JP7269146B2 - Fluid-filled anti-vibration device - Google Patents

Description

The present invention relates to a fluid-filled vibration damping device used for an automobile engine mount or the like.

2. Description of the Related Art Conventionally, self-switching fluid-filled vibration damping devices that automatically switch vibration damping characteristics according to input vibration are known as fluid-filled vibration damping devices used for automobile engine mounts and the like. A self-switching fluid-filled vibration damping device is disclosed, for example, in Japanese Patent Application Laid-Open No. 2004-069005 (Patent Document 1). Specifically, the partition wall that separates the pressure receiving chamber and the equilibrium chamber has a through hole that communicates the pressure receiving chamber and the equilibrium chamber with each other, and has a structure in which a movable plate is arranged on the flow path of the through hole. . When low-frequency, large-amplitude vibration is input, the through-hole is closed by the movable plate, and relative internal pressure fluctuations between the pressure-receiving chamber and the equilibrium chamber are effectively generated. The pressure receiving chamber and the equilibrium chamber are communicated with each other through a gap between the portion and the partition wall, thereby avoiding a high dynamic spring.

By the way, in the movable plate structure such as the fluid-filled vibration damping device described in Patent Literature 1, there is a case where the impact sound caused by the impact of the movable plate against the partition wall becomes a problem. Therefore, the applicant of the present application has proposed a structure in which the hammering sound at the time of characteristic switching is reduced in Japanese Patent Application Laid-Open No. 2012-241842 (Patent Document 2). That is, a second orifice passage is formed in a partition member that separates the pressure receiving chamber and the equilibrium chamber, and is disposed on the second orifice passage, and the relative pressure fluctuations of the pressure receiving chamber and the equilibrium chamber oscillate. The switching portion of the tilting elastic movable body abuts against the inner surface of the wall of the second orifice passage to switch communication and blocking of the second orifice passage. According to this, since the direction of contact between the switching portion and the partition member is different from the direction in which the hydraulic pressure acts, the impact force caused by the contact of the switching portion with the partition member is reduced, and the generation of hammering noise is prevented. be.

Japanese Patent Application Laid-Open No. 2004-069005 JP 2012-241842 A

However, in the fluid-filled vibration damping device described in Patent Document 2, when the input vibration is large, it is assumed that the flow restriction of the fluid due to the contact of the switching portion with the partition member becomes insufficient. That is, since the contact surfaces of the switching portion and the partition member are substantially parallel to the direction in which the hydraulic pressure acts on the switching portion, when a large hydraulic pressure acts on the switching portion, the contact portion of the switching portion with the partition member This is because it is thought that the switching portion may slip and unintentionally separate from the partition member.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a fluid-filled vibration damping device with a novel structure in which characteristics can be switched with high reliability and abnormal noise can be prevented when the characteristics are switched.

Hereinafter, preferred embodiments for understanding the present invention will be described. can be recognized and employed as independently as possible, and can also be employed in combination with any of the components described in other aspects as appropriate. Accordingly, the present invention can be implemented in various alternatives without being limited to the embodiments described below.

In the first mode, a main liquid chamber and a sub-liquid chamber each containing an incompressible fluid are formed on both sides of a partition member, and a communication passage is provided for communicating the main liquid chamber and the sub-liquid chamber with each other. In the formed fluid-filled vibration damping device, the elastic movable body arranged in the partition member is supported by a support portion supported by the partition member, and in a direction crossing the flow channel length direction of the communication flow channel. a valve portion protruding from the portion and disposed on the communication flow path, and the inner wall surface of the communication flow path is provided with a displacement of the valve portion in the flow path length direction of the communication flow path. Abutment surfaces that contact the valve portion are provided on both sides of the communication flow path in the flow path length direction with respect to the valve portion, and the contact surfaces are inclined with respect to the flow path length direction of the communication flow path. A contact reaction force between the valve portion and the corresponding contact surface acts in the direction of compressing the valve portion toward the support portion.

According to the fluid-filled vibration damping device constructed according to this aspect, for example, when a small-amplitude vibration is input, the valve portion is slightly deformed according to the internal pressure fluctuation, and the fluid flow through the communication flow path causes Anti-vibration effect is exhibited. In response to the input of large-amplitude vibration, the valve portion of the elastic movable body is largely elastically deformed by the action of the hydraulic pressure and comes into contact with the contact surface of the partition member, thereby blocking the communication flow path and Fluctuations in the internal pressure of the liquid chamber are efficiently induced.

When the valve portion comes into contact with the contact surface, the valve portion is compressed toward the support portion by the contact reaction force. displacement with deformation of Therefore, the valve portion is stably held in contact with the contact surface, and stable blocking of the communication channel by the valve portion is realized. In particular, since the contact surface is inclined with respect to the flow path length direction of the communication flow path, which is the direction in which the hydraulic pressure acts on the valve section, the displacement of the valve section in the flow path length direction of the communication flow path is large. As the pressure increases, the force for pressing the valve portion against the contact surface increases, and the amount of compressive deformation of the valve portion increases, thereby stiffening the spring of the valve portion. Therefore, even when the amplitude of the input vibration is large and the amount of displacement of the valve portion is large, the valve portion is stably held in contact with the contact surface, thereby avoiding unintended communication of the communication passage.

A second aspect is the fluid-filled vibration damping device according to the first aspect, wherein the protruding tip surface of the valve portion including the contact portion with the contact surface is a curved convex surface, and the corresponding The tangent surface is a curved concave surface.

According to the fluid-filled vibration damping device constructed according to this aspect, the contact surface of the partition member is a curved concave surface. The angle of inclination of the contact surface with respect to the direction of action of (flow path length direction of the communication flow path) increases. Therefore, as the amount of displacement of the valve portion increases, the force that presses the valve portion against the contact surface increases, making it difficult to release the contact state between the valve portion and the contact surface.

Since the protruding tip surface of the valve portion including the contact portion with the contact surface is formed into a curved convex surface, unintended deformation such as stick-slip is less likely to occur in the valve portion, and the deformation mode of the valve portion is stabilized. , a stable operation of the valve portion is realized.

A third aspect is the fluid-filled vibration damping device according to the second aspect, wherein the curvature of the portion of the projecting tip surface of the valve portion that contacts the contact surface of the partition member is equal to the contact surface. is made larger than the curvature of .

According to the fluid-filled vibration damping device constructed according to this aspect, for example, the valve portion is slid along the contact surface due to the action of the hydraulic pressure, so that the valve portion is compressed toward the support portion. Therefore, the contact state of the valve portion with respect to the contact surface is easily maintained. In addition, by reducing the curvature of the contact surface, the component force acting in the direction perpendicular to the contact surface when the valve portion and the contact surface contact becomes small, thereby preventing a striking sound at the time of contact. be.

A fourth aspect is the fluid-filled vibration damping device according to any one of the first to third aspects, wherein the valve portion and the wall inner surface of the communication flow path are separated from each other, and the valve portion and the inner wall surface of the communication channel.

According to the fluid-filled anti-vibration device constructed according to this aspect, for example, when a small-amplitude vibration is input, a fluid flow is generated between the main fluid chamber and the sub-liquid chamber through the communication region, and the fluid-filled anti-vibration device The anti-vibration effect is exhibited by the low dynamic spring of the vibrating device. Moreover, since the valve portion is separated from the inner wall surface of the communication channel in the initial state, the responsiveness of the valve portion to the action of the hydraulic pressure can be improved.

A fifth aspect is the fluid-filled vibration damping device according to any one of the first to fourth aspects, wherein the base end portion of the valve portion connected to the support portion The deformable portion is formed thinner than the support portion in the flow path length direction of the communication flow path.

According to the fluid-filled vibration damping device constructed according to this aspect, the proximal end portion of the valve portion is formed as a thin deformation-allowing portion, so that the displacement of the distal end portion of the valve portion due to the action of the hydraulic pressure causes deformation. It is allowed by elastic deformation of the allowance part. Moreover, the distal end portion of the valve portion abuts against the contact surface and moves toward the support portion, and the deformation permitting portion is compressed between the distal end portion of the valve portion and the support portion, making it difficult for the deformation permitting portion to deform. As a result, separation from the contact surface due to excessive displacement of the distal end portion of the valve portion is prevented, and the blocking state of the communication channel by the valve portion is stably maintained.

A sixth aspect is the fluid-filled vibration damping device according to any one of the first to fifth aspects, wherein the elastic movable body is annular, and the support portion and the valve portion are both It is provided continuously over the entire circumference.

According to the fluid-filled vibration damping device constructed according to this mode, the elastic movable body is stably supported by the partition member because the supporting portion is provided continuously over the entire circumference. In addition, since the valve portion is provided continuously over the entire circumference, it becomes easier to adjust the operating characteristics of the valve portion, for example.

A seventh aspect is the fluid-filled vibration damping device according to any one of the first to sixth aspects, wherein the elastic movable body extends in the circumferential direction, and the valve portion extends from the support portion to the It is provided so as to protrude toward the outer peripheral side of the partition member.

According to the fluid-filled vibration damping device constructed according to this aspect, the communication channel in which the valve portion is arranged can be provided further to the outer peripheral side, and the resonance frequency of the fluid flowing through the communication channel, in other words, the resonance frequency of the fluid flowing through the communication channel If so, it becomes possible to set the tuning frequency of the communication channel with a greater degree of freedom.

Advantageous Effects of Invention According to the present invention, in a fluid filled type vibration damping device, characteristic switching can be realized with high reliability, and abnormal noise at the time of characteristic switching can be prevented.

1 is a longitudinal sectional view showing an engine mount as a first embodiment of the invention; FIG. 2 is a perspective view of a partition member with an elastic movable body that constitutes the engine mount shown in FIG. 1. FIG. Vertical cross-sectional view of the partition member with elastic movable body shown in FIG. The perspective view of the partition member with an elastic movable body shown in FIG. FIG. 3 is a longitudinal cross-sectional view of an elastic movable body that constitutes the engine mount shown in FIG. FIG. 2 is an enlarged vertical cross-sectional view showing a main part of the engine mount shown in FIG. 1, showing an initial state in which no vibration is input; FIG. 2 is an enlarged vertical cross-sectional view showing a main portion of the engine mount shown in FIG. 1, showing a state in which the valve portion deformed by the input of vibration is in contact with the second contact surface; FIG. 2 is an enlarged vertical cross-sectional view showing a main portion of the engine mount shown in FIG. 1, showing a state in which the valve portion in contact with the second contact surface is compressed toward the support portion; FIG. 2 is a vertical cross-sectional view showing essential parts of an engine mount as a second embodiment of the present invention; FIG. 3 is a vertical cross-sectional view showing essential parts of an engine mount as a third embodiment of the present invention;

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the drawings.

FIG. 1 shows an automobile engine mount 10 as a first embodiment of a fluid-filled vibration damping device constructed according to the present invention. The engine mount 10 has a structure in which a first mounting member 12 and a second mounting member 14 are elastically connected by a main rubber elastic body 16 . In the following description, the vertical direction basically means the vertical direction in FIG. 1, which is the direction in which the central axis of the mount extends.

The first mounting member 12 is a member made of metal or the like. The first mounting member 12 has a substantially cylindrical shape as a whole, and is provided with a flange-shaped portion 18 protruding toward the outer periphery at the upper end portion. The first mounting member 12 has a threaded hole 20 that extends linearly in the axial direction on the central axis and opens to the top.

The second mounting member 14 is a member made of metal or the like, similar to the first mounting member 12, and has a thin, large-diameter, substantially cylindrical shape. The second mounting member 14 has a stepped portion in its axially intermediate portion, and the second mounting member 14 has a stepped cylindrical shape in which the upper side of the stepped portion has a larger diameter than the lower side thereof.

The first mounting member 12 and the second mounting member 14 are arranged on substantially the same central axis at axially displaced positions, and are elastically connected to each other by a main rubber elastic body 16 . The main rubber elastic body 16 has a substantially truncated cone shape as a whole, and the first mounting member 12 is fixed to the end on the small diameter side, and the second mounting member 12 is attached to the outer peripheral surface of the end on the large diameter side. , the upper portion of the mounting member 14 is fixed. The main rubber elastic body 16 is formed, for example, as an integrally vulcanized molded product including the first mounting member 12 and the second mounting member 14 .

The main rubber elastic body 16 has a recess 22 that opens to the axial end face on the large diameter side. The recess 22 has an upside-down mortar-shaped upper bottom wall, and the diameter gradually decreases upward. The main rubber elastic body 16 also has a seal rubber layer 24 extending downward from the outer peripheral side of the recess 22 . The seal rubber layer 24 is integrally formed with the main rubber elastic body 16 and fixed to the inner peripheral surface of the lower portion of the second mounting member 14 . The seal rubber layer 24 is made thinner than the peripheral wall of the opening of the recess 22 in the main rubber elastic body 16 . As a result, the opening of the recess 22 is located on the inner peripheral side of the inner peripheral surface of the seal rubber layer 24 , and a step is formed in the main rubber elastic body 16 at the proximal end of the seal rubber layer 24 .

A flexible membrane 26 is attached to the lower portion of the second attachment member 14 . The flexible film 26 is a thin rubber film, and has an annular fixing member 28 fixed to its outer peripheral end. Then, for example, in a state in which the fixing member 28 is inserted into the inner circumference of the second mounting member 14, the diameter of the second mounting member 14 is reduced so that the fixing member 28 is inserted into the second mounting member 14. can be attached to A seal rubber layer 24 is interposed between the second mounting member 14 and the fixing member 28, and the outer peripheral surface of the fixing member 28 is pressed against the inner peripheral surface of the second mounting member 14 via the seal rubber layer 24. Thus, the space between the second mounting member 14 and the fixing member 28 is fluid-tightly sealed.

By attaching the flexible membrane 26 to the second attachment member 14, a fluid chamber 30 fluid-tightly separated from the outside is defined between the main rubber elastic body 16 and the flexible membrane 26. . The fluid chamber 30 contains an incompressible fluid such as water, ethylene glycol, or silicone oil. Although the fluid enclosed in the fluid chamber 30 is not limited to the illustrated one, it is preferably a low-viscosity fluid of 0.1 Pa·s or less, for example.

A partition member 32 is arranged in the fluid chamber 30 . As shown in FIGS. 2 and 3, the partition member 32 has a substantially disk shape as a whole and has a first partition plate 34 and a second partition plate 36 .

The first partition plate 34 is a rigid member made of metal, synthetic resin, or the like, and as shown in FIGS. The first partition plate 34 has an outer peripheral portion cut out in a part of the circumferential direction, and the cutout forms a first communication port 38 constituting an end portion of a first orifice passage 76 to be described later. ing. The outer peripheral portion of the first partition plate 34 is thicker on one side in the circumferential direction of the first communication port 38 than on the other side. It changes smoothly in the circumferential direction.

As shown in FIG. 3, the first partition plate 34 has a radially intermediate portion formed with a first concave groove 40 extending continuously in the circumferential direction while opening to the bottom surface. The first groove 40 has an inner wall surface on the inner peripheral side that widens substantially in the axial direction, and an inner wall surface on the outer peripheral side that extends obliquely with respect to the axial direction as a first contact surface 42 . . The first contact surface 42 is inclined toward the outer periphery toward the opening side of the first groove 40 . The first contact surface 42 may be a flat surface, but is a curved surface in this embodiment, and the inclination angle with respect to the axial direction decreases toward the opening side of the first groove 40 .

A plurality of first through holes 44 are formed in the upper bottom wall portion of the first groove 40 . In this embodiment, the first through holes 44 are slit-shaped long holes extending in the circumferential direction, and three of them are arranged substantially evenly in the circumferential direction.

The second partition plate 36 is a rigid member similar to the first partition plate 34, and has a generally disk shape as a whole. The outer peripheral portion of the second partition plate 36 extends spirally, and a notch opening downward at one end in the circumferential direction forms the end of a first orifice passage 76 to be described later. A communication port 46 is formed.

A second recessed groove 48 is formed in the inner peripheral portion of the second partition plate 36 so as to extend continuously in the circumferential direction while opening to the upper surface. The second recessed groove 48 has an inner wall surface on the inner peripheral side that widens substantially in the axial direction, and an inner wall surface on the outer peripheral side that extends obliquely with respect to the axial direction to form a second contact surface 50. . The second contact surface 50 is inclined toward the outer periphery toward the opening side of the second groove 48 . The second contact surface 50 may be a flat surface, but is a curved surface in this embodiment, and the inclination angle with respect to the axial direction decreases toward the opening side of the second groove 48 .

A plurality of second through holes 52 are formed in the bottom wall portion of the second groove 48 . In this embodiment, the second through-holes 52 are slit-shaped corresponding to the first through-holes 44, and three are provided at positions corresponding to the first through-holes 44 in the partition member 32 in the axial direction. It is

The partition member 32 shown in FIGS. 2 and 3 is constructed by stacking the first partition plate 34 and the second partition plate 36 on each other substantially on the same central axis and fixing them with a plurality of screws 54. be. A circumferential groove 56 is formed in the outer peripheral portion of the partition member 32 and extends spirally in the circumferential direction while opening to the outer peripheral surface.

Between the first partition plate 34 and the second partition plate 36 of the partition member 32, an annular housing area 58 extending in the circumferential direction is formed. The accommodation area 58 is formed by axial opening portions of the first groove 40 and the second groove 48 facing each other in the axial direction. The inner wall surface of the housing area 58 on the outer peripheral side is composed of the first contact surface 42 and the second contact surface 50, and is a curved concave surface that slopes inward and outward in the axial direction. there is The first partition plate 34 and the second partition plate 36 are in contact with each other on the outer peripheral side of the housing area 58 and are separated from each other in the axial direction on the inner peripheral side of the housing area 58 .

An elastic movable body 60 is attached to the partition member 32 . The elastic movable body 60 is made of rubber or the like, and as shown in FIGS. 4 and 5, has an annular shape continuous in the circumferential direction. The elastic movable body 60 extends in the circumferential direction with a substantially constant cross-sectional shape, and has a substantially gourd-shaped cross-sectional shape as a whole in this embodiment.

More specifically, the elastic movable body 60 includes an annular support portion 62 forming an inner peripheral portion, and an annular valve portion 64 forming an outer peripheral portion. The support portion 62 has a substantially circular cross section. The support portion 62 has an annular seal lip 65 that protrudes upward and downward and continues over the entire circumference.

The valve portion 64 protrudes outward from the support portion 62 in a direction perpendicular to the axis. A deformation-allowing portion 68 is made thinner in the axial direction than the displacement contact portion 66 .

The displaceable contact portion 66 has a substantially circular cross section in the longitudinal section shown in FIG. , is a curved convex surface. In addition, at least at the contact portion described later between the displacement contact portion 66 and the inner wall surface (contact surfaces 42 and 50) on the outer peripheral side of the accommodation area 58, the protruding tip surface 69 of the displacement contact portion 66 formed as a curved convex surface The curvature is made larger than the curvature of the inner wall surface on the outer peripheral side of the accommodation area 58 which is the curved concave surface. The protruding tip surface 69 is a surface on the outer peripheral side of the displacement contact portion 66, and is, for example, the surface of the outer circumference side half circumference of the displacement contact portion 66 having a substantially circular cross section.

The deformation allowance portion 68 is integrally formed with the displacement contact portion 66 and the support portion 62 , and the displacement contact portion 66 and the support portion 62 are connected to each other through the deformation allowance portion 68 . Relative displacement of the displacement contact portion 66 with respect to the support portion 62 is permitted by elastic deformation of the deformation permitting portion 68 . The surfaces on both sides of the deformation allowance portion 68 in the thickness direction are smoothly connected to the surface of the support portion 62 and the surface of the displacement contact portion 66 . As a result, the entire surface of the valve portion 64 including the surface of the connecting portion with the support portion 62 is configured as a smoothly continuous surface, and stress concentration is less likely to occur on the surface of the valve portion 64 .

The elastic movable body 60 is attached to the partition member 32 by sandwiching the support portion 62 between the first partition plate 34 and the second partition plate 36 . In the state where the elastic movable body 60 is attached to the partition member 32 , the valve portion 64 of the elastic movable body 60 is arranged within the housing area 58 of the partition member 32 . The valve portion 64 is allowed to deform and displace in the accommodation area 58 . In particular, in this embodiment, the displacement contact portion 66 is separated from the inner wall surface (contact surfaces 42 and 50) on the outer peripheral side of the accommodation area 58 toward the inner periphery, and the displacement contact portion 66 and the accommodation area 58 are separated from the outer periphery of the accommodation area 58. A communicating region 70 is formed between the inner surface of the side wall. As a result, the entire valve portion 64 is arranged in a free state without being restrained by the partition member 32 .

The elastic movable body 60 has a thin deformation-allowing portion 68 between a support portion 62 sandwiched by the partition member 32 and a displacement abutment portion 66 arranged in the housing area 58 . Accordingly, even if the support portion 62 is axially compressed and deformed by the partition member 32 , the deformation of the support portion 62 is less likely to be transmitted to the displacement contact portion 66 due to the deformation of the deformation permitting portion 68 . Therefore, the displacement contact portion 66 is less likely to change in shape due to the holding of the support portion 62, and the displacement contact portion 66 is maintained in its initial shape. As a result, when the displaceable contact portion 66 and the first and second contact surfaces 42 and 50 contact each other, the contact state is stabilized, and the switching of the second orifice passage 78 by the valve portion 64 is high. achieved with precision.

The partition member 32 to which the elastic movable body 60 is attached is arranged in the fluid chamber 30 as shown in FIG. That is, the partition member 32 expands in the direction perpendicular to the axis in the fluid chamber 30 , and the outer peripheral surface of the partition member 32 is pressed against the inner peripheral surface of the second mounting member 14 via the seal rubber layer 24 . The partition member 32 is inserted into the inner periphery of the second mounting member 14 covered with the seal rubber layer 24, for example, and is subjected to a diameter-reducing process on the second mounting member 14, thereby It is attached to the second attachment member 14 .

By interposing the seal rubber layer 24 between the second mounting member 14 and the partition member 32, the partition member 32 is fluid-tightly assembled to the second mounting member 14, and the fluid chamber 30 sandwiches the partition member 32. It is divided into upper and lower sides. That is, on the upper side of the partition member 32, there is provided a pressure receiving chamber 72 as a main liquid chamber whose wall portion is partly constituted by the main rubber elastic body 16 and in which internal pressure fluctuations are induced when vibration is input. Below the partition member 32, an equilibrium chamber 74 is provided as a secondary liquid chamber whose wall portion is partly composed of the flexible film 26 and whose volume is allowed to change. Since the pressure receiving chamber 72 and the equilibrium chamber 74 are both part of the fluid chamber 30, they are each filled with an incompressible fluid.

Since the outer peripheral surface of the partition member 32 is fluid-tightly covered with the second mounting member 14 covered with the seal rubber layer 24, the opening of the peripheral groove 56 of the partition member 32 on the outer peripheral side is fluid-tightly closed. . Both ends of the circumferential groove 56 communicate with the pressure receiving chamber 72 through the first communication port 38 and communicate with the equilibrium chamber 74 through the second communication port 46 . As a result, a first orifice passage 76 communicating between the pressure receiving chamber 72 and the equilibrium chamber 74 is provided using the circumferential groove 56 and the first and second communication ports 38 and 46 . The first orifice passage 76 has its tuning frequency, which is the resonant frequency of the flowing fluid, adjusted by the ratio of passage cross-sectional area to passage length. A specific tuning frequency of the first orifice passage 76 is not particularly limited, but is set, for example, to a low frequency of about several Hz corresponding to engine shake.

The first through hole 44 of the partition member 32 is open to the pressure receiving chamber 72, the second through hole 52 is open to the equilibrium chamber 74, and the accommodation area 58 is formed between the first and second through holes 44. , 52 to the pressure receiving chamber 72 and the equilibrium chamber 74 . As a result, the first and second through holes 44 and 52 and the accommodation area 58 form a second orifice passage 78 as a communication passage for communicating the pressure receiving chamber 72 and the equilibrium chamber 74 with each other. The second orifice passage 78, like the first orifice passage 76, has its tuning frequency set by the ratio of passage cross-sectional area to passage length. Although the specific tuning frequency of the second orifice passage 78 is not particularly limited in the same way as the first orifice passage 76, it is, for example, approximately ten and several Hz corresponding to idling vibration, or several ten Hz corresponding to booming running noise. It is set to medium to high frequency. The tuning frequency of the second orifice passage 78 is set higher than that of the first orifice passage 76 . Therefore, fluid flow through the second orifice passage 78 can occur with the first orifice passage 76 substantially blocked by anti-resonance.

A valve portion 64 of the elastic movable body 60 is arranged on the flow path of the second orifice passage 78, as shown in FIGS. Therefore, the tuning frequency of the second orifice passage 78 is set in consideration of the narrowing of the second orifice passage 78 by the valve portion 64 and the like. The valve portion 64 is provided on the outer peripheral side with respect to the support portion 62 supported by the partition member 32, and the second orifice passage 78 in which the valve portion 64 is arranged is provided on the outer peripheral side of the partition member 32. It is Therefore, it is easy to secure a large cross-sectional area of the second orifice passage 78, and it is possible to tune the second orifice passage 78 to a higher frequency.

The first and second contact surfaces 42, 50 forming the inner wall surface of the second orifice passage 78 are inclined with respect to the axial direction, which is the flow path length direction of the second orifice passage 78, and the valve They are arranged on both sides of the portion 64 in the axial direction. As a result, at least the protruding distal end portion of the valve portion 64 is arranged at a position overlapping the first and second contact surfaces 42 and 50 in axial projection.

In the engine mount 10 having such a structure, for example, the first mounting member 12 is mounted on the power unit via an inner bracket (not shown), and the second mounting member 14 is mounted on the vehicle body via an outer bracket (not shown). can be attached to As a result, the power unit is supported on the vehicle body via the engine mount 10 in a vibration-isolating manner.

Vibration in the axial direction is input between the first mounting member 12 and the second mounting member 14 when the engine mount 10 is attached to the vehicle. When the input vibration is a low-frequency, large-amplitude vibration corresponding to engine shake, fluid flow through the first orifice passage 76 actively occurs between the pressure receiving chamber 72 and the balancing chamber 74 in a resonant state. As a result, the vibration damping effect based on the flow action of the fluid is exhibited, and the vibration damping action can be effectively obtained.

In the second orifice passage 78, a large input acts on the valve portion 64 of the elastic movable body 60 in the axial direction, which is the flow path length direction of the second orifice passage 78. Therefore, the displacement of the valve portion 64 is The contact portion 66 is largely displaced in the axial direction. As a result, as shown in FIG. 7, the projecting end surface 69 of the displacement contact portion 66 is pressed against the first and second contact surfaces 42 and 50 of the partition member 32, and the second orifice passage 78 is closed. It is shut off by the valve portion 64 . As a result, the fluid flow through the second orifice passage 78 is blocked and the internal pressure of the pressure receiving chamber 72 fluctuates efficiently, so that the vibration damping effect due to the fluid flow through the first orifice passage 76 is advantageously exhibited. be done.

Since the valve portion 64 includes the displacement abutment portion 66 that constitutes the tip portion and the deformation allowance portion 68 that is thinner in the axial direction than the displacement abutment portion 66 and constitutes the base end portion, deformation The displacement contact portion 66 is likely to be displaced by the elastic deformation of the allowance portion 68 . Therefore, when a large amplitude vibration is input, the displacement contact portion 66 is sufficiently pressed against the first and second contact surfaces 42 and 50, and the second orifice passage 78 is effectively blocked by the valve portion 64. be done.

Since the deformation permitting portion 68 which is more deformable than the displacement contact portion 66 is provided in the valve portion 64 , deformation of the displacement contact portion 66 is suppressed when the valve portion 64 is deformed. Shape stability is ensured. Therefore, unintended communication of the second orifice passage 78 due to deformation of the displaceable contact portion 66 is avoided, and switching between communication and blocking of the second orifice passage 78 by the valve portion 64 is realized with high reliability. be.

The first and second contact surfaces 42 and 50 are inclined with respect to the axial direction, which is the direction in which the hydraulic pressure acts on the displaceable contact portion 66 . Therefore, the displacement contact portion 66 pressed against the first and second contact surfaces 42 and 50 is supported by the components of the contact reaction forces with the first and second contact surfaces 42 and 50. It is pushed toward the portion 62 side (inner peripheral side). As a result, as shown in FIG. 8, the relatively thin deformation-allowing portion 68 is compressed between the displacement contact portion 66 and the support portion 62, and the spring of the deformation-allowing portion 68 nonlinearly hardens. . As a result, the displacement of the displacement abutting portion 66 due to the elastic deformation of the deformation-allowing portion 68 is restricted to a certain extent, and the excessive displacement and deformation of the valve portion 64 cause unintended communication of the second orifice passage 78 and the valve portion 64 . catching etc. is prevented.

7 and 8 illustrate the state in which the valve portion 64 is deformed and displaced toward the equilibrium chamber 74 and is in contact with the second contact surface 50. When the internal pressure decreases relative to the equilibrium chamber 74 , the valve portion 64 is deformed and displaced toward the pressure receiving chamber 72 and comes into contact with the first contact surface 42 .

A protruding tip surface 69 of the displacement contact portion 66 is a curved convex surface, and an inner wall surface on the outer peripheral side of the housing area 58 formed by the first and second contact surfaces 42 and 50 is a curved concave surface. there is Therefore, when the displaceable contact portion 66 comes into contact with the inner wall surface of the housing area 58 on the outer peripheral side, the contact state and the deformation state of the displaceable contact portion 66 are stabilized. Furthermore, when the displacement contact portion 66 moves while being in contact with the inner wall surface on the outer peripheral side of the housing area 58, excessive compression of the deformation permitting portion 68 and catching of the displacement contact portion 66 are unlikely to occur, and smooth movement is achieved. Realized.

The vertical cross-sectional curvature of the projecting tip surface 69 is larger than the vertical cross-sectional curvature of the wall inner surface on the outer peripheral side of the housing area 58 formed by the first and second contact surfaces 42 and 50 . Therefore, for example, when the displaceable contact portion 66 slides against the first and second contact surfaces 42 and 50 due to the action of the hydraulic pressure, the displaceable contact portion 66 becomes the component force of the contact reaction force. is guided to the inner circumference side. As a result, the deformation-allowing portion 68 is compressed toward the support portion 62, and the contact state of the displacement contact portion 66 with the first and second contact surfaces 42, 50 changes to the spring of the compressed deformation-allowing portion 68. easier to maintain by In addition, since the curvatures of the first and second contact surfaces 42 and 50 are relatively small, when the valve portion 64 contacts the first and second contact surfaces 42 and 50, the first and second contact surfaces 42 and 50 are The component force acting in the direction perpendicular to the second contact surfaces 42 and 50 is reduced, and the striking sound at the time of contact is prevented.

If the input vibration is a medium to high frequency, small amplitude vibration corresponding to the tuning frequency of the second orifice passage 78, then the first orifice passage 76 tuned to a lower frequency than the frequency of the input vibration will be anti-resonant. It is considered as a substantial cutoff state by

The fluid actively flows through the second orifice passage 78 in a resonant state. At this time, the valve portion 64 of the elastic movable body 60 slightly deforms and displaces in the resonant state, thereby causing the second orifice passage 78 to flow. It does not impede fluid flow through orifice passage 78 . Therefore, the sealing of the pressure receiving chamber 72 due to the substantial blocking of the first orifice passage 76 is avoided by the fluid flow through the second orifice passage 78, and the vibration damping effect due to the low dynamic spring of the engine mount 10. (vibration insulating action) is exhibited.

A communication region 70 is provided between the displacement contact portion 66 and the wall inner surface on the outer peripheral side of the accommodation region 58 , and in the initial state where no vibration is input, the displacement contact portion 66 is connected to the wall inner surface on the outer peripheral side of the accommodation region 58 . , minute deformation and displacement of the valve portion 64 occur with high sensitivity. Therefore, the valve portion 64 is deformed or displaced to follow the vibration input of minute amplitude and high frequency, and the vibration damping effect due to the fluid flow in the second orifice passage 78 is exhibited.

FIG. 9 shows part of an engine mount as a second embodiment of a fluid-filled vibration damping device constructed according to the present invention. In the following description, members and portions that are substantially the same as those of the first embodiment are denoted by the same reference numerals in the drawings, and description thereof is omitted.

That is, in FIG. 9, the elastic movable body 60 is arranged in the partition member 80 . The partition member 80 is provided with a storage area 58 , which communicates with the pressure receiving chamber 72 through the first through hole 44 , and communicates with the equilibrium chamber 74 through the second through hole 52 . By doing so, a second orifice passage 78 is formed.

The inner wall surface of the housing area 58 on the outer peripheral side has a first contact surface 82 on the pressure receiving chamber 72 side and a second contact surface 84 on the equilibrium chamber 74 side. The first contact surface 82 is an inclined surface that gradually inclines toward the inner periphery toward the pressure receiving chamber 72 side, and in this embodiment, the inclination angle with respect to the axial direction (vertical direction in FIG. 9) is substantially constant. It is The second contact surface 84 is an inclined surface that gradually inclines toward the equilibrium chamber 74, and in this embodiment, the inclination angle is substantially constant. Therefore, in the longitudinal section shown in FIG. 9, the first and second contact surfaces 82, 84 are linear.

Similarly to the engine mount 10 of the first embodiment, the engine mount having the structure according to the present embodiment also achieves both anti-vibration performance against low-frequency vibrations and anti-vibration performance against medium to high-frequency vibrations. can be obtained at altitude.

FIG. 10 shows part of an engine mount as a third embodiment of a fluid-filled vibration damping device constructed according to the present invention. That is, the engine mount shown in FIG. 10 has a structure in which an elastic movable body 90 is arranged in the partition member 32 .

The elastic movable body 90 includes a support portion 62 and a valve portion 92. The valve portion 92 has a substantially constant thickness and is shaped like an annular plate that spreads in the direction perpendicular to the axis. Both sides of the valve portion 92 of the present embodiment in the thickness direction (axial direction) are substantially flat surfaces, and the projecting tip end surface (outer peripheral surface) is a cylindrical surface extending linearly in the axial direction. , corner portions 94 are formed at both ends in the axial direction of the projecting tip.

Similarly to the engine mount 10 of the first embodiment, the engine mount having the structure according to the present embodiment also achieves both anti-vibration performance against low-frequency vibrations and anti-vibration performance against medium to high-frequency vibrations. can be obtained at altitude.

It is also possible to employ the elastic movable body 90 having the structure according to the present embodiment in combination with the partition member 80 having the structure according to the second embodiment. Also in this case, as in the first to third embodiments, both anti-vibration performance against low-frequency vibration and anti-vibration performance against medium to high-frequency vibration are exhibited.

Although the embodiments of the present invention have been described in detail above, the present invention is not limited by the specific descriptions. For example, the elastic movable body is not limited to an annular shape in which the support portion and the valve portion are continuously provided over the entire circumference. That is, the elastic movable body may, for example, extend linearly, may extend curvedly, or may extend in a meandering or curved manner.

Although one elastic movable body is provided in the above embodiment, a plurality of elastic movable bodies may be provided. The plurality of elastic movable bodies may have the same shape, or at least one may have a different shape from the others.

The specific shape of the elastic movable body is not limited, and the specific shapes of the support portion and the valve portion may be changed as appropriate. For example, as shown in FIG. 10, the deformation-allowing portion made thin in the valve portion is not essential. Also, the displacement abutting portion of the valve portion may have a cross-sectional shape other than circular, and for example, an elliptical cross-section may be employed. Furthermore, the cross-sectional shape of the support portion may be, for example, a polygon such as a quadrangle, or an irregular shape. Moreover, in the elastic movable body, the valve portion may be provided on the inner peripheral side of the support portion.

In the above embodiment, the second orifice passage 78 extending linearly in the axial direction was exemplified as the communication passage, but the shape of the communication passage is not particularly limited. It may be provided with a portion extending to the Therefore, the length direction of the communication channel is not necessarily constant, and may vary depending on the part of the communication channel.

10 Engine mount (fluid-filled anti-vibration device)
12 First mounting member 14 Second mounting member 16 Main rubber elastic body 18 Flange-shaped portion 20 Screw hole 22 Recess 24 Seal rubber layer 26 Flexible film 28 Fixing member 30 Fluid chambers 32, 80 Partition member 34 Partition plate 36 Second partition plate 38 First communication port 40 First concave grooves 42, 82 First contact surface (contact surface)
44 first through hole 46 second communication port 48 second grooves 50, 84 second contact surface (contact surface)
52 Second through hole 54 Screw 56 Circumferential groove 58 Accommodating area 60, 90 Elastic movable body 62 Supporting part 64, 92 Valve part 65 Seal lip 66 Displacement abutting part 68 Deformation permitting part 69 Protruding tip surface 70 Communication area 72 Pressure receiving chamber (main liquid chamber)
74 equilibrium chamber (secondary liquid chamber)
76 first orifice passage 78 second orifice passage (communication passage)
94 corner

Claims (7)

A main liquid chamber and a sub-liquid chamber filled with an incompressible fluid are formed on both sides of the partition member, and a communication passage is formed to connect the main liquid chamber and the sub-liquid chamber to each other. In the type anti-vibration device,
An elastic movable body arranged in the partition member is arranged on the communication channel by protruding from the support portion supported by the partition member and the support portion in a direction crossing the length direction of the communication channel. and a valve portion,
The inner wall surface of the communication channel has a contact surface that contacts the valve portion when the valve portion is displaced in the channel length direction of the communication channel. It is provided on both sides of the road length direction,
The contact surface is inclined with respect to the flow path length direction of the communication flow path, and a component of the contact reaction force between the valve portion and the contact surface compresses the valve portion toward the support portion. A fluid-filled anti-vibration device designed to act in a direction. 2. A fluid filled type vibration damping device according to claim 1, wherein a protruding tip surface of said valve portion including a contact portion with said contact surface is a curved convex surface, and said contact surface is a curved concave surface. 3. A fluid-filled vibration damping device according to claim 2, wherein the curvature of the portion of the protruding end surface of the valve portion that contacts the contact surface of the partition member is larger than the curvature of the contact surface. 4. The method according to any one of claims 1 to 3, wherein the valve portion and the inner wall surface of the communicating channel are separated from each other, and a communicating region is provided between the valve portion and the inner wall surface of the communicating channel. A fluid-filled vibration isolator as described. 2. A base end portion of the valve portion connected to the support portion is a deformation-permitting portion that is thinner than a tip end portion of the valve portion and the support portion in the flow path length direction of the communication flow path. 5. The fluid-filled vibration isolator according to any one of items 1 to 4. 6. The fluid-filled type waterproof device according to claim 1, wherein the elastic movable body is annular, and both the support portion and the valve portion are continuously provided over the entire circumference. vibration device. The fluid enclosure according to any one of claims 1 to 6, wherein the elastic movable body extends in the circumferential direction, and the valve portion protrudes from the support portion toward the outer peripheral side of the partition member. anti-vibration device.

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