JP2006250180A - Vibration control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To support an input load by an air spring and to set damping with respect to vibrations sufficiently. <P>SOLUTION: In a vibration control device 10, elastic rolling elements 62 are interposed between an outer circumferential side rolling face 26 of an outer cylinder member 12 and an inner circumferential side rolling face 36 of an inner cylinder member 28 along a radial direction in a compression state, the rolling elements 62 are rolled between the elastic rolling elements 62 and the inner circumferential side rolling face 36 along with relative movement along an axial direction of the outer cylinder member 12. Since shear deformation is generated in the elastic rolling elements 62 in the input of vibrations, the damping with respect to the vibrations are generated by action of internal friction or the like of the elastic rolling elements. In the vibration control device, an internal volume of the air chamber 76 is increased/decreased in the input of the vibrations and fluid communicates between the air chamber 76 and a balance chamber 60 through an orifice passage 48, so that resistance of air passing through the orifice passage 48 generates the damping with respect to the vibrations. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention is used to support vibration generating parts such as an engine, a motor, and a compressor that generate vibration on a vibration receiving part such as a floor or a vehicle body, and to prevent vibration transmission from the vibration generating part to the vibration receiving part. The present invention relates to a vibration isolator.

  As an anti-vibration device for supporting a machine for generating vibrations for general industrial use, an anti-vibration rubber using rubber and a combination of a metal coil spring and a damper are known ( For example, see Patent Document 1).

  In the case of a machine that generates low-frequency vibrations that cannot be vibration-proof unless the natural frequency of the support system in the vibration-proof device is 10 Hz or less, the vibration-proof rubber requires shear support or tilt support. In such a support form, there were problems such as sag and durability. In the case of anti-vibration rubber, it is generally desirable to use it on the compression side, considering the durability and sag during load support. The natural frequency of the system is 10 Hz or more. As a result, the input frequency range where vibration can be prevented is 14 Hz (from the vibration transmissibility curve in the vibration isolation theory, the forced vibration is 1.4 times or more the natural frequency of the support system. If it is not a number, the vibration transmissibility will not be less than 1).

  On the other hand, when an air chamber partitioned from the outside is provided in the apparatus and an air spring that bears a supporting load by the air pressure in the air chamber is used, a natural frequency of 10 Hz or less can be obtained. Since it does not damp itself, it must be equipped with a damper. In such an anti-vibration device using an air spring, for example, in order to obtain damping against vibration, an air chamber whose internal volume expands or contracts with vibration input, and this air chamber is filled with air of a pressure corresponding to the input load. An orifice communicating with the equilibrium chamber is provided, and attenuation is obtained by resistance of air flowing through the orifice when vibration is input. However, it is difficult to sufficiently increase the damping against vibration only by the resistance of air passing through such an orifice. For this reason, when a larger damping is required, it is necessary to add a damper mechanism such as a hydraulic damper or a friction damper to the apparatus.

In addition, in a vibration isolator using an air spring, for example, a vibration input side mounting member and a support side mounting bracket are connected by a bellows, and the bellows, the vibration input side mounting member and the support side mounting member are externally connected. Some of them constitute an air chamber partitioned from However, when the mounting member on the vibration input side and the mounting bracket on the support side are connected by the bellows, the bellows generally has low rigidity in the direction (lateral direction) perpendicular to the load support direction. For example, it is necessary to provide a restriction mechanism such as a link mechanism for the moving direction of the attachment member on the vibration input side and the attachment member on the support side.
Japanese Patent Application Laid-Open No. 2002-295587

  However, when a damper mechanism or a movement direction limiting mechanism is provided in a vibration isolator using an air spring, the number of parts increases and the structure of the apparatus becomes complicated, and when the damper mechanism is omitted and attenuation is obtained only by an orifice. May have insufficient damping against vibration.

  In view of the above facts, an object of the present invention is to provide a vibration isolator having a simple structure that can support an input load with an air spring and can set a sufficiently large damping against vibration.

  In order to achieve the above object, a vibration isolator according to claim 1 of the present invention is connected to one of a vibration generating portion and a vibration receiving portion, and includes a first mounting member formed in a substantially cylindrical shape, and a vibration generating portion. And a second mounting member that is connected to the other of the vibration receiving portions and disposed on the inner peripheral side of the first mounting member, and is formed in a cylindrical shape with both ends opened, and one end portion of the first mounting member While being fixed to the surface part over the entire circumference, the other end part is fixed to the surface part of the second mounting member over the entire periphery, and the one end part and the other end part are respectively movable along the axial direction. The bellows member is supported by the bellows member, the first mounting member, the second mounting member, and the pressure chamber partitioned from the outside by the elastic rolling element, and the first mounting member and the second mounting member. An equilibrium chamber filled with a fluid having a pressure corresponding to the input load A restriction passage that allows the pressure chamber and the equilibrium chamber to communicate with each other, and a substantially annular shape made of an elastic material, and between the inner peripheral surface of the first mounting member and the outer peripheral surface of the second mounting member The inner surface of the first mounting member and the second mounting are interposed according to relative movement along the axial direction of at least one of the first mounting member and the second mounting member. And an elastic rolling element that rolls between the outer peripheral surface of the member.

  In the vibration isolator according to claim 1 of the present invention, the elastic rolling element is interposed between the inner peripheral surface of the first mounting member and the outer peripheral surface of the second mounting member so as to be compressed along the radial direction. Vibration input by rolling between the inner peripheral surface of the outer cylindrical member and the outer peripheral surface of the inner cylindrical member in accordance with the relative movement along the axial direction of at least one of the first mounting member and the second mounting member. Sometimes, the elastic rolling element can cause shear deformation while rolling between the inner peripheral surface of the first mounting member and the outer peripheral surface of the second mounting member, Damping against vibration can be obtained by the action of internal friction or the like.

  Furthermore, in the vibration isolator according to the first aspect, when the vibration is input, the internal volume of the pressure chamber expands and contracts, and the fluid moves back and forth between the pressure chamber and the equilibrium chamber through the restriction passage. Damping against vibration can also be obtained by the flow resistance.

  Therefore, according to the vibration isolator according to claim 1, in addition to being able to generate vibration damping due to the flow resistance of the fluid passing through the restricted passage, the inner peripheral surface of the first mounting member and the outer periphery of the second mounting member Attenuation against vibration can also be generated by an elastic rolling element that shears and deforms while rolling with the surface, so that attenuation against input vibration can be made sufficiently large, and vibration transmitted to the vibration receiving part can be sufficiently low level. Can be.

  Moreover, in the vibration isolator which concerns on Claim 1, according to the relative movement along the axial direction of at least one of the 1st attachment member and the 2nd attachment member, the elastic rolling element and the inner peripheral surface of the 1st attachment member, and the 2nd attachment member By rolling between the outer peripheral surface, the elastic rolling element generates damping, and the moving direction can be limited so that the first mounting member and the second mounting member move only in the axial direction. If it is matched with the axial direction, there is no need to provide a movement direction limiting mechanism independently as in the prior art.

  As a result, according to the vibration isolator according to the first aspect, the structure of the damper mechanism can be simplified, and it is not necessary to provide an independent moving direction limiting mechanism. It can be simplified.

  According to a second aspect of the present invention, there is provided the vibration isolator according to the first aspect, wherein a tension stopper means for restricting a relative displacement of the first mounting member and the second mounting member in the axial direction in the axial direction is provided. It is characterized by that.

  According to a third aspect of the present invention, there is provided the vibration isolator according to the first or second aspect, wherein the first stopper and the second stopper limit the relative displacement of the first mounting member and the second mounting member in the axial direction to the compression side. Is provided.

  A vibration isolator according to claim 4 is the vibration isolator according to claim 1, 2 or 3, wherein at least one of the inner peripheral surface of the first mounting member and the outer peripheral surface of the second mounting member is disposed on the shaft. It is characterized by being formed as a tapered surface inclined with respect to the direction.

  As described above, according to the vibration isolator of the present invention, the input load can be supported by the air spring, and attenuation against vibration can be set sufficiently large.

  Hereinafter, a vibration isolator according to an embodiment of the present invention will be described with reference to the drawings.

(First embodiment)
1 and 2 show a vibration isolator according to an embodiment of the present invention. Note that the symbol S indicates the axial center of the apparatus, and the following description will be made with the direction along the axial center S as the axial direction.

  As shown in FIG. 1, the vibration isolator 10 is formed in a substantially cylindrical shape as a whole, and the vibration isolator 10 has one end side along the axial direction (the upper end in FIG. 1B). The outer cylinder member 12 formed in a substantially hat shape is disposed on the side). The outer cylinder member 12 is opened from the lower end side, and the top surface side is closed by a disc-shaped top plate portion 14. A base end portion of a round bar-shaped stopper shaft 16 is fixed to the center portion of the bottom surface of the top plate portion 14, and the stopper shaft 16 projects downward from the top plate portion 14 along the axis S.

  The stopper shaft 16 is provided with a male screw portion 18 at the tip, and this nut 22 is screwed. The stopper shaft 16 is fitted with a ring-shaped stopper ring 20 on the base end side of the nut 22, and the stopper ring 20 is fixed to the upper surface of the nut 22. A ring-shaped stopper rubber 24 is fixed to the outer peripheral side of the stopper shaft 16 on the lower surface side of the top plate portion 14.

  On the inner peripheral surface of the outer cylinder member 12, an outer peripheral side rolling surface 26 formed of a tapered surface (conical curved surface) inclined with respect to the axial direction is formed on the lower end side. The outer cylinder member 12 has a certain inclination that gradually increases the inner diameter of the outer cylinder member 12 from the upper end toward the lower end.

  The vibration isolator 10 is provided with an inner cylinder member 28 formed in a substantially cylindrical shape at an intermediate portion along the axial direction. The inner cylinder member 28 is provided with an upper cylindrical portion 30 having an inner diameter and an outer diameter constant on the upper end side, and a flange-shaped intermediate step portion 32 extending from the lower end portion of the upper cylindrical portion 30 to the outer peripheral side. Is formed. The inner cylindrical member 28 is coaxially provided with a lower cylindrical portion 34 having an inner diameter and an outer diameter larger than those of the upper cylindrical portion 30 on the lower end side of the upper cylindrical portion 30 through the intermediate step portion 32. The upper cylindrical portion 30 has an outer peripheral surface as an inner peripheral rolling surface 36 from a cylindrical curved surface parallel to the axial direction. Thus, the radial width gradually increases from the lower end side to the upper end side between the outer peripheral side rolling surface 26 of the outer cylindrical member 12 and the inner peripheral side rolling surface 36 of the inner cylindrical member 28. A narrowing gap is formed.

  On the lower end side of the lower cylindrical portion 34, an enlarged diameter portion 40 having an increased inner diameter and outer diameter is formed via a flange-shaped lower stepped portion 38 extending to the outer peripheral side. The flange part 42 extended from the lower end part of this to the outer peripheral side is formed. A thick disc-shaped lid member 44 is fitted into the enlarged diameter portion 40, and the lid member 44 closes the lower end portion of the lower cylindrical portion 34. The lid member 44 is integrally formed with an insertion portion 46 which is inserted into the inner peripheral side of the lower cylindrical portion 34 on the upper side thereof. The lid member 44 is formed with an orifice passage 48 penetrating along the axis S between the upper end surface and the lower end surface.

  In the vibration isolator 10, a bottomed cylindrical partition wall member 50 is disposed below the inner cylinder member 28. The inner diameter of the partition member 50 is smaller than the inner diameter of the enlarged diameter portion 40 in the inner cylinder member 28, and a flange portion 52 extending to the outer peripheral side is formed at the upper end portion. The partition wall member 50 abuts the flange portion 52 against the flange portion 42 of the lower cylindrical portion 34, and abuts the inner peripheral side of the flange portion 52 on the upper end surface against the lower surface portion of the lid member 44. In the vibration isolator 10, the flange portion 52 of the partition member 50 and the flange portion 42 of the lower cylindrical portion 34 are fastened and fixed so as to be in pressure contact with each other by a fastening member (not shown) made of a bolt or the like.

  In the vibration isolator 10, an annular seal ring 54 is interposed between the flange portions 42 and 52 in a compressed state, and the lower end surface of the lower step portion 38 and the upper surface portion of the lid member 44 in the lower cylindrical portion 34. A pair of seal rings 56 and 58 are interposed between the two. Thereby, the space between the lower cylindrical portion 34 and the lid member 44 and the space between the lower cylindrical portion 34 and the partition wall member 50 are sealed so as to be airtight.

  Here, the columnar space formed inside the partition wall member 50 is an equilibrium chamber 60 filled with air of a predetermined pressure by an air compressor 72 described later. The equilibrium chamber 60 is formed in the lid member 44. It communicates with a space SI formed on the inner peripheral side of the inner cylinder member 28 through a drilled orifice passage 48.

  In the vibration isolator 10, the stopper shaft 16 of the outer cylinder member 12 is inserted into the inner peripheral side of the upper cylindrical portion 30 and the lower cylindrical portion 34 of the inner cylinder member 28, and is fixed to the distal end side of the stopper shaft 16. The nut 22 and the stopper ring 20 are supported on the inner peripheral side of the lower cylindrical portion 34. The stopper ring 20 has an outer diameter larger than the inner diameter of the upper cylindrical portion 30. Thereby, in the vibration isolator 10, when the outer cylinder member 12 moves (rises) relatively upward along the axial direction from the position (initial position) shown in FIG. When the distance rises by a distance LU equal to the distance between 20 and the intermediate stepped portion 32, the stopper ring 20 reaches a tension limit point where it abuts against the intermediate stepped portion 32 of the inner cylindrical member 28.

  Further, in the vibration isolator 10, when the outer cylinder member 12 is moved (lowered) relatively downward along the axial direction from the initial position, the outer cylinder member 12 has the stopper rubber 24 and the upper end surface of the inner cylinder member 28. Is lowered by a distance LD equal to the interval of, the stopper rubber 24 of the outer cylinder member 12 reaches a compression limit point where it presses against the upper end surface of the upper cylindrical portion 30. At this time, since the stopper rubber 24 is formed of a rubber material, it is possible to prevent the occurrence of hitting sound when the stopper rubber 24 collides with the upper cylindrical portion 30. In addition, the elastic material such as rubber is fixed to the upper surface side of the stopper ring 20, or the stopper ring 20 is formed of an elastic material such as rubber, thereby generating a hitting sound when the outer cylindrical member 12 moves to the tension limit point. You may make it prevent.

  As shown in FIG. 1, the inner cylindrical member 28 is disposed coaxially with the outer cylindrical member 12, and the upper cylindrical portion 30 is inserted into the inner peripheral side of the outer cylindrical member 12. Between the outer peripheral side rolling surface 26 of the outer cylinder member 12 and the outer peripheral side rolling surface 26 of the upper cylindrical portion 30, a rubber such as NR (natural rubber) or NBR (nitrile rubber) is formed in an annular shape. The formed elastic rolling element 62 is interposed. Here, by molding the elastic rolling element 62 with rubber such as NR or NBR, even if the elastic rolling element 62 is always used under a condition where a compressive load is applied, the permanent deformation generated in the elastic rolling element 62 is sufficiently obtained. It can be made small, and damage due to cracks and the like does not occur over a long period of time. The elastic rolling element 62 is in a non-deformed state in which no elastic deformation occurs, and has a circular cross section along the radial direction.

  The elastic rolling element 62 is inserted into the outer peripheral side of the upper cylindrical portion 30 while being inserted into the inner peripheral side of the outer cylinder member 12. At this time, the elastic rolling elements 62 are in pressure contact with the outer circumferential rolling surface 26 of the outer cylinder member 12 and the inner circumferential rolling surface 36 of the upper cylindrical portion 30, respectively, so that the outer circumferential rolling surface 26 and the inner circumferential rolling surface are rolled. The surface 36 is always compressed along the radial direction. The elastic rolling element 62 in a compressed state is elastically deformed into a substantially elliptical shape in which the cross-sectional shape is slightly inclined so as to approach the axial center S side upward with respect to the axial direction. ing.

  In the vibration isolator 10, as described above, the outer cylinder member 12 is movable relative to the inner cylinder member 28 between the tension limit point and the compression limit point along the axial direction. When the cylindrical member 12 moves in the tension direction or the compression direction between the tension limit point and the compression limit point, the elastic rolling element 62 moves along the outer peripheral side rolling surface 26 and the inner peripheral side rolling surface according to the movement of the outer cylindrical member 12. Roll between 36. At this time, when the outer cylinder member 12 moves in the pulling direction (upward), the elastic rolling element 62 rotates in the direction of the arrow RT shown in FIG. 1 and the outer cylinder member 12 moves in the compression direction. When moving, the cross section rotates in the direction of arrow RP shown in FIG.

  As shown in FIG. 1, the vibration isolator 10 is partitioned on the inner peripheral side of the outer cylindrical member 12 from the outside by the outer cylindrical member 12 and the elastic rolling element 62, and on the inner peripheral side of the inner cylindrical member 28. A space SO communicating with the formed space SI is formed.

  In the vibration isolator 10, a substantially thin cylindrical bellows member 64 is disposed on the outer peripheral side of the outer cylinder member 12 and the inner cylinder member 28. The bellows member 64 is formed using a rubber material as a base material, and a reinforcing cord 65 made of high-tensile glass fiber, metal wire, resin fiber, or the like extends in the circumferential direction between an outer peripheral surface and an inner peripheral surface. It is inserted to do. The bellows member 64 is inserted with one reinforcing cord 65 spirally wound so that the pitch along the axial direction is substantially constant, or a plurality of reinforcing cords 65 each formed in an annular shape. Are inserted so that the pitch along the axial direction is substantially constant. As a result, the bellows member 64 can be easily bent and deformed in a U shape at an arbitrary portion between the upper end portion and the lower end portion, but is expanded toward the outer peripheral side by the reinforcing cord 65 or contracted toward the inner peripheral side. To be prevented.

  A cored bar member 66 formed in a cylindrical shape with a narrow width along the axial direction is vulcanized and bonded to the bellows member 64 at the upper end part of the outer peripheral surface, and a cored bar member 67 is inserted into the lower end part. One cored bar member 66 is fitted and inserted through the upper end portion of the bellows member 64 in the vicinity of the substantially central portion of the outer peripheral surface of the outer cylindrical member 12, and the outer peripheral surface of the outer cylindrical member 12 through the upper end portion of the bellows member 64. It is fixed to the entire circumference.

  The other metal core member 67 is fitted and inserted into the upper end of the outer peripheral surface of the lower cylindrical portion 34 via the lower end portion of the bellows member 64, and the outer peripheral surface of the lower cylindrical portion 34 via the lower end portion of the bellows member 64. It is fixed to the entire circumference. At this time, the bellows member 64 is formed with a slack portion 68 curved in a U shape between the upper end portion and the lower end portion. Thereby, the bellows member 64 can move along the axial direction between the tension limit point and the compression limit point by changing the size of the slack portion 68 so that the upper end portion is integrated with the outer cylinder member 12. become. On the inner peripheral side of the bellows member 64, a space SB partitioned from the outside by the bellows member 64, the outer cylinder member 12, the elastic rolling element 62, and the inner cylinder member 28 is formed.

  As shown in FIG. 1, a plurality of ventilation holes 70 (for example, for example) penetrating the inner cylinder member 28 along the radial direction are formed at the boundary between the upper cylindrical portion 30 and the intermediate step portion 32 in the inner cylinder member 28. 4 holes at 90 ° intervals). These vent holes 70 communicate the space SI on the inner peripheral side of the inner cylinder member 28 with the space SB on the inner peripheral side of the bellows member 64. Thereby, in the vibration isolator 10, the space SO on the inner peripheral side of the outer cylinder member 12, the space SI on the inner peripheral side of the inner cylinder member 28, and the space SB on the inner peripheral side of the bellows member 64 communicate with each other. SI and SB form an air chamber 76 partitioned from outside in the apparatus. The air chamber 76 communicates with the equilibrium chamber 60 in the partition wall member 50 through the orifice passage 48 of the lid member 44.

  As shown in FIG. 1, the vibration isolator 10 is provided with an air compressor 72 connected to the equilibrium chamber 60 through a pressure pipe 74. The air compressor 72 includes a pressure adjustment mechanism (not shown), and compresses air into the equilibrium chamber 60 so that the air pressure in the equilibrium chamber 60 is maintained at a pressure (set pressure) set by the pressure adjustment mechanism. Supply or leak the air in the equilibrium chamber 60 to the outside. At this time, since the air is communicated with each other through the orifice passage 48, the air pressure in the air chamber 76 becomes substantially equal to the air pressure in the equilibrium chamber 60.

  In the vibration isolator 10 of the present embodiment, the outer cylinder member 12 is connected and fixed to a vibration generating portion such as an engine, a motor, and a compressor via a bracket member (not shown), and the inner cylinder member 28 is connected to the partition member 50 and It is connected and fixed to vibration receiving portions such as a floor, a frame, and a vehicle body via a bracket member (not shown). Thereby, the vibration isolator 10 elastically supports the vibration generating unit on the vibration receiving unit while receiving an input load from the vibration generating unit.

  At this time, the air filled in the air chamber 76 acts as an air spring for supporting the input load, that is, for generating a reaction force equal to the input load. Therefore, the air pressure in the air chamber 76 and the equilibrium chamber 60 is set to a magnitude corresponding to the input load to the vibration isolator 10 by the air compressor 72. Specifically, the air pressure in the air chamber 76 and the equilibrium chamber 60 is such that the outer cylinder member 12 is in a state where the vibration isolator 10 receives a static load from the vibration generating unit, as shown in FIG. It is set so as to be located at a position near the center between the tension limit point and the compression limit point or a slightly upper position (initial position).

  At this time, in the vibration isolator 10, when the input load increases with the air pressure in the air chamber 76 kept constant, the outer cylinder member 12 moves in the compression direction (downward) as shown in FIG. The internal volume of the air chamber 76 is reduced. On the contrary, when the input load decreases while the air pressure in the air chamber 76 is kept constant, the outer cylinder member 12 moves in the pulling direction (upward), and the internal volume of the air chamber 76 is expanded.

  In the vibration isolator 10 according to the present embodiment, the load from the vibration generating unit is supported by the air pressure filled in the air chamber 76, thereby comparing with the vibration isolator using a rubber elastic body as a spring element. The natural frequency of the device (support system) can be set to a low value (for example, less than 10 Hz).

  Next, the operation of the vibration isolator 10 according to the present embodiment will be described.

  In the vibration isolator 10, when a load is input from the vibration generating unit or the vibration receiving unit, the air compressor 72 is operated, compressed air is supplied into the equilibrium chamber 60 by the air compressor 72, or air is supplied from the equilibrium chamber 60. By leaking, the air pressure in the equilibrium chamber 60 is adjusted to a set pressure corresponding to the input load. Thereby, in the vibration isolator 10, the air pressure in the air chamber 76 also becomes a set pressure by the air compressor 72, and the input load is supported by the air pressure in the air chamber 76.

  In the vibration isolator 10, when vibration is input from the vibration generating unit, the outer cylinder member 12 is relatively moved (vibrated) in the tension direction and the compression direction in synchronization with the input of the vibration, and the relative movement of the outer cylinder member 12 is performed. Accordingly, the elastic rolling element 62 rolls between the outer circumferential rolling surface 26 of the outer cylindrical member 12 and the inner circumferential rolling surface 36 of the inner cylindrical member 28. At this time, since the elastic rolling element 62 is compressed along the radial direction between the outer cylinder member 12 and the inner cylinder member 28, the elastic rolling element 62 is between the outer circumferential rolling surface 26 and the inner circumferential rolling surface 36. In the elastic rolling element 62 that rolls at, shear deformation along the radial direction occurs in the cross section along the radial direction. As a result, the elastic rolling element 62 generates damping against vibration due to internal friction or the like accompanying shear deformation.

  Further, in the vibration isolator 10, when vibration is input from the vibration generating unit, the outer cylinder member 12 is relatively moved (vibrated) in the tension direction and the compression direction in synchronization with the input of the vibration, and the outer cylinder member 12 is relatively moved. The internal volume of the air chamber 76 expands and contracts as it moves. At this time, since the air chamber 76 communicates with the equilibrium chamber 60 through the orifice passage 48 formed in the lid member 44, air flows between the air chamber 76 and the equilibrium chamber 60 through the orifice passage 48. Come and go. Thereby, in the vibration isolator 10, the vibration is also attenuated by the flow resistance of the air flowing through the orifice passage 48 when the vibration is input.

  As described above, in the vibration isolator 10 according to the present embodiment, the elastic rolling element 62 is interposed between the outer peripheral rolling surface 26 of the outer cylindrical member 12 and the inner peripheral rolling surface 36 of the inner cylindrical member 28. By being interposed so as to be compressed along the radial direction and rolling between the outer peripheral rolling surface 26 and the inner peripheral rolling surface according to the relative movement along the axial direction of the outer cylinder member 12. At the time of vibration input, the elastic rolling element 62 can roll between the outer peripheral side rolling surface 26 and the inner peripheral side rolling surface 36, and shear deformation can be caused by the elastic rolling element 62. Damping with respect to vibration can be obtained by the action of the internal friction of the rolling element 62 or the like.

  Furthermore, in the vibration isolator 10 according to the present embodiment, the internal volume of the air chamber 76 expands and contracts when vibration is input, and fluid flows back and forth between the air chamber 76 and the equilibrium chamber 60 through the orifice passage 48. Attenuation against vibration can also be obtained by the flow resistance of air passing through the passage 48.

  Therefore, according to the vibration isolator 10 according to the present embodiment, in addition to being able to generate vibration attenuation due to the flow resistance of the air passing through the orifice passage 48, the outer peripheral rolling surface 26 and the inner peripheral rolling surface. Since the elastic rolling element 62 that shears and deforms while rolling with the vibration can also generate damping with respect to the input vibration, the damping with respect to the input vibration can be sufficiently increased, and the vibration transmitted to the vibration receiving portion can be sufficiently low. it can.

  Further, in the vibration isolator 10 according to the present embodiment, the elastic rolling element 62 rolls between the outer circumferential rolling surface 26 and the inner circumferential rolling surface 36 in accordance with the relative movement along the axial direction of the outer cylindrical member 12. As a result, the elastic rolling element 62 generates a damping, and the moving direction can be limited so that the outer cylinder member 12 moves only in the axial direction substantially coincident with the load input direction. There is no need to provide a separate limiting mechanism.

  Therefore, according to the vibration isolator 10 according to the present embodiment, the damping mechanism can be greatly simplified and the moving direction is limited as compared with a vibration isolator that obtains attenuation using a hydraulic damper, a friction damper, or the like. Since it is not necessary to provide a mechanism independently, the number of parts of the apparatus can be reduced and the apparatus structure can be simplified.

  Further, in the vibration isolator 10 according to the present embodiment, the rubber elastic body is compressed and deformed to support the support load by supporting the input load from the vibration generating unit by the pressure of the air filled in the air chamber 76. Compared to the case, the natural frequency of the device (support system) can be significantly reduced, so that the natural frequency of the device can be easily set to a sufficiently low value, for example, less than 10 Hz.

  As a result, according to the vibration isolator 10, even if the frequency range of vibration input from the vibration generating unit is low (for example, less than 14 Hz), the vibration transmissibility with respect to such low frequency range vibration is less than 1. Since the vibration input from the vibration generator can be reliably absorbed, the vibration transmitted from the vibration generator to the vibration receiver can be made sufficiently low.

  In the vibration isolator 10 according to the present embodiment, the input load is supported by the air (air spring) in the air chamber 76 where no sag occurs, and the rubber elastic rolling element 62 does not directly support the input load. Compared with a vibration isolator that supports an input load with a rubber elastic body, the durability of the device can be improved, and performance deterioration and damage can be prevented over a long period of time.

  Further, in the vibration isolator 10 according to the present embodiment, the outer peripheral rolling surface 26 of the outer cylinder member 12 is a curved surface inclined with respect to the axial direction, and the outer peripheral rolling surface 26 and the inner cylindrical member 28 are Since a gap is formed between the inner circumferential side rolling surface 36 and the width along the radial direction gradually narrows from the lower end side toward the upper end side, the amount of movement of the outer cylinder member 12 in the compression direction is reduced. As it increases, the damping against the vibration generated by the elastic rolling element 62 can be increased non-linearly.

  In the above description of the present embodiment, the case where vibration that is amplified along the axial direction is input to the vibration isolator 10 is described. However, the rigidity of the device (support system) along the direction perpendicular to the axis is axial. Therefore, even if a load along the direction perpendicular to the axis is input, the relative movement along the direction perpendicular to the axis of the outer cylinder member 12 with respect to the inner cylinder member 28 is slight. It will be something. However, when vibration along the direction perpendicular to the axis is input, the elastic rolling element 62 undergoes elastic deformation along the radial direction. Obtainable.

  Further, in the vibration isolator 10 according to the present embodiment, the outer cylinder member 12 is connected to the vibration generating unit, and the inner cylinder member 28 is connected to the vibration receiving unit. On the contrary, the outer cylinder member 12 is vibrated. While connecting with a receiving part, you may connect the inner cylinder member 28 with a vibration generation part. Further, in the vibration isolator 10, air is used as a fluid to be filled in the air chamber 76 and the equilibrium chamber 60, but the air chamber 76 and the equilibrium chamber 60 are replaced with high water such as water, silicone oil, or ethylene glycol. You may make it fill with a viscous fluid. Such a highly viscous fluid has a higher viscous resistance when passing through the orifice passage 48 than air, so that the attenuation obtained when the fluid passes through the orifice passage 48 can be increased.

(Second Embodiment)
Next, a vibration isolator according to the second embodiment of the present invention will be described. Note that in the vibration isolator 80 according to the second embodiment, the same reference numerals are given to the same components and operations as those of the vibration isolator 10 according to the first embodiment, and the description thereof is omitted.

  FIG. 3 shows a vibration isolator 80 according to a seventh embodiment of the present invention.

  The anti-vibration device 80 shown in FIG. 3 differs from the anti-vibration device 10 according to the first embodiment. This is a point that the holding portion 82 is formed so as to extend along the circumferential direction. Thereby, in the area | region in which the rolling holding | maintenance part 82 was formed in the outer peripheral surface of the inner cylinder member 28, a space | interval with the outer peripheral side rolling surface 26 will spread, and the elastic rolling element 62 will contact the rolling holding | maintenance part 82. In this state, the amount of compressive deformation along the radial direction of the elastic rolling element 62 is smaller than that in contact with the upper and lower regions of the rolling holding portion 82, so that the outer cylinder member 12 is in the compression direction or the tensile direction. When the elastic rolling element 62 moves away from the rolling holding portion 82, the amount of compressive deformation along the radial direction of the elastic rolling element 62 increases. Therefore, in the vibration isolator 80, when the outer cylinder member 12 is at an initial position substantially at the center between the compression limit point and the tension limit point, the outer cylinder member 12 has a resistance to deformation in the radial direction of the elastic rolling element 62. A holding force corresponding to is applied.

  As a result, in the vibration isolator 80 according to the present embodiment, even if the air pressure in the air chamber 76 is kept constant, if the change in the support load is less than the holding force generated by the rolling holding portion 82, The outer cylinder member 12 can be held at the initial position without relatively moving along the axial direction.

It is side surface sectional drawing which shows the structure of the vibration isolator which concerns on the 1st Embodiment of this invention. It is side surface sectional drawing which shows the state which the input load with respect to the vibration isolator shown by FIG. 1 increased, and the outer cylinder member fell from the initial position. It is side surface sectional drawing which shows the structure of the vibration isolator which concerns on the 2nd Embodiment of this invention.

Explanation of symbols

10 Vibration isolator 12 Outer cylinder member (first mounting member)
16 Stopper shaft (Tension stopper means)
20 Stopper ring (Tension stopper means)
24 Stopper rubber (compression stopper means)
26 Outer peripheral side rolling surface (inner peripheral surface of first mounting member, tapered surface)
28 Inner cylinder member (second mounting member)
36 Inner circumferential rolling surface (outer circumferential surface of second mounting member)
48 Orifice passage (restricted passage)
50 Bulkhead member 60 Equilibrium chamber 62 Elastic rolling element 64 Bellows member 72 Air compressor 74 Pressure piping 76 Air chamber (pressure chamber)
80 Vibration isolator 82 Rolling holding part

Claims (4)

A first mounting member connected to one of the vibration generating portion and the vibration receiving portion and formed in a substantially cylindrical shape;
A second mounting member connected to the other of the vibration generating unit and the vibration receiving unit and disposed on the inner peripheral side of the first mounting member;
Both ends are formed in a cylindrical shape that opens, and one end is fixed to the entire surface of the first mounting member, and the other end is formed on the entire surface of the second mounting member. A bellows member that is fixed over and has one end and the other end movable along the axial direction;
A pressure chamber partitioned from the outside by the bellows member, the first mounting member, the second mounting member and the elastic rolling element;
An equilibrium chamber filled with a fluid having a pressure corresponding to an input load supported by the first mounting member and the second mounting member;
A restriction passage that allows the pressure chamber and the equilibrium chamber to communicate with each other;
It is formed in a substantially annular shape by an elastic material, and is interposed between the inner peripheral surface of the first mounting member and the outer peripheral surface of the second mounting member so as to be compressed along the radial direction, An elastic rolling element that rolls between the inner peripheral surface of the first mounting member and the outer peripheral surface of the second mounting member in accordance with the relative movement along the axial direction of at least one of the first mounting member and the second mounting member;
And a vibration isolator.   2. The anti-vibration device according to claim 1, further comprising tension stopper means for restricting relative displacement of the first mounting member and the second mounting member in the axial direction in the axial direction.   The vibration isolator according to claim 1 or 2, further comprising compression stopper means for restricting relative displacement of the first attachment member and the second attachment member toward the compression side in the axial direction.   The at least one of the inner peripheral surface of the first mounting member and the outer peripheral surface of the second mounting member is formed as a tapered surface inclined with respect to the axial direction. Anti-vibration device.

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