JPH10306842A - Active type damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a stable damping effect by integratedly mounting a temperature sensor for obtaining a temperature signal as one of control signals of supply current against a coil member. SOLUTION: First and second rubber elastic bodies 20, 22 constituting a vibration system are constituted into an integrated rubber elastic body 74, and a temperature sensor 76 is fitted in the annular groove 61 of a metal fitting 18 covered with it. Heat generated by current supply to coils 26, 28 is continuously generated during operation of a damper 10, in addition to this the heat is apt to be accumulated in the interior by the construction of the damper 10, and hence the damper 10 itself becomes at high temperature and temperature change of the rubber elastic bodies 20, 22 cannot be avoided. By adjusting supply current to the coils 26, 28 by means of a supply current control device 78 based on the temperature change of the rubber elastic bodies 20, 22 detected with the temperature sensor 76, characteristic change of spring constant and the like accompanying the temperature change can be lightened or dissolved. Hence a stable damping effect can be provided.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration damper mounted on a vibration damping object to reduce vibration, and more particularly to an electromagnetic vibration means including a coil member and a magnet member. BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an active vibration damper that actively suppresses vibration by applying a vibration force based on an electromagnetic force generated by power supply to a vibration damping target.

[0002]

2. Description of the Related Art Conventionally, as a means for reducing the vibration of a vibration damping object which is a member in which vibration (including noise caused by vibration) is a problem, such as an automobile body, a conventional method is known. As described in Japanese Unexamined Patent Publication No. Hei 7-190139, etc., by providing an exciting force generating means and applying an exciting force corresponding to the vibration to be damped to the vibration damping target,
A vibration damper that actively reduces vibration of a vibration damping target has been proposed.

In order to obtain an effective vibration damping effect in such an active vibration damper, it is preferable to use a vibration force generating means that can easily control the frequency, magnitude, phase, etc. of the vibration force. Generally, by disposing a coil member and a magnet member so as to be relatively displaceable, an exciting force based on an electromagnetic force generated between the coil member and the magnet member due to energization of the coil member is exerted on the vibration damping target. Electromagnetic vibration means are employed. In addition, in order to obtain a larger vibration force, such a vibration means generally forms one vibration system by supporting one of the coil member and the magnet member with a rubber elastic body, and utilizes the resonance action. Thus, a configuration is adopted in which the excitation force is efficiently applied to the vibration damping target.

[0004] In such an active vibration damper, the frequency range in which an advantageous transfer effect of the exciting force utilizing the resonance action of the vibration system is exhibited corresponds to the natural frequency range of the vibration system. Since it is limited to a narrow area, it is extremely important to tune the natural frequency of the vibration system in accordance with the vibration frequency to be damped.

However, in the conventional active vibration damper,
Even if the natural frequency of the vibration system was tuned to the vibration frequency to be damped, the intended damping effect was not always effectively exhibited when actually mounted on the vibration damping target and operated. In the actual mounting state, the natural frequency of the vibration system is not stable and deviates from the initial set frequency. In some cases, it was difficult to demonstrate.

In addition, in the conventional active vibration damper, an advantageous exciting force transmitting effect based on the resonance action of the vibration system is exhibited only in the natural vibration frequency range of one vibration system. Due to the limitation, there is also a problem that it is extremely difficult to obtain an effective vibration damping effect with respect to a plurality of vibrations in a wide or wide frequency range.

Furthermore, in order to obtain an effective vibration damping effect in an active vibration damper, it is not sufficient to simply set only the excitation frequency in accordance with the vibration frequency to be damped, but it is not sufficient to set the vibration in the vibration damping target. Considering the size (amplitude) and phase of
It is also extremely important to adjust the amplitude and phase of the excitation force transmitted to the vibration damping target. Therefore, for example, in a vibration damper mounted on a vehicle body of an automobile, since the vibration frequency, amplitude, and phase of the vehicle body generally change with a change in the engine speed, the coil is controlled based on a preset map. The generated excitation force is adjusted by adjusting the phase and magnitude of the current supplied to the members according to the engine speed.

However, in the conventional active damper, even if a map for controlling the current supplied to the coil member is set in consideration of the dynamic characteristics of the damper, the damper is actually controlled. When mounted on a vibration target and operated, the intended vibration damping effect was not always effective in many cases.In an actual mounting state, the amplitude and phase of the excitation force exerted on the vibration control target In some cases, the deviation from the target value makes it difficult for an effective vibration damping effect to be exerted with respect to vibration for vibration prevention.

[0009]

Here, the present invention has been made in view of the above-mentioned circumstances, and the problem to be solved is that even in an actual mounted state, active excitation by transmission of an exciting force is performed. Provided is an active vibration damper provided with an electromagnetic vibration means capable of effectively exhibiting a vibration damping effect against vibration for the purpose of vibration isolation and obtaining a stable vibration damping effect. It is in.

Further, the present invention provides an active device capable of exhibiting an effective vibration damping effect even with respect to a plurality of vibrations in a wide or wide frequency range, based on advantageous transmission of a vibrating force utilizing resonance of a vibration system. It is also an object to provide a mold damper.

[0011]

In order to solve such a problem, the present inventor has conducted a number of experiments and made intensive studies. As a result, an active vibration damper having an electromagnetic vibration means has a problem in terms of its control. In addition to the fact that the coil member continues to generate heat when energized during operation, the amount of heat generated in the coil member is liable to be trapped inside due to its structure. It is newly found that the fact that the temperature change due to self-heating is unavoidable is likely to be a major cause of the conventional problem that it is difficult to stably exhibit the vibration damping effect.

That is, in order to obtain an effective vibration damping effect,
In order to obtain an exciting force corresponding to the magnitude of the vibration to be damped, in addition to supplying a high frequency current corresponding to the vibration frequency to be damped to the coil member of the vibration damper Since a relatively large current is applied to the rubber elastic body, the amount of heat generated by the coil member tends to increase, and the internal heat generation of the rubber elastic body itself tends to increase. As a result, the generated heat is accumulated in the vibration damper and becomes high temperature. As a result, the temperature change of the rubber elastic body constituting the vibration system also becomes large, so that the characteristics such as the spring constant are not largely changed. In addition to this, the deviation of the natural frequency of the vibration system also increases, and the transmission characteristics of the excitation force, such as the phase angle, are likely to change greatly. When performing map control of power supply to coil members, it becomes difficult to exhibit effective damping effects because the prerequisites at the time of map setting are shifted, making it difficult for effective damping effects to be exhibited. It became clear that the effect was reduced. In actual use,
The temperature change due to changes in the operating conditions and the environment is added to the current generated by the coil members, so that the rubber elastic body is exposed to a wider temperature change. Therefore, a decrease in the vibration damping effect due to the change in the vibration tends to be a more serious problem.

Conventionally, in a vibration isolating support such as an engine mount using a rubber elastic body, a change in spring constant of the rubber elastic body due to a change in environmental temperature due to heat generation of the internal combustion engine or the like is taken into consideration. In addition, anti-vibration supports have been proposed which compensate for the deviation of the anti-vibration characteristics due to a change in the spring constant of the rubber elastic body. It ’s just something we considered,
In the case where there is no external heating element such as an internal combustion engine, temperature compensation is not performed. In short, in the related art, there is no recognition of the problem that the vibration damping characteristic is shifted due to the coil member serving as the heating element, which is peculiar to the vibration damper having the electromagnetic driving means. It was. In particular, in the case of an active vibration damper in which a vibration damping effect is obtained by utilizing the resonance action of a vibration system composed of a rubber elastic body, a spring constant or the like due to a characteristic change caused by a temperature change of the rubber elastic body. The characteristic change directly affects the vibration damping effect. Therefore, in this respect, the vibration isolating support such as the engine mount is not a problem caused by the temperature change of the rubber elastic body. The technical meaning is different, and the reduction of the vibration suppression effect due to the temperature change of the rubber elastic body that constitutes the vibration system uses the resonance action of the vibration system composed of the rubber elastic body to obtain the vibration suppression effect It should be recognized as a very serious problem unique to active vibration dampers.

Here, the inventions according to claims 1 to 9 are all based on the above-mentioned knowledge newly obtained by the inventor of the present invention.

A feature of the invention according to claim 1 is that at least one of the coil member and the magnet member is elastically supported by a rubber elastic body, and is disposed so as to be relatively displaceable. In an active vibration damper configured to apply an exciting force based on an electromagnetic force generated by energizing a member to a vibration damping object to actively reduce vibration of the vibration damping object, A temperature sensor for obtaining a temperature signal as one of signals for controlling a supply current to a member is integrally mounted.

According to the first aspect of the present invention, in a vibration damper having a specific structure provided with a coil member constituting an electromagnetic vibration means, a temperature sensor is provided on the vibration damper itself. Therefore, a temperature change of the rubber elastic body including a temperature rise caused by the current generated by the coil member, which can be said to be a heating element that generates heat by energization, is detected. Then, since the temperature of the vibration damper itself is measured by the integrally mounted temperature sensor, the current supplied to the coil member is adjusted based on the temperature detection signal from the temperature sensor, and the temperature is changed due to the temperature change. By controlling the excitation force so as to exhibit an effective vibration damping effect by compensating for changes in characteristics such as the spring constant of the rubber elastic body, the energization and heating of the coil member can be performed even if the external environment temperature does not change. It is possible to very advantageously address the problem inherent in active dampers with electromagnetic vibration means and the newly recognized problem that the temperature change is increased by
As a result, an effective anti-vibration effect against the vibration to be anti-vibrated is stably exhibited.

The coil member and the magnet member are relatively displaced by the Lorentz force directly applied to the coil member by energizing the coil member in the magnetic field of the magnet member, and the magnetic force generated by energizing the coil member. The electromagnetic force in the present invention may include a relative displacement force due to the attraction / repulsion of the magnetic force of the magnet member and the magnetic force of the magnet member. It includes various relative displacement forces generated between the member and the magnet member.

The coil member generates an electromagnetic force between itself and the magnet member when energized, and may be one or more. On the other hand, the magnet member is a permanent magnet, and may be a ceramic magnet (sintered magnet) such as a ferrite magnet or a rare earth magnet, or a metal magnet.

The invention described in claim 2 is the first invention.
In the active vibration damper having a structure according to the invention described in (1), an internal space partitioned from an external space by the rubber elastic body is formed, and the temperature of the internal space is measured by the temperature sensor. Is characterized by the following. In such a vibration damper having such an internal space, particularly, heat generated by energizing heat generated by the coil member and internal heat generated by the rubber elastic body is likely to be trapped and easily affected by the generated heat. Since it is detected, by adjusting the current supplied to the coil member based on the detected temperature, it is possible to more advantageously and promptly cope with the heat generated by the coil member and the internal heat generated by the rubber elastic body. As a result, a stable vibration damping effect can be obtained advantageously.

In the active vibration damper having the structure according to the first or second aspect of the present invention, the mounting position and the like of the temperature sensor are not particularly limited, but may be caused by heat generation of the coil member. The temperature change of the rubber elastic body is determined appropriately in consideration of the mounting strength and the structure so that the temperature change of the rubber elastic body can be detected advantageously and stably. For example, as described in claim 3, It is particularly effective that the temperature sensor is fixedly attached to an attachment member for attaching the rubber elastic body to the vibration damping target. That is, since the mounting member attaches the rubber elastic body to the vibration damping target, if the temperature sensor is mounted on the mounting member, the temperature sensor is fixed close to the rubber elastic body and to the vibration damping target. It can be attached firmly,
This is advantageous in terms of temperature measurement and mounting strength.

The invention described in claim 4 is the first invention.
4. An active vibration damper having a structure according to any one of the above-described aspects, wherein a cover member that covers the coil member and the magnet member is provided.
When such a cover member is provided, heat is likely to be trapped inside, but by adjusting the current supplied to the coil member based on the temperature detected by the temperature sensor, the adverse effect of the heat trapped inside by the cover member is reduced or Thus, the cover member prevents foreign matter from entering between the coil member and the magnet member that are relatively displaced, thereby improving the operation stability and durability. Can be achieved advantageously.

The invention described in claim 5 is the first invention.
An active vibration damper having a structure according to any one of claims 1 to 4, characterized in that it is mounted in an engine room of an automobile. When a vibration damper is installed in an engine room of an automobile, the rubber elastic body is exposed to a larger temperature change due to a change in the outside air temperature and heat generated by the internal combustion engine in addition to the energized heat generated by the coil member. By adjusting the current supplied to the coil member based on the temperature detected by the temperature sensor, the characteristic change of the rubber elastic body due to the temperature change can be compensated with high accuracy, and the intended vibration damping effect can be stably obtained. You can do it.

[0023] The invention described in claim 6 is the first invention.
In the active vibration damper having a structure according to any one of claims 1 to 5, the coil member and the magnet member are each elastically supported by the rubber elastic body,
A first vibration system and a second vibration system having different natural frequencies are configured. In such a vibration damper having two vibration systems having different natural frequencies, the resonance operation of the vibration system is exhibited in each of the natural frequency ranges, thereby reducing power consumption (for the coil member). Power supply) can exert an effective excitation force on the vibration damping object,
An excellent vibration damping effect can be exerted on vibrations in a plurality or in a wide frequency range.

In the active vibration damper having the structure according to the sixth aspect of the present invention, the first and second vibration systems constituted by the coil member and the magnet member have different natural frequencies. The specific configuration is not limited at all, and for example, the configuration described in claim 7 is advantageously employed. That is, according to a seventh aspect of the present invention, in the active vibration damper having the structure according to the sixth aspect, the coil member and the annular mounting member fixed to the vibration damping target are connected to each other. While one of the support portions of the magnet member is spaced apart from the inner peripheral side of the mounting member, the other support portion of the coil member and the magnet member is positioned on the outer peripheral side of the mounting member. The support portions are elastically moved by the rubber elastic body interposed between the mounting member and the radially opposed surfaces of the support portions and the mounting member. It is characterized by the fact that it is connected. In the active vibration damper having the structure according to the seventh aspect of the present invention, the coil member and the magnet member are elastically supported by rubber elastic members independent of each other, so that they have different natural frequencies. Two oscillation systems that can be tuned are advantageously configured. In addition, since the rubber elastic body constituting each vibration system is easily configured as a shear deformation rubber, the tuning range of the natural frequency can be advantageously secured even in a low frequency range.

The invention described in claim 8 is the first invention.
8. The active vibration damper having a structure according to any one of claims 7 to 7, wherein the magnet member is disposed in a hollow hole of the coil member, and magnetic poles are set at both axial ends of the magnet member. And a pair of yoke members which are axially separated from and opposed to both axial end surfaces of the magnet member are respectively superposed and fixed on the axial end portions of the coil member. A central shaft protruding from both sides in the axial direction of the magnet member is provided so as to be displaceable in the axial direction through the respective yoke members. In the active vibration damper having the structure according to the eighth aspect of the present invention, the coil member and the magnet member are efficiently disposed, and the coil member and the magnet member are energized by energizing the coil member. The electromagnetic force is efficiently applied in the meantime, and an exciting force on the object to be damped is advantageously generated.

Further, in particular, the invention according to claim 8 is employed in combination with the invention according to claim 7, and one end of a center shaft provided on the magnet member is provided on the inner peripheral side of the annular mounting member. While positioning as a support, on the outer peripheral side of the mounting member,
By disposing the annular support portion provided on the coil member, the two vibration systems can be advantageously configured with good space efficiency by the magnet member and the coil member.

According to a ninth aspect of the present invention, there is provided an active vibration damping device having a structure according to any one of the first to eighth aspects, wherein a frequency component corresponding to the vibration to be damped is provided. A power supply control device that determines a phase and an amplitude of a supply current to the coil member according to a value of a temperature signal obtained by the temperature sensor based on a preset map. And That is, since the spring characteristics and the like and the vibration transmission characteristics and the like of the rubber elastic body generally change substantially corresponding to the temperature,
In accordance with the value of the temperature signal obtained by the temperature sensor, by adjusting the phase and amplitude of the supplied current to the coil member and thus the generated excitation force, the excitation force is changed to follow the vibration to be damped. An effective anti-vibration effect can be obtained stably. Also, there, the control corresponding to the detected temperature of the supply current to the coil member,
For example, the control can be performed by feedback control using a temperature correction formula or the like obtained in advance, but the structure and control method of the control device can be simplified particularly by adopting the map control as described in claim 9. As a result, cost and design are advantageous, and excellent responsiveness is achieved.

[0028]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, in order to clarify the present invention more specifically, one embodiment of the present invention will be described in detail with reference to the drawings.

First, FIG. 1 shows a vibration damper 10 as one embodiment of the present invention. This vibration damper 10
A coil member 12 having an air-core coil structure;
And the magnet member 14 disposed in the state of being accommodated in the air core portion of the vibration damping member 16 with respect to the mounting bracket 18 attached to the vibration damping target 16 via the first rubber elastic body 20 and the second rubber elastic body 22. , Each of which has an elastically supported structure, and controls an exciting force in the axial direction (vertical direction in the figure) based on an electromagnetic force generated between the coil member 12 and the magnet member 14. The object 16 can be affected.

More specifically, the coil member 12 includes a first coil 26 and a second coil 28, each of which is covered with an insulating protective material 24.
8 are superposed in the axial direction, and a total of 11 laminated plates 3 each formed of a ferromagnetic material having a substantially annular plate shape
0 is superposed between the coils 26 and 28 and on both sides in the axial direction. In short, the first and second coils 26 and 28 and the laminated plate 30 are stacked on each other in the axial direction so as to form a thick cylindrical shape having a predetermined axial length as a whole. Thus, a substantially air-core-structured coil is constituted as a whole.

Further, the first and second coils 26, 26
A substantially disk-shaped upper yoke plate 32 and a lower yoke plate 34 each serving as a yoke member made of a ferromagnetic material are superimposed on both axial sides of a superimposed body of the laminated plate 30 and the outermost laminated plate 30. , 30 are superimposed. Also,
The upper yoke plate 32 and the lower yoke plate 34 respectively
A small-diameter cylindrical sliding sleeve 36 extending through the central portion in the axial direction is attached. In short, these upper and lower yoke plates 32 and 34 are formed by the first and second coils 2.
The coils 38, 28 and the laminated plate 30 are assembled so as to cover the air core 38 of the coil from both sides in the axial direction. The first and second coils 26 and 28, the laminate 30 and the upper and lower yoke plates 3
The two and 34 are inserted into the holding cylinder 40 and are axially sandwiched by the annular locking pieces 42 and the caulking locking pieces 44 provided at both ends in the axial direction of the holding cylinder 40, so that they are overlapped. In this state, the coil members 12 are fixed to each other, and thus the coil member 12 having an air-core structure as a whole is configured. The holding cylinder 40 may be made of a ferromagnetic material or a non-magnetic material.

On the other hand, the magnet member 14 is provided with a ring-shaped permanent magnet 46 formed of a known permanent magnet material, and a circular magnet made of a ferromagnetic material is provided on both axial sides of the permanent magnet 46. Ring block-shaped upper and lower blocks 48, 50
Are superimposed. A circular rod-shaped center shaft 52 is inserted through the center holes of the permanent magnet 46 and the upper and lower blocks 48 and 50, and upper and lower fixing rings 53 and 54 fitted to the center shaft 52 so as to be fixed in position. The permanent magnet 46 and the upper and lower blocks 48 and 50 are sandwiched in the axial direction between them, so that the permanent magnet 46 and the upper and lower blocks 48 and 50 are fixed in an axially intermediate portion of the center shaft 52 in a superposed state.

Here, the magnetic poles of the permanent magnet 46 are set on both sides in the axial direction, so that the axial end on the upper block 48 side as a whole has an N pole and the lower block 5
The axial end on the 0 side is set to the S pole.
The center shaft 52 is desirably formed of a non-magnetic material such as aluminum. The outer diameters of the permanent magnet 46 and the upper and lower blocks 48 and 50 are slightly smaller than the inner diameters of the coils 26 and 28 and the laminated plate 30 constituting the coil member 12, and the permanent magnet 46 and the upper and lower blocks The axial overlapping dimension of 48 and 50 is sufficiently smaller than the dimension between the opposing surfaces of the upper and lower yoke plates 32 and 34 in the coil member 12. Thereby, the permanent magnet 46 in the magnet member 14 and the upper and lower blocks 48,5
The overlapped portion of 0 is accommodated in the air core 38 of the coil member 12, and is disposed in the air core 38 so as to be displaceable in the axial direction.

The upper and lower ends of the center axis 52 of the magnet member 14 in the axial direction are connected to the upper and lower yoke plates 32 of the coil member 12.
It is inserted through sliding sleeves 36, 36 fixed to 34. The center shaft 52 is connected to the sliding sleeve 36,
By being slidably guided in the axial direction by 36, the magnet member 14 is positioned and held on the same axis with respect to the coil member 12, and relative displacement in the axial direction is allowed. The coil member 1 of the magnet member 14
The relative displacement amount in the axial direction with respect to 2 is limited by the contact of the upper and lower blocks 48, 50 of the magnet member 14 with the upper and lower yoke plates 32, 34 of the coil member 12, but the contact surface is limited. The upper and lower yoke plates 32, 34 are provided with sliding sleeves 36, 36, and upper and lower fixing rings 53, 54, which are opposed to each other. The lower yoke plate 34 can be brought into contact with the lower yoke plate 34.

Further, the coil member 12 and the magnet member 14 assembled in such a manner as to be relatively displaceable are attached to the mounting bracket 18 attached to the vibration damping target 16 by the first elastic rubber support 20 and the second elastic member 20. Are elastically connected and supported via the supporting rubber elastic body 22 described above. Here, the mounting bracket 18 has a constant substantially U shape over the entire circumferential direction.
It has a substantially annular shape as a whole having a U-shaped groove-shaped cross-sectional shape. That is, the mounting bracket 18 has an annular plate-shaped mounting seat 56 at the bottom wall, and is superimposed on the vibration damping target 16 at the mounting seat 56 and fixed by a plurality of bolts 57. On the other hand, an outer supporting cylinder portion 58 which rises in a tapered cylindrical shape by being inclined inwardly by the outer peripheral side vertical wall portion is formed, and is formed to be cylindrical by the inner peripheral side vertical wall portion. An inner support cylinder portion 60 is configured.

The mounting member 18 is located on one side of the coil member 12 and the magnet member 14 in the axial direction (downward in the figure).
At a predetermined distance on the side of the annular groove 61 having a U-shaped cross section.
Are open on the side of the coil member 12 and the magnet member 14, and are opposed to each other on substantially the same axis. Under such an arrangement, a cover member 62 having a substantially large diameter inverted cup shape is externally fitted and fixed to the coil member 12 from above in the axial direction (the side opposite to the mounting member 18). The entire coil member 12 including 14 is covered. In addition, a bulging portion 63 bulging outward is provided at the upper bottom portion of the cover fitting 62 in order to prevent the upper end portion of the central shaft 52 from abutting when the magnet member 14 is displaced in the axial direction. . Further, the material of the cover fitting 62 may be a ferromagnetic material or a non-magnetic material, but by employing a ferromagnetic material, it is possible to reduce or avoid the adverse effect of an external electromagnetic field. It is.

The opening of the cover fitting 62 is integrally formed with a caulking portion 64 having a flange-like portion extending radially outward, and is connected to the caulking portion 64 in a substantially annular shape. The metal fitting 66 is fixed by caulking. The connecting fitting 66 is integrally formed with a tapered cylindrical portion 68 extending downward in the axial direction (on the side of the mounting bracket 18). They are opposed to each other in a substantially parallel diagonally outward direction at a predetermined distance. An annular first rubber elastic body 20 is interposed between the facing surfaces of the outer support cylindrical portion 58 and the tapered cylindrical portion 68, and is provided on the inner and outer peripheral surfaces of the first rubber elastic body 20. By vulcanizing and bonding the opposing surfaces of the outer support tubular portion 58 and the tapered tubular portion 68, the mounting fitting 18 and the connecting fitting 66 are elastically connected.
Are elastically supported by the mounting bracket 18 via a first rubber elastic body 20. Thus, a first vibration system composed of a mass-spring system having the coil member 12 as a mass and the first rubber elastic body 20 as a spring is configured.

On the other hand, in the magnet member 14, the central shaft 52 extends axially downward (toward the mounting bracket 18) and projects from the coil member 12. Thus, a small-diameter inverted cup-shaped connecting fitting 70 is fixed by bolts. The connecting metal fitting 70 is inserted into the inner supporting cylindrical part 60 of the mounting fitting 18 and disposed on the same axis, and the cylindrical wall part 72 of the connecting metal fitting 70 is connected to the inner supporting cylindrical part of the mounting fitting 18. For 60,
They are arranged substantially in parallel in a radially inward direction at a predetermined distance from each other. An annular second rubber elastic body 22 is interposed between the opposing surfaces of the inner support cylindrical part 60 and the cylindrical wall part 72, and is provided on the inner and outer peripheral surfaces of the second rubber elastic body 22. By vulcanizing and bonding the opposing surfaces of the cylindrical wall portion 72 and the inner support cylindrical portion 60, the mounting member 18 and the connecting metal member 70 are elastically connected to each other. Thus, it is elastically supported via a second rubber elastic body 22. Thus, a second vibration system including a mass-spring system having the magnet member 14 as a mass and the second rubber elastic body 22 as a spring is configured.

Further, the first rubber elastic body 20 constituting the first vibration system and the second rubber elastic body 22 constituting the second vibration system are constituted by an integral rubber elastic body 74. , And is formed as an integrally vulcanized molded product including the mounting bracket 18 and the two connecting brackets 66 and 70. A temperature sensor 76 is fitted and fixedly assembled in the annular groove 61 of the mounting bracket 18 covered with the rubber elastic body 74. As the temperature sensor 76, any conventionally known temperature sensor can be adopted. For example, a temperature measuring resistor using a resistance change of a metal, a thermistor using a resistance or a characteristic change of a semiconductor, or the like, A thermocouple, a pyroelectric temperature sensor, a crystal temperature sensor, and the like can also be adopted in consideration of a temperature change, an environment, and the like exerted on the vibration damper.

The temperature of the vibration damper is detected by the temperature sensor 76. In the present embodiment, in particular, the rubber elastic body 74 and the cover fitting 62 separate the vibration damper from the external space. A temperature near the surface of the rubber elastic body 74 on which the temperature sensor 76 is disposed is detected as a temperature on the inner space side of the vibrator. Further, a detection signal as a temperature detected by the temperature sensor 76 is input to a power supply control device 78 for controlling a current supplied to the coils 26 and 28. Second rubber elastic body 2
By supplying an appropriate current to the coils 26 and 28 while taking into account the temperature changes of 0 and 22, vibrations that can exert an effective vibration damping effect on the vibration damping target 16 are exerted. I have.

That is, in the vibration damper 10 having the above-described structure, when the coils 26 and 28 of the coil member 12 are energized, magnetic poles are formed on both sides of the coil member 12 in the axial direction. Permanent magnet 46 in
In addition, a magnetic attraction or repulsion is exerted on the upper and lower blocks 48 and 50, or
Lorentz force is applied to the current flowing through the coils 26 and 28 disposed in the magnetic field due to the above, and as a result, a relative axial driving force is applied between the coil member 12 and the magnet member 14. Thus, based on the elastic deformation of the first rubber elastic body 20 and the second rubber elastic body 22, relative displacement in the axial direction is generated with respect to the coil member 12 and the magnet member 14. Therefore, the coil member 12
When an alternating current is supplied to the coils 26 and 28, the magnetic poles on the upper and lower sides of the coil member 12 change, so that an exciting force is generated between the coil member 12 and the magnet member 14. Then, by transmitting the excitation force to the vibration damping target 16 via the mounting bracket 18, the vibration in the vibration damping target 16 can be actively suppressed and controlled.

Here, in order to obtain an effective active vibration damping effect for the vibration damping object 16, the vibration damping object 1 is attached via the mounting bracket 18 from the first and second rubber elastic bodies 20 and 22.
6 by the power supply control device 78 so that the exciting force transmitted to 6 has a frequency and an amplitude (magnitude) corresponding to the vibration to be damped in the vibration damping target 16 and is substantially in opposite phase. It is necessary to control the current supplied to the coils 26, 28.

Therefore, in the power supply control device 78 of the present embodiment, the supply current to the coil members 26 and 28 is obtained based on a reference signal having a frequency component corresponding to the vibration to be damped. For example, when suppressing body vibration of an automobile, a signal obtained by directly detecting vibration of a body to be damped by an acceleration sensor or the like, or a detection signal of a rotation angle of a crankshaft of an internal combustion engine, or the like is used. By using it as a reference signal, a supply current having a frequency component corresponding to the vibration to be damped is advantageously generated.

The phase and amplitude of the supply current are determined based on a map determined in advance by experiments and the like and in correspondence with appropriate reference factors. If you want to suppress,
Using the rotational speed of the internal combustion engine as a reference factor, the phase and amplitude of the supply current are adjusted or set so as to correspond to the phase and amplitude of the body vibration that changes according to the rotational speed of the internal combustion engine due to engine mounting characteristics and the like. This will be advantageously determined. Further, at this time, a map corresponding to the detected temperature value detected by the temperature sensor is selected from a plurality of maps set for each predetermined temperature range.

As a result, it is possible to avoid deviation from the optimum value or the target value of the vibration control due to a change in characteristics such as a spring constant caused by a temperature change of the first and second rubber elastic bodies 20 and 22. Therefore, an exciting force having a phase and a magnitude (amplitude) capable of exhibiting an effective damping effect is advantageously and stably applied to the damping target. That is, the heat generated by energizing the coils 26 and 28 continues to be generated while the vibration damper 10 is operating (while power is being supplied), and also accumulates internally from the structure of the vibration damper 10. Since the temperature of the vibration damper 10 itself becomes high and temperature changes of the first and second rubber elastic bodies 20 and 22 cannot be avoided, the power supply control device 78 Supply current to the temperature sensors 76 and 28
First and second rubber elastic bodies 20, 2 detected by
2, the first and second rubber elastic bodies 20 and 22 change in characteristics such as a spring constant due to the temperature change, in other words, the first and second rubber elastic bodies 20 and 22 function as an exciting force transmitting body. It is possible to reduce or eliminate the decrease in the vibration damping effect due to the change in the excitation force transmission characteristics of the second rubber elastic bodies 20 and 22, and it is possible to obtain a stable vibration damping effect. .

Further, in the vibration damper 10, since the first vibration system is constituted by the coil member 12 and the second vibration system is constituted by the magnet member 14, the first and second vibration systems are formed. By utilizing the resonance action of the vibration system, the vibrating force generated between the coil member 12 and the magnet member 14 is more efficiently controlled around the natural frequencies of the first and second vibration systems. The vibration can be exerted on the vibration target 16, whereby a more excellent vibration damping effect can be obtained. In particular, since the first vibration system and the second vibration system have respective natural frequencies set in different frequency ranges, a plurality of or a wide frequency range is utilized by utilizing the resonance action of the vibration systems. It is possible to obtain an excellent vibration damping effect in, for example, when used as a body vibration damper for an automobile, the natural frequency of the first vibration system in a high frequency range equivalent to muffled sound. On the other hand, by tuning the natural frequency of the second vibration system to a low frequency range corresponding to idle vibration or the like, for any vibration in the low frequency range and the high frequency range,
It is possible to obtain an effective vibration damping effect using the resonance action of the vibration system.

The natural frequency of each vibration system is adjusted by adjusting the spring constants of the first and second rubber elastic bodies 20 and 22 while taking into account the mass of the coil member 12 and the magnet member 14 as described above. In particular, in the second vibration system, the permanent magnet 46 and the upper and lower blocks 4
Since the mass of the magnet member 14 is increased by 8, 50 and the second rubber elastic body 22 is mainly deformed by shearing, its natural frequency is advantageously tuned to a low frequency range. While it is possible,
In the first vibration system, the first rubber elastic body 20 is disposed between the outer supporting cylinder portion 58 and the tapered cylinder portion 68 which are respectively inclined and obliquely opposed in the oblique axial direction, so that the compression / tensile deformation is reduced. Since it can be generated, its natural frequency can be tuned advantageously in a high frequency range.

In particular, in the vibration damper 10 of the present embodiment, the first rubber elastic body 20 forming the first vibration system and the second rubber elastic body 22 forming the second vibration system are Since the first rubber elastic body 20 and the second rubber elastic body 22 can be easily set for each of the spring constants because of the substantially separate structure, the first vibration system and the second vibration There is an advantage that the natural frequency of the system can be easily tuned to each target frequency range.

Further, in the vibration damper 10, since the power supply control device 78 controls the energization of the coils 26 and 28 in consideration of the temperature change, the first and second vibration systems are constituted. The temperature of the first rubber elastic body 20 and the second rubber elastic body 22 changes due to the influence of the coil member 12 serving as a heating element due to energization, and the natural frequencies of the first and second vibration systems shift. Even in such a case, the energization control of the coils 26 and 28 is performed in consideration of the deviation of the natural frequency so that an exciting force enough to exert an effective damping effect on the damping target 16 is exerted. It is possible to achieve a stable damping effect.

Further, in the vibration damper 10 of the present embodiment, the coil member 12 is covered with the cover metal 62 and the opening of the cover metal 62 is formed of the first rubber elastic body 2.
0 and the second rubber elastic body 22 so as to cover the space defined substantially by the cover metal fitting 62 and the first and second rubber elastic bodies 20 and 22 from the external space. Since the coil member 12 and the magnet member 14 are provided, the invasion and biting of foreign matter between the relative displacement members of the coil member 12 and the magnet member 14 and between sliding parts are advantageously prevented, and stable. Operation is realized. Here, in the vibration damper 10, the current supplied to the coils 26 and 28 is reduced in consideration of the change in the excitation force transmission characteristic caused by the temperature change of the first and second rubber elastic bodies 20 and 22. Since it is controlled, the structure in which the coil member 12 is covered with the cover fitting 62 and the first and second rubber elastic bodies 20 and 22 is employed, so that the heat generated by the coil member 12 is more easily accumulated. Therefore, the change and instability of the vibration damping performance due to the above are advantageously reduced.

Although the embodiment of the present invention has been described in detail above, this is a literal example, and the present invention is not interpreted in any limited manner by the specific description of the embodiment. .

For example, the first rubber elastic body for supporting the coil member and the second rubber elastic body for supporting the magnet member may be formed as an integral shape that is not clearly divided, or may be formed as a completely divided separate elastic body. It can also be formed of body rubber.

Further, either the coil member or the magnet member can be fixedly attached to the attachment member.

Further, the specific structure of the electromagnetic driving means including the coil member and the magnet member is not limited at all, and the relative displacement force between the coil member and the magnet member by energizing the coil member. A variety of structures that can be used are adopted. For example, a gap portion is provided on a magnetic path in the form of a closed magnetic circuit formed by a permanent magnet and a yoke member,
A voice coil structure in which a coil member is inserted and arranged in such a gap portion, or an iron core is mounted on a coil constituting the coil member, and the iron core and the magnetic pole forming surfaces of the magnet member are opposed to each other at a predetermined distance. Accordingly, an electromagnet structure or the like that can be displaced toward or away from each other in the opposite direction by the attraction / repulsion of the magnetic force can be adopted.

Further, the arrangement position and the mounting structure of the temperature sensor are not limited at all, and are appropriately determined in consideration of the arrangement environment and structure of the vibration damper.

In addition, although not enumerated one by one, the present invention
Based on the knowledge of those skilled in the art, the present invention can be implemented in a form in which various changes, modifications, improvements, and the like are made.
It goes without saying that all such embodiments are included within the scope of the present invention, without departing from the spirit of the present invention.

[0057]

As is clear from the above description, in the active vibration damper having the structure according to the first to ninth aspects of the present invention, any of the active vibration dampers of the electromagnetic type caused by the heat generated by the energization of the coil member. It is possible to effectively cope with the unique and new problems inherent in the active vibration damper having the vibration means, and to reduce the change in the vibration transmission characteristic caused by the temperature change of the rubber elastic body. It is possible to reduce or avoid the accompanying decrease in the vibration damping effect, thereby effectively and stably exerting the target vibration damping effect on the vibration damping target.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a vibration damper as one embodiment of the present invention.

[Explanation of symbols]

 REFERENCE SIGNS LIST 10 damper 12 coil member 14 magnet member 16 damping target 18 mounting bracket 20 first rubber elastic body 22 second rubber elastic body 26 first coil 28 second coil 46 permanent magnet 48 upper block 50 lower block 76 Temperature sensor 78 Power supply control device

Claims (9)

[Claims] 1. A coil member and a magnet member, at least one of which is elastically supported by a rubber elastic body, is disposed so as to be relatively displaceable, and a coil based on an electromagnetic force generated by energizing the coil member. In an active vibration damper in which a vibration force is exerted on a vibration damping target to actively reduce the vibration of the vibration damping target, a temperature as one of control signals of a supply current to the coil member is provided. An active vibration damper, wherein a temperature sensor for obtaining a signal is integrally mounted. 2. The device according to claim 1, wherein an internal space separated from the external space is formed by the rubber elastic body, and the temperature of the internal space is measured by the temperature sensor. Active damper. 3. The active vibration damper according to claim 1, wherein the temperature sensor is fixedly mounted on a mounting member for mounting the rubber elastic body to the vibration damping target. 4. The active vibration damper according to claim 1, further comprising a cover member that covers said coil member and said magnet member. 5. The active vibration damper according to claim 1, which is mounted in an engine room of an automobile. 6. A first vibration system and a second vibration system having different natural frequencies from each other, wherein the coil member and the magnet member are elastically supported by the rubber elastic body, respectively. Item 6. The active vibration damper according to any one of Items 1 to 5. 7. A supporting portion of one of said coil member and said magnet member is located at an inner peripheral side of said mounting member with respect to an annular mounting member fixed to said vibration damping target. On the other hand, the other supporting portion of the coil member and the magnet member is located at a distance from the outer peripheral side of the mounting member, and each of the supporting portions, with respect to the mounting member,
7. The active vibration damper according to claim 6, wherein said rubber elastic bodies are elastically interposed between radially opposed surfaces of said support portions and said mounting member. 8. The magnet member is disposed in a hollow hole of the coil member, and magnetic poles are set at both ends in the axial direction of the magnet member. A pair of yoke members, which are opposed to each other in the axial direction, are fixed to each other in the axial direction at both ends in the axial direction of the coil member, and a central shaft protruding on both axial sides of the magnet member is provided. The active vibration damper according to any one of claims 1 to 7, wherein said active vibration damper is disposed so as to be axially displaceable through said respective yoke members. 9. A temperature signal value obtained by the temperature sensor based on a preset map, wherein a phase and an amplitude of a supply current to the coil member having a frequency component corresponding to vibration to be damped are obtained. The active vibration damper according to any one of claims 1 to 8, further comprising a power supply control device that is determined according to the following.