JPH10252817A - Vibration control supporting device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To decide a characteristic of the force, which is to be generated by an actuator, on the basis of the only spring constant of a plate spring without lowering the durability of a seal member. SOLUTION: In this device, a peripheral part of a partitioning wall forming member 11A is formed with a rib part 11d, which is projected from a top surface side of the member 11A and connected in the circumferential direction, so as to enlarge the area of the peripheral surface of the partitioning wall forming member 11A. Outer diameter of the partitioning wall forming member 11A is enlarged, and a cross dimension (a) of a clearance between the peripheral surface of the partitioning wall forming member 11A and an upper spacer 5. Thickness of a seal member 16 is increased and the volume thereof is secured so that the seal member 16 is fixed between the peripheral surface of the rib 11d and the upper spacer 5, and a spring constant of the seal member 16 in the thickness direction (vertical direction) is reduced, and a spring constant thereof in the cross direction (horizontal direction) is increased so that the seal member is form soft in the thickness direction and hard in the cross direction. Spring constant of the seal member 16 in the thickness, direction is set sufficiently smaller in comparison with a spring constant of a plate spring 13 in the same direction.

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 supporting body such as a vehicle body while damping the vibration. In a vibration isolating support device, a fluid chamber is defined by a supported elastic body, and a vibration transmission rate can be reduced by actively changing the volume of the fluid chamber.
This is an improvement in the structure of a seal member provided to prevent leakage of a fluid in a fluid chamber.

[0002]

2. Description of the Related Art As a prior art of this kind, for example, FIG.
And Japanese Patent Application No. 8-59219 previously proposed by the present applicant.

More specifically, a vibration isolating support device as a prior art will be described with reference to FIG. 6. This vibration isolating support device 1 is a flat fixing member 2 fixed to a vibrating body such as an engine.
A bolt 2a for attachment to the engine is integrally provided on the upper surface of the fixing member 2, and the center of the upper surface of the supporting elastic body 3 is vulcanized and bonded to the back surface of the fixing member 2. ing.

The supporting elastic body 3 is a thick circular rubber-like elastic body whose central portion is raised above the peripheral edge portion, and its outer peripheral surface is vulcanized and bonded to the inner peripheral surface of the upper end portion of the cylindrical member 4. Have been. The cylindrical member 4 is fixed to the inner peripheral surface of the outer cylinder 7 together with the upper spacer 5 for fixing the seal member, the lower spacer 6 for supporting the leaf spring, and the edge 10a of the yoke 10A of the electromagnetic actuator 10. ing. That is, with the cylindrical member 4, the upper spacer 5, the lower spacer 6, and the edge 10a pressed into the inner surface of the outer cylinder 7 in this order, the upper end and the lower end of the outer cylinder 7 are bent inward. Thereby, each member is integrated.

The electromagnetic actuator 10 includes a cylindrical yoke 10A made of iron, an exciting coil 10B fixed on the upper surface of the yoke 10A with its axis up and down, and a yoke 10A.
Permanent magnet 1 fixed to the center of the upper surface with the poles pointing up and down
A fixing bolt (not shown) or the like is fixed to the lower end surface of the yoke 10A, and the yoke 10A is fixed to a support such as a vehicle body using the bolt.
Note that a weight sensor or the like (not shown) is interposed between the yoke 10A and the support to detect residual vibration required for vibration reduction control.

On the other hand, a movable member 11 is disposed above the electromagnetic actuator 10 so as to be vertically displaceable in the outer cylinder 7. The movable member 11 is composed of a substantially disk-shaped metal partition wall forming member 11A and a substantially disk-shaped iron magnetic path member 11B, and the partition wall forming member 11A and the magnetic path member 11B are formed. Is a partition wall forming member 11A located farther from the electromagnetic actuator 10.
Cylindrical portion 11a protruding downward from the center of the rear surface of
Is formed at the center of the magnetic path member 11B located closer to the electromagnetic actuator 10 and protrudes toward the upper surface side.
It is integrated by being press-fitted into 1b. A stopper member made of a ring-like rubber-like elastic body for preventing a direct collision between the magnetic path member 11B and the electromagnetic actuator 10 is provided on a peripheral edge of a lower surface (a surface on the side of the electromagnetic actuator 10) of the magnetic path member 11B. 11C is fixed.

[0007] The tip of the cylindrical portion 11b abuts against the back surface of the partition wall forming member 11A.
A ring-shaped continuous leaf spring accommodation space 12 is formed between the partition wall forming member 11A and the magnetic path member 11B. A leaf spring 13 for elastically supporting the movable member 11 is accommodated in the leaf spring accommodation space 12. The upper surface of the inner peripheral portion of the leaf spring 13 is
A supports a thick portion 11c formed so as to surround the distal end portion of the cylindrical portion 11b in the center of the back surface, and the outer peripheral back surface of the leaf spring 13 is formed into a ring shape formed on the inner peripheral surface of the lower spacer 6. The movable member 11 is elastically supported by the outer cylinder 7 via a leaf spring 13 by being supported by a support portion 6a formed of a continuous convex portion.

The upper surface of the partition wall forming member 11A is flat, and a fluid chamber 15 is formed by the upper surface, the lower surface of the support elastic member 3, and the inner peripheral surface of the cylindrical member 4.
A fluid is sealed in 5. However, in order to prevent the leakage of the fluid from the fluid chamber 15 to the leaf spring accommodating space 12 side, there is a gap between the outer peripheral surface of the partition wall forming member 11A of the movable member 11 that moves up and down and the inner peripheral surface of the upper spacer 5. , The sealing member 16 is fixed.

That is, the sealing member 16 is a ring-shaped rubber-like elastic body, and its inner peripheral surface is
1A is vulcanized and adhered to the outer peripheral surface of the upper spacer 5.
Is vulcanized and bonded to the inner peripheral surface of the movable member 11, and its elastic deformation allows relative displacement of the movable member 11 in the vertical direction with respect to the upper spacer 5 and the outer cylinder 7.

In the vibration isolating support device 1 having such a configuration, the magnetic force generated by the electromagnetic actuator 10 is changed by a drive signal supplied from a controller (not shown), and the movable member 11 is displaced in the vertical direction, so that the fluid chamber is displaced. 15 changes, and the change in volume acts on the expansion direction spring of the support elastic body 3, so that an active support force is generated between the fixing member 2 and the outer cylinder 7. Therefore, the electromagnetic actuator 10
By appropriately generating a drive signal to be supplied to the external member 7 according to an adaptive algorithm or the like, the vibration transmitted from the fixed member 2 side to the outer cylinder 7 side can be canceled or reduced by the supporting force, so that the vibration level on the supporting body side can be reduced. It can be reduced.

[0011]

Indeed, the anti-vibration support device 1 as shown in FIG. 6 is different from a mere passive support device made of a rubber-like elastic body or the like, and has an active support force. Can be generated, so that the vibration level on the support side can be reduced more remarkably.

The support force of the vibration isolating support device 1 is as follows:
As described above, since it is generated by a change in the volume of the fluid chamber 15 due to the vertical movement of the movable member 11, in order to generate a large supporting force, the pressure receiving area of the movable member 11,
That is, whether the area of the upper surface of the partition wall forming member 11A is increased,
At least one of increasing the vertical stroke of the movable member 11 or increasing the expansion direction spring of the support elastic body 3 may be realized. However, in order to increase the stroke of the movable member 11, it is necessary to mount the electromagnetic actuator 10 that is large enough, which is not desirable in terms of installation space and cost.
If the expansion direction spring is hardened, the support direction spring may be hardened and the vibration transmissibility may be deteriorated.

Therefore, in practice, in order to obtain a sufficient supporting force, it is necessary to increase the area of the upper surface of the partition wall forming member 11A.
When the area of the upper surface is increased, the outer diameter dimension is increased. Then, since the dimension of the outer cylinder 7 is restricted due to the space for disposing the vibration isolating support device 1, the width dimension (dimension a in FIG. 6) of the seal member 16 is inevitably reduced. .

The smaller the width of the seal member 16 is, the smaller the volume of the seal member 16 is.
As a result, the spring constant of the seal member 16 increases, and the movable member 11 is elastically supported by both the leaf spring 13 and the seal member 16. A supporting force generation system (a transmission system in which the magnetic force generated by the electromagnetic actuator 10 is input and the supporting force generated in the anti-vibration support device 1 is output) must be designed in consideration of the 16 spring constants. .
However, the spring constant of the seal member 16 made of a rubber-like elastic body changes under the influence of the temperature of the fluid in the fluid chamber 15 and also changes with time. For this reason, the characteristics of the force to be generated by the actuator are not determined, which hinders the design of a control system for favorably reducing vibration.

Further, when the volume of the sealing member 16 is reduced, there is a disadvantage that the durability of the movable member 11 against elastic deformation accompanying the vertical displacement is reduced. In order to increase the durability of the sealing member 16 made of a rubber-like elastic body,
Although the spring constant in the vertical direction may be increased, the spring constant of the seal member 16 cannot be ignored any more.

The present invention has been made in view of the unsolved problem of such a prior-art anti-vibration support device, and is capable of reducing the force generated by an actuator without reducing the durability of a seal member. It is an object of the present invention to provide an anti-vibration support device whose characteristics can be determined only by the spring constant of a leaf spring.

[0017]

In order to achieve the above object, the invention according to claim 1 is directed to a supporting elastic body, a first member to which one end of the supporting elastic body is fixed, and a supporting elastic body. A second member having the other end fixed thereto, a fluid chamber defined by the support elastic body and the second member, and having a fluid sealed therein; and a second member displaceable in a direction of changing a volume of the fluid chamber. A movable member elastically supported by the two members, and a force for displacing the movable member in response to a drive signal, supported by the second member so as to be located on the opposite side of the fluid chamber with respect to the movable member. The movable member has a partition wall forming part that forms a part of the partition wall of the fluid chamber, and the outer periphery of the partition wall forming part has the movable member displacement. Direction and continuous in the circumferential direction A sealing member is fixed over the entire circumferential direction between the outer peripheral surface of the partition wall forming portion including the outer peripheral surface of the rib portion and the inner peripheral surface of the second member. The member is elastically supported on the second member by a plate spring disposed on the opposite side of the fluid chamber with the seal member interposed therebetween, and the spring constant of the seal member in the movable member displacement direction is The spring constant of the leaf spring in the direction of displacement of the movable member is sufficiently small.

According to a second aspect of the present invention, in the vibration damping support device according to the first aspect, the second member is a cylindrical member, and the second member is provided at one end of the cylindrical member. The support elastic body is fixed, and the fluid chamber is defined by the support elastic body, an inner peripheral surface of the cylindrical member, and a partition wall forming portion of the movable member.

According to a third aspect of the present invention, in the anti-vibration support device according to the first or second aspect, the seal member is soft in the movable member displacement direction,
A hard elastic member is used in the direction of increasing or decreasing the gap between the partition wall forming portion and the second member.

According to a fourth aspect of the present invention, in the anti-vibration support device according to the first to third aspects, a plurality of seal members separated in the direction of displacement of the movable member are fixed as the seal members. .

According to a fifth aspect of the present invention, in the vibration-damping support device according to the fourth aspect of the present invention, a gap formed between the plurality of seal members and the actuator side with respect to the partition wall forming portion. A passage is provided for communication with the space.

According to a sixth aspect of the present invention, in the vibration damping support device according to the fifth aspect of the present invention, the passage is arranged at a position closest to the fluid chamber among the plurality of seal members. Holes penetrated other seal members except the members.

According to a seventh aspect of the present invention, in the vibration damping support device according to the first to sixth aspects, each of the movable member side end and the second member side end of the leaf spring is provided. Is a free end displaceable with respect to the movable member and the second member.

Further, according to an eighth aspect of the present invention, in the vibration-damping support device according to the first to seventh aspects, the leaf spring is formed by stacking a plurality of leaf springs. Here, in the invention according to claim 1, since the rib portion is formed on the outer peripheral portion of the partition wall forming portion, the rib portion is formed on the outer peripheral surface of the partition wall forming portion without greatly increasing the mass of the partition wall forming portion. The area increases. In addition, it is desirable that the outer peripheral surface of the partition wall forming portion itself and the outer peripheral surface of the rib portion be continuous without any level difference in order to avoid stress concentration on a part of the seal member.

If the area of the outer peripheral surface of the partition wall forming portion is increased, the size of the sealing member fixed between the outer peripheral surface of the partition wall forming portion and the second member in the thickness direction (movable member displacement direction) can be increased. . For this reason, even if the dimension of the seal member in the width direction (the width direction of the gap between the partition wall forming portion and the second member) is reduced, the volume of the seal member can be secured, which is advantageous for ensuring the durability of the seal member.

If the reduction in the durability of the seal member can be avoided by securing the volume, the spring constant in the thickness direction of the seal member can be reduced without any particular problem. That is, in the present invention, the spring constant in the thickness direction of the seal member is sufficiently smaller than the spring constant of the leaf spring in the same direction (for example, the former spring constant is reduced to about several percent of the latter spring constant). ), The durability of the seal member is not significantly reduced, and the spring constant in the thickness direction of the seal member can be substantially neglected. It can be determined only by the spring constant of the spring.

According to the second aspect of the present invention, since the second member is a cylindrical member, the fluid chamber can be easily defined, and it is convenient to dispose the seal member and the actuator. .

According to the third aspect of the present invention, the movable member is prevented from tilting because the seal member is hardened in the width direction by increasing the spring constant in the width direction of the seal member. It is advantageous above.

In the invention according to the fourth aspect, a plurality of seal members are provided, but the actual sealing function is achieved by the seal member which is disposed closest to the fluid chamber among the plurality of seal members. The function is achieved, and the total durability of the plurality of seal members is secured by the other seal members. Further, since the plurality of seal members are separated in the thickness direction, the spring constant in the thickness direction of the plurality of seal members as a whole can be suppressed low.

Further, if a predetermined passage is provided as in the invention according to the fifth and sixth aspects, air will not be trapped in the gap between the seal members. Even if the seal member expands due to the heat generated in the above, it is possible to prevent unnecessary stress from being applied to the seal member and the durability thereof from being impaired.

In the invention according to claim 7, since both ends of the leaf spring are free ends, the both ends of the leaf spring can be freely displaced in the plane direction. For this reason,
During the elastic deformation of the leaf spring accompanying the displacement of the movable member, it is possible to prevent stress from being concentrated on a specific part, and to avoid fatigue due to repetition.

In the invention according to claim 8, the required characteristics can be realized in detail and easily by appropriately selecting the spring constant of each leaf spring to be superimposed.

[0033]

According to the present invention, the structure is such that the spring constant in the thickness direction of the seal member can be substantially ignored without causing an increase in the mass of the movable member and a significant decrease in the durability of the seal member. A reduction in the active support force due to an increase in mass and a decrease in the durability of the vibration isolating support device itself can be avoided, and even if the spring constant of the seal member changes due to the influence of heat or deterioration over time, the force generated by the actuator is There is an effect that the transfer characteristic is not largely changed, which is advantageous in designing a control system for always obtaining a good vibration damping effect.

In particular, according to the third aspect of the invention, the movable member can be hardly inclined, so that the possibility that the movable member collides with the actuator can be reduced. Further, with the invention according to claim 4, it is possible to ensure the durability of the seal member and reduce the spring constant in the thickness direction of the seal member.
Relatively easy to achieve.

According to the fifth and sixth aspects of the invention, there is an effect that the durability of the seal member can be further improved. Further, according to the invention of claim 7, there is an effect that the durability of the leaf spring can be improved.

Further, according to the invention of claim 8, there is an effect that the degree of freedom of design is increased, and as a result, the design cost can be reduced.

[0037]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 3 are views showing a first embodiment of the present invention. FIG. 1 is a schematic diagram of a vehicle to which an active vibration control device which is an embodiment of a vibration isolation support device according to the present invention is applied. It is a side view.

First, the structure will be described. A vehicle body including suspension members and the like is provided via an anti-vibration support device (active engine mount) 1 in which an engine 30 can generate an active support force according to a drive signal. It is supported by 35. Actually, between the engine 30 and the vehicle body 35, a plurality of engine mounts that generate a passive supporting force according to the relative displacement between the engine 30 and the vehicle body 35 are interposed in addition to the vibration isolating support device 1. ing. As a passive engine mount, for example, a normal engine mount that supports a load with a rubber-like elastic body, or a known fluid-filled mount in which a fluid is sealed inside a rubber-like elastic body so that a damping force can be generated. An insulator or the like can be applied.

FIG. 2 shows a specific configuration of the vibration isolation support device 1. The same members and parts as those of the preceding vibration isolator and support device shown in FIG. 6 are denoted by the same reference numerals, and redundant description will be omitted.

That is, the anti-vibration support device 1 in the present embodiment is similar to the anti-vibration support device shown in FIG.
By changing the volume of the fluid chamber 15 by the vertical displacement of 1, the expansion direction spring of the support elastic body 3 is deformed to generate an active support force. Also,
The movable member 11 is elastically supported on the outer cylinder 7 side by a leaf spring 13 accommodated in the leaf spring accommodation space 12, similarly to the configuration in FIG. The leaf spring 13 is formed by stacking a plurality of (in this example, three) leaf springs 13A made of metal having a planar shape as shown in FIG. 3, and each leaf spring 13A is shown in FIG. As shown in FIG.
And a plurality of arms 13b extending from the periphery 13a toward the center. And the peripheral part 13
a is supported on the upper surface of the support portion 6a formed on the lower spacer 6, and the arm portion 13b supports the thick portion 11c from below.

As described above, the leaf spring 13 is connected to the plurality of leaf springs 1.
The reason why the 3A is overlapped is that the characteristics required for the leaf spring 13 can be realized in detail and easily by appropriately selecting the spring constant and the like of each leaf spring 13A.

The arm 13b as an end on the movable member side
The tip is displaceable (only in contact with) the thick portion 11c, and the peripheral portion 1 as the second member side end
3a is also displaceable (only in contact) with respect to the support 6a. That is, the inner end and the outer end of the leaf spring 13 are free ends, and can be displaced in the horizontal direction along with the vertical displacement of the movable member 11. This is to prevent stress from being concentrated on a specific part during the elastic deformation of the leaf spring 13 due to the vertical displacement of the movable member 11, and to avoid repetitive metal fatigue.

In the present embodiment, the rib 11 is formed on the outer peripheral portion of the partition wall forming member 11A constituting the movable member 11 so as to protrude toward the upper surface side and continue in the circumferential direction.
d is formed. The rib portion 11d is a short cylindrical protrusion that rises so as to prevent a step from being formed between the rib portion 11d and the outer peripheral surface of the partition wall forming member 11A, and substantially increases the area of the outer peripheral surface of the partition wall forming member 11A. ing.

Further, in the present embodiment, the outer diameter of the partition wall forming member 11A is increased so that the width dimension a of the gap between the outer peripheral surface of the partition wall forming member 11A and the upper spacer 5 is increased.
Is made smaller than the case shown in FIG. Therefore, the width dimension a of the seal member 16 fixed in the gap is smaller than that in the case shown in FIG.

However, the outer peripheral surface of the rib 11d and the upper spacer 5
Since the thickness of the seal member 16 is increased so that the seal member 16 is also fixed between them, the volume of the seal member 16 is equal to that shown in FIG. The spring constant of the seal member 16 is different between the thickness direction (vertical direction in FIG. 2) and the width direction (horizontal direction in FIG. 2). Specifically, the spring constant in the thickness direction is small, and the spring constant in the width direction is small. The spring constant has increased. Therefore, the seal member 16 is a member that is soft in the thickness direction and hard in the width direction.

Further, the spring constant in the thickness direction of the sealing member 16 is selected to be sufficiently smaller than the spring constant of the leaf spring 13 in the same direction. For example, the spring constant in the thickness direction of the seal member 16 is set to about several percent of the spring constant of the leaf spring 13 in the same direction.

On the other hand, the exciting coil 10 B of the electromagnetic actuator 10 generates a predetermined electromagnetic force in accordance with a drive signal y which is a current supplied from the controller 25. The controller 25 includes a microcomputer, necessary interface circuits, an A / D converter, and a D / A
The anti-vibration support device 1 includes a converter, an amplifier, a storage medium such as a ROM and a RAM, and generates an active support force that can reduce vibration generated in the engine 30. Is generated and output.

Here, for example, in the case of a reciprocating four-cylinder engine, the engine vibration of the engine rotation secondary component is generated by the vehicle body 3
The main reason is that the drive signal y is generated and output in synchronization with the engine rotation secondary component, so that the vehicle body side vibration can be reduced. Therefore, in the present embodiment, an impulse signal synchronized with the rotation of the crankshaft of the engine 30 (for example, in the case of a reciprocating four-cylinder engine, one for each rotation of the crankshaft by 180 degrees) is generated and the reference signal x Pulse signal generator 26 which outputs as
, And the reference signal x is supplied to the controller 25.

The yoke 1 of the electromagnetic actuator 10
A load sensor (not shown) is sandwiched between the lower end surface of 0A and the vehicle body 35, and the detection result of the weight sensor is supplied to the controller 25 as a residual vibration signal e. As the load sensor, a piezoelectric element, a magnetostrictive element, a strain gauge, or the like can be applied.

Then, based on the supplied residual vibration signal e and reference signal x, the controller 25 uses a synchronous filtered filter which is one of the successively updating adaptive algorithms.
By executing the XLMS algorithm, a drive signal y for the anti-vibration support device 1 is calculated, and the drive signal y
Is output to the anti-vibration support device 1.

More specifically, the controller 25 has an adaptive digital filter W having a variable filter coefficient W _i (i = 0, 1, 2,..., I-1: I is the number of taps). At a predetermined sampling clock interval from the time when the reference signal x is input, the adaptive digital filter W
Of one of outputting a filter coefficient W _i in the order as the drive signal y, it is adapted to execute a process of appropriately updating the filter coefficient W _i of the adaptive digital filter W based on the reference signal x and the residual vibration signal e.

The updating equation of the adaptive digital filter W is expressed by F
The following equation (1) is obtained according to the filtered-X LMS algorithm. _{W i (n + 1) =} W i (n) -μR T e (n) ...... (1) where, indicates that the value in (n), (n + 1 ) term is attached is sampling time n, n + 1, μ is a convergence coefficient. The update reference signal R ^T is theoretically expressed as
The reference signal x is transmitted to the electromagnetic actuator 1 of the vibration isolator 1
0 and a value obtained by filtering a transfer function C between the load sensors with a transfer function filter C ＾ modeled by a finite impulse response filter, and the magnitude of the reference signal x is “1”.
Therefore, when the impulse responses of the transfer function filter C ＾ are generated one after another in synchronization with the reference signal x, they coincide with the sum of the impulse response waveforms at the sampling time n. Also, theoretically, the reference signal x is filtered by the adaptive digital filter W to generate the drive signal y. However, since the size of the reference signal x is “1”, the filter coefficient W _i is sequentially determined. Output as the drive signal y to
The result is the same as when the result of the filter processing is the drive signal y.

Next, the operation of this embodiment will be described. That is, in a situation where idle vibration or muffled sound vibration is generated in the engine 30, the sampling clock of the sampling clock is input from the controller 25 to the electromagnetic actuator 10 of the anti-vibration support device 1 from the time when the reference signal x is input. At intervals, the filter coefficients W _i of the adaptive digital filter W are sequentially supplied as drive signals y.

As a result, the drive signal y is supplied to the exciting coil 10B.
However, since a constant magnetic force is already applied to the magnetic path member 11B by the permanent magnet 10C, the magnetic force of the exciting coil 10B is generated by the permanent magnet 10C.
Act to increase or decrease the magnetic force of. That is, in a state where the drive signal y is not supplied to the excitation coil 10B, the movable member 11 including the magnetic path member 11B applies the supporting force of the leaf spring 13 and the permanent magnet 10C.
Will be displaced to a neutral position that is balanced with the magnetic force. When the drive signal y is supplied to the exciting coil 10B in this neutral state, if the magnetic force generated in the exciting coil 10B by the drive signal y is in the opposite direction to the magnetic force of the permanent magnet 10C, the movable member 11 Actuator 10
Is displaced in the direction in which the clearance with the 増 大 increases. Conversely, if the magnetic force generated in the exciting coil 10B is in the same direction as the magnetic force of the permanent magnet 10C, the movable member 11 is displaced in a direction in which the clearance with the electromagnetic actuator 10 decreases.

As described above, the movable member 11 can be displaced in both the forward and reverse directions.
The partition wall forming member 11A forming a part of the partition wall is also displaced,
As a result, the volume of the fluid chamber 15 changes, and the expansion spring of the support elastic body 6 is deformed by the change in volume, so that the anti-vibration support device 1 generates an active support force in both forward and reverse directions.

Each filter coefficient W _i of the adaptive digital filter W serving as the drive signal y is determined by a synchronous Filtered-
Since the sequentially updated by according to X LMS algorithm above (1), after the convergence to the optimal values each filter coefficient W _i of the adaptive digital filter W has passed a certain time, the drive signal y is antivibration By being supplied to the support device 1, idle vibration and muffled sound vibration transmitted from the engine 30 to the vehicle body 35 via the vibration isolation support device 1 are reduced.

In the present embodiment, since the outer diameter of the partition wall forming member 11 of the movable member 11 is increased to increase the area of the upper surface, the fluid chamber with respect to the stroke of the movable member 11 is increased. 15 can be made larger than the case shown in FIG. As a result, it is extremely advantageous to generate a sufficiently large supporting force without using a large-sized electromagnetic actuator 10 or making the expansion direction spring of the supporting elastic body 3 hard.

Further, since the volume of the seal member 16 does not always decrease significantly, the durability of the seal member 16 against the vertical displacement of the movable member 11 is not reduced, and the thickness direction spring constant of the seal member 16 is not reduced. To the leaf spring 1
3, the spring constant in the thickness direction of the seal member 16 is made sufficiently smaller than that in the same direction so that the spring constant in the thickness direction of the seal member 16 can be substantially ignored even if it changes due to various causes. There is an advantage that the characteristics of the generated force can be determined in consideration of only the spring constant of the leaf spring 13.

Further, since the width dimension a of the seal member 16 is reduced and the spring constant in the width direction is increased, the structure is very advantageous in that the inclination of the movable member 11 is prevented. That is, the electromagnetic actuator 10
When the electromagnetic actuator 10 attracts the movable member 11, the movable member 11 remains strictly horizontal due to the unevenness of the generated electromagnetic force in the circumferential direction and the unevenness of the spring constant of the leaf spring 13 in the circumferential direction. Instead of approaching the electromagnetic actuator 10, the inclined movable member 11 becomes larger as it approaches the electromagnetic actuator 10 because the magnetic force generated by the electromagnetic actuator 10 is inversely proportional to the square of the distance. The movable member 11 tends to tilt, and the movable member 11
, A part in the circumferential direction collides with the yoke 10 </ b> A or the like (one side contact) and causes abnormal noise. On the other hand, it cannot be expected that the movable member 11 is prevented from being tilted in the leaf spring 13 whose inner and outer ends are free ends.

On the other hand, if the width direction spring constant of the seal member 16 is large, the elastic deformation restoring force in the width direction of the seal member 16 effectively functions to prevent the movable member 11 from tilting. As a result, a large inclination of the movable member 11 can be prevented, so that the possibility of the movable member 11 coming into contact with the electromagnetic actuator 10 can be further reduced.

In this embodiment, since the area of the outer peripheral surface of the partition wall forming member 11A is substantially increased by forming the rib portion 11d, the partition wall forming member 11A is formed in order to increase the area of the outer peripheral surface. Unlike a measure for increasing the thickness of the member 11 itself, there is an advantage that the mass of the movable member 11 does not need to be increased. Incidentally, when the mass of the movable member 11 is increased, the stroke of the movable member 11 is reduced as much as the output of the electromagnetic actuator 10 is the same, and the generated force is reduced.

Here, in this embodiment, the fixing member 2 corresponds to the first member, and the cylindrical member 4, the upper spacer 5, the lower spacer 6, and the outer cylinder 7 correspond to the second member. The partition wall forming member 11A corresponds to a partition wall forming portion.

FIGS. 4 and 5 are views showing a second embodiment of the present invention. In this embodiment, as in the first embodiment, the anti-vibration support device 1 according to the present invention is used. Since the present invention is applied to a vehicle, and the overall configuration is the same as that of the first embodiment, its illustration and description are omitted. FIG.
2 is a cross-sectional view showing the configuration of the vibration isolation support device 1 in the same manner as FIG. 2 of the first embodiment, and the same members and portions as those in FIG. Description is omitted.

That is, in the present embodiment, two seal members 16A and 16B are fixed between the outer peripheral surface of the partition wall forming member 11A and the inner peripheral surface of the upper spacer 5. One sealing member 16A is fixed between the outer peripheral surface of the rib portion 11d and the inner peripheral surface of the upper spacer 5.
Separates the fluid chamber 15 from the leaf spring accommodating space 12. The other seal member 16B is separated from the seal member 16A so that a gap is formed between the seal member 16A and the seal member 16B, specifically, a portion of the outer peripheral surface of the partition wall forming member 11A near the leaf spring accommodating space 12. It is fixed between the upper spacer 5 and the inner peripheral surface.

Each of these seal members 16A and 16B is a member made of a ring-like rubber-like elastic material.
As shown in FIG. 5 which is a plan sectional view of the sealing member 16B fixed downward, holes 16a as passages penetrating in the vertical direction are formed at four locations equally spaced in the circumferential direction. ing.

Therefore, the gap between the seal members 16A and 16B is formed by the partition wall forming member 11A through the holes 16a.
It communicates with the leaf spring accommodating space 12 on the electromagnetic actuator 10 side.

The other structure is the same as that of the first embodiment. Even with such a configuration, the volume of the entire seal member is secured by the two seal members 16A and 16B. Therefore, even if the width dimension a is reduced, the durability of the entire seal member does not decrease. . Accordingly, the spring constants of the seal members 16A and 16B in the thickness direction and the width direction are set to be equal to those of the seal member 16 of the first embodiment.
There is no problem even in the case of the first embodiment. By doing so, the same operation and effect as in the first embodiment can be obtained. In this case, since the two seal members 16A and 16B are fixed vertically separated from each other, the thickness of the entire seal member is smaller than that of the first embodiment in which one seal member 16 is fixed. It is easy to reduce the spring constant in the width direction and increase the spring constant in the width direction.

Further, in the present embodiment, since the hole 16a is formed in the lower seal member 16B, the air in the space between the seal members 16A and 16B expands due to the heat generated from the electromagnetic actuator 10. However, it is possible to prevent the internal pressure of the space from rising. Therefore, it is possible to prevent the durability of the seal members 16A and 16B from being reduced due to the stress due to the increase in the internal pressure.

In each of the above-described embodiments, the vibration isolating support device 1 is not configured to generate fluid resonance. For example, the variable-capacity auxiliary fluid chamber defined by a diaphragm or the like is provided outside. A mass-spring system is provided around the cylinder 7 and communicates the auxiliary fluid chamber and the fluid chamber 15 via an orifice, the fluid in the orifice is used as a mass, and the expansion direction spring of the support elastic body 3 and the diaphragm are used as springs. By making the resonance frequency substantially equal to the frequency of the engine shake, for example, it can be used as a general fluid-filled type vibration-proof support device.

The object to which the present invention is applied is not limited to a vehicle. The present invention can be applied to an anti-vibration support device for reducing vibrations generated except for the engine 30. Regardless of the above, the same operation and effect as those of the above embodiments can be obtained. For example, the present invention is applicable to an anti-vibration support device that reduces vibration transmitted from a machine tool to a floor or a room.

Further, in each of the above embodiments, the synchronous filter is used as an algorithm for generating the drive signal y.
Although the dX LMS algorithm is applied, the applicable algorithm is not limited to this, and may be, for example, a normal Filtered-X LMS algorithm or the like.

[Brief description of the drawings]

FIG. 1 is a schematic side view of a vehicle showing a first embodiment.

FIG. 2 is a cross-sectional view illustrating a configuration of an anti-vibration support device.

FIG. 3 is a plan view of a leaf spring.

FIG. 4 is a cross-sectional view illustrating a configuration of an anti-vibration support device according to a second embodiment.

FIG. 5 is a plan sectional view of a seal member fixed downward.

FIG. 6 is a cross-sectional view illustrating a configuration of a preceding anti-vibration support device.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 anti-vibration support device 2 fixing member (first member) 3 supporting elastic body 4 cylindrical member (second member) 5 upper spacer (second member) 6 lower spacer (second member) 7 outer cylinder (second member) 10 electromagnetic actuator 11 movable member 11A partition wall forming member 11B magnetic path member 11d rib portion 12 leaf spring accommodation space 13 leaf spring 15 fluid chamber 16 seal member 16A, 16B seal member 16a hole (passage)

Claims (8)

[Claims] 1. A support elastic body, a first member to which one end of the support elastic body is fixed, a second member to which the other end of the support elastic body is fixed, the support elastic body, and the second member A fluid chamber defined therein and having a fluid sealed therein, and the second fluid chamber being displaceable in a direction of changing the volume of the fluid chamber.
A movable member elastically supported by a member, and a force generated by the second member so as to be located on a side opposite to the fluid chamber with the movable member interposed therebetween and displacing the movable member in response to a drive signal; The movable member has a partition wall forming part that forms a part of the partition wall of the fluid chamber, and the outer peripheral portion of the partition wall forming part has the movable member displacement direction. A rib portion that protrudes in the circumferential direction and is formed in the circumferential direction, and a seal is formed over the entire circumferential direction between the outer circumferential surface of the partition wall forming portion including the outer circumferential surface of the rib portion and the inner circumferential surface of the second member. While the member is fixed, the movable member is elastically supported by the second member by a plate spring disposed on the opposite side of the seal member from the fluid chamber, and the movable member of the seal member The spring constant in the displacement direction is An anti-vibration support device, wherein the spring constant is sufficiently smaller than a spring constant of the movable member in a direction of displacement of the movable member. 2. The second member is a cylindrical member,
The support elastic body is fixed to one end side of the cylindrical member, and the fluid chamber is defined by the support elastic body, an inner peripheral surface of the cylindrical member, and a partition forming portion of the movable member. 2. The anti-vibration support device according to claim 1, wherein: 3. The prevention device according to claim 1, wherein the sealing member is an elastic member that is soft in a direction in which the movable member is displaced and hard in a direction in which a gap between the partition wall forming portion and the second member increases and decreases. Vibration support device. 4. A plurality of seal members separated from each other in a direction in which the movable member is displaced are fixed as the seal members.
An anti-vibration support device according to claim 3. 5. The anti-vibration support device according to claim 4, wherein a passage is provided for communicating a gap formed between the plurality of seal members with a space closer to the actuator than the partition wall forming portion. 6. The anti-vibration support device according to claim 5, wherein the passage is a hole penetrating another seal member of the plurality of seal members except a seal member disposed closest to the fluid chamber. 7. The movable member-side end and the second member-side end of the leaf spring are each a free end displaceable with respect to the movable member and the second member.
An anti-vibration support device according to claim 6. 8. The anti-vibration support device according to claim 1, wherein the leaf spring is configured by stacking a plurality of leaf springs.