JP3009797B2 - Fluid-filled cylindrical mounting device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a mounting device which is interposed between an engine and a vehicle body and is used as an anti-vibration measure when the engine is mounted on a vehicle, and more particularly to a flow of a fluid enclosed therein. The present invention relates to a fluid-filled cylindrical mount device that suppresses the transmission of vibration based on the following.

[0002]

2. Description of the Related Art Conventionally, as a mounting device used as an anti-vibration measure when an engine is mounted on a vehicle body, a cylindrical mounting device in which an elastic body made of rubber is interposed between an inner cylinder and an outer cylinder is known. Are known. In this cylindrical mounting device, the inner cylinder is fixed using a bolt or the like between a pair of brackets fixed to the vehicle body side, and the engine is supported on the outer cylinder via a fixing bracket or the like. In this way, the engine is supported by the vehicle body via the cylindrical mount device, so that the vibration and the like of the engine are attenuated by the elastic body and are prevented from being transmitted to the vehicle body.

However, in the above-mentioned technology, a single rubber is used as a vibration isolator. However, a mounting device using the single rubber has a problem that a spring constant is increased particularly in a high frequency range. As a result, vibration in the high frequency range cannot be sufficiently attenuated, and it is not possible to sufficiently prevent muffled noise and engine noise, which is sufficient for recent demands such as quietness of vehicles. There was a problem that we could not respond.

Therefore, in recent years, as a technique for reducing a spring constant in a high frequency range, for example, Japanese Patent Laid-Open No.
A fluid-filled cylindrical mount device as disclosed in Japanese Patent Application Publication No. 529 is known. As shown in FIGS. 8 and 9, this conventional fluid-filled cylindrical mount device has an inner cylinder 41.
An elastic body 43 made of rubber is interposed between the outer cylinder 42 and the outer cylinder 42. A recess 44 is formed in the upper part of the outer peripheral surface of the elastic body 43, and a fluid chamber 45 in which a predetermined low-viscosity incompressible fluid is hermetically sealed is formed between the recess 44 and the outer cylinder 42. Have been. A movable block 46 made of an aluminum alloy or the like is movably accommodated in the fluid chamber 45.

Further, another recess 48 is formed in the lower part of the outer peripheral surface of the elastic body 43, and between the recess 48 and the outer cylinder 42,
A fluid chamber 49 in which a predetermined low-viscosity incompressible fluid is hermetically sealed.
Are formed. The fluid chamber 49 and the fluid chamber 45 are mutually connected by an orifice passage 50.

[0008] In the fluid-filled cylindrical mount device configured as described above, when vibration is input in the vertical direction in FIGS. 8 and 9, the elastic body 43 is deformed by the vibration, and the fluid chamber 45 is deformed. Inside dimensions (A in FIGS. 8 and 9)
Is changed. Then, with the change of the inside dimension A,
The internal pressure of the fluid chamber 45 is fluctuated, and the fluid flows between the fluid chamber 45 and the fluid chamber 49 via the orifice passage 50 based on the fluctuation. Note that the outflow and inflow of the fluid into and out of the fluid chamber 49 can be made possible by the thinned portion of the elastic body 43 constituting a part of the wall of the fluid chamber 49 and the flexible film 51. It is easily allowed by the volume change of the fluid chamber 49 due to the elastic deformation of the flexible film 51. The damping coefficient in the low frequency range can be improved based on the flow action and resonance action of the fluid flowing through the orifice passage 50, and the vibration isolation performance in the low frequency range can be improved.

When the inner dimensions of the fluid chamber 45 are changed by the deformation of the elastic body 43 due to the input of the vibration, the fluid in the fluid chamber 45 is moved around the movable block 46 and the fluid chamber 45.
Between the inner wall of That is, a fluid flow path through which fluid flows in response to vibration input is formed between the movable block 46 and the inner wall of the fluid chamber 45, and this fluid flow path becomes the fluid working area 47. Then, the spring constant in a predetermined high frequency range is reduced based on the flow action and resonance action of the fluid flowing in the fluid action area 47.

Therefore, in this conventional fluid-filled cylindrical mount device, a soft spring characteristic can be effectively exhibited with respect to input vibration in a predetermined high frequency range, and the vibration transmissibility in the high frequency range is high. , And quietness in the vehicle can be improved.

[0009]

By the way, in the frequency range where the effect of reducing the spring constant can be exhibited, the hardness of the elastic body 43 and the volume of the fluid working area 47 are adjusted to flow through the fluid working area 47. The desired frequency range can be set by tuning the resonance frequency of the fluid.
However, in the related art, only one fluid action region 47 having a predetermined volume is formed between the inner wall of the fluid chamber 45 and the movable block 46. Therefore, even if the resonance frequency of the fluid flowing through the fluid action region 47 is tuned as described above, the frequency range in which the effect of reducing the spring constant can be exhibited can be set to only one frequency range. . Therefore, according to this conventional technique, the effect of reducing the spring constant is exhibited only in one predetermined high frequency range, and the spring constant cannot be reduced over a wide frequency range. There has been a problem that it is not possible to sufficiently meet higher requirements such as quietness.

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and an object of the present invention is to reduce a spring constant over a wide frequency range, particularly in a high frequency range, and to provide a vibration isolation performance. It is an object of the present invention to provide a fluid-filled cylindrical mount device that can improve the performance.

[0011]

In order to achieve the above object, the present invention provides an inner cylinder and an outer cylinder, an elastic body interposed between the inner cylinder and the outer cylinder, and A fluid chamber formed between the outer cylinder and the elastic body, in which a fluid is hermetically sealed, a movable member movably housed inside the fluid chamber, and formed between the movable member and the fluid chamber; A fluid passage having a predetermined volume through which a fluid flows in response to a predetermined vibration input; and in a fluid-filled cylindrical mount device interposed between an engine and a vehicle body, the movable member has an outer peripheral portion. Less
And a single member having one inner peripheral portion,
A fluid flow path is formed between the outer peripheral portion and the inner peripheral portion of the movable member.
Having a plurality of different flow paths extending in the vibration direction
It becomes .

[0012]

According to the present invention, therefore, with the input of vibration,
Extends in the vibration direction through the outer and inner peripheries of the movable member
The fluid flows through a plurality of different flow paths. Then, each flow path <br/> based on flow action and resonance of the fluid flowing, the spring constant is reduced in the high frequency range, vibration damping effect is exhibited in that the high frequency range.

[0013] The fluid flow path has at least one outer peripheral portion.
The outer peripheral portion and the inner peripheral portion of a single movable member having an inner peripheral portion
A plurality of different flow paths extending in the vibration direction through
Have . Therefore, the resonance frequency of the fluid flowing through each flow path can be tuned to different values. Accordingly, the frequency range in which the effect of reducing the spring constant can be exhibited can be set to a plurality of frequency ranges corresponding to the respective resonance frequencies, and vibration isolation over a wide frequency range in a high frequency range. The effect can be obtained.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment in which the present invention is embodied in an engine mount of an automobile will be described in detail with reference to FIGS.

1 to 3 are a front sectional view, a front view, and a side sectional view, respectively, showing an engine mount 1 in this embodiment. The engine mount 1 includes a cylindrical inner cylinder 2 and an outer cylinder 3. The outer cylinder 3 is eccentric in one radial direction (up and down direction in FIG. 1) on the outer peripheral side of the inner cylinder 2, and is separated by a predetermined interval. It is arranged. An anti-vibration rubber 4 as an elastic body is interposed and fixed between the inner cylinder 2 and the outer cylinder 3.

As shown in FIG. 4, the engine mount 1 in this embodiment is arranged between a pair of brackets 6 fixed to the vehicle body 5 side. The engine mount 1 is fixed between the brackets 6 by screwing and tightening nuts to bolts (not shown) inserted into the inner cylinder 2 and the bracket 6. The outer cylinder 3 is connected to the engine 7 via the fixing bracket 8, and in this state, the engine 7 is supported on the vehicle body 5 via the engine mount 1 in a vibration-proof manner. In the engine mounted state shown in FIG. 4, the outer cylinder 3 is lowered with respect to the inner cylinder 2 by the elastic deformation of the vibration isolating rubber 4 due to the weight of the engine 7, and the inner cylinder 2 and the outer cylinder 3 are substantially the same. It is arranged on the axis. In the present embodiment, it is assumed that main vibrations are input in the eccentric directions of these two tubes 2 and 3 (vertical direction in FIG. 1).

As shown in FIG. 1 to FIG.
The inner cylinder 2 is vulcanized and bonded on its inner peripheral surface, and a substantially cylindrical mounting sleeve 9 positioned eccentrically with respect to the inner cylinder 2 by a predetermined amount is vulcanized on its outer peripheral surface. A circumferential groove 10 having a predetermined width is formed over the entire circumference at a central portion in the axial direction of the outer peripheral surface of the mounting sleeve 9. In the circumferential groove 10, on the side where the separation distance between the inner cylinder 2 and the mounting sleeve 9 in the eccentric direction is small,
A recess 11 that opens to the outer peripheral side is formed, and the recess 11 extends over substantially half the circumference of the mounting sleeve 9 in the circumferential direction.

The mounting sleeve 9 is attached to the vibration isolating rubber 4.
At a position corresponding to the concave portion 11, a hollow portion 12 penetrating in the axial direction between the inner cylinder 2 and the mounting sleeve 9 and extending substantially half way in the circumferential direction is formed. The lightening portion 12 causes a bounding direction of the weight and vibration load of the engine 7 between the inner cylinder 2 and the outer cylinder 3 (a direction in which the outer cylinder 3 is relatively lowered with respect to the inner cylinder 2). The occurrence of tensile stress in the vibration isolating rubber 4 when a load of? Is applied is reduced as much as possible. Also, this lightening portion 12
A rubber plate 13 having a substantially arc-shaped cross section is inserted therein, and an annular portion 13 a formed at one end of the rubber plate 13 is
It is inserted and fixed to one end of the inner cylinder 2.

Further, the vibration-proof rubber 4 has a portion radially opposed to the hollow portion 12 with the inner cylinder 2 interposed therebetween, in other words, a separation distance between the inner cylinder 2 and the mounting sleeve 9 in the eccentric direction. On the side where is larger, there is formed a recess 14 opening to the outer peripheral side. At a position corresponding to the opening of the recess 14, a window 15 is cut out in the circumferential groove 10 of the mounting sleeve 9, and the recess 14 is opened to the outside through the window 15. A substantially arc-shaped passage member 16 is mounted in the circumferential groove 10 of the mounting sleeve 9 so as to close the window portion 15.
And a first fluid chamber 17 is formed.

A rubber sheet 18 is fixed to both sides of the opening of the recess 11 so as to close the opening of the recess 11 formed in the circumferential groove 10 of the mounting sleeve 9. Both ends of the sheet 18 are fixed to both ends of the passage member 16. Then, a second fluid chamber 19 is formed between the rubber sheet 18 and the recess 11. or,
The rubber sheet 18 is formed in a thin shape,
The diaphragm film 18 is easily elastically deformed, and the volume of the second fluid chamber 19 is freely changed based on the elastic deformation of the diaphragm film 18.

FIG. 5 is an exploded plan view showing the passage member 16.
Are formed. One end of the meandering groove 20 communicates with the first fluid chamber 17 through the through hole 21, and the other end communicates with the second fluid chamber 19 through the through hole 22.

Then, the member composed of the inner cylinder 2, the vibration isolating rubber 4, the mounting sleeve 9, and the like,
Are externally fitted, and the outer sleeve 3 is fitted over the mounting sleeve 9.
The openings of the circumferential groove 10 and the meandering groove 20 of the passage member 16 are closed. A pair of air chambers 23 is formed between the rubber sheet 18 and the outer cylinder 3 that constitute the diaphragm film, and the first fluid chamber 17 and the first fluid chamber 17 are formed between the meandering groove 20 and the outer cylinder 3. A meandering orifice passage 24 communicating with the second fluid chamber 19 is formed. The outer cylinder 3 has an air chamber 2
An open hole 3a for communicating the air 3 with the atmosphere is formed.
Note that a thin seal rubber layer 25 is disposed on the inner peripheral surface of the outer cylinder 3, and airtightness or liquid tightness between the outer cylinder 3 and the mounting sleeve 9 and the passage member 16 is reliably maintained.

A predetermined low-viscosity incompressible fluid is sealed in the fluid chambers 17, 19 and the orifice passage 24. In addition, as a fluid to be enclosed, for example, water, ethylene glycol, propylene glycol, other alkylene glycol, low-viscosity silicone oil,
Alternatively, a mixed solution thereof or the like is appropriately used.

In the engine mounted state shown in FIG. 4, the outer cylinder 3 is lowered with respect to the inner cylinder 2 by the elastic deformation of the vibration isolating rubber 4, and the vertical dimension inside the first fluid chamber 17 is reduced. Therefore, the internal pressure of the same chamber 17 increases. Therefore, the fluid in the first fluid chamber 17 is pushed out of the first fluid chamber 17, and is pushed through the orifice passage 24 to the second fluid chamber 19.
Is flowed into. At this time, in the second fluid chamber 19, the flow of the fluid into the second fluid chamber 19 is easily permitted by the elastic deformation of the diaphragm film 18.

A movable block 26 as a movable member is movably accommodated in the first fluid chamber 17.
The movable block 26 is formed of a synthetic resin material such as nylon [6], a metal material, or the like. The block 26 floats or sinks in the first fluid chamber 17 when no vibration is input. I have.

In the first fluid chamber 17, a column 27 is integrally formed with the vibration isolating rubber 4 so as to protrude upward, and the upper surface of the column 27 is, as shown in FIG. In the mounted state, it is pressed against the inner peripheral surface of the passage member 16. The movable block 26 has a through hole 2.
8 is formed, and the movable block 2
6 is loosely fitted to the column 27.

In this embodiment, the first fluid chamber 17
A first fluid flow path 29 is formed in a region surrounded by the inner peripheral wall of the movable block 26 and the outer peripheral surface of the movable block 26. Further, a second fluid flow path 30 is formed in a region surrounded between the outer peripheral surface of the columnar body 27 and the inner peripheral surface of the through hole 28 of the movable block 26. That is, in the present embodiment, the first fluid chamber 17
Inside, two fluid flow paths 29 and 30 are formed between the same chamber 17 and the movable block 26.

As shown in FIG. 3, in this embodiment, the clearance a between the inner peripheral wall of the first fluid chamber 17 and the outer peripheral surface of the movable block 26 is equal to the outer peripheral surface of the columnar body 27 and the movable block. 26 is set to be larger than the clearance b between the through hole 28 and the inner peripheral surface. That is, in the present embodiment, the volume of the first fluid channel 29 is set to be larger than the volume of the second fluid channel 30, and the amount of fluid in the first fluid channel 29 is It is larger than the fluid amount in the second fluid flow path 30.

Next, the operation of the engine mount 1 configured as described above will be described. When a vertical vibration is input between the inner cylinder 2 and the outer cylinder 3 due to the operation of the engine 7 or the running of the vehicle, the first vibration is caused by the elastic deformation of the vibration isolating rubber 4 caused by the vibration. The vertical dimension inside the fluid chamber 17 is changed. Then, the internal pressure of the first fluid chamber 17 fluctuates in accordance with the change of the vertical dimension, and based on the fluctuation, the first fluid chamber 17 and the second fluid chamber 19 pass through the orifice passage 24. Fluid flow occurs. At this time, the outflow and inflow of the fluid to and from the second fluid chamber 19 are easily permitted by the volume change of the second fluid chamber 19 due to the elastic deformation of the diaphragm film 18.

Based on the flow action and resonance action of the fluid flowing through the orifice passage 24, an anti-vibration effect against input vibration in a predetermined frequency range is exhibited. By adjusting the cross-sectional area and length of the orifice passage 24 and tuning the resonance frequency of the fluid flowing through the orifice passage 24, the frequency range in which the anti-vibration effect can be exhibited can be appropriately set. it can. In particular, since such an orifice passage 24 can improve the damping coefficient in a low frequency range and exhibit excellent damping performance against input vibration in a low frequency range such as an engine shake, the orifice passage 24 has a low frequency range. Can be improved.

When the vertical dimension inside the first fluid chamber 17 is changed by the elastic deformation of the vibration isolating rubber 4 due to the input of the vibration, the fluid flows in the first fluid chamber 17. . That is, the fluid flows through the first fluid flow path 29 or the second fluid flow path 30, and based on the flow action and the resonance action of the fluid flowing through these flow paths 29, 30, the fluid in a predetermined high frequency range. The spring constant is reduced. Therefore, in the engine mount 1 of this embodiment, a soft spring characteristic can be effectively exhibited with respect to the input vibration in a predetermined high frequency range, and the vibration transmissibility in the high frequency range is reduced, and A great anti-vibration effect can be obtained.

In the present embodiment, the volume of the first fluid channel 29 is set to be larger than the volume of the second fluid channel 30, and the amount of fluid in the first fluid channel 29 is reduced. , The amount of fluid in the second fluid flow path 30 is larger. Therefore, the resonance frequencies of the fluid flowing through the fluid flow paths 29 and 30 also have different values. Therefore, the frequency range in which the effect of reducing the spring constant can be exhibited can be set to two frequency ranges corresponding to the respective resonance frequencies,
In a high frequency range, a vibration isolation effect can be obtained over a wide frequency range.

FIGS. 6 and 7 show experimental results obtained by measuring the damping characteristic and the spring characteristic with respect to the vibration frequency of the engine mount 1 according to the present embodiment.
In these figures, Comparative Example 1 shows the results of an engine mount having no fluid chamber and using a single rubber as a vibration isolator. Comparative Example 2 has two fluid chambers communicated with each other via an orifice passage, and a movable block is disposed in one of the fluid chambers, and one fluid flow path is provided between the fluid chamber and the movable block. 9 shows the results of the formed engine mount. That is, Comparative Example 2 shows the result of the same configuration as the engine mount of the related art shown in FIGS. 8 and 9. Comparative Example 3 shows the result of an engine mount in which the hardness of the vibration-proof rubber is higher than that of the engine mount of Comparative Example 2.

As apparent from FIG. 6, in the engine mount 1 of the present embodiment, the attenuation coefficient in a low frequency range is improved. Therefore, excellent damping performance is exhibited for input vibrations in a low frequency range, whereby the vibration isolation performance in a low frequency range is improved, and the riding comfort of the vehicle can be improved.

As is apparent from FIG. 7, in the engine mount 1 of the present embodiment, the spring constant in the high frequency range is reduced, so that the vibration transmissibility in the high frequency range can be reliably reduced. Can be. Therefore, the vibration of the engine 7 is less likely to be transmitted to the vehicle body, the vibration noise felt inside the vehicle can be reduced, and the quietness of the vehicle can be improved. Moreover, the frequency range in which the effect of reducing the spring constant can be exhibited is two high frequency ranges (P1, P2 in FIG. 7) corresponding to the muffled sound region and the engine noise region.
Since it is set to 2), it is possible to obtain an anti-vibration effect over a wide frequency range in a high frequency range. For this reason, it is possible to extremely effectively improve the quietness and the like of the vehicle.

That is, based on the flow action and the resonance action of the fluid flowing through the first fluid flow path 29 having a larger volume than the second fluid flow path 30, a high frequency The spring constant in the region P2 is reduced. Also, based on the flow action and resonance action of the fluid flowing through the second fluid flow path 30 having a smaller volume than the first fluid flow path 29, the high frequency region P corresponding to the muffled sound region is generated.
1, the spring constant is reduced. The frequency range in which the effect of reducing the spring constant can be exerted is adjusted by adjusting the hardness of the vibration isolating rubber 4 and the volumes of the fluid flow paths 29 and 30.
By tuning the resonance frequency of the fluid flowing through each of the fluid flow paths 29 and 30, it is possible to set a desired high frequency range.

As shown in FIG. 6, the damping characteristics of the engine mount of Comparative Example 3 are the same as those of the engine mount 1 of this embodiment. However, in the engine mount of Comparative Example 3, the damping coefficient in the low frequency region is reduced by increasing the hardness of the vibration isolating rubber in addition to the flow action and resonance action of the fluid flowing through the orifice passage. It has been improved to the same level as Therefore, in the case of the comparative example 3, since the hardness of the vibration-proof rubber is high, as shown in FIG.
This does not reduce the spring constant in the high frequency range.

As shown in FIG. 7, the engine mount of Comparative Example 2 can sufficiently reduce the spring constant in a high frequency range even when compared with the engine mount 1 of the present embodiment. It is. That is, since the engine mount of Comparative Example 2 has a softer vibration-proof rubber than that of Comparative Example 3, the spring constant can be reduced.

However, in the engine mount of Comparative Example 2, since only one fluid flow path is formed between the fluid chamber and the movable block, the frequency range in which the effect of reducing the spring constant can be exhibited is limited to the engine range. There is only one frequency region corresponding to the noise region. Moreover, in the engine mount of the comparative example 2, the hardness of the vibration isolating rubber is softer than that of the engine mount of the comparative example 3, so that the damping coefficient in the low frequency range is improved as shown in FIG. You don't get it.

That is, in this embodiment, the upper surface of the columnar body 27 is pressed against the inner peripheral surface of the passage member 16 when the engine is mounted. Therefore, the load of the engine 7 is also applied to the column 27, and the column 2
7, the engine 7 can be supported. Therefore, even when the hardness of the vibration isolating rubber 4 is equal to that of the comparative example 2, the same effect as when the hardness of the vibration isolating rubber 4 is increased to the same as that of the comparative example 3 in a low frequency range, that is, the damping coefficient. Can also be improved. Moreover, even if the damping coefficient is improved, the actual hardness of the vibration-isolating rubber 4 can be made equal to that of Comparative Example 2, so that the spring constant in a high frequency range can be reduced. is there.

Therefore, in the engine mount 1 of the present embodiment, both of the contradictory characteristics of improving the damping coefficient in the low frequency range and reducing the spring constant in the high frequency range can be achieved.

In other words, in this embodiment, the load of the engine 7 is also applied to the column 27 as described above.
Even if the hardness of the engine 7 is low, the engine 7 can be reliably supported. Therefore, the spring constant of the vibration isolating rubber 4 itself can be reduced, and the vibration transmissibility of the rubber isolating rubber 4 can be reduced, which can greatly contribute to the improvement of the vibration isolating performance particularly for input vibration in a high frequency range.

Further, since the movement in the bounding direction is restricted to some extent by the columnar body 27, the vertical dimension inside the first fluid chamber 17 becomes too small, and the movable block 26
Is not trapped vertically in the first fluid chamber 17. Accordingly, the movable block 26 in the first fluid chamber 17 may be prevented from moving up and down, or the movable block 26 and the passage member 16 may be pressed into contact with each other, and
6 is not damaged.

In this embodiment, the movable block 26 is moved up and down while being guided by the column 27. Therefore, the movable block 26 moves in a state where its direction is securely held without tilting or falling down with the vertical movement. In addition, even when vibration is input in an oblique direction, the movable block 26 does not move laterally beyond the clearance b between the movable block 26 and the column 27. Therefore, there is no danger that the corners of the movable block 26 collide with the inner wall of the first fluid chamber 17 and damage the anti-vibration rubber 4 to reduce its durability. Further, since the movable block 26 is moved up and down stably, the obtained spring characteristics and damping characteristics are also stable and good.

In addition, in the engine mount 1 of the present embodiment, the movable block 26 is inserted into the columnar body 27 formed in the first fluid chamber 17 through the through hole 2 at the time of assembly.
It only has to be inserted with 8. Therefore, there is also an advantage that the above-described various effects can be achieved with a simple configuration without complicating the configuration.

It should be noted that the present invention is not limited to the above-described embodiment, but may be embodied by changing the configuration of each unit as follows, for example, without departing from the spirit of the present invention. ( 1 ) The columnar body 27 is formed in any shape such as a circular column or a square column, and the shape of the through hole 28 of the movable block 26 is appropriately changed in accordance with the shape of the columnar body 27.

[0047]

As described above in detail, according to the present invention, the movable member is accommodated in the fluid chamber and the fluid passage is formed as the fluid passage.
Single movable with outer periphery and at least one inner periphery
The member extends in the vibration direction through the outer and inner
A plurality of different flow paths . Therefore, the resonance frequency of the fluid flowing through each fluid flow path can be tuned to different values. Therefore, the frequency range in which the effect of reducing the spring constant can be exhibited can be set to a plurality of frequency ranges corresponding to the respective resonance frequencies, and the vibration isolation effect can be obtained over a wide frequency range in the high frequency range. It has an excellent effect of being able to do it.

[Brief description of the drawings]

FIG. 1 is a front sectional view showing an embodiment in which a fluid-filled cylindrical mount device of the present invention is embodied in an engine mount.

FIG. 2 is a front view of an engine mount.

FIG. 3 is a side sectional view of an engine mount.

FIG. 4 is a front sectional view showing the engine mount when the engine is mounted.

FIG. 5 is an exploded plan view showing a passage member.

FIG. 6 is a graph showing an experimental result of measuring an attenuation characteristic with respect to a vibration frequency.

FIG. 7 is a graph showing an experimental result of measuring a spring characteristic with respect to a vibration frequency.

FIG. 8 is a front sectional view showing a conventional fluid-filled cylindrical mount device.

FIG. 9 is a side sectional view of the fluid-filled cylindrical mount device.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Engine mount, 2 ... Inner cylinder, 3 ... Outer cylinder, 4 ... Anti-vibration rubber, 5 ... Car body, 7 ... Engine, 17 ... First fluid chamber,
26: movable block, 27: columnar body, 28: through hole, 2
9: first fluid flow path, 30: second fluid flow path.

────────────────────────────────────────────────── ─── Continuation of front page (56) References JP-A-2-292540 (JP, A) JP-A-3-84244 (JP, A) JP-A-2-140050 (JP, U) (58) Survey Field (Int.Cl. ⁷ , DB name) F16F 13/06 B60K 5/12

Claims (1)

(57) [Claims] 1. An inner cylinder and an outer cylinder; an elastic body interposed between the inner cylinder and the outer cylinder; and an elastic body formed between the inner cylinder, the outer cylinder, and the elastic body, wherein a fluid is hermetically sealed. A fluid chamber, a movable member movably accommodated inside the fluid chamber, and a predetermined volume formed between the movable member and the fluid chamber, through which the fluid flows with a predetermined vibration input. A fluid-filled cylindrical mount device interposed between an engine and a vehicle body, the movable member having an outer peripheral portion and at least one inner peripheral portion.
The fluid flow path is provided by the movable member.
Extending in the vibration direction through the outer peripheral portion and the inner peripheral portion, respectively.
A fluid-filled cylindrical mount device characterized by having a plurality of different flow paths .