JPH01229132A - Fluid sealed type mount device - Google Patents

Abstract

PURPOSE:To bring a good vibro-isolating effect into full play over a wide range of frequency by constituting a part of a partition member with an elastic partition film, while forming an intermediate chamber partitively between a movable member and this elastic partition film, and installing an orifice passage which makes this intermediate chamber communicate with a balance chamber. CONSTITUTION:At least a part of a partition member 34 is constituted of an elastic partition film 46 which absorbs a fluid pressure differential between a pressure chamber 36 and a balance chamber 38. Then, a rigid movable member 60 is installed in the partition member 34. An intermediate chamber 62 is formed partitively in an interval between this rigid movable member 60 and the elastic partition film 46. A high damping effect is brought into full play by a first orifice passage 56 which installs a second orifice passage 66, making the intermediate chamber 62 communicate with the balance chamber 38, in the rigid movable member 60 and a low motion spring effect as well by the second orifice passage 66, respectively. Thus, a good vibro-isolating effect can be brought into full play 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 automobile 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, as well as a wide frequency range from medium frequency small amplitude to high frequency minute amplitude. Excellent vibration isolation characteristics are required for input vibrations, and in particular, a good damping effect is required for low-frequency, large-amplitude input vibrations.

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 elastic body interposed between them is used. At the same time, a partition part shrine, at least a part of which is made of a flexible membrane, is disposed with respect to the second support, and the partition part +, (and the first part) are elastically connected to each other. A fluid storage chamber filled with a predetermined incompressible fluid is formed between the support and the fluid storage chamber, and a partition is arranged inside the fluid storage chamber so that the inside thereof can be divided into a pressure receiving chamber on the first support side and a pressure receiving chamber on the first support side. It has been proposed to use a so-called fluid-filled mount which is partitioned into two equilibrium chambers on the support side and is provided with an orifice passage that allows the pressure receiving chamber and the equilibrium chamber to communicate with each other.

According to the fluid-filled mounting device having such a structure, by tuning the resonance frequency of the incompressible fluid flowing in the orifice passage to a low frequency range, the liquid column of the fluid in the orifice passage can be reduced. Based on the resonance effect,
This makes it possible to obtain excellent damping characteristics for input vibrations in the low frequency range.

However, in a mounting device having such a structure, although an excellent damping effect on input vibrations in the low frequency range can be obtained by performing the above-mentioned tuning on the orifice passage, when vibrations are input in the medium to high frequency range, Since it becomes difficult for the incompressible fluid to flow through the orifice passage, the mount becomes a highly dynamic spring, which actually reduces the vibration damping function. , Japanese Unexamined Patent Publication No. 57-9340Σ, etc., for a mount device having the above-mentioned structure, a movable member that can be deformed or displaced by a predetermined dimension in the vibration input direction is disposed on the partition member, and the movable member is A device has been proposed in which the fluid pressure difference between the pressure receiving chamber and the equilibrium chamber is absorbed by deformation or displacement to avoid an increase in the fluid pressure within the pressure receiving chamber.

However, the absorption of hydraulic pressure by such movable members also
It is accompanied by fluid flow, and can exhibit a particularly excellent vibration transmissibility reduction effect near the resonance frequency of the flowing fluid. However, when the vibration is manually applied in a frequency range higher than the resonance frequency, the mount height increases significantly. This will cause a dynamic spring. 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. One of the reasons is that it is difficult to obtain a sufficient vibration isolation effect against input vibration in the frequency range.

In particular, for automobile engine mounts, it has a high damping capacity of 20 to 50 Hz, as well as a high damping capacity when low frequency and large amplitude vibrations such as engine shake of about 5 to 15 Hz are input.
100 to 300, which can cause muffled noise, etc. when inputting medium frequency and small amplitude vibrations such as engine idle vibrations of around Hz.
Since excellent low dynamic spring characteristics are required when vibrations of high frequency and minute amplitude of about Hz are input, the required characteristics can still be fully satisfied even by providing the above-mentioned movable member. The problem was the high dynamic spring when inputting vibrations in the frequency range.

(Problem to be solved) Here, the present invention has been made against the background of the above-mentioned circumstances. Provided is a fluid-filled mounting device that can exhibit excellent low dynamic spring characteristics for input vibrations of small frequency amplitude and high frequency minute amplitude, and can realize good vibration isolation characteristics over a wide frequency range. There is a particular thing.

(Solution Means) In order to solve this problem, the present invention provides a first support body and a second support body that are arranged facing each other at a predetermined distance from each other 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 is elastically connected to the second support by a rubber elastic body interposed therein. A fluid storage chamber filled with a predetermined incompressible fluid is formed between the first support and the fluid storage chamber. In the fluid-filled mount device, the fluid-filled mount device is partitioned into a pressure receiving chamber and an equilibrium chamber on the side of the second support body, and is provided with a first orifice passage that allows the pressure receiving chamber and the equilibrium chamber to communicate with each other. at least a portion of the pressure receiving chamber and the equilibrium chamber by an elastic partition membrane having a reinforcing material embedded therein and deformable by a predetermined amount in the vibration input direction so as to absorb the fluid pressure difference between the pressure receiving chamber and the equilibrium chamber. While configuring
A rigid movable member that can be displaced a predetermined distance in the vibration input direction is spaced a predetermined distance from the pressure receiving chamber side or the equilibrium chamber side with respect to the elastic partition membrane, and is connected to the partition member or the second support member. and defining an intermediate chamber between the rigid movable member and the elastic partition membrane, and communicating the intermediate chamber with the pressure receiving chamber or the equilibrium chamber with respect to the rigid movable member. An orifice passage is provided, and based on the elastic deformation of the elastic partition membrane, fluid flow is allowed in the second orifice passage, while the second It is characterized in that it is configured to prevent free flow of fluid through the orifice passage.

(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 second and second supports, respectively, which face each other at a predetermined distance in the vibration input direction (in the vertical direction in the figure). It is arranged so that

The first support fitting 10 has a thick disk shape with a relatively small diameter, and a mounting bolt 20 that extends axially outward is erected at the center of its axially outer surface. On the other hand, the second support fitting 12 has a bag-like structure having a relatively large diameter as a whole, with an opening part of the fitting 16 being integrally fixed to the opening of the bottom fitting 14 in the shape of a cylinder with a bottom. A plurality of mounting bolts 22 are provided on the bottom wall of the bottom metal fitting 14 and extend axially outward.

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, , the annular rubber elastic body 18 fluid-tightly closes the opening of the second support fitting 12, and the outer peripheral portion 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.

In addition, in the engine mount in this embodiment, the first support metal fitting 10 is attached to the engine unit side with the mounting bolt 20, while the second support metal fitting 1 is attached to the engine unit side with the mounting bolt 20.
2 is attached to the vehicle body side with mounting bolts 22, thereby supporting the engine unit against the vehicle body in a vibration-proof manner.

Here, inside the second support fitting 12, a diaphragm 26 as a partition member made of a flexible rubber membrane extends its outer peripheral edge between the bottom fitting 14 and the opening fitting 16. It is disposed by fluid-tightly sandwiching the outer peripheral edge.

As a result, a sealed space as a fluid storage chamber is formed between the diaphragm 26 and the first support fitting 10, and a part of the space is defined by the rubber elastic body 18. A predetermined incompressible fluid such as water or polyalkylene gellicol is sealed within the space. Note that the space between the diaphragm 26 and the bottom metal fitting 14 is
Air chamber 28 for allowing deformation of the diaphragm 26
It is said that

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 partition member 34 divides the fluid storage space F into the rubber elastic body 1.
A pressure receiving chamber 36 is located on the 8 side and causes internal pressure fluctuations when vibrating human power is applied, and an equilibrium chamber 3B is located on the diaphragm 26 side and the internal pressure fluctuations are avoided by deformation of the diaphragm 26.
It is divided into two parts.

Here, the partition member 34 includes an annular support portion 3 having a substantially annular disk shape disposed along the inner circumferential surface of the fluid storage space.
0 and a substantially disc-shaped partition wall 32 disposed inside the annular support 30.

More specifically, the annular support portion 30 is composed of two annular plates 44 and 46 superimposed in the axial direction, and the outer peripheral edge thereof is connected to the bottom metal fitting 14 and the opening metal fitting 16. By being fluid-tightly sandwiched therebetween, it is arranged in a fixed position relative to the second support fitting 12. Further, an annular space extending in the circumferential direction is formed within the annular support portion 30, and the annular space is connected to the pressure receiving chamber 36 through communication holes 52.54 formed in each annular plate 44.46. and the equilibrium chamber 38, so that the pressure receiving chamber 36 and the equilibrium chamber 38 are communicated with each other.
A first orifice passage 56 of a predetermined length is formed which allows the two to communicate with each other.

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 is created between the chamber 38 and the chamber 38 through the first orifice passage 56.

Further, the partition wall portion 32 that cooperates with the annular support portion 30 to constitute the partition member 34 is disposed in the center hole 40 of the annular support portion 30, and the partition wall portion 32 is located at the center of the annular support portion 30. Hole 40 is closed.

This partition wall portion 32 is made of a predetermined rubber material.
A substantially disc-shaped elastic partition membrane 4G and a thin-walled short cylindrical mounting fitting 48 vulcanized and bonded to the outer peripheral surface of the elastic partition membrane 46.
It is composed of C.

Further, inside the elastic partition membrane 46, a reinforcing material 50 such as a canvas is embedded over almost the entire surface of the elastic partition membrane 46 at the center in the axial direction, thereby improving the strength of the elastic partition membrane 46. At the same time, the amount of elastic deformation is regulated to a predetermined amount. And, such a partition wall portion 32 is
With respect to the inside of the central hole 40 of the annular support part 30,
By press-fitting and fixing the metal fitting 48, the center hole 4
The inside of the pressure receiving chamber 36 is partitioned in the direction perpendicular to the axis and assembled in a fixed position.

When vibration is input, the pressure receiving chamber 36 and the equilibrium chamber 38
When a fluid pressure difference is caused between the partition wall 32
The elastic partition IJJ membrane 46 constituting the annular support part 30 is deformed by a predetermined amount in the direction of absorbing the fluid pressure difference. The enclosed fluid is substantially allowed to flow within the bore 40.

Furthermore, in the partition member 34 having such a structure, the partition member 34 is located within the central hole 40 of the annular support portion 30 closer to the equilibrium chamber 38 than the position where the partition wall portion 32 is disposed, Two supporting pieces 58 and 58 are formed on the inner circumferential surface of the central hole 40, extending over the entire circumference in the circumferential direction and spaced apart from each other by a predetermined distance in the axial direction.
A substantially disk-shaped movable member 60 is disposed with the outer peripheral edge inserted between the two ends. As a result, the movable member 60 is exposed a predetermined distance from the partition wall 32 in the vibration input direction and is disposed substantially parallel to each other, and the partition wall 32 and the movable member 60, there is an intermediate chamber 62 defined between the pressure receiving chamber 36 and the equilibrium chamber 38 by the two members 32 and 60.
is being formed.

By the way, the movable member 60 is made of a rigid material such as metal, and the thickness of its outer peripheral edge is thinner than the distance between the opposing surfaces of the support pieces 58 and 58. 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 58 and 58.

Note that buffer rubber layers 68 are provided on both sides of the outer peripheral edge of the movable member 60, respectively, in order to reduce the impact when the movable member 60 comes into contact with the support pieces 58 and 51H and prevent the generation of abnormal noise. ing.

Further, the movable member 60 has a cylindrical portion 64 having a predetermined length extending toward one side in the axial direction at its central portion, and inside the cylindrical portion 64, the movable member A second orifice passage 66 is formed to connect both sides of 6o, that is, the intermediate chamber 62 and the equilibrium chamber 38.

In such a movable member 60, the support piece 5
8.58, when the elastic partition membrane 46 is deformed to a predetermined amount, an increase in the hydraulic pressure in the intermediate chamber 62 is avoided, and the central hole 40 due to the deformation of the elastic partition membrane
The elastic partition membrane 4 allows substantial fluid flow between the pressure receiving chamber 36 and the equilibrium chamber 38 through the
If the deformation of the elastic partition membrane 6 becomes excessive, the fluid pressure fluctuation in the intermediate chamber 62 corresponding to the fluid pressure fluctuation in the pressure receiving chamber 36 based on the deformation of the elastic partition membrane 46 causes the intermediate chamber 62 and the equilibrium chamber to 3
8 through the second orifice passage 66.

That is, in the engine mount of the present embodiment having the above-described structure, the fluid flow path in which the enclosed fluid is caused to flow based on the fluid pressure fluctuation of the pressure receiving chamber 36 upon input of vibration; A first orifice passage 56 and a central hole 40 are provided between the pressure receiving chamber 36 and the equilibrium chamber 38, and a second orifice passage 56 is provided between the intermediate chamber 62 and the equilibrium chamber 38. The central hole 40 is defined by an elastic partition membrane 46 and the movable member 6o, and the second orifice passage 56 is defined by an elastic partition B! 46 respectively prevent free flow of fluid.

And here, the first orifice passage 5
6 is able to withstand input vibrations of low frequency and large amplitude with frequency: 5 to 15) Iz and amplitude: ±111, which corresponds to engine shake, bounce, etc., due to the liquid column resonance of the fluid flowing inside. Its length and cross-sectional area are tuned to provide excellent vibration damping performance. Furthermore, depending on the amount of deformation of the elastic partition membrane 46, the fluid pressure fluctuations within the pressure receiving chamber 36 at the time of low frequency, large amplitude vibration input may not be fully absorbed, and the pressure receiving chamber 36 may not have sufficient capacity. The first orifice passage 56 is set to a size large enough to cause internal pressure fluctuations, thereby ensuring a sufficient amount of fluid flowing through the first orifice passage 56 when low frequency and large amplitude vibrations are input. It has become.

Further, the second orifice passage 66 has a frequency of 20 to 50 Hz, an amplitude of ±Q, which corresponds to idle vibration, etc.
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 medium-frequency, small-amplitude input vibrations of about 2 ml. -ing and again,
The amount of deformation of the elastic partition membrane 46 is set to be large enough to sufficiently absorb fluid pressure fluctuations within the pressure receiving chamber 36 that occur when such medium-frequency, small-amplitude vibrations are input. Depending on the amount of displacement of the movable member 60, the fluid pressure fluctuations in the intermediate chamber 62 caused by the deformation of the elastic partition membrane 46 cannot be fully absorbed when such medium-frequency, small-amplitude vibrations are input. The size is set to be large enough to generate sufficient internal pressure fluctuations within the second orifice passage 62, thereby ensuring a sufficient amount of fluid flowing through the second orifice passage 66 when medium frequency and small amplitude vibrations are input. It is now possible to do so. It should be noted that the first orifice passage 56 is substantially closed when such medium-frequency, small-amplitude vibration is input, and 9? It stops functioning.

Furthermore, the central hole 40 provided in the annular support part 30 constituting the partition member 34 has a frequency of 100-300112. Amplitude: The elastic partition membrane 4
The length and flow cross-sectional area of the movable member 60 are tuned so that excellent low dynamic spring characteristics can be exhibited by the liquid column resonance effect of the fluid flowing inside the movable member 60 based on the deformation of the movable member 60 and the displacement of the movable member 60. It is. Furthermore, the amount of displacement of the movable member 60 is such that when such high-frequency, small-amplitude vibrations are input, fluid pressure fluctuations in the intermediate chamber 62, which is occupied by the deformation of the elastic partition 11N46, can be sufficiently absorbed by the displacement. The size is set to , so that a substantial fluid flow of C is caused through the central hole 40 when vibrations of high frequency and minute amplitude are input. It should be noted that when such high-frequency, minute-amplitude vibrations are input, the second orifice passage 66 as well as the first orifice passage 56 become closed, and almost no longer function.

Therefore, in the engine mount of this embodiment, low-frequency, large-amplitude input vibrations can be well damped based on the liquid column resonance effect of the fluid flowing through the first orifice passage 56. In addition, based on the liquid column resonance effect of the fluid flowing through the second orifice passage 66 and the central hole 40 of the annular support section 30, human vibrations of medium frequency and small amplitude to high frequency and minute amplitude can be effectively blocked. It is possible.

As a result, the engine mount of this embodiment has a high damping ability for low frequency, large amplitude input vibrations, and a high damping ability for high frequency, small amplitude input vibrations, compared to the conventional fluid-filled second mount device as described above. By using such an engine mount I, it is possible to extremely advantageously achieve an improvement in the low dynamic spring characteristic against small amplitude input vibrations while ensuring low dynamic spring characteristic against the input vibration of medium-sized waves with small amplitude. In particular, the vibration damping effect against eye vibration can be extremely effectively improved.

In addition, in the engine mount I according to this embodiment, the elastic partition membrane 46 is configured as a partition member 34 with a mounting fitting 48 integrally vulcanized and bonded to the outer circumference, and the elastic partition membrane 46 is configured as a partition member 34 that is integrally vulcanized and bonded to the outer circumferential portion, and is attached to the annular support portion 30. However, the center hole 40 of the mounting bracket 40
Since the elastic partition membrane 46 is press-fitted into the annular support part 30, it is easy to assemble it. It also has the advantage of being easier to manufacture.

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

For example, as shown in FIG. 2, the movable member 60 is positioned closer to the pressure receiving chamber 36 than the partition wall 32,
It is also possible to arrange it within the center hole 40 of the partition member 34, and even in such an arrangement, the first orifice passage 56, the second orifice passage 66, the center hole 40, etc. Therefore, by performing the same tuning as in the above embodiment, the effects of the present invention can be effectively exhibited. In addition, in this second drawing, in order to facilitate understanding, the same reference numerals are given to the members having the same structure as in the first embodiment. .

Further, in the embodiment described above, the elastic partition membrane 46 and the movable member 60 were formed to have approximately the same area, but they do not necessarily need to be set to have the same area.

Furthermore, the first orifice passage 56 does not necessarily need to be provided in the partition member 34; for example, the first orifice passage 56
It is also possible to form it on the outside of 2 or the like.

Further, depending on the form of the first orifice passage 56, the movable member 60 may be disposed relative to the second support fitting 12.

Further, the specific shape of the second orifice passage 56 is not limited to the linear shape shown in the example, but can be formed in various shapes, such as a spiral shape, for example.

In addition, in the above embodiment, a specific example was described in which the present invention was applied to an automobile engine mount, but the present invention can also be applied to vibration-proof support mounts, connection mounts, etc. in other devices. Of course, it can also be effectively applied.

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. 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 mounting device structured according to the present invention, low-frequency, large-amplitude A high damping effect on input vibrations, and also a low dynamic spring effect on medium frequency and small amplitude input vibrations due to the fluid flow through the second orifice passage, further accompanied by the deformation of the elastic partition membrane and the displacement of the movable member. Based on the fluid flow, the low dynamic spring effect on high frequency small amplitude input vibration is
Each can be put to effective use.

Therefore, according to the present invention, compared to conventional fluid-filled mounting devices, it is possible to ensure high damping ability against low frequency, large amplitude input vibrations, and low dynamic spring characteristics against high frequency, minute amplitude input vibrations. At the same time, 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 in the quality of life can be achieved extremely effectively.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal cross-sectional view showing an automobile engine mount according to one embodiment of the present invention, and FIG. 2 is a longitudinal cross-sectional view showing an automobile engine mount according to another embodiment of the invention. 10. First support fitting 12. Second support fitting 13:
::(J,, elastic body 26, diaphragm, 34
: Partition member 36/Pressure receiving chamber 38: Equilibrium chamber 40: Central hole 46: Elastic partition membrane 48 Second mounting bracket 50, reinforcing material 56: First orifice passage 58: Support piece 60: Movable member 62: Intermediate chamber 66: First Second Orifice Passage Applicant Tokai Rubber Industries Co., Ltd. Figure 1 2 //2'2゜2''2

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 comprising a first orifice passage that communicates with an equilibrium chamber, at least a portion of the partition member is configured to absorb a fluid pressure difference between the pressure receiving chamber and the equilibrium chamber. The elastic partition membrane has a reinforcing material embedded therein and is deformable by a predetermined amount in the vibration input direction. A rigid movable member that is spaced apart and capable of displacing a predetermined distance in the vibration input direction is provided on the partition member or the second support, and an intermediate chamber is provided between the rigid movable member and the elastic partition membrane. A second orifice passage is provided for the rigid movable member to communicate the intermediate chamber with the pressure-receiving chamber or the equilibrium chamber, and the second The second orifice passage is characterized by allowing fluid to flow within the second orifice passage, while preventing free flow of fluid through the second orifice passage based on deformation restriction by the reinforcing material of the elastic partition membrane. Fluid-filled mounting device.