JP4244366B2 - Control method of active control mount - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a control method for an active control mount which is an anti-vibration support for an engine and which uses a vibration means to block vibration.
[0002]
[Prior art]
As a liquid seal engine mount, the liquid chamber is divided into a main liquid chamber and a sub liquid chamber by a partition wall member, and both the liquid chambers are connected by a resonance orifice such as a damping orifice or an idle orifice, and are prevented by liquid column resonance of the resonance orifice. What is shaken is well known. Also known is an active control mount that provides vibration means in the liquid chamber and vibrates in the same phase as the input vibration, thereby controlling the internal pressure of the liquid chamber to prevent vibration.
[0003]
[Patent Document 1]
Japanese Patent Laid-Open No. 5-321975 [Patent Document 2]
Japanese Patent Application Laid-Open No. 11-125303
[Problems to be solved by the invention]
The liquid-sealed engine mount performs vibration isolation only at a preset resonance frequency, and the resonance orifice does not function for vibration isolation at other frequencies.
On the other hand, the active control mount can prevent vibrations against a wide range of frequencies of input vibration, but in a damping region that requires high damping that affects riding comfort, or in a region where resonance such as a frame is likely to occur, such as an idle region, Anti-vibration is insufficient.
[0005]
Therefore, it is conceivable to combine the damping orifice or idle orifice of the liquid seal engine mount with the active control mount. However, the resonance orifice in this case is meaningless unless the amount of liquid flowing inside is increased to increase the resonance efficiency of the liquid column resonance, but because the vibration is controlled in the same phase, it flows into the resonance orifice. The amount of liquid to be increased does not increase and the efficiency of liquid column resonance cannot be expected to increase.
[0006]
Further, the liquid column resonance of the damping orifice has amplitude dependency, and when the input vibration becomes low amplitude, the amount of inflowing liquid decreases and the resonance frequency shifts to the high frequency side. For this reason, liquid column resonance due to the damping orifice may not be generated at a predetermined frequency. Therefore, in the riding comfort region, it is desired that the amount of liquid to the damping orifice can be increased and the resonance frequency can be made constant.
[0007]
In the idle region, it is desired to increase the supply of the liquid amount to the idle orifice to increase the resonance efficiency, and to prevent the resonance on the frame side. In addition, since the idle frequency changes in a relatively wide range depending on the operating condition of the engine, it is also desired that vibration can be prevented in a wider range by changing the resonance frequency following the change in the idle frequency in a wide range of frequencies. . The present invention aims to realize these requirements.
[0008]
[Means for Solving the Problems]
In order to solve the above-mentioned problem, a first aspect of the control method of the active control mount of the present application includes a liquid chamber provided with vibration means, and the liquid chamber is excited by vibration of the vibration means with respect to vibration input from the engine. In the active control mount designed to absorb the change in internal pressure, the liquid chamber includes a main liquid chamber on the vibration input side partitioned by a partition wall member, a sub liquid chamber on the opposite side, and the main liquid chamber, A resonance orifice that generates a liquid column resonance by connecting the sub liquid chambers, and vibrates in the opposite phase to the input vibration by the vibration means provided on the main liquid chamber side to increase the resonance efficiency of the resonance orifice. As you raise it ,
The resonance frequency is changed by controlling the excitation force of the excitation means to decrease as the frequency of the input vibration increases at the same time while oscillating in the opposite phase .
[0009]
An active control mount comprising a liquid chamber provided with a vibration means and absorbing a change in internal pressure of the liquid chamber by vibration of the vibration means with respect to vibration input from the engine,
The liquid chamber includes a main liquid chamber on the vibration input side partitioned by a partition wall member, a sub liquid chamber on the opposite side, and a resonance orifice that connects the main liquid chamber and the sub liquid chamber to generate liquid column resonance. And vibration of the opposite phase to the input vibration by the vibration means provided on the main liquid chamber side to increase the resonance efficiency of the resonance orifice,
While oscillating in the opposite phase, the oscillating force of the oscillating means is made constant at the same time, and the oscillating phase is changed so that the phase shift on the oscillating side increases as the frequency of the input vibration increases. Thus, the resonance frequency is changed .
[0010]
A third aspect of the present invention is the method according to the first or second aspect , wherein the resonance orifice is an idle orifice.
[0013]
A fourth aspect of the present invention is characterized in that, in any one of the first to third aspects , the antiphase control is performed within a range in which the liquid column resonance of the resonance orifice is controlled, and the other phases are controlled in the same phase.
[0014]
A fifth aspect is characterized in that, in any one of the first to fourth aspects , the exciting means is driven by a solenoid.
[0015]
【The invention's effect】
According to the first aspect of the present invention, in the region where the liquid column resonance is generated by the resonance orifice, the vibration of the opposite phase is performed by the vibration means. As a result, the amount of liquid flowing into the resonance orifice is increased, so that the resonance efficiency is increased and the vibration is prevented by the resonance orifice. For this reason, even in these regions where vibration control was insufficient with the conventional active control mount, sufficient vibration isolation was made possible by the resonant orifice.
Further, if the excitation force is changed with the excitation means remaining in the opposite phase, the resonance frequency can be changed following the change. Accordingly, it is possible to realize vibration isolation by liquid column resonance in a wide frequency range.
[0016]
According to claim 2, when the phase shift is changed while the excitation force is kept constant during the anti-phase control by the excitation means, the resonance frequency of the resonance orifice changes following this change. Accordingly, it is possible to realize vibration isolation by liquid column resonance in a wide frequency range.
[0017]
According to the third aspect, in the idle region, the vibration means vibrates in the opposite phase, thereby increasing the amount of liquid flowing into the idle orifice and increasing the resonance efficiency. In addition, the phase generated by the idle orifice is utilized to suppress the resonance on the frame side, thereby reducing the vibration transmission to the frame side.
[0020]
According to the fourth aspect of the present invention , the vibration control is performed by the resonance orifice having the opposite phase in the region where the liquid column resonance is necessary. Enables a wide range of vibration isolation control.
[0021]
According to the fifth aspect of the present invention , since the excitation means is driven by the solenoid, there is a limit excitation force of antiphase excitation determined by the performance of the solenoid, and the resonance control range based on the inverse phase extends to the limit excitation force. By doing so, reverse phase excitation using a solenoid becomes possible.
[0022]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments will be described below with reference to the drawings. 1 to 4 show a first embodiment in which a resonance orifice is a damping orifice. FIG. 1 is a sectional view of a liquid ring engine mount provided with a damping orifice (a sectional view taken along line 1-1 in FIG. 2). FIG. 3 is a diagram showing a change in resonance efficiency, and FIG. 4 is a diagram showing setting of a resonance control region.
[0023]
1 and 2, the liquid-sealed engine mount 1 includes a first mounting bracket 2 continuous to an engine (vibration source) (not shown), a second mounting bracket 3 connected to the vehicle body (not shown), The main liquid chamber 5 formed inside the insulator 4, the sub liquid chamber 7 connected via the damping orifice 6, and the first mounting bracket 2 of the main liquid chamber 5. And vibration means 8 provided on the side.
[0024]
The sub-liquid chamber 7 is formed by surrounding the outer circumference of the cylindrical metal fitting 9 surrounding the main liquid chamber 5 with a partition wall member, and the diaphragm 10 compensates the volume change. The cylindrical fitting 9 communicates with the damping orifice 6 through a passage 11.
[0025]
The damping orifice 6 is formed on the outer periphery of a circular orifice member 12 fitted in the main liquid chamber 5 and communicates with the main liquid chamber 5 through an inlet 13 formed in a part thereof. The damping orifice 6 generates liquid column resonance by a predetermined damping region vibration input, and the resonance frequency is set to, for example, about 8 to 12 Hz so as to be highly attenuated. An opening 14 is formed in the central portion of the orifice member 12 to communicate the liquid in the main liquid chamber 5 to the working chamber 15 on the vibration means 8 side.
[0026]
The vibration means 8 includes a disk-shaped vibration plate 16 that advances and retreats in the working chamber 15, a seal rubber 17 that seals the periphery of the vibration chamber 16 and the wall of the working chamber 15, and an armature connected to the center of the vibration plate 16. 18 and a solenoid 19 for moving the armature 18 back and forth in the vertical direction of the figure. The solenoid 19 is retracted downward in the figure by excitation, and is advanced upward in the figure by the elasticity of the seal rubber 17 by demagnetization.
[0027]
The operation control of the solenoid 19 is performed by the electronic control unit 20. Various sensor signals such as an engine displacement sensor 21, an engine rotation sensor 22, a load sensor 23, and an acceleration sensor 24 are input to the electronic control unit 20, and an input applied from the engine to the first mounting bracket 2 based on the input signals. Determine vibration. The displacement sensor 21 is used as necessary.
[0028]
Next, control of the vibration means 8 will be described. The electronic control unit 20 calculates the amplitude, phase, etc. of the input vibration, whether or not it is in the riding comfort region, and controls the operation of the solenoid 19 so as to vibrate in the opposite phase when the input vibration is a shake vibration. For this reason, when shake vibration is input to the liquid ring engine mount 1, the vibration control plate 16 vibrates in the vertical direction in FIG. Do.
[0029]
As a result, the amount of liquid flowing from the main liquid chamber 5 to the damping orifice 6 is increased, and as a result, liquid column resonance in the damping orifice 6 is generated with high efficiency. For this reason, sufficient vibration isolation can be achieved even in a damping region where vibration suppression has been insufficient with conventional active control mounts.
[0030]
This state is apparent in FIG. A in the figure indicates the relationship between the frequency and the dynamic spring constant. The resonance frequency B2 by the antiphase control has a lower dynamic spring than the resonance frequency B1 in the normal state where the control of this embodiment is not performed, and the low frequency side. Shift to. If the difference between these resonance frequencies and anti-resonance peaks P1 and P2 is H1 and H2, H2 during antiphase control is greater than H1, indicating that the resonance efficiency is high.
[0031]
B in the figure shows the relationship between the frequency and the phase, and the phase peak Q2 generated by the liquid column resonance during the antiphase control is larger than the phase peak Q1 generated by the liquid column resonance at the normal time. It shows that it is highly efficient.
[0032]
Further, as shown in FIG. 3C, the liquid column resonance due to the damping orifice 6 tends to shift to the high frequency side when the input vibration has a low amplitude. Therefore, the electronic control unit 20 calculates the amplitude of the input vibration from the signal from the displacement sensor 21 and the like, and causes the solenoid 19 to output an excitation force having a large amplitude corresponding to the decrease in the amplitude. As a result, the resonance frequency of the damping orifice 6 is kept constant irrespective of the amplitude change of the input vibration, so that liquid column resonance can be generated at the resonance frequency that is always set. Moreover, even if the input vibration from the engine has a low amplitude, it is possible to increase the liquid volume of the damping orifice by changing the excitation force of the anti-phase control, so that the resonance frequency can be kept constant, and the amplitude fluctuation of the input vibration can be reduced. Regardless of this, a predetermined vibration isolation effect can be achieved.
[0033]
Note that the maximum amplitude of the excitation by the solenoid is determined as shown in FIG. In other words, the excitation force of the solenoid has a linear relationship that falls to the right with respect to the amplitude of the insulator. That is, if the amplitude of the input vibration is increased, the resonance efficiency of the liquid column resonance is increased. Therefore, the force B required for securing the flow rate at the resonance orifice gradually decreases with the increase of the input amplitude of the engine, and the necessary excitation is performed. The power is reduced. The excitation force varies depending on the piston area of the excitation plate.
[0034]
On the other hand, the limit excitation force in the opposite phase is determined by the solenoid, and the control excitation force and the engine vibration input A, which is the sum A + B of the engine vibration input A that gradually increases as the input amplitude of the engine increases and the required excitation force B that gradually decreases. Intersection with. The amplitude of the engine input vibration at this point is the maximum amplitude that can be controlled in reverse phase.
This is the limit excitation force of the antiphase excitation determined by the performance of the solenoid, and the antiphase excitation using the solenoid becomes possible by setting the resonance control range by the antiphase to the limit excitation force.
[0035]
Next, a second embodiment for the purpose of controlling the idle area will be described. 5 to 10 show a second embodiment in which the resonance orifice is an idle orifice, FIG. 5 is a cross-sectional view of a liquid ring engine mount provided with the idle orifice, and FIG. 6 is a liquid column when the excitation force is changed. FIG. 7 is a diagram showing the resonance change, FIG. 7 is a diagram showing the relationship between the change in the control phase shift and the excitation force when the phase is changed with constant excitation force, and FIG. 8 is the case where the phase is changed with constant excitation force FIG. 9 and FIG. 10 are diagrams showing continuous control during idling to general running.
[0036]
FIG. 5 shows a liquid ring engine mount provided with an idle orifice 30. In this example, instead of the damping orifice 6, only the idle orifice 30 set to have a resonance frequency in the idle region and at the start, for example, a region of about 20 to 60 Hz, is used, and the other configuration is exactly the same as in FIG. Therefore, description of the structure is omitted.
[0037]
Also in this example, when there is an input vibration in the idle region, the solenoid 19 drives the vibration plate 16 in the opposite phase by the electronic control unit 20 and the main liquid chamber 5 is excited in the opposite phase. As a result, the amount of liquid flowing into the idle orifice 30 is increased and the resonance efficiency is increased as in the case shown in FIG.
[0038]
By increasing the resonance efficiency, the input vibration is absorbed by the liquid column resonance in the idle orifice 30. As a result, a low dynamic spring can be realized, and the vibration transmission of the input vibration to the frame side can be more reliably cut off. For this reason, it is possible to reduce the occurrence of resonance on the frame side by utilizing the phase generated by the idle orifice, thereby reducing vibration transmission to the frame side.
[0039]
Further, when the input vibration frequency in the idle region fluctuates within a wide range to some extent, the resonance frequency can be controlled to follow and change.
[0040]
As shown in FIG. 6, when the excitation force is decreased and changed stepwise in accordance with the increase of the frequency in the antiphase excitation state, the resonance frequency that appears as the bottom of the dynamic spring is R1, R2,. And gradually shift to the high frequency side. At this time, the opposite phase is taken out corresponding to each resonance frequency, and the phase curve P in the figure shows this. Also, as indicated by the dynamic spring curve K, the dynamic efficiency of the resonance frequency gradually increases, so that the resonance efficiency gradually decreases.
[0041]
Therefore, if the excitation force is changed to 0, the resonance frequency can be gradually changed to the higher frequency side, and frequency-dependent control following the input vibration becomes possible. For this reason, when the input vibration frequency in the idle region fluctuates in a wide range to some extent, the resonance frequency can be controlled to follow and change. Note that switching to the same phase control is performed when the excitation force becomes zero. In this way, it is possible to control continuously from the idle to the subsequent general running with the same active control mount.
[0042]
FIG. 7 shows control with constant excitation force. In this example, since the phase is changed, control is performed based on the phase control deviation δ with respect to the input vibration. That is, A of FIG. 7 shows the waveform of the input vibration on the upper stage, and shows the excitation waveform from the side of the vibration plate 16 on the lower stage. In this example, the phase on the excitation side is delayed by δ.
[0043]
For this reason, a difference can be made between the scalar amounts S1 and S2 of the vector at the time of the antiphase with respect to the vibration input, so that the antiphase vector component changes according to the deviation δ as seen in B on the right side of the figure. Therefore, even if the excitation force of the solenoid is constant, changing the phase control deviation δ is substantially the same as changing the excitation force.
[0044]
Therefore, as shown in FIG. 8, if the excitation force of the solenoid is kept constant and the excitation phase is changed from 0 deg to 90 deg, the resonance frequency and the resonance efficiency change in the same manner as in FIG. Control becomes possible. FIG. 8 shows a phase curve in the upper stage, a dynamic spring curve in the middle stage, and a curve of a change in phase control deviation in the lower stage with respect to the change in the resonance frequency on the horizontal axis.
[0045]
FIG. 9 shows an example of control extending during idle to normal travel using the phase control shown in FIGS. In this example, in the idle region, control is performed by constant excitation force and phase change shown in FIG. That is, the uppermost stage in the figure is the curve of the excitation force with respect to the vibration input, and the second stage from the top is the curve of the antiphase control, and the excitation force and the phase are controlled like these curves.
[0046]
As a result, the output side shows the third stage resonance efficiency curve and the bottommost dynamic spring curve in the figure. That is, when δ of the phase control changes from 0 to 180, the resonance efficiency decreases linearly. On the other hand, the dynamic spring changes in a mountain shape with δ = 90 as the apex, but this range becomes a possible region of resonance control in the resonance orifice. Between δ = 90 and 180 is a transition region that gradually changes to in-phase excitation control.
[0047]
When δ = 180, general in-phase excitation control is subsequently performed thereafter. In the same phase control, the phase is constant. In this way, by combining the anti-phase control and the in-phase excitation control, it is possible to control from the damping region where the orifice resonance is necessary and the idle region to the normal traveling with the same active control mount.
[0048]
Moreover, in the region where the liquid column resonance is required, the liquid column resonance of the resonance orifice due to the reverse phase is generated and the vibration is prevented by the resonance orifice. A wide range of vibration isolation control is possible with the active control mount.
[0049]
FIG. 10 shows a case where control is performed to change the excitation force with the opposite phase shown in FIG. 6 being constant. Also in this case, as in FIG. 9, in the idle region, the excitation force is gradually decreased with respect to the increase in the frequency of the input vibration, and at the same time when the idle region is removed, the in-phase excitation control is changed. In the in-phase excitation control, as the input vibration frequency increases, the follow-up performance of the actuator as the excitation means gradually decreases. In this case as well, the same active control mount can be used from the damping area where the orifice resonance is required and the idle area to the normal running. In addition, vibration isolation by liquid column resonance can be realized in a wide frequency range.
[0050]
The present invention is not limited to the above-described embodiments, and various modifications and applications can be made within the principle of the invention. For example, if an elastic film is provided on the main liquid chamber 5 side of the idle orifice 30, the damping orifice 6 and the idle orifice 30 can be provided simultaneously. The above example relates to the damping orifice 6 and the idle orifice 30. However, a resonant orifice that operates at other frequencies may be provided.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a liquid ring engine mount provided with a damping orifice. FIG. 2 is a top view of the liquid ring engine mount. FIG. 3 is a graph showing a change in resonance efficiency. Fig. 5 is a cross-sectional view of a liquid ring engine mount provided with an idle orifice. Fig. 6 is a diagram showing a change in liquid column resonance when an excitation force is changed. Fig. 7 is a change in control phase shift and an excitation force. FIG. 8 is a diagram showing a change in liquid column resonance when the phase is changed with a constant excitation force. FIG. 9 is a diagram showing continuous control during idling to general running with a constant excitation force. Fig. 10 is a diagram showing continuous control during idling to general running with constant reverse phase.
1: liquid seal engine mount, 2: first mounting bracket, 3: second mounting bracket, 4: insulator, 5: main liquid chamber 5, 6: damping orifice, 7: auxiliary liquid chamber 7, 8: vibration means, 15: Working chamber, 16: Vibration plate, 20: Electronic control unit, 30: Idle orifice

Claims (5)

In an active control mount that includes a liquid chamber provided with a vibration means and absorbs a change in internal pressure of the liquid chamber by vibration of the vibration means in response to vibration input from the engine.
The liquid chamber includes a main liquid chamber on the vibration input side partitioned by a partition wall member, a sub liquid chamber on the opposite side, and a resonance orifice that connects the main liquid chamber and the sub liquid chamber to generate liquid column resonance. And vibration of the opposite phase to the input vibration by the vibration means provided on the main liquid chamber side to increase the resonance efficiency of the resonance orifice ,
A control method for an active control mount, wherein the resonance frequency is changed by controlling the excitation force of the excitation means so as to decrease as the frequency of the input vibration increases while simultaneously oscillating in an opposite phase . In an active control mount that includes a liquid chamber provided with a vibration means and absorbs a change in internal pressure of the liquid chamber by vibration of the vibration means in response to vibration input from the engine.
The liquid chamber includes a main liquid chamber on the vibration input side partitioned by a partition wall member, a sub liquid chamber on the opposite side, and a resonance orifice that connects the main liquid chamber and the sub liquid chamber to generate liquid column resonance. And vibration of the opposite phase to the input vibration by the vibration means provided on the main liquid chamber side to increase the resonance efficiency of the resonance orifice,
While oscillating in the opposite phase, the oscillating means is made constant at the same time, and the oscillating phase is changed so that the phase shift on the oscillating side increases as the frequency of the input vibration increases. A method for controlling an active control mount, characterized in that the resonance frequency is changed by means of the method. 3. The method of controlling an active control mount according to claim 1, wherein the resonance orifice is an idle orifice. Performs control of the opposite phase between controlling the liquid column resonance of the resonant orifice, of the active control mount as claimed in any one of claims 1 to 3 for the rest, characterized in that the control in the same phase Control method. The method of the active control mount as claimed in any one of claims 1-4, wherein the vibration means is characterized in that it is driven by a solenoid.

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