JP2006029591A - Liquid filled vibration control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To damp low-frequency engine idling vibration with high damping force. <P>SOLUTION: This liquid filled vibration control device comprises a rubber insulator 4 arranged between a first connection member 91 and a second connection member 95 for absorbing/interrupting the vibration of a vibrating body, a main chamber 5 whose chamber wall is formed by part of the insulator 4 and in which liquid is filled, a sub chamber 6 which is connected to the main chamber 5 via a first orifice 11 and whose chamber wall is partially defined by a first diaphragm 7, a second orifice 12 for connecting the sub chamber 6 to a third liquid chamber 23, an orifice forming member 1 on which the first orifice 11 and the second orifice 12 are provided, and a liquid chamber forming member 2 which is provided inside the orifice forming member 1 and at the center of which a second diaphragm 22 is provided for defining the third liquid chamber 23 from the main chamber 5. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a liquid-filled vibration isolator having an anti-vibration mechanism formed so as to cut off vibration in a specific frequency range, and in particular, two frequencies such as engine idling vibration and engine shake vibration. The present invention relates to a liquid-filled vibration isolator that exhibits a high damping characteristic in any case and thereby attenuates both the vibrations.

Among anti-vibration devices, especially in the case of engine mounts for automobiles, the engine as the power source is used under various conditions from idling to the maximum rotational speed. Therefore, it must be able to handle a wide range of frequencies. Therefore, there are two liquid chambers inside, connected between them with an orifice, and liquid-filled vibration proofing designed to cut off vibration at a specific frequency by resonating the liquid in the orifice at a specific frequency. An apparatus has been devised and is already known. Among such liquid-filled vibration isolator, the type having two orifices includes, for example, those described in JP-A-2001-20992.
JP 2001-20992 A

  By the way, in the above-mentioned conventional one, the dynamic spring constant of the whole vibration isolator is reduced by the liquid column resonance action of the liquid existing in one of the orifices. With respect to engine shake vibration, which is a problem during traveling, a damping function is exhibited by the action of a damping force based on the flow resistance of the liquid in the other orifice. However, recent automobile engines employ a lean combustion system or a low engine idling rotational speed from the viewpoint of reducing fuel consumption, and the idling operation state of the engine is unstable. As a result, the occurrence of vibrations in the rotational 0.5 frequency range of the engine is a problem. It is an object of the present invention to provide a liquid-filled vibration isolator in which the idling vibration in such a low frequency region is controlled by the high damping function of the idling vibration-compatible orifice ( Problem).

  In order to solve the above problems, the following measures are taken in the present invention. That is, in the first aspect of the present invention, the first connecting member attached to the vibrating body, the second connecting member attached to the member on the vehicle body side, the first connecting member and the second connecting member A rubber-like insulator that absorbs and blocks vibration from the vibrating body, a main chamber in which a chamber wall is formed by a part of the insulator and in which a liquid is enclosed, and the main chamber A sub-chamber connected to the chamber via a first orifice and partly defining a chamber wall by the first diaphragm; a partition member partitioning the main chamber from the sub-chamber; A third liquid chamber in which a part of the chamber wall is defined by a second diaphragm with respect to the chamber, and a second orifice connecting the third liquid chamber and the sub chamber. For liquid-filled vibration isolator with two orifices The second orifice is provided outside the third liquid chamber so that the second orifice has a circular double winding shape in plan view, and the first orifice is The configuration is such that it is provided on the outside of the second orifice and has a circular arc shape formed in a part of the ring in plan view.

  By adopting such a configuration, in the present invention, it is possible to reduce engine idling vibration, particularly vibration in a low frequency (low frequency) region corresponding to engine rotation 0.5th order vibration. It becomes like this. In particular, in the present invention, since one of the orifices is made to cope with engine rotation 0.5th order vibration, such low frequency (low frequency) vibration can be reduced. In addition, since the other orifice is adapted to cope with engine rolling vibration and engine shake vibration, engine vibration can be suppressed (vibrated) or shut off during engine idling operation and vehicle running. It becomes like this.

  Next, the invention described in claim 2 will be described. The basic point of this is the same as that of the first aspect. That is, according to the present invention, in the liquid-filled vibration isolator according to claim 1, the first orifice and the second orifice are both highly attenuated with respect to the engine idling vibration input and the engine shake vibration input. It was decided to adopt a configuration that exhibited the characteristics. By adopting such a configuration, in the present invention as well, the engine idling vibration and the engine shake vibration during vehicle traveling can be suppressed (vibrated) as in the first aspect. Become. In particular, in the present invention, both the orifices are set so as to have a high damping characteristic. Therefore, the engine rotation 0.5 order vibration during engine idling operation or the engine during engine idling operation. The rolling vibration can be suppressed (damped) by the high damping force formed by the two orifices. As a result, it is possible to efficiently suppress vibrations of a relatively low frequency that occur during engine idling operation. Further, the suppression (vibration) of the engine shake vibration generated during the traveling of the vehicle can be suppressed (vibrated) by the damping force of the orifice. Thus, in the present invention, both low-frequency vibrations during engine idling and engine shake vibrations generated during vehicle travel are both suppressed by the high damping force formed by the two orifices. Thus, the vibration damping action is effectively exhibited.

  According to the present invention, the first connecting member attached to the vibrating body, the second connecting member attached to the member on the vehicle body side, and the like between the first connecting member and the second connecting member A rubber-like insulator that absorbs and blocks vibration from the vibrating body, a main chamber in which the chamber wall is formed by a part of the insulator and in which a liquid is sealed, and a first chamber in the main chamber A sub-chamber that is connected through an orifice and is partly formed by a first diaphragm, and a partition member that partitions the main chamber and the sub-chamber; A type having two orifices consisting of a third liquid chamber in which a part of the chamber wall is defined by a second diaphragm and a second orifice connecting the third liquid chamber and the sub chamber. The above-mentioned second orientation The first orifice is provided outside the second orifice, and is formed in an annular double winding form in plan view. In view of the engine idling vibration, in particular, the engine rotation 0.5th order vibration is adopted. The vibration in the corresponding low frequency (low frequency) region can be reduced. In particular, in the present invention, since one of the orifices is made to cope with engine rotation 0.5th order vibration, such low frequency (low frequency) vibration can be reduced. In addition, since the other orifice is adapted to cope with engine rolling vibration and engine shake vibration, engine vibration can be suppressed (vibrated) or shut off during engine idling operation and vehicle running. It became so.

  In the present invention, the first orifice and the second orifice are both configured to exhibit a high damping characteristic with respect to the engine idling vibration input and the engine shake vibration input. As a result, engine idling vibration and engine shake vibration during vehicle travel can be suppressed (vibrated). In particular, in the present invention, both the orifices are set so as to have a high damping characteristic. Therefore, the engine rotation 0.5 order vibration during engine idling operation or the engine during engine idling operation. The rolling vibration can be suppressed (damped) by the high damping force formed by the two orifices. As a result, it has become possible to efficiently suppress relatively low frequency vibrations that occur during engine idling operation. Further, the suppression (vibration suppression) of engine shake vibration that occurs during the running of the vehicle can be suppressed (vibration suppression) by the damping force of each orifice. As described above, in the present invention, both low frequency vibration during engine idling operation and engine shake vibration generated during vehicle running can be suppressed by the high damping force formed by the two orifices. As a result, the vibration control action can be effectively exhibited.

  An embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 1, the configuration of the present embodiment includes a first connecting member 91 attached to the vibrating body, a second connecting member 95 attached to a member on the vehicle body side, and the first connecting member. A rubber-like insulator 4 between the member 91 and the second connecting member 95 that absorbs and blocks vibration from the vibrating body, and a chamber wall is formed by a part of the insulator 4. A main chamber 5 in which liquid is sealed and a part of the chamber wall are connected to the main chamber 5 via a first orifice (first orifice) 11 and a first diaphragm (first diaphragm) 7. It functions as a partition for partitioning the sub chamber 6 and between the main chamber 5 and the sub chamber 6, and includes the first orifice 11 and the second orifice (second orifice) 12, etc. Orifice provided The component member 1 is provided inside the orifice forming member 1, and the third liquid chamber 23 and the space between the third liquid chamber 23 and the main chamber 5 are formed at the central portion thereof. A liquid chamber forming member 2 in which a second diaphragm (second diaphragm) 22 is provided, and the orifices 11 and 12 and the third liquid chamber are provided on the lower end side of these orifice forming member 1 and liquid chamber forming member 2. 23 and a partition member 8 for partitioning and forming between the sub chamber 6 and the sub chamber 6.

  In the structure as described above, the orifice forming member 1 is formed of a predetermined plastic material or aluminum alloy material, and has an annular shape in plan view. That is, the orifice forming member 1 is provided with two orifices 11 and 12 in an annular shape as shown in FIG. Specifically, a first orifice 11 is formed on the outermost side of the orifice forming member 1 and has an annular shape and is formed so as to make one round. The first orifice 11 is formed to connect the main chamber 5 and the sub chamber 6 and has a main chamber side opening hole 115 and a sub chamber side opening hole 116. It is what. A second orifice 12 having a double winding shape is provided inside the first orifice 11. The second orifice 12 connects the sub chamber 6 and the third liquid chamber 23, and operates based on the vibration input propagated to the liquid in the main chamber 5. By the operation of 22 (see FIG. 1), the liquid in the third liquid chamber 23 is caused to flow to the sub chamber 6 side. In the above-described configuration, the first orifice 11 is formed for the purpose of damping a low-frequency vibration corresponding to the engine rotation 0.5th order frequency of the idling vibration. It is what. Therefore, in order to suppress the rotational 0.5th order vibration of the engine, it is formed outside the orifice forming member 1 so as to obtain a high damping force with respect to the input of the low frequency vibration. The second orifice 12 is provided inside the first orifice 11 and around the third liquid chamber 23 in a double winding shape. In other words, the second orifice 12 is folded back when it makes a round around the opening hole 121 on the third liquid chamber 23 side, and after returning to the double winding shape, it passes through the sub chamber side opening hole 126. The sub chamber 6 communicates with the sub chamber 6. Inside these two orifices 11 and 12, a liquid chamber forming member 2 formed of a rubber-like member and having a cup shape is provided. A concave portion that contributes to the formation of the third liquid chamber 23 is provided at the central portion of the liquid chamber forming member 2, and the main chamber 5 is partitioned above the concave portion. A second diaphragm 22 to be formed is integrally provided. The liquid chamber forming member 2 and the orifice forming member 1 are integrally coupled, and the third liquid chamber 23 is connected to the second orifice 12 through the second orifice-side opening hole 121. (See FIG. 2). In the lower part of the orifice forming member 1 and the liquid chamber forming member 2 having such a configuration, the third liquid chamber 23, the first orifice 11 and the second orifice 12 are liquid-tight with respect to the sub chamber 6. A partition member 8 for blocking is provided (see FIG. 1).

  The partition member 8 basically has a disk shape, and is formed of a press-formed product based on a steel plate or a formed product of an aluminum alloy plate material. A liquid chamber forming member 2 made of a rubber material or EPDM or the like and an orifice forming member 1 having an annular shape are installed on such a disk-shaped partition member 8, and each of the members 1, 2 is arranged. Are held in pressure contact with each other, the first orifice 11, the second orifice 12, and the third liquid chamber 23 are integrally formed. As a result, the partition member 8, the orifice forming member 1 and the liquid chamber forming member 2 are in close contact with each other, and the sealing performance in the first orifice 11, the second orifice 12, the third liquid chamber 23, etc. is improved. Become. In addition, what consists of such a structure WHEREIN: The flange 88 is provided in the place of the peripheral terminal part of the said partition member 8. As shown in FIG. The flange 88 is joined with the peripheral end portion 44 of the insulator 4 formed so as to sandwich the peripheral end portion of the orifice forming member 1 and the peripheral portion of the first diaphragm 7 being overlapped together. These are connected to the peripheral portion of the second connecting member 95 through clinch connecting means or the like. The partition member 8, the orifice forming member 1, the liquid chamber forming member 2, the first diaphragm 7, and the like are integrally coupled to the peripheral portion of the second connecting member 95 in this way, thereby Between the partition member 8 and the first diaphragm 7, a sub chamber 6 defined by the first diaphragm 7 and the like is formed. The partition member 8 that partitions and forms the upper portion of the sub chamber 6 is provided with a sub chamber side opening hole 116 of the first orifice 11 and a sub chamber opening hole 126 of the second orifice 12. These opening holes 116 and 126 communicate with the main chamber 5 side through the first orifice 11 or the third liquid chamber 23 side through the second orifice 12, respectively. Is.

  Next, the operation mode and the like of the present embodiment having such a configuration will be described. That is, the vibration from the vibrating body side is propagated to the insulator 4 made of a rubber material or the like through the upper connecting member 91 as shown in FIG. Accordingly, the insulator 4 vibrates or deforms to absorb or block most of the input vibration. Therefore, most vibrations are cut off at the insulator 4, but some of them are not cut off at the insulator 4, and the following liquid chambers 5, 6, 23 and the orifices 11 are next. , 12 will be interrupted. Next, specific actions in these liquid chambers and orifices will be described. First, with respect to the input of engine idling vibration, the following measures are taken in the present embodiment. That is, the idling vibration targeted in this embodiment is a vibration in a very low frequency range of about 5 Hz corresponding to the engine rotation 0.5th order vibration. It is difficult to cut off this vibration by reducing the dynamic spring constant of the engine mount as in the conventional case. In the conventional system, as shown in FIG. 4, the peak value is generated when engine shake vibration having a specific frequency (frequency) is targeted, as shown in FIG. In the region, almost no damping force is generated. Therefore, in the conventional system, it is impossible to suppress (suppress) the 0.5th-order vibration of the engine by the damping force of the engine mount. In view of such a point, in the present embodiment, the low frequency vibration is suppressed (vibrated) by enhancing the damping function of the orifice with respect to the low frequency vibration input of about 5 Hz. It is said. Specifically, when the low-frequency vibration is transmitted to the liquid in the main chamber 5 via the insulator 4, first, the liquid existing in the main chamber 5 is passed through the first orifice 11 to the sub chamber 6 side. To flow. A predetermined damping force is exerted by the flow resistance of the liquid in the first orifice 11 to suppress the 0.5th-order rotation of the engine. That is, as shown in part A of FIG. 3, a high damping force is exerted with respect to a vibration input around 5 Hz, thereby suppressing the rotational 0.5th order vibration of the engine having a frequency around 5 Hz. To control).

  Further, in the present embodiment, regarding engine idling vibration, engine rolling vibration in a frequency region around 15 Hz is a problem, and vibration suppression is also required. In the present embodiment, the damping function of the engine rolling vibration in the frequency range around 15 Hz is dealt with by increasing the damping function of the engine mount. Specifically, the engine rolling vibration around 15 Hz is suppressed (damped) by the damping function formed by the second orifice 12 provided in a double winding shape inside the first orifice 11. (Refer to part B in FIG. 3). That is, in response to the input of this engine rolling vibration, the second diaphragm 22 facing the main chamber 5 vibrates. In response to the vibration of the second diaphragm 22, the liquid in the third liquid chamber 23 flows through the second orifice 12 to the sub chamber 6 side. That is, the liquid in the third liquid chamber 23 flows from the third liquid chamber side opening hole 121 of the second orifice 12 into the second orifice 12 and passes through the second orifice 12 to the sub chamber side opening hole. The fluid flows from 126 to the sub chamber 6. Due to the flowing action of the liquid in the second orifice 12, a high damping force can be obtained with respect to a frequency (frequency) around 15 Hz as shown in part B of FIG. The engine damping vibration is suppressed (damped) by this high damping force.

  Next, regarding the engine shake vibration, which is a problem during the running of the vehicle, in the present embodiment, the frequency value of the engine shake vibration is within the range of 10 to 15 Hz. Therefore, the second orifice 12 is suppressed (damped) by a damping force based on the flow action of the liquid in the second orifice 12. Specifically, in the present embodiment, mainly by setting the diameter and length of the second orifice 12 shown in FIG. 2 to appropriate values, high damping characteristics are exhibited with respect to the input of engine shake vibration. I will let you. As a result, engine shake vibration that occurs during vehicle travel is effectively suppressed (damped).

  As described above, in the present embodiment, the vibration isolation during idling operation including low frequency including engine rotation 0.5th order vibration, etc. is performed by the liquid chambers 5, 6, 23 and the orifices 11, 12. It is suppressed (damped) by the high damping force formed by In addition, these orifices are used to suppress engine shake vibration, which is a problem during vehicle travel.

It is a longitudinal cross-sectional view which shows the whole structure of this invention. It is a cross-sectional view showing the configuration of each orifice and the third liquid chamber constituting the main part of the present invention, and is a cross-sectional view taken along the line AA of FIG. It is a figure (graph) which shows the damping characteristic with respect to idling vibration including the engine rotation 0.5th order vibration in the liquid enclosure type vibration isolator which concerns on this invention. It is a figure (graph) which shows the damping characteristic with respect to an engine idling vibration of the conventional one.

Explanation of symbols

1 Orifice forming member 11 First orifice (first orifice)
115 Main chamber side opening hole 116 Sub chamber side opening hole 12 Second orifice (second orifice)
121 Third liquid chamber side opening hole 126 Sub chamber side opening hole 2 Liquid chamber forming member 22 Second diaphragm (second diaphragm)
23 Third liquid chamber 4 Insulator 44 Peripheral terminal portion 5 Main chamber 6 Sub chamber 7 First diaphragm (first diaphragm)
8 Partition member 88 Flange 91 First connecting member 95 Second connecting member

Claims (2)

A first connecting member attached to the vibrating body, a second connecting member attached to the vehicle body side member, and a vibration between the first connecting member and the second connecting member between the first connecting member and the second connecting member. And a rubber-like insulator for blocking, a main chamber in which a chamber wall is formed by a part of the insulator, and a liquid is sealed, and is connected to the main chamber via a first orifice. And a sub-chamber in which a part of the chamber wall is partitioned by the first diaphragm, a partition member for partitioning the main chamber and the sub-chamber, and a chamber wall by the second diaphragm with respect to the main chamber A liquid-filled type vibration damping device having two orifices, each of which includes a third liquid chamber in which a part of the third liquid chamber is formed, and a second orifice connecting the third liquid chamber and the sub chamber. In the second orifice, the third liquid The first orifice is provided on the outside of the second orifice, and the plan view thereof is provided on the outside of the second orifice. A liquid-filled vibration isolator having a circular arc shape formed by a part of an annular ring. 2. The liquid filled type vibration damping device according to claim 1, wherein both the first orifice and the second orifice exhibit a high damping characteristic with respect to an engine idling vibration input and an engine shake vibration input. A liquid-filled vibration isolator having a structure.

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