JP2010255831A - Vibration control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibration control device for developing a vibration damping function and a low dynamic spring function against idling vibration and engine shaking vibration while reducing a dynamic spring constant with respect to an input of a high frequency and small amplitude vibration such as vehicle-room muffled sound vibration or lockup vibration. <P>SOLUTION: A fluid chamber 5 is partitioned into a main liquid chamber 7 and a sub liquid chamber 8 with a partition member 6. Both the liquid chambers 7, 8 are made to independently communicate with a first restricting passage 9 and a second restricting passage 10, respectively. At the other end of a cylindrical member 2, a negative pressure actuator 12 is provided for displacing a diaphragm 4 between a position of closing an opening end 9a of the first restricting passage 9 and a position of isolating it from the opening end. A sealed air chamber is defined between a diaphragm 4 in its attitude of closing the opening end 9a of the first restricting passage 9 and the negative pressure actuator 12 for thrusting the diaphragm 4 against the position of closing the opening end 9a. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  This invention is based on the flow of incompressible liquid sealed inside, and is an anti-vibration device capable of exerting an excellent vibration damping function regardless of the generated vibration frequency. The present invention relates to an anti-vibration device, and is applied to, for example, an engine mount to effectively attenuate and dampen each of idling vibration and engine shake vibration, as well as a high-frequency small-amplitude vibration of 50 to 150 Hz. The present invention proposes a technique that effectively suppresses an increase in dynamic spring constant (high dynamic spring) with respect to vibration due to booming noise, lock-up vibration, and the like by high-frequency resonance of a spring element or the like, and attenuates it together.

  As a conventional liquid vibration isolator which is applied as an engine mount and switches the flow path of a sealed liquid under the action of a negative pressure actuator, there is one disclosed in Patent Document 1.

As shown in a longitudinal sectional view including the central axis in FIG. 5, the vibration generating side member, for example, the outer peripheral surface of the core member 111 connected to the engine, and the vibration transmitting side member, for example, the cylinder connected to the vehicle body. The inner peripheral surface of the cylindrical member 112 is liquid-tightly connected by an elastic member 113 such as rubber, and the opening end of the cylindrical member 112 is liquid-tightly sealed by the diaphragm 114. The diaphragm 114 and the elastic member 113 are sealed. And, more precisely, a space surrounded by the elastic member lining portion of the cylindrical member 112 is defined as a fluid chamber 115 filled with an incompressible liquid, and the fluid chamber 115 is partitioned. The member 116 is divided into a main liquid chamber 117 located on the elastic member 113 side and a sub liquid chamber 118 located on the diaphragm 114 side, and both the liquid chambers 117 and 1 are separated. 8 exhibits a vibration damping function for the window hole 119 that provides an anti-vibration function for idling vibration that is 20 to 40 Hz mid-frequency medium amplitude vibration, and for engine shake vibration that is 5 to 20 Hz low-frequency large-amplitude vibration. The central portion of the diaphragm 114 is connected to the orifice passage 120 independently of each other by an output member 122 of the negative pressure actuator 121 disposed on the opposite side of the diaphragm 114 from the main liquid chamber 117. 123 is pressed against the opening peripheral edge of the window hole 119 of the partition member 116 so that the window hole 119 is held in a closed state, and a recess 124 communicating with the atmosphere is formed on the front end surface of the output member 122. , Allowing elastic deformation of the diaphragm 114 into the recess 124 and the bottom of the diaphragm 114 to the bottom surface of the recess 124. It is intended to limit the elastic deformation of the diaphragm 114 by contact, to open or close a window hole 119 by the operation of the negative pressure actuator 121.

  This liquid vibration isolator is applied to an engine mount, with the core member 111 connected to the engine and the cylindrical member 112 connected to the vehicle body, respectively, and idling vibration from the engine, That is, when the medium frequency medium amplitude vibration is input, the output member 122 is displaced downward in the drawing by the operation of the negative pressure actuator 121, so that the central portion 123 of the diaphragm 114 is moved to the window hole 119 of the partition member 116. The main liquid chamber 117 and the sub liquid chamber 118 communicate with each other through the window hole 119 while being separated from the peripheral edge. Under this communication state, the partition between the main liquid chamber 117 and the sub liquid chamber 118 is released, and both the liquid chambers 117, 118 become substantially one fluid chamber 115, and the elastic member 113 is elastic. Since the pressure fluctuation of the fluid chamber 115 based on the deformation is absorbed by the elastic deformation of the diaphragm 114, an effective anti-vibration effect (vibration insulation effect based on low dynamic spring characteristics) is exhibited against idling vibration. It can be done.

  On the other hand, with respect to the input of engine shake vibration, which is low-frequency large-amplitude vibration when the vehicle is running, by introducing atmospheric pressure into the negative pressure actuator 121, as shown in FIG. The central portion 123 is pressed against the opening peripheral edge of the window hole 119 under the action of the built-in pulling to close the window hole 119, so that the engine shake vibration is input and the respective liquid chambers 117 and 118 are in the closed state. The liquid flows through the orifice passage 120. In this case, an excellent vibration damping effect is exhibited based on the resonance action, flow resistance, and the like of the liquid flowing through the orifice passage 120.

  Further, when high-frequency small-amplitude vibrations such as vehicle interior noise and lock-up vibration are input when the vehicle is running, the window hole 119 is closed at the central portion 123 of the diaphragm 114 as described above. The central portion 123 of the diaphragm 114 is elastically deformed without contacting the bottom surface of the recess 124 within the recess 124 communicating with the atmosphere under a small pressure fluctuation in the main liquid chamber 115. The diaphragm 114 absorbs the pressure fluctuation in the main liquid chamber 115, thereby exhibiting a good vibration isolation effect (vibration insulation effect based on the low dynamic spring characteristic) against high frequency small amplitude vibration.

JP 2008-121811 A

  However, in the above disclosed technique, the window hole 119 as a through hole is formed in the central portion of the partition member 116 made of a thin disk-shaped member, and the window hole 119 itself is a substantial liquid storage. Since it does not have a volume, it cannot perform actions such as liquid column resonance inherent to the enclosed liquid for medium-frequency medium amplitude vibration input such as idling vibration, and furthermore, resonance vibration of the spring element. Because it is not possible to reduce the spring constant of the device, it is not only possible to exhibit an excellent vibration insulation function for medium-frequency amplitude vibrations, but also cannot exhibit a vibration damping function. There is a problem that the increase in the dynamic spring constant cannot be denied, and there is a problem that the damping of the vibration is delayed, and the output member 12 for high frequency small amplitude vibration input of 50 to 150 Hz. Since the recess 124 formed in the front end surface of the spring is communicated with the atmosphere via the plurality of communication grooves 125, the spring element cannot resonate under the hard spring characteristic, and the vibration of the frequency Therefore, in the above disclosed technique, an increase in the dynamic spring constant inherent to the apparatus at high frequency vibration input is also unavoidable. There was a problem that could not bring.

  The present invention has an object to solve the above-described problems of the disclosed technology, and an object of the present invention is to provide a sealed liquid for both idling vibration and engine shake vibration. In addition to exerting a vibration damping function based on liquid column resonance, etc., it is possible to bring about a low dynamic spring. On the other hand, by resonating the spring element under the spring characteristics of the required hardness, the vibration is attenuated and the resonance frequency and the dynamic spring constant in the vicinity of the resonance frequency are effectively reduced. It is in providing the vibration isolator which can do.

The vibration isolator of the present invention includes a core member connected to one side of the vibration generation side member or the vibration transmission side member and a cylindrical member connected to the other side, and an outer peripheral surface of the core member And connecting one end portion inner peripheral surface of the cylindrical member in a liquid-tight manner over the entire circumference by an elastic member made of a rubber material or the like, and sealing the other end of the cylindrical member in a liquid-tight manner with a diaphragm, The space surrounded by the diaphragm and the cylindrical member and the elastic member that may be lined by the elastic member, and sometimes the core member that may be exposed from the elastic member, is incompressible. For example, a fluid chamber in which a liquid such as water, alkylene glycol, polyalkylene glycol, or silicone oil is sealed is formed. The main liquid chamber located on the side and the secondary liquid chamber located on the diaphragm side are divided into the first restriction passage that causes the idling vibration to be attenuated, and the engine shake vibration is attenuated. In each of the second restriction passages to be brought into communication with each other, the diaphragm is disposed on the other end side of the tubular member, the opening end of the first restriction passage is closed, and the first restriction passage. A negative pressure actuator is provided for displacement between a position spaced from the open end of the passage;
An airtight air chamber is defined between a diaphragm in a posture in which the opening end of the first restriction passage is closed and a negative pressure actuator that presses the diaphragm toward the closing position of the opening end.

  In this case, the airtight air chamber is a pinhole that is closed during the operation of the airtight air chamber, which will be described later, for balancing the airtight air chamber pressure with the external air pressure against atmospheric pressure fluctuation, temperature fluctuation, etc. It is also possible to provide a small hole of a degree.

  Preferably, the hermetic chamber portion of the negative pressure actuator that contributes to the compartment of the hermetic air chamber is configured by a rigid member having no volume change.

  Also preferably, the diaphragm is convexly supported on the negative pressure actuator side or the opposite side in the actuator surrounding area of the diaphragm which is pressed and supported by the negative pressure actuator under the closed posture of the first restriction passage. In addition, a slack portion that can be a molded portion is provided to facilitate realization of required spring characteristics.

  By the way, each of the hermetic chamber portion and the diaphragm pressing portion of the negative pressure actuator is formed integrally with each other, or is configured by a mutually integrated rigid member formed by fixing or fixing a separate object. The periphery of the integrated portion can be hermetically connected to the housing via a flexible film body that allows an elastic film body, and the flexible film body is attached to the negative pressure actuator as the negative pressure is introduced. The integral member can be displaced away from the first restricting passage with excellent sensitivity, and conversely, with the introduction of atmospheric pressure into the actuator, the integral member is For example, it can be smoothly displaced toward the first restricting passage under the action of the spring means.

  In addition, in the negative pressure actuator, a spring means that constantly generates a pressing force in a direction in which the diaphragm closes the opening end of the first restriction passage, that is, a return spring can be provided. The actuator structure can be made simple enough, as well as quickly operating the negative pressure actuator as expected.

アイドル周波数をｆ_１（ダイアフラム全体のばね定数をＫ_１）に対して、共振周波数を３倍（３ｆ_１）にしたいときは、アクチュエータ囲繞域のばね定数を９Ｋ_１とすることで、所要の共振周波数を実現することができる。 Preferably, the spring constant in the direction of the central axis of the first restricting passage in the actuator surrounding area of the diaphragm supported by the negative pressure actuator in the closed posture of the opening end of the first restricting passage of the diaphragm, Increased the resonance frequency of the diaphragm's actuator surrounding area in the closed state of the open end of the first restriction passage by the diaphragm as needed, by making it larger than the same spring constant of the entire diaphragm, as expected. The resonance of the actuator surrounding area in the high frequency range can be realized.

When the resonance frequency is to be tripled (3f ₁ ) with respect to the idle frequency f ₁ (the spring constant of the entire diaphragm is K ₁ ), the required resonance can be achieved by setting the spring constant of the actuator surrounding area to 9K _1. A frequency can be realized.

  Here, since the spring hardness of the diaphragm is determined by the distance between the diaphragm in a posture in which the opening end of the first restriction passage is closed and the bottom of the airtight air chamber, the spring hardness is determined by the hardness of the rubber. The amount of air in the airtight air chamber can be appropriately controlled.

  In the apparatus as described above, when the diaphragm and the negative pressure actuator are integrally formed, the diaphragm is separated from the opening end by closing the opening end of the first restriction passage by the action of the negative pressure actuator. The diaphragm can be directly displaced to the position where the diaphragm is to be closed, and the opening end closing posture and the separation posture from the opening end of the diaphragm can always be constant.

  Further, when the negative pressure actuator is connected to the diaphragm at the diaphragm pressing portion made of a rigid member of the negative pressure actuator, the opening end of the first restriction passage is closed as expected by the diaphragm, and The required separation of the diaphragm from its open end can be further ensured.

In the vibration isolator of the present invention, it is applied as an engine mount. For example, in a state where the core member is connected to the engine side member and the cylindrical member is connected to the vehicle body side member, For input of idling vibration (medium frequency (20 to 40 Hz), medium amplitude (0.05 to 0.2 mm) vibration), the negative pressure actuator is operated to move the diaphragm from the opening end of the first restriction passage. The first restriction passage is tuned by allowing the respective liquids in the main liquid chamber and the sub liquid chamber to flow under a free deformation of the diaphragm through the first restriction passage having a sufficient volume. The idling vibration can be effectively damped based on the liquid column resonance, flow resistance, etc. of the liquid in the passage at the frequency.
In addition, the idling vibration can be effectively reduced to a low dynamic spring even for the vehicle body side member at least at the resonance frequency and in the vicinity thereof based mainly on the resonance of the entire diaphragm.

On the other hand, atmospheric pressure is introduced into the negative pressure actuator for the input of 5 to 20 Hz engine shake vibration (vibration with low frequency and large amplitude (0.5 to 1 mm)) during vehicle travel. Then, under the action of the built-in spring means, with the pressing portion of the negative pressure actuator, the diaphragm is pressed and supported around the opening end of the first restricting passage, and the opening end is substantially closed. By preventing the flow of liquid through one restricting passage and allowing the liquid in both chambers to flow through the second restricting passage, also under the free deformation of the outer part of the diaphragm actuator enclosure. Based on the liquid column resonance of the liquid in the passage at the tuning frequency of the second restriction passage, the engine shake vibration can be effectively damped and the dynamic spring can be reduced.
The second restriction passage is in a so-called clogged state with respect to vibrations having a higher frequency (20 to 40 Hz) such as idling vibrations, and allows the flow of liquid in each liquid chamber. It will be in an unobtainable state.

  In addition, in this vibration isolator, a diaphragm is provided for a vibration input having a high frequency (50 to 150 Hz) and a small amplitude such as a vibration of a vehicle interior noise during driving of the vehicle and a vibration during lock-up. The open end is closed in the same manner as described above, and under this state, the diaphragm is pressed and supported by the negative pressure actuator toward the first restricting passage, so that the surface area of the actuator surrounding area of the diaphragm becomes the entire diaphragm. Due to the smaller surface area, the spring constant of the diaphragm itself in the direction of the central axis of the first restricting passage is larger in the small area than in the large area, and the actuator surrounding area of the diaphragm A hermetic air chamber partitioned from the negative pressure actuator assists in increasing the spring constant, and the diaphragm Based on the fact that the actuator surrounding area has a harder spring characteristic, the actuator surrounding area of the diaphragm is tuned so as to resonate in this high frequency range (50 to 150 Hz), so that the movement in the vicinity of the tuning frequency can be achieved. The spring constant can be effectively reduced, and as a result, it is possible to realize a sufficiently low dynamic spring against the vibration of the vehicle interior noise and the vibration at the time of lockup, effectively isolating high-frequency vibration from the vehicle body. can do.

  In this case, the airtight air chamber has a small hole, such as a pinhole, for balancing the pressure in the airtight air chamber with the external pressure with respect to atmospheric pressure fluctuation, for example, temperature fluctuation of about −30 ° C. to 100 ° C. However, when the diaphragm actuator surrounding area resonates in the axial direction of the first restricting passage, one or a plurality of through-holes are substantially closed, so the airtight air pressure is reduced. Compared to the outside air pressure, the pressure can be increased or reduced as expected.

  Here, when the airtight chamber part that contributes to the compartment of the airtight air chamber of the negative pressure actuator is configured with a rigid member, the possibility of the volume change of the airtight air chamber is removed, and the internal pressure of the airtight air chamber is required. The realization of the pressure increase / decrease can be simplified.

  In addition, the diaphragm is pressed and supported by the negative pressure actuator under the closing posture of the first restriction passage, and the negative pressure actuator side or the opposite side is convex in the actuator surrounding area of the diaphragm. When a slack part that can be processed is provided, vibration change in the actuator actuator area of the diaphragm is facilitated, and tuning of the resonance frequency of the enclosure area is simplified as required, and the required spring is specified. It can be realized quickly.

  Then, each of the hermetic chamber portion and the diaphragm pressing portion of the negative pressure actuator is configured by a rigid member integrated with each other in advance or afterwards, and the periphery of the integrated portion is an elastic film body. When airtightly connected to the housing via a flexible membrane body, the integrated part of the negative pressure actuator can be displaced quickly and smoothly as expected under the deformation of the flexible membrane body. In addition, it is possible to always ensure the closing of the opening end of the first restricting passage with the diaphragm pressing portion, and it is possible to always change the airtight chamber portion having a constant volume integrally with the diaphragm pressing portion.

  By the way, when the spring means for constantly generating the pressing force in the direction in which the diaphragm closes the opening end of the first restriction passage is disposed in the negative pressure actuator, the negative pressure actuator having a simple and simple structure is provided. The operation as expected can always be performed reliably.

  In addition, the spring constant in the central axis direction of the first restriction passage in the actuator surrounding area of the diaphragm supported by the negative pressure actuator in the closed posture of the opening end of the first restriction passage of the diaphragm By increasing the resonance frequency of the diaphragm actuator surrounding area itself in the diaphragm posture that closes the open end of the restriction passage, if necessary, by increasing the resonance frequency of the vibration isolator, It is possible to reduce the dynamic spring as expected at the resonance frequency and the vicinity thereof.

  Here, when the diaphragm in a posture in which the opening end of the first restriction passage is closed and the rigidity of the airtight air chamber are combined, the deformation of the actuator surrounding area of the diaphragm is facilitated, and the volume of the airtight air chamber is In this connection, the pressure increase / decrease of the hermetic air chamber pressure and the spring constant of the actuator surrounding area of the diaphragm can be sufficiently effective to realize the required resonance frequency.

  Here, when the diaphragm and the negative pressure actuator are integrally formed, the deformation and displacement of the diaphragm can be interlocked with the operation of the airtight chamber portion and the diaphragm pressing portion as the operation portion of the negative pressure actuator. Thus, the opening end of the first restricting passage of the diaphragm and the separation from the opening end can always be ensured, and at the same time, both the postures thereof can be always constant.

  By the way, when the diaphragm and the negative pressure actuator are integrally formed in this way, when the negative pressure actuator is connected to the diaphragm at the diaphragm pressing portion made of a rigid member of the negative pressure actuator, the diaphragm as described above. It is possible to further ensure the closing and separation, and the stabilization of each posture.

It is a longitudinal section showing a central axis showing one embodiment of this invention. It is a longitudinal cross-sectional view which shows the apparatus shown in FIG. 1 by damping postures, such as an engine shake vibration and a vehicle interior sounding vibration. It is a graph which illustrates typically low dynamic spring formation of idling vibration and booming sound vibration. It is a longitudinal cross-sectional view similar to FIG. 1 which shows other embodiment. It is the same longitudinal cross-sectional view as FIG. 1 which shows a prior art.

  In the first embodiment of the vibration isolator of the present invention, as shown in FIG. 1, a core member 1 connected to either one of a vibration generating side member of an engine and other members or a vibration transmitting side member of an automobile body or the like. And each of the cylindrical members 2 connected to the other side is provided, and the outer peripheral surface of these core members 1 and the inner peripheral surface of one end portion of the cylindrical member 2, in the figure, an inverted truncated cone shape or The inner peripheral surface having an inverted truncated pyramid shape is liquid-tightly connected to the entire circumference by an elastic member 3 made of rubber, elastomer, plastic or the like, and the other end of the cylindrical member 2 is liquid-tightly sealed by a diaphragm 4. To do.

  In the figure, the elastic member 3 is used to line up to the lower end edge of the equal-diameter portion 2a of the cylindrical member 2, but this lining by the elastic member 3 is not essential.

  Here, at least a space surrounded by the diaphragm and the cylindrical member 2 including the lining of the elastic member 3 and the elastic member 3, sometimes in addition to the space surrounded by the core member 1 exposed from the elastic member 3. The space to be formed is a fluid chamber 5 in which a required incompressible liquid is enclosed, and this fluid chamber 5 is divided into a main liquid chamber 7 located on the elastic member 3 side and a diaphragm 4 side by a partition member 6. The auxiliary liquid chamber 8 is divided into two liquid chambers 7 and 8, which are provided in the partitioning member 6 in the drawing, and a first restriction passage 9 that attenuates idle vibration and engine shake vibration. In general, the second restriction passages 10 that cause attenuation and have a smaller cross-sectional area and a longer length than the restriction passage 9 are communicated independently of each other.

  Here, the second restriction passage 10 opens to the main liquid chamber 7 through a wall through hole (not shown) provided at one end, and opens to the sub liquid chamber 8 through a wall through hole (not shown) provided at the other end. To do.

  And the other end side of the cylindrical member 2 is accommodated in the housing 11, and the diaphragm 4 is closed at the position where the opening end 9a of the first restricting passage 9 on the side of the secondary liquid chamber 8 is closed. Thus, a negative pressure actuator 12 is provided that is displaced from a position away from the opening end 9a, and the diaphragm in a posture in which the opening end 9a of the first restriction passage 9 is closed as illustrated in FIG. 4 and an airtight air chamber 13 is defined between the diaphragm 4 and the negative pressure actuator 12 that presses the diaphragm 4 toward the first restriction passage 9 at the closed position of the opening end 9a.

1 and 2, at the lower end portion of the cylindrical member 2, a partition wall portion 10a of a restriction passage 10 provided in the partition member 6, an annular member 4a obtained by vulcanizing and bonding the diaphragm 4, etc. The upper end portion 11a of the negative pressure actuator housing 11 is integrally caulked and fixed, but this is not an essential configuration for the present invention.
In addition, here, the flexible film body 15 that can be an elastic film body that is airtightly connected to the periphery of the airtight chamber portion 14a and the diaphragm pressing portion 14b of the negative pressure actuator 12 and is configured to be integrated with a rigid material. Is fixed by caulking to the inner peripheral surface of the equal-diameter barrel portion of the housing 11 via a rigid cylinder 15a that is air-tightly connected to the outer periphery thereof by vulcanization bonding or the like. This is not an essential configuration.

On the other hand, the space defined between the diaphragm 4 and the negative pressure actuator 12 communicates with the atmosphere so as to ensure free and smooth displacement and deformation of the diaphragm 4 and the flexible film body 15. is required.
In addition, the airtight chamber portion 14a has an air pressure inside the airtight air chamber 13 when the airtight air chamber 13 is partitioned in cooperation with the diaphragm 4 without being affected by temperature change, pressure change, or the like. It is preferable to provide a through hole such as a pinhole so that the air hole 13 is closed when the airtight air chamber 13 is in a pressure-increasing / decreasing state. It must be of small dimensions.

Further, the negative pressure actuator 12 is connected to a negative pressure chamber 16 inside the negative pressure chamber 16 via a valve 17 and is connected to a negative pressure supply source (not shown). A spring means 18, which can be a coil spring, for example, is disposed on the bottom wall and each of the integrated structures of the hermetic chamber portion 14 a and the diaphragm pressing portion 14 b.
This spring means 18 as a return spring functions so as to always generate a pressing force in such a direction that the diaphragm 4 closes the opening end 9 a of the first restriction passage 9.

In the apparatus as described above, the hermetic chamber portion 14a that contributes to the section of the hermetic air chamber 13 of the negative pressure actuator 12 is preferably composed of a rigid member, as described above, and preferably a diaphragm. The diaphragm pressing portion 14b of the negative pressure actuator 12 that presses and supports the diaphragm 4 at the closed position of the opening end 9a is formed of a rigid member that presses the diaphragm 4 around the opening end 9a, and more preferably. The rigid member hermetic chamber portion 14a and the rigid member diaphragm pressing portion 14b are integrally configured as described above.
In this integration, as shown in FIGS. 1 and 2, in addition to the case where both parts 14a and 14b are integrally formed, both parts 14a and 14b formed separately are integrated by required dimming. It shall include cases where it is fixed or fixed.

  Preferably, the diaphragm 4 is pressed and supported by the negative pressure actuator 12 under the closed posture of the opening end 9a of the first restriction passage 9 in the actuator surrounding area 4b as shown in FIG. In addition, a slack portion, which can be a molded portion that is convex toward the negative pressure actuator 12 side or the opposite side, is formed.

  Here, the spring constant of the diaphragm 4 in the central axis direction of the restriction passage 9 of the actuator surrounding region 4b under the closed posture of the opening end 9a is, for example, similar to the spring constant of the entire diaphragm. When the required resonance frequency is 3 times, the spring constant is increased 9 times.

  In the case where the vibration isolator configured as described above is applied as an engine mount for an automobile, for example, the core member 1 is disposed on the engine side for the automobile, and the tubular member 2 is disposed on the vehicle body side. Under each connected state, when idling vibration when the vehicle is stopped is input thereto, the negative pressure actuator 12 is operated to introduce negative pressure from the negative pressure supply source into the negative pressure chamber 16, The negative pressure chamber pressure is resisted against the spring force of the spring means 18, and the integrated structure of the airtight chamber portion 14 a and the diaphragm pressing portion 14 b is shown in FIG. Displace downward.

  As a result, the diaphragm 4 is displaced away from the open end 9a of the first restricting passage 9 as shown in FIG. 1 based on the weight of the liquid itself and the internal sealing liquid. Under vibration, the liquid in the main and sub liquid chambers 7 and 8 flows from the high pressure side to the low pressure side through the restriction passage 9, and as a result, the first restriction passage having a predetermined volume. In FIG. 9, effective damping of idling vibration is performed based on the occurrence of flow resistance, liquid column resonance at a predetermined frequency, and the like.

  Note that this idling vibration is also effectively prevented from vibration against the vehicle body based on the resonance of the entire diaphragm in addition to the elastic elastic deformation of the elastic member 3 in the vertical direction in the figure. When the resonance frequency of the entire 4 is set to 30 Hz, the vertical dynamic spring constant of the entire apparatus is greatly reduced at the frequency of 30 Hz and its vicinity as illustrated by the solid line in FIG.

  On the other hand, in response to the input of the engine shake vibration when the vehicle is running, atmospheric pressure is introduced into the negative pressure chamber 16 of the negative pressure actuator 12, and the air chamber portion 14a and the diaphragm 14b of the actuator 12 are connected. The unitary structure is displaced upward relative to the first restricting passage 9 under the action of the built-in spring means 18.

As a result, the rigid member pressing portion 14b of the negative pressure actuator 12 presses and supports the diaphragm 4 around the opening end 9a of the first restricting passage 9, for example, around the opening end flange, as shown in FIG. Then, the opening end 9 a is substantially closed with the diaphragm 4.
Under this state, the flow of the liquid in the main and sub liquid chambers 7 and 8 through the restriction passage 9 is prevented, so that the liquid in both the liquid chambers 7 and 8 Under the free deformation of the outer portion of the actuator surrounding area 4b, the fluid flows from the high pressure side to the low pressure side through the second restriction passage 10, and the inside of the passage at the tuning frequency of the second restriction passage 10 is obtained. The engine shake vibration can be effectively damped based on the liquid column resonance and flow resistance of the liquid.
By the way, the second restriction passage 10 is in a so-called clogged state with respect to vibrations at a higher frequency than engine shake vibrations (5 to 20 Hz) such as idling vibrations (20 to 40 Hz). The flow of the liquid in 7, 8 is prevented from flowing through the restriction passage 10.

Further, for the input of high frequency small amplitude vibration of 50 to 150 Hz, such as vehicle interior noise during lock-up, vibration during lockup, etc., the first effect of the diaphragm 4 as shown in FIG. While maintaining the closed state of the open end 9a of the restriction passage 9, the actuator 4b of the diaphragm 4 and, in particular, the vibration of the slack portion is caused, and the actuator 4b itself has a high spring constant, and the actuator of the diaphragm 4 Due to the further increase of the spring constant based on the action of the hermetic air chamber 13 defined between the surrounding area 4b and the negative pressure actuator 12, the actuator surrounding area 4b provides a hard spring characteristic, and the actuator area of the diaphragm 4 By tuning so that 4b resonates in the high frequency range, the resonance frequency and The dynamic spring constant of the device in the vicinity of the frequency of the vehicle can be reduced as shown by the broken line in FIG. 3, and therefore, the dynamic spring constant for the vehicle booming sound vibration and the like is more effectively reduced. Therefore, it is possible to effectively prevent the occurrence of a cabin noise and the occurrence of shock vibration at the time of lock-up.
In this case also, vibration is attenuated based on resonance in liquid.

  FIG. 4 is a longitudinal sectional view including a central axis showing another embodiment of the present invention. In particular, the diaphragm 4 and the negative pressure actuator 12 are integrally formed so that the diaphragm 4 is deformed and displaced. Is configured to directly follow the operation of the negative pressure actuator 12, and the configuration of the other parts is such that the housing 11 is circumscribed by the flanged cup-shaped inner member 11b and the body of the cup-shaped inner member 11a. Except for the point constituted by the outer member 11c, it is almost the same as described above.

  As shown in this figure, the rigid material hermetic chamber portion 14 a that mainly contributes to the section of the hermetic air chamber 13 of the negative pressure actuator 12, and the diaphragm 4 are mainly connected to the opening end 9 a of the first restricting passage 9. The rigid material diaphragm pressing portion 14b that functions to be pressed and supported at the closed position is an integrated member that is fixed or fixed afterwards, and the lower end flange portion of the rigid material diaphragm pressing portion 14b in the drawing is allowed. The upper end flange portion of the drawing is connected to the flexure body 15 in an airtight manner over the entire circumference, and the diaphragm 4 and the negative pressure actuator 12 are connected to the diaphragm 4 in an airtight manner by vulcanization or the like. Integration is realized.

Further, here, a slack portion having a convex shape on the opposite side to the negative pressure actuator 12 is provided in the actuator surrounding area 4b of the diaphragm 4, so that the vibration displacement of the actuator surrounding area 4b is facilitated.
According to this integrated structure of the diaphragm 4 shown in the figure, the thickness in the actuator surrounding area 4b can be easily increased with respect to the thickness outside the actuator surrounding area 4b. The resonance frequency can be easily tuned to a required frequency on the high frequency side.

  The anti-vibration device configured as described above is applied to each of the idling vibration, engine shake vibration, vehicle interior noise vibration, and lock-up vibration when applied as an engine mount for an automobile. It can function in the same manner as the devices shown in FIGS. 1 and 2, exhibits the vibration damping function as described above, and can bring about a dynamic spring constant reduction characteristic.

DESCRIPTION OF SYMBOLS 1 Core member 2 Cylindrical member 2a Equal-diameter part 3 Elastic member 4 Diaphragm 4a Annular member 4b Actuator surrounding area 5 Fluid chamber 6 Partition member 7 Main liquid chamber 8 Sub-liquid chamber 9 First restriction passage 9a Open end 10 Second Restriction passage 10a Partition wall portion 11 Housing 11a Upper end portion 11b Cup-shaped inner member 11c Outer member 12 Negative pressure actuator 13 Airtight air chamber 14a Airtight chamber portion 14b Diaphragm pressing portion 15a Rigid cylindrical body 16 Negative pressure chamber 17 Valve 18 Spring means

Claims (10)

A core member connected to either one of the vibration generation side member or the vibration transmission side member and a cylindrical member connected to the other side are provided, and the outer peripheral surface of the core member and one end of the cylindrical member are provided. The partial inner peripheral surface is liquid-tightly connected to the entire circumference by an elastic member, and the other end of the cylindrical member is liquid-tightly sealed by a diaphragm. At least the diaphragm, the cylindrical member, and the elastic member The enclosed space is a fluid chamber filled with liquid, and the fluid chamber is partitioned by a partition member into a main liquid chamber located on the elastic member side and a sub liquid chamber located on the diaphragm side. The liquid chambers are communicated independently of each other in the first restriction passage that attenuates the idling vibration and the second restriction passage that attenuates the engine shake vibration, and the other end of the cylindrical member To, the diaphragm, and a position to close the open end of the first restricting passage, the negative pressure actuator for displacing over between a position away from the open end of the first restricting passage is provided,
An anti-vibration device in which an airtight air chamber is defined between a diaphragm in a posture in which the opening end of the first restriction passage is closed and a negative pressure actuator that presses the diaphragm to a closing position of the opening end.   The vibration isolator according to claim 1, wherein the airtight chamber portion of the negative pressure actuator that contributes to the compartment of the airtight air chamber is configured by a rigid member.   A slack that protrudes to the negative pressure actuator side or the opposite side in the actuator surrounding area of the diaphragm that is pressed and supported by the negative pressure actuator under the closed posture of the opening end of the first restriction passage of the diaphragm The vibration isolator according to claim 1 or 2, further comprising a portion.   The diaphragm pressing portion of the negative pressure actuator that presses and supports the diaphragm at the closed position of the opening end of the first restriction passage is configured by a rigid member that presses the diaphragm all around the opening end. The vibration isolator in any one of Claims 1-3.   Each of the hermetic chamber portion and the diaphragm pressing portion of the negative pressure actuator is configured by a rigid member integrated with each other, and the integrated portion is hermetically connected to the housing via the flexible film body. The vibration isolator according to any one of claims 1 to 4.   The vibration isolator according to any one of claims 1 to 5, wherein spring means for constantly generating a pressing force in a direction in which the diaphragm closes the opening end of the first restriction passage is disposed in the negative pressure actuator.   The spring constant in the central axial direction of the first restricting passage in the actuator surrounding area of the diaphragm supported by the negative pressure actuator in the closed posture of the opening end of the first restricting passage of the diaphragm is the same as the whole diaphragm. The vibration isolator according to any one of claims 1 to 6, wherein the vibration isolator is larger than the spring constant.   The vibration isolator according to any one of claims 1 to 7, wherein the diaphragm in a posture in which the opening end of the first restriction passage is closed and the rigidity of the airtight air chamber are combined.   The vibration isolator according to any one of claims 1 to 8, wherein the diaphragm and the negative pressure actuator are integrally formed.   The vibration isolator according to any one of claims 4 to 9, wherein the negative pressure actuator is connected to the diaphragm at a diaphragm pressing portion made of a rigid member of the negative pressure actuator.

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