JPH01229131A - Fluid sealed type mount device - Google Patents

Abstract

PURPOSE:To realize a good vibro-isolating characteristic extending over a wide range of frequency by forming an intermediate chamber partitively between a rigid movable member and an elastic partition film, and installing an orifice passage which makes this intermediate chamber communicate with a balance chamber. CONSTITUTION:A rigid movable member 32 is installed in a partition member 34 so as to absorb a fluid pressure differential between a pressure chamber 36 and a balance chamber 38. In this movable member 32, there is provide with an orifice passage 62 which makes the pressure chamber 36 communicate with the balance chamber 38. Also there is provided with an elastic partition film 66 which closes an interconnecting passage 64. A high damping effect is brought into full play by a first orifice passage 56 and a low motion spring effect as well by a second orifice passage 62, respectively. Thus, a good vibro- isolating characteristic is realizable over a wide range of frequency.

Description

DETAILED DESCRIPTION OF THE INVENTION (Technical Field) The present invention relates to a fluid-filled mount device, and in particular has high damping characteristics for input vibrations of low frequency and large amplitude, as well as a wide frequency range from medium frequency and small amplitude to high frequency and minute amplitude. The present invention relates to a fluid-filled mount device suitable for use in automatic military engine mounts, etc., which can advantageously exhibit excellent low dynamic spring characteristics against a wide range of input vibrations.

(Prior art) Mounting devices such as automobile engine mounts are generally required to have excellent vibration damping characteristics against input vibrations of low frequency and large amplitude, and are also required to have excellent vibration damping characteristics for input vibrations in a wide frequency range from medium frequency and small amplitude to high frequency and minute amplitude. Excellent vibration isolation characteristics are required for vibrations, and in particular, it is required to exhibit a good damping effect against input vibrations of low frequency and large amplitude.

Therefore, in recent years, as such a mounting device, a first support body and a second support body are arranged facing each other at a predetermined distance in the main vibration input direction, and a rubber interposed between them is used. J. A partition member is elastically connected by an elastic body, and at least a part of the partition wall member is made of a flexible membrane, and the partition member and the first support member are elastically connected to each other. A fluid storage chamber containing a predetermined incompressible fluid is formed between the support and the fluid storage chamber, and a partition member is disposed within the fluid storage chamber, and the inside thereof is connected to a pressure receiving chamber on the first support side. and the flat i on the second support side
It is divided into a button chamber and an orifice passage that communicates the pressure receiving chamber and the equilibrium chamber with each other.
%-L body encapsulation type mounting device has been proposed.

According to the fluid phase displacement mount device with a similar structure,
By tuning the resonant frequency of the J1 compressible fluid flowing in the orifice passage to a low frequency range, the low IK1 wavenumber range is achieved based on the liquid column resonance effect of the fluid flowing in the orifice passage. This is due to its excellent damping properties against human vibration.

7) However, the mounting device G with such a structure can be made by applying the above-mentioned steps to the re-fitting passage, thereby reducing the amount of manual effort required in the low l^1 wave number range. Although a damping effect against the vibration can be obtained, the vibration in the high frequency range is 1,1l-11', and as the contractile fluid flows through the orifice passage and becomes silicic. As a result, there was a problem in that the mount had a high dynamic spring, and even worse, the anti-vibration function was deteriorated.

On the other hand, in 1985-9340 (publications, etc.), for the mounting device of the above-mentioned 11 structure, the partition member can be deformed or displaced in any predetermined manner in the direction of vibration input. It has been proposed that a movable member is disposed, and the fluid pressure difference between the pressure receiving chamber and the pressure balancing chamber is absorbed by the deformation or displacement of the movable member, thereby avoiding an increase in fluid pressure within the transfer chamber. has been done.

However, the absorption of hydraulic pressure by such movable members also
Fluid? It is accompanied by A motion, and can exhibit a particularly excellent vibration transmissibility reduction effect near the resonance frequency of the flowing fluid. However, when vibration is input in a frequency range higher than the resonance frequency, the mount can exhibit significant high vibration. This will cause spring formation. Therefore, in order to avoid deterioration of vibration isolation performance due to the increase in the mount moving spring as much as possible, the resonance frequency of the flowing fluid accompanying the displacement of the movable member is usually set in a high frequency range. It was difficult to obtain a sufficient vibration isolation effect against input vibration in the frequency range.

Especially for car engine mounts,
5-15) High damping ability when inputting low-frequency, large-amplitude vibrations such as engine shake of about Iz, and 20-50
100 which can cause lido 1 etc. when manual vibration of medium frequency and small amplitude such as engine-noise vibration of around Hz is applied.
When inputting vibrations of high j-11 waves and small amplitudes of about 300 II Z, excellent low: i, I, J, L, and J characteristics are required, so by providing the above-mentioned movable part However, the required characteristics can still be fully satisfied.
In particular, the use of high dynamic springs in manually operated ICs in the medium frequency range has been a problem.

(Problems to be solved) The present invention has been made against the background of the above-mentioned circumstances, and the problems to be solved are as follows:
In addition to high damping characteristics for low-frequency, large-amplitude human-powered vibrations, it also has high damping characteristics for medium-frequency, small-amplitude, and high-frequency input vibrations of tens of amplitudes.
All of them can exhibit excellent low dynamic vibration properties, and 11 is good vibration isolation in a wide frequency range. An object of the present invention is to provide a fluid-filled mounting device that can realize the '1' property.

(Solution Means) In order to solve this problem, the invention provides a first support body and a second support body that are arranged facing each other at a predetermined distance in the main vibration input direction. A partition member, at least a part of which is made of a flexible membrane, is disposed on the second support, and the partition member and the second support are elastically connected by an interposed rubber elastic body. A fluid storage chamber in which a predetermined incompressible fluid is sealed is formed between the fluid storage chamber and the first support, and a partition member is disposed within the fluid storage chamber, and the inside thereof is divided into a pressure receiving chamber on the first support side. In the fluid-filled mounting device, the fluid-filled mount device is provided with a first orifice passage that partitions the pressure receiving chamber and the equilibrium chamber on the second support side into communication with each other. A rigid movable member that can be displaced a predetermined distance in the vibration input direction is provided so as to absorb the fluid pressure difference between the pressure receiving chamber and the equilibrium chamber. a second orifice passage that communicates with the equilibrium chamber side; and a second orifice passage that is arranged in a communication passageway of the second orifice passageway to the pressure receiving chamber side or the equilibrium chamber side, and closes the communication passageway. An elastic partition membrane in which a predetermined reinforcing material is embedded is provided, and based on the elastic deformation of the elastic partition membrane, fluid flow is allowed in the second orifice passage, while reinforcing the weakly resistant partition membrane. The first point is that the structure is configured to prevent free flow of fluid through the second orifice passage based on the deformation restriction by H. ! This is considered to be an I symptom.

(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, FIG. 1 shows a specific example of an automobile engine mount to which the present invention is applied. In this figure, reference numerals 10 and 12 denote first and second support fittings as the second and second supports, respectively, which are separated by a predetermined distance in the vibration input direction (in the figure, downward direction). They are arranged so as to face each other.

The first support fitting 10 has a relatively small diameter 17 inner disk shape, and a mounting bolt 20 extending axially outward is provided upright at the center of its axially outer surface. On the other hand, the second support fitting 12 has a cylindrical bottom fitting 14 with a bottom.
The opening metal fitting 16 is integrally caulked and fixed to the opening of the bottom metal fitting 14, forming a relatively large-diameter bag-like structure as a whole. A plurality of mounting poles 1-22 are erected and extend in the direction.

The second support metal fitting 12 is arranged concentrically with the second support metal fitting 10 with its inner space opening toward the first support metal fitting 10, and in this arrangement state, , in a state where the annular rubber elastic body 18 fluid-tightly closes the opening of the second support fitting 12, the outer circumferential surface of the first support fitting 10 and the second support fitting The first support fitting 1 is integrally vulcanized and bonded to the inner peripheral surface of the opening of the first support fitting 1.
0 and the second support fitting 12 are elastically connected by the rubber elastic body 18. In addition, in the figure, 24 is an annular reinforcing metal fitting embedded in the rubber elastic body 18 concentrically with the rubber elastic body 18.

The engine mount in this embodiment is such that the first support fitting 10 or the mounting bolt 20 is used to attach the engine unit to the engine unit, while the second support fitting 12 is attached to the engine unit by the first bolt 22. The engine unit is attached to the vehicle body, thereby providing anti-vibration support for the engine unit relative to the vehicle body.

Here, the second support fitting 12 includes:
A diaphragm 26 as a partition member made of a flexible coil and a membrane is disposed so that its outer peripheral edge is fluid-tightly sandwiched between the bottom metal fitting 14 and the opening metal fitting 16. Accordingly, the diaphragm 26 and the first support fitting 1
0, a sealed space as a fluid storage chamber is formed, a part of which is defined by the rubber elastic body 18,
A predetermined incompressible fluid such as water or polyalkylene glycol is sealed in this sealed space. Note that the space between the tire phragm 26 and the bottom metal fitting 14 is an air chamber 28 for allowing the diaphragm 26 to deform.

The second support fitting 12 also includes a diaphragm 2.
6, a partition member 34 having an approximately disk shape as a whole is disposed, the outer peripheral edge of which is fluid-tightly held between the bottom metal fitting 14 and the opening metal fitting 16. The fluid storage space is divided into the rubber elastic body 1 by the partition member 34.
A pressure receiving chamber 36 is located on the diaphragm 26 side and causes internal pressure fluctuations upon vibration input, and an equilibrium chamber 38 is located on the diaphragm 26 side and prevents internal pressure fluctuations by deformation of the diaphragm 26.
It is divided into two parts.

Here, the partition member 34 is a substantially annular support member 3 disposed along the inner peripheral surface of the fluid accommodation space.
0, and a substantially disc-shaped movable member 32 disposed inside the annular support member 30.

More specifically, the annular support member 30 is composed of two annular plates 44 and 46 superimposed in the axial direction, and its outer peripheral edge is connected to the bottom metal fitting 14 and the opening metal fitting. The device is fixedly disposed on the second support fitting 12 by being fluid-tightly sandwiched between the device and the device 16.

Further, an annular space extending in the circumferential direction is formed within the annular support member 30, and the annular space 7
Communication hole 52 formed in each annular plate 4.1.46
．． A first orifice 1 m path 56 having a predetermined length is connected to the pressure receiving chamber 36 and the equilibrium chamber 38 through the pressure receiving chamber 36 and the pressure receiving chamber 38, respectively, thereby allowing the receiving 1+ chamber 36 and the flat iS+' 138 to communicate with each other. It is being formed.

When vibration is input between the first support fitting 10 and the second support fitting 12 and a fluid pressure difference is induced between the pressure receiving chamber 36 and the equilibrium chamber 38, the pressure receiving chamber 36 and the equilibrium chamber 38 are brought into equilibrium. Fluid flow through the first orifice passageway 56 is permitted between the chamber 38 and the chamber 38 .

Further, on one surface of the annular support member 30, two support strips 140 and 40 extending all around the circumference are formed at a predetermined distance from each other in the axial direction. In cooperation with the annular support member 30, the partition portion 10, l'34
A substantially disk-shaped movable portion 10A32 constituting the movable member 32 is disposed with its outer peripheral edge inserted between the support pieces 40 and 40, and the movable member 32 provides an annular support. The central hole portion of member 30 is closed.

This flexible part assembly 32 is made of a rigid material such as metal, and the thickness 1 of its outer peripheral edge is connected to the support piece 40.4.
By being thinner than the distance between 00 opposing surfaces,
It is supported to be movable in the axial direction, which is the vibration input direction, by a predetermined dimension regulated by contact with the support pieces 401 and 10. As a result, when a fluid pressure difference is generated between the pressure receiving chamber 36 and the equilibrium chamber 38, the movable member 32 can be displaced by a predetermined distance in a direction to absorb the fluid pressure difference. This movable member 3
2, the incompressible fluid is made to flow substantially between the pressure receiving chamber 36 and the equilibrium chamber 38 through the central hole of the annular support member 30, in other words, through the inner hole 42 of the support piece 40. It has become. Note that buffer rubber layers 4 are provided on both sides of the outer peripheral edge of the movable member 32, respectively, in order to reduce the impact 11 when abutting against the support pieces 40 and 40 and prevent the generation of abnormal noise.
8 is provided.

Further, the movable portion 32 is provided with a cylindrical portion 58 extending toward one side in the axial direction in its central portion, and furthermore, a small diameter cylindrical portion is provided on the distal end side of the cylindrical portion 58. A reduced diameter portion 60 is formed in a predetermined body portion.

A second orifice passage 62 is formed inside the reduced diameter portion 600), which connects both sides of the movable portion +A32, that is, the pressure receiving chamber 36 side and the equilibrium chamber 38 side. On the other hand, a cylindrical portion 58 that allows the second orifice passage 62 to communicate with the pressure receiving chamber 36
An elastic partition membrane (56
is arranged, and the communication channel 64 is closed.

The elastic partition membrane 66 is made of a predetermined rubber material and has a disk shape, and inside the elastic partition membrane 66, a reinforcement made of canvas or the like is provided almost entirely in the center in the axial direction. By being buried throughout, the strength is improved and the amount of elastic deformation is restricted to a predetermined amount. Further, the elastic partition membrane 66 is vulcanized and bonded on its outer circumferential surface to the inner circumferential surface of a thin-walled cylindrical mounting bracket 68, and the mounting bracket 68 is attached to the movable member 32.
By being press-fitted and fixed into the cylindrical part 58 of
It is placed in a state where the communication channel 64 is closed.

The elastic partition membrane 66 allows the pressure receiving chamber 36 and the equilibrium chamber 38 to be connected through the second orifice passage 62.
When a fluid pressure difference is created between the pressure receiving chamber 36 and the equilibrium chamber 38 when vibration is input to the mount, the elastic partition membrane 66 , by a predetermined amount in the direction of absorbing the fluid pressure difference, so that the incompressible fluid is substantially caused to flow within the second orifice passage 62 as the elastic partition membrane 66 deforms. It has become.

In other words, in the engine mount of this embodiment having the structure as described above, the pressure receiving chamber 36 and the equilibrium chamber 38 are
The first orifice passage 56, the second orifice passage 62, and the support piece 40 serve as fluid flow paths that allow fluid to flow between the compartments when vibration is input.
A second orifice passage 62 is provided with a second orifice passage 62, and the second orifice passage 62 is opened by the bullets 1 and 1 by the partition membrane 66, respectively. Distribution is being blocked.

And here, the first orifice passage 5
(6 is the fluid flowing inside) ■ Due to the resonance effect, it is able to withstand low-frequency, large-amplitude input vibrations with a frequency of 5 to 1511Z and an amplitude of about 11, which corresponds to engine mounts, bounces, etc. Its length and cross-sectional area are tuned to provide excellent vibration damping performance. Furthermore, the amount of deformation of the elastic partition membrane 66 and the amount of displacement of the movable member 32 may vary depending on the deformation and displacement of the elastic partition membrane 66 and the amount of displacement of the movable member 32, respectively.
Fluid pressure fluctuations within the pressure receiving chamber 36 at L% are absorbed.

The pressure is set to a size that is large enough to generate sufficient internal pressure fluctuations within the pressure receiving chamber 36, so that during low-frequency, large-amplitude vibration manual force, the pressure is A sufficient amount of fluid is ensured to flow.

Further, the second orifice passage 62 has a frequency of -20 to 50)jz and an amplitude of ±0.
2 The length and cross-sectional area of the flow are tuned so that excellent low dynamic spring characteristics can be exhibited due to the liquid column resonance effect of the fluid flowing inside it in response to input vibrations of medium frequency and small amplitude of about *yh. It is being done. and again,
Depending on the amount of displacement of the movable member 32, fluctuations in the fluid pressure within the pressure receiving chamber 36 at the time of medium frequency and small amplitude vibration input may not be fully absorbed, and sufficient deformation may occur in the elastic partition membrane 66. In addition, the deformation amount of the elastic partition membrane 66 is set to be large enough to sufficiently absorb the fluid pressure fluctuations in the pressure receiving chamber 36 that occur when such medium-frequency, small-amplitude vibrations are introduced. The size of the second orifice passage 62 is set so that a sufficient amount of fluid can be ensured to flow through the second orifice passage 62 when medium-frequency and small-amplitude vibrations are input. It should be noted that the first orifice passage 56 is substantially in a closed state when such medium frequency and small amplitude vibrations are input, so that it hardly functions.

It disappears.

Furthermore, the inner hole 42 of the support piece 40 provided in the annular part assembly 30 constituting the partition member 34 is
Frequency: 100 to 300 tlZ, Amplitude: ±0
．． Its length and flow cross-sectional area are tuned so that it can exhibit excellent low dynamic spring characteristics due to the liquid column resonance effect of the fluid flowing inside it in response to input vibrations with a high frequency and minute amplitude of about 0.05 am. There is. Furthermore, the amount of displacement of the movable member 32 is set to a value of 4 J that can sufficiently absorb the fluid pressure fluctuation within the pressure receiving chamber 36 that occurs when such high-frequency, minute-amplitude vibration is input.
As a result, fluid flows through the inner hole 42 of the support piece 40 when high frequency and small amplitude vibrations are input. Note that when such high frequency and minute amplitude vibrations are input, the first orifice passage 56 as well as the second orifice passage 62 become closed, so that the pressure receiving chamber 36 due to the +, tit deformation of the elastic partition membrane 66 is closed.
The liquid pressure absorption effect inside the tank also becomes almost ineffective.

Therefore, in the engine mount of this embodiment, the flow F) is allowed to flow through the first orifice passage 56.
Based on the liquid column resonance effect of the fluid caused by J, low frequency and large amplitude human vibration can be well damped, and the second orifice passage 62 and the inner hole 42 of the support piece 40
Based on the liquid column resonance effect of the fluid flowing through the filter, it is possible to effectively block input vibrations of medium frequency and small amplitude to high frequency and minute amplitude.

As a result, the engine mount of this embodiment has a higher damping ability for low-frequency, large-amplitude input vibrations, and a higher damping ability for high-frequency, small-amplitude input vibrations than the conventional fluid-filled mount device as described above. It is possible to extremely advantageously achieve low dynamic spring characteristics against input vibrations of medium frequency and small amplitude while ensuring low dynamic spring characteristics against input vibrations. This means that the vibration damping effect against vibration can be extremely effectively achieved.

In addition, in the LJ engine mount according to this embodiment, the elastic partition membrane 66 is fastened to the inner circumferential surface of the metal fitting 08, and by press-fitting the metal fitting 68, 3J1 on the movable member 32 (j, it will be fixed S
), the bullet 191 partition membrane 66-6
Attaching the SJl to the J moving part 32 can be advantageously and easily done with sufficient adhesive strength and (+f%) assemblability, and this elastic partition membrane 6
Compared to the case where the U7 is directly vulcanized and welded to the movable member 32, the U7 has the advantage of being easier to manufacture.
-ing

Another specific example of an automobile engine mount having a structure according to the present invention will be explained based on FIG. In contrast to the embodiment, since this shows another form of lateral movement of the partition part H, the first and second trowels are phantom U7 (,1 , [9] are given the same reference numerals as in the embodiment (FIG. 1), and detailed explanation thereof will be omitted.

That is, as shown in FIG. 2, in the engine mount of this embodiment, the annular support member 30 constituting the partition part 34 has two parts superimposed in the axial direction.
It is composed of two annular plates 74 and 76, and its outer peripheral edge is held between the bottom metal fitting 14 and the opening metal fitting 16, so that it is fixed to the second support metal fitting 12. ing. And, such an annular plate 74
．． Support pieces 40 extending in the circumferential direction are positioned at a predetermined distance apart from each other in the axial direction by the inner circumferential edges of 76.
．． It consists of 40.

Further, the support pieces 40, 40 are disposed so as to be displaceable by a predetermined distance in the vibration input direction, with the outer peripheral edge being held between the support pieces 40, 40.
The movable member 32, which cooperates with the annular support member 30 to form the partition portion +A' 34, has an outer peripheral portion composed of two rigid annular plates 78 and 80 superimposed in the axial direction. A first orifice passage 56 extending in the L1 direction is formed between the overlapping surfaces of the circular plates 78 and 80.
A rigid plate 84 is provided with a cylindrical part 82 in the center thereof, and a second orifice passage 62 is formed inside the cylindrical part 82. The partition membranes 66 are respectively fitted and fixed at a predetermined distance in the axial direction.

Even in the engine mount of this embodiment having such a structure, the fluid flows through the first orifice passage 56, the second orifice passage 62, and the inner hole 42 of the support piece 40. By tuning the liquid column resonance frequency of the fluid, the amount of deformation of the elastic partition membrane 66, and the amount of displacement of the movable member 32, respectively, in the same manner as in the first embodiment, an excellent This resulted in the realization of an engine mount that exhibits a vibration-proofing effect.

Although the embodiments of the present invention have been described in detail above, these are literal illustrations, and the present invention is not to be construed as being limited to these specific examples.

For example, in the embodiments described above, the elastic partition membrane 66 was arranged in the communication channel 64 that communicated the second orifice passage 62 with the pressure receiving chamber 36 side, but such an elastic partition membrane 66 It is also possible to arrange the second orifice passage 62 in the communication flow path that communicates with the equilibrium chamber 38, and in this case, the effects of the present invention can also be effectively exhibited by tuning similar to the above embodiment. It is possible that the

Further, the first orifice passage 56 does not necessarily need to be provided in the partition member 34, and can also be formed, for example, on the outside of the second support fitting 12.

Furthermore, the specific form of the second orifice passage is as follows:
It is not limited in any way, and in addition to the illustrated linear form,
For example, it is of course possible to form it in a spiral shape.

In addition, in the above embodiment, the engine mount for an automobile
- Although the present invention has been described as a specific example of the application of the present invention, the present invention can also be effectively applied to vibration-proof support mounts I, connection mounts, etc. in other devices. Of course, it is something.

In addition, the present invention may be implemented in various changes, modifications, improvements, etc. based on the knowledge of those skilled in the art, and such embodiments may be incorporated into the present invention. Deviating from the purpose.

It goes without saying that unless otherwise specified, all are included within the scope of the present invention.

(Effects of the Invention) As is clear from the above description, in the mounting i-device having the structure according to the present invention, low frequency large The high damping effect on high amplitude input vibrations also has a low damping effect on medium frequency small amplitude and high frequency small amplitude input vibrations due to the fluid flow through the second orifice passage and the fluid flow accompanying the displacement of the moving part +1. Each dynamic spring effect can be effectively exerted.

Therefore, according to the present invention, compared to conventional fluid-filled mount devices, a high damping capacity against low-frequency, large-amplitude input vibrations and low dynamic spring characteristics against high-frequency, small-amplitude input vibrations are ensured. However, it is possible to extremely advantageously improve the low dynamic spring characteristics against input vibrations of medium frequency and small amplitude. This means that improvements can be made extremely effectively.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional view showing one embodiment of the invention applied to an automobile engine mount, and FIG. 2 is a longitudinal sectional view showing an engine mount as another embodiment of the invention. 10: First support fitting 12: Second support fitting 18: Rubber elastic body 26: Diaphragm 32: Movable member
34 Partition member 36: Pressure receiving chamber 38: Equilibrium chamber 40: Support piece 42: Inner hole 56/first orifice passage 62: Second orifice passage 64: Communication passage 66: Elastic partition membrane 68: Mounting metal fittings 70: Reinforcement User applicant: Tokai Rubber Industries Co., Ltd.

Claims (1)

[Claims] A first support body and a second support body, which are disposed facing each other at a predetermined distance in the main vibration input direction, are elastically connected by a rubber elastic body interposed between them, while the first support body and the second support body are A partition member, at least a part of which is made of a flexible membrane, is disposed on the second support, and a predetermined incompressible fluid is sealed between the partition member and the first support. Further, a partition member is disposed within the fluid storage chamber to partition the interior into a pressure receiving chamber on the first support side and an equilibrium chamber on the second support side, and to separate the pressure receiving chambers from each other. In a fluid-filled mounting device including a first orifice passage that communicates with an equilibrium chamber, the partition member is configured to absorb a fluid pressure difference between the pressure receiving chamber and the equilibrium chamber; a second orifice passage that provides communication between the pressure receiving chamber side and the equilibrium chamber side with respect to the movable member, while providing a rigid movable member that can be displaced a predetermined distance in the vibration input direction;
An elastic partition membrane in which a predetermined reinforcing material is embedded is arranged in a communication flow path of the second orifice passage to the pressure receiving chamber side or the equilibrium chamber side and closes the communication flow path. , based on the elastic deformation of the elastic partition membrane, fluid flow is allowed in the second orifice passage, while fluid flow through the second orifice passage is restricted based on the deformation restriction by the reinforcing material of the elastic partition membrane. A fluid-filled mounting device characterized in that it is configured to prevent free flow of fluid.