JP2510914B2 - Fluid-filled 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 fluid-filled mount device used for an automobile engine mount or the like, and more particularly to a fluid-filled mount device capable of externally controlling vibration damping characteristics.

[0002]

2. Description of the Related Art Conventionally, both sides of a rubber elastic body facing in a vibration input direction have been used as a type of vibration-proof connection or support device interposed between members constituting a vibration transmission system such as an automobile engine mount. In addition, there is known a mounting device having a structure in which a first supporting metal fitting and a second supporting metal fitting, which are respectively attached to respective ones of the vibration-proof connected or supported members, are fixed to each other.

Further, in recent years, as one method for realizing a higher vibration isolation characteristic, a part of the wall portion of the mount device is made of the rubber elastic body,
By providing a fluid chamber in which a predetermined incompressible fluid is sealed inside and controlling the internal pressure of the fluid chamber that is generated at the time of vibration input, the mount anti-vibration characteristics are switched and controlled according to the input vibration, etc. A fluid-filled mount device has been proposed.

For example, in Japanese Patent Laid-Open No. 60-8540 and Japanese Patent Laid-Open No. 59-1828, a part of the wall portion of the fluid chamber is constituted by a vibrating plate made of a magnetic material or a permanent magnet. A mounting device has been proposed in which the diaphragm is driven by a solenoid to generate pulsation inside the fluid chamber and control the internal pressure thereof. In Japanese Utility Model Laid-Open No. 3-73741, a ring-shaped coil is concentrically arranged inside or outside a ring-shaped permanent magnet, and either one of the permanent magnet and the coil is fixed to a diaphragm. Accordingly, a mounting device has been proposed in which the diaphragm is driven based on the electromagnetic force generated by energizing the coil to control the internal pressure of the fluid chamber.

However, in any of these mounting devices, the driving force exerted on the diaphragm cannot be effectively and stably obtained, and it is difficult to sufficiently obtain the vibration force of the diaphragm. In addition, since vibration control is extremely difficult, practically satisfactory vibration damping characteristics could not be obtained.

That is, in the mounting device as described above, the magnetic path formed by the solenoid or the permanent magnet is in the form of an open magnetic path, and the magnetic flux density in the region where the diaphragm or coil is placed. Since it is not possible to efficiently secure the internal pressure of the fluid chamber, it is possible to secure sufficient driving force of the diaphragm and perform effective internal pressure control of the fluid chamber, especially when inputting vibration in the middle and low frequency range where the input vibration load is large. There is a problem in that it is difficult and the size of the mounting device is unavoidable because the size of the solenoid, the permanent magnet and the like are increased.

Further, in such a mounting device,
The magnetic path formed by the solenoid or permanent magnet
Both of them are in the form of an open magnetic circuit and cannot form a region where the magnetic flux density is substantially constant.Therefore, when the diaphragm is driven and displaced, the magnetic flux density exerted on the diaphragm or coil. Changes drastically, and as a result, the driving force exerted on the diaphragm becomes unstable, making it difficult to control the vibration state of the diaphragm. And, because of that, the pulsating waveform induced in the fluid chamber is distorted, and it is unavoidable that the fluid pressure control in the fluid chamber is distorted.
The inherent problem was that the desired mount anti-vibration characteristics could not be obtained.

Further, even if the vibration isolation characteristic against the input vibration in a certain specific frequency range is improved by controlling the internal pressure of the fluid chamber by vibrating the vibrating plate, the pulsating waveform of the pulsating waveform caused in the fluid chamber as described above is obtained. Distortion results in amplification of vibration in other frequency regions, and there is also a problem that it is extremely difficult to obtain an effective vibration damping effect as a whole.

[0009]

The present invention has been made in view of the circumstances as described above, and the problem to be solved is to a diaphragm forming a part of a wall portion of a fluid chamber. It is an object of the present invention to provide a fluid-filled mount device capable of controlling vibration damping characteristics, which is provided with a driving means for a diaphragm that can obtain a sufficient driving force and can suppress distortion in the driving force.

[0010]

In order to solve such a problem, a feature of the present invention resides in that a first support fitting and a second support fitting are respectively provided on both side portions of a rubber elastic body facing each other in a vibration input direction. A fluid-filled mount device in which a fluid chamber in which a predetermined incompressible fluid is sealed and which is fixedly provided is formed by forming a part of the wall portion with such a rubber elastic body, and the wall of the fluid chamber is Part of the part is composed of a vibrating plate that is displaceably supported by the second support fitting, while a permanent magnet is disposed behind the vibrating plate, and first poles are provided on both poles of the permanent magnet. And the second yoke are connected to each other to form a magnetic path having an annular gap portion between the end facing surfaces of the first yoke and the second yoke, and along the gap portion. Ring-shaped extending in the circumferential direction The dynamic coil with displaceably arranged, and ligated to the movable coil to the diaphragm, in at energization of the movable coil that is adapted to vibrate the vibrating plate.

[0011]

The embodiments of the present invention will now be described in detail with reference to the drawings in order to clarify the present invention more specifically.

First, FIG. 1 shows an automobile engine mount having a structure according to the present invention. In this figure, 10 is a first support metal fitting, and 12 is a second support metal fitting, which are arranged to face each other with a predetermined distance therebetween, and a rubber elastic body 14 interposed between them.
They are elastically connected to each other. In such an engine mount, one of the first support metal fitting 10 and the second support metal fitting 12 is attached to the power unit side or the body side so that the power unit is vibration-proof supported with respect to the body. Becomes

More specifically, the first support fitting 10 is composed of an upper fitting 16 and a lower fitting 18 each having a bottomed cylindrical shape. The upper metal fitting 16 has a cylindrical wall portion having a cylindrical shape, and an outer flange portion 20 is formed in the opening thereof. In addition, the lower metal member 18 has a tapered cylindrical shape in which the cylindrical wall portion expands toward the opening side, and the outer flange portion 22 is formed in the opening portion. And
The upper and lower metal fittings 16 and 18 are overlapped with each other on the opening side, and are bolted at both outer flange portions to form the first support metal fitting 10.

Further, inside the first support fitting 10, between the upper and lower fittings 16 and 18, the upper and lower fittings 1 are provided.
A cavity is formed by the recesses 23 and 25 of 6 and 18. A flexible film 24 having a substantially thin disk shape is accommodated and arranged in the void, and the outer peripheral edge portion is sandwiched between the outer flange portions 20 and 22 of the upper and lower metal fittings 16 and 18. It is installed by. That is, this flexible film 24
Thus, the space is fluid-tightly divided into the recess 23 side of the upper metal fitting 16 and the recess 25 side of the lower metal fitting 18.

On the other hand, the second support fitting 12 has an annular block shape with a substantially large diameter. The second support fitting 12 is positioned to face the lower fitting 18 of the first support fitting 10 at a predetermined distance in the axial direction. The axial end surface of the second support fitting 12 facing the first support fitting 10 is a tapered surface corresponding to the outer peripheral surface of the cylindrical wall of the lower fitting 18.

A rubber elastic body 14 is interposed between the first support metal fitting 10 and the second support metal fitting 12, and the rubber elastic body 14 is used to connect the both metal fittings 10, 1.
2 are elastically connected. Such rubber elastic body 14
Has a tapered cylindrical shape, and the outer peripheral surface of the cylindrical wall portion of the lower metal fitting 18 is fixed to the opening end surface on the small diameter side, while the second end relative to the opening end surface on the large diameter side. The end face in the axial direction of the support metal fitting 12 is fixed. That is, the rubber elastic body 14 is formed as an integrally vulcanized molded product having the lower metal fitting 18 and the second support metal fitting 12.

The rubber elastic body 14 connects the first support metal fitting 10 and the second support metal fitting 12 so that the inner hole of the second support metal fitting 12 is provided between the first support metal fitting 10 and the second support metal fitting 12. A recess 26 that is open to the bottom is formed.

Further, inside the second support fitting 12,
A diaphragm 27 having a substantially thin disk shape is disposed at the opening of the recess 26. At the outer peripheral edge of the vibrating plate 27, an annular plate-shaped support rubber 2 spreading radially outward
The mounting ring 30 is attached via 8 and the mounting plate 30 is bolted to the second support fitting 12, so that the diaphragm 27 is attached to the second support fitting 12. ing. That is, this diaphragm 27
Is attached to the second support fitting 12 so as to be displaceable based on the elastic deformation of the support rubber 28.

By mounting the vibrating plate 27 on the second support fitting 12, the opening of the recess 26 is fluid-tightly covered. Then, a fluid chamber 32 in which a predetermined incompressible fluid is enclosed is formed therein. Examples of such an enclosed fluid include water and alkylene glycol,
Polyalkylene glycol, silicone oil and the like are preferably used.

That is, in the fluid chamber 32, a part of the wall portion thereof is constituted by the rubber elastic body 14, and the wall between the first support metal fitting 10 and the second support metal fitting 12 is provided. At the time of vibration input, the internal pressure fluctuation is caused based on the elastic deformation of the rubber elastic body 14.

On the other hand, the same incompressible fluid as the fluid chamber is sealed in the recess 25 side of the lower metal fitting 18 among the voids formed inside the first support metal fitting 10. As a result, the recess 25 of the lower metal fitting 18 forms an equilibrium chamber 34 in which the volume change is easily allowed due to the deformation of the flexible film 24. The space on the side of the recess 23 of the upper metal fitting 16 that is located on the opposite side of the equilibrium chamber 34 with the flexible film 24 sandwiched therebetween serves as an air chamber 36 that allows the deformation of the flexible film 24. There is.

Furthermore, the fluid chamber 32 and the equilibrium chamber 34
On the bottom wall portion of the lower metal fitting 18 that forms the partition wall for partitioning the and the disk metal fittings 38 are superposed and fixed by bolts.
The disc metal fitting 38 is provided with a circumferential groove 40 extending in the circumferential direction on the overlapping surface with the lower metal fitting 18. As a result, when they are stacked on the lower metal fitting 18, between the overlapping surfaces of the disk metal fitting 38 and the lower metal fitting 18,
It extends in a predetermined length in the circumferential direction, and both ends in the circumferential direction are communication holes 42, 44 provided in the lower metal fitting 18 and the disk metal fitting 38.
An orifice passage 46 communicating with the fluid chamber 32 or the equilibrium chamber 34 is formed therethrough.

When an internal pressure fluctuation is induced in the fluid chamber 32 at the time of vibration input, between the fluid chamber 32 and the equilibrium chamber 34,
By causing the fluid to flow through the orifice passage 46, a predetermined vibration isolation effect is exhibited based on the fluid flow action or resonance action. In the present embodiment, the length and cutoff of the orifice passage 46 are adjusted so that a high damping effect can be exerted when a low-frequency large-amplitude vibration such as a shake is input based on the resonance action of the fluid that is made to flow through the orifice passage 46. Area etc. are tuned.

Further, an electromagnetic drive means 48 is mounted on the second support fitting 12 and is arranged behind the vibrating plate 27 forming a part of the wall portion of the fluid chamber 32.

The electromagnetic drive means 48 has a circular block-shaped permanent magnet 50. The permanent magnet 50 is housed inside a bottom metal fitting 54 having a bottomed cylindrical shape with an outer flange portion 52 provided on the peripheral edge of the opening. The end faces on the magnetic pole side are arranged in contact with each other.

On the other magnetic pole side end surface of the permanent magnet 50, the end fitting 5 having a substantially thick disk shape is formed.
6 are arranged in contact with each other. Here, the outer diameter of the end fitting 56 is larger than that of the permanent magnet 50 and smaller than the inner diameter of the cylindrical wall portion of the bottom fitting 54, and is a predetermined dimension radially outward from the permanent magnet 50. It is made to project by. The end fitting 56 and the bottom fitting 54 are connected and fixed by a plurality of fixing bolts 58, so that the permanent magnet 50 is clamped and fixed between the fittings 56 and 54. .

Further, a substantially annular peripheral edge metal fitting 60 is disposed in the opening of the bottom metal fitting 54 and is fixed by a bolt. The peripheral metal fitting 60 is positioned so as to project inward in the radial direction at the opening of the bottom metal fitting 54, and its outer peripheral surface is brought into contact with the bottom metal fitting 54, while its inner peripheral surface is an end portion. It is made to face the outer peripheral surface of the metal fitting 56 at a predetermined distance in the radial direction.

The bottom metal fitting 54, the end metal fitting 56 and the peripheral metal fitting 60 are all made of a ferromagnetic material such as iron. Thereby, around the permanent magnet 50,
A magnetic path having a substantially closed magnetic path shape is formed, and an annular or cylindrical gap continuous in the circumferential direction is provided between the radially facing surfaces of the end fitting 56 and the peripheral fitting 60 located on the magnetic path. The part 62 is formed.

As is apparent from this, in the present embodiment, the bottom metal fitting 54 and the peripheral metal fitting 60 constitute the first yoke forming the magnetic path, while the end metal fitting 56 forms the magnetic field. A second yoke is formed that defines the path. Further, the fixing bolt 58 connecting the bottom metal fitting 54 and the end metal fitting 56 is made of a non-magnetic material such as an aluminum alloy to prevent short circuit of the magnetic path.

Further, the end fitting 5 for forming such a magnetic path.
A movable member 64 made of a non-magnetic material such as a synthetic resin or an aluminum alloy is arranged on the surface 6 at a predetermined distance. The movable member 64 is formed to have a substantially bottomed cylindrical shape as a whole, and the cylindrical tube wall portion 6 is formed.
6 is inserted and positioned in the gap portion 62 on the magnetic path. Then, the cylindrical wall portion 6 of the movable member 64.
A slight gap is formed between 6 and the facing surface forming the gap portion 62, whereby the movable member 64 can be displaced in the axial direction.

A ring-shaped or cylindrical movable coil 68 is disposed in the gap portion 62 in which the cylindrical wall portion 66 of the movable member 64 is positioned. It is fixed to the outer peripheral surface of the wall portion 66. As a result, the movable coil 68 and the movable member 64 can be integrally displaced within the gap portion 62. In the figure, reference numeral 70 denotes a power supply lead wire of the movable coil 68, which is guided inside through a through hole 72 provided in the bottom metal fitting 54.

In particular, in this embodiment, the axial length of the movable coil 68 is set to be shorter than the peripheral metal fitting 60 forming the gap portion 62 by a predetermined dimension, and in the gap portion 62 as will be described later. Even when the movable coil 68 is displaced, the movable coil 68 does not protrude beyond the axial end of the peripheral metal fitting 60. That is, thereby, even when the movable coil 68 is displaced, the movable coil 68 is
On the other hand, a substantially constant magnetic flux density is exerted.

In the electromagnetic drive means 48 thus formed, as shown in the drawing, the outer flange portion 52 of the bottom metal fitting 54 is superposed on the axial end surface of the second support metal fitting 12 and is bolted. In addition to being fixed, the movable member 64 is integrally assembled by being superposed on the back surface of the diaphragm 27 and fixed by bolts. Further, in such an assembled state, the movable coil 68 mounted on the movable member 64 is positioned at a substantially central portion on the gap portion 62 of the magnetic path in the electromagnetic drive means 48.

Therefore, in the engine mount having the above-described structure, by applying an alternating current to the movable coil 68, an electromagnetic force (Lorentz force) according to Fleming's left-hand rule is generated on the movable coil 68. As a result, a driving force proportional to the current is exerted on the diaphragm 27 via the movable member 64 to which the movable coil 68 is attached. The energization of the movable coil 68 is controlled, and the internal pressure of the fluid chamber 32 can be controlled by vibrating the vibrating plate 27 according to the internal pressure variation of the fluid chamber 32 caused by the input vibration. Therefore, it becomes possible to appropriately change the vibration damping characteristics of the mount.

Specifically, for example, when a low frequency vibration is input, the diaphragm 27 is vibrated in the same phase as the input vibration,
By positively generating the internal pressure of the fluid chamber 32 and increasing the flow rate of the fluid that is made to flow through the orifice passage 46, high damping characteristics can be exhibited, and the input of medium to high frequency vibrations can be achieved. At times, the vibration plate 27 is vibrated in the opposite phase to the input vibration, and the fluid chamber 32
By absorbing or reducing the internal pressure of, the low dynamic spring characteristics can be exhibited.

In particular, in such an engine mount, since the magnetic field in the region in which the movable coil 68 is arranged is formed by the gap portion 62 on the closed magnetic path, the magnetic flux density thereat is sufficient. And it can be easily secured. Thereby, the moving coil 68
On the other hand, since a large magnetic flux density is exerted, a large electromagnetic force is generated, and it is possible to sufficiently secure the driving force of the diaphragm 27 with a compact mount structure, and to secure the driving force of the fluid chamber. Since the internal pressure can be effectively controlled, the intended vibration damping property can be sufficiently exhibited.

Further, since the magnetic field in the region where the movable coil 68 is disposed is formed by the gap 62 on the closed magnetic path, the magnetic flux density in the region can be made uniform, and the movable coil 68 can be achieved. The magnetic flux density exerted on the movable coil 68 even when is displaced,
The generated electromagnetic force can be maintained at a substantially constant value.
Therefore, since it becomes possible to stably obtain an electromagnetic force substantially proportional to the amount of current flowing through the movable coil 68, it becomes easy to control the vibration of the movable coil 68, and hence the diaphragm 27, and The occurrence of distortion can be effectively prevented, which makes it possible to control the internal pressure of the fluid chamber 32 to a high degree of precision, and the desired vibration damping characteristics can be exhibited more highly and stably. Of.

In addition, since the vibration control of the diaphragm 27 can be performed with high accuracy and the distortion of the pulsation (internal pressure fluctuation) generated in the fluid chamber 32 is reduced or prevented, such distortion is prevented. Therefore, problems such as amplification of vibration in a region other than the frequency for the purpose of image stabilization are not a problem.

Incidentally, Table 1 below shows the experimental results of measuring the vibration-damping characteristics of the engine mount having the above-mentioned structure. In the experiment, the static spring constant: Ks = 24.0 (kg / mm) was used, and the dynamic spring constant was K * (kg / mm) with and without vibration control of the diaphragm 27. mm) and phase angle: δ (de
g) was measured under the same vibration input conditions, and the effect of improving the vibration damping characteristics was evaluated by the reduction rate of the dynamic spring constant.

[0040]

[Table 1]

From the results shown in Table 1 above, the engine mount having the structure of this embodiment has excellent anti-vibration characteristics against input vibrations in a wide frequency range from idling vibrations to chilling noises and engine secondary vibrations. It is understood that it can be demonstrated and can be sufficiently put to practical use.

The embodiments of the present invention have been described in detail above, but these are literal examples and the present invention should not be construed as being limited to such specific examples.

For example, in the above-described embodiment, the equilibrium chamber 3 which is in communication with the fluid chamber 32 through the orifice passage 46.
However, the orifice passage and the equilibrium chamber are not necessarily provided.

Even in the mounting device having neither the orifice passage nor the equilibrium chamber, the effect as described above based on the switching control of the vibration damping characteristics is effectively exhibited by controlling the internal pressure of the fluid chamber. You will get it.

Further, the structure of the yoke portion for forming the magnetic path including the permanent magnet is not construed as being limited to that of the above-mentioned embodiment, and the shape and size of the mount device required are required. It can be appropriately changed according to the above.

Furthermore, in order to maintain the magnetic flux density exerted on the movable coil at a substantially constant value more advantageously even when the movable coil is displaced, for example, as shown in FIG. Yoke members 76, 7 forming part 74
A moving coil 80 that is sufficiently longer than the axial length of 8 is adopted, or as shown in FIG.
It is also effective to employ the movable coil 82 that is sufficiently shorter than the axial length of the yoke members 76 and 78 forming the No. 4 in consideration of the displacement amount thereof.

In addition, in the above-described embodiment, a specific example of the present invention applied to an engine mount for an automobile is shown. However, in addition to this, vibration isolation in an automobile body mount, a differential mount, or various devices other than the automobile Of course, the same can be applied to the connection or support mounting device.

Although not listed one by one, the present invention is
Based on the knowledge of those skilled in the art, it can be implemented in various modified, modified, and improved modes, and
It goes without saying that all such embodiments are included within the scope of the present invention, without departing from the spirit of the present invention.

[0049]

As is apparent from the above description, in the fluid-filled mount device having the structure according to the present invention, the region in which the movable coil is arranged has a closed magnetic circuit shape. On the road, since the yokes are formed as the gap portions that are positioned to face each other, a sufficient and uniform magnetic flux density can be secured in such a region.

As a result, a large magnetic flux density is exerted on the movable coil, so that a large driving force can be exerted on the diaphragm when the movable coil is energized. Moreover, even when the movable coil is displaced, A change in the magnetic flux density exerted thereon can be prevented, and a stable driving force can be exerted.

Therefore, in the fluid-filled mount device according to the present invention, the vibration of the diaphragm can be stably performed with a sufficient driving force, and its control is easy. The desired anti-vibration property can be exhibited highly and stably.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view showing an automobile engine mount as one embodiment of the present invention.

FIG. 2 is an explanatory view schematically showing an example of the arrangement of the movable coil in the gap portion, which is preferably adopted in the mount device according to the present invention.

FIG. 3 is an explanatory view schematically showing another example of the arrangement of the movable coil in the gap portion, which is preferably adopted in the mount device according to the present invention.

[Explanation of symbols]

 10 1st support metal fittings 12 2nd support metal fittings 14 Rubber elastic body 27 Vibration plate 28 Support rubber 32 Fluid chamber 48 Electromagnetic drive means 50 Permanent magnet 54 Bottom metal fittings 56 End metal fittings 60 Peripheral metal fittings 62 Gap part 64 Movable member 66 Tube Wall part 68 Moving coil 74 Gap part 76,78 Yoke member 80,82 Moving coil

Claims (1)

(57) [Claims] 1. A fluid chamber in which a first non-compressible fluid is sealed and a first supporting metal member and a second supporting metal member are respectively fixed to both side portions of a rubber elastic body facing in a vibration input direction. In the fluid-filled mount device in which a part of the wall portion is provided by such a rubber elastic body, a part of the wall portion of the fluid chamber is displaceably supported by the second support fitting. And a first magnet and a second yoke are respectively connected to both poles of the permanent magnet, and the first yoke and the second yoke are connected to the first yoke. And forming a magnetic path having an annular gap between the end facing surfaces of the second yoke and
Further, a ring-shaped movable coil extending in the circumferential direction along the gap portion is disposed so as to be displaceable, the movable coil is connected to the diaphragm, and the diaphragm is applied by energizing the movable coil. A fluid-filled mount device characterized by being shaken.