JPH1078079A - Vibration isolating support device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To surely prevent collision between a movable member and an electromagnetic actuator. SOLUTION: In a lower surface side in a central part 11A of a leaf spring 11, a magnetic path member 12 consisting of magnetisable material is fixed. A central part 12A of the magnetic path member 12 is a disk-shaped member with a thickness a little thicker than the other part and a protruding side of this central part 12A of large thickness is fixed to a side of the leaf spring 11 to be faced thereto. External diametric dimension of the magnetic path member 12 is formed a little larger than an external diameter of an excitation coil 10B of an electromagnetic actuator 10, a peripheral edge part 12B thereof is opposed to a surface of a yoke 10A in the outer side from the excitation coil 10B. In a side of the electromagnetic actuator 10 in the peripheral edge part 12B of the magnetic path member 12, a notch 12C is formed over a total periphery of the magnetic path member 12 and in this notch C, a rubber ring 13 formed of rubber-shaped elastic unit is fixed to a total region by vulcanization bonding. A contact surface 13A of the rubber ring 13 is formed in a thickness of degree slightly protruding from a lower surface of the magnetic path member 12.

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, which generates vibrations while supporting the supporting body such as a vehicle body while damping the vibration. Defining a fluid chamber by a supporting elastic body,
An anti-vibration support device adapted to change a container of the fluid chamber by displacing a movable member forming a part of a partition of the fluid chamber by a magnetic force of an electromagnetic actuator, thereby generating an active support force. In this case, the collision between the movable member and the electromagnetic actuator, which causes abnormal noise, can be reliably prevented, the durability is improved, and the output of the anti-vibration support device is advantageously increased.

[0002]

2. Description of the Related Art As a conventional anti-vibration support device, there is a device disclosed in Japanese Patent Application Laid-Open No. Hei 7-310776 previously proposed by the present applicant. The anti-vibration support device disclosed in the above publication is
A fluid-filled anti-vibration support device capable of generating an active support force, comprising: a support elastic body interposed between a vibrator and a support; and a fluid chamber defined by the support elastic body. The fluid chamber is provided with a movable member elastically supported so as to seal the fluid and change the volume of the fluid chamber. Then, the movable member is appropriately displaced by an electromagnetic actuator composed of a permanent magnet and an electromagnet to change the volume of the fluid chamber, to elastically deform the support elastic body in the expansion direction, and to reduce the vibration transmitted to the vibration isolation support device. A control force that can be offset is generated.

Further, in the vibration isolating support device disclosed in the above-mentioned publication, an auxiliary elastic body is interposed between the movable member and the electromagnetic actuator. Since the supporting force of the movable member can be made to have a two-stage characteristic while preventing a direct collision with the electromagnetic actuator, there is an advantage that the movable member can behave stably. In the above publication, the auxiliary elastic body functioning as a stopper member is interposed between the end surface of the bobbin of the electromagnet constituting the electromagnetic actuator and the movable member so as not to affect the performance of the electromagnetic actuator. Examples are disclosed.

[0004]

Indeed, according to the anti-vibration support device disclosed in the above publication, an auxiliary elastic body functioning as a stopper member is interposed between the movable member and the electromagnetic actuator. Therefore, it is possible to avoid collision between the movable member and the electromagnetic actuator by appropriately selecting the thickness and the like of the auxiliary elastic body.

However, the present inventors have conducted more detailed experiments and the like. As a result, the structure in which the auxiliary elastic body is interposed between the end surface of the bobbin of the electromagnet and the movable member as described above is as follows.
To avoid collision between the movable member and the electromagnetic actuator,
In addition, it was found that the structure was disadvantageous for obtaining sufficient durability. Further, it has been found that the configuration in which the auxiliary elastic body as the stopper member is directly adhered to the back surface of the movable member as disclosed in the above-mentioned publication may lead to a decrease in the output of the vibration isolation support device.

The present invention has been made in view of the problems that have not been solved in such a conventional anti-vibration support device, and it is possible to reliably prevent a collision between a movable member and an electromagnetic actuator, and to improve durability. It is another object of the present invention to provide a vibration isolating support device having a structure that is advantageous in increasing the output of the vibration isolating support device.

[0007]

In order to achieve the above object, according to the first aspect of the present invention, there is provided a supporting elastic body interposed between a vibrating body and a supporting body, and a fluid chamber defined by the supporting elastic body. And a fluid sealed in the fluid chamber, a movable member forming a part of the partition of the fluid chamber and displaceable in a direction for changing the volume of the fluid chamber, and displacing the movable member in the direction. An electromagnetic actuator that generates a force,
In the anti-vibration support device provided with, a stopper member for preventing collision between the movable member and the electromagnetic actuator, between the peripheral edge of the surface of the movable member facing the electromagnetic actuator and the electromagnetic actuator It is arranged to exhibit the stopper function.

In order to achieve the above object, the invention according to claim 2 provides a supporting elastic body interposed between the vibrating body and the supporting body, a fluid chamber defined by the supporting elastic body, and a fluid chamber defined by the supporting elastic body. A sealed fluid, a movable member forming a part of a partition of the fluid chamber and displaceable in a direction for changing the volume of the fluid chamber, and an electromagnetic actuator for generating a force for displacing the movable member in the direction And a leaf spring whose peripheral portion is supported on a side of the vibrating body and the support body to which the electromagnetic actuator is attached, and a movable portion formed of a magnetizable material and a central portion of the leaf spring. A magnetic path member fixed to the electromagnetic actuator side surface, and in a vibration isolation support device including a stopper member for preventing a collision between the magnetic path member and the electromagnetic actuator, It is disposed so as to exert a stopper function between the periphery of the surface facing the electromagnetic actuator side of the serial magnetic path member and the said electromagnetic actuator.

According to a third aspect of the present invention, in the vibration damping support device according to the first and second aspects, the stopper member is a rubber-like elastic body. According to a fourth aspect of the present invention, in the anti-vibration support device according to the second aspect of the present invention, a recess is formed in a peripheral portion of a surface of the magnetic path member facing the electromagnetic actuator, and a recess is formed in the recess. A rubber-like elastic body was provided as the stopper member.

Further, according to a fifth aspect of the present invention, in the vibration damping support device according to the fourth aspect of the present invention, the concave portion is formed on the entire peripheral portion, and the rubber-like elastic material is formed over the entire region of the concave portion. Was arranged.

According to a sixth aspect of the present invention, in the vibration damping support device according to the fourth aspect of the present invention, the concave portions are formed intermittently in the peripheral portion, and the rubber-like elastic members are provided in each of the concave portions. Was arranged.

According to a seventh aspect of the present invention, in the anti-vibration support device according to the fourth to sixth aspects, the recess is a notch formed at a corner of the peripheral edge.
According to an eighth aspect of the present invention, in the vibration damping support device according to the fourth to seventh aspects, the concave portion is formed such that an outer peripheral side of the magnetic path member is deeper than a central side. did.

According to a ninth aspect of the present invention, in the vibration damping support device according to the eighth aspect of the present invention, the thickness of the rubber-like elastic body is set such that the outer peripheral side of the magnetic path member is closer to the center. Thicker than

According to a tenth aspect of the present invention, in the vibration damping support device according to the fourth to ninth aspects, a nonmagnetic material is provided on the electromagnetic actuator side so as to abut the rubber-like elastic body. Was formed.

According to an eleventh aspect of the present invention, in the vibration damping support device according to the fourth to ninth aspects, a resin member is fixed to an end surface of the rubber-like elastic body on the side of the electromagnetic actuator. did.

According to a twelfth aspect of the present invention, in the vibration damping support device according to the second aspect of the present invention, the stopper member includes a peripheral portion of a surface of the magnetic path member facing the electromagnetic actuator and the peripheral portion. A resin member fixed to at least one of the electromagnetic actuator.

Here, in the invention according to claim 1,
Since the position of the stopper member for preventing direct collision between the movable member and the electromagnetic actuator is specified as described above, not only when the movable member approaches the electromagnetic actuator while being parallel, but also when the movable member Even when approaching the electromagnetic actuator with a large inclination, the stopper function can be reliably exhibited. In other words, the movable member may approach the electromagnetic actuator while being inclined, for example, due to variations in the characteristics of the member supporting the movable member in the circumferential direction and variations in the magnetic force generated by the electromagnetic actuator in the circumferential direction. Even in the case of such an inclination, if the position of the stopper member is set as in the invention according to the first aspect, it is possible to reliably prevent a direct collision between the movable member and the electromagnetic actuator.

If the stopper member is disposed at the above position, the stopper member can be disposed outside the magnetic circuit constituted by the electromagnetic actuator and the movable member. For this reason, since the stopper member can be made independent from the design of the magnetic circuit, it can be designed independently according to each functional requirement.

Also, in the invention according to claim 2, the position of the stopper member for preventing a direct collision between the magnetic path member constituting the movable member and the electromagnetic actuator is specified as described above. Therefore, not only when the magnetic path member approaches the electromagnetic actuator while being parallel, but also when the magnetic path member approaches the electromagnetic actuator in a state where the magnetic path member is greatly inclined, the stopper function can be reliably exhibited.
Since the stopper member can be made independent from the design of the magnetic circuit, it can be designed independently according to each functional requirement.

According to the third aspect of the present invention, the rubber-like elastic member as the stopper member is provided so that when the movable member or the magnetic path member is too close to the electromagnetic actuator, the peripheral portion of the movable member or the magnetic path member and the electromagnetic actuator are connected to each other. Since the elastic member is elastically deformed in the compression direction, the function as the stopper member can be surely exhibited. The rubber-like elastic body may be fixed to the periphery of the movable member or the magnetic path member, or may be fixed to a predetermined portion of the electromagnetic actuator facing the periphery.

According to the fourth aspect of the present invention, the rubber-like elastic body as the stopper member is not directly fixed to the peripheral surface of the magnetic path member, but is formed in the peripheral section of the magnetic path member. For example, even if the thickness of the rubber-like elastic body protruding from the surface of the magnetic path member is not so large, the amount of compressive deformation when the rubber-like elastic body functions as a stopper member is reduced. The magnetic path member can be made closer to the electromagnetic actuator than when the rubber-like elastic body is directly fixed to the surface of the magnetic path member. That is, when the rubber-like elastic body is directly fixed to the surface of the magnetic path member, the spring constant of the rubber-like elastic body increases dramatically with the increase in the amount of compressive deformation. The magnetic path member cannot be brought closer to the electromagnetic actuator side than when the compression deformation of the rubber-like elastic body sandwiched therebetween becomes substantially impossible. On the other hand, when the rubber-like elastic body is provided as in the invention according to claim 4, when the rubber-like elastic body functions as the stopper member, the portion that is accommodated in the concave portion of the magnetic path member is also compressed and deformed. To do
By appropriately selecting the thickness and the like of the rubber-like elastic body so that the spring constant of the rubber-like elastic body becomes extremely large when the magnetic-path member comes extremely close to the electromagnetic actuator, the magnetic-path member and the electromagnetic actuator can be connected to each other. The magnetic path member can be brought extremely close to the electromagnetic actuator side while reliably preventing a direct collision. Then, as the approach amount of the magnetic path member to the electromagnetic actuator decreases, the stroke range of the magnetic path member increases accordingly, and as the stroke range of the magnetic path member increases, the volume fluctuation range of the fluid chamber also increases. This is advantageous in generating a large supporting force in the vibration isolating support device.

Furthermore, if the rubber-like elastic body is disposed over the entire peripheral portion of the magnetic path member as in the invention according to claim 5, the magnetic path member can be tilted no matter what state the magnetic path member is inclined. Direct collision between the actuator and the electromagnetic actuator can be reliably prevented.
Further, even when the rubber-like elastic bodies are arranged so as to be scattered around the periphery of the magnetic path member as in the invention according to claim 6, by appropriately setting the arrangement interval of each rubber-like elastic body, Direct collision between the road member and the electromagnetic actuator can be reliably prevented, and the amount of the rubber-like elastic material used can be reduced by the amount of the rubber-like elastic material dispersed.

The recess for disposing the rubber-like elastic body may be a groove, a hole, or the like. There is an advantage that it can be completed.

Further, as in the invention according to claim 8, it is preferable that the concave portion for disposing the rubber-like elastic body is formed so that the outer peripheral side of the magnetic path member is deeper than the central side. In this case, for example, if the rubber-like elastic body has a uniform thickness, the contact surface of the rubber-like elastic body with the electromagnetic actuator is:
The outer periphery of the magnetic path member is relatively retracted more than the center side, but in such a case, if the magnetic path member approaches the electromagnetic actuator while being inclined, a wider portion of the contact surface of the rubber-like elastic body is electromagnetically retracted. Since it comes into contact with the actuator, the entire stopper member receives a compressive load, which is preferable in terms of durability.

On the other hand, the thickness of the rubber-like elastic body may be greater on the outer peripheral side of the magnetic path member than on the central side, as in the ninth aspect of the present invention. In other words, since the magnetic path member approaches the electromagnetic actuator while being inclined, the rubber-like elastic body tends to be more worn on the outer peripheral side of the magnetic path member than on the center side. If the thickness is made thicker, there is an advantage that the service life is extended.

Further, in the invention according to claim 10,
Since the rubber-like elastic body fixed to the magnetic path member comes into contact with the layer made of a non-magnetic material provided on the electromagnetic actuator side, the wear of the rubber-like elastic body can be suppressed. In other words, the layer made of a non-magnetic material is not affected by the magnetic flux generated by the electromagnetic actuator, and its temperature is lower than that of the yoke of the electromagnetic actuator. The body is less likely to wear.

Further, if a member made of resin (for example, synthetic resin such as PTFE) is fixed to the rubber-like elastic body as in the invention according to claim 11, a low spring constant by the rubber-like elastic body can be secured. The wear resistance of the contact portion of the stopper member can be improved.

According to the twelfth aspect, the peripheral portion of the magnetic path member and the electromagnetic actuator collide indirectly via the resin (for example, synthetic resin such as PTFE) serving as the stopper member. As compared with the case where the magnetic path member made of a magnetic material such as iron and the yoke directly collide with each other, their wear resistance is improved. In particular, when the electromagnet of the electromagnetic actuator is disposed in the yoke, when the resin is poured around the bobbin of the electromagnet, a portion of the end face of the yoke facing the peripheral edge of the magnetic path member is used. The resin member as the stopper member can be substantially provided on the side of the electromagnetic actuator only by expanding the width of the stopper member, so that the stopper member can be provided without increasing the number of parts and the like.

[0029]

As described above, according to the present invention, the position of the stopper member is appropriately selected. Therefore, even when the movable member or the magnetic path member approaches the electromagnetic actuator while being inclined, the movable member can be moved. And the magnetic path member can be prevented from directly colliding with the electromagnetic actuator,
There is an effect that generation of abnormal noise and wear of each member can be prevented.

In particular, in the invention according to claim 4, since a concave portion for arranging the rubber-like elastic body is formed in the peripheral portion of the magnetic path member, direct collision between the magnetic path member and the electromagnetic actuator is ensured. Since the magnetic path member can be brought extremely close to the electromagnetic actuator side while preventing the vibration, the vibration-proof support device is advantageous in generating a large supporting force, and a good vibration-proof effect can be obtained.

According to the invention of claim 5, since the direct collision between the magnetic path member and the electromagnetic actuator can be more reliably prevented, the effect of the present invention can be more reliably exhibited.
On the other hand, according to the invention of claim 6, the amount of the rubber-like elastic material used can be reduced by the amount of the rubber-like elastic material dispersed, which is advantageous in cost.

The invention according to claim 7 is advantageous in reducing the manufacturing cost because the labor of processing the notch as the concave portion can be simplified. Furthermore, the invention according to claims 8 and 9 is advantageous for improving the durability of the stopper member and extending the service life.

According to the tenth aspect of the present invention, the rubber-like elastic body can be made harder to wear, which is more advantageous for improving the durability of the stopper member and extending the service life. According to the eleventh aspect of the present invention, the wear resistance of the contact portion of the stopper member can be further improved, whereby the service life can be extended.

According to the twelfth aspect of the present invention, the wear resistance of each member can be improved, and the stopper member can be provided without increasing the number of parts and the like. It is also advantageous.

[0035]

Embodiments of the present invention will be described below with reference to the drawings. FIGS. 1 and 2 are diagrams showing a configuration of a first embodiment of the present invention.
An anti-vibration support device according to the present invention is applied to a so-called active engine mount that actively reduces vibration transmitted from an engine to a vehicle body. FIG. 1 is a sectional view showing the overall configuration of the engine mount 1, and FIG. 2 is an overall configuration diagram showing a state where the engine mount 1 is actually mounted.

First, the structure of the engine mount 1 will be described. The engine mount 1 has a cap 2 integrally provided with a bolt 2a for attachment to the engine 30 as a vibrating body and having a hollow inside and an open lower part. On the lower outer surface of the cap 2, the upper end of the inner cylinder 3 whose axis faces in the vertical direction is fixed by welding. On the outer peripheral surface of the inner cylinder 3, the inner peripheral side of a thick cylindrical support elastic body 6 whose inner peripheral surface side is slightly raised upward is vulcanized and bonded, and the outer peripheral surface of the support elastic body 6 is an outer cylinder. 7 is vulcanized and bonded to the upper part of the inner peripheral surface.

The entire outer cylinder 7 is accommodated in an upper portion of a cylindrical case 40 whose axis is oriented in the up-down direction.
The upper end of the case 40 is swaged to the upper end of the outer cylinder 7 from above, and the lower end of the case 40 is the lower end surface of the yoke 10A of the electromagnetic actuator 10 housed below the outer cylinder 7 housing position. Is caulked together with the bottom plate 41. The engine mount 1 is provided with a mounting bolt 42 penetrating the bottom plate 41 downward.
It is fixed to the member 35 side.

The electromagnetic actuator 10 includes a cylindrical iron yoke 10A, an excitation coil 10B wound around the center of the yoke 10A with its axis up and down, and a portion of the yoke 10A surrounded by the excitation coil 10B. The yoke 10A is press-fitted into the case 40 and fixed thereto.

The outer cylinder 7 has a small-diameter portion 7A recessed radially inward at the axial center thereof.
A thin film elastic body 43 is fixed to the inner surface of the case 40 so as to form a ring-shaped cavity 44 so as to be located outside of A. The cavity 44 communicates with the atmospheric pressure through a through hole (not shown) formed on the side surface of the case 40.

On the other hand, inside the small diameter portion 7A, a fluid chamber 15 is provided.
A ring-shaped orifice member 45 having a U-shaped cross section is fixed so as to project inward, and an orifice 45a is provided between the inner surface of the orifice member 45 and the inner surface of the outer cylinder 7. Between the orifice structure 45 and the outer cylinder 7,
A thin film elastic body 6a continuous with the supporting elastic body 6 is interposed.

The orifice 45a is provided with the orifice structure 4
5 communicates with the fluid chamber 15 through a through hole (not shown) formed at an arbitrary position in the circumferential direction, and is displaced, for example, by 180 degrees in the circumferential direction from the through hole of the orifice constituting body 45 and the thin film elastic body 6a and the outer cylinder. Through a through hole (not shown) formed in the nozzle 7, it communicates with the sub-fluid chamber 16 defined between the outer surface of the small-diameter portion 7 </ b> A and the thin-film elastic body 43. And the fluid chamber 1
5, a fluid such as oil is sealed in the sub-fluid chamber 16 and the orifice 45a.

A gap adjusting ring 46 is interposed between the lower end surface of the outer cylinder 7 and the upper surface of the yoke portion 10A, and the engine load on the support elastic body 6 is transferred from the outer cylinder 7 through the gap adjusting ring 46. The data is input to the yoke 10A. A load sensor 22 is provided between the lower surface of the yoke 10A and the bottom plate 41, and the detection result of the load sensor 22 is transmitted to the controller 20 by a residual vibration signal e.
It is supplied as. That is, the yoke 10
A part of the load on the engine 30 side input to the
1 is transmitted to the bottom plate 41 through the peripheral portion of the engine 1 and transmitted to the member 35 side, but another part of the load on the engine 30 side input to the yoke 10A is applied to the load sensor 22.
Is input to the bottom plate 41 and transmitted to the member 35 side from the bottom plate 41, so that the detection value of the load sensor 22 indicates the vibration through the engine mount 1.

The gap adjusting ring 46 is divided into an upper ring 46A and a lower ring 46B, and a peripheral edge of the circular metal leaf spring 11 is interposed between the upper ring 46A and the lower ring 46B. The portion 11B is sandwiched and fixed. Note that a seal ring 46C is embedded in a surface of the upper ring 46B on the leaf spring 11 side.

Further, a magnetic path made of a magnetizable material (for example, iron) is provided on the lower surface side (electromagnetic actuator 10 side) of the central portion 11A of the leaf spring 11 by a screw 11b inserted from the upper surface side of the leaf spring 11. The member 12 is fixed.

The magnetic path member 12 is a disc-shaped member whose center portion 12A is slightly thicker than the other portions, and the projecting side of the thick center portion 12A faces the leaf spring 11 side. And is fixed to the leaf spring 11 side by the screw 11b. The outer diameter of the magnetic path member 12 is slightly larger than the outer diameter of the exciting coil 10B of the electromagnetic actuator 10, and the peripheral portion 12B faces the surface of the yoke 10A outside the exciting coil 10B. .

A notch 12C having a rectangular cross section as a concave portion is formed on the peripheral edge 12B of the magnetic path member 12 on the side of the electromagnetic actuator 10 over the entire circumference of the magnetic path member 12, and this notch is formed. Inside 12C, a rubber ring 13 made of a rubber-like elastic body as a stopper member is fixed to the entire area by vulcanization bonding. The rubber ring 13
Has a contact surface 13A facing the electromagnetic actuator 10 side,
It is formed to a thickness that slightly protrudes from the lower surface of the magnetic path member 12.

Here, the characteristics of the fluid mount determined by the flow path shape of the orifice 45a and the spring constant of the support elastic member 6 are determined when the engine shakes during running, that is, when the engine is shaken.
It is adjusted so as to exhibit a high dynamic spring constant and a high damping force when the engine mount 1 is vibrated at 15 Hz.

The exciting coil 10B of the electromagnetic actuator 10 generates a predetermined electromagnetic force according to a drive signal y which is a current supplied from the controller 20 through a harness (not shown). The controller 20 includes a microcomputer, a necessary interface circuit, an A / D converter, a D / A converter, an amplifier, and the like, and performs idle vibration or muffled sound vibration / acceleration that is higher in frequency than the engine shake. Vibration is the member 35
In this case, a drive signal y for the engine mount 1 is generated and output so that an active supporting force capable of reducing the vibration is generated in the engine mount 1.

In the case of a reciprocating four-cylinder engine, for example, in the case of a reciprocating four-cylinder engine, the main cause is that the engine vibration of the engine rotation secondary component is transmitted to the member 35. If the drive signal y is generated and output in synchronization, the vibration on the vehicle body side 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 The pulse signal generator 21 which outputs the reference signal x
Is supplied to the controller 20 as a signal indicating the state of occurrence of vibration in the engine 30.
Further, the controller 20 is also supplied with the residual vibration signal e from the load sensor 22 as described above.

Then, based on the supplied residual vibration signal e and the reference signal x, the controller 20 controls the synchronous Filtered-X LMS which is one of adaptive algorithms.
By executing the algorithm, a drive signal y for the engine mount 1 is calculated, and the drive signal y is output to the engine mount 1.

More specifically, the controller 20 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
Are sequentially output as the drive signal y, and 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 is executed.

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 a value obtained by filtering a transfer function C between the electromagnetic actuator 10 and the acceleration sensor 22 of the engine mount 1 with a transfer function filter C ＾ modeled by a finite impulse response type filter. Since the value is "1", it matches the sum of the impulse response waveforms at the sampling time n when the impulse responses of the transfer function filter C # are successively generated in synchronization with the reference signal x.

Further, theoretically, the reference signal x is filtered by the adaptive digital filter W to generate the drive signal y. However, since the magnitude of the reference signal x is "1", the filter coefficient W _{Even if i} is sequentially output as the drive signal y, the result is the same as when the result of the filter processing is set as the drive signal y.

[0054] Although operations in these controllers 20 is intended in practice to be executed in a microprocessor, as its functional configurations, drives the filter coefficients W _i of the adaptive digital filter W from the time when the reference signal x is input A drive signal output unit for sequentially outputting as a signal y, an update reference signal operation unit for convolving the reference signal x and the transfer function filter Cｘ to calculate an update reference signal R ^T , and an update reference signal R ^T The above (1) based on the residual vibration signal e
And a filter coefficient updating unit for updating the filter coefficients W _i of the adaptive digital filter W according to equation.

Next, the operation of this embodiment will be described. In other words, when the engine shake occurs, the spring constant of the support elastic body 6 and the flow path shape of the orifice 45a are appropriately selected. As a result, the engine mount 1 functions as a support device having a high dynamic spring constant and a high damping force. The engine shake generated on the engine 30 side is attenuated by the engine mount 1, and the vibration level on the member 35 side is reduced. It is not necessary to actively displace the magnetic path member 12 for the engine shake.

On the other hand, when the fluid in the orifice 45a is in a stick state and the vibration of the frequency equal to or higher than the idle vibration frequency at which the fluid cannot move between the fluid chamber 15 and the sub-fluid chamber 16 is input, the controller Reference numeral 20 executes predetermined arithmetic processing, outputs a drive signal y to the electromagnetic actuator 10, and causes the engine mount 1 to generate an active supporting force capable of reducing vibration.

That is, the filter coefficient W _i of the adaptive digital filter W is applied to the electromagnetic actuator 10 of the engine mount 1 from the controller 20 at the sampling clock interval from the time when the reference signal x is input.
Are sequentially supplied as the drive signal 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 12 by the permanent magnet 10C,
It can be considered that the magnetic force of the exciting coil 10B acts to increase or decrease the magnetic force of the permanent magnet 10C. That is, when the drive signal y is not supplied to the excitation coil 10B, the magnetic path member 12 is displaced to a neutral position where the support force of the leaf spring 11 and the magnetic force of the permanent magnet 10C are balanced. When the drive signal y is supplied to the excitation coil 10B in this neutral state, if the magnetic force generated in the excitation coil 10B by the drive signal y is in the opposite direction to the magnetic force of the permanent magnet 10C, the magnetic path member 12
Is displaced in a direction in which the clearance with the electromagnetic actuator 10 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 magnetic path member 12 is displaced in a direction in which the clearance with the electromagnetic actuator 10 decreases.

As described above, the magnetic path member 12 can be displaced in both the forward and reverse directions.
Is changed, and the expansion spring of the support elastic body 6 is deformed by the change in the volume, so that the engine mount 1 generates an active support force in both forward and reverse directions.

Then, each filter coefficient W _i of the adaptive digital filter W serving as the drive signal y is determined by a synchronous filter
Since the sequentially updated by according to red-X LMS algorithm described 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 Engine mount 1
The idle vibration and the muffled sound vibration transmitted from the engine 30 to the member 35 via the engine mount 1 are reduced.

Further, in the present embodiment, the magnetic path member 12
Because the rubber ring 13 is fixed to the peripheral portion 12B of
Direct collision between the magnetic path member 12 and the electromagnetic actuator 10 can be reliably prevented, and generation of abnormal noise and wear of the magnetic path member 12 and the yoke 10A due to the collision can be prevented. In particular, the arrangement position of the rubber ring 13 is
Therefore, not only when the magnetic path member 12 approaches the electromagnetic actuator 10 with the magnetic path member 12 being parallel, but also when the magnetic path member 12 approaches the electromagnetic actuator 10 in a state where the magnetic path member 12 is largely inclined in the roll direction, the magnetic path member 12 and the yoke 10A Collision can be reliably exhibited.

Further, since the notch 12C is formed in the peripheral edge portion 12B of the magnetic path member 12 and the rubber ring 13 is provided in the notch 112C, the magnetic path member 12 is moved toward the electromagnetic actuator 10 side. Can be very close. That is, when the portion of the rubber ring 13 housed in the notch 12C also functions as a stopper, it is compressed and deformed.
If the thickness and the like of the rubber ring 13 are appropriately selected so that the spring constant of the rubber ring 13 becomes extremely large at the time when the magnetic path member 12 is extremely close to the This makes it possible to bring the electromagnetic actuator 10 very close to the electromagnetic actuator 10 side. Then, the smaller the approach amount of the magnetic path member 12 to the electromagnetic actuator 10 becomes, the larger the stroke range of the magnetic path member 12 becomes. Therefore, it is advantageous in increasing the support force of the engine mount 1 generated by the mechanism described above. Therefore, if a large supporting force can be generated, a better vibration isolating effect can be obtained.

Further, since the notch 12C is formed as a concave portion, there is an advantage that the manufacturing cost can be reduced as compared with a case where a groove or a hole is formed instead of the notch 12. Further, since the rubber ring 13 as a stopper member is provided over the entire peripheral portion 12B of the magnetic path member 12, the magnetic path member 12 and the electromagnetic actuator 10 can be connected regardless of the inclination direction of the magnetic path member 12. Direct collision can be prevented.

If the rubber ring 13 as a stopper member is fixed to the peripheral edge 12 B of the magnetic path member 12, the rubber ring 13 may be fixed to the electromagnetic actuator 10.
And the magnetic circuit member 12 can be disposed outside the magnetic circuit. For this reason, since the stopper member can be made independent from the design of the magnetic circuit, there is also an advantage that the stopper member can be designed independently according to each functional requirement.

On the other hand, in the present embodiment, since the sub-fluid chamber 16 is formed outside the outer cylinder 7, for example, the sub-fluid chamber 16 and the orifice structure 45 are arranged above the fluid chamber 15. There is also an advantage that the height dimension of the engine mount 1 can be reduced as compared with the configuration in which the above is performed.

Further, since the orifice member 45 is formed so as to protrude radially inward at a substantially central portion in the vertical direction of the fluid chamber 15, the inside of the fluid chamber 15 is vertically divided by the orifice member 45. Structure. Then, assuming that the space of the inner diameter portion of the orifice component 45 is the orifice 45b, a structure is obtained in which two fluid chambers formed with the orifice component 45 as a boundary communicate with each other via the orifice 45b. So, orifice 4
Considering a fluid resonance system in which the fluid in 5b is a mass and the expansion direction spring of the supporting elastic body 6 and the leaf spring 11 are springs, and if the resonance frequency of the fluid resonance system is tuned appropriately, furthermore, for various vibration frequencies, The engine mount 1 can exhibit a good vibration-proof effect.

Here, in the present embodiment, a movable member is constituted by the leaf spring 11 and the magnetic path member 12.
FIG. 3 is a diagram showing a second embodiment of the present invention,
FIG. 2 is a cross-sectional view illustrating a configuration of a main part of the engine mount 1.
Note that the same reference numerals are given to members and parts equivalent to those in the first embodiment, and a duplicate description thereof will be omitted.

That is, in the present embodiment, the notch 12C formed in the peripheral edge 12B of the magnetic path member 12 is
It is formed so as to be linearly inclined so that the side is deeper than the center portion 12A side. The rubber ring 13 is disposed in the notch 12C, and the thickness of the rubber ring 13 is such that the contact surface 13A is positioned with respect to the surface of the yoke 10 in a state where the magnetic path member 12 is not inclined. The outer peripheral surface 12D side is thicker than the central portion 12A side so as to be parallel to each other. Note that the inclination angle of the notch 12C is equal to or less than the maximum inclination angle of the magnetic path member 12 that can be obtained from an experiment or the like. Desirably, the inclination angle of the notch 12C is the maximum inclination angle of the magnetic path member 12, so that the bottom surface of the notch 12C and the yoke 10A
Make it parallel to the surface.

With this configuration, when the magnetic path member 12 approaches the electromagnetic actuator 10 while being inclined, the rubber ring 13 that is most likely to be worn due to contact with the yoke 10 is provided.
Because the outer diameter side is thicker, the rubber ring 1
The service life of 3 can be lengthened accordingly.

Other functions and effects are the same as those of the first embodiment. Note that the notch 12C may be formed linearly and obliquely as shown in FIG. 3, or may be formed stepwise and obliquely as shown in FIG. 4, or furthermore, as shown in FIG. As shown in FIG.

FIG. 6 is a view showing a third embodiment of the present invention, and is a cross-sectional view showing a configuration of a main part of the engine mount 1. As shown in FIG. Note that the same reference numerals are given to members and parts equivalent to those in the first embodiment, and a duplicate description thereof will be omitted.

That is, in the present embodiment, instead of providing a stopper member on the magnetic path member 12 side, a stopper member is provided on the electromagnetic actuator 10 side, so that the peripheral portion 12B of the magnetic path member 12 and the yoke 10A are connected. Prevents direct collision. That is, the yoke 10A of the electromagnetic actuator 10 is formed with a circular groove 10E for accommodating the bobbin 10D around which the exciting coil 10B is wound, and the groove 10E is accommodated in the state where the bobbin 10D is accommodated.
The bobbin 10D is fixed in the groove 10E by pouring molten PTFE as a synthetic resin into the inside and curing the PTFE. Therefore, the PTF poured into the groove 10E
By increasing E, the surface of the yoke 10A is slightly raised from the surface of the yoke 10A.
The TFE layer 10F is formed. The PTFE layer 10
F is formed to have such a width that its surface and the peripheral portion 12B of the magnetic path member 12 face each other.

With such a configuration, since the peripheral portion 12B of the magnetic path member 12 and the PTFE layer 10F collide with each other, the comparatively hard magnetic path member 12 and the yoke 10A directly collide with each other. Thus, the wear resistance can be improved. Moreover, the PTFE layer 10F as a stopper member
Is originally necessary for fixing the bobbin 10D, so that the stopper member can be provided without substantially increasing the number of parts, which is advantageous in cost.

Other functions and effects are the same as those of the first embodiment. FIG. 7 is a diagram showing the fourth embodiment of the present invention, and is a cross-sectional view showing a configuration of a main part of the engine mount 1. Note that the same reference numerals are given to members and parts equivalent to those in the first embodiment, and a duplicate description thereof will be omitted.

That is, this embodiment is a combination of both the first embodiment and the third embodiment. That is, the rubber ring 13 as a stopper member is fixed to the peripheral edge portion 12B of the magnetic path member 12, while
A PTFE layer 10F as a stopper member is also formed on the surface of the yoke 10A, and the rubber ring 13 and the PTFE layer 1 are formed.
0F collides. However, in the present embodiment, unlike the third embodiment, the surface of the PTFE layer 10F is at the same height as the surface of the yoke 10A, but the surface of the PTFE layer 10F is originally the yoke 10A.
Whether or not it protrudes from the surface is not an essential problem for the stopper member.

With such a configuration, the rubber ring 13
Then, the PTFE layer 10F made of a non-magnetic material comes into contact with the PTFE layer 10F, so that abrasion of the rubber ring 13 can be suppressed. That is, since the PTFE layer 10F is softer than the yoke 10A, the rubber ring 13 in contact with the yoke 10A is less likely to be worn. In addition, since the PTFE layer 10F is made of a non-magnetic material and has no heat generation effect due to the magnetic flux generated by the electromagnetic actuator 10, the temperature of the yoke 10A
The rubber ring 13 that is in contact with the rubber ring 13 is less likely to be worn by the lower temperature. In addition, the service life of the rubber ring 13 can be prolonged by an amount that is hardly worn.

Other functions and effects are the same as those of the first embodiment. FIG. 8 is a view showing a fifth embodiment of the present invention, and is a cross-sectional view showing a configuration of a main part of the engine mount 1. Note that the same reference numerals are given to members and parts equivalent to those in the first embodiment, and a duplicate description thereof will be omitted.

That is, in the present embodiment, the lower ring 46B of the gap adjusting ring 46 is further extended downward to be interposed between the yoke 10A and the case 40,
A notch 10G is formed in the peripheral portion of the surface of the yoke 10A,
The lower ring 46B is inserted into the notch 10G.
A ring-shaped convex portion 46C is formed on the inner peripheral portion of. The outer diameter of the magnetic path member 12 is set so that the rubber ring 13 as a stopper member and the convex portion 46C face each other.

With such a configuration, the rubber ring 13
And the convex portion 46 </ b> C come into contact with each other, so that abrasion of the rubber ring 13 can be suppressed. That is, since the lower ring 46B is irrelevant to the magnetic circuit, it can be formed of a non-magnetic material, for example, aluminum.
Does not generate heat due to the magnetic flux generated. Therefore, the rubber ring 13 contacting the projection 46C is less likely to be worn. In addition, the service life of the rubber ring 13 can be prolonged by an amount that is hardly worn.

Other functions and effects are the same as those in the first embodiment. FIG. 9 is a cross-sectional view illustrating a configuration of a main part of the engine mount 1 according to a sixth embodiment of the present invention. Note that the same reference numerals are given to members and parts equivalent to those in the first embodiment, and a duplicate description thereof will be omitted.

That is, in the present embodiment, a resin member having the same diameter as the rubber ring 13 is provided on the end face of the rubber ring 13 fixed to the peripheral edge 12 B of the magnetic path member 12 on the side of the electromagnetic actuator 10. A ring 14 made of PTFE is fixed. In this embodiment, the rubber ring 13 and the ring 14 constitute a stopper member.

With such a configuration, the spring constant as the stopper member is ensured by the rubber ring 13 and the PTFE ring 14 which is harder than the rubber-like elastic body contacts the yoke 10A. The wear resistance of the contact portion of the stopper member can be improved, and the service life of the stopper member can be prolonged accordingly.

Other functions and effects are the same as those of the first embodiment. In the example shown in FIG. 9, a case is described in which the PTFE ring 14 is fixed to the rubber ring 13 having the same shape as that of the first embodiment.
Such a ring 14 may be fixed to a contact surface of a rubber-like elastic body having a shape as in the second, fourth, fifth, and sixth embodiments, for example. The same operation and effect as those of the example shown in FIG. 9 can be obtained.

FIG. 10 is a diagram for explaining the seventh embodiment of the present invention, and is a bottom view of the magnetic path member 12. As shown in FIG. That is, in the first embodiment and the like, FIG.
As shown in FIG. 5, a notch 12C is formed on the entire periphery of the peripheral portion 12B of the magnetic path member 12, and a rubber ring 13 as a stopper member is fixed to the entire area of the notch 12C. On the other hand, in the present embodiment, as shown in FIG. 10B, a plurality of concave portions 12E are formed intermittently at predetermined intervals in the circumferential direction at the peripheral edge portion 12B of the magnetic path member 12, and each of them is formed. Recess 12
E, a columnar rubber-like elastic body 17 as a stopper member
Is arranged. With such a configuration, the concave portion 12E
If the formation interval of the elastic members is sufficiently narrow, the direct collision between the magnetic path member 12 and the electromagnetic actuator can be reliably prevented, and the amount of the rubber elastic members used by the amount of the rubber elastic members 17 scattered is reduced. There is an advantage that less is required.

Other functions and effects are the same as those of the first embodiment. In each of the above embodiments, the case where the anti-vibration support device according to the present invention is applied to the engine mount 1 that supports the engine 30 is shown. The present invention is not limited to the mount 1, and may be, for example, an anti-vibration support device of a machine tool accompanied by vibration.

In each of the above embodiments, the vibration damping effect is obtained by using the fluid resonance obtained by the orifice 45a or the like. However, when the vibration damping effect by the fluid resonance is not required, The orifice member 45a and the like need not be provided.

In each of the above embodiments, the drive signal y is generated in accordance with the synchronous Filtered-XLMS algorithm. However, the applicable algorithm is not limited to this.
It may be a red-X LMS algorithm or a frequency domain LMS algorithm. If the characteristics of the system are stable, the drive signal y may be generated by a digital filter or an analog filter having fixed coefficients without using an adaptive algorithm such as an LMS algorithm.

[Brief description of the drawings]

FIG. 1 is a sectional view of an engine mount according to a first embodiment of the present invention.

FIG. 2 is an overall configuration diagram showing an arrangement state of an engine mount.

FIG. 3 is a sectional view showing a main part of a second embodiment.

FIG. 4 is a cross-sectional view showing a modification of the second embodiment.

FIG. 5 is a sectional view showing another modified example of the second embodiment.

FIG. 6 is a cross-sectional view showing a main part of a third embodiment.

FIG. 7 is a sectional view showing a main part of a fourth embodiment.

FIG. 8 is a cross-sectional view illustrating a main part of a fifth embodiment.

FIG. 9 is a sectional view showing a main part of a sixth embodiment.

FIG. 10 is a bottom view of a magnetic path member according to a seventh embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Engine mount (anti-vibration support device) 6 Support elastic body 10 Electromagnetic actuator 11 Leaf spring 12 Magnetic path member 12A Central part 12B Peripheral part 12C Notch (recess) 13 Rubber ring (stopper member) 13A Contact surface 15 Fluid chamber 16 Sub-fluid chamber 20 Controller 30 Engine (vibrating body) 35 Member (support)

Claims (12)

[Claims] 1. A supporting elastic body interposed between a vibrating body and a supporting body, a fluid chamber defined by the supporting elastic body, a fluid sealed in the fluid chamber, and a part of a partition of the fluid chamber. And a movable member displaceable in a direction that changes the volume of the fluid chamber, and an electromagnetic actuator that generates a force for displacing the movable member in the direction. And a stopper member for preventing collision with the electromagnetic actuator is provided so as to exhibit a stopper function between a peripheral portion of a surface of the movable member facing the electromagnetic actuator and the electromagnetic actuator. Characteristic anti-vibration support device. 2. A supporting elastic body interposed between a vibrating body and a supporting body, a fluid chamber defined by the supporting elastic body, a fluid sealed in the fluid chamber, and a part of a partition of the fluid chamber. And a movable member that can be displaced in a direction that changes the volume of the fluid chamber, and an electromagnetic actuator that generates a force that displaces the movable member in the direction. A leaf spring whose peripheral portion is supported on the side of the support on which the electromagnetic actuator is mounted, and a magnetic path member made of a magnetizable material and fixed to a surface of the central portion of the leaf spring on the electromagnetic actuator side; And a stopper member for preventing a collision between the magnetic path member and the electromagnetic actuator, a surface facing the electromagnetic actuator side of the magnetic path member. Vibration-damping support device characterized by being arranged to exert a stopper function between the peripheral portion and the electromagnetic actuator. 3. The anti-vibration support device according to claim 1, wherein the stopper member is a rubber-like elastic body. 4. A concave portion is formed in a peripheral portion of a surface of the magnetic path member facing the electromagnetic actuator, and a rubber-like elastic body as the stopper member is provided in the concave portion.
The anti-vibration support device according to the above. 5. The method according to claim 1, wherein the recess is formed over the entire periphery.
5. The rubber-like elastic body is provided in the whole area of the concave portion.
The anti-vibration support device according to the above. 6. The anti-vibration support device according to claim 4, wherein the concave portions are formed intermittently in the peripheral edge portion, and the rubber-like elastic body is provided in each of the concave portions. 7. The anti-vibration support device according to claim 4, wherein the recess is a notch formed at a corner of the peripheral edge. 8. The anti-vibration support device according to claim 4, wherein the concave portion is deeper on the outer peripheral side of the magnetic path member than on the central side. 9. The anti-vibration support device according to claim 8, wherein the thickness of the rubber-like elastic body is greater on the outer peripheral side of the magnetic path member than on the central side. 10. The anti-vibration support device according to claim 4, wherein a layer made of a non-magnetic material is provided on the side of the electromagnetic actuator so as to contact the rubber-like elastic body. 11. The anti-vibration support device according to claim 4, wherein a resin member is fixed to an end surface of the rubber-like elastic body on the side of the electromagnetic actuator. 12. The device according to claim 2, wherein the stopper member is a resin member fixed to at least one of a peripheral portion of a surface of the magnetic path member facing the electromagnetic actuator and the electromagnetic actuator. Anti-vibration support device.