JP2001200885A - Active damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a new structural active damper capable of effectively and stably damping vibrations transmitted from a power unit by a small amount of energy consumption. SOLUTION: A mass member 66 vibrated by a vibrating means 20 is elastically supported by a mount rubber elastic element 18 arranged on a vibration transmitting path, thereby composing a vibration system. By using a resonant action of the vibration system, vibrating force is efficiently applied on an isolating support system 10.

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 an anti-vibration support system of a power unit to reduce vibration of a support member for supporting the power unit through an engine mount. BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an active vibration damper that actively or destructively suppresses transmission vibration from a power unit.

[0002]

2. Description of the Related Art In order to reduce vibration in a support member for supporting a power unit such as an internal combustion engine, a support mechanism in which the power unit is supported by an engine mount with respect to the support member using an engine mount has been used. Then
In order to further improve the vibration isolation performance, for example, in an automobile, an engine is operated by a drive signal synchronized with the rotation of the engine to apply a vibration force corresponding to a transmitted vibration from a power unit to a vehicle body as a support member, thereby enabling an engine. There has been proposed an active-type vibration damper that actively or actively suppresses transmission vibration from a power unit including the above. For example, those described in JP-A-6-235438 and the like,
That is it.

However, in order to obtain an effective vibration damping effect by such an active vibration damper, it is necessary to employ a vibration means capable of generating a vibration force corresponding to the vibration to be damped. Therefore, especially when the supporting member is large and the vibration energy is large, such as the body of an automobile, the vibration means is increased in size, or the energy consumption of the vibration means (electric power, etc.)
However, there was a problem that it was unavoidable to increase the size of the support member, and there was also a problem that it was difficult to obtain a satisfactory vibration damping effect because it was difficult to apply a sufficient excitation force to the support member. .

Further, in a vehicle body, not only vibrations synchronized with the engine rotation transmitted from the power unit but also various vibrations not synchronized with the engine rotation transmitted from the suspension system are generated. The active damper could be adversely affected by vibrations that are not synchronized with engine rotation, resulting in unstable operation.

[0005]

The present invention has been made in view of the circumstances described above, and an object of the present invention is to effectively and stably reduce the vibration transmitted from a power unit with a small amount of energy consumption. An object of the present invention is to provide an active damper having a novel structure capable of damping.

[0006]

An embodiment of the present invention which has been made to solve such a problem will be described below. The components in each of the embodiments described below can be adopted in any combination as much as possible. Further, aspects and technical features of the present invention are not limited to those described below.
It is to be understood that the present invention is described in the entire specification and drawings, or is recognized based on the inventive concept that can be understood by those skilled in the art from the description.

That is, in a first aspect of the present invention relating to an active vibration damper, a power unit is mounted on an anti-vibration support system in which a power unit is elastically supported by an engine mount using an engine mount. An active vibration damper provided with vibration means for actively suppressing vibration in the support member, wherein the mass member is capable of being relatively displaced in a vibration direction to be damped with respect to a fixed member attached to the support member. In addition, the mass member is elastically supported by a mount rubber elastic body disposed on a vibration transmission path from the power unit to the support member in the engine mount, while the fixing member and An active vibration damper that applies a vibration force by the vibration means between mass members is characterized.

In such an active vibration damper having the structure according to this aspect, a vibration system is constituted by a mass member vibrated by vibrating means being elastically supported by a mount rubber elastic body. Therefore, the vibration force generated by the vibration means is efficiently exerted on the vibration isolating support system by utilizing the resonance action of the vibration system, whereby a large vibration energy is generated by a small vibration energy. An exciting force can be exerted on the vibration transmission system, so that an effective active vibration damping effect can be obtained.

Further, in the active vibration damper according to this aspect, the spring system for elastically supporting the mass member on the vibration isolating support system is configured by using a mount rubber elastic body constituting the engine mount. Therefore, the number of parts can be reduced and the structure can be simplified, and in addition, the generated excitation force is applied to the mount rubber elastic body constituting the transmission path of the vibration from the power unit to the support member. ,
Since it is directly affected, adverse effects due to other vibrations not related to the vibration from the power unit are avoided as much as possible, and it is possible to stably obtain an effective anti-vibration effect against the vibration from the power unit. It is.

According to a second aspect of the present invention, in the active vibration damper having the structure according to the first aspect, the mass member is independent of the mount rubber elastic body and the mount rubber elastic body. A vibration system having multiple degrees of freedom is characterized by being elastically supported in series or in parallel by at least one supporting rubber elastic body. In such an active vibration damper having a structure according to this aspect,
By configuring a vibration system having multiple degrees of freedom, it is possible to obtain an efficient vibration damping effect based on a resonance action in each of a plurality of natural frequency ranges. Specifically, for example, the present invention is applied to an active damper for an automobile to form a two-degree-of-freedom vibration system, and an idling vibration region around 15 to 45 Hz;
Efficient vibration suppression for both idling vibration and muffled sound based on the resonance action of the vibration system including the mass member by tuning the natural frequency to the muffled sound range around ~ 150 Hz. The effect can be obtained.

According to a third aspect of the present invention, there is provided an active vibration damper having a structure according to the first or second aspect, wherein the first mounting member mounted on the power unit side in the engine mount. Wherein the mass member and the vibrating means are arranged between the second mounting member attached to the support member side and the mass member and the vibrating means are incorporated in the engine mount. I do. In such an active vibration damper having the structure according to this aspect, the vibration damper can be integrated into the engine mount, thereby controlling the vibration isolation support system by the support member of the power unit. It becomes possible to easily mount the shaker. In particular, in the engine mount, a storage area partitioned from the external space is formed,
It is also possible to incorporate a vibration damper into it, and if such a structure is adopted, it is possible to cover and protect the vibration means by the engine mount. Effects such as elimination of the need are also exhibited.

According to a fourth aspect of the present invention, there is provided an active vibration damper having a structure according to any one of the first to third aspects, wherein the engine mount is provided on the first mounting member side in the engine mount. A cylindrical portion that opens toward the second mounting member is provided on the second mounting member, the mount rubber elastic body has a substantially truncated conical shape, and the first mounting member is fixed to the small-diameter side end surface and the large-diameter side. An opening portion of the cylindrical portion of the second mounting member is fixed to the outer peripheral surface of the end portion, and a cylindrical connecting fitting is embedded and fixed to a radially intermediate portion of the mount rubber elastic body, and the connection is performed. The mass member is connected and supported by a metal fitting. In the active vibration damper having the structure according to this aspect, the mass member can be advantageously and stably supported by the mount rubber elastic body. Note that the mass member can be positioned, for example, on the large-diameter end surface side of the mount rubber elastic body and housed and disposed in the cylindrical portion of the second mounting member. Alternatively, an annular mass member is used. Then, it is also possible to position it on the outer peripheral surface of the mount rubber elastic body and to dispose it between the opposing surfaces of the first mounting member and the second mounting member, and the disposing position is particularly limited. Not something.

According to a fifth aspect of the present invention, there is provided an active vibration damper having a structure according to the fourth aspect, wherein the connecting fitting is tapered with respect to a portion embedded and fixed in the mount rubber elastic body. It is characterized by having corners. In the active vibration damper having the structure according to this aspect, the change in the spring characteristic of the engine mount exerted by the mount rubber elastic body is avoided as much as possible by adjusting the angle of the taper angle. In addition, the characteristic of the support spring of the mass member can be adjusted, whereby the natural frequency of the vibration system including the mass member, that is, the active vibration isolation effect is efficiently exhibited based on the resonance action. The vibration frequency range can be easily tuned.

[0014]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, in order to clarify the present invention more specifically, embodiments of the present invention will be described in detail with reference to the drawings.

First, FIG. 1 shows an anti-vibration support system 1 having an engine mount 12 according to a first embodiment of the present invention and supporting a power unit by a body in an automobile.
0 is indicated schematically. In such an anti-vibration support system 10 for a vehicle, a power unit 22 including an engine and a transmission is elastically anti-vibration supported by a body 26 as a support member via a plurality of engine mounts 12. Vibration transmitted from the engine mount 12 to the body 26 is reduced by the engine mount 12. The engine mount 12 is configured such that both the load supported by the power unit 22 and the vibration load are input in the direction of the center axis of the mount extending substantially in the vertical direction. In the following description, the up-down direction refers to the up-down direction in FIG. 1 in principle.

Here, the engine mount 12 interposed between the power unit 22 and the body 26 includes a first mounting member 14 as a first mounting member and a second mounting member, which are spaced apart from each other in the center axis direction of the mount. The second mounting member 16 as a member is constituted by being elastically connected by a mount rubber elastic body 18. The first mounting member 14 is mounted on the power unit 22 side, and the second mounting member 16 is mounted on the power unit 22. Is attached to the body 26 side.

More specifically, the first mounting member 14 is formed of a rigid material such as iron and has a substantially circular flat plate shape. A first mounting bolt 32 protruding upward in the axial direction is integrally formed at the center portion, and the first mounting bracket 14 is fixed to the power unit 22 by the first mounting bolt 32. The bracket 24 is fixedly attached to the provided bracket 24.

The second mounting member 16 is composed of a cylindrical member 34 having a large diameter and a substantially cylindrical shape as a whole, and a bottom metal member 36 having a large diameter and a substantially bottomed cylindrical shape as a whole. An opening of a bottom fitting 36 arranged to open vertically upward is overlapped with a lower opening of a cylindrical fitting 34 arranged to open in the vertical direction, and Flange part 3 integrally formed on the periphery of opening
By caulking and fixing the caulking portion 40 integrally formed on the lower opening peripheral edge of the cylindrical metal fitting 34 with respect to 8, the second mounting bracket 16 is formed as a whole with a deep bottom cup shape. Note that a tapered cylindrical portion 42 that gradually expands upward in the axial direction is formed integrally with the upper opening of the cylindrical metal fitting 34. In the center of the bottom wall of the bottom fitting 36, a second mounting bolt 4 protruding downward in the axial direction is provided.
4 are integrally formed, and the second mounting bolt 4
4 allows the second mounting bracket 16 to be mounted on the body 26. In addition, the second mounting bracket 1
6 is formed of a rigid material such as iron, similarly to the first mounting member 14.

A first mounting member 14 is arranged at a distance from the opening of the second mounting member 16, and the first mounting member 14 and the second mounting member 16 are arranged in a vertical direction. Are arranged on the same central axis extending apart from each other.

A mount rubber elastic body 18 for elastically connecting the first fitting 14 and the second fitting 16 is provided.
Has a truncated cone shape as a whole, and has a mortar-shaped central recess 46 that opens toward the large-diameter end surface. And, the small diameter side end face is the first mounting bracket 1
4 is vulcanized and adhered to the central lower surface, while the outer peripheral surface of the large-diameter end is vulcanized and adhered to the inner peripheral surface of the cylindrical fitting 34 constituting the second mounting bracket 16. As a result, the mount rubber elastic body 18 is a thick-walled tapered cylinder extending from the central portion on the lower surface of the first mounting member 14 toward the opening of the second mounting member 16 while gradually increasing in diameter vertically downward. The inner peripheral surface 48 and the outer peripheral surface 50 of the portion extending between the first mounting bracket 14 and the second mounting bracket 16 are tapered cylinders, each of which extends at a substantially constant angle. Surface. Furthermore, the mounting rubber elastic body 18
A cylindrical covering rubber portion 52 that covers the inner peripheral surface of the cylindrical metal fitting 34 over substantially the entire surface is integrally formed at the large-diameter side end portion.

The first mounting member 14 and the second mounting member 16 are elastically connected to each other by the mount rubber elastic body 18 so that the opening above the second mounting member 16 in the axial direction is mounted. The cover is covered by the rubber elastic body 18. Thus, between the second mounting bracket 16 and the mount rubber elastic body 18, the hollow interior of the second mounting bracket 16 and the central recess 46 of the mount rubber elastic body 18 are provided. Cooperate to form a hollow internal cavity 54.

The inner space 54 has a bottom fitting 36.
An intermediate plate 56 as a cylindrical connection fitting having an outer diameter smaller than the inner diameter of the engine mount 12 is accommodated and arranged coaxially with the mount center axis of the engine mount 12.
Is embedded and fixed so that the upper end portion in the axial direction of the mounting rubber elastic member 18 penetrates the substantially radially intermediate portion of the mount rubber elastic body 18 in the axially upward direction. Thereby, in a state where the intermediate plate 56 is suspended and supported by the mount rubber elastic body 18,
It is arranged in the internal space 54. The portion of the intermediate plate 56 embedded in the mount rubber elastic body 18 includes:
A plurality of communication holes 58 penetrating the inner and outer peripheral surfaces are provided at predetermined intervals in the circumferential direction, and the mount rubber elastic body 18 is formed between the inner peripheral side and the outer peripheral side of the intermediate plate 56 by the communication holes 58. They are interconnected and integrally formed. The intermediate plate 56 is formed of a rigid material such as iron.

Further, the actuator 20 is accommodated in the internal space 54 and is arranged so as to extend between the intermediate plate 56 and the bottom wall of the second mounting member 16. The actuator 20 includes a fixing member 64 as a fixing member and a mass member 66 as a mass member, and includes an actuator mechanism that applies an exciting force between the fixing member 64 and the mass member 66. ing.
The fixing bracket 64 is fixed to the bottom wall of the second mounting bracket 16 with bolts or the like, while the mass bracket 66 is fixed.
Are press-fitted and fixed to the lower end of the intermediate plate 56. When the actuator mechanism is operated and controlled by an external controller (not shown), an exciting force is generated between the fixing bracket 64 and the mass fitting 66, and the exciting force is generated by the second mounting bracket 16, The intermediate rubber 56 is extended between the mount rubber elastic body 18.

Here, as the actuator 20, for example, those shown in FIGS. 2 and 3 are used. FIG. 2 shows an electromagnetic actuator 62 in which a fixing bracket 64 and a mass bracket 66 are opposed to each other while being separated from each other in the central axis direction. Then, the fixing bracket 64 and the mass metal fitting 66
The two metal fittings 64, 66 are attached to both metal fittings 64, 66 by an electromagnetic actuator mechanism incorporated between them.
Exciting force is applied in a direction to make the 6 approach / separate from each other.

In this case, the fixing bracket 64 is composed of a first metal plate 68 and a second metal plate 70 each having a disk shape.
Are overlapped and fixed to each other with fixing bolts 72. Also, the second sheet metal fitting 70
At the center of the housing is formed a housing recess 74 which is opened on the surface to be overlapped with the first metal plate 68, and the head is housed in the housing recess 74, and the leg portion extends upward in the axial direction. The guide rod 78 is fixed by a support bolt 76 from which is projected. The guide rod 78 is formed of a hard material such as a metal, and extends linearly with a substantially constant cross-sectional shape. A stopper 80 that extends in a direction perpendicular to the axis is formed integrally with the protruding tip.

In the center of the upper surface of the second metal plate 70,
A bobbin 82 projecting axially upward in a cup shape is overlapped, and is fixed to the second metal plate 70 by a guide rod 78 fixed by a support bolt 76. The bobbin 82 is formed of an electrical insulating material such as a synthetic resin, and has a coil 84 wound and fixed to a cylindrical portion provided at an axially protruding distal end portion.

Further, a bolt hole 86 is formed in the first metal plate 68 constituting the fixing metal member 64 so as to extend axially downward at a central portion thereof. The fixing fitting 64 is attached to the bottom fitting 36 by interpolating 88.

On the other hand, the mass metal fitting 66 is formed of a ferromagnetic material such as iron and a material made of a material having a high specific gravity in a large-diameter circular block shape. A hole 94 is formed, and a sliding bush 96 made of a cylindrical low-friction resin sleeve or the like is incorporated in the guide hole 94. Furthermore, an annular concave groove 98 is formed in the mass metal fitting 66 so as to continuously extend in the circumferential direction at the radially intermediate portion and open on one side in the axial direction (the lower side in FIG. 2). This annular groove 9
A permanent magnet 100 is inserted and arranged in 8 and is fixed to the inner surface of the outer peripheral side wall of the annular groove 98. In addition, even if the permanent magnet 100 is continuous over the entire circumference in the circumferential direction,
In addition, it may be discontinuous. And this permanent magnet 1
00, both magnetic poles are set on the inner peripheral surface side and the outer peripheral surface side, so that a donut-shaped magnetic path as a whole is formed in the mass metal fitting 66, and an annular concave is formed on the magnetic path. The groove 98 is positioned to form a generally cylindrical magnetic gap.

The mass metal fitting 66 is opposed to the fixed metal fitting 64 on the same central axis. Note that an annular additional mass 90 extending in the circumferential direction on the outer peripheral edge portion is superimposed on the lower end surface of the mass metal fitting 66, and is fixed by a connecting bolt 102. A guide rod 78 protruding from the fixing bracket 64 is slidably inserted into a sliding bush 96 provided in the guide hole 94 of the mass metal fitting 66. Based on the guide action, the mass metal fitting 66 is stably displaced relative to the fixing metal fitting 64 in the approaching / separating direction on the central axis with the elastic deformation of the mount rubber elastic body 18. .

An annular cushion rubber 104 protruding toward the fixing bracket 64 is fixed to the mass metal fitting 66 outside the axially lower opening of the guide hole 94.
The mass metal fitting 66 abuts on the fixing metal fitting 64 side (the bottom wall of the bobbin 82) via the cushion rubber 104,
The amount of relative displacement in the approach direction in the axial direction between the fixing metal fitting 64 and the mass metal fitting 66 is limited in a buffered manner. A large-diameter recess 106 is formed at an open end of the mass metal fitting 66 on the outer side of the guide hole 94 (the side opposite to the fixing metal fitting 64), and a guide rod is formed in the large-diameter recess 106. 78 stopper portions 80 are accommodated and arranged. When the mass metal member 66 is relatively displaced in the direction away from the fixing metal member 64, the stopper 80 of the guide rod 78 abuts against the bottom surface of the large-diameter recess 106 of the mass metal member 66, so that both of them can be used. The relative displacement of the metal fittings 64 and 66 is limited. In addition, large-diameter recess 1
A cushion rubber 108 is provided on the bottom surface of the cylinder 06 so that the stopper 80 of the guide rod 78 abuts on the cushion.

Further, a coil 84 supported by a fixing bracket 64 via a bobbin 82 or the like is inserted and arranged in the annular groove 98 of the mass metal fitting 66.
Are disposed axially displaceable between radially opposed surfaces of the inner peripheral side wall surface of the inner peripheral wall surface and the outer peripheral side wall surface of the annular groove 98 formed by the permanent magnet 100. A drive current is supplied to the coil 84 from an external control device (not shown) through a power supply lead wire (not shown). When the drive current is supplied to the coil 84,
An electromagnetic force is generated between the coil 84 and the mass metal fitting 66, so that a relative displacement force in the approach / separation direction on the central axis is exerted on the fixing metal fitting 64 and the mass metal fitting 66. I have. In particular, by making the direction of the current flowing through the coil 84 opposite, the relative displacement force exerted between the fixing bracket 64 and the mass fitting 66 can be reversed, and the alternating current is supplied to the coil 84. The energization causes a relative excitation force to be applied to the fixing bracket 64 and the mass fitting 66.

FIG. 3 shows a negative pressure type actuator 111.
And a mass metal member 114 as a mass member is elastically connected to the fixing metal member 112 by a rubber elastic body 116, and is applied from a negative pressure applied from a negative pressure source 118 and from the atmosphere. The mass metal fitting 114 can be pneumatically vibrated with respect to the fixed metal fitting 112 by the atmospheric pressure. Then, by vibrating the vibration system including the mass metal fitting 114 and the rubber elastic body 116 with air pressure, the mass metal fitting 114 exerts an active vibration damping effect on the mount rubber elastic body 18 via the intermediate plate 56. You are getting it. In particular, it is possible to obtain a more effective vibration damping effect by utilizing the resonance action of the vibration system including the mass metal fitting 114 and the rubber elastic body 116.

More specifically, the fixing bracket 112 includes a first mounting plate 113 and a second mounting plate
17 mutually fixed. Further, the first mounting plate body 113 has a disk shape, and at the center thereof, a housing recess 121 for housing the support bolt 122 is provided, and around the housing recess 121, the mounting bolt 117 is provided. Is provided. Furthermore, the second mounting plate 115 has a cup shape that opens upward in the axial direction.
And a hard material such as metal. The support bolt 122 protrudes downward in the axial direction, and the fixing bracket 112 is fixedly attached to the bottom bracket 36 by the support bolt 122.

On the other hand, the mass metal fitting 114 is formed of a material having a high specific gravity such as an iron-based metal, has a solid block shape, and is opposed to the fixing metal 112 so as to be spaced upward in the axial direction. .

On one side of the mass metal fitting 114 in the axial direction, a ring-shaped connecting metal fitting 124 is arranged to be spaced apart and opposed on the same central axis, and the mass metal fitting 114 and the connecting metal fitting 124 are formed in an annular shape. It is elastically connected by a rubber elastic body 116. The rubber elastic body 116 has a tapered cylindrical shape whose diameter gradually decreases upward in the axial direction, and a small-diameter side end face of the rubber elastic body 116 projects from a central portion of an axial lower end face of the mass metal fitting 114. Trapezoidal connection 126
Is vulcanized and adhered to the outer peripheral surface. Also, the mass metal fitting 114
An inner lower corner portion of the connection fitting 124 opposed to the outer peripheral surface of the connecting portion 126 is chamfered in a round shape, and the large diameter end surface of the rubber elastic body 116 is added to the round surface 128. Sulfur adhesive. In other words, the outer peripheral surface of the connecting portion 126 of the mass metal fitting 114 and the round surface 128 of the connecting metal member 124 are spaced apart from each other and opposed to each other.
The rubber elastic body 116 is interposed between the opposing surfaces of the
14 and the connection fitting 124 are integrally vulcanized and bonded.

Then, the connecting fitting 124 is attached to the fixing fitting 11.
2 is fixed by bolts or the like, so that the mass fitting 114 is fixed to the fixing fitting 11 via a rubber elastic body 116.
2 are elastically supported. In particular, in the present embodiment,
The rubber elastic body 116 is disposed on the same central axis as the mass metal fitting 114, and the center of gravity of the mass metal fitting 114 is located on the elastic main axis of the rubber elastic body 116. Thereby, based on the elastic deformation of the rubber elastic body 116, the mass metal fitting 114 can be stably displaced in the central axis direction with respect to the fixing metal 112. In the present embodiment, the rubber elastic body 116 and the mass metal fitting 114
Is desirably mounted in a state in which the central axis extends substantially in the vertical direction which is also the input direction of the vibration to be damped, whereby the displacement of the mass metal fitting 114 can be further stabilized.

Further, the mass metal fitting 1 is
14, the peripheral wall portion is provided between the facing surfaces of the fixing fitting 112 and the mass fitting 114 by the rubber elastic body 11.
6, a working air chamber 130 is formed which is sealed from the external space. Further, the fixing fitting 112 is provided with an air through-hole 132 extending in the axial direction at a central portion in the axial direction of the second mounting plate 115, and the air through-hole 13 is provided.
One end of the opening 2 communicates with the working air chamber 130, while the other end of the air through hole 132 is opened at a port 134 protruding from the outer peripheral surface of the fixture 112. An air supply / discharge conduit 136 is connected to the port 134 so that the air pressure is applied to the working air chamber 130 through the air supply / discharge conduit 136 so that the mass metal fitting 114 is vibrated. Has become.

That is, the air supply / discharge conduit 136 is
For the port 134 of the negative pressure type actuator 111,
A tube that connects the output port 138 of the negative pressure source 118 to the atmosphere, and is formed of a material having a rigidity enough to withstand the applied negative pressure, for example, metal, rubber, synthetic resin, or the like. An electromagnetic switching valve 140 is provided at an intermediate portion of the air supply / discharge pipe 136. The electromagnetic switching valve 140 is a three-way switching valve having three ports, and includes, for example, a spool-type or poppet-type main body and a solenoid, and performs port switching control at a speed of several tens of times per minute. What can be used is suitably adopted. In the electromagnetic switching valve 140, the first port 142 is connected to the negative pressure type actuator 111, the second port 144 is connected to the negative pressure source 118, and the third port 146 is connected to the atmosphere. They are communicating. In the present embodiment, the third port 146 of the electromagnetic switching valve 140 is connected to the third port 146.
A pipe portion that opens the valve 6 to the atmosphere is an air communication pipe 148 as a vibration air communication path. Further, as the negative pressure source 118, a negative pressure generated in an intake system of an internal combustion engine, which is appropriately configured using an appropriate accumulator (accumulator) or the like is advantageously employed.

Thus, the electromagnetic switching valve 140 is switched at an appropriate cycle, and the working air chamber 130 of the negative pressure type actuator 111 is alternately connected to the negative pressure source 118 and the atmosphere. , Working air chamber 13
0, the negative pressure and the atmospheric pressure are alternately applied, and the electromagnetic switching valve 14
When a pressure fluctuation is generated in a cycle corresponding to the switching cycle of 0, an exciting force is applied to the mass metal fitting 114 accordingly. Also, as is apparent from this, in the present embodiment, the negative pressure source 118
The negative pressure acting area to which the negative pressure of
6 and the working air chamber 130.

The negative pressure type actuator 111 having the above-mentioned structure is operated by a control signal (not shown) corresponding to an external vibration to be damped. The control signal corresponding to the vibration to be damped is a signal corresponding to the frequency or phase of the vibration to be damped, such as an ignition signal of an internal combustion engine, a sensor of the vibration to be damped, or the like. Can be suitably adopted, whereby air pressure fluctuations of a frequency corresponding to the vibration to be damped are generated in the working air chamber 130 of the negative pressure type actuator 111, and the corresponding exciting force is applied to the mass. The vibrating force applied to the metal fitting 114 and corresponding to the vibration to be damped is applied to the mount rubber elastic body 18 via the intermediate plate 56.

The electromagnetic and negative pressure type actuators 62 and 111 shown in FIGS. 2 and 3 irrespective of which one is adopted, the mass metal fittings 66 and 114 as described above.
Is fixed to the intermediate plate 56 of the engine mount 12 by press-fitting, and the fixing brackets 64 and 112 are fixed to the second mounting bracket 16 by bolts. Then, by inputting a drive current or an electric signal synchronized with an engine speed or an ignition signal or the like from a control device (not shown) to the electromagnetic actuator 62 or the negative pressure actuator 111, the electromagnetic actuator 62 or the negative pressure actuator 111 By applying an exciting force corresponding to the engine rotation generated by the engine 111 to the mount rubber elastic body 18 via the intermediate plate 56, the power unit 2
2 can exert a destructive or positive reduction effect on vibrations caused by engine rotation transmitted to the body 26 via the engine mount 12.

In the engine mount 12 having the above-described structure, one vibration system having the mass metal fitting 66 and the intermediate plate 56 as masses and the mount rubber elastic body 18 as a spring is configured. As a result, the exciting force generated by the exciting means is efficiently exerted on the anti-vibration support system 10 by utilizing the resonance action of the oscillation system. Therefore, for example, by tuning the natural frequency of such a vibration system to the idling frequency range, even if the drive current such as the drive current in the electromagnetic actuator 62 or the drive pressure such as the negative pressure in the negative pressure actuator 111 is small, the resonance effect is utilized. As a result, a large excitation force is exerted on the vibration isolation support system 10, and an effective vibration damping effect can be obtained.

In addition, in the engine mount 12, since the spring in the vibration system having the mass metal fitting 66 and the intermediate plate 56 as masses is formed by using the mount rubber elastic body 18, the vibration system generates the spring. The applied vibration force is directly exerted on the mount rubber elastic body 18 constituting the transmission path of the vibration from the power unit 22 to the body 26, and therefore, is not related to the vibration from the power unit 22. As a result, the effective active vibration damping effect can be stably obtained with respect to the vibration caused by the rotation of the engine transmitted from the power unit 22.

Further, the engine mount 12 of the present embodiment
In the above, an internal space 54 is formed, which is defined by the first and second mounting members 14 and 16 and the mount rubber elastic body 18 and is substantially partitioned from the external space. Since the actuator 20 is housed and arranged, there is also an effect that the actuator 20 is advantageously held from external water and dust without providing a special sealing mechanism or the like to the actuator.

Next, FIG. 4 shows an engine mount 152 according to a second embodiment of the present invention, which can be suitably used in the anti-vibration support system 10 in an automobile as described above. In each of the following embodiments, members and parts having the same structure as the engine mount in the first embodiment are denoted by the same reference numerals as those in the first embodiment. Therefore, detailed description thereof will be omitted.

That is, the biggest difference between the engine mount 152 of the present embodiment and the engine mount 12 of the first embodiment is that the electromagnetic actuator 62 or the negative pressure actuator 111 is fixed to the intermediate plate 56. is there.

More specifically, the mass metal fitting 66 is formed with an outer diameter dimension smaller than the inner diameter dimension of the intermediate plate 56 by a predetermined dimension, and on the outer peripheral surface of the mass metal fitting 66,
A supporting rubber elastic body 154 extending continuously or discontinuously in the axial direction intermediate portion in the circumferential direction is vulcanized and bonded, and through this supporting rubber elastic body 154, the mass metal fitting 66 is attached to the intermediate plate 56 with respect to the intermediate plate 56. , Elastically connected. In addition, on the outer peripheral surface of the supporting rubber elastic body 154, a cylindrical metal fitting 1 is formed.
The outer peripheral surface of the supporting rubber elastic body 154 is fixed to the intermediate plate 56 by press-fitting and fixing the cylindrical metal fitting 155 to the lower end portion of the intermediate plate 56 which is vulcanized and adhered to the mount rubber elastic body 18. It is fixed. In this embodiment, the height of the supporting rubber elastic body 154 is
The length is not substantially embedded in the mount rubber elastic body 18 inside the engine mount 152.

In the engine mount 152 of the present embodiment, a vibration system having two degrees of freedom is constituted by the mass metal fitting 66, the intermediate plate 56, the mount rubber elastic body 18 and the support rubber elastic body 154. In such a vibration system, two natural frequencies are developed, and therefore, by appropriately tuning each of these natural frequencies according to the vibration frequency to be damped, based on the respective resonance action, It is possible to effectively obtain an active vibration damping effect with respect to a plurality of vibrations in a wide frequency range. Specifically, for example, 15 to 4
By tuning the natural frequencies to an idling vibration region around 5 Hz and a muffled sound region around 70 to 150 Hz, for both idling vibration and muffled sound, based on the resonance action of the vibration system, An efficient damping effect can be obtained.

In particular, in this embodiment, since the support rubber elastic body 154 independent of the support spring system of the power unit in the engine mount 152 is provided, the support rubber elastic body 154 is not restricted by the support characteristics of the power unit. There is an advantage that the vibration damper characteristics can be tuned by adjusting.

In the engine mounts of the first and second embodiments, tuning of the vibration damper characteristics while avoiding the influence on the support characteristics of the power unit as much as possible is performed, for example, as shown in FIG. As described above, it is also effective to process the upper end portion of the intermediate plate 56.

That is, in the engine mount 156 according to the third embodiment of the present invention shown in FIG.
The upper end portion of the intermediate plate 56 embedded and fixed in the mount rubber elastic body 18 is a tapered cylindrical portion 158 having a tapered shape whose diameter gradually increases toward the open end portion over a predetermined length. Note that the upper end of the tapered cylindrical portion 158 does not penetrate the mount rubber elastic body 18 and the mount rubber elastic body 1
8 and the rubber elastic body 1
When forming 8, the portion embedded in the mount rubber elastic body 18 (the tapered tubular portion 158 in the present embodiment) as in the first and second embodiments,
Even if the communication hole (58) is not provided, the mount rubber elastic body 1
The inner peripheral part and the outer peripheral part of 8 are mutually connected.

In the engine mount 156 having such a structure, since the intermediate plate 56 is provided with the tapered cylindrical portion 158, when the intermediate plate 56 is displaced in the axial direction, the mount rubber elastic body 18 is formed. The compressive deformation exerted can be increased, and the tapered cylindrical portion 15
By changing the taper angle of 8, it is possible to adjust the ratio of the shear stress to the compressive stress generated in the mount rubber elastic body 18 with the axial displacement of the intermediate plate 56.

Therefore, in the engine mount 156, by adjusting the taper angle of the tapered cylindrical portion 158, the support rubber elastic body can be adjusted without changing the spring constant of the mount rubber elastic body 18 in the engine mount 156. By adjusting the spring constant of 154, the resonance frequency of a vibration system including the mass metal fitting 66 and the supporting rubber elastic body 154 can be tuned.

FIG. 6 shows an engine mount 160 according to a fourth embodiment of the present invention. The biggest difference between the engine mount 160 of the present embodiment and the engine mount 12 of the first embodiment is that the mass metal fitting 66 in the electromagnetic actuator 62 or the negative pressure actuator 111 is elastically supported on the mount rubber elastic body 18. In the structure.

More specifically, the mount rubber elastic body 18 according to the present embodiment has a large diameter
Cylindrical covering rubber portion 5 covering substantially the entire inner peripheral surface of
2, the inner peripheral surface of the cylindrical fitting 34 extends over substantially the entire surface, and substantially extends over the entire upper surface of the flange 38 formed integrally with the peripheral edge of the opening of the bottom fitting 36. The bottom wall 36 has a thick cylindrical portion 162 which has an inner diameter smaller than the inner diameter of the cylindrical wall of the bottom fitting 36 and is projected radially inward. Further, at the lower end of the inner peripheral surface of the cylindrical portion 162, a ring-shaped connecting metal (intermediate plate) 56 having a height approximately half the height of the cylindrical portion 162 is vulcanized while being embedded. It is glued and fixed. In the present embodiment, the lower end of the intermediate plate 56 is
The height is substantially the same as the upper surface of the flange portion 38 of the bottom fitting 36.

In the engine mount 160 having such a structure, the intermediate plate 56 is elastically supported near the large-diameter end of the mount rubber elastic body 18 so that the spring characteristics of the engine mount are not changed. Since the spring constant of the vibration system including the mass metal fitting 66 can be set large, the degree of freedom in tuning can be advantageously secured. In particular, in the present embodiment, the large-diameter end surface of the mount rubber elastic body 18 is connected to the flange portion 38 of the bottom fitting 36.
With this, the support spring constant can be set higher.

Although the embodiments of the present invention have been described in detail above, these are merely examples, and the present invention
The specific descriptions in these embodiments are not to be construed as limiting in any way.

For example, the supporting portion of the mass rubber in the mount rubber elastic body is not limited to the radially intermediate portion or the large-diameter end portion of the mount rubber elastic body as illustrated.
It is set arbitrarily for any part of the mount rubber elastic body. As long as such a structure is adopted, the effect of the present invention as described above is effectively exhibited. In particular, as shown in FIG. 7 as a comparative example, the mount rubber elastic body and the mount rubber elastic body are separately provided. Support rubber elastic body 170
It is apparent that the effect of the present invention is more effectively exhibited in terms of simplification of the mount structure and the like than in the case where the mass member is elastically supported by the above.

The intermediate plate 56 does not have to be continuous in the circumferential direction as in the above-described embodiment. For example, only the upper end may be divided in the circumferential direction. The intermediate plate 56 does not need to have a cylindrical shape, and may have a polygonal tube shape or the like.
If the cross section of the mount rubber elastic body is not circular, the shapes of the intermediate plate and the actuator can be appropriately changed accordingly.

Further, the supporting rubber elastic body may not be single, but may be double or triple. By configuring a third or higher order vibration system as double, triple, or the like, more resonance frequencies can be tuned.

Further, the structure and the shape of the supporting rubber elastic body are not limited at all. For example, the supporting rubber elastic body employed in the above-described embodiment may have a circumferentially divided structure. is there.

Further, in the above-described embodiment, the mass member and the like are accommodated in the accommodation space defined inside the engine mount. However, the mass member and the like may be arranged in the external space. good. Specifically, for example, in the above embodiment, the intermediate plate 56 is mounted on the mount rubber elastic body 18.
It is also possible to arrange an annular mass member between the opposing surfaces of the mount rubber elastic body 18 and the first mounting member 14 so as to protrude toward the outer peripheral side of. In the case where such an arrangement structure of the mass member is adopted, a conventionally known fluid-filled mount in which an incompressible fluid is filled using a housing space defined inside the engine mount. It is also possible to configure a mechanism.

Further, in the above-described embodiment, a specific example in which the present invention is applied to an engine mount having a structure in which the first mounting member and the second mounting member are arranged to face each other in one direction has been described. For example, an outer cylinder member as a second attachment member is spaced apart from the shaft member as the first attachment member in the system direction, and the shaft member and the outer cylinder member are mounted in a thick cylindrical shape. The present invention can be applied to a cylindrical engine mount or the like suitably used in an FF-type automobile and the like elastically connected by a rubber elastic body, and an active vibration damper can be formed.

In addition, it goes without saying that the present invention is not limited to the above-described engine support mechanism for an automobile, but can be applied to a vibration isolation support mechanism for various engines other than an automobile.

In addition, although not enumerated one by one, the present invention
Based on the knowledge of those skilled in the art, various changes, modifications, improvements and the like can be performed in embodiments, and unless such embodiments depart from the spirit of the present invention.
Both are included in the scope of the present invention,
Needless to say.

[0066]

As is apparent from the above description, in the active vibration damper having the structure according to the present invention, the mass member vibrated by the vibrating means is mounted on the mount provided on the vibration transmission path. Since the vibration system is constituted by being elastically supported by the rubber elastic body, it is possible to efficiently apply a vibration force to the vibration isolating support system by utilizing the resonance action of the vibration system. It is.

[Brief description of the drawings]

FIG. 1 is a schematic explanatory view showing a main part of an automotive anti-vibration support system using an engine mount according to a first embodiment of the present invention.

FIG. 2 is an explanatory longitudinal sectional view showing a specific example of an electromagnetic actuator that can be employed in the engine mount shown in FIG. 1;

FIG. 3 is an explanatory longitudinal sectional view showing a specific example of a negative pressure type actuator that can be employed in the engine mount shown in FIG. 1;

FIG. 4 is an explanatory longitudinal sectional view showing an engine mount according to a second embodiment of the present invention.

FIG. 5 is an explanatory longitudinal sectional view showing an engine mount as a third embodiment of the present invention.

FIG. 6 is an explanatory longitudinal sectional view showing an engine mount according to a fourth embodiment of the present invention.

FIG. 7 is an explanatory longitudinal sectional view showing an engine mount as a comparative example.

[Explanation of symbols]

 12, 152, 156, 160 Engine mount 14 First mounting bracket 16 Second mounting bracket 18 Mount rubber elastic body 20 Actuator 22 Power unit 26 Body 34 Cylindrical portion 56 Intermediate plate 64, 112 Fixing bracket 66, 114 Mass fitting 154 Support rubber elastic

Claims (5)

[Claims] 1. A vibration means for mounting a power unit on an anti-vibration support system in which a power unit is elastically anti-vibration supported by using an engine mount with respect to a support member to actively suppress vibration in the support member. In the active vibration damper provided, a mass member is disposed so as to be relatively displaceable in a vibration direction to be damped with respect to a fixed member attached to the support member, and the support member is moved from the power unit in the engine mount. While the mass member is elastically supported by the mount rubber elastic body disposed on the vibration transmission path to the vibration member, the vibrating force by the vibrating means is exerted between the fixed member and the mass member. An active vibration damper characterized by: 2. The mass member is elastically supported in series or in parallel by the mount rubber elastic body and at least one supporting rubber elastic body independent of the mount rubber elastic body, so that a multi-degree of freedom is provided. 2. The vibration system according to claim 1,
4. The active vibration damper according to claim 1. 3. In the engine mount, the mass member and the vibration means are disposed between a first mounting member mounted on the power unit side and a second mounting member mounted on the support member side. 3. The active vibration damper according to claim 1, wherein the mass member and the vibration means are incorporated in the engine mount. 4. In the engine mount, a cylindrical portion that opens toward the first mounting member is provided on the second mounting member, and the mount rubber elastic body has a substantially truncated cone shape, and has a small diameter. The first mounting member is fixed to the side end surface, and the opening of the cylindrical portion of the second mounting member is fixed to the outer peripheral surface of the large-diameter end portion, while the radially intermediate portion of the mount rubber elastic body is fixed. The active vibration damper according to any one of claims 1 to 3, wherein a tubular connecting fitting is embedded and fixed to the portion, and the mass member is connected and supported by the connecting fitting. 5. The active vibration damper according to claim 4, wherein a taper angle is given to a portion of the connection fitting embedded and fixed in the mount rubber elastic body.