JP3473293B2 - Active vibration control device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention causes a vibration transmitted from a vibration body such as an engine to a support body such as a vehicle body to interfere with a control vibration generated from a control vibration source interposed between the vibration body and the support body. The present invention relates to an active vibration control device which is reduced by, in particular, detecting residual vibration after interference between vibration generated from a vibrating body and control vibration generated from a control vibration source, and based on at least the residual vibration. The residual vibration is accurately detected in an active vibration control device that drives a controlled vibration source.

[0002]

2. Description of the Related Art A conventional technique of this kind is disclosed in, for example, Japanese Patent Laid-Open No. 7-233852.
In the device disclosed in this publication, a load sensor is used as a means for detecting residual vibration. That is, the above-mentioned publication discloses a so-called active engine mount which is disposed between an engine (vibrating body) and a vehicle body (support) and is capable of generating an active supporting force. To briefly explain the structure, a support spring made of a rubber-like elastic material is interposed between a case fixed to the engine side and a center boss fixed to the vehicle body side, and the support spring is filled with fluid. A fluid chamber is defined, and a vibrating plate that can vibrate in a direction that changes the volume of the fluid chamber is elastically supported by a leaf spring, and an electromagnetic actuator that vibrates the vibrating plate is fixed in the case. A rubber-like elastic body is attached to the surface of the center boss on the vehicle body side, and a plate-like member having a hollowed central portion is vertically interposed between the rubber-like elastic body and the vehicle body. The load sensor is housed in the hollow central portion of the plate-shaped member. That is, since the load sensor is sandwiched between the rubber-like elastic body and the vehicle body, it is possible to detect a change in the force transmitted from the center boss to the vehicle body side as a change in the load. Therefore, by driving the electromagnetic actuator so that the residual vibration which is the output of the load sensor becomes small, the vibration transmitted to the vehicle body side through the active engine mount can be reduced.

[0003]

However, in the structure as disclosed in the above publication, the load sensor is attached to the center boss via the rubber-like elastic body, so that the deterioration of the rubber-like elastic body over time or There is a case where the output of the load sensor and the force transmitted to the vehicle body side through the engine mount do not accurately correspond to each other due to insufficient rigidity, and in this case, there is a problem that it is difficult to increase the accuracy of the vibration reduction control. Moreover, in the engine mount disclosed in the above publication, the load sensor is housed in the central portion of the plate-shaped member and is sandwiched between the rubber-like elastic body and the vehicle body side. In addition, a large proportion of the force is transmitted to the vehicle body side through the plate-shaped member, which makes it difficult to accurately detect the residual vibration.

On the other hand, as disclosed in FIG. 5 of Japanese Patent Application Laid-Open No. 8-145114 previously proposed by the present applicant,
All the force transmitted to the vehicle body side through the engine mount is temporarily concentrated on the yoke of the electromagnetic actuator, and a load sensor is provided between the flat plate part integrated with the stud bolt fixed to the yoke end face and the yoke end face. If the structure is such that the stud bolt is sandwiched and the other end side of the stud bolt is connected to the vehicle body side, the ratio of the force passing through the load sensor increases, so that more accurate residual vibration can be detected. However, in such a structure, since the load sensor itself is a member that determines the strength of the engine mount, it is a disadvantageous structure for ensuring the original strength of the engine mount. That is, since the load sensor is arranged so as to surround the stud bolt, this load sensor is
It is strong against vibrations in the vertical direction of the engine mount, but cannot bear part of the force against vibrations in the lateral direction. Therefore, for lateral vibration of the engine mount, the load concentrates only on the stud bolts, so it is necessary to increase the diameter of the stud bolts to increase its strength. Is limited. Moreover, since the load sensor is sandwiched by using the stud bolt, if the stud bolt becomes loose, the preload applied to the load sensor may change and the detection accuracy may decrease.

The present invention has been made by paying attention to various problems of such a conventional device. By improving the arrangement structure of a load sensor for detecting residual vibration, more accurate It is an object of the present invention to provide an active vibration control device capable of detecting various residual vibrations and thereby performing highly accurate vibration reduction control.

[0006]

In order to achieve the above object, the invention according to claim 1 is capable of generating a control vibration which is interposed between a vibrating body and a supporting body and which interferes with a vibration emitted from the vibrating body. Control vibration source, residual vibration detection means for detecting the residual vibration after the interference and outputting it as a residual vibration signal, and control means for generating and outputting a drive signal for driving the control vibration source based on the residual vibration signal. And a supporting elastic body interposed between the vibrating body and the supporting body, and a fluid chamber defined by the supporting elastic body and containing a fluid. ,
A movable member that forms a part of the partition wall of the fluid chamber and is displaceable in a direction that changes the volume of the fluid chamber; and the movable member is disposed between the support elastic body and the support body. An electromagnetic actuator that generates a force for displacing in a direction, and a case that houses the electromagnetic actuator and to which the support elastic body is attached is fixed to the support body.
In a state of not contacting the lid member and the support to be fixed ,
Wherein by fixing the electromagnetic actuator yoke, a structure in which all the forces transmitted to the support side from the vibration member side through the control vibration source is once concentrated on the yoke, a peripheral portion of the front Kifuta member, wherein By coupling to the surface of the yoke facing the support body side, a gap is formed between the yoke and a portion inside the peripheral portion of the lid member, and the load sensor as the residual vibration detecting means is It was sandwiched between the lid member and the yoke so as to be located at the center of the gap. In order to achieve the above-mentioned object, the invention according to claim 2 intervenes with a control vibration source which is interposed between a vibrating body and a support and is capable of generating control vibration that interferes with vibration emitted from the vibrating body. Active vibration control including residual vibration detection means for detecting the residual vibration after and outputting it as a residual vibration signal, and control means for generating and outputting a drive signal for driving the controlled vibration source based on the residual vibration signal. In the device, the control vibration source includes a supporting elastic body interposed between the vibrating body and the supporting body, a fluid chamber defined by the supporting elastic body and containing a fluid, and a part of a partition wall of the fluid chamber. And a movable member that is displaceable in a direction that changes the volume of the fluid chamber and a force that is disposed between the support elastic body and the support body and that displaces the movable member in the direction. Electromagnetic actu Comprises a chromatography data, and the yoke of the electromagnetic actuator,
In a state where the yoke end portion is inserted inside one end portion of the cylindrical case so as to project to the outside of the case, the case is fixed to the outer peripheral surface of the yoke, and the yoke is projected to the outside of the case. Fix the lid member to the end face on the side,
By interposing the supporting elastic body between the inside of the other end of the case and the vibrating body, all the forces transmitted from the vibrating body side to the supporting body side through the controlled vibration source are the yoke. The structure to concentrate once on
By coupling the peripheral portion of the cover member to the surface of the yoke facing the support body side, a gap is formed between a portion inside the peripheral portion of the cover member and the yoke, and the residual vibration is generated. A load sensor as a detection means was sandwiched between the lid member and the yoke so as to be located at the center of the gap.

[0007] Incidentally, before Kifuta member is preferably a high rigidity metal such as iron, it may not be metallic as long as the material sufficiently rigid to obtain. According to a third aspect of the present invention, in the active vibration control device according to the first or second aspect of the present invention, the lid member is formed into a disc shape with a raised peripheral edge portion, and the raised peripheral edge of the lid member. The portion was brought into contact with the surface of the predetermined member facing the support body side, and the peripheral portion of the lid member and the predetermined member were joined by caulking.

[0008]

[0009]

[0010]

[0011]

According to a fourth aspect of the present invention, in the active vibration control device according to the first to third aspects, the movable member is attached to the electromagnetic actuator of the vibrating body and the supporting body. 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.

Further, according to a fifth aspect of the invention, in the active vibration control device according to the first to fourth aspects of the invention, a variable volume auxiliary fluid chamber communicating with the fluid chamber via an orifice is provided. A fluid is enclosed in the fluid chamber, the orifice, and the sub-fluid chamber.

Here, in the invention according to claim 1,
Since the vibration generated in the vibrating body and transmitted to the control vibration source will interfere with the control vibration generated in the control vibration source,
By appropriately adjusting the frequency and amplitude of the control vibration, the vibration transmitted to the support side can be reduced or canceled.
Therefore, in order to recognize the reduced state of vibration, the residual vibration signal detected by the residual vibration detecting means is supplied to the control means,
The control means appropriately generates and outputs a drive signal based on the residual vibration signal.

Further, the load sensor as the residual vibration detecting means is directly sandwiched between the yoke and the lid member without interposing a rubber-like elastic body or the like, and moreover, in the yoke from the vibrating body side through the control vibration source. All the forces transmitted to the support side are concentrated. That is, in claim 1.
In the invention, the support elastic body defines the fluid chamber.
And part of the partition wall of the fluid chamber is formed by the movable member.
The electromagnetic force generated by the electromagnetic actuator.
The movable member is displaced by and the volume of the fluid chamber changes.
And its volume change acts on the expansion direction spring of the supporting elastic body.
Becomes a force, and that force is applied between the vibrating body and the support.
It provides active support. And the electromagnetic actuator
Is disposed between the support elastic body and the support,
The electromagnetic actuator is designed so that vibration and control vibration interfere with each other.
Is a member that is arranged closer to the support than the mounting position.
The vibration of the eta clearly causes interference between vibration and control vibration.
It is a member that is disposed closer to the support than the position. And
Cover the case fixed to the yoke of the electromagnetic actuator with the lid.
Since it is not in contact with any member or support, use a support elastic body.
All the vibrations that are input to the case through
Will be concentrated on. Furthermore, by positioning the center of the gap formed between the load sensor yoke <br/> and the lid member, because as space is formed around the load sensor, is inputted to the yoke It is possible to avoid that most of the vibrations bypass the load sensor and are transmitted to the support body side. For these various reasons, the load sensor
Residual vibration can be detected more accurately, which enables highly accurate vibration reduction control.

On the other hand, since the peripheral portion of the lid member is connected to the side of the predetermined member, the strength against the lateral vibration input to the controlled vibration source can be ensured relatively easily. Also, the claims
The invention according to claim 2 more specifically defines the invention according to claim 1.
And the yoke end of the electromagnetic actuator is
It projects to the outside of the case, and in that state the case is
Is fixed, the lid member and case fixed to the end face of the yoke are fixed.
The case is not in contact with the support.
It is a touch. And the electromagnetic actuator housing side of the case
The support elastic body is directly or indirectly inside the end opposite to
Supported by the support elastic body
All the applied vibrations will once concentrate on the yoke.
It Therefore, even in the invention according to claim 2, the above
An effect equivalent to that of the invention according to claim 1 is exhibited. Also,
In the invention according to claim 3 , since the peripheral edge portion of the disk-shaped lid member is raised and the raised peripheral edge portion is in contact with the predetermined member, a gap for disposing the load sensor is surely provided. Is formed. Then, the peripheral portion of the lid member and Yo
Since it is joined to the load by caulking, it is possible to give an appropriate preload to the load sensor by adjusting the rising degree of the peripheral portion appropriately, and it does not loosen as in the case of screwing. Therefore, the possibility that the size of the preload changes with use and the detection accuracy deteriorates can be greatly reduced.

[0017]

[0018]

[0019]

[0020]

[0021]

Further, in the invention according to claim 4 ,
Since the elastic supporting force of the leaf spring supporting the movable member and the electromagnetic force generated from the electromagnetic actuator act on the magnetic path member forming the movable member, the elastic member is displaced to a position where the elastic supporting force and the electromagnetic force are balanced. can do. Therefore, by appropriately adjusting the electromagnetic force generated by the electromagnetic actuator, the magnetic path member of the movable member can be displaced to an arbitrary position, so that a control force having a desired frequency and amplitude can be generated.

According to the invention of claim 5 ,
Since the fluid chamber and the variable-volume sub-fluid chamber are communicated with each other through the orifice, vibrations of a frequency that allows fluid to flow between the fluid chamber and the sub-fluid chamber are input through the orifice. In some situations, this source of controlled vibration can function as a normal fluid-filled support device that produces a passive bearing force, and the fluid in the orifice is in a stick state (immovable state). With respect to high-frequency vibration, it is equivalent to the absence of the sub-fluid chamber and the orifice, so that the same action as the invention according to claims 1 to 4 is exhibited.

[0024]

As described above, according to the present invention,
Since a gap is formed between the yoke and the lid member and the load sensor is sandwiched in the center of the gap, residual vibration can be detected more accurately by the load sensor, which allows highly accurate vibration reduction control. Therefore, the vibration level on the support side can be favorably reduced, and the strength of the controlled vibration source that functions as a support device can be easily secured.

Particularly, in the invention according to claim 3 , an appropriate preload can be given to the load sensor,
Since it is possible to reduce the possibility that the size of the preload changes, it is possible to more reliably perform highly accurate vibration reduction control.

Further, according to the invention of claim 5 , the control vibration source can be made to act as an ordinary fluid-filled type supporting device for generating a passive supporting force. Further good vibration damping effect can be obtained.

[0027]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. 1 and 2 are diagrams showing a configuration of a first embodiment of the present invention. In this embodiment, an active vibration control device according to the present invention is used to reduce vibrations transmitted from an engine to a vehicle body. It is applied to a so-called active engine mount that actively reduces. 1 is a sectional view showing the overall structure of the engine mount 1, and FIG. 2 is an overall structure diagram showing a state in which the engine mount 1 is actually mounted.

First, the structure will be described. The engine mount 1 has a flat plate-shaped mounting member 2 integrally provided on the upper portion with a bolt 2a for mounting the engine 30 as a vibrating body. An upper end of a substantially conical inner cylinder 3 whose axis is oriented in the vertical direction and whose lower end has a smaller diameter than the upper end of the opening is fixed to the lower surface by welding. On the upper surface of the mounting member 2 and the outer peripheral surface of the inner cylinder 3, an inner peripheral side of a thick-walled cylindrical support elastic body 6 having a slightly raised inner peripheral surface side is vulcanized and adhered, and the outer peripheral surface of the support elastic body 6 is Is vulcanized and bonded to the upper portion of the inner peripheral surface of the outer cylinder 7.

The outer cylinder 7 as a whole is housed together with spacer rings 7a and 7b in the upper portion of a cylindrical case 40 whose axis is oriented in the vertical direction, and the upper end of the case 40 is the upper end of the outer cylinder 7. It is caulked from above.

The electromagnetic actuator 10 is housed inside the lower end of the case 40. The electromagnetic actuator 10 includes a cylindrical iron yoke 10A, an exciting coil 10B wound around a bobbin (not shown) embedded in the central portion of the yoke 10A with its axis oriented vertically, and surrounded by an exciting coil 10B of the yoke 10A. The permanent magnet 10C is fixed to the upper surface of the closed portion with its poles facing up and down, and the yoke 10A has its case 4 so that its end portion on the bottom surface 10a side projects to the outside of the case 40.
0, and the lower end 40a of the case 40 is fixed to the outer peripheral surface of the yoke 10A.

Specifically, on the outer peripheral surface of the yoke 10A,
Relatively large step portion 1 having a small diameter on the side close to the bottom surface 10a
0b and a relatively small step portion 10c located above the step portion 10b and having a small diameter on the side close to the upper surface are formed, and the lower end portion 40a of the case 40 is arranged from the outside to the inside so as to go around the step portion 10b. Is caulking towards. In addition, a small diameter portion 40b is formed on the inner peripheral surface of the case 40 so that the step portion 10c bites into it. Therefore, by caulking the lower end portion 40a of the case 40 as described above, the large-diameter portion between the step portions 10b and 10c is made into the case 40.
Since it comes to bite into the inner peripheral surface of, the lower end portion 40a of the case 40 is fixed to the outer peripheral surface of the yoke 10A by caulking.

Further, the outer cylinder 7 has a small diameter portion 7A recessed inward in the radial direction at the central portion in the axial direction thereof.
A thin film elastic body 43 forming a cavity 44 is fixedly provided on the inner surface of the case 40 at an arbitrary position in the outer circumferential direction on the outer side 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. The rubber-like elastic body 45 forming the orifice 45a is housed in the other portion outside the small diameter portion 7A.
One end side of the orifice 45a in 5 communicates with the sub-fluid chamber 16 defined by the surface of the thin film elastic body 43 opposite to the cavity 44 and the outer surface of the outer cylinder 7.

On the other hand, the fluid chamber 15 is provided inside the small diameter portion 7A.
A ring-shaped orifice forming member 46 having a U-shaped cross section is fixed so as to project inward, and an orifice 46a is formed between the inner surface of the orifice forming member 46 and the inner surface of the outer cylinder 7.

The orifice 46a communicates with the fluid chamber 15 through a through hole (not shown) formed at an arbitrary position in the circumferential direction of the orifice forming body 46, and extends from the through hole of the orifice forming body 46 in the circumferential direction. For example 180
It is communicated with the other end side of the orifice 45a in the rubber-like elastic body 45 through a through hole (not shown) formed in the outer cylinder 7 with a deviation. A fluid such as oil is enclosed in the fluid chamber 15, the sub-fluid chamber 16 and the orifices 45a and 46a.

A gap adjusting ring 47 is interposed between the lower end surface of the outer cylinder 7 and the upper surface of the yoke portion 10A. The gap adjusting ring 47 is divided into an upper ring 47A and a lower ring 47B.
A peripheral edge portion 11B of a circular metal leaf spring 11 is sandwiched and fixed between 7A and the lower ring 47B. A seal ring 47C is embedded in the surface of the upper ring 47B on the leaf spring 11 side. Further, the leaf spring 11
Lower surface side of the central portion 11A (electromagnetic actuator 10 side)
Is a screw 11b inserted from the upper surface side of the leaf spring 11.
Thus, the magnetic path member 12 made of a magnetizable material (for example, iron) is fixed.

The magnetic path member 12 is a disk-shaped member whose central portion 12A is slightly thicker than the other portions, and the projecting side of the thick central portion 12A faces the leaf spring 11 side. It is fixed to the leaf spring 11 side by the screw 11b as described above. 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 its peripheral portion 12B faces the surface of the yoke 10A outside the exciting coil 10B. .

On the bottom surface 10a of the yoke 10A, which is the end surface on the side protruding to the outside of the case 40, a circular recess 10d is formed in the center thereof, and a ring-shaped continuous recess 10e is formed in the periphery thereof. And its annular recess 1
Further on the outer side of 0e, a cylindrical rising portion 10f is formed and an iron lid member 48 is fixed. The lid member 48 is a disk-shaped member made of iron having a rising portion 48a formed on the peripheral edge portion, and a plate-shaped portion inside the peripheral edge portion has a member 35 as a support member elastically supported by the vehicle body 36. The mounting bolt 42 for fixing to the side is pierced downward, and the end of the rising portion 48a is curved outward in the radial direction to form the flange portion 48b, and the flange portion 48b is brought into contact with the bottom surface of the annular recess 10e. In this state, the rising portion 10f of the bottom surface 10a is caulked inward to fix the flange portion 48b in the annular recess 10e. In this way, since the rising portion 10f is curved from the outside to the inside, the entire front and back surfaces and the outer peripheral surface of the flange portion 48b can be coupled in the annular recess 10e, and the lid member 48 is attached to the bottom surface 10a of the yoke 10A. Can be firmly fixed.

Between the bottom surface 10a of the yoke 10A and the lid member 48, the depth of the annular recess 10e and the lid member 4 are provided.
A gap 49 having a size corresponding to the height of the rising portion 48 a of the load sensor 22 is formed so that the load sensor 22 is located between the bottom surface 10 a and the lid member 48 so as to be located at the center of the gap 49. Is provided. The load sensor 22 is housed in the recess 10d at the center of the bottom surface 10a. The detection result of the load sensor 22 is supplied to the controller 20 as a residual vibration signal e. That is, all the forces generated on the engine 30 side and input to the engine mount 1 are generated by the support elastic body 6, the outer cylinder 7,
Through the case 40, the gap adjusting ring 47, etc., the yoke 10
Once concentrated on A, part of the concentrated force is the load sensor 2
2, the other force is transmitted to the lid member 48 side through the rising portion 48a, and the force input to the lid member 48 is transmitted to the member 35 side. The value represents the vibration transmitted to the member 35 side through the engine mount 1.

Here, the characteristics of the fluid mount determined by the flow passage shapes of the orifices 45a and 46a and the spring constant of the supporting elastic body 6 are that the engine mount 1 is added when an engine shake occurs during running, that is, at 5 to 15 Hz. It is adjusted to show a high dynamic spring constant and a high damping force when shaken.

The exciting coil 10B of the electromagnetic actuator 10 is adapted to generate a predetermined electromagnetic force according to the drive signal y which is a current supplied from the controller 20 through a harness (not shown). The controller 20 is configured to include a microcomputer, a necessary interface circuit, an A / D converter, a D / A converter, an amplifier, and the like, and at the time of idle vibration or muffled sound vibration / acceleration, which is vibration of a higher frequency than engine shake. Vibration is member 35
Input to the engine mount 1, 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, for example, a reciprocating four-cylinder engine, idle vibration and muffled sound vibration are mainly caused by transmission of engine vibration of the engine rotation secondary component 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 is generated in synchronization with the rotation of the crankshaft of the engine 30 (for example, in the case of a reciprocating four-cylinder engine, one impulse signal is generated each time the crankshaft rotates 180 degrees), and the reference signal x is generated. Is provided with a pulse signal generator 21 for outputting the reference signal x
Is supplied to the controller 20 as a signal indicating the generation state of vibration in the engine 30.
The residual vibration signal e is also supplied to the controller 20 from the load sensor 22 as described above.

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

Specifically, the controller 20 has an adaptive digital filter W with a variable filter coefficient W _i (i = 0, 1, 2, ..., I-1: I is the number of taps), and the latest The adaptive digital filter W at a predetermined sampling clock interval from the time when the reference signal x is input.
While the filter coefficient W of No. 1 is sequentially output as the drive signal y, the filter coefficient W _i of the adaptive digital filter W is appropriately updated based on the reference signal x and the residual vibration signal e.

The updating formula of the adaptive digital filter W is F
The following equation (1) follows the iltered-X LMS algorithm. W _i (n + 1) = W _i (n) −μR ^T e (n) (1) Here, the terms with (n) and (n + 1) represent values at sampling times n and n + 1, μ is a convergence coefficient. Further, theoretically, the update reference signal R ^T is
The reference signal x is a value obtained by filtering the transfer function C between the electromagnetic actuator 10 of the engine mount 1 and the acceleration sensor 22 with a transfer function filter C ^ modeled by a finite impulse response type filter. Since the length is "1", it coincides with the sum at the sampling time n of the impulse response waveforms when the impulse responses of the transfer function filter C ^ are generated one after another 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 same result as when the filter processing result is used as the drive signal y is obtained.

The operation in these controllers 20 is actually executed in the microprocessor, but the functional configuration is such that the filter coefficient W _i of the adaptive digital filter W is driven from the time when the reference signal x is input. A drive signal output section that sequentially outputs as a signal y, an update reference signal calculation section that calculates the update reference signal ^RT by convolving the reference signal x and the transfer function filter C ^, and an update reference signal ^RT . Based on the residual vibration signal e, the above (1)
A filter coefficient updating unit for updating each filter coefficient W _i of the adaptive digital filter W according to the formula.

Next, the operation of this embodiment will be described. That is, when an engine shake occurs, the spring constant of the support elastic body 6 and the flow passage shapes of the orifices 45a and 46a 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. Therefore, the engine shake generated on the engine 30 side is damped by the engine mount 1, and the vibration level on the member 35 side is reduced. It should be noted that it is not necessary to positively displace the magnetic path member 12 with respect to the engine shake.

On the other hand, when a vibration having a frequency higher than the idle vibration frequency at which the fluid in the orifices 45a and 46a is in a stick state and cannot move between the fluid chamber 15 and the sub-fluid chamber 16 is input, , Controller 2
0 executes a predetermined arithmetic processing, and the electromagnetic actuator 1
The drive signal y is output to 0, and the engine mount 1 is caused 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 driving signal y is applied 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 generated by the exciting coil 10B acts to strengthen or weaken the magnetic force of the permanent magnet 10C. That is, when the drive signal y is not supplied to the exciting coil 10B, the magnetic path member 12 is displaced to a neutral position in which the supporting 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 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 magnetic path member 12 is generated.
Is displaced in the direction in which the clearance with the electromagnetic actuator 10 increases. On the contrary, 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 the 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. If the magnetic path member 12 is displaced, the main fluid chamber 15 can be moved.
The volume of the engine mount 1 changes, and the expansion spring of the support elastic body 6 deforms due to the change in the volume, so that an active support force is generated in the engine mount 1 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 a synchronous filter.
Since it is sequentially updated by the above equation (1) according to the red-X LMS algorithm, after a certain amount of time has passed and each filter coefficient W _i of the adaptive digital filter W has converged to the optimum value, the drive signal y is Engine mount 1
Is supplied to the member 35, the idle vibration and the muffled sound vibration transmitted to the member 35 side via the engine mount 1 are reduced.

Further, in the present embodiment, the load sensor 2
2 is directly sandwiched between the iron yoke 10A and the lid member 48 without a rubber-like elastic body or the like, and the electromagnetic actuator 10 arranged between the supporting elastic body 6 and the member 35. Is a member clearly disposed on the member 35 side from the position where the vibration and the control vibration interfere with each other, and the yoke 10A of the electromagnetic actuator 10 passes from the engine 30 side to the member 35 side through the engine mount 1. All the forces to be transmitted are concentrated, and a space is formed around the load sensor 22 so that a part of the vibration concentrated on the yoke 10A is always transmitted to the lid member 48 side through the load sensor 22. Therefore, the residual vibration can be detected more accurately by the load sensor 22.

The residual vibration signal e, which is the output of the load sensor 22, is different from the reference signal x in which the generation timing of each pulse is important, and as shown in the above equation (1), its amplitude is the actual residual vibration signal e. Although it is important to accurately represent the magnitude of vibration, the load sensor 2 according to the present embodiment
In No. 2, since the residual vibration can be accurately detected as described above, the vibration reduction control can be performed with high accuracy.

Moreover, the rising portion 48a of the lid member 48
Is joined to the bottom surface 10a of the yoke 10A by caulking, so that the lid member 48 is integrated with the yoke 10A not only in the vertical direction but also in the horizontal direction. Therefore, for example, when the engine is shaken, the engine mount 1
Sufficient strength is secured for the lateral vibration input to the. In addition, the rising portion 48a serves to form the gap 49.

By appropriately selecting the height of the rising portion 48a and the depth of the annular recess 10e, the load sensor 22 can be provided with an appropriate preload, and if the appropriate preload can be provided, the engine mount 1 can be provided. The residual vibration signal e can be reliably changed in both the positive and negative directions according to the increase or decrease of the input load. Further, if the rising portion 48a is joined to the bottom surface 10a by caulking, it does not loosen as in the case of screwing. Therefore, the size of the gap 49 increases and the size of the preload changes with use. The likelihood of doing so is greatly reduced. This also makes it possible to expect good vibration reduction control. Further, in the present embodiment, the lower end portion 40a of the case 40 is fixed to the outer surface of the yoke 10A by caulking, and the bottom surface 10 of the yoke 10A protruding to the outside of the case 40 is fixed.
Since the lid member 48 is fixed to a and the lower surface side of the lid member 48 is brought into contact with the member 35 side to be fixed,
The case 40 can be surely brought into non-contact with the lid member 48 and the member 35, and all the force input to the support elastic body 6 can be concentrated on the yoke 10A. Therefore, the good vibration reduction control as described above can be realized.

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 46 are provided 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

Further, since the orifice forming body 46 is formed so as to project radially inward at the substantially vertical center of the fluid chamber 15, the inside of the fluid chamber 15 is divided into upper and lower parts with the orifice forming body 46 as a boundary. It has a different structure. Then, considering the space of the inner diameter portion of the orifice forming body 46 as the orifice 46b, a structure is obtained in which the two fluid chambers formed at the boundary of the orifice forming body 46 communicate with each other through the orifice 46b. Therefore, orifice 4
Considering a fluid resonance system in which the fluid in 6b is a mass and the expansion direction spring of the support elastic body 6 and the leaf spring 11 are springs, and the resonance frequency of the fluid resonance system is appropriately tuned, various vibration frequencies can be obtained. In addition, the engine mount 1 can exhibit excellent vibration damping effect.

Here, in the present embodiment, the leaf spring 11 and the magnetic path member 12 constitute a movable member, the engine mount 1 corresponds to the control vibration source, and the load sensor 2
2 corresponds to the residual vibration detecting means.

FIG. 3 is a view showing a second embodiment of the present invention and is a sectional view showing the structure of the engine mount 1. The mounting state of the engine mount 1 is the same as the first
The illustration and description thereof, which are the same as those of the first embodiment, are omitted, and the same members as those of the first embodiment,
The same reference numerals are given to the parts, and the duplicated description will be omitted.

[0061] That is, in this embodiment, on the outer peripheral surface of the yaw click 10A, without forming the step portion 10b, and 10c, also,
The small diameter portion 40b is not formed on the inner peripheral surface of the case 40.
Therefore, the lower end portion 40a of the case 40 is not fixed to the outer peripheral surface of the yoke 10A by caulking, but is welded over the entire circumferential direction between the lower end surface of the case 40 and the outer peripheral surface of the yoke 10A. It is fixed to the outer peripheral surface of the yoke 10A.

Even with such a configuration, the engine 30
All the vibrations input from the engine mount 1 to the engine mount 1 are once concentrated on the yoke 10A, and other configurations such as the lid member 48 are the same as those in the first embodiment. It is possible to obtain the same operational effect as.

Moreover, since the lower end portion 40a of the case 40 is fixed to the outer peripheral surface of the yoke 10A by welding, it is necessary to form a step or the like on the outer peripheral surface of the yoke 10A as compared with the case of fixing by caulking. There is also an advantage that the cost of parts can be reduced accordingly.

[0064]

[0065]

[0066]

[0067]

[0068]

[0069]

In each of the above embodiments, the active vibration control device according to the present invention is applied to the engine mount 1 that supports the engine 30, but the active vibration control device according to the present invention is used. The application target of is not limited to the engine mount 1, and may be, for example, an active vibration control device of a machine tool accompanied by vibration.

In each of the above embodiments, the case 40 is used.
Is fixed to the yoke 10A by caulking or welding, but the invention is not limited to this, and a structure of fixing with a bolt may be used.

In each of the above embodiments, the vibration damping effect is obtained also by utilizing the fluid resonance obtained by the orifices 45a, 46a and the like. However, when the vibration damping effect due to the fluid resonance is unnecessary. Is the orifice structure 4
6 and the like may not be provided.

Further, in each of the above embodiments, the drive signal y is generated according to the synchronous Filtered-XLMS algorithm, but the applicable algorithm is not limited to this, and for example, a normal Filter is used.
The red-X LMS algorithm may be used, or the frequency domain LMS algorithm may be used. If the system characteristics are stable, the drive signal y may be generated by a coefficient fixed digital filter or analog filter without using an adaptive algorithm such as the LMS algorithm. In addition, when the frequency of the input vibration is constant, the frequency of the drive signal y is fixed to the frequency of the vibration, and only the phase of the drive signal y or the phase and the amplitude of the drive signal y are reduced. Feedback control such as gradually changing may be used.

[Brief description of drawings]

FIG. 1 is a cross-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.

[Figure 3] Ru der sectional view of an engine mount according to the second embodiment of the present invention.

[Explanation of symbols]

1 engine mount (control vibration source) 6 resilient support member 10 electromagnetic actuator 10A yaw click 11 leaf spring 12 magnetic path member 15 fluid chamber 16 auxiliary fluid chamber 20 the controller 22 load sensor (residual vibration detecting means) 30 Engine (vibrator) 35 Member (support) 48 Lid member 48a Rising portion 49 Gap

─────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-8-177960 (JP, A) JP-A-8-145114 (JP, A) JP-A-7-233852 (JP, A) Actual Kaihei 6- 87749 (JP, U) (58) Fields surveyed (Int.Cl. ⁷ , DB name) F16F 13/26

Claims (5)

(57) [Claims] 1. A control vibration source interposed between a vibrating body and a support body and capable of generating a control vibration that interferes with a vibration emitted from the vibrating body, and a residual vibration after the interference is detected to obtain a residual vibration signal. An active vibration control device comprising: a residual vibration detecting means for outputting; and a control means for generating and outputting a drive signal for driving the control vibration source based on the residual vibration signal, wherein the control vibration source is the vibration A supporting elastic body interposed between the body and the supporting body, a fluid chamber defined by the supporting elastic body and containing a fluid, and forming a part of a partition wall of the fluid chamber and changing the volume of the fluid chamber. A movable member that is displaceable in the moving direction, and an electromagnetic actuator that is disposed between the support elastic body and the supporting body and that generates a force that displaces the movable member in the direction. The case and the resilient support member accommodates over data is attached, the lid member is fixed to the support as well as the the support in a non-contact state, by fixing the yoke of the electromagnetic actuator, the control all of the forces transmitted to the support side from the vibration member side through the vibration source is a structure that once concentrated in the yoke, before Symbol
A peripheral portion of the lid member, by binding to a surface facing the support side of the yoke, a gap is formed between the inner portion and the yoke of the circumferential region of the lid member, and the residual vibration detecting An active vibration control device, wherein a load sensor as a means is sandwiched between the lid member and the yoke so as to be located at the center of the gap. 2. A control vibration source interposed between a vibration body and a support body and capable of generating a control vibration that interferes with a vibration emitted from the vibration body, and a residual vibration after the interference is detected to obtain a residual vibration signal. An active vibration control device comprising: a residual vibration detecting means for outputting; and a control means for generating and outputting a drive signal for driving the control vibration source based on the residual vibration signal, wherein the control vibration source is the vibration A supporting elastic body interposed between the body and the supporting body, a fluid chamber defined by the supporting elastic body and containing a fluid, and forming a part of a partition wall of the fluid chamber and changing the volume of the fluid chamber. A movable member that is displaceable in the moving direction, and an electromagnetic actuator that is disposed between the support elastic body and the supporting body and that generates a force that displaces the movable member in the direction. The yoke of the yoke is fixed to the outer peripheral surface of the yoke while the yoke is inserted inside one end of the cylindrical case so that the yoke end projects outside the case. The lid member is fixed to the end surface on the side protruding to the outside of the case, and the supporting elastic body is interposed between the inside of the other end of the case and the vibrating body, so that the control vibration source is used. a structure in which all the forces transmitted to the support side from the vibration member side is temporarily concentrate on the yoke, a peripheral portion of the front Kifuta member, by binding to a surface facing the support side of the yoke, the lid member A gap is formed between a portion inside the peripheral edge of the yoke and the yoke, and a load sensor as the residual vibration detecting means is provided so as to be located at the center of the gap. Active vibration control system, characterized in that sandwiched between. 3. A disk having a raised peripheral edge portion of the lid member.
And the rising peripheral edge of the lid member is the predetermined portion.
The surface of the material facing the support side, and
3. The active vibration control device according to claim 1 , wherein the edge portion and the predetermined member are joined together by caulking . 4. The movable member is the vibrating body and a support body.
Of which the electromagnetic actuator is installed
It consists of a leaf spring whose edges are supported, and a magnetizable material.
Surface of the central portion of the leaf spring on the electromagnetic actuator side
Active vibration control device according to any one of claims 1 to 3 and a magnetic path member fixed to. 5. The fluid chamber communicates with an orifice.
With a variable volume sub-fluid chamber,
A contract in which a fluid is enclosed in the orifice and the sub-fluid chamber.
Motomeko 1 to active vibration control <br/> equipment according to claim 4.