JPH10227329A - Vibro-isolating support device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibro-isolating support device which can stabilize vibration control performance by decreasing stress generated in a plate-like spring member by which a movable plate is supported, and retaining a gap arranged between the movable plate and an electromagnetic actuator to a predetermined value. SOLUTION: The peripheral end part of a spring member 48 and the periphery of a hole part are supported at a free end by a second spacer 50 arranged in a device case 43 and a contracted part formed in a movable plate 46. Hereby, the inner circumferential and peripheral end parts of the spring member 48 can be displaced freely in a surface direction. Also, a film-like seal elastic body 47 is arranged between a first spacer 44 and the periphery of the movable plate 46, and the spring constant of this seal elastic body 47 in a direction to support the movable plate 46, is set to below 1/2 a value of the spring constant of the spring member 48. Hereby, even though this vibro-isolating support device is used under a high temperature environment, a gap between the movable plate 46 and an electromagnetic actuator 52 can always retain an initial value.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an anti-vibration support device for supporting a vibrating body such as an engine of a vehicle, which generates periodic vibrations, while supporting the vibrating body on a support such as a vehicle body. Also, the present invention relates to an anti-vibration support device in which a fluid chamber is defined by a support elastic body interposed between supports and a volume of the fluid chamber is actively changed to reduce a vibration transmissibility.

[0002]

2. Description of the Related Art In general, an engine mount, which is an anti-vibration support device used to support a power unit of a vehicle, mainly has good anti-vibration against idle vibration, engine shake, muffled sound vibration, noise vibration during acceleration, and the like. It is required that the vibration-proof function is exhibited. Among these various vibrations, the characteristics required of the vibration-proof support device in order to reduce the engine shake which is a vibration having a relatively large amplitude of about 5 to 15 Hz are as follows. Idle vibration, which has a relatively large amplitude of about 20 to 30 Hz while having a high dynamic spring constant and high damping, and muffled sound vibration, which is a relatively small and medium amplitude vibration of about 80 to 800 Hz. The characteristics required of the vibration isolation support device to reduce the noise and vibration during acceleration are a low dynamic spring constant and low attenuation. Therefore, it is difficult to prevent all vibrations with an engine mount including only a normal elastic body or a conventional liquid-filled engine mount.

[0003] In view of the above, an anti-vibration support device capable of actively damping and supporting a vibrating body such as an engine of an automobile has been disclosed in Japanese Patent Application Laid-Open No. 8-145114 filed earlier by the present applicant. There is technology.

In this prior art, as shown in FIG. 4, a vibrating body 1 and a supporting elastic body 3 interposed between the vibrating body 1 and a supporting body 2 are provided.
A fluid chamber 4 defined by the support elastic body 3, a fluid sealed in the fluid chamber 4, and a plate-shaped spring member (a leaf spring in the publication) 5a forming a part of a partition of the fluid chamber 4. A movable plate 5 composed of a magnetizable movable plate (in the publication, a magnetic path member) 5b fixed to the lower center of the spring member 5a, and an electromagnetic actuator 6 for applying a displacement force to the magnetic path member 5b by generating an electromagnetic force. A pulse signal generator 7 for detecting a state of occurrence of vibration of the vibrating body 1 and generating a reference signal; a load sensor 8 for detecting residual vibration on the support 2 side and outputting it as a residual vibration signal; And a controller 9 that outputs a drive signal to the electromagnetic actuator 8 based on the signal. In this vibration-proof support device, an actuator case 10 is interposed between a support elastic body 3 and a support body 2, an electromagnetic actuator 6 is disposed in the actuator case 10, and the actuator case 10 is supported. The elastic body side has a flange shape, and a flange portion of the actuator case,
The outer peripheral edges of the elastic body 11, the force transmitting member 12, and the spring member 5a are overlapped in this order, and are caulked to the end of the cylindrical member 13 that fixes the support elastic body 3 inside.

According to the vibration isolating support device, when a vibration is input from the vibrating body 1 side, the pulse generator 7 generates a reference signal corresponding to the reference signal and outputs it to the controller 9, and the residual vibration is applied to the supporting body 2. Is generated, the load sensor 8 outputs to the controller 9 as residual vibration. Then, the controller 9 outputs a drive signal to the electromagnetic actuator 6, and the electromagnetic actuator 6 appropriately displaces the magnetic path member 5b, changes the volume of the fluid chamber 4, and the vibration transmission force to the support 2 side is "0". Can be controlled so that

[0006]

As described above, the outer peripheral edge of the spring member 5a is sandwiched between the ends of the force transmitting member 12 and the cylindrical member 13, and a movable plate is provided at the lower center. 5b is fixed, but since the spring member 5a is a member that deforms with the displacement of the movable plate 5b, stress concentration occurs at the outer peripheral edge and the central portion, and the local stress generated at those portions is increased. Tends to be large. Moreover, since the stress is constantly repeated while the electromagnetic actuator is moving, the spring member 5a may be fatigued. Therefore, when a large displacement is required for the movable plate 5b, the stress generated in the spring member also increases, and there is a problem that an expensive leaf spring must be used in consideration of the durability performance as a vibration-proof support device. Occurs.

When the above-mentioned vibration isolating support device is used in a high temperature environment, the force transmitting member 12 and the actuator case 10
There is a possibility that the elastic body 11 sandwiched between the elastic member 11 and the spring constant decreases due to the high temperature, causing deformation such as settling. When the elastic body 11 is deformed, and a gap alpha ₁ changes between the magnetic path member 5b and the electromagnetic actuator 6 that was initially set, without volume change of the desired main fluid chamber 4 is obtained, anti-vibration performance Cannot be stabilized.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and it is intended to reduce the stress generated in a plate-like spring member supporting a movable plate to improve the durability and to improve the durability of the movable plate and the electromagnetic force. It is an object of the present invention to provide an anti-vibration support device capable of stabilizing anti-vibration performance by always keeping a gap provided between actuators constant.

[0009]

According to a first aspect of the present invention, there is provided an anti-vibration support apparatus according to the first aspect of the present invention, wherein a support elastic member interposed between the vibrating member and the support member is connected to the support elastic member. A main fluid chamber defined in the support elastic body and filled with a fluid, a variable-volume sub-fluid chamber communicating with the main fluid chamber via an orifice, and a main fluid chamber. A fluid sealed in the sub-fluid chamber and the orifice, a magnetizable movable plate displaced in a direction that changes the volume of the main fluid chamber, and a movable plate disposed in the device case and generating a magnetic force. An electromagnetic actuator that applies a displacement force to the electromagnetic actuator; a plate-shaped spring member that elastically supports the movable plate so that the movable plate faces the electromagnetic actuator with a predetermined gap; Transmitted to the body And a control means for supplying a control signal to the electromagnetic actuator so as to reduce movement. In the vibration-isolation supporting device, the spring member has a hole formed in a central portion thereof, and a peripheral edge and an outer periphery of the hole. The spring member includes a cylindrical first spacer disposed on the support elastic body side in the device case, and a cylindrical second spacer abutting on the electromagnetic actuator. And the outer peripheral end of the spring member is received from the electromagnetic actuator side by the second spacer,
The outer periphery of the spring member and the outer periphery of the hole are supported at the free end by engaging the periphery of the hole with the constriction formed in the movable plate, while the outer periphery of the first spacer and the periphery of the movable plate are supported. Between the second spacer and the outer periphery of the movable plate, a film-like sealing elastic body that seals the fluid in the main fluid chamber is provided to elastically support the movable plate, and The spring constant of the member in the direction supporting the movable plate was set to a value equal to or less than 1/2 of the spring constant of the spring member.

According to a second aspect of the present invention, in the anti-vibration support device according to the first aspect, the electromagnetic actuator is formed in an annular shape on a column-shaped yoke and an opposing surface of the yoke facing the movable plate. The yoke has a structure including an embedded excitation coil, and the second spacer abutting on the opposing surface of the yoke facing the movable plate is formed of a nonmagnetic material.

[0011]

According to the vibration isolating support device of the first aspect,
A spring member is provided between a cylindrical first spacer disposed on the support elastic body side in the device case and a cylindrical second spacer abutting on the electromagnetic actuator, and an outer peripheral end of the spring member is provided. Part is received from the electromagnetic actuator side by the second spacer, and the periphery of the hole formed in the center of the spring member is engaged with the constriction formed in the movable plate to form the outer peripheral end of the spring member and the periphery of the hole. Since the free end is supported, the inner and outer peripheral ends of the spring member can be freely displaced in the plane direction,
During the deformation of the spring member accompanying the displacement of the movable plate, generation of large local stress, that is, stress concentration can be avoided, and fatigue due to repetition can also be avoided.

Further, since the spring member has a structure in which a slit is formed between the peripheral edge and the outer periphery of the hole formed in the center, the contact area between the movable plate and the spring member is reduced. As a result, when the spring member is deformed together with the displacement of the movable plate, the periphery of the hole of the spring member supported at the free end slides with respect to the movable plate. Wear is reduced, and the amount of metal powder generated from both is reduced accordingly. Therefore, the durability of the vibration isolating support device is improved by reducing the wear, and the generation of the metal powder in the sliding portion and the generation of a scratch due to the reduction in the amount of generated metal powder are suppressed.

Further, since the film-like sealing elastic body is provided between the first spacer and the outer periphery of the movable plate or between the second spacer and the outer periphery of the movable plate, the main fluid chamber is provided. And the airtightness of the electromagnetic actuator side can be reliably maintained. The seal elastic body elastically supports the movable plate together with the spring member. The spring constant of the seal elastic body in the direction in which the movable plate is supported is a value equal to or less than 1/2 of the spring constant of the spring member. Is set to That is, the seal elastic body is a soft spring member that hardly supports the movable plate, and the spring member is a hard spring member for elastically supporting the movable plate. Here, if the seal elastic body elastically supports the movable plate as a hard spring member and the spring member is a soft member, if the vibration isolating support device is used in a high temperature environment, the seal elastic body may be in a high temperature state. The spring constant may be reduced and deformed, and the movable plate may move to the electromagnetic actuator side, and the gap between the initially set movable plate and the upper surface of the electromagnetic actuator may change.

Therefore, in the present invention, the spring member is a rigid spring member for elastically supporting the movable plate, so that the gap always keeps the initial value even when the anti-vibration support device is used in a high temperature environment. Since there is no possibility that the displacement amount of the main fluid chamber changes, the desired volume fluctuation of the main fluid chamber, that is, the vibration isolation performance can be stabilized.

According to the second aspect of the present invention, the effect of the first aspect can be obtained, and when the electromagnetic actuator operates, the exciting coil buried annularly in the yoke generates a magnetic force line. If there is a member made of a magnetic material near the position where the lines of magnetic force are generated, the lines of magnetic force may leak to the member side and the displacement of the movable plate may change. Therefore, according to the present invention, the second spacer that contacts the surface of the electromagnetic actuator facing the movable plate and supports the spring member is disposed near the position where the magnetic force lines are generated. Since it is formed of a nonmagnetic material such as an aluminum alloy, there is no possibility that the lines of magnetic force leak to the second spacer side and the displacement amount of the movable plate changes. Therefore, it is possible to further stabilize the desired volume fluctuation of the main fluid chamber, that is, the vibration isolation performance.

[0016]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a perspective view showing a so-called active engine mount (hereinafter simply referred to as an engine mount) that actively reduces vibration transmitted from an engine side as a vibrating body to a vehicle body-side member as a support. ). The engine mount indicated by reference numeral 20 in FIG. 1 is disposed on the rear side of the vehicle body of the horizontally mounted engine 22, the upper part of which is attached to the bracket 24, and the lower part thereof is fixed to the vehicle body 26 by a member 28 as a support. Attached to.

As shown in FIG. 2, the engine mount 20 incorporates mounting parts such as an outer cylinder 34, an orifice constituting member 36, and a support elastic body 32 defining a main fluid chamber inside an apparatus case 43. At the bottom of these mounting parts,
An electromagnetic actuator 52 as an actuator for displacing a movable plate elastically supported while forming a part of a partition wall of the main fluid chamber in a direction in which the volume of the main fluid chamber changes, and a load sensor 54 for detecting a vibration state of the member 28 This is a device that incorporates

That is, the engine mount 20 is
An engine-side connecting member 30 having the connecting bolt 30a fixed upward is provided. This engine side connecting member 30
A hollow cylindrical body 30b having an inverted trapezoidal cross section is fixed to a lower portion of the hollow cylindrical body 30b.

The lower side of the engine-side connecting member 30 and the hollow cylindrical body 3
The supporting elastic body 32 is fixed by vulcanization bonding so as to cover the periphery of Ob.

The support elastic body 32 is a thick, substantially cylindrical elastic body that is gently inclined downward from the center to the outer periphery, and has a hollow section 32a having a mountain-shaped cross section formed on the inner surface. I have. A lower end portion 32b of the resilient support member 32 which is a thin shape, the axis (hereinafter, referred to as the mounting shaft) P ₁
Is connected to the inner peripheral surface of the orifice component member 36 facing the vibrating body supporting direction (in this case, the vertical direction) coaxially with the hollow cylindrical body 30b by vulcanization bonding.

The orifice constituting member 36 is a member in which a small-diameter cylindrical portion 36c is continuously formed between an upper cylindrical portion 36a and a lower cylindrical portion 36b having the same outer diameter, and an annular concave portion is provided on the outer circumference. . An opening 36d is formed in the small-diameter cylindrical portion 36c, and the inside and the outside of the orifice constituting member 36 communicate with each other through the opening 36d.

The orifice member 36 includes an outer cylinder 3.
4 is externally fitted, and the annular concave portion of the orifice constituting member 36 is surrounded by the inner peripheral surface of the outer cylinder 34, thereby defining an annular space in the circumferential direction. A diaphragm 42 is provided in the annular space.

That is, the inner diameter of the outer cylinder 34 is the same as the outer diameter of the upper and lower cylindrical portions 36a and 36b of the orifice member 36, and the axial length is the same as that of the orifice member 36. Is a cylindrical member set to. The outer cylinder 34 is formed with a slit-shaped opening 34a facing the annular concave portion other than the position where the opening 36d is formed in the circumferential direction.

The diaphragm 42 is a rubber thin film elastic body, is connected to the entire periphery of the opening edge of the opening 34a, closes the opening 34a, and swells toward the annular recess of the orifice constituting member 36. It is arranged in the state where it did. The outer cylinder 34 is fitted inside the upper part of the device case 43.

The device case 43 has an upper end caulking portion 43a having a circular opening having a diameter smaller than the outer diameter of the upper end cylindrical portion 36a at the upper end thereof, and the shape of the case body connected to the upper end caulking portion 43a. Is a cylindrical member having the same inner diameter as the outer diameter of the outer cylinder 34 and continuous to the lower end opening (the lower end opening is indicated by a broken line in FIG. 1).

Then, the outer cylinder 34 in which the support elastic body 32, the orifice constituting member 36 and the diaphragm 42 are integrated is fitted into the inside of the apparatus case 43 from the lower end opening thereof, and the outer cylinder 34 The upper ends of the orifice constituting members 36 are in contact with each other, so that they are disposed in the upper part in the apparatus case 43. here,
An air chamber 42a is defined in a portion surrounded by the inner peripheral surface of the device case 43 and the diaphragm 42.
An air hole 42b is formed at a position facing a, and the air chamber 42a and the atmosphere communicate with each other through the air hole 42b.

Further, a seal ring (first spacer) 44, a gap holding ring 50 (second spacer), and a leaf spring (plate-like spring member) supported by the gap holding ring 50 are provided at a lower portion in the apparatus case 43. 48, a movable plate 46 engaged with an inner peripheral end 48a of a leaf spring 48, a seal ring 44
And a seal rubber (membrane-like seal elastic body) 47, an electromagnetic actuator 52, and a load sensor 54 which are disposed between the upper and outer peripheries of the movable plate 46 are sequentially incorporated. By closing the opening with the lid member 57 and caulking the lower end of the device case 43 inward in the radial direction, the lower caulking portion 43c is formed as shown by the solid line in FIG.

That is, the seal ring 44 is an annular member having the same outer diameter as the inner diameter of the device case 43 and having substantially the same diameter as the outer diameter of the lower end cylindrical portion 36b of the orifice constituting member 36. On the upper surface of the seal ring 44, the outer cylinder 3
4 and the lower end of the orifice constituting member 36 are in contact with each other.

The gap holding ring 50 is made of a non-magnetic material such as an aluminum alloy.
3 has the same outer diameter as the inner diameter, and a step portion 5
Oa is an annular member provided between the seal ring 44 and the yoke 52a of the electromagnetic actuator 52 to set a gap between the lower surface of the movable plate 46 and the upper surface of the electromagnetic actuator 52 to a predetermined value. . The step portion 50a of the gap retaining ring 50 supports the outer peripheral end portion 48c of the leaf spring 48 from below.

As shown in FIG. 3, the leaf spring 48
A ring-shaped thin plate provided with an inner peripheral end 48a by forming a circular hole (hole) in the center of the disk-shaped thin plate. Radial slits 48b are formed at equal intervals from the inner peripheral end 48a. The leaf springs 48 are formed in the same shape and the area of the inner peripheral end portion 48a is reduced.
8 with the gap retaining ring 50 described above.
Abut on the step 50a. Note that a predetermined gap is provided between the upper leaf spring 48 and the seal ring 44.

The movable plate 46 includes a magnetic path portion 46a located on the side of the electromagnetic actuator 52 and a disk portion 46b coaxially fixed above the magnetic path portion 46a. This is a member provided with a constricted portion 46c between itself and the portion 46b. Then, the two leaf springs 48
Is loosely fitted with a predetermined gap in the constricted portion 46c at the inner peripheral end 48a.

Thus, the leaf spring 48 has its outer peripheral end 48c supported by the gap holding ring 50 at its free end, and its inner peripheral end 48a is supported by the constricted portion 46c of the movable plate 46 at its free end. I have.

Further, the seal rubber 47 is provided with the seal ring 4.
4 is an annular film formed by vulcanization bonding between the inner peripheral surface of the movable plate 46 and the outer peripheral surface of the disk portion 46b of the movable plate 46, and elastically supports the movable plate 46 together with the leaf spring 48.

Here, the vertical spring constant of the seal rubber 47 supporting the movable plate 46 is set to a value not more than よ り of the vertical spring constant of the leaf spring 48 supporting the movable plate 46. ing.

The electromagnetic actuator 52 abutting on the lower surface of the gap retaining ring 50 is surrounded by a cylindrical yoke 52a, an exciting coil 52b coaxially embedded on the upper end side of the yoke 52a, and an exciting coil 52b. And a permanent magnet 52c having a magnetic pole fixed vertically in the upper surface range of the yoke 52a.

As shown in FIG. 2, a lid member 57 for covering the load sensor 54 from below is provided with a disc-shaped bottom lid 58 and
A large-diameter tube portion 59 that rises from the outer peripheral edge of the bottom lid 58 toward the yoke 52a side;
9 and an outer peripheral locking portion 60 extending annularly outward from the upper peripheral edge in the radial direction. A plurality of press-fit holes are formed on the outer peripheral side of the bottom cover 58, and the vehicle-body-side connecting bolt 56 is press-fitted into these press-fit holes.

Then, the lower surface of the load sensor 54 is brought into contact with the center of the upper surface of the lid member 57, and the outer periphery locking portion 60 is swaged and fixed by forming the lower end swaging portion 43c of the device case 43 shown by the solid line in FIG. When the bottom cover 58 moves, the load sensor 5
4 is pressed against the yoke side 52a to apply a predetermined preload, and the lid member 57 is integrated with the apparatus case 43.

By the way, the hollow portion 32 of the support elastic body 32
Assuming that the space surrounded by the outer peripheral surface of the orifice component member 36 and the leaf spring 48 is a main fluid chamber 66, the main fluid chamber 66
A fluid such as oil is sealed in a communication path from the space through the opening 36d to the space where the diaphragm 42 is bulged.

The internal space near the diaphragm 42 is defined as a sub-fluid chamber 67, and the sub-fluid chamber 67 and the main fluid chamber 6
An orifice 68 is used as a communication passage between the six fluid passages 6, and when the volume of the main fluid chamber 66 fluctuates, fluid resonance occurs due to the auxiliary fluid chamber 67 and the orifice 68.

Here, the characteristics of the fluid resonance system determined by the mass of the fluid in the orifice 68 and the shape of the flow path in the expanding direction of the support elastic body 32 are determined when the engine shakes during running, that is, at 5 to 15 Hz. It is adjusted so as to exhibit a high dynamic spring constant and a high damping force when the engine mount 20 is vibrated.

The exciting coil 52b of the electromagnetic actuator 52 is connected to the controller 74 via a harness. As shown in the block diagram of FIG.
, A predetermined electromagnetic force is generated.

The controller 74 includes a microcomputer, necessary interface circuits, an A / D converter, and a D / A
It is configured to include a converter, an amplifier and the like, and is a vibration in a frequency band in which fluid cannot move between the main fluid chamber 66 and the sub-fluid chamber 67 through the orifice 68, that is, a vibration higher in frequency than the engine shake described above. When the idle vibration, the muffled sound vibration, and the vibration at the time of acceleration are input, the control vibration having the same cycle as the vibration is generated in the engine mount 20 and the transmission force of the vibration to the member 28 becomes “0”. As described above (more specifically, the drive signal y is changed so that the exciting force input to the engine mount 20 by the vibration of the engine 22 is offset by the control force obtained by the electromagnetic force of the electromagnetic actuator 52). Generated excitation coil 52b
To be supplied.

Here, the idle vibration and the 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. Therefore, 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.

Then, the load sensor 54 detects the vibration state of the member 28 in the form of a load and outputs it as a residual vibration signal e. The residual vibration signal e is supplied to the controller 74 as a signal representing vibration after interference. Have been.
Then, based on the reference signal x and the residual vibration signal e, the controller 74 generates and outputs a drive signal y in accordance with a Filtered-X LMS algorithm, which is one of the successively updated adaptive algorithms.

Next, the engine mount 20 of the present embodiment will be described.
The operation of the anti-vibration mechanism will be described. When the engine 22 is started and vibration is input to the engine mount 20, the controller 74 executes a predetermined calculation process, outputs a drive signal y to the electromagnetic actuator 52, and reduces the vibration to the engine mount 20. Generates active control power to gain.

That is, the filter coefficient of the adaptive digital filter W is supplied from the controller 74 to the electromagnetic actuator 52 of the engine mount 22 at a predetermined sampling clock interval from the time when the reference signal x and the residual vibration signal e are inputted. Are sequentially supplied as the drive signal y. As a result, a magnetic force corresponding to the drive signal y is generated in the exciting coil 52b, but the movable plate 46 has already
Since the constant magnetic force by 2c is given, 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.
That is, when the drive signal y is not supplied to the excitation coil 52b, the movable plate 46 is displaced to a neutral position where the elastic support force of the leaf spring 48 and the magnetic force of the permanent magnet 52c are balanced. When the drive signal y is supplied to the excitation coil 52b in this neutral state, if the magnetic force generated in the excitation coil 52b by the drive signal y is in the opposite direction to the magnetic force of the permanent magnet 52c, the movable plate 46 It is displaced in a direction in which the clearance with the actuator 52 increases. Conversely, if the magnetic force generated in the exciting coil 52b is in the same direction as the magnetic force of the permanent magnet 52c, the movable plate 46 is displaced in a direction in which the clearance with the electromagnetic actuator 52 decreases.

As described above, the leaf spring 48 can be displaced up and down by the magnetic force generated by the electromagnetic actuator 52. When the leaf spring 48 is displaced up and down, the main fluid chamber 66 is displaced.
Of the supporting elastic body 32 due to the change in volume.
Expansion spring (considering a dynamic model, the supporting elastic body 32
Are interposed in parallel. ) Is deformed, an active supporting force is generated on the engine mount 20 in both forward and reverse directions. Then, each filter coefficient W of the adaptive digital filter W that becomes the drive signal y
Since ₁ is sequentially updated according to the synchronous Filtered-X LMS algorithm, after converged to each filter coefficient W _i is the optimum value of the adaptive digital filter W has passed a certain time, the drive signal y is an engine mount 2
By being supplied to 0, idle vibration and muffled sound vibration transmitted from the engine 22 to the member 28 via the engine mount 20 are reduced.

Next, the movable plate 46 is connected to the electromagnetic actuator 5.
The function and effect of the leaf spring 48 for providing and maintaining a gap with respect to 2, the support structure of the leaf spring 48, and the seal rubber 47 for sealing the fluid in the main fluid chamber 66 will be described.

FIG. 2 shows a state in which the electromagnetic actuator 52 is not excited. The inner peripheral end 48a of the leaf spring 48 made of a ring-shaped thin plate has a magnetic path portion a of the movable body spring 48 and a disk portion 46b. Are loosely fitted with a predetermined gap provided in the constricted portion 46c formed therebetween. The outer peripheral end 4848c of the leaf spring 48 is also disposed between the seal ring 44 and the gap holding ring 50, and the gap holding ring 50
Is loosely fitted in contact with the stepped portion 50a of the second member. Therefore, when the electromagnetic actuator 52 is excited, the movable plate 46, which is a magnetic material, moves toward the electromagnetic actuator 52, that is, in the vertical direction shown in the drawing, so that the inner peripheral end 4
When the excitation of the electromagnetic actuator 52 is released, the inner peripheral end 48a of the leaf spring 48 together with the movable plate 46 also rises to the state shown in FIG. At this time, in the present embodiment, the inner peripheral end 48a of the leaf spring 48 is
In addition, since the outer peripheral end 48c is supported at the free end, the stress generated due to the deformation of the leaf spring 48 is not locally concentrated, and is stabilized over the entire width of the leaf spring 48. Therefore, the maximum stress generated in the leaf spring 48 is smaller than that of the conventional structure in which the leaf spring is fixedly supported, and even when the movable plate 46 is finely vibrated to cancel out (attenuate) the vibration input, the leaf spring 48 can be used. Since the tire 48 hardly causes fatigue, the durability of the engine mount 20 is improved.

Further, by arranging the two leaf springs 48, the spring constant of the leaf spring 48 can be finely changed and set. For example, various uses required according to vehicle characteristics can be finely and easily performed. Can be realized.

On the other hand, a film-like seal rubber 47 provided between the inner peripheral surface of the seal ring 44 and the outer peripheral surface of the disk portion 46b of the movable plate 46 is used to seal the liquid in the main fluid chamber 66 and the electromagnetic actuator 52. Airtightness can be reliably maintained. The seal rubber 47 elastically supports the movable plate 46 together with the leaf spring 48. The spring constant of the seal rubber 47 (strictly speaking, the vertical spring constant for supporting the movable plate 46) is It is set to a value that is 1/2 or less than the spring constant of 48. That is, the seal rubber 47 is a soft spring member that hardly supports the movable plate 46, and the plate spring 48 is a hard spring member that elastically supports the movable plate 46. Here, when the movable plate 46 is elastically supported by the seal rubber 47 as a hard spring member (a member with a large spring constant) and the leaf spring 48 is soft (a member with a small spring constant),
When the engine mount 20 is used in a high-temperature environment, when the seal rubber 47 is in a high-temperature state, the spring constant decreases and deforms downward, and at the same time, the movable plate 46 also moves downward. Lower surface and electromagnetic actuator 5
2 may change. Therefore, in the present embodiment, since the leaf spring 48 is a rigid spring member that elastically supports the movable plate 46, the gap α always retains the initial value even when the engine mount 20 is used in a high temperature environment, and the drive signal There is no possibility that the displacement amount of the movable plate 46 with respect to y changes, and the desired volume fluctuation of the main fluid chamber 66, that is, the vibration isolation performance can be stabilized.

Further, when the drive signal y is input to the electromagnetic actuator 52, as shown in FIG. 2, the exciting coil 52b annularly buried in the yoke 52a generates the magnetic force line M, and the position where the magnetic force line M is generated. When a member made of a magnetic material exists near the movable member 46, the displacement of the movable plate 46 may change due to the magnetic field lines M leaking to the member side. However, in the present embodiment, the gap holding ring 50 that contacts the outer periphery of the upper surface of the electromagnetic actuator 52 and supports the leaf spring 48 is disposed near the position where the magnetic field lines M are generated. Is formed of a non-magnetic material such as an aluminum alloy, there is no possibility that the line of magnetic force M leaks to the gap holding ring side and the displacement amount of the movable plate 46 is changed.
, That is, the anti-vibration performance can be stabilized.

In the above embodiment, two leaf springs 48 are used.
Are shown, but if more leaf springs 48 are overlapped, the spring constant of the leaf springs 48 can be changed and set more finely.

In the above embodiment, the seal rubber 47 is used.
To the inner peripheral surface of the seal ring 44 and the disk portion 4 of the movable plate 46.
6b, the gist of the present invention is not limited to this. For example, between the inner peripheral surface of the gap holding ring 50 and the outer periphery of the magnetic path portion 46a of the movable plate 46. Even if the seal rubber 47 is provided, the liquid tightness on the main fluid chamber 66 side and the air tightness on the electromagnetic actuator 52 side can be reliably maintained. Also in this case, the spring constant of the seal rubber 47 is set to a value that is １ ／ or less than the spring constant of the leaf spring 48.

Further, in the above embodiment, the engine 22
Is applied to an engine mount 20 that supports the vibration control device, but the application object of the anti-vibration support device according to the present invention is not limited to the engine mount 20. And so on.

[Brief description of the drawings]

FIG. 1 is an overall configuration diagram showing an arrangement state of an anti-vibration support device according to the present invention.

FIG. 2 is a view showing a cross section along the axial direction of the vibration isolating support device of the present invention.

FIG. 3 is a view showing a shape of a spring member according to the present invention.

FIG. 4 is a diagram showing a structure of a conventional vibration-proof support device.

[Explanation of symbols]

 Reference Signs List 20 engine mount (anti-vibration support device) 22 engine (vibration body) 28 member (support) 32 support elastic body 43 device case 44 seal ring (first spacer) 46 movable plate 46c constriction 47 seal rubber (film-like seal elasticity) Body) 48 leaf spring (spring member) 48a inner peripheral end of leaf spring 48b slit 48c outer peripheral end of leaf spring 50 gap retaining ring (second spacer) 50a step 52 electromagnetic actuator 52a yoke 52b exciting coil 66 main fluid chamber 67 Sub-fluid chamber 68 Orifice

Claims (2)

[Claims] 1. A supporting elastic body interposed between a vibrating body and a supporting body, an apparatus case connected to the supporting elastic body, and a main fluid defined in the supporting elastic body and having a fluid sealed therein. A chamber, a volume-variable sub-fluid chamber communicating with the main fluid chamber via an orifice, a fluid sealed in the main fluid chamber, the sub-fluid chamber and the orifice, and a direction in which the volume of the main fluid chamber is changed. A movable magnetizable plate that is displaced, an electromagnetic actuator that is disposed within the device case and generates a magnetic force to apply a displacement force to the movable plate, and that the movable plate has a predetermined gap with respect to the electromagnetic actuator. A plate-like spring member that elastically supports the movable plate so as to face the movable plate; and a control unit that supplies a control signal to the electromagnetic actuator so as to reduce vibration transmitted from the vibrating body to the supporting body. In the anti-vibration support device provided, the spring member has a structure in which a hole is formed in a center portion thereof and a slit is formed between a peripheral edge and an outer periphery of the hole portion,
The spring member is provided between a cylindrical first spacer disposed on the support elastic body side in the apparatus case and a cylindrical second spacer abutting on the electromagnetic actuator, and the spring member Of the spring member is received from the electromagnetic actuator side by the second spacer, and the peripheral edge of the hole is engaged with a constricted portion formed in the movable plate, so that the outer peripheral end of the spring member and the peripheral edge of the hole are free. While supporting the end, between the first spacer and the outer periphery of the movable plate, or between the second spacer and the outer periphery of the movable plate, a film-like sealing elasticity for sealing the fluid in the main fluid chamber side. A body is disposed to elastically support the movable plate, and a spring constant of the seal member in a direction supporting the movable plate is set to a value equal to or less than 1/2 of a spring constant of the spring member. And anti-vibration support device. 2. The electromagnetic actuator has a structure including a columnar yoke, and an exciting coil buried annularly on a surface of the yoke facing the movable plate, facing the movable plate. 2. The anti-vibration support device according to claim 1, wherein the second spacer contacting the facing surface is formed of a non-magnetic material.