JPH06193671A - Control type vibration isolator - Google Patents

Abstract

PURPOSE:To provide a control type vibration isolator that is excellent in stability and durability and able to absorb such a vibration as extending over a wide range of frequencies with certainty. CONSTITUTION:A vibrating plate 24 facing to a pressure receiving liquid chamber 45 is elastically supported on a sticking part 30 via a coil spring 51 made up of a piano wire or the like. This vibrating plate 24 is liquid-tightly connected to a vibrating plate supporting fitting 20 via a ringlike fibered rubber membrane 22. Since this vibrating plate 24 is not merely elastically supported by a rubber lump, but supported by the coil spring 51 which prevents any variation in a spring constant and fatigue, setting from occurring even under the condition of high temperature, a vibro-isolating characteristic is stabilized for a long period of time. In addition, the coil spring 51 is able to take a stroke large enough as compared with the rubber lump and a plate spring or the like, and a spring constant is also extensively selected, so that it is able to cope with the larger amplitude of vibration than that in the past.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a control type vibration damping device,
For example, the present invention relates to a liquid-filled type control type vibration damping device for preventing transmission of engine vibration to a vehicle body.

[0002]

2. Description of the Related Art An engine of an automobile is supported on a vehicle body by a vibration isolator, which prevents transmission of engine vibration to the vehicle body.

As such a vibration isolator, a liquid-filled control type vibration isolator has been proposed (Japanese Patent Application No. 4-1884).
No. 14, etc.).

As shown in FIG. 4, this control type vibration damping device 1
10 has a pressure receiving liquid chamber 112 and a sub liquid chamber 113,
The pressure receiving liquid chamber 112 and the sub liquid chamber 113 are connected by a limiting passage 122. A diaphragm 114 elastically supported by a rubber block 120 faces the pressure receiving liquid chamber 112.
A thin diaphragm 115 faces 13.

In this control type vibration control device 110, when a low frequency vibration such as a shake vibration is input, the restricted passage 1
The liquid flows back and forth through 22, and a large damping force is generated to absorb the vibration. It should be noted that the rubber block 120 is the diaphragm 11
The rigidity against hydraulic pressure is set higher than that of No. 5, so that it is hardly deformed at low frequency vibration.

The vibrating plate 114 is driven by the electromagnetic actuator 116, and the control device 118 adjusts to the high frequency vibration when the high frequency vibration is input and the restriction passage 122 is clogged. The electromagnetic actuator 116 is driven and controlled in such a manner that the vibration plate 114 is vibrated in a direction in which a pressure increase in the pressure receiving liquid chamber 112 is avoided, that is, so that the spring constant of the control type vibration damping device 110 does not increase. .

[0007]

By the way, in the conventional vibration damping device such as the control type vibration damping device 110, since the vibrating plate 114 is supported by the elastic body such as the rubber block 120, the vibration damping device near the engine is provided. Rubber block 1 in a high temperature environment with heat
When the force from the electromagnetic actuator 116 constantly acts on the rubber 20, the rubber lump 120 is set. If the rubber lump 120 becomes settled and the spring constant of the rubber lump 120 becomes too low, the diaphragm 114 moves when low-frequency vibration is input, the amount of liquid flowing through the restriction passage 122 decreases, and the damping force increases. There is a problem that decreases. In addition, the distance between the electromagnetic actuator 116 and the vibration plate 114 is changed to change the vibration plate 114.
It causes troubles such as the movement amount of.

Further, in the method of supporting the vibration plate 114 with the rubber block 120, the stroke of the vibration plate 114 cannot be made large, and it may not be possible to cope with vibration having a large amplitude. Furthermore, the spring constant of the rubber block 120 is set within a very narrow range.

Although it is conceivable to form the entire diaphragm with a leaf spring or the like, a large stroke cannot be taken with the leaf spring, and there is a concern that cracks may occur due to fatigue. Furthermore, a sealing structure such as an O-ring is required to maintain the sealing property against liquid.

Further, the applicant of the present application has proposed a method of supporting the diaphragm with a rubber block and a coil spring (Japanese Patent Application No. 4-116377), but the rubber block cannot take a large stroke as described above. Therefore, the stroke of the diaphragm is limited even when used together with the coil spring.

In view of the above facts, it is an object of the present invention to provide a control type vibration damping device having high stability and high durability which can surely absorb vibrations in a wide range of frequencies.

[0012]

According to the present invention, there is provided a first member connected to one of a vibration generating section and a vibration receiving section, and a second member connected to the other of the vibration generating section and the vibration receiving section. , An elastic body provided between the first member and the second member, a pressure receiving liquid chamber that expands and contracts when vibration occurs by using the elastic body as a part of a partition wall, and a limiting passage to the pressure receiving liquid chamber. Of the auxiliary liquid chamber connected to the pressure receiving liquid chamber, the vibrating member forming another part of the partition wall of the pressure receiving liquid chamber, the electromagnetic actuator that generates a vibrating force for vibrating the vibrating member, and the vibration of the vibration receiving portion. A vibration control sensor for detecting a vibration, and a control type vibration control device including a control means for driving and controlling the electromagnetic actuator based on a signal from the vibration detection sensor, wherein the vibration member is the first member or the Coil spring elastically supported by the second member And grayed, is characterized in that said comprising a fiber-containing rubber film connecting the vibration member and the first member or the second member liquid-tightly, a.

[0013]

The control type vibration damping device of the present invention is used by connecting one of the first member and the second member to the vibration generating portion and the other to the vibration receiving portion.

When vibration is input to this control type vibration damping device,
The elastic body deforms and the pressure receiving liquid chamber expands and contracts. At the time of low frequency vibration, the liquid in the pressure receiving liquid chamber moves back and forth between the sub liquid chamber through the restriction passage to generate a damping force, and the vibration is absorbed.

On the other hand, when a high-frequency vibration that causes clogging of the restriction passage is input, the control device controls the vibration amplitude of the vibration receiving portion detected by the vibration detecting sensor to be small, that is, the pressure receiving pressure. The vibrating member is vibrated by the electromagnetic actuator so that the pressure inside the liquid chamber does not rise.

In this control type vibration damping device, the vibrating member is not elastically supported by the rubber lump, and the coil spring does not cause a change in spring constant, fatigue, or fatigue even under high temperature conditions. Since it is elastically supported by, the anti-vibration property is stable for a long time. In addition, the rubber film with fibers keeps the sealing property and suppresses the swelling of the rubber by the fibers against the increase in the liquid pressure in the pressure receiving liquid chamber at the time of low frequency vibration input, so that the pressure escapes You can prevent the decrease.

The vibrating member of the present invention is liquid-tightly connected to the first member or the second member with a fiber-containing rubber film that does not limit the stroke of the vibrating member like a rubber block. A large stroke corresponding to the coil spring can be taken.

Further, the coil spring can have a larger stroke than rubber lumps, leaf springs, etc., and the spring constant can be selected in a wide range, so that it is possible to cope with vibration with a larger amplitude than before, and the electromagnetic actuator. You can freely adapt to your ability.

Further, since the vibrating member is supported by the coil spring, even if the rubber film containing fibers is set, the movement of the vibrating member is not affected. The coil spring can also apply an urging force in the returning direction of the vibrating member.

[0020]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of the present invention will be described with reference to FIGS.

As shown in FIG. 2, the antivibration device main body 10
Is provided with a cup-shaped lower mount 12 as a first member. The bottom plate 12B of the lower mount 12 is disk-shaped, and mounting bolts 14 are erected on the lower surface. Around the bottom plate 12B is a cylindrical standing wall portion 12A,
A flange portion 12C extending outward in the radial direction is formed on the upper end portion.

In this embodiment, the lower mount 12 is mounted on the vehicle body 16 of an automobile and is fixed by screwing a nut 18 onto the mounting bolt 14.

An annular diaphragm support metal fitting 20 is disposed above the lower mount 12. The outer peripheral edge portion of the fiber-containing rubber film 22 which is thin and annular is liquid-tightly vulcanized and adhered to the inner peripheral edge portion of the diaphragm support metal fitting 20. The outer peripheral edge portion of the diaphragm 24 serving as a disk-shaped vibrating member is liquid-tightly vulcanized and adhered. The fiber-containing rubber film 22 is formed by embedding a canvas cloth made of an organic fiber such as nylon or polyester inside a thin rubber film. The rubber film 22 containing fibers
May be one that does not allow liquid to permeate, and may be a woven fabric, a non-woven fabric, or the like coated with rubber.

The diaphragm 24 is magnetized so that poles are formed in the axial direction (thickness direction).

An outer cylinder 26 is coaxially arranged outside the diaphragm support fitting 20. The outer cylinder 26 has a diameter that increases toward the upper side, and an annular elastic body 28 is vulcanized and adhered to the inner circumference. A part of the elastic body 28 is thinly extended to the vicinity of the lower end of the inner circumference of the outer cylinder 26, and the outer circumference of the cylindrical portion 20B of the diaphragm support fitting 20 is in close contact.

A flange portion 26A is provided at the lower end portion of the outer cylinder 26, and the outer periphery of the flange portion 26A is narrowed inward so that the diaphragm support metal fitting 20 is provided between the flange portion 26A and the flange portion 12C of the lower mount 12. It is sandwiched.

A fixing portion 30 is provided at the center of the elastic body 28. The fixing portion 30 is cup-shaped and has a flange portion 30B formed at the upper end thereof. The elastic body 28 extends from the outer peripheral surface of the cylindrical portion 30A to a part of the flange portion 30B.
Is vulcanized and bonded.

An air chamber forming portion 32 as a second member is arranged above the fixing portion 30.

The air chamber forming portion 32 is formed in a substantially hat shape, and the lower end flange portion 32A is caulked and fixed to the outer periphery of the flange portion 30B of the fixing portion 30.

A diaphragm 34 is disposed between the fixing portion 30 and the air chamber forming portion 32, and a peripheral portion of the diaphragm 34 has a flange portion 30B of the fixing portion 30 and a flange portion of the air chamber forming portion 32. It is sandwiched between 32A and 32A.

An air chamber 36 is provided between the air chamber forming portion 32 and the diaphragm 34, and the inside is communicated with the outside air as necessary. Further, a mounting bolt 38 for mounting on the engine side is provided upright on the outer shaft core of the air chamber forming portion 32.

A bracket 40 mounted on the engine 52 is mounted on the air chamber forming portion 32, and a nut 42 is screwed into a mounting bolt 38 penetrating the bracket 40.

A sub-liquid chamber 44 is formed between the fixed portion 30 and the diaphragm 34, and a pressure receiving liquid chamber 45 is formed between the fixed portion 30 and the diaphragm 24. Bottom part 30 of fixing part 30
A pipe 46 is fixed to the center of C, and the pipe 46 constitutes a restriction passage that connects the pressure receiving liquid chamber 45 and the sub liquid chamber 44 to each other.

The pressure receiving liquid chamber 45 and the sub liquid chamber 44 are filled with a liquid such as ethylene glycol.

An electromagnet 50 as an electromagnetic actuator is attached to the lower mount 12. The electromagnet 50 is
The upper surface is separated from the lower surface of the diaphragm 24 by a predetermined dimension, and the portion facing the diaphragm 24 is a pole.

To the bottom portion 30C of the fixing portion 30, one end of a coil spring 51 formed of a metal wire material such as a piano wire arranged coaxially with the outer cylinder 26 is fixed. The other end of the coil spring 51 is fixed to the central portion of the vibration plate 24.
It is elastically supported by the fixing portion 30 via. Here, when the engine 52 is mounted on the air chamber forming portion 32 and a load (1 G) of the engine is applied, it is preferable that the dimension between the bottom portion 30C and the diaphragm 24 be the free length of the coil spring 51. The coil spring 51 preferably has a low spring constant.

As shown in FIG. 1, the engine 52 is provided with a pulse sensor 54 for detecting an explosion pulse of the engine. This pulse sensor 54 is a waveform shaper 5.
6. A correction sine wave generator 58 forming another part of the generating means via a frequency converter 57 forming a part of the generating means.
It is connected to the. The waveform shaper 56 shapes the explosion pulse into a predetermined rectangular pulse. In addition, the frequency converter 5
7 can convert the frequency of the pulse from the waveform shaper 56 into a predetermined frequency.

On the other hand, a vibration sensor 60 as a vibration detection sensor for detecting the amplitude of vibration of the vehicle body 16 is attached to the vehicle body 16 of the automobile. An acceleration sensor or the like can be used as the vibration sensor 60.

Next, details of the corrected sine wave generator 58 will be described. The corrected sine wave generator 58 includes a comparator 61, a reference oscillator 62, a reference pulse generator 64, and a modulator 68.

The reference oscillator 62 is a reference pulse generator 64.
And the modulator 68. This reference transmitter 62
Outputs a sine wave of a predetermined frequency.

The reference pulse generator 64 is the reference oscillator 62.
The reference pulse of the same cycle as the sine wave of is output.

The reference pulse generator 64 is connected to the comparator 61 which is connected to the waveform shaper 56 and the modulator 68. The comparator 61 compares the period of the waveform-shaped explosion pulse output from the waveform shaper 56 with the period of the reference pulse of the reference oscillator 62, and outputs a comparison signal to the modulator 68.

The modulator 68 modulates the cycle of the sine wave output from the reference oscillator 62 based on the comparison signal from the comparator 61, and outputs a modulated sine wave.

The modulator 68 is connected with a phase adjuster 70 which constitutes a part of the control means.
0 shifts the phase of the sine wave output from the modulator 68 by a predetermined amount.

An amplifier 72, which constitutes another part of the control means, is connected to the phase adjuster 70, and the amplifier 72 amplifies the amplitude of the sine wave output from the phase adjuster 70 to make the electromagnet 50. Output to coil.

A gain controller 74, which constitutes yet another part of the control means, is connected to the amplifier 72. The above-described vibration sensor 60 is connected to the gain controller 74, and the gain of the amplifier 72 is adjusted so that the vibration amplitude of the vehicle body becomes zero.

Next, the operation of this embodiment will be described. When a low-frequency large-amplitude vibration such as an engine shake is input to the vibration isolator body 10, the vibration is generated in the air chamber forming portion 32 and the fixing portion 30.
Is transmitted to the elastic body 28 via the
Elastically deforms and the pressure receiving liquid chamber 45 expands and contracts. Pressure receiving chamber 45
When the liquid is expanded or contracted, the liquid inside moves back and forth between the pressure receiving liquid chamber 45 and the sub liquid chamber 44 via the pipe 46, and the liquid flows in the pipe 4
Resonance within 6 produces a large damping force.
This absorbs low frequency vibrations. here,
Since the expansion of the fiber-containing rubber film 22 is limited even when tension is applied, the vibration plate 24 when the pressure receiving liquid chamber 45 is greatly expanded or contracted.
Can be restricted, and the amount of liquid flowing through the restriction passage at the time of low frequency vibration is not reduced. On the other hand, when a high-frequency small-amplitude vibration such as idle vibration or muffled sound is input and the expansion / contraction amount of the pressure receiving liquid chamber 45 is small, the fiber-containing rubber film 22 can allow the vibration of the vibrating member. .

On the other hand, when a high-frequency small-amplitude vibration such as an idle vibration or a muffled sound is input, the vibration plate 24 of the vibration isolator body 10 of the present embodiment prevents the hydraulic pressure of the pressure receiving liquid chamber 45 from rising. Therefore, even if the pipe 46 becomes clogged, the low dynamic spring constant can be maintained and the high frequency vibration can be effectively absorbed.

In the following, the diaphragm 24 is used when high-frequency vibration is input.
The details of the control for vibrating will be described.

When the engine 52 is a 4-cycle 4-cylinder engine and it is desired to absorb engine vibration of the same cycle as the explosion cycle, the vibration of the diaphragm 24 is controlled by focusing on the secondary component of engine rotation.

The engine explosion pulse detected by the pulse sensor 54 is input to the waveform shaper 56, shaped into a predetermined rectangular pulse, and output. The pulse output from the waveform shaper 56 is output to the corrected sine wave generator 58 via the frequency converter 57.

The engine 52 is a four-cycle four-cylinder engine, and the engine vibration of the same cycle as the explosion cycle vibrates twice for one rotation of the crankshaft, so the rotational order is the second order. When the engine 52 is a four-cycle four-cylinder engine, the frequency of the explosion pulse is twice for one rotation of the crankshaft, and therefore the frequency converter 57 does not frequency-convert the pulse output from the waveform shaper 56. To do so.

On the other hand, the reference oscillator 62 generates a sine wave having a predetermined frequency, and this sine wave is input to the reference pulse generator 64 and the modulator 68. The reference pulse generator 64 generates a reference pulse having the same period as the sine wave of the reference oscillator 62, and this reference pulse is input to the comparator 61. Comparator 61
Outputs a comparison signal by comparing the cycle of the engine explosion pulse with the cycle of the reference pulse, and this comparison signal is input to the modulator 68. The modulator 68 modulates the sine wave output from the reference oscillator 62 based on the comparison signal so as to have the same period as the explosion pulse of the engine, and the modulated sine wave is input to the phase adjuster 70.

The phase adjuster 70 adjusts the phase of the sine wave output from the modulator 68 so that the engine vibration and the electromagnetic force are synchronized with each other. In the present embodiment, the phase adjuster 70
Thereby advances the phase of the sine wave output from the modulator 68 by a predetermined amount. This is because the coil of the electromagnet 50 has an inductance and a resistance, and the phase of the electromagnetic force is delayed with respect to the input sine wave. This is to synchronize with the electromagnetic force.

On the other hand, the gain controller 74 is used for the vehicle body 1
The gain of the amplifier 72 is adjusted so that the amplitude of the vibration of 6 is 0 (to minimize the vibration of the vehicle body).

As a result, the vibration plate 24 vibrates so as to suppress the pressure increase in the pressure receiving liquid chamber 45 in response to the vibration generated by the explosion of the engine, and the increase in the dynamic spring constant of the vibration isolator body 10 can be suppressed. . Therefore, transmission of high-frequency engine vibration to the vehicle body side can be effectively prevented. Further, with the above-described configuration, the increase in the pressure of the pressure receiving liquid chamber 45 can be suppressed by following the change in the engine speed, that is, the increase and decrease in the frequency of the engine vibration. Vibrations can be reliably absorbed.

Further, unlike the rubber or the like, the diaphragm 24 is elastically supported by the coil spring 51, which hardly changes with time, so that the distance to the electromagnet 50 does not change and the diaphragm 24 is constantly fixed. It is supported at a position and does not unnecessarily move at the time of inputting low-frequency vibrations, thus degrading the vibration isolation characteristics.

Further, the coil spring 51 can have a larger stroke than a rubber lump or a leaf spring, and the spring constant can be selected in a wide range. Therefore, the vibration isolator main body 10 of this embodiment has a larger amplitude than the conventional one. It is possible to cope with the vibration of.

The diaphragm 24 is a coil spring 51.
The coil spring 51 may be disposed in the lower mount 12 so that the diaphragm 24 is supported by the bottom plate 12B of the lower mount 12, as shown in FIG.

In the above embodiment, the engine 52 has four
In the cycle 4-cylinder engine, the example in which the vibration plate 24 is controlled so as to absorb the vibration generated twice per one rotation of the crankshaft, that is, the vibration having the second order of rotation is shown. However, in the present embodiment, the order of rotation is two. It is also possible to absorb vibrations of a predetermined order other than the following. For example, in the case of absorbing vibration of the first order of rotation (for example, vibration due to unbalance of rotating parts), the frequency converter 57 reduces the frequency of the pulse output from the waveform shaper 56 to ½. In the case of absorbing the vibration of the fourth order in the rotation order, the frequency converter 57
Then, the frequency of the pulse output from the waveform shaper 56 may be doubled. As a result, the order of engine vibration and the order of vibration of the diaphragm 24 can be matched.

In the above embodiment, the pulse sensor 54 is used to detect the explosion pulse of the engine. However, a microcomputer for calculating the ignition timing is used as the pulse sensor and the ignition timing is used as the explosion pulse. Alternatively, an angular position detection sensor that detects the rotation angle of the crankshaft or the rotation angle of the camshaft may be used as the pulse sensor.

[0062]

As described above, since the control type vibration damping device of the present invention has the above-mentioned constitution, it is excellent in the stability and durability of the characteristics and can surely absorb the vibration over a wide range of frequencies. Have the effect.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a vibration control device body according to an embodiment of the present invention.

FIG. 2 is a block diagram of a vibration isolation device according to an embodiment of the present invention.

FIG. 3 is a cross-sectional view of a vibration control device body according to another embodiment of the present invention.

FIG. 4 is a cross-sectional view of a conventional vibration damping device body.

[Explanation of symbols]

 10 Vibration proof device main body 12 Lower mount (first member) 22 Rubber film containing fibers 24 Vibration plate (vibration member) 28 Elastic body 32 Air chamber forming part (second member) 44 Sub liquid chamber 45 Pressure receiving liquid chamber 46 Pipe (restricted passage) 50 Electromagnetic actuator 51 Coil spring 60 Vibration sensor 70 Phase adjuster (control means) 72 Amplifier (control means) 74 Gain controller (control means)

Claims (1)

[Claims] 1. A first member connected to one of the vibration generating portion and the vibration receiving portion, a second member connected to the other of the vibration generating portion and the vibration receiving portion, the first member and the An elastic body provided between the second member, a pressure receiving liquid chamber that expands and contracts when vibration is generated by using the elastic body as a part of a partition wall, and a sub liquid chamber connected to the pressure receiving liquid chamber via a restriction passage. A vibration member that constitutes another part of the partition wall of the pressure receiving liquid chamber, an electromagnetic actuator that generates a vibrating force for vibrating the vibration member, and a vibration detection sensor that detects vibration of the vibration receiving portion, A control type vibration damping device comprising control means for driving and controlling the electromagnetic actuator based on a signal from the vibration detection sensor, wherein the vibrating member is elastically attached to the first member or the second member. A coil spring to support, and the vibrating section Control vibration insulator, characterized in that it and a fiber-containing rubber film which connects liquid-tightly with the first member or the second member and the.