JP3564594B2 - Anti-vibration device - Google Patents

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a vibration damping device having a set of liquid-filled vibration damping units on both sides of a vibrating body such as an engine, and more particularly, to each of the equilibrium chambers forming the set of liquid-filled vibration damping units. The present invention relates to a negative pressure introduction type liquid-filled type vibration damping device having a switching means which operates so as to introduce a negative pressure or an atmospheric pressure while being appropriately switched.
[0002]
[Prior art]
Among the vibration isolators, especially in the case of an engine mount for an automobile, the engine as a power source is used under various conditions from an idling operation state to a maximum rotation speed. Therefore, it must be able to handle a wide range of frequencies. Therefore, in order to cope with such a plurality of conditions, a liquid chamber is provided inside, and a fluid bag that changes volume at a specific frequency is provided in the liquid chamber, or via a diaphragm or the like. A liquid-filled type vibration damping device having a negative pressure chamber (equilibrium chamber) formed in a partitioned manner has been devised, and is already known, for example, from Japanese Patent Publication No. 6-29634.
[0003]
[Problems to be solved by the invention]
By the way, in the prior art, when the idling vibration is input, the fluid bag or the diaphragm or the like is actuated so that the hydraulic pressure in the main chamber does not rise, thereby providing a suspension system (anti-vibration system) for the idling vibration. This is to reduce the overall spring constant. On the other hand, with respect to an engine shake which is a problem during running of the vehicle, a negative pressure or the like is continuously introduced into a negative pressure chamber (equilibrium chamber) formed by the fluid bag or the diaphragm. Thus, in response to the vibration input of the engine shake, the liquid in the main chamber is positively flown to the sub-chamber through the orifice. That is, in response to the input of the engine shake, the hydraulic pressure in the main chamber is increased and the liquid in the main chamber is caused to flow into the orifice, whereby a high damping characteristic is obtained. is there. By the way, in such a system, the above-mentioned liquid filled type vibration damping device (vibration isolating unit) is installed in a pair state before and after, or left and right of a vibrating body such as an engine, and each of these liquid filled type vibration damping units is installed. Negative pressure or atmospheric pressure is supplied to each equilibrium chamber forming a vibration isolator (vibration isolating unit) in an appropriately switched state. Therefore, switching means for switching the introduction of the negative pressure or the atmospheric pressure to the respective equilibrium chambers forming each liquid-filled type vibration damping device (vibration damping unit) are also provided on each of the left and right sides. In addition, it is necessary to individually control the phases of the cycles of introducing the negative pressure or the atmospheric pressure into the left and right equilibrium chambers and the like. As a result, there is a problem that the switching means and the control means must be large-scale. In order to solve such a problem, a set of a negative pressure introduction type liquid-filled vibration isolator (vibration isolating unit) is mounted on a vibrating body such as an engine and the operation of each such vibration isolating unit. It is intended to provide a liquid-filled type vibration damping device that controls one set of the above-described vibration damping units by providing one switching means for controlling the vibration control unit and through the one switching means and the phase control means. It is an object (problem) of the present invention.
[0004]
[Means for Solving the Problems]
In order to solve the above problems, the present invention has taken the following measures. That is, with respect to the liquid-filled type vibration damping device, the upper connecting member attached to the vibrating body, the lower connecting member attached to the vehicle body side member and the like, and the upper connecting member and the lower connecting member interposed between the vibrating body and An insulator that absorbs and blocks the vibration of the main body, a main chamber in which a chamber wall is formed by a part of the insulator and in which a liquid is sealed, and a diaphragm connected to the main chamber via an orifice and a diaphragm. a sub-chamber in which a part of the chamber wall is partitioned and formed by the equilibrium chamber which are partitioned and formed through another diaphragm with respect to the upper Symbol main chamber, fluid-filled vibration isolating unit comprising (anti-vibration unit) Based on the above, one such liquid-filled type vibration-isolating unit (vibration isolating unit) is provided on each side of the vibrating body, and the A switching operation is performed so that either one of negative pressure or atmospheric pressure is introduced into each equilibrium chamber and the corresponding equilibrium chamber continuously or alternately in synchronization with engine vibration. While connecting with one switching means, it is connected with the switching means so that pressure fluctuation is propagated to any one of the equilibrium chambers in a state (frequency) synchronized with engine vibration, On the other hand, the other one is connected to the switching means via a phase control means, and further provided with control means for controlling the switching operation of the switching means formed as described above. The following configuration was adopted.
[0005]
By adopting such a configuration, the device of the present invention exhibits the following operation. That is, according to the first aspect of the present invention, first, the switching means is operated in response to idling vibration, whereby a negative pressure or an atmospheric pressure is specified to the liquid-filled vibration-proof unit (vibration-proof unit). Are introduced alternately with a frequency of By such an operation, a negative pressure or an atmospheric pressure is alternately introduced at a specific frequency into the equilibrium chamber of one of the above-described liquid-sealed type vibration-proof units (vibration-proof units). As a result, the pressure (volume) in the equilibrium chamber changes, whereby the fluctuation of the hydraulic pressure in the main chamber caused by the idling vibration input through the insulator is controlled. With this hydraulic pressure control action, the absolute spring constant (overall spring constant) and phase of the spring system formed by one of the vibration isolation units are controlled.
[0006]
At this time, since the phase control means is provided on the way to the balance chamber of the other one of the vibration isolation units, the negative pressure or the atmospheric pressure of which the phase conversion is controlled by the phase control means is performed. Is propagated. In other words, the pressure fluctuation, which is switched by the switching means and comprises the negative pressure or the atmospheric pressure, is controlled by the phase control means so that the phase thereof is adjusted to a specific value with respect to the pressure fluctuation sent to the one equilibrium chamber. It is sent out to the other equilibrium chamber in the state where it was set. The phase difference between the two during the propagation of this pressure fluctuation is generally set to a value of 180 °, but in principle, the direction of all the vibration isolating units must also be changed. The so-called combined vector value, which is expressed as the sum of the input loads considered, is a value close to zero (0). In such a state, when the idle vibration is propagated into the main chamber forming the main anti-vibration unit, the liquid in the main main chamber is subjected to hydraulic pressure fluctuation. It is controlled so that pressure (volume) fluctuation occurs in a state having a specific phase difference with the one vibration isolation unit, and the hydraulic pressure fluctuation is controlled by the volume fluctuation of the equilibrium chamber. Become. That is, in response to the input of the idling vibration, the vector value of the suspension system (vibration isolation system) becomes a value close to zero (0), whereby the idling vibration is cut off.
[0007]
Next, the second aspect of the invention will be described. This is also basically the same as the first aspect. The feature is that in a vibration damping device having a negative pressure introduction type liquid filled vibration damping unit, the phase control means is connected to a path connecting the switching means and one of the equilibrium chambers, An expansion chamber having a predetermined volume and provided in the middle thereof, and a diaphragm having a predetermined spring constant and provided in the expansion chamber are provided.
[0008]
By adopting such a configuration, in the case of the present invention, the phase control of the pressure fluctuation introduced into one of the equilibrium chambers is performed by a simple diaphragm mechanism. That is, phase conversion (control) can be performed in a space (expansion chamber) having a predetermined volume and a diaphragm provided therein, and phase control means can be provided in a narrow space. become. In addition, since a long path or the like is not required, it is possible to prevent a reduction in output and the like, and it is possible to increase the output of the vibration isolation unit.
[0009]
Next, a third aspect of the present invention will be described. This is also basically the same as the first and second aspects. The feature is that in a vibration damping device having a negative pressure introduction type liquid filled vibration damping unit, the phase control means is connected to a path connecting the switching means and one of the equilibrium chambers, An expansion chamber having a predetermined volume, provided in the middle thereof, a diaphragm provided in the expansion chamber and having a predetermined spring constant, and a diaphragm provided at the diaphragm and having a predetermined volume. And a mass having a mass of
[0010]
By adopting such a configuration, the device of the present invention exhibits the following operation. That is, by appropriately selecting the spring constant of the diaphragm or the mass of the mass, the phase of the pressure fluctuation of the equilibrium chamber on the side introduced via the present phase control means can be arbitrarily set. Become. As a result, the vibration isolation characteristics of the suspension system (vibration isolation system) can be freely set, and the vibration isolation effect against idling vibration can be maximized.
According to a fourth aspect of the present invention, in the vibration damping device according to the third aspect, a communication hole that communicates the expansion chambers on both sides of the diaphragm is provided in the mass.
[0011]
BEST MODE FOR CARRYING OUT THE INVENTION
An embodiment of the present invention will be described with reference to FIGS. Although it relates to the embodiment of the present invention, as shown in FIG. 1, the configuration is a liquid-filled type vibration damping unit ( The anti-vibration units 1A and 1B and the pair of anti-vibration units 1A and 1B are switched so that negative pressure or atmospheric pressure is supplied continuously or alternately in synchronization with engine idling vibration. One switching means 3 for operating, and a negative pressure or an atmospheric pressure appropriately switched by the switching means 3 to each of the vibration isolation units 1A and 1B, and a path 2, 2 'comprising a hose or the like. And phase control means 6 provided at one of the paths (2) and (2) for controlling the phase of the input pressure fluctuation to an appropriate state. , Switching And control means 5 for controlling the switching operation of the stage 3, in which the basic in that it consists of.
[0012]
In such a basic configuration, the switching means 3 includes, as shown in FIG. 2, a switching valve 31 formed of a three-way valve or the like, and a solenoid 32 for driving the switching valve 31. A throttle valve 33 for adjusting the introduction speed of the atmospheric pressure to the introduction speed of the negative pressure is provided on the side of the atmospheric pressure introduction port of the switching valve 31 having such a configuration. I have. As shown in FIG. 1, a resonance tank 35 having a predetermined capacity is provided on the negative pressure introducing side. By providing such a resonance tank 35, when the distance (pipe distance) from the negative pressure source formed by the engine suction negative pressure or the like to the equilibrium chamber 13 becomes long, the resistance or the like in the pipe is increased. This prevents the negative pressure from dropping. That is, by providing such a resonance tank 35, a predetermined amount of negative pressure is always supplied accurately into the equilibrium chamber 13 with a predetermined cycle. The second diaphragm 11 to be formed can be vibrated with a large amplitude value.
[0013]
As shown in FIG. 1, the paths 2, 2 'connecting between the switching means 3 and the vibration isolating units 1A, 1B installed on the vibrating body 4 are composed of pipes such as hoses. It is. The phase control means 6 as shown in FIGS. 3 to 5 is provided at one of the paths (2, 2 '). This phase control means 6 is basically provided with an expansion chamber 61 having a predetermined volume and a predetermined spring constant (Kd) as shown in FIG. 1 or FIG. And a diaphragm 62 and a mass 66 having a predetermined mass (M). Then, the natural frequency (f ₀ ) of the phase control means 6 is specified by the ratio between the spring constant (Kd) and the mass (M). When the idling frequency of the engine 4 supported by the vibration isolator, that is, the switching frequency of the switching unit 3 is a value of f (Hz), the natural frequency of the phase control unit 6 ( By appropriately selecting the value of f ₀ ) as shown in FIG. 6, the pressure fluctuation in the vibration isolating unit 1B introduced via the phase control means 6 can be directly reduced to the vibration isolating side on the opposite side where the pressure fluctuation is introduced. It becomes possible to provide a predetermined phase difference with respect to the unit in the unit 1A. When pressure fluctuation of a predetermined frequency is introduced with a phase difference of, for example, 180 ° between the left and right anti-vibration units 1A and 1B having such a configuration, the dynamic spring constant in each of the anti-vibration units 1A and 1B is reduced. At the same time, the input value of the force caused by the vibration of the engine to the body side (vehicle body side) via the vibration isolation units 1A and 1B is reduced (attenuated).
[0014]
The phase control means 6 having such a configuration has a predetermined mass (M) at the diaphragm 62 as shown in FIG. 4 in addition to the one having the diaphragm 62 as shown in FIG. The one provided with the mass 66 is exemplified. By appropriately selecting the mass (M) of the mass 66, the value of the natural frequency (f ₀ ) of the phase control means 6 can be freely changed. By setting the value of the f ₀ as appropriate, it is possible to choose the right and left of the image-stabilizing unit 1A in the present vibration damping device, a phase difference between 1B appropriate.
[0015]
Further, in such a phase control means 6, as shown in FIG. 5, a communication hole 65 composed of a fine hole is provided at the mass 66. When the switching means 3 is operating in a pressure fluctuation state having a predetermined frequency, the diaphragm 62 is operated, and when the switching means 3 is in a state of continuous introduction of a negative pressure, this phase is changed. A constant negative pressure is also introduced through the communication hole 65 to the vibration isolating unit 1B connected via the control means 6. As a result, the equilibrium chamber 13 (see FIG. 2) of both the vibration isolation units 1A and 1B is brought into a state of zero volume due to the introduction of the negative pressure, and the liquid in the main chamber 12 in each of the vibration isolation units 1A and 1B in this state Is made to flow toward the sub chamber 16 via the first orifice 15. As a result, the damping force of each of the anti-vibration units 1A and 1B is increased, and engine shake is suppressed. That is, the type having the communication hole 65 shown in FIG. 5 can exert the effect of absorbing and blocking the engine shake which is a problem during traveling.
[0016]
Next, control for controlling the switching operation of the switching means 3 which operates so as to send out a predetermined negative pressure or the like to the respective paths 2, 2 'and the phase control means 6 having such a configuration while appropriately switching them. The means 5 comprises a microcomputer or the like formed on the basis of arithmetic means such as a microprocessor unit (MPU), detects vibration from a vibrating body such as an engine, and switches the switching means according to the vibration. The switching operation of No. 3 is controlled.
[0017]
Next, a predetermined negative pressure or the like is introduced through the switching means 3, the phase control means 6, and the paths 2, 2 ', etc. having such a configuration, and the vibrating body 4 such as the engine is supported. Each of the vibration units 1A and 1B includes a liquid-sealing type vibration-isolating device (liquid-sealing type vibration-isolating unit) 1 as shown in FIG. As shown in FIG. 1, the liquid-filled type vibration damping units (vibration damping units) 1 are mounted on both sides of a vibrating body 4 such as an engine, one by one, in a pair. It is to be formed. The specific configuration of such an anti-vibration unit 1 will be described below. That is, as shown in FIG. 2, the anti-vibration unit 1 includes an upper connecting member 9 attached to the vibrating body 4, a lower connecting member 99 attached to the vehicle body, and an upper connecting member 9 and a lower connecting member 99. An insulator 7 that absorbs and blocks vibration from the vibrating body 4 and a main chamber 12 that is provided in series with the insulator 7 and that is filled with a liquid that is an incompressible fluid; The sub-chamber 16 is connected to the main chamber 12 via the first orifice 15 and a part of the chamber wall is defined by the first diaphragm 17. The air chamber 18 is basically provided with an air chamber 18 provided at a distance and an equilibrium chamber 13 formed separately from the main chamber 12 via another diaphragm (second diaphragm) 11. That.
[0018]
In such a basic configuration, the insulator 7 is made of a vibration-proof rubber material, and is integrally connected to the upper connecting member 9 by a vulcanization bonding means or the like. . A main chamber 12 in which a chamber wall is formed as a part of the insulator 7 is provided below the insulator 7 having such a configuration. Further, an equilibrium chamber 13 into which a negative pressure or an atmospheric pressure is alternately introduced in a predetermined cycle is provided below the main chamber 12 or the like. In addition, as shown in FIG. 2, between the equilibrium chamber 13 having such a configuration and the main chamber 12, the liquid resonance including the second diaphragm 11, the second orifice 125, and the third liquid chamber 123 is provided. A mechanism is provided. Thereby, the pressure fluctuation brought to the equilibrium chamber 13 is caused by the vibration of the second diaphragm 11, furthermore, by the liquid vibration in the third liquid chamber 123 and the liquid resonance in the second orifice 125. , To the liquid in the main chamber 12. As a result, the fluctuation of the hydraulic pressure propagated in the main chamber 12 is adjusted to a state close to a normal sine wave.
[0019]
Next, an operation mode and the like of the present embodiment having such a configuration will be described. First, as shown in FIG. 2, the vibration from the vibrating body 4 is propagated through the upper connecting member 9 to the insulator 7 made of a rubber material or the like. Most of the vibration transmitted to the insulator 7 is absorbed or cut off by deformation of the insulator 7 or the like. However, some of the components are not cut off at the insulator 7 but are cut off at a vibrating mechanism section including the next equilibrium chamber 13 and the like. The specific operation and the like will be described below. In other words, with respect to idling vibration, by operating the switching means 3, a negative pressure or an atmospheric pressure is alternately introduced into the liquid filled type vibration damping unit (vibration damping unit) 1 at a specific frequency. To By such an operation, a negative pressure or an atmospheric pressure is alternately introduced at a specific frequency into the equilibrium chamber 13 of one of the liquid-filled vibration-proof units (vibration-proof units) 1A shown in FIG. Become. As a result, the pressure (volume) in the equilibrium chamber 13 changes, and the hydraulic pressure fluctuation in the main chamber 11 caused by idling vibration input through the insulator 7 is controlled. As a result, the absolute spring constant (overall spring constant) and phase of the spring system formed by the vibration isolation unit 1A are controlled.
[0020]
On the other hand, at this time, since the equilibrium chamber 13 is connected to the equilibrium chamber 13 of the other vibration isolation unit 1B via the phase control means 6, it is introduced through the phase control means 6. The negative pressure and the atmospheric pressure are input (introduced) with a predetermined phase difference with respect to the pressure fluctuation input to the equilibrium chamber 13 of the one vibration isolation unit 1A. Generally, this phase difference is set to a value near 180 °, but in a vibration system, the phase difference may be adjusted to 90 ° or 0 ° (in-phase). Incidentally, hitting the adjustment (control) of the phase difference, for example, the mass 66 in FIG. 4, to control the value of f ₀ of the phase control means 6 by adjusting the value of the mass (M), Thus, the value of the phase difference can be adjusted (controlled) (see FIG. 6). In such a state, when idling vibration is propagated into the main chamber 12 (see FIG. 2) that forms the main anti-vibration units 1A and 1B, the liquid in the main chamber 12 receives a fluctuation in liquid pressure. The fluctuation (change) of the hydraulic pressure is transmitted to the second diaphragm 11 forming the equilibrium chamber 13 via the second orifice 125 and the third liquid chamber 123. At this time, the second diaphragm 11 operates so as to control the fluctuation (change) of the hydraulic pressure in the main chamber 12. Further, each of the equilibrium chambers 13 and the second diaphragm 11 of each of the left and right anti-vibration units 1A and 1B operates with a phase difference of 180 °. As a result, the absolute spring constant and phase are controlled with respect to the input of the idling vibration, the vector value of the suspension system (vibration isolation system) becomes close to zero (0), and the idling vibration is cut off. .
[0021]
Next, the liquid flows through the first orifice 15 that connects the main chamber 12 and the sub chamber 16 in FIG. 2 with respect to the engine shake that is a vibration of a lower frequency than the idling vibration. In this way, absorption and cutoff of the engine shake are achieved. That is, in the present embodiment, first, the switching means 3 is operated so that the negative pressure is continuously supplied to each of the equilibrium chambers 13 forming the pair of vibration isolation units 1A and 1B in FIG. I do. Therefore, in the present embodiment, as shown in FIG. 5, a communication hole 65 composed of a fine hole is provided at a mass 66 provided in the phase control means 6, and the path 2 provided with the phase control means 6 is provided. A continuous state of negative pressure is also formed on the side. In such a state, the switching means 3 is operated so that the negative pressure is introduced into the two equilibrium chambers 13. As a result, each of the equilibrium chambers 13 is kept in a state where the volume is zero. Therefore, in each of the vibration isolating units 1A and 1B, the liquid flows in the first orifice 15 formed between the main chamber 12 and the sub-chamber 16, and the liquid flows. A predetermined damping force is generated by viscous resistance. Then, the engine shake is attenuated (suppressed) by the damping force (high damping characteristic). As described above, according to the present embodiment, the idling vibration and the engine shake can be efficiently absorbed and cut off by operating one switching means 3.
[0022]
【The invention's effect】
According to the present invention, with respect to a vibration isolator supporting a vibrating body such as an engine, liquid-filled vibration isolating units are provided in a pair on both sides of the vibrating body, and respective balances forming the two vibration isolating units are provided. One switching means which operates to introduce a negative pressure or an atmospheric pressure into the chamber is provided, and a control means for controlling the switching operation of the switching means is provided. Since the pressure fluctuation is introduced via the control means, the diaphragms of the equilibrium chambers forming the respective vibration isolation units can be vibrated in a state synchronized with the idling vibration. The absolute spring constant (overall spring constant) and the phase formed by both anti-vibration units are adjusted so that the value of the combined vector in the suspension system (anti-vibration system) is close to zero (0). It has become possible to achieve the reduction. As a result, it is possible to cut off idling vibration by operating one switching unit.
[0023]
In addition, for the engine shake which is a problem during running of the vehicle, a communication hole is provided at the mass forming the phase control means, thereby continuously supplying a negative pressure to each of the equilibrium chambers. As a result, the flow of the liquid into the orifices in both vibration isolating units is promoted, and thereby high damping characteristics can be exhibited. As a result, the engine shake can be attenuated (suppressed).
[0024]
As described above, according to the present invention, a negative pressure or the like is introduced into each of the vibration isolating units provided on both sides of the vibrating body via one switching means, so that an active control mounting device (ACM) Can be formed with a relatively simple configuration.
[Brief description of the drawings]
FIG. 1 is a perspective view showing the overall configuration of the present invention.
FIG. 2 is a longitudinal sectional view showing an entire configuration of a liquid-filled type vibration damping unit which is a main part of the present invention.
FIG. 3 is a diagram showing a basic configuration of a phase control unit according to the present invention.
FIG. 4 is a cross-sectional view showing a general structure of a phase control unit according to the present invention.
FIG. 5 is a cross-sectional view showing a modification of the phase control means according to the present invention.
FIG. 6 is a graph (graph) showing characteristics of the phase control means according to the present invention.
[Explanation of symbols]
1 Liquid-filled vibration-proof unit (vibration-proof unit)
1A One anti-vibration unit 1B The other anti-vibration unit 11 Second diaphragm 12 Main chamber 123 Third liquid chamber 125 Second orifice 13 Equilibrium chamber 15 First orifice 16 Sub chamber 17 First diaphragm 18 Air chamber 2 Path 2 ′ Path 3 switching means 31 switching valve 32 solenoid 33 throttle valve 35 resonance tank 4 vibrator (engine)
5 Control means 6 Phase control means 61 Expansion chamber 62 Diaphragm 65 Communication hole 66 Mass 7 Insulator 9 Upper connecting member 99 Lower connecting member

Claims (4)

An upper connecting member attached to the vibrating body, a lower connecting member attached to the vehicle body , an insulator interposed between the upper connecting member and the lower connecting member for absorbing and blocking vibration from the vibrating body, and one of the insulators A main chamber in which a chamber wall is formed and a liquid is sealed, and a sub-chamber connected to the main chamber via an orifice and partly formed by a diaphragm by a diaphragm When the equilibrium chamber which are partitioned and formed through another diaphragm with respect to the upper Symbol main chamber, the fluid-filled vibration isolating unit comprising the foundation, one each the fluid-filled vibration isolating units on both sides of the vibrating body Each of the two equilibrium chambers of the two liquid-sealed type vibration damping units, and one of the negative pressure and the atmospheric pressure is continuously provided in each of the equilibrium chambers. Along with connecting the one of the switching means for a switching operation so as to alternately introduced in a state of being synchronized with the engine vibration, to those of either of the above equilibrium chamber-like synchronized with the engine vibration pressure fluctuations in the state is connected to the switching means so as to propagate, on the other hand, it is to the remaining one of those, so as to connected to the switching means in a state in which through the phase control means, further, such structure And a control means for controlling a switching operation of the switching means. 2. An anti-vibration device according to claim 1, wherein said phase control means is provided in the middle of a path connecting said switching means and one of said equilibrium chambers, said expansion chamber having a predetermined volume. A diaphragm provided in the expansion chamber and having a predetermined spring constant. 2. An anti-vibration device according to claim 1, wherein said phase control means is provided in the middle of a path connecting said switching means and one of said equilibrium chambers, said expansion chamber having a predetermined volume. A diaphragm provided in the expansion chamber and having a predetermined spring constant, and a mass provided at the diaphragm and having a predetermined mass. Shaking device. 4. The vibration damping device according to claim 3, wherein the mass is provided with a communication hole communicating with the expansion chambers on both sides of the diaphragm.

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