JPH09257092A - Vibration control support device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent centralization of a stress to an elastic member to maintain a moving plate in a given position based on an actuator to drive a moving plate and ensure or improve durable performance through suppression and prevention of the occurrence of fatigue thereof, in a vibration control support device to constitute a fluid chamber in a support elastic body located between a vibration body, such as an engine, and a support body, such as a car body, and actively damp vibration from the vibration body by fluctuating the volume of a fluid chamber by fluctuating the volume of the fluid chamber by the moving plate. SOLUTION: A receiving part 55 on the moving plate side consisting of a recessed part extending along a peripheral direction is formed at the outer peripheral end part of the under surface of a moving plate 46 and mail, an receiving part 58 on the actuator side consisting of the recessed part extending along a peripheral direction in a similar manner above-mentioned is formed at the outer peripheral end part of the yoke 52a of an electromagnetic actuator 52. An elastic member 48 consisting of a corrugation board-form wave spring 48a being formed in an annular shape but partially discontinued is contained in a gap between the two receiving parts 55 and 58. A vertical contact end part is rendered peripherally slidable along with compression deformation.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for supporting a vibrating body such as an engine of a vehicle on a support such as a vehicle body while isolating the vibration, and more particularly to a device for supporting a fluid by a vibrating body and a support elastic body interposed between the supports. The present invention relates to a vibration isolation support device that defines a chamber and actively changes the volume of the fluid chamber to reduce the vibration transmissibility.

[0002]

2. Description of the Related Art An example of such an anti-vibration support device is disclosed in Japanese Patent Application Laid-Open No. 7-269645. This anti-vibration support device relates to, for example, a device that supports a vehicle engine on a vehicle body, and is a fluid chamber (working chamber) formed between a support elastic body (expansion spring) and a storage body (outer shell). And a variable volume sub-fluid chamber which communicates with the fluid chamber through an orifice (buffer hole) and is defined by a diaphragm (bellow), and a direction which is disposed in the fluid chamber and changes the volume of the fluid chamber. A movable plate (vibration plate) that is actively displaced in the direction, an actuator (magnet body) that displaces the movable plate in the volume change direction of the fluid chamber, and to maintain the movable plate at a predetermined position with respect to the actuator And a ring-shaped leaf spring (plate-shaped elastic member) interposed between the movable plate and the storage body and elastically supporting the movable plate on the storage body. Of course, although not disclosed in the publication, vibrations transmitted from the vibrating body to the support body are reduced by driving the actuator to displace the movable plate and consequently changing the volume of the fluid chamber. Therefore, the control means for supplying the control signal to the actuator is essential. By the way, in this anti-vibration support device, a rubber seal member is disposed between the movable plate and the housing so that the actuator is separated from the fluid chamber by the movable plate including the plate spring. .
However, this seal member may be arranged between the movable plate and the actuator. The outer peripheral edge portion of the ring-shaped leaf spring is tightly fitted and fixed in the recess formed in the housing, and the inner peripheral edge portion is in contact with the movable plate.

Further, according to this vibration isolating support device, for a vibration input of a comparatively low frequency capable of moving the fluid between the fluid chamber and the sub-fluid chamber through the orifice, for example, an engine shake, the orifice concerned. Due to the fluid resonance in the inside, it becomes a vibration damping support device with a high dynamic spring constant and a high damping force, while when a vibration of a relatively high frequency that makes movement of the fluid through the orifice impossible is input, By displacing the movable plate so as to cancel the pressure fluctuation of the fluid due to the vibration input, the volume in the fluid chamber changes and the vibration damping support device has a low dynamic spring constant. That is, according to the above-described conventional vibration-damping support device, it is possible to prevent vibration from both a low-frequency vibration input requiring a high dynamic spring constant and high damping and a high-frequency vibration input requiring a low dynamic spring constant. A vibration effect is obtained.

[0004]

By the way, in order to fix the outer peripheral edge portion of the leaf spring formed in the ring shape to the housing as described above, for example, both sides of the leaf spring (the conventional vibration-proof support) are used. In the device, it is necessary that the side surface of the fluid chamber and the side surface of the actuator) are firmly fixed to each other by interference fitting or caulking. However, since this leaf spring is deformed along with the displacement of the movable plate, if the outer peripheral edge portion of the leaf spring thus formed in a ring shape is firmly sandwiched between the storage bodies, Stress concentration occurs at the sandwiched end portion, that is, at the fixed inner end portion of the leaf spring formed in a ring shape, and the local stress generated at that portion is likely to increase. Moreover, this stress concentration is constantly repeated during the operation of the actuator, which may cause fatigue of the leaf spring. Therefore, when a large displacement is required for the movable plate, the stress generated in the plate spring also becomes large, which causes a problem in the durability performance of the vibration-proof support device.

In order to solve such a problem, by increasing the width of the ring-shaped leaf spring, the generated stress is relatively small even if the displacement of the movable plate is the same. Therefore, it is possible to secure the durability performance as the vibration isolation support device. However, enlarging the width of the leaf spring in this manner is substantially limited because it is necessary to increase the size of the container itself while ensuring the equivalent fluid chamber volume variation capability of the movable plate. In large vehicle spaces, it may not be possible to place such a large anti-vibration support device.

This problem similarly occurs when the inner peripheral edge of the ring-shaped leaf spring is fixed to the movable plate. The present invention has been developed in view of these problems, and it is an object of the present invention to provide an anti-vibration support device capable of improving the durability performance by reducing the stress generated in the elastic member without increasing the size of the container. It is intended.

[0007]

In order to solve the above problems, a vibration isolating support device according to a first aspect of the present invention comprises a vibrating body and a supporting elastic body interposed between the supporting bodies, and the supporting elastic body. And a fluid chamber defined in the supporting elastic body and having a fluid enclosed therein, and a direction that forms a part of the partition wall of the fluid chamber and changes the volume of the fluid chamber. A movable plate that can be displaced, an actuator that is disposed in the housing to apply a displacement force to the movable plate, and a control signal to the actuator to reduce the vibration transmitted from the vibrating body to the support body. A supply control unit and a corrugated plate-like member that is interposed between the movable plate and the storage body or between the movable plate and the actuator to maintain the movable plate at a predetermined position with respect to the actuator. The elastic member and the actuator Is characterized in that a seal member disposed between said movable plate and housing body or actuator to isolate over data from the fluid chamber.

According to a second aspect of the present invention, there is provided a vibration isolating support device, wherein the vibrating body side connecting member is connected to the vibrating body, the supporting body side connecting member is connected to the supporting body, and the vibrating body side connecting member or A support elastic body connected to any one of the support side connecting members, a storage body connected between the support elastic body and the other of the vibrating body side connecting member or the support side connecting member, and the support elastic body. A fluid chamber defined in the body and having a fluid enclosed therein; a magnetizable movable plate that forms a part of a partition wall of the fluid chamber and is displaceable in a direction that changes the volume of the fluid chamber; An actuator that is disposed in the housing and that generates a magnetic force to apply a displacement force to the movable plate, and control means that supplies a control signal to the actuator so as to reduce the vibration transmitted from the vibrating body to the support body. And the A seal member disposed between the movable plate and the container or the actuator to separate the user from the fluid chamber, a movable plate side receiving portion formed on the movable plate, and the container or the actuator. The formed storage body or actuator side receiving portion, and the movable plate side end portion is movably supported by the movable plate side receiving portion in order to maintain the movable plate at a predetermined position with respect to the actuator, and the storage body or actuator. A corrugated plate-like elastic member whose side end is movably supported by the storage body or the actuator-side receiving portion and which is annular but is not continuous in part is provided.

In any of the above-mentioned inventions, in any of the vibration-proof support devices, as the elastic member for maintaining the movable plate at a predetermined position, a corrugated plate-like elastic member which is annular but not partially continuous, so-called. Use a wave spring. This wave plate-shaped elastic member, called a wave spring, obtains elastic force by deforming the wave of the wave plate in a direction in which the amplitude of the wave decreases, that is, in the compression direction. If the value portion is brought into contact with the movable plate side, the minimum value portion of the amplitude of the wave is brought into contact with the storage body side or the actuator side, and the compressive elastic force of the elastic member is obtained when the both approaches each other. To use. Incidentally, this annular corrugated plate-like elastic member expands in the circumferential direction when it is compressed and deformed so that the amplitude of the wave becomes small as described above. However, the end of the discontinuous portion is absorbed by moving in the circumferential direction. And
The contact end (movable plate side end) on the movable plate side of such a ring-shaped corrugated elastic member is formed on the movable plate as in the vibration isolating support device according to claim 2, for example. The elastic member is movably supported, and the contact end of the elastic member on the housing or actuator side (housing or actuator contact end) is also formed on the housing or actuator. When the elastic member is movably supported in the circumferential direction and the elastic member extends in the circumferential direction along with the compressive deformation of the annular corrugated elastic member, the movable plate side end of the elastic member and the housing or actuator. The compressive elastic force is exerted on the elastic member while the side end portion slides. Therefore, since this corrugated plate-like elastic member develops a compressive elastic force without stress concentration anywhere, it is possible to avoid fatigue due to repetition when the movable plate is vibrated as described above. Therefore, durability performance can be secured or improved without increasing the size of the device.

According to a third aspect of the present invention, in the vibration-damping support device, the elastic member is arranged in the fluid chamber, and the movable plate is supported from the fluid chamber side with respect to the actuator. It is a feature.

According to a fourth aspect of the present invention, the vibration-damping support device is characterized in that the elastic member is disposed between the movable plate and the actuator, and the movable plate is supported from the actuator side. It is what

In these inventions, both contact ends of the ring-shaped corrugated elastic member of the vibration-damping support device according to claim 1 or 2 are movably supported. For example, since it is sufficient to provide a reaction force that simply maintains the movable plate at a predetermined position with respect to the attraction force of the movable plate such as a permanent magnet, it is arranged on the fluid chamber side, for example. Alternatively, it may be arranged on the actuator side. As a result, the flexibility of the layout of the annular corrugated elastic member is increased, and fine tuning according to the vehicle characteristics is enabled.

[0013]

As described above, according to the vibration isolating support device of the first aspect of the present invention, the corrugated plate-like elastic member interposed between the movable plate and the housing or the actuator is circumferentially arranged. Since the compressive elastic force is expressed while stretching, stress concentration does not occur in this corrugated elastic member, and fatigue due to repetition can be avoided, so vibration-proof support without increasing the size of the device. The durability performance of the device can be secured or improved.

According to a second aspect of the present invention, the movable plate side end portion of the corrugated plate-like elastic member, which is annular but is not partially continuous, is provided on the movable plate side. , And when the housing or the actuator-side contact end portion is movably supported on the housing or the actuator side, respectively, when the annular corrugated plate-like elastic member is stretched in the circumferential direction while being compressed and deformed, Since the compressive elastic force is developed in the elastic member while the movable plate side end of the elastic member and the housing or actuator side end slide, stress concentration does not occur in this corrugated elastic member, Since fatigue due to can also be avoided, the durability performance as the vibration-proof support device can be secured or improved without increasing the size of the device.

According to the vibration isolating support device of the third or fourth aspect of the present invention, the annular corrugated plate-like elastic member is simply applied to a movable plate attracting force such as a permanent magnet. As long as it provides a reaction force for maintaining the movable plate at a predetermined position, it may be arranged on the fluid chamber side or the actuator side, for example.
As a result, the flexibility of the layout of the annular corrugated elastic member is increased, and fine tuning according to the vehicle characteristics is enabled.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a first embodiment of the present invention will be described with reference to the drawings. 1 is a so-called active engine mount (hereinafter, simply referred to as an engine mount) in which the vibration isolating support device according to the present invention actively reduces vibration transmitted from an engine side as a vibrating body to a vehicle body side member.
It is applied to

An engine mount designated by the reference numeral 20 in FIG. 1 is provided on the rear side of the vehicle body of an engine 22 mounted horizontally, and an upper portion of the engine mount serves as a support body fixed to a bracket 24 on the engine side and a lower body serves as a support body fixed to a vehicle body 26. Is attached to the member 28.

2 to 6 show a concrete structure of an engine mount 20 in which the vibration-damping support device according to claims 1 and 2 of the present invention is embodied. The engine mounts 20 are parallel to each other. A connecting member (vibrating body side connecting member) 30 having two engine-side mounting bolts 30a spaced apart from each other is fixed upward, and a hollow cylindrical portion 30b having an inverted trapezoidal cross section is provided below the connecting member 30. Is fixed. A support elastic body 32 is provided on the lower surface side of the connecting member 30 so as to cover the periphery of the connecting member 30 and the hollow cylindrical portion 30b.
Are fixed by vulcanization adhesion.

The support elastic body 32 is an elastic body having a substantially conical cylindrical shape having a wall thickness that is gently inclined downward from the central portion toward the outer peripheral portion, and the outer peripheral surface thereof has an axial center of the hollow cylindrical portion. Thirty
It is joined by vulcanization adhesion to the inner peripheral surface of the inner cylinder (first cylindrical member) 34 which is coaxial with b and faces the vibrating body supporting direction (in this case, the vertical direction).

As shown in FIG. 2, the inner cylinder 34 is gradually reduced in diameter from an upper end cylinder portion 34a to form an inclined portion 34b, and an inclined portion 34b is formed. A small-diameter tubular portion 34c having a smaller diameter than the tubular portion 34a is formed. An annular portion 34d is formed radially outward from the lower end of the small-diameter tubular portion 34c, and the upper end tubular portion 3 extends downward from the outer peripheral end of the annular portion 34d.
A lower end tubular portion 34e having the same outer diameter as that of 4a is formed. . The small-diameter cylindrical portion 34c has a first opening hole 34f and a second opening hole 34g formed at positions symmetrical to each other with respect to the axis.

A thin film elastic body 32a continuous from the lower side of the supporting elastic body 32 is joined to the inner peripheral surfaces of the inclined portion 34b of the inner cylinder 34 and the small diameter cylindrical portion 34c, and this thin film elastic body 32a. Further extends to the annular portion 34d side and the lower end tubular portion 34e side of the inner cylinder 34, and is coupled to the inner peripheral surfaces of the annular portion 34d and the lower end tubular portion 34e. Here, the lower end portion of the thin film elastic body 32a has a thickened shape.

The thin film elastic body 32a has the first opening 3
4f is closed to form the first diaphragm 32c. Further, the second opening hole 34g is opened without being blocked by the thin film elastic body 32a.

A hollow portion 32b having a mountain-shaped cross section which forms a fluid chamber is formed inside the support elastic body 32.
The first orifice constituting member 36 is fitted in the inner cylinder 34 (strictly, inside the thin film elastic body 32a) so as to be positioned below the hollow portion 32b.

The first orifice constituting member 36 is provided with a minimum diameter tubular portion 36a formed to have a diameter smaller than that of the small diameter tubular portion 34c of the inner cylinder 34. It is a tubular member on which annular portions 36b and 36c are formed. The outer peripheral diameter of the upper annular portion 36b is the inner cylinder 3
It is formed to have a diameter slightly smaller than that of the small-diameter cylindrical portion 34c of No. 4. The annular portion 36c of the lower side, with has a smaller diameter than the lower cylindrical portion 34e of the inner cylinder 34, the cylindrical end portion 36c ₁ is formed downward from the outer peripheral edge. Further, a third opening hole 36d is formed in the minimum diameter cylindrical portion 36a at a position facing the second opening hole 34g formed in the inner cylinder 34.

Here, the lower end portion of the thin film elastic body 32a having the increased thickness as described above has a lower end tubular portion 34e of the inner tube 34.
By being sandwiched between the first orifice component member 36 and the tubular end portion 36c ₁ , the first orifice component member 36 is slightly compressed downward in the radial direction while being compressed.

Further, as shown in FIG. 2 or 7, at the lower end of the minimum diameter cylindrical portion 36a corresponding to the annular portion 36c of the first orifice constituting member 36, the bottom portion of the minimum diameter cylindrical portion 36a. 36e is formed. This bottom 36e
Forms a part of the circular bottom plate of the minimum diameter cylindrical portion 36c at the same height as the annular portion 36c, but in reality, a communication hole 36g is formed in the central portion thereof, which will be described later. The first orifice 68A and the first sub fluid chamber 68B communicate with each other. Further, at the outer peripheral end of the upper surface of the bottom portion 36e, a container-side receiving portion 36f formed of a recess having a rectangular cross section along the circumference thereof is formed.

On the other hand, a plurality of leg members 53 for connecting a later-described movable plate 46 are inserted into the communication holes 36g of the bottom portion 36e. A male screw portion 53a is formed on the lower end portion of the leg member 53, a small diameter portion 53b having a smaller diameter than the lower portion is formed on the upper end portion thereof, and a female screw portion 53c is formed on the upper surface thereof. A disc-shaped flat plate member 55a is fixed to the small diameter portion 53b of each leg member 53. In this flat plate member 55a, each small diameter portion 53b of the leg member 53 is fitted into each through hole formed in the flat plate member 55a from below, and then a screw member 57 is screwed into the female screw portion 53c from above. And is fixed to the leg member 53. A movable plate side receiving portion 55, which is a recess having a rectangular cross section along the circumferential direction, is formed on the outer peripheral end of the lower surface of the flat plate member 55a. A communication hole 55c similar to the bottom portion 36e is also formed in the central portion of the flat plate member 55a, and a first orifice 68 described later is formed.
It is configured so as not to prevent communication between A and the first sub-fluid chamber 68B.

An elastic member composed of an annular wave plate-shaped wave spring 48a, which will be described later, is provided in the annular gap having a rectangular cross section between the movable plate side receiving portion 55 and the storage body side receiving portion 36f. 48 is interposed. By the way, since the leg member 53 is fixed to the movable plate 46 described later and the first orifice constituting member 36 is fixed to the actuator case 42 which constitutes the storage body together with the actuator sub-case described later, the first spring constituent member 36 is separated from the wave spring 48a. It can be said that the elastic member 48 is interposed between the movable plate and the storage body. The closed space between the cavity 32b of the support elastic body 32 and the movable plate 46, which will be described later, serves as the main fluid chamber 66 in which the fluid is sealed. Therefore, the elastic member 48 including the wave spring 48a is arranged in the fluid chamber. Will be installed. The operation of the elastic member 48 formed of the annular wave plate-shaped wave spring 48a will be described in detail later, but a brief description thereof will be given here. In FIG. 2 or FIG. Is attracted to the electromagnetic actuator 52 side, and as a result, the flat plate member 55a fixed to the movable plate 46 approaches the bottom portion 36e of the first orifice component 36 extending from the container, that is, the movable plate. Side receiving part 55
When approaching the storage body side receiving portion 36f and the gap between them becomes smaller, the elastic member 48 composed of the wave spring 48a exerts compressive elastic force by compressive deformation.

On the other hand, an outer cylinder 38 as a second cylindrical member is fitted on the inner cylinder 34, and between the inner cylinder 34 and the outer cylinder 38, an inclined portion 34b of the inner cylinder 34 is provided. An annular space is defined in the circumferential direction by surrounding the recess formed by the outer surfaces of the small-diameter cylindrical portion 34c and the annular portion 34d with the inner peripheral surface of the outer cylinder 38. The second orifice component 40 and the second diaphragm 43 are arranged in this annular space.

That is, the outer cylinder 38 has a cylindrical member whose inner peripheral diameter is the same as or slightly larger than the outer peripheral diameter of the inner cylinder 34 and whose axial length is the same as the inner cylinder 34. A thin liquid-tight sealing material 38a made of an elastic body is joined to the inner peripheral surface of the sealing material 38a. A substantially rectangular opening 38b, which is long in the circumferential direction, is formed at a substantially central portion in the height direction of the outer cylinder 38 so as to face a substantially one-third portion of the concave portion. The second diaphragm 43 is attached in 38b. The second diaphragm 43 is a rubber-like thin film elastic body, and as shown in FIG. 5, for example, is coupled to the entire circumference of the opening edge of the opening 38b to close the opening 38b, and Part 3
It is arranged in a state of bulging from 8b toward approximately 1/3 of the recess.

Further, the second orifice constituting member 40
Are disposed in the remaining annular space (an annular space corresponding to approximately ⅔ of the recess) that has become a small space due to the disposition of the second diaphragm 43, and is clearly shown in FIGS. 5 and 6. As described above, the partition wall member 40a and the passage forming member 40b are made of a hard elastic body.

Of these, the partition member 40a closes the annular space in the annular space adjacent to the one end 43a in the longitudinal direction of the second diaphragm 43 which is elongated in the circumferential direction according to the shape of the opening 38b. So as to fit between the inner cylinder 34 and the outer cylinder 38.
The second diaphragm 43 from the annular space side by 0a.
Fluid flow to the side is blocked.

The passage forming member 40b is separated from the partition wall member 40a by a predetermined distance (hereinafter, the end portion corresponding to this position will be referred to as a partition wall member side end portion) in the longitudinal direction of the second diaphragm. Is continuously formed in the annular space up to a position (hereinafter, an end corresponding to this position is referred to as a diaphragm side end) close to the other end 43c of the. Then, a second passage 40b ₂ that communicates from the partition member member side end portion to the diaphragm side end portion along the circumferential direction above the passage forming member 40b,
A first passage 40b ₁ that communicates from the partition member side end portion to the second opening hole 34g of the inner cylinder 34 is also formed below the same along the circumferential direction. Note that the second
The length of the passage 40b ₂ is about 2 times the length of the first passage 40b _1.
It is set to double.

The upper side of the actuator case 42 is externally fitted to the outer cylinder 38 containing these constituent members. The actuator case 42 has an upper end crimped portion 42a having a circular opening with a diameter smaller than the outer peripheral diameter of the inner cylinder 34 formed at the upper end portion, and the shape of the case body continuous with the upper end crimped portion 42a is This is a member having a cylindrical shape whose peripheral diameter is the same as the outer peripheral diameter of the outer cylinder 38 and continues to the lower end opening (the lower end opening is shown by the broken line in FIG. 2). Then, the support elastic body 32 and the inner cylinder 3
The outer cylinder 38 integrated with 4 is fitted into the actuator case 42 through the lower end opening so that the support elastic body 32 is located above, and the outer cylinder 38 and the inner cylinder 38 are attached to the lower surface of the upper end caulking portion 42a. The upper ends of the cylinders 34 come into contact with each other, so that they are arranged in the upper portion of the actuator case 42. Here, as shown in FIGS. 2 and 5, an air chamber 43b is defined in a portion surrounded by the inner peripheral surface of the actuator case 42 and the second diaphragm 43. An air hole 42c is formed at a position facing the air chamber 43b, and the air chamber 43b communicates with the atmosphere via the air hole 42c.

On the other hand, the actuator sub case 41 is fitted inside the lower space of the actuator case 42 formed as described above. The actuator sub-case 41 forms a part of the housing according to the present invention, and its appearance is a bottomed cylindrical shape having an outer diameter that fits tightly into the lower space of the actuator case 42, and its uppermost end. The portion is folded back inward to form a locking portion 41a.

Then, this actuator sub case 4
An electromagnetic actuator 52 is disposed below the unit 1.
The electromagnetic actuator 52 has a structure similar to that of an existing electromagnetic actuator, and as a whole, the cylindrical yoke 5 that is tightly fitted in the actuator sub case 41.
2a, an exciting coil 52b housed in a groove formed in a ring shape from the upper surface of the yoke 52a, and a permanent magnet housed in a recess formed inside the groove housing the exciting coil 52b. It is composed of a magnet 52c. Incidentally, a part of the side surface of the yoke 52a (the left end portion in FIG. 2).
Is formed with a groove-shaped communication passage 52d continuous from the upper surface of the yoke 52a, and a third diaphragm 51 is attached to an opening on the side surface of the actuator sub case 41 facing the communication passage 52d. The side surface of the actuator case 42 facing the third diaphragm 51 has an opening 42d that communicates with the outside. The operation of the third diaphragm 51 will be described later in detail.

Then, a gap holding ring 50 having a predetermined height is placed on the outer peripheral portion of the upper surface of the yoke 52a of the electromagnetic actuator 52, and a disc-like shape is provided inside the gap holding ring 50 with a rubber seal member 49 interposed therebetween. The outer peripheral surface of the movable plate 46 made of a magnetic material is movably supported. Of these, the gap retaining ring 50 has a length in the axial direction, so that a predetermined gap is provided between the lower surface of the movable plate 46 and the upper surface of the electromagnetic actuator 52. The annular member is set to a value obtained by adding the dimension of the gap to the axial length from the bottom to the lower surface. The rubber seal member 49 keeps the movable plate 46 and the electromagnetic actuator 52 in a liquid-tight state, and the movable plate 46 moves at least in the direction in which the electromagnetic actuator 52 exerts the attraction force, that is, in the vertical direction in FIG. Possibly supported by the gap retaining ring 50.

Further, the gap retaining ring 50 is
After the spacer 47 having a predetermined thickness is placed on the upper surface of the above, the uppermost end of the actuator sub case 41 is folded back inward to form the locking portion 41a.

As described above, the spring member 48 and the movable plate 4 are
6. After the electromagnetic actuator 52 and the like are installed inside the actuator sub case 41, the tubular end portion 36c ₁ corresponding to the lowermost end portion of the first orifice component 36 is attached to the locking portion 41a of the actuator sub case 41. The leg member 53 is placed in the communication hole 36g formed in the bottom portion 36e of the first orifice component 36, and the male screw portion 53a formed at the lower end portion thereof is attached to the movable plate 46.
Is screwed into a female screw portion 46b formed on the upper surface of the plate, and thereafter, the flat plate member 55a is integrated with the movable plate 46 as described above, and the ring-shaped wave spring 48a is formed. The elastic member 48 is interposed between the movable plate side receiving portion 55 and the storage body side receiving portion 36f.

The actuator sub case 41 assembled in this way is inserted into the space below the outer cylinder 38 below the actuator case 42, and the load sensor 54 is arranged below the actuator sub case 41. Below this, a vehicle body side connecting member (support body side connecting member) 56 having a substantially disc shape, in which two vehicle body side mounting bolts 56a that are spaced apart from each other are fixed downward, is provided, and then the lower end of the actuator case 42 is arranged. The portion is deformed inward in the radial direction to form the lower end crimped portion 42d as shown by the solid line in FIG.

In this way, the actuator case 42
When the lower end caulking portion 42d is formed on the lower end portion of the vehicle body, the peripheral edge portion of the vehicle body side connecting member 56 is fixed in a state of being covered from the outside. At this time, the actuator sub case 41 is attached to the outer cylinder 38.
Since it is pushed to the side, the lower end cylinder portion 34e of the inner cylinder 34
And lower ends of the first orifice component 36 of the tubular end portion 36c ₁ elastic film 32a extending from sandwiched is the resilient support member 32 is between the locking of the actuator sub-case 41 Since the upper surface of the portion 41 a is pressed upward and comes into close contact with the compressed state, the fluid in the main fluid chamber 66 constituted by the hollow portion 32 b of the support elastic body 32 and the movable plate 46 is transferred to the inner cylinder 34. It is possible to prevent leakage to the outside and the outside of the actuator sub case 41. Further, as will be described in detail later, the main fluid chamber 6
6 through the third opening hole 36d and the second opening hole 34g, and the first passage 40b _{1 of} the second orifice component member 40.
And fluid ranged second passage 40b ₂ is leaking to the outside of the outer tube 38 is sealed by a fluid-tight seal member 38a that is sandwiched and the inner cylinder 34 and the outer cylinder 38.

Further, as clearly shown in FIG. 7, the first orifice constituting member 36 and its receiving member side receiving member which are pressed against the locking portion 41a side of the actuator sub case 41 by the thin film elastic body 32a of the supporting elastic body 32. Part 36f
Are integrally fixed to the actuator sub-case 41 and the actuator case 42 that form the housing of the present invention. Further, the flat plate member 55a is integrally fixed to the movable plate 46. And in this state,
The movable plate side end portion of the elastic member 48 formed of the annular corrugated wave spring 48a, that is, the upper end portion of FIG. 2 or 7 is only in contact with the movable plate side receiving portion 55, Moreover, the end of the elastic member 48 on the side of the storage body, that is, FIG.
Alternatively, since the lower end portion of FIG. 7 is only in contact with the storage body side receiving portion 36f, the elastic member 48 including the annular and corrugated wave spring 48a is connected to the movable plate side receiving portion 55. Since the elastic member 48 can move in the circumferential direction in the annular gap having a rectangular cross section with the receiving portion 36f on the housing body side, the elastic member 48 also moves with respect to the movable plate 46.
Even for a storage body described later, it is movably supported at least in the circumferential direction.

By the way, in this embodiment, the electromagnetic actuator 52, the movable plate 46, etc. are installed in the actuator sub case 41.
The reason why it is housed inside is to improve the efficiency of the assembling work by the so-called sub-assembly process and to further improve the sealing property of each component that is reluctant to get wet with liquid. Therefore, as shown in FIG. 7, a thin film seal member 41b is attached to the inner peripheral surface of the actuator sub case 41 by coating or the like.
The leakage of fluid from the outer peripheral surface of 0 to the electromagnetic actuator 52 side is sealed.

Further, a rebound stopper 60 is fixed to the upper part of the actuator case 42. As shown in FIGS. 2 to 4, the bound stopper 60 extends between the two engine-side mounting bolts 30a extending upward from the connecting member 30 in a direction orthogonal to a line connecting the bolts. An extending stopper body 60a and a pair of stopper legs 6 that are gradually lowered from both ends of the stopper portion 60a and are coupled to the outer periphery of the actuator case 42.
It is a member provided with 0b. And engine mount 2
When the support elastic body 32 is excessively elastically deformed upward in the 0 rebound operation, the connection member 30 contacts the lower surface of the stopper portion 60a, so that the support elastic body 32 is prevented from being excessively deformed. It has become.

Next, the engine mount 20 of the present embodiment will be described.
The vibration input damping action of will be briefly described. In the engine mount 20 of the present embodiment, with respect to the main fluid chamber 66 constituted by the hollow portion 32b of the support elastic body 32, the inner peripheral surface of the first orifice constituting member 36 and the upper surface of the movable plate 46, The outer peripheral side of the 1-orifice component 36 is the first
The second orifice forming member 40 communicates with the main fluid chamber 66 through the third opening hole 36d of the orifice forming member 36.
The first passage 40b ₁ of the first orifice forming member 3
6 through the third opening hole 36 and the second opening hole 34g of the inner cylinder 34, from the first passage 40b ₁ to the space where the second diaphragm 43 is bulged, the partition member 40a and the partition member 40a. The gap between the second orifice constituting member 40 and the second passage 40b ₂ of the second orifice constituting member 40 communicate with each other.

Then, a fluid such as water is sealed in the communication passage from the main fluid chamber 66 to the space in which the second diaphragm 43 is expanded, and the first and second orifice component members 36, The first to third orifices 68A, 70A, 72A and the first to third sub-portions that generate fluid resonance when the volume of the main fluid chamber 66 changes due to the 40 and the first and second diaphragms 32c and 43. Fluid chamber 68
B, 70B, 72B are formed.

That is, the first orifice 68A is shown in FIG.
As shown in FIG.
The movable plate 4 above e, that is, the space surrounded by the minimum diameter tubular portion 36a and below the first orifice 68A.
The space defined by 6 becomes the first sub-fluid chamber 68B.
Further, as shown in FIG. 5, the second orifice 70A is an internal space of the inner cylinder 34, and the internal space of the inner cylinder 34 near the first diaphragm 32c serves as a second auxiliary fluid chamber 70B. Further, the third orifice 72A is, as shown in FIGS. 5 and 6, the first passage 40b of the second orifice constituting member 40.
₁ through the second passage 40b ₂ and then the second diaphragm 4
3 is a space up to the position where the second diaphragm 43 bulges inward, and the third sub-fluid chamber 72B is a space where the second diaphragm 43 bulges inward.

The characteristic of the fluid resonance system constituted by the first orifice 68A and the first sub-fluid chamber 68B is that the damping peak frequency (the frequency at which the maximum damping) occurs is vibration / acceleration of muffled sound in the passenger compartment. Noise vibration (80-800Hz)
The above is adjusted to match the frequency. Further, the second orifice 70A and the second auxiliary fluid chamber 70B
The characteristic of the fluid resonance system is that the damping peak frequency is an idling vibration (20 to 30 Hz) that occurs when the vehicle is stopped.
The degree is adjusted to match the frequency. Further, the third orifice 72A and the third sub-fluid chamber 72B
The characteristic of the fluid resonance system constituted by is adjusted so that its damping peak frequency matches the frequency of engine shake vibration (20 Hz or less) generated during braking or the like.

On the other hand, the exciting coil 52b of the electromagnetic actuator 52 is connected to the controller 74 via a harness, and as a drive current supplied from the controller (control means) 74, as shown in the block diagram of FIG. A predetermined electromagnetic force is generated according to the drive signal y.

The controller 74 includes a microcomputer (not shown), necessary interface circuits, A /
It is configured to include a D converter, a D / A converter, an amplifier, and the like, and in the case where vibration of a high frequency above the idle vibration frequency (for example, muffled sound vibration) is input,
The control vibration having the same cycle as the vibration and the phase opposite to that of the vibration is generated in the engine mount 20 so that the transmission force of the vibration to the member 28 becomes “0” (more specifically, on the engine 22 side). A driving signal y is generated and supplied to the exciting coil 52b so that the exciting force input to the engine mount 20 due to the vibration is offset by the control force obtained by the electromagnetic force of the electromagnetic actuator 52). .

Here, idle vibration and muffled sound vibration are as follows.
For example, in the case of a reciprocating four-cylinder engine,
The main cause is that the engine vibration of the next component is transmitted to the member 28 via the engine mount 20, so if the drive signal y is generated and output in synchronization with the secondary component of the engine rotation, the vibration transmission rate. Can be reduced. Therefore,
In the present embodiment, the rotation is synchronized with the rotation of the crankshaft of the engine 22 (for example, in the case of a reciprocating four-cylinder engine,
A pulse signal generator 76 is provided for generating an impulse signal (each time the crankshaft rotates 180 degrees) and outputting the impulse signal as a reference signal x.
Is supplied to the controller 74 as a signal indicating the state of occurrence of the vibration at.

On the other hand, as described above, the engine mount 2
0 has a built-in load sensor 54, detects the vibration state of the member 28 in the form of a load, outputs it as a residual vibration signal e, and supplies the residual vibration signal e to the controller 74 as a signal representing the vibration after interference. Has been done.

Then, the controller 74, based on the reference signal x and the residual vibration signal e, is a Filtered-X LM which is one of the adaptive algorithms of the successive update type.
The drive signal y is generated and output according to the S algorithm.

That is, the filter coefficient of the adaptive digital filter W is sequentially output to the electromagnetic actuator 52 of the engine mount 22 from the controller 74 at a predetermined sampling clock interval from the time when the reference signal x is input. supplied as y. As a result, a magnetic force corresponding to the drive signal y is generated in the exciting coil 52b,
Since the movable plate 46 is already given a constant magnetic force by the permanent magnet 52c, it can be considered that the magnetic force by the exciting coil 52b acts to strengthen or weaken the magnetic force of the permanent magnet 52c. However, in this embodiment, from the state shown in FIG. 7, the movable plate 46 is displaced only in the direction in which a compressive elastic force is obtained by compressing and deforming the elastic member 48 including the annular wave plate-shaped wave spring 48a. For this reason, if it is considered that the magnetic force of the permanent magnet 52c and the elastic force of the elastic member 48 including the wave spring 48a are in balance in the state shown in FIG.
Excitation coil 5 of electromagnetic actuator 52 for displacing 6
The magnetic force generated by 2b acts only in the direction that strengthens the magnetic force of the permanent magnet 52c. That is, the exciting coil 52
In the state where the drive signal y is not supplied to b, that is, in the state shown in FIG. 7, the magnetic force of the permanent magnet 52c acts on the movable plate 46 as a force for moving the movable plate 46 toward the electromagnetic actuator 52 side. In this state, the compressive elastic force generated in the elastic member 48 composed of the wave spring 48a acts so as to separate the movable plate 46 from the electromagnetic actuator 52.
To a predetermined position with respect to the electromagnetic actuator 52. Then, when the drive signal y is supplied to the exciting coil 52b from this state, the magnetic force generated in the exciting coil 52b by the drive signal y mainly acts in the same direction as the magnetic force of the permanent magnet 52c. The movable plate 46 is displaced in the direction in which the clearance with the electromagnetic actuator 52 decreases. Of course, this movable plate 46
The amount of displacement of the movable plate 46 depends on the magnitude of the drive signal (mainly current value) y supplied to the exciting coil 52b of the electromagnetic actuator 52.
Is set to a position most distant from the electromagnetic actuator 52, and the electromagnetic actuator 52 side can be displaced in both up and down directions.

As described above, the movable plate 46 can be displaced in both up and down directions by the magnetic force generated by the electromagnetic actuator 52, and if the movable plate 46 is displaced vertically, the main fluid chamber 66 can be moved.
Of the supporting elastic body 32 due to the change in volume.
, The active support force in both the forward and reverse directions is generated in the engine mount 20. Then, each filter coefficient W _i of the adaptive digital filter W which becomes the drive signal y is a synchronous Filtered-X.
Since the sequentially updated according to the LMS algorithm, after converged to optimum values each filter coefficient W _i of the adaptive digital filter W has passed a certain time, the drive signal y
Is supplied to the engine mount 20, so that the member 2 is moved from the engine 22 through the engine mount 20.
Idle vibrations and muffled sound vibrations transmitted to the side 8 are reduced.

Here, when the frequency of the vibration input from the engine 22 side to the engine mount 20 is near the engine shake vibration frequency at the time of braking, in the present embodiment, the main fluid chamber 66 is set to the first The third auxiliary fluid chamber 72B is connected to the third auxiliary fluid chamber 72A through the three orifices 72A,
Moreover, since the damping peak frequency of the fluid resonance system matches the shake vibration frequency, when the volume of the main fluid chamber 66 fluctuates, the main fluid chamber 66 passes through the third orifice 72A.
And, fluid resonance occurs between the third sub-fluid chamber 72B. As a result, a high damping force can be applied to the shake vibration, and a good vibration damping effect can be obtained.

Further, when the frequency of the vibration input from the engine 22 side to the engine mount 20 is near the idle vibration frequency when the vehicle is stopped, in the present embodiment, the main fluid chamber 66 is connected to the second orifice 70A. Second through
Since it is also communicated with the sub-fluid chamber 70B and the damping peak frequency of the fluid resonance system is matched with the idle vibration frequency, when the volume of the main fluid chamber 66 changes, the main fluid chamber 66 and Fluid resonance occurs between the second sub-fluid chambers 70B, and the electromagnetic actuator 52 is driven in accordance with this, as described above.
Greater control power can be generated. Therefore, it is possible to superimpose the control vibration having a large amplitude on the idle vibration having a large amplitude generated particularly on the engine 22 side, and obtain a good vibration damping effect.

Further, when the frequency of vibration input from the engine 22 side to the engine mount 20 is near the frequency of muffled sound vibration or noise vibration during acceleration, in the present embodiment, the main fluid chamber 66 is Since it is communicated with the first sub-fluid chamber 68B via the one orifice 68A, and the damping peak frequency of the fluid resonance system is made to coincide with the frequencies of muffled noise vibration and noise vibration during acceleration, the main fluid chamber 66
If the volume of the fluid changes, the fluid resonance occurs between the main fluid chamber 66 and the first sub fluid chamber 68B through the first orifice 68A.
By driving 2, it is possible to generate a larger control force.

By the way, in this embodiment, since the rubber seal member 47 is interposed between the movable plate 46 and the gap retaining ring 50, the air sealed between the movable plate 46 and the electromagnetic actuator 52 is sealed. A chamber is formed. When the drive signal y is supplied to the exciting coil 52b of the electromagnetic actuator 52 to displace the movable plate 46 as described above, the air in the sealed air chamber acts as an air spring. However, since the spring constant of the air spring in the air chamber changes due to the volume variation according to the internal air temperature (substantially also affected by the environmental temperature), the displacement of the movable plate 46 with respect to the same drive signal y is changed. The amount may change depending on the air temperature at that time. Therefore, in the present embodiment, the third diaphragm 51 is interposed between the upper surface of the yoke 52a serving as the air chamber and the atmosphere so that the air spring constant in the air chamber is always constant.

By the way, the wave spring 48a is used.
As shown in FIG. 8, the elastic member 48 is formed by bending a corrugated thin plate into an annular shape. When viewed from the side as shown in FIG. When the upper end and lower end of the amplitude are pressed, a compressive elastic force is obtained by the restoring force. Therefore, when the movable plate 46 approaches the electromagnetic actuator 52 side as described above, and the movable plate side receiving portion 55 of the flat plate member 55a and the storage body side receiving portion 36f of the first orifice component 36 approach each other,
The upper and lower ends of the wave of the wave spring 48a that are in contact with the receiving portions 55 and 36f are pressed, whereby the wave spring is deformed so that the amplitude of the wave is reduced and a compressive elastic force is exerted. The compressive elastic force and the magnetic force of the permanent magnet 52c are balanced to maintain the movable plate 46 at a predetermined position.

On the other hand, when the elastic member 48 made of the wave spring 48a is compressed and deformed so that the amplitude of the wave becomes small, the elastic member 48 naturally tries to extend in the circumferential direction. Here, if the annular wave springs 48a are connected in series, the circumferential extension due to the compressive deformation cannot be absorbed, and the radial expansion is inevitably caused. Therefore, the wave spring 48a that is usually formed in an annular shape is
As shown in FIG. 8a, a part of the shape is not continuous or is cut, and the circumferential extension due to the compressive deformation is absorbed by the circumferential displacement of both ends of the discontinuous portion 48b. , So that it does not expand in the radial direction.

Therefore, the elastic member 48 composed of the wave spring 48a has a movable plate side end portion (that is, an upper end portion) which is in contact with the movable plate side receiving portion 55 due to the compressive deformation thereof, and the storage body side receiving portion. The container-side end portion (that is, the lower end portion) in contact with 36f tries to move together in the circumferential direction. However, since the contact ends of the elastic member 48 of the present embodiment are both in contact with both the receiving portions 55 and 36f, that is, they are only movably supported, the compressive deformation causes Each contact end has both receiving parts 55, 36f
Move while touching. Therefore, stress concentration does not occur anywhere in the elastic member 48 including the wave spring 48a, and the maximum stress generated in the elastic member 48 as a result is higher than that in the conventional fixed end support structure such as a leaf spring. Since it can be made small, it is less likely to be fatigued even if the movable plate 46 is repeatedly reciprocated, and the durability performance as a vibration-proof support device is secured or improved without increasing the size of the conventional leaf spring. You can

By the way, as shown in FIG. 9, the elastic member 48 formed of the annular wave plate-shaped wave spring 48a linearly increases the compressive elastic force (stress in the figure) with the compressive deformation. However, when the compressive deformation further progresses and the amplitude of the wave disappears and the plate becomes flat, the compressive elastic force (stress) is saturated at a value smaller than the maximum allowable stress, which is non-linear.

Next, a second embodiment of the support structure of the elastic member 48 in the vibration-proof support device for maintaining the movable plate 46 at a predetermined position with respect to the electromagnetic actuator 52 will be described.

FIG. 10 is a detailed view showing the support structure of the elastic member 48 of the present embodiment in comparison with FIG. 2 or FIG. 7 of the first embodiment. Members equivalent to those of the first embodiment are not shown. The same reference numerals are given and detailed description thereof is omitted. The greatest difference between the present embodiment and the first embodiment is that the elastic member 48 also made of the wave spring 48a is different from the elastic member 48 made of the wave spring 48a in the main fluid chamber 66 side. 48 is disposed on the electromagnetic actuator 52 side. The elastic member 48 including the wave spring 48a of the present embodiment is
It is the same as or substantially the same as that of the first embodiment except that the diameter of the annular shape is larger than that of the first embodiment.

Therefore, in this embodiment, the actuator-side receiving portion 58, which is a recess having a rectangular cross section along the circumferential direction, is formed at the outer peripheral end of the upper surface of the yoke 52a of the electromagnetic actuator 52. On the other hand, a movable plate side receiving portion 55 composed of a concave portion having a rectangular cross section along the circumferential direction is also formed at the outer peripheral end portion of the lower surface of the movable plate 46 facing the movable plate 46. An elastic member 48 including a wave spring 48a is interposed. The wave spring 48a also has an annular shape as a whole, but the fact that a part thereof is not continuous is the same as or substantially the same as that of the first embodiment. Along with this, the leg member, the flat plate member, and the like of the first embodiment are also removed.

Here, as in the first embodiment, the movable plate 46 approaches the electromagnetic actuator 52 side, so that the movable plate side receiving portion 55 of the movable plate 46 and the yoke 52.
When the actuator-side receiving portion 58 of “a” approaches, the wave spring 48 in contact with both receiving portions 55, 58.
The upper end portion (that is, the movable plate side contact end portion) and the lower end portion (that is, the actuator side contact end portion) of the wave a are pressed, whereby the wave is deformed so that the amplitude of the wave is reduced, and the compressive elastic force is generated. The compressive elastic force is developed and the magnetic force of the permanent magnet 52c is balanced to maintain the movable plate 46 at a predetermined position. The elastic member 48 composed of the wave spring 48a is moved by the compressive deformation of the elastic member 48 and the movable plate side receiving portion 55 is formed.
The movable plate side end (that is, the upper end) that is in contact with the actuator and the actuator side end (that is, the lower end) that is in contact with the actuator side receiving portion 58 move in the circumferential direction by the extension in the circumferential direction. try to. However, since the contact ends of the elastic member 48 of the present embodiment are both in contact with both the receiving portions 55 and 58, that is, are movably supported, the contact ends of the elastic member 48 are changed by the compression deformation. The part moves while contacting both receiving parts 55 and 58. Therefore, stress concentration does not occur anywhere in the elastic member 48 composed of the wave spring 48a, and the maximum stress generated in the elastic member 48 as a result is higher than that in the conventional fixed end support structure such as a leaf spring. Since it can be made small, it is less prone to fatigue even if the movable plate 46 is repeatedly reciprocated, and the durability performance as a vibration-proof support device is secured or improved without increasing the size as in a conventional leaf spring. You can

By the way, as described above, when the respective contact ends of the elastic member 48 composed of the wave spring 48a and the movable plate side or actuator side receiving portions 55 and 58 move while contacting each other, that is, when both slide. Since both are worn, there is a risk that metal powder will be generated. When the metal powder is generated in this way, it may enter the sliding part or the movable part and cause a new scratch. However, in this embodiment, since the elastic member 48 including the wave spring 48a is interposed between the movable plate 46 and the electromagnetic actuator 52, metal powder is generated between them due to the sliding as described above. However, since the metal powder is adsorbed by the magnetic force of the permanent magnet 52c and does not enter into other sliding parts and movable parts, there is an advantage that new scratches are less likely to occur.

In each of the above-described embodiments, only the case where the seal member for isolating the actuator is provided between the movable plate and the storage body is described. Thus, it may be arranged between the movable plate and the actuator.

Further, in each of the above embodiments, the shape or the number of the orifices and the sub-fluid chambers for damping the vibration input is not limited to the above, and may be set appropriately according to the damping specification characteristics.

Further, in each of the above-mentioned embodiments, the actuator for driving the movable plate is the electromagnetic actuator, and the permanent magnet is used for always attracting the movable plate to the actuator side. However, these functional elements are limited to the above. However, existing actuators or suction means may be appropriately selected and used.

Further, in each of the above-described embodiments, only the anti-vibration supporting device interposed between the engine of the vehicle and the vehicle body has been described. However, the anti-vibration supporting device of the present invention includes another vibration source and it. It can be developed in any manner between the supporting body and the supporting body.

[Brief description of drawings]

FIG. 1 is a schematic configuration diagram showing an example in which a vibration-damping support device of the present invention is interposed between a vehicle engine and a vehicle body.

FIG. 2 is a front vertical cross-sectional view showing an example of the anti-vibration support device adopted in FIG.

3 is a partial side sectional view of the anti-vibration support device of FIG.

FIG. 4 is a plan view of the anti-vibration support device of FIG.

5A and 5B are operation explanatory views of a damping effect by the vibration isolation support device shown in FIG.

6 is an explanatory diagram of a fluid resonance system of engine shake vibration formed in the vibration isolation support device shown in FIG.

FIG. 7 is a detailed explanatory view of an elastic member and its supporting structure showing the first embodiment of the vibration isolating support device of the present invention.

8A and 8B are explanatory views of an elastic member employed in the anti-vibration support device of the present invention, FIG. 8A is a perspective view, and FIG. 8B is a side view.

FIG. 9 is an explanatory diagram of stress characteristics of an elastic member used in the vibration-damping support device of the present invention.

FIG. 10 is a detailed explanatory view of a spring member and its supporting structure showing a second embodiment of the vibration isolating support device of the present invention.

[Explanation of reference numerals] 20 is an engine mount (anti-vibration support device) 22 is an engine (vibration body) 26 is a vehicle body (support body) 30 is a connection member (vibration body side connection member) 32 is a support elastic body 32c is a first diaphragm 34 Is an inner cylinder 36 is a first orifice constituting member 36e is a bottom portion 36f is a receiving member side receiving portion 36g is a communicating hole 38 is an outer cylinder 40 is a second orifice constituting member 40b ₁ is a first communicating hole 40b ₂ is a second communicating hole 41 Actuator sub case (housing) 42 is actuator case (housing) 43 is second diaphragm 46 is movable plate 47 is spacer (housing) 48 is spring member 49 is rubber seal member 50 is gap retaining ring (housing) 51 The third diaphragm 52 is an electromagnetic actuator (actuator) 53 is a leg member 55 is a receiving body side receiving portion 57 is a screw member 5 Is an actuator side receiving portion 66 is a main fluid chamber (fluid chamber) 68A is a first orifice 68B is a first sub fluid chamber 70A is a second orifice 70B is a second sub fluid chamber 72A is a third orifice 72B is a third sub fluid chamber 74 is a controller (control means)

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Yosuke Akatsu Nissan Motor Co., Ltd. 2 Takaracho, Kanagawa-ku, Yokohama-shi, Kanagawa

Claims (4)

[Claims] 1. A support elastic body interposed between a vibrating body and a support body, a storage body connected to the support elastic body, and a fluid chamber defined in the support elastic body and having a fluid enclosed therein. A movable plate that forms a part of the partition wall of the fluid chamber and is displaceable in a direction that changes the volume of the fluid chamber; and an actuator that is provided in the housing and applies a displacement force to the movable plate. Controlling means for supplying a control signal to the actuator so as to reduce the vibration transmitted from the vibrating body to the support body; and the movable plate and the movable plate for maintaining the movable plate in a predetermined position with respect to the actuator. A corrugated plate-like elastic member interposed between the housing and the movable plate and the actuator, and between the movable plate and the housing or the actuator to isolate the actuator from the fluid chamber. Arrangement Anti-vibration support device, comprising: 2. A vibrating body-side coupling member that is coupled to the vibrating body, a supporting-body-side coupling member that is coupled to the support, and a supporting elastic body that is coupled to one of the vibrating-body-side coupling member or the supporting-body-side coupling member. And a storage body connected between the supporting elastic body and the other of the vibrating body side connecting member or the supporting body side connecting member, and a fluid chamber defined in the supporting elastic body and having a fluid sealed therein. A movable plate that forms a part of the partition wall of the fluid chamber and is displaceable in a direction that changes the volume of the fluid chamber; and the movable plate that is disposed in the housing and generates a magnetic force. An actuator for applying a displacement force to the actuator, control means for supplying a control signal to the actuator so as to reduce vibration transmitted from the vibrating body to the support, and the movable means for isolating the actuator from the fluid chamber. A seal member arranged between the plate and the housing or the actuator, a movable plate side receiving portion formed on the movable plate, and a housing or actuator side receiving portion formed on the housing or actuator, In order to maintain the movable plate at a predetermined position with respect to the actuator, the movable plate side end is movably supported by the movable plate side receiving part, and the storage body or actuator side end part is the storage body or actuator side receiving part. An anti-vibration support device comprising: a corrugated plate-like elastic member that is movably supported on the first end and is annular, but is not partially continuous. 3. The spring member is disposed in the fluid chamber,
The anti-vibration support device according to claim 1 or 2, wherein the movable plate is supported from the fluid chamber side with respect to the actuator. 4. The anti-vibration support device according to claim 1, wherein the spring member is disposed between the movable plate and the actuator, and the movable plate is supported from the actuator side.