JPH0633987A - Vibration control device - Google Patents

Abstract

PURPOSE:To take in vibration of a wide frequency range using the device stated in the title and used against engine vibration by causing vibration of a liquid-sealed vibration control device and a vibrating member in a pressure liquid room with the same frequency and the same waveform as vibration of a vibrating portion, the vibration control device damping vibration by means of movement of a liquid between the pressure liquid room and an auxiliary liquid room. CONSTITUTION:A liquid-sealed vibration control device is disposed between a vehicle body 16 and an engine mounting bracket 40. In the liquid-sealed vibration control device, an elastic body 28 is deformed by engine vibration input thereto via the engine mounting bracket 40 and then a pressure liquid room 45 is enlarged or contracted. As a result, a liquid is moved from the pressure liquid room 45 to an auxiliary liquid room 44 through a limiting passage 46. Then a damping force is generated and absorbs the engine vibration. Vibration of the vehicle body 16 is detected and then an electromagnetic actuator 50 is driven to cause vibration of a vibrating plate 24 in the pressurized liquid room 45 with the same waveform and the same frequency as the detected vibration so as to restrain pressure buildup within the pressure liquid room 45 and control a dynamic spring constant.

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,
In particular, it relates to a control type vibration damping device for preventing transmission of engine vibration to the 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.

A liquid-filled type vibration damping device has been proposed as such a vibration damping device. The liquid-filled type vibration damping device has a pressure receiving liquid chamber and a sub liquid chamber, and the pressure receiving liquid chamber and the sub liquid chamber are connected by a restriction passage. When vibration is input to the vibration isolator, the liquid resonates in the restriction passage to generate a damping force and the vibration is absorbed.

[0004]

By the way, the engine generates a rotational force by the explosion of the fuel in the cylinder. Due to the rotational force caused by this explosion, torque variation occurs in the crankshaft, and the engine is vibrated. The largest engine vibration is due to this torque fluctuation.

The ratio between the engine speed and the generated frequency, that is, how many vibrations occur per crankshaft rotation is called the rotational order, for example, the rotational speed is 3000 rpm.
At this time, if vibration of 100 Hz is generated, the rotation order is the second order (100 ÷ 3000 ÷ 60 = second order).

For example, in the case of a 4-cycle single-cylinder engine, the change in rotational force due to explosion is the crankshaft 2
One cycle is required for rotation. That is, when the engine is a 4-cycle 4-cylinder engine, vibration occurs twice for one rotation of the crankshaft (because there are four explosions for two rotations of the crankshaft), and therefore the order of rotation is 2. The following (By the way, when the engine is a 4-cycle 6-cylinder engine, the engine rotation tertiary component causes the largest vibration).

The number of revolutions of the engine is as wide as several hundred to several thousand, and the vibration force due to the pressure fluctuation of the explosion, that is, the frequency of engine vibration is also wide. However, the range of the resonance frequency in the restricted passage is narrow, and the vibration of the predetermined frequency can be effectively absorbed. However, when the vibration of the frequency exceeding the predetermined frequency is input, the dynamic spring constant increases and the vibration absorption capability decreases. . In order to solve the above drawbacks, a liquid-filled type vibration damping device having a plurality of restricted passages has been proposed, but the internal structure becomes complicated and the size becomes large. Therefore, the number of restricted passages provided in an actual vibration isolation device is limited to 2 to 3,
It was not possible to reliably absorb vibrations over a wide range of frequencies.

In view of the above facts, an object of the present invention is to provide a control type vibration damping device capable of reliably absorbing vibrations over a wide range of frequencies.

[0009]

In order to achieve the above object, a control type vibration damping device of the present invention comprises a first member connected to one of a vibration generating portion and a vibration receiving portion, a vibration generating portion and a vibration. A second member connected to the other of the receiving portions, an elastic body provided between the first member and the second member, and a pressure receiving force that expands and contracts when vibration occurs with the elastic body as a part of a partition wall. A liquid chamber, a sub-liquid chamber connected to the pressure receiving liquid chamber through a restriction passage, a vibrating member that constitutes another part of the partition wall of the pressure receiving liquid chamber and is oscillatably supported, and the vibrating member. An electromagnetic actuator that generates an exciting force for vibrating, a generation unit that generates a vibration waveform having the same frequency as the frequency of a predetermined order waveform of the vibration generation unit, and a vibration detection that detects the amplitude of the vibration of the vibration receiving unit. A sensor, a vibration waveform generated by the generating means, and the vibration The phase of the vibration waveform is adjusted so as to be synchronized with the vibration waveform of the material, and the amplitude of the vibration waveform generated by the generating means is adjusted so that the amplitude of the vibration of the vibration receiving portion becomes small and the actuator is driven. Control means,
It is characterized by having.

[0010]

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 engine which is the vibration generating portion and the other to the vibration receiving portion.

When engine vibration is input to the liquid-filled type vibration damping device, the elastic body is deformed and the pressure receiving liquid chamber is expanded or contracted. As a result, the liquid in the pressure receiving liquid chamber moves back and forth between the sub liquid chamber and the sub liquid chamber via the restriction passage to generate a damping force, and the engine vibration is absorbed.

On the other hand, the generating means generates a vibration waveform having the same frequency as the frequency of the waveform of a predetermined order of engine vibration. The control device adjusts the phase of the vibration waveform so that the vibration waveform generated by the generation means and the vibration waveform of the vibrating member are synchronized, and further, the vibration amplitude of the vibration receiving portion detected by the vibration detection sensor is small. The amplitude of the vibration waveform generated by the generating means is adjusted so that the actuator is driven.

Therefore, the control type vibration damping device of the present invention is
Even if the frequency of vibration rises and the restriction passage becomes clogged, the vibrating member vibrates and suppresses the increase in hydraulic pressure in the pressure receiving liquid chamber, so the dynamic spring constant does not increase, ensuring high frequency vibration. Can be absorbed into.

[0014]

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.

A diaphragm support metal fitting 20 is arranged above the lower mount 12. The diaphragm support fitting 20 is composed of an annular fixing portion 20A and a tubular portion 20B integrally extending upward on the inner circumference of the fixing portion 20A. An annular elastic support 22 is vulcanized and adhered to the inner peripheral surface of the tubular portion 20B, and a diaphragm 24 as a vibrating member is vulcanized and adhered to the inner peripheral surface of the elastic support 22. The diaphragm 24 is magnetized so that poles are formed in the axial 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 a 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. The fixed portion 20A is sandwiched.

A fixing portion 30 is arranged 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 flange portion 32A at the lower end is caulked and fixed at 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 edge 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 formed 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, to which an engine 52 is attached, 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 84 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.

As shown in FIG. 1, the engine 52 is provided with a pulse sensor 54 for detecting an engine explosion pulse. 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, the 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 period 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 to 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 and outputs 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 the vibration of the engine 52 is input to the vibration isolator main body 10, the vibration is transmitted to the elastic body 28 via the air chamber forming portion 32 and the fixing portion 30, whereby the elastic body 28 is elastically deformed and the pressure receiving liquid chamber 45 is expanded or contracted. To do. When the pressure receiving liquid chamber 45 expands or contracts, 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 resonates in the pipe 46, so that a large damping force is generated. This absorbs engine vibration.

Further, in the vibration isolator main body 10, the pressure receiving liquid chamber 4
Since the vibration of the vibrating plate 24 is controlled so that the hydraulic pressure of No. 5 does not rise, the dynamic spring constant does not increase even if vibration of a high frequency such that the liquid does not flow in the pipe 46 is input. It is possible to absorb high frequency vibrations.

The control for vibrating the diaphragm 24 will be described in detail below. Engine 52 has 4 cycles 4
When the engine is a cylinder engine and it is desired to absorb the engine vibration of the same cycle as the explosion cycle, the vibration of the diaphragm 24 is controlled by focusing on the engine rotation secondary component.

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. 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 accordance with 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 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.

In this embodiment, the engine 52 is a four-cycle four-cylinder engine, and the diaphragm 24 is controlled so as to absorb the vibration generated twice per one rotation of the crankshaft, that is, the vibration of the secondary order. Although an example is shown, in the present embodiment, vibration of a predetermined order other than the second order of rotation can be absorbed. For example, vibration of the first order of rotation (for example, muffled noise, vibration due to imbalance of rotating parts, etc.)
In the case of absorbing the
The frequency of the pulse output from 6 may be halved, and when absorbing the vibration of the fourth order in the rotation order, the frequency converter 57 doubles the frequency of the pulse output from the waveform shaper 56. You can do this. As a result, the order of engine vibration and the order of vibration of the diaphragm 24 can be matched.

In this embodiment, the pulse sensor 54 is used to detect the engine explosion pulse.
A microcomputer that calculates the ignition timing may be used as a pulse sensor, and the ignition timing may be used as an explosion pulse. Also, an angular position detection sensor that detects the rotation angle of the crankshaft and the rotation angle of the camshaft may be used as the pulse sensor. May be.

[0050]

As described above, according to the present invention, the vibrating member is vibrated with the vibration waveform having the same frequency as the frequency of the predetermined order waveform of the engine vibration and synchronized, and the hydraulic pressure of the pressure receiving liquid chamber rises. Therefore, even when a high frequency vibration is input, the dynamic spring constant is not increased, and vibrations over a wide range of frequencies can be reliably absorbed, which is an excellent effect.

[Brief description of drawings]

FIG. 1 is a block diagram of an embodiment of the present invention.

FIG. 2 is a cross-sectional view of the vibration control device body of FIG.

[Explanation of symbols]

 10 Vibration Isolator 12 Lower Mounting Base (First Member) 24 Vibration Plate (Vibration Member) 28 Elastic Body 32 Air Chamber Forming Part (Second Member) 44 Sub Liquid Chamber 45 Pressure Received Liquid Chamber 46 Pipe (Restricted Passage) 50 Electromagnetic actuator 58 Corrected sine wave generator (generation means) 57 Frequency converter (generation means) 60 Vibration sensor (vibration detection 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 vibrating member that constitutes another part of the partition wall of the pressure receiving liquid chamber and is supported so as to vibrate; an electromagnetic actuator that generates a vibrating force for vibrating the vibrating member; and a predetermined order of a vibration generating unit. The generation means for generating a vibration waveform having the same frequency as the frequency of the waveform, the vibration detection sensor for detecting the amplitude of the vibration of the vibration receiving portion, the vibration waveform generated by the generation means and the vibration waveform of the vibration member Adjusting the phase of the vibration waveform to synchronize And a control unit that drives the actuator by adjusting the amplitude of the vibration waveform generated by the generation unit so that the vibration amplitude of the vibration receiving unit becomes small. .