JP4073028B2 - Fluid filled cylindrical vibration isolator - Google Patents

Description

  The present invention relates to a cylindrical vibration isolator in which an outer cylindrical member is disposed apart from the outer peripheral side of an inner shaft member, and both of these metal fittings are connected by a main rubber elastic body. A fluid that is suitably used as a suspension bush, an engine mount, a subframe mount, a body mount, a differential mount, etc. The present invention relates to a sealed cylindrical vibration isolator.

  Conventionally, as a kind of anti-vibration coupling body or anti-vibration support body interposed between members constituting a vibration transmission system, an inner shaft member and an outer cylinder member spaced apart on the outer peripheral side thereof are made of a main rubber elastic body. In a cylindrical vibration isolator connected to each other, an incompressible fluid is sealed inside, and a fluid-filled cylindrical shape is obtained by utilizing a resonance action of a fluid caused at the time of vibration input, etc. Anti-vibration devices are known.

  More specifically, such a cylindrical vibration isolator generally has an inner shaft member and a diameter of an intermediate sleeve spaced apart on the outer peripheral side thereof as disclosed in Japanese Utility Model Laid-Open No. 1-149044. A main rubber elastic body is disposed between the direction-opposing surfaces, and an outer cylindrical member is fitted and fixed to the intermediate sleeve. By adopting such a structure, the pocket portion formed so as to open to the outer peripheral surface through the window portion provided in the intermediate sleeve is fluid-tightly sealed by the outer fitting fixing of the outer cylinder member, so that the fluid of the sealed structure It becomes possible to easily form the enclosing region. In addition, such a fluid-filled region is generally provided so that the flow of the incompressible fluid is efficiently generated at the time of vibration input in the direction perpendicular to the axis between the inner shaft member and the outer cylindrical member. A plurality of fluid chambers formed on both side portions sandwiching the inner shaft member in the direction perpendicular to the axis between the opposing surfaces in the direction perpendicular to the axis of the cylindrical member, and an orifice passage communicating these fluid chambers with each other.

  In such a conventional fluid-filled cylindrical vibration isolator, when a vibration is input, a fluid flow through the orifice passage is generated based on a relative pressure fluctuation caused between a plurality of fluid chambers. An effective vibration isolation effect can be obtained by utilizing the resonance action of the fluid flowing through the orifice passage.

  However, the anti-vibration effect based on the resonance action of the fluid flowing through the orifice passage can be exhibited only in a relatively narrow frequency range, and especially in the orifice passage tuned to the frequency range intended for anti-vibration. There is a problem that the vibration resistance is significantly increased and the vibration isolation performance is greatly lowered when vibration is input in a frequency range higher than the frequency.

  In addition, at the time of shock vibration input, the fluid flow through the orifice passage cannot follow, and a large pressure fluctuation is caused to the fluid chamber, and accordingly, shock vibration is caused, Occurrence of abnormal noise and vibration due to gas phase separation in the sealed fluid may be a problem.

  Therefore, in order to cope with such a problem, Patent Document 1 (DE 4332367A1) forms a relief flow channel between two fluid chambers connected by an orifice passage, There has been proposed a structure in which a seal lip made of a rubber elastic body is projected. In other words, during normal vibration input, the relief flow path is maintained in the closed state by the seal lip, but when a significant pressure difference occurs between the fluid chambers, the seal lip is elastically deformed to create a gap. Thus, the relief flow path is brought into a communication state through the gap, and the fluid flow between the fluid chambers is allowed, so that significant pressure fluctuations in the fluid chambers are eliminated.

  However, in the conventional structure disclosed in Patent Document 1, the relief flow path is maintained in a blocked state by pressing the protruding tip surface of the seal lip against the inner peripheral surface of the relief flow path. In the opening / closing operation of the seal lip, rubbing between the seal lip and the inner surface of the relief flow path occurs. For this reason, there has been a problem that the wear of the seal lip is inevitable and a stable operation cannot be desired over a long period of time. In addition, since the opening and closing operation of the seal lip depends on the coefficient of friction at the contact surface between the seal lip and the relief flow path, there is a problem that the operation of the seal lip is stable and difficult due to variations in manufacturing conditions and processing conditions. There was.

  In Patent Document 2 (Japanese Patent Publication No. 7-92106), a special annular member is externally fitted and fixed to the inner shaft member, and a passage that connects the two fluid chambers to each other is connected to the annular member. A structure in which a check valve is provided at the opening of the passage to the fluid chamber is proposed. With such a structure, it is possible to configure a check valve in a form that does not contact the inner surface of the passage, and by doing so, it is possible to avoid wear of the check valve and variations in operation. However, as is apparent from the drawing of Patent Document 2, in this fluid-filled cylindrical vibration isolator of the conventional structure, an annular elastic member constituting a check valve is assembled to the inner shaft member, and a passage is formed. Since it is necessary to externally fix the annular member for use, the structure is complicated, the number of parts is large, and the manufacture and assembly are very difficult and complicated. In addition, it is necessary not only to form a relief flow path so that the inside of the annular member extends in a tunnel shape, but also a check valve disposed in the opening of the annular member. Therefore, manufacturing and assembly are further complicated, and its practical use has been extremely difficult.

German published patent publication 4332367 Japanese Patent Publication No. 7-92106

  Here, the present invention has been made in the background as described above, and the problem to be solved is a significant pressure fluctuation caused in the fluid chamber due to input of an impact load or the like. Relief flow path that can be reduced or avoided with stable operation characteristics based on high reliability and durability, fluid-filled type with a highly practical new structure that can be realized with a small number of parts and a simple structure The object is to provide a cylindrical vibration isolator.

  Hereinafter, embodiments of the present invention made to solve such problems will be described. In addition, the component employ | adopted in each aspect as described below is employable by arbitrary combinations as much as possible. Further, aspects or technical features of the present invention are not limited to those described below, but are described in the entire specification and drawings, or an invention that can be understood by those skilled in the art from those descriptions. It should be understood that it is recognized based on thought.

That is, according to the first aspect of the present invention, the main rubber elastic body is disposed between the radially inner surfaces of the inner shaft member and the intermediate sleeve spaced apart on the outer peripheral side thereof, and the outer cylinder is disposed with respect to the intermediate sleeve. A plurality of fluid chambers in which relative pressure fluctuations are generated at the time of vibration input between the inner shaft member connected by the main rubber elastic body and the radially opposed surfaces of the outer cylindrical member while the member is fitted and fixed. In order to obtain a vibration-proofing effect based on the fluid action of the fluid that is formed in the circumferential direction and forms an orifice passage that communicates the plurality of fluid chambers with each other so that the orifice passage flows when vibration is input. In the fluid-filled cylindrical vibration isolator, a plurality of window portions are provided in the intermediate sleeve to form a plurality of pocket portions that open to the outer peripheral surface through the respective window portions. The plurality of fluid chambers are formed by fluid-tightly covering the portion with the outer cylinder member, while opening in the outer peripheral surface in the axially intermediate portion of the intermediate sleeve and extending in the circumferential direction between the plurality of window portions A groove member extending in the groove is provided, a separate passage member is fitted into the groove, and the passage member is fluidly pressed into the groove by the outer cylinder member and fixedly assembled in the circumferential direction. A relief flow path extending between the plurality of fluid chambers is formed by the passage member, and at least one opening of the relief flow path is more radial than the inner peripheral surface of the outer cylinder member The elastic valve body, which is positioned inwardly and is protruded from the bottom surface of the concave groove of the intermediate sleeve toward the opening, does not reach the inner peripheral surface of the outer cylinder member. Forming one of the relief channels. While part is superposed on the end surface of one circumferential of the passage member provided Ru brought substantially close the opening of the relief channel, elastic through the relief channel when a large amplitude vibration is input wherein through the relief flow path a plurality of fluid chambers, characterized in that as may communicate by elastic valve body with a pressure applied to the valve body is elastically deformed.

  In such a liquid-filled cylinder type vibration isolator having the structure according to the first aspect, it is possible to efficiently secure a space by configuring the relief flow path using the concave groove of the intermediate sleeve. it can. In addition, the concave groove in such an intermediate sleeve is a configuration generally employed for forming an orifice passage or the like, as disclosed in, for example, Japanese Utility Model Laid-Open No. 1-149044. The relief channel can be configured with a simple structure.

  In addition, since the intermediate sleeve is fixed to the outer peripheral surface of the main rubber elastic body by integral vulcanization adhesion, the valve protruding on the outer peripheral surface can be easily integrated with the main rubber elastic body using the main rubber elastic body. Can be formed.

  In addition, the passage member that forms the relief flow path is formed separately from the main rubber elastic body and the intermediate sleeve, and the relief flow path can be easily inserted into the concave groove by fitting it into the concave groove from the outer peripheral surface. Can be formed.

  In addition, the one opening of the relief flow path is positioned radially away from the inner peripheral surface of the outer cylindrical member, and the elastic valve body is formed with a protruding height that does not reach the inner peripheral surface of the outer cylindrical member. Thus, even when vibration is input to the fluid chamber and the elastic valve body is elastically deformed, the elastic valve body does not slide against the outer cylinder member, and the operation of the elastic valve body is inhibited by friction. Can be avoided. Further, it is possible to prevent the elastic valve body from being worn or damaged due to friction, resulting in unstable operation.

  Further, a second aspect of the present invention is the fluid-filled cylindrical vibration isolator having the structure according to the first aspect, wherein the two relief channels are formed by the passage member, and the two relief channels are formed. Each of the elastic valve bodies is formed on both sides in the circumferential direction of the passage member so as to substantially close the openings to the fluid chambers on the opposite sides.

  In such a fluid-filled cylindrical vibration isolator having a structure according to this aspect, vibration in the frequency range higher than the tuning frequency of the orifice passage or fluid flow through the orifice passage can completely follow the fluid chamber. When no large amplitude vibration is input, one of the two relief flow paths is brought into a communication state by elastic deformation of the elastic valve element, and the other is closed by the elastic valve element. Therefore, no matter which direction the vibration in the radial direction is applied, the relief flow path is surely connected, so that it is possible to reliably avoid the pressure increase in the fluid chamber and to stabilize the vibration isolation performance. Can demonstrate.

  Moreover, when attaching a channel | path member with respect to a ditch | groove, a channel | path member can be positioned in the circumferential direction with the both elastic valve bodies superimposed on the circumferential direction both end surfaces. Therefore, the passage member can be easily assembled at the correct position.

  Further, since the two relief flow paths are formed by one passage member, it is possible to realize with a small number of parts.

  According to a third aspect of the present invention, there is provided a fluid-filled cylindrical vibration isolator having a structure according to the first or second aspect, wherein the elastic valve body is elastically biased to provide the passage member. It is assembled in an abutting state with respect to the opening of the relief flow path on the circumferential end face.

  In the fluid-filled cylindrical vibration isolator having such a structure according to this aspect, the elastic valve body can be reliably brought into contact with the opening of the relief flow path. Therefore, at the time of vibration input in the frequency range where the orifice passage is tuned, pressure fluctuations in the fluid chamber can be efficiently secured, and a sufficient amount of fluid flow through the orifice passage can be secured, and the vibration isolation effect by the orifice passage can also be obtained. It can be obtained more advantageously.

  According to a fourth aspect of the present invention, there is provided a fluid-filled cylindrical vibration isolator having a structure according to any one of the first to third aspects, wherein the pair of windows in the intermediate sleeve are arranged in the radial direction. A pair of fluids that are located on both sides of the inner shaft member in the radial direction are formed by opening a pair of pockets that are opposed to each other and are covered with outer cylindrical members. While forming the chamber, the first concave groove and the second concave groove are formed across the end portions on both sides in the circumferential direction of the fluid chambers, and the passage member is assembled to the first concave groove. On the other hand, the orifice passage is formed in the second concave groove.

  In the fluid-filled cylindrical vibration isolator having the structure according to this aspect, the orifice passage connecting the pair of fluid chambers is formed by using the second concave groove formed in the intermediate sleeve. The orifice passage can be easily formed with a simple structure. Further, since the orifice passage is formed in the intermediate sleeve, a large passage length of the orifice passage can be secured, and a frequency range in which the orifice passage can be tuned is widened.

  According to a fifth aspect of the present invention, in the fluid-filled cylindrical vibration isolator having the structure according to any one of the first to fourth aspects, the main rubber elastic body includes the inner shaft member and the outer cylinder. A pair of pocket portions are formed in the main rubber elastic body so as to be disposed over substantially the entire circumference in the circumferential direction between the radially opposed surfaces of the member, and to be opened on both sides of the inner shaft member. The pockets are opened through the pair of windows provided in the intermediate sleeve.

  In the fluid-filled cylindrical vibration isolator having the structure according to this aspect, the positive pressure is generated in one of the fluid chambers on the compression side when vibration is input in the radial direction in which the fluid chambers are opposed to each other. And a negative pressure is generated in the other fluid chamber on the pulling side. Therefore, a relative pressure difference between the fluid chambers is greatly induced at the time of vibration input, and fluid flow through the orifice passage is more positively and effectively generated. It can be obtained more advantageously.

  According to a sixth aspect of the present invention, in the fluid-filled cylindrical vibration isolator having the structure according to any one of the first to fifth aspects, a seal rubber layer is attached to the inner surface of the concave groove in the intermediate sleeve. It is formed.

  In the fluid-filled cylindrical vibration isolator having the structure according to this aspect, the both side surfaces and the inner peripheral surface of the passage member are fluid-tightly overlapped with the concave grooves and assembled, thereby assembling between the fluid chambers. The sealing performance for preventing the short circuit in the cylinder is improved, and the desired vibration isolation performance based on the fluid flow between the fluid chambers can be obtained more advantageously.

  According to a seventh aspect of the present invention, in the fluid-filled cylindrical vibration isolator having the structure according to any one of the first to sixth aspects, a communication groove that opens on an inner peripheral surface of the passage member is formed. In addition, the relief flow path is formed by covering the communication groove with the bottom surface of the concave groove in the intermediate sleeve.

  In the fluid-filled cylindrical vibration isolator having such a structure according to this aspect, it is easy to manufacture a passage member formed as a separate body. Moreover, it is easy to dispose the opening of the relief channel away from the inner peripheral surface of the outer cylinder member.

  As is clear from the above description, according to the present invention, significant pressure fluctuations induced in the fluid chamber due to input of an impact load or the like are stabilized with high reliability and durability. It is possible to realize a fluid-filled cylindrical vibration isolator having a highly practical new structure in which a relief flow path that can be reduced or avoided with operating characteristics can be realized with a small number of parts and a simple structure.

  In particular, in the fluid-filled cylindrical vibration isolator having a structure according to the present invention, the passage member that forms the relief flow path is accommodated in the concave groove provided in the intermediate sleeve, and is between the intermediate sleeve and the outer cylindrical member. Therefore, the passage member can be assembled with excellent assembling workability and sealability as well as excellent space efficiency.

  Hereinafter, in order to clarify the present invention more specifically, embodiments of the present invention will be described in detail with reference to the drawings.

  First, FIG. 1 and FIG. 2 show an anti-vibration bush 10 according to an embodiment of the present invention that is used for a suspension bush of an automobile or the like. In the vibration isolating bushing 10, an inner cylinder fitting 12 as an inner shaft member and an outer cylinder fitting 14 as an outer cylinder member are disposed at a predetermined distance in the radial direction, and interposed therebetween. The main rubber elastic body 16 is connected by the mounted rubber elastic body 16. The anti-vibration bushing 10 is interposed between the anti-vibration-coupled members by attaching the anti-vibration bush 10 to each of the anti-vibration-coupled members of the inner cylinder fitting 12 and the outer cylinder fitting 14. Yes.

  More specifically, the inner cylinder fitting 12 has a small-diameter, generally cylindrical shape, and has a slightly larger diameter in the vicinity of the center in the axial direction than in other portions.

  Further, a metal sleeve 26 as a thin large-diameter cylindrical intermediate sleeve is disposed on the substantially same central axis at a predetermined distance outside the inner cylindrical metal member 12 in the radial direction. The axial length of the metal sleeve 26 is smaller than the axial length of the inner cylindrical metal member 12, and both axial end portions of the inner cylindrical metal member 12 protrude axially outward from the metal sleeve 26. .

  Further, a pair of open windows 28 and 30 as window portions are formed in the axially central portion of the metal sleeve 26 so as to face each other in one radial direction. Each of the opening windows 28 and 30 has a substantially rectangular shape, and is formed through the metal sleeve 26. Furthermore, a small-diameter portion 32 is formed between the edge portions on both sides in the circumferential direction of the pair of opening windows 28 and 30 so as to be located in the central portion of the metal sleeve 26 in the axial direction. Circumferential grooves 34 and 36 as wide groove-like grooves extending continuously in the circumferential direction across the circumferential end portions 28 and 30 are formed in the outer peripheral surface of the metal sleeve 26.

  A main rubber elastic body 16 is disposed between the radially opposing surfaces of the inner cylinder fitting 12 and the metal sleeve 26. The main rubber elastic body 16 has a thick cylindrical shape as a whole, and is interposed between the radially opposing surfaces of the inner cylinder fitting 12 and the metal sleeve 26 over substantially the entire circumference. As shown in FIGS. 3 and 4, the outer peripheral surface of the main rubber elastic body 16 is vulcanized and bonded to the inner peripheral surface of the metal sleeve 26, and the inner peripheral surface is the outer periphery of the inner cylindrical metal member 12. By being vulcanized and bonded to the surface, the main rubber elastic body 16 is formed as an integrally vulcanized molded product 38 having the inner cylindrical fitting 12 and the metal sleeve 26. In particular, in the present embodiment, both end portions in the axial direction of the metal sleeve 26 are directly exposed to the outer peripheral surface of the integrally vulcanized molded product 38, and after vulcanization molding of the main rubber elastic body 16, if necessary. By subjecting the metal sleeve 26 to diameter reduction processing such as eight-way drawing, pre-compression is applied to the main rubber elastic body 16 to reduce tensile stress.

  A covering rubber layer 40 as a thin seal rubber layer integrally formed with the main rubber elastic body 16 is formed on the inner peripheral surfaces of the peripheral grooves 34 and 36 formed in the metal sleeve 26. , 36 is entirely covered with a covering rubber layer 40.

  Furthermore, the pair of pocket portions 42, the axial center portion of the main rubber elastic body 16 are opposed to each other in one radial direction (up and down direction in FIG. 2) sandwiching the inner cylindrical fitting 12. 44 is formed. The pair of pocket portions 42 and 44 open to the outer peripheral surface of the main rubber elastic body 16 through opening windows 28 and 30 formed in the metal sleeve 26, respectively. The depth dimensions of the pocket portions 42 and 44 are set so as not to reach the inner cylindrical fitting 12 slightly, and the circumferential dimensions of the pocket portions 42 and 44 are the circumferential length of the main rubber elastic body 16. It is supposed to be less than half a circle. In particular, in the present embodiment, each of the pocket portions 42 and 44 has a substantially flat bottom surface that linearly extends in a direction orthogonal to the radial direction, and a mold that is split in the left-right direction in FIG. It can be used.

  In addition, an orifice member 48 is assembled on the outer peripheral surface of the integrally vulcanized molded product 38 of the main rubber elastic body 16 as described above.

  As shown in FIGS. 5, 6, and 7, the orifice member 48 is made of a resin having an arc plate shape that is curved in an arc plate shape (substantially C shape) and extends in the circumferential direction with a substantially constant thickness as a whole. The width dimension of the member is slightly smaller than the width dimension of the circumferential grooves 34 and 36. The orifice member 48 has an inner peripheral surface whose curvature is substantially the same as that of the outer peripheral surfaces of the circumferential grooves 34 and 36 in the metal sleeve 26, and the curvature of the outer peripheral surface thereof is the inner peripheral surface of the metal sleeve 26. It is set to be almost the same as the curvature of.

  Such an orifice member 48 is disposed across the opening windows 28 and 30 and the circumferential groove 34 of the metal sleeve 26 in the circumferential direction with respect to the integrally vulcanized molded product 38. That is, the orifice member 48 is fitted from the side on which the circumferential groove 34 is formed in the radial direction, and its circumferential central portion is assembled on the circumferential groove 34 provided in the metal sleeve 26 and both end portions. Are assembled and positioned at both ends in the circumferential direction of a circumferential groove 36 provided in the metal sleeve 26.

  In attaching the orifice member 48 to the integrally vulcanized molded product 38 in the present embodiment, the orifice vulcanized product 38 is fitted into the cutout portion 50 of the orifice member 48 from the radially outer side, whereby the orifice member 48 is fixed. It is assembled to the integrally vulcanized molded product 38 in an externally fitted state. However, the circumferential length of the notch 50 of the orifice member 48 is shorter than the circumferential length of the circumferential grooves 34 and 36 and is difficult to fit. Therefore, a mounting groove 52 continuously extending in the width direction (axial direction) is formed on the outer peripheral surface at the center in the circumferential direction of the orifice member 48 formed of a deformable resin material such as polyamide over the entire length in the width direction. Is formed. Due to the mounting groove 52, the member thickness of the orifice member 48 is thin at the center in the circumferential direction and is easy to bend, so that the notch 50 of the orifice member 48 can be elastically expanded and expanded. It is like that. That is, both end portions of the orifice member 48 can be separated from each other, and the circumferential length of the notch 50 can be made longer than the circumferential length of the circumferential grooves 34 and 36. Thus, the integral vulcanized molded product 38 can be fitted into the inner circumferential space of the orifice member 48 from the notch 50, and the orifice member 48 can be assembled on the outer circumferential surface of the integral vulcanized molded product 38. ing.

  As shown in FIG. 2, the orifice member 48 has a length in the circumferential direction of about 3/4 of the metal sleeve 26 in the assembled state to the integrally vulcanized molded product 38. Is formed with an orifice forming groove 54 continuously extending from one end to the other end in a constant cross-sectional shape. The orifice forming groove 54 communicates with the pocket portions 42 and 44 through a communication hole 56 that passes through the inner peripheral wall portion and opens to the inner peripheral surface of the orifice member 48 in the vicinity of both ends in the circumferential direction of the orifice member 48. . Further, both end surfaces in the width direction of the orifice member 48 are fluid-tightly superimposed on both side surfaces of the circumferential groove 34, and the mounting groove 52 is substantially closed.

  On the other hand, in the circumferential groove 36, a passage member 58 is attached between the circumferential ends of the orifice member 48, that is, in the notch 50 of the orifice member 48. As shown in FIG. 8, the passage member 58 is integrally formed by connecting two flow path forming portions 60, 60 having a substantially rectangular parallelepiped shape in a crank shape, and has a substantially crank shape as a whole. It is a block body. The passage member 58 is preferably made of a hard material such as synthetic resin or metal. Further, the maximum width dimension of the passage member 58 is slightly smaller than the width dimension of the circumferential groove 36, and the radial thickness thereof is substantially constant, and is slightly smaller than the depth of the circumferential groove 36. . Further, the passage member 58 is curved in the circumferential direction, the curvature of the inner circumferential surface thereof is substantially the same as the curvature of the circumferential direction of the bottom surface of the circumferential groove 36, and the curvature of the outer circumferential surface thereof is a metal sleeve. 26 is substantially the same as the circumferential curvature of the outer peripheral surface of 26.

  Furthermore, as shown in FIG. 9, each channel forming portion 60, 60 has a communication groove that opens to the inner peripheral surface and extends over the entire circumferential length of each channel forming portion 60, 60. A flow path forming groove 62 is formed. The flow path forming groove 62 extends substantially linearly in the circumferential direction with a constant cross-sectional shape over the entire length.

  Such a passage member 58 is mounted on the outer circumference of the circumferential groove 36 on substantially the same circumference as the orifice member 48. An opening to the inner peripheral surface of the flow path forming groove 62 formed in the passage member 58 is covered with a covering rubber layer 40 formed on the bottom surface of the peripheral groove 36 to form a relief flow path extending in the circumferential direction. The pressure relief flow path 64 is formed. Further, the opening portions of the pressure relief flow passages 64 respectively opened at both ends of the passage member 58 are communicated with the pocket portions 42 and 44 through the communication holes 56 formed in the orifice member 48, and FIG. 11, an elastic valve in which a central opening 66 of a pressure relief channel 64 that opens to the center side of the passage member 58 is formed to protrude radially outward at the bottom surface of the circumferential groove 36. The passage member 58 is positioned in the circumferential direction by being superposed on the flow path closing valve body 68 as a body.

  The flow path closing valve body 68 is a plate-like protrusion formed of a thin rubber, and is slightly smaller than the depth of the circumferential groove 36 in the radially outward direction at the bottom surface of the circumferential grooves 34 and 36. It protrudes at a low height and is formed integrally with the covering rubber layer 40. Further, in the vicinity of the center in the circumferential direction of the circumferential groove 36, the two flow path closing valve bodies 68 are formed so as to protrude side by side in the width direction at a position slightly shifted in the circumferential direction. Each of the passages 64 overlaps one central opening 66 and covers the central opening 66. Further, the flow path closing valve body 68 has an inclined surface opposite to the passage member 58 and gradually becomes thinner toward the tip than the base.

  By arranging the pressure relief flow path 64 and the flow path closing valve body 68 in this way, the circumferential position of the passage member 58 can be fixed. Furthermore, in one of the pressure relief channels 64, if a pressure higher than a certain level is applied in the circumferential direction from the pressure relief channel 64 to the channel block valve body 68, the channel block valve body 68 is elastically deformed by the pressure. The pressure relief flow path 64 is in a communication state in the circumferential direction. At that time, in the other pressure relief flow path 64 1, pressure is applied to the flow path closure valve body 68 from the side opposite to the pressure relief flow path 64, so that the flow path closure valve body 68 is further strengthened. The pressure relief flow path 64 is pressed against the central opening 66, so that the pressure relief flow path 64 is kept closed, and a pressure higher than a certain level is applied to the flow path closure valve body 68. In such a case, one of them is in a communication state and the other is in a closed state.

  The flow path closing valve body 68 is given an urging force so as to be always elastically pressed against the central opening 66 of the pressure relief flow path 64 that is overlaid. Thus, the central opening 66 of the pressure relief channel 64 can be reliably closed in a state where no vibration is input or in a state where the input vibration is not a shocking large amplitude vibration. Further, the passage member 58 can be accurately positioned in the circumferential direction.

  As described above, after the orifice member 48 and the passage member 58 are assembled to the outer peripheral surface of the integrally vulcanized molded product 38 of the main rubber elastic body 16, the integral vulcanized molded product 38, the orifice member 48, and the passage member 58 are assembled. The outer cylinder fitting 14 is attached in an extrapolated state so as to cover each of the outer peripheral surfaces.

  As shown in FIGS. 1 and 2, the outer cylinder fitting 14 has a thin large-diameter cylindrical shape, and an orifice member 48 with respect to the integrally vulcanized molded product 38 of the main rubber elastic body 16. And, after the passage member 58 is assembled, it is extrapolated and reduced in diameter by an eight-way restrictor or the like, so that the metal sleeve 26, the orifice member 48 and the passage member 58 are fitted and fixed to the outer peripheral surface. That is, the orifice member 48 and the passage member 58 are fixedly assembled to the metal sleeve 26 by the outer cylinder fitting 14. Further, a seal rubber 70 is fixedly formed on the inner peripheral surface of the outer cylinder fitting 14, and the outer sleeve fitting 14 is compressed by reducing its diameter with an eight-way restrictor or the like, so that the metal sleeve 26 and the outer cylinder are pressed. Between the fitting surfaces of the metal fittings 14, between the fitting surfaces of the orifice member 48 and the outer cylindrical metal fitting 14, and between the fitting surfaces of the passage member 58 and the outer cylindrical metal fitting 14, are sealed in a fluid-tight manner.

  Then, the orifice member 48, the passage member 58, and the outer cylinder fitting 14 are assembled to the integrally vulcanized molded product 38 of the main rubber elastic body 16 as described above, so that the openings of the pair of pocket portions 42 and 44 are opened. Are each covered fluid-tightly. As a result, a pair of first and second fluid chambers 72 and 74 are formed in the pair of pocket portions 42 and 44 as a fluid sealing region in which a part of the wall portion is constituted by the main rubber elastic body 16. . Further, the pair of first and second fluid chambers 72 and 74 are filled with an incompressible fluid, respectively. As such an incompressible fluid, water, alkylene glycol, polyalkylene glycol, silicone oil, or the like is employed. In order to advantageously obtain a vibration isolation effect based on the resonance action of the fluid described later, in this embodiment, the viscosity A low-viscosity fluid having a viscosity of 0.1 Pa · s or less is preferably employed. That is, in the pair of first and second fluid chambers 72 and 74, relative internal pressure fluctuations are generated based on elastic deformation of the main rubber elastic body 16 when the vibration is input in the radial direction in which they are opposed to each other. It is like that. The fluid can be sealed by, for example, assembling the outer cylinder fitting 14 to the integrally vulcanized molded product 38 in the fluid.

  Furthermore, the orifice forming groove 54 formed on the outer peripheral surface of the orifice member 48 is fluid-tightly covered by the assembly of the outer cylinder fitting 14, and the pair of first and second fluid chambers 72 and 74 are mutually connected. A communicating orifice passage 76 is formed. In particular, in this embodiment, it is formed in the length of about 2/3 circumference in the circumferential direction along the inner peripheral surface of the outer cylinder metal fitting 14. The orifice passage 76 has an appropriate passage length and passage sectional area in consideration of the wall spring rigidity of the pair of first and second fluid chambers 72 and 74 and the density of the enclosed incompressible fluid. By being set, the vibration isolation effect based on the resonance action of the fluid flowing through the inside is tuned so as to be effectively exhibited against the vibration in the target frequency range. Further, the mounting groove 52 formed on the outer peripheral surface of the orifice member 48 in order to facilitate the attachment of the orifice member 48 to the integrally vulcanized molded product 38 is a coated rubber layer in which both ends thereof are attached to the peripheral groove 34. In addition to being closed by 40, the opening to the outer peripheral surface is covered with a seal rubber 70 formed on the inner peripheral surface of the outer cylinder fitting 14. Therefore, it is substantially blocked and does not have any influence on the vibration isolation performance.

  On the other hand, the outer cylinder fitting 14 is attached in an extrapolated state, and the diameter is reduced by an eight-way throttle or the like, whereby the passage member 58 is pressed radially inward by the outer cylinder fitting 14 and the inner circumferential surface of the circumferential groove 36. When the covering rubber layer 40 formed in the step is pressed, the passage member 58 is brought into close contact with the circumferential groove 36. Thereby, the inner peripheral side opening of the flow path forming groove 62 provided in the passage member 58 is covered with the covering rubber layer 40, and the pressure relief flow path 64 opened in the circumferential direction is formed as a fluid-tight flow path. At the same time, the incompressible fluid sealed in the first and second fluid chambers 72 and 74 is also filled in the pressure relief flow path 64 communicated with the first and second fluid chambers 72 and 74. It becomes. Further, the pressure relief flow path 64 is communicated with the first and second fluid chambers 72 and 74 through the communication hole 56 formed in the orifice member 48, so that the first and second fluid chambers 72 and 74 are communicated. The pressure fluctuation induced in the step is transmitted to the pressure relief flow path 64 and the flow path closing valve body 68 as the fluid flow of the incompressible fluid from the positive pressure side to the negative pressure side.

  In this case, the orifice member 48 and the passage member 58 are fluid-tightly assembled to the circumferential grooves 34 and 36 through the covering rubber layer 40 at their inner circumferential surfaces and both axial end surfaces. In addition, the outer cylinder fitting 14 is fluidly assembled to the respective outer peripheral surfaces of the orifice member 48 and the passage member 58 via the seal rubber 70. Accordingly, both the orifice member 48 and the passage member 58 are assembled fluid-tightly with respect to the outer cylinder fitting 14 and the metal sleeve 26, and each of the orifice member 48 and the passage member 58, the outer cylinder fitting 14 and the metal sleeve 26 is provided. The occurrence of a short circuit between the first and second fluid chambers 72 and 74 between the members is prevented, and the flow of the sealed fluid between the first and second fluid chambers 72 and 74 is prevented from flowing through the orifice passage 76 and the pressure relief. It occurs only through the flow path 64.

  Under such an assembled state, stopper members 78 are attached to both ends in the axial direction of the inner cylindrical metal member 12 in an extrapolated state. The stopper member 78 includes a stopper support fitting 80 and a stopper rubber 82. The stopper support fitting 80 is a substantially cylindrical member as a whole, and includes a bent portion 84 having one end bent and extending outward in the radial direction. In addition, a stopper rubber 82 is continuously fixed to the radially outer end of the bent portion 84 of the stopper support fitting 80 over the entire circumference in the circumferential direction. In a state where the bent portion 84 and the stopper rubber 82 are positioned, they are assembled to both ends in the axial direction of the inner cylindrical metal member 12 in an extrapolated state. The stopper member 78 causes the relative displacement between the inner cylinder fitting 12 and the outer cylinder fitting 14 by the stopper rubber 82 coming into contact with the metal sleeve 26 when a large vibration is applied to the vibration isolating bush 10. Restricted.

  In the vibration isolating bushing 10 having the above-described structure, vibrations in the direction in which the fluid chambers are opposed to each other in the direction perpendicular to the axis, and vibrations having a frequency at which the orifice passage 76 is tuned are applied to the vibration isolating bushing 10. When input is made, the incompressible fluid sealed in the first and second fluid chambers 72 and 74 is positively caused to flow through the orifice passage 76, and a vibration isolation effect due to the resonance action of the fluid is exhibited. The At that time, the pressure relief flow path 64 is substantially closed by the flow path closing valve body 68, and the pressure fluctuation in the fluid chamber is effectively ensured. It can be prevented from lowering.

  On the other hand, when vibration having a frequency higher than the frequency at which the orifice passage 76 is tuned is input to the vibration isolating bushing 10, the orifice passage 76 is substantially closed by an anti-resonant action, and the fluid flow is reduced. Does not occur. Here, the flow passage closing valve body 68 is elastically deformed by the pressure fluctuation induced in the fluid chamber by the input of vibration, and either one of the pressure relief flow passages 64 is brought into a communication state. As a result, the pressure generated in one fluid chamber by the vibration input is released to the other fluid chamber through the pressure relief flow path 64, and a significant reduction in the vibration isolation performance can be prevented.

  Furthermore, for example, at the time of input of shocking vibration such as overcoming a step, the fluid flow through the orifice passage 76 cannot follow the pressure fluctuation generated in the fluid chamber. When such a shocking vibration is input, a large pressure fluctuation occurs in the first and second fluid chambers 72 and 74. Therefore, the flow path closing valve body 68 is elastically deformed by the applied pressure, and the pressure relief flow. The passage 64 is in a communicating state, and the pressure is released to the other first and second fluid chambers 72 and 74, so that a reduction in the vibration isolation performance can be avoided.

  That is, when vibration is input to the vibration isolating bush 10 in the radial direction, whichever of the first and second fluid chambers 72 and 74 is positive, that is, in the circumferential groove 36. Regardless of which direction of fluid flow occurs in the circumferential direction, any one of the flow paths 64 releases pressure fluctuations induced in the first fluid chamber 72 (second fluid chamber 74) on the positive pressure side. By being in the communication state, it is possible to surely escape to the second fluid chamber 74 (first fluid chamber 72) on the negative pressure side.

  Further, the pressure relief passage 64 is formed by using the passage formation groove 62 formed in the passage member 58 separated from the integrally vulcanized molded product 38, so that the pressure relief passage 64 can be easily formed. In addition to being able to be formed, the flow path length, the flow path cross-sectional area, and the like can be freely taken, and the pressure relief flow path 64 corresponding to the required performance can be realized with a simple structure. In addition, since the metal sleeve 26 and the passage member 58 are both formed of a pressure relief passage 64 by a hard member, the effective sectional area of the pressure relief passage 64 is stably secured, and the pressure relief operation is performed. High reliability is also maintained.

  Further, by forming the flow path forming groove 62 on the inner peripheral surface of the passage member 58, the pressure relief flow path 64 can be easily formed on the inner peripheral side from the outer cylinder fitting 14. Therefore, the flow path closing valve body 68 that covers the opening of the pressure relief flow path 64 can be formed with a protruding height that does not come into contact with the outer cylinder fitting 14. It is possible to avoid wear of the flow path closing valve body 68 and instability of the operation caused by sliding contact with 14.

  Further, the flow path closing valve body 68 is formed so as to protrude integrally with the covering rubber layer 40 formed integrally with the main rubber elastic body 16 on the bottom surface of the circumferential groove 36. As a result, the number of parts can be reduced, and the anti-vibration bush 10 having a structure according to the present invention can be realized with a simple structure.

  Further, since the flow path closing valve body 68 is formed with an urging force that comes into contact with the passage member 58, it is not a shocking large-amplitude vibration, and further has a frequency equal to or lower than the tuning frequency of the orifice passage 76. When vibration is input to the vibration isolating bush 10, the pressure relief flow path 64 is reliably closed by the flow path closing valve body 68 to which the urging force is applied, and the fluid chambers are connected through the orifice passage 76. A sufficient amount of flowing fluid can be ensured, and vibration-proof performance based on the resonance action of the fluid through the orifice passage 76 can be effectively exhibited. In addition, this prevents the blockage failure due to the flow block valve 68 of the pressure relief flow channel 64 due to component dimensional errors and assembly errors.

  In the present embodiment, since the flow path closing valve body 68 is formed near the center in the circumferential direction of the circumferential groove 36, it is integrally molded with the main rubber elastic body 16 regardless of the shape of the pair of pocket portions 42, 44. can do. That is, when the integral vulcanization molded product 38 having the main rubber elastic body 16 and the flow path closing valve body 68 is vulcanized, the pocket portions 42 and 44 are formed depending on the shape of the pocket portions 42 and 44. In order to avoid undercuts due to the convex portions provided in the pair of middle molds that set the side surface shape, it is necessary to fit the middle molds from the radial direction where the pair of pocket parts 42 and 44 face each other. When the middle mold is removed, the channel closing valve body 68 formed to project in a direction substantially perpendicular to the direction in which the pocket portions 42 and 44 face each other causes an undercut depending on the position, but in this embodiment, By forming the flow path closing valve body 68 at the substantially center in the circumferential direction of the circumferential groove 36, the flow path closing valve body 68 is formed in the combination part of the middle mold, and when removing the middle mold Undercut does not occur. As in the present embodiment, the pocket portions 42 and 44 have a substantially flat bottom surface and a shape that extends over the entire length in the direction in which the pair of circumferential grooves 34 and 36 are opposed to each other. When the undercut by the pocket portions 42 and 44 is avoided, the middle mold can be attached from the direction in which the pair of circumferential grooves 34 and 36 face each other. Can be freely set in the circumferential direction.

  Furthermore, the orifice passage 76 and the pressure relief passage 64 are formed by fitting the orifice member 48 and the passage member 58 in the circumferential grooves 34 and 36 in the metal sleeve 26, respectively, and then extrapolating the outer tube fitting 14 and the eight-way restriction. The orifice forming groove 54 formed in the orifice member 48 and the flow path forming groove 62 formed in the passage member 58 are each formed into a fluid-tight flow path by reducing the diameter by, for example. Therefore, the fluid-tight orifice passage 76 and the pressure relief passage 64 can be formed by a simple structure and a manufacturing process, respectively.

  Further, the tuning frequency of the orifice passage 76 is set by the ratio of the passage cross-sectional area: A and the passage length: L: A / L. In this embodiment, the orifice passage 76 has the outer periphery of the metal sleeve 26. By adopting the orifice member 48 formed along the surface and extending to the fluid chambers 72 and 74, the orifice passage 76 can be formed with a sufficient length. Therefore, the degree of freedom of the passage length of the orifice passage 76 can be increased, and the tuning frequency of the orifice passage 76 can be set in a wide frequency range according to the required vibration isolation characteristics.

  Moreover, the axial center part of the inner cylinder metal fitting 12 is made large diameter compared with another part, Therefore The projection area of the axis direction of the inner cylinder metal fitting 12 can be increased. Therefore, when vibration in a direction in which the pair of circumferential grooves 34 and 36 are opposed to each other in the radial direction is input to the vibration isolating bush 10, the inner cylindrical metal member 12 with respect to the main rubber elastic body 16 and the fluid chambers 72 and 74. The projected area of the effective piston area can be made large, and the anti-vibration effect can be advantageously obtained.

  Further, when the stopper member 78 is attached to both end portions in the axial direction of the inner cylinder fitting 12, when a shocking large amplitude vibration is input to the vibration isolating bush 10, the stopper member 78 comes into contact with the outer cylinder fitting 14. Thus, the relative displacement amount of the inner cylinder fitting 12 with respect to the outer cylinder fitting 14 is limited.

  Although some of the embodiments of the present invention have been described above, these are merely examples, and the present invention should not be construed as being limited to specific descriptions in the embodiments.

  For example, in the above-described embodiment, the first and second fluid chambers 72 and 74 are both pressure receiving chambers in which internal pressure fluctuations are positively generated based on elastic deformation of the main rubber elastic body 16 when vibration is input. In addition, relative pressure fluctuations are generated in the two fluid chambers 72 and 74 at the time of vibration input, and fluid flow is generated between the first and second fluid chambers 72 and 74 through the orifice passage 76. ing. However, for example, one of the fluid chambers is a pressure receiving chamber in which an internal pressure fluctuation occurs due to vibration input, and is configured to have substantially the same structure as the first or second fluid chambers 72 and 74 in the above embodiment. The other fluid chamber is configured as an equilibrium chamber in which a part of the wall portion is made of a flexible film that can be easily deformed and volume change is allowed, as shown in Japanese Patent Application Laid-Open No. 2003-120744. The present invention can also be applied to the vibration isolating bush.

  In the above embodiment, the pressure relief flow path 64 is formed by covering the flow path forming groove 62 formed in the inner circumferential surface of the passage member 58 with the bottom surface of the circumferential groove 36. For example, the flow path 64 may be formed in the passage member 58 so as to penetrate the passage member 58 in the circumferential direction and have a tunnel structure, and at least one opening portion has a diameter larger than that of the inner peripheral surface of the outer cylinder fitting 14. What is necessary is just to be opened in the direction inner side.

  In the embodiment, two flow path forming grooves 62 are formed for one passage member 58, and two pressure relief passages 64 are realized by one passage member 58. Only one relief channel may be formed for one passage member 58, and a plurality of three or more concave grooves may be formed for one passage member. A plurality of relief flow paths may be formed for one passage member.

  Furthermore, the number of passage members 58 to be assembled to the circumferential groove 36 is not necessarily one, and a plurality of passage members 58 can be assembled. Specifically, for example, one relief groove is formed for one passage member, and two passage members 58 are assembled to the circumferential groove 36, thereby opening openings on the opposite sides in the circumferential direction. Two relief channels superimposed on the elastic valve body can be formed on one circumferential groove 36.

  Further, the flow path closing valve body 68 does not necessarily have to be formed integrally with the main rubber elastic body 16, and further, the material does not necessarily have to be rubber if the material can be elastically deformed. Specifically, for example, a metal leaf spring protrudes radially outward from the bottom surface of the circumferential groove 36 and is fixed to the metal sleeve 26, and the leaf spring is covered with a seal rubber layer to form the elastic valve body. It can also be realized.

  Furthermore, in the above-described embodiment, the flow path closing valve body 68 is pressed against the opening of the pressure relief flow path 64 by an urging force in advance in order to reliably close the opening of the pressure relief flow path 64. In addition, it is not always necessary to apply a biasing force to the flow path closing valve body 68, and the flow path closing valve body 68 may be set appropriately depending on the required vibration isolating performance. In the case where no urging force is applied, even if there is a slight gap between the opening of the pressure relief flow path 64 and the opening of the flow path closing valve body 68, the fluid tightness can be maintained by the action of pressure.

  Furthermore, in the above-described embodiment, the flow path closing valve body 68 is formed at the substantially center in the circumferential direction of the circumferential groove 36, and the central opening 66 of the pressure relief flow path 64 overlaps the flow path closing valve body 68. Although the passage member 58 has a crank shape so as to be matched, the formation position of the flow path closing valve body 68 is not limited at all by the embodiment. Specifically, for example, the passage member 58 may be a substantially rectangular block body, and the flow path closing valve body 68 may be formed to protrude at substantially both ends in the circumferential direction of the circumferential groove 36. It can be realized with a simpler shape.

  In addition, the shape of the pair of pocket portions 42 and 44 is not limited at all by the above-described embodiment, and may be a concave dent that opens through the opening windows 28 and 30 provided in the metal sleeve 26. In the case where the flow path closing valve body 68 is formed so as to protrude in a portion other than the center in the circumferential direction in the circumferential groove 36, an undercut is generated in the molding die depending on the shape of the pocket portions 42 and 44 and the mold splitting direction. There is a possibility, and for the reason of manufacturing, it is desirable to adopt the shape of the pocket portions 42 and 44 in which the bottom surface and both end surfaces in the circumferential direction are substantially flush as shown in the embodiment.

  Further, the passage member 58 and the orifice member 48 do not need to be made of resin as in the above-described embodiment, and various metal materials and the like can be appropriately selected and employed.

  Further, in the present embodiment, the orifice passage 76 is formed in a form extending in the circumferential direction by using the orifice member 48 formed separately, but the specific shape of the orifice passage 76 is required to be vibration-proof performance. However, the present invention is not limited to the above embodiment. Further, for the formation of the orifice passage 76, it is desirable to use the separately formed orifice member 48 for stabilization of vibration isolation performance, but it is not always necessary to adopt it. Specifically, for example, an orifice passage is formed between the small-diameter portion 32 of the metal sleeve 26 and the outer tube fitting 14, or the main rubber elastic body 16 is positioned in a direction in which the pair of pocket portions 42 and 44 face each other. It can also be formed as a hole penetrating through.

  Moreover, in the said embodiment, although the center part of the axial direction was expanded, the inner cylinder metal fitting 12 does not necessarily need to be expanded, and it is good also as a cylindrical shape without the unevenness | corrugation to radial direction.

  In the above-described embodiment, the stopper members 78 attached to both ends in the axial direction of the inner cylindrical metal member 12 are not necessarily provided, and even when provided, the form is not limited by the embodiment. .

  In addition, although not enumerated one by one, the present invention can be implemented in a mode with various changes, modifications, improvements, and the like based on the knowledge of those skilled in the art, and such embodiments are not limited to the present invention. It goes without saying that all are included in the scope of the present invention without departing from the spirit of the present invention.

It is a longitudinal cross-sectional view which shows the vibration proof bush as one Embodiment of this invention, Comprising: It is a figure equivalent to the II cross section in FIG. It is a cross-sectional view of the vibration isolating bush in FIG. It is a longitudinal cross-sectional view which shows the integral vulcanization molded product which comprises the vibration proof bush in FIG. 1, Comprising: It is a figure corresponded in the III-III cross section in FIG. FIG. 4 is a front view of the integrally vulcanized molded product shown in FIG. 3. It is a rear view which shows the orifice member which comprises the vibration proof bush in FIG. FIG. 6 is a plan view of the orifice member shown in FIG. 5. FIG. 7 is a front view of the orifice member shown in FIGS. 5 and 6. It is a perspective view which shows the channel | path member which comprises the anti-vibration bush in FIG. FIG. 9 is a bottom view of the passage member shown in FIG. 8. It is a front view which shows the attachment state of the channel | path member with respect to the integral vulcanization molded product shown by FIG. It is a perspective view of the integral vulcanization molded product shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Anti-vibration bush 12 Inner cylinder metal fitting 14 Outer cylinder metal fitting 16 Main body rubber elastic body 26 Metal sleeve 28 Open window 30 Open window 32 Small diameter part 34 Circumferential groove 36 Peripheral groove 38 Integrated vulcanization molded product 42 Pocket part 44 Pocket part 48 Orifice member 58 passage member 64 pressure relief flow path 68 flow path closing valve body 72 first fluid chamber 74 second fluid chamber 76 orifice passage

Claims (7)

A main rubber elastic body is disposed between the radially opposite surfaces of the inner shaft member and the intermediate sleeve spaced apart on the outer peripheral side, and the outer cylinder member is fitted and fixed to the intermediate sleeve. A plurality of fluid chambers in which relative pressure fluctuations are generated at the time of vibration input between the radially opposed surfaces of the inner shaft member and the outer cylindrical member connected by an elastic body are separated in the circumferential direction. In a fluid-filled cylindrical vibration damping device in which an orifice passage that communicates a plurality of fluid chambers with each other is formed, and a vibration damping effect is obtained based on a fluid action of fluid that flows through the orifice passage when vibration is input. ,
A plurality of window portions are provided in the intermediate sleeve, a plurality of pocket portions that open to the outer peripheral surface through the respective window portions are formed, and the plurality of pocket portions are covered with the outer cylinder member in a fluid-tight manner. A fluid groove is formed on the outer circumferential surface of the intermediate sleeve in the axial direction and extends in the circumferential direction between the plurality of windows, and is provided separately from the groove. The passage member is fitted and the outer cylinder member presses the passage member fluid-tightly into the concave groove and fixedly assembled, thereby extending in the circumferential direction and extending between the plurality of fluid chambers. A relief flow path is formed by the passage member, and at least one opening of the relief flow path is spaced radially inward from the inner peripheral surface of the outer cylinder member, and the concave groove of the intermediate sleeve is formed. From the bottom to the opening A protruding elastically deformable elastic valve body is formed at a protruding height that does not reach the inner peripheral surface of the outer cylinder member, and the circumference of the passage member provided with the one opening of the relief flow path while superimposed on one end face direction Ru brought substantially close the opening of the relief channel, the elastic valve with pressure applied to the elastic valve body through the relief channel when a large amplitude vibration is input body fluid-filled cylindrical vibration damping device is a plurality of fluid chambers through the relief channel by elastically deforming, characterized in that as can communicate.
  Two of the relief flow paths are formed by the passage member, and the elastic valve body is disposed in the passage so as to substantially close the openings to the fluid chambers on the opposite sides of the two relief flow paths. The fluid-filled cylindrical vibration damping device according to claim 1, wherein one each is formed on both sides in the circumferential direction of the member.   3. The fluid-filled cylindrical proof according to claim 1, wherein the elastic valve body is assembled in an abutting state with an opening of the relief flow path on the circumferential end surface of the passage member with an elastic biasing force. Shaker.   In the intermediate sleeve, a pair of window portions are formed so as to be opposed to each other in the radial direction, and a pair of pocket portions that are opened through the respective window portions are covered with outer cylinder members, whereby an inner shaft member is formed. Forming a pair of fluid chambers located on both sides sandwiched in the radial direction, and forming a first groove and a second groove across the end portions on both sides in the circumferential direction of the fluid chamber, The fluid-filled cylindrical vibration isolator according to any one of claims 1 to 3, wherein the passage member is assembled to the first groove, and the orifice passage is formed to the second groove.   The main rubber elastic body is disposed over the entire circumference in the circumferential direction between the radially opposed surfaces of the inner shaft member and the outer cylindrical member, and is opened on both sides of the inner shaft member. 5. The fluid sealing according to claim 1, wherein a pair of pocket portions are formed in the main rubber elastic body, and each of the pocket portions is opened through the pair of windows provided in the intermediate sleeve. Type cylindrical vibration isolator.   The fluid-filled cylindrical vibration isolator according to any one of claims 1 to 5, wherein a seal rubber layer is formed on the inner surface of the concave groove in the intermediate sleeve. 7. The relief channel is formed by forming a communication groove that opens on an inner peripheral surface of the passage member, and covering the communication groove with a bottom surface of the concave groove in the intermediate sleeve. The fluid-filled cylindrical vibration isolator as described.

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