative examples, in which (a) shows phase angle:
(b) shows the frequency characteristic of δ, and (b) shows the frequency characteristic of the absolute spring constant 2 to 0. Also, Figure 5 shows
FIG. 6 is a cross-sectional view showing another specific example of the invention applied to an automobile engine mount, and FIG. 6 is a cross-sectional view taken along the line Vl--Vl in FIG. 5. Furthermore, FIG. 7 is a cross-sectional view showing still another embodiment of an automobile engine mount constructed according to the present invention. lO: Inner cylinder metal fitting 12: Outer cylinder metal fitting 14: Rubber elastic body 16, 40, 56j Engine mount 24: Axial side walls (thin wall part) 30; Fluid chamber (pressure receiving chamber) 32; Projection block 34: Fluid action area (Vibration acting part) 48; Fluid chamber (equilibrium chamber) 50 Niorifice passage 52; Flexible membrane Applicant: Tokai Rubber Industries, Ltd. Figure 3 Figure 4 (a) (deg) mt* (Hz) (b) Circumference ! L most (Hz) 7th rI! J Procedural Amendment Commissioner Yoshi 1) Moon Takeshi 1, Indication of the case 1988 Patent Application No. 152961 2, Name of the invention Fluid-filled cylindrical mounting device 3, Person making the amendment Relationship to the case Patent Applicant name Tokai Rubber Industries Co., Ltd. 4, agent (1) Detailed description of the invention column 6 in the specification, content of amendments (1) “Preferably 3
〜IO+111IJ is preferably 2〜10IIIJ
Correct to. (2) "Preferably 1000" on page 16, lines 8-9 of the same
+nm” or more” to “preferably 800IIIm” or more”
Correct to. that's all

Claims (3)

[Claims] (1) In a cylindrical mount device in which an inner cylindrical metal fitting and an outer cylindrical metal fitting arranged concentrically or eccentrically with each other are elastically connected by a rubber elastic body interposed between them, the diameter At least one fluid chamber is formed between the inner cylindrical metal fitting and the outer cylindrical metal fitting in a vibration input direction in which a low-viscosity incompressible fluid is sealed and into which vibration to be damped is input. A predetermined portion of the peripheral wall made of the rubber elastic body, which defines at least a portion of the fluid chamber, is formed into a thin wall portion capable of expanding and deforming, while the inner cylindrical metal fitting is provided inside the fluid chamber. and a working protrusion that protrudes at a predetermined height in the vibration input direction from one side of the outer cylindrical fitting toward the other side, and the working protrusion and the inner surface of the fluid chamber are fixedly provided. A fluid-filled cylindrical mount device characterized in that a vibration action gap of a predetermined size is formed between surfaces facing each other in a vibration input direction. (2) A configuration in which the operating protrusion protrudes from the outer cylindrical fitting side toward the inner cylindrical fitting side by fixing a housing member housed in the fluid chamber to the outer cylindrical fitting. The fluid-filled cylindrical mount device according to claim 1, wherein the cylindrical mount device is formed of: (3) The fluid chamber is formed as a pressure receiving chamber in which internal pressure fluctuations are caused by elastic deformation of the rubber elastic body when vibration is input between the inner and outer cylindrical metal fittings, and the inner and outer cylindrical metal fittings and an equilibrium chamber in which the predetermined incompressible fluid is sealed and at least a portion of which is defined by a flexible membrane to avoid input of vibration, independent of the pressure receiving chamber. 2. The fluid-filled cylindrical mount device according to claim 1, further comprising at least one orifice passageway for communicating the pressure receiving chamber and the equilibrium chamber with each other.