WO2011108597A1 - 防振構造体 - Google Patents
防振構造体 Download PDFInfo
- Publication number
- WO2011108597A1 WO2011108597A1 PCT/JP2011/054780 JP2011054780W WO2011108597A1 WO 2011108597 A1 WO2011108597 A1 WO 2011108597A1 JP 2011054780 W JP2011054780 W JP 2011054780W WO 2011108597 A1 WO2011108597 A1 WO 2011108597A1
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- WIPO (PCT)
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- end side
- vibration
- composite laminate
- stress
- rubber
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
- F16F1/40—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers consisting of a stack of similar elements separated by non-elastic intermediate layers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/0052—Physically guiding or influencing
- F16F2230/007—Physically guiding or influencing with, or used as an end stop or buffer; Limiting excessive axial separation
Definitions
- the present invention has a composite laminated material in which a plurality of hard plates and soft plates having viscoelastic properties are alternately laminated.
- a vibration generating portion such as an engine or a motor is supported on a vibration receiving portion such as a vehicle body.
- the present invention relates to a vibration isolating structure that is used to attenuate and absorb vibration transmitted from the vibration generating unit to the vibration receiving unit.
- the vibration generating part is supported on the vibration receiving part by a vibration-proof structure using a composite laminated material in which a hard plate having the above rigidity and a soft plate such as rubber having viscoelastic properties are alternately laminated.
- a composite laminated material in which a hard plate having the above rigidity and a soft plate such as rubber having viscoelastic properties are alternately laminated.
- the composite laminate is interposed between the vibration generator and the vibration receiver, so that the vibration generated from the vibration generator is attenuated and absorbed by the composite laminate and the vibration is expanded by the resonance phenomenon. By preventing this, the vibration level transmitted to the vibration receiving portion is reduced.
- Such a composite laminate is made so that it can be relatively deformed in the horizontal direction while supporting the weight of the vibration generating portion. Therefore, when the vibration is applied in a state where the load of the vibration generating portion is supported, that is, in a state where a positive pressure is applied to the composite laminate, the composite laminate mainly undergoes shear deformation along the horizontal direction. Since the lower end side is constrained by the vibration receiving portion side, the composite laminate material undergoes a torsional deformation at the time of vibration input having a large amplitude. A compressive load acts on the other end, and a tensile load acts on the other end.
- the compressive load and tensile load acting on the composite laminate will increase as the twist deformation of the composite laminate increases, that is, the amplitude of the input vibration increases.
- the composite laminate material has a relatively large constraining surface but a small free surface area. Therefore, when a tensile load is applied, concentration of hydrostatic water stress occurs at the center of the constraining surface, and it is easy to be damaged. End up.
- the soft material is thickened at the portion where the hydrostatic pressure stress due to the twisting deformation is increased, thereby increasing the free surface area of the soft material.
- the internal stress of the material is reduced.
- the present invention has been made in consideration of the above facts, and even when a vibration having a large amplitude along the shearing direction is input to cause a twist deformation in the composite laminate, the composite laminate is effectively damaged.
- An object of the present invention is to provide an anti-vibration structure that can be suppressed.
- the vibration-proof structure includes a composite laminated material in which a hard plate having a plurality of rigidity and a soft plate having a viscoelastic property are alternately laminated,
- the composite laminated material is provided so as to be sandwiched from the outside in the laminating direction, and is connected to a vibration generating unit and a vibration receiving unit, respectively, and the laminating direction of the composite laminated material,
- the hydrostatic stress with respect to the tensile load along the laminating direction of the portion corresponding to one end side and the other end side of the orthogonal shear direction is the hydrostatic pressure stress with respect to the tensile load along the laminating direction of the other portion of the composite laminate.
- a stress reduction portion that reduces the amount of the stress.
- the vibration when vibration is generated in the vibration generating portion, the vibration is attenuated by the viscoelastic deformation of the plurality of soft materials constituting the composite laminated material and transmitted to the vibration receiving portion. Vibration is reduced.
- the stress reduction part is provided.
- the hydrostatic stress with respect to the tensile load along the laminating direction of the composite laminate is reduced on one end side and the other end side. Therefore, by setting the direction from the one end side to the other end side so as to correspond to the amplitude direction of the input vibration, the hydrostatic pressure stress acting on the composite laminate can be reduced. That is, when a vibration with a large amplitude is input in a direction (shear direction) orthogonal to the laminating direction of the composite laminate, and the torsional deformation occurs in the composite laminate, the hydrostatic stress acting on the composite laminate is Reduced.
- the stress reduction part is not provided about parts other than the one end side and the other end side of a composite laminated material, rigidity can be maintained.
- the stress reduction portion is configured such that the length from the one end side to the other end side of the soft plate is shorter than the length between the end portions at other positions. It is characterized by including.
- the hydrostatic pressure against the tensile load on one end side and the other end side of the composite laminated material Stress can be reduced.
- the vibration isolating structure according to a third aspect of the present invention is the vibration isolating structure according to the second aspect, wherein the composite laminated material is circular when viewed from the laminating direction, and the stress reducing portion is the soft plate. It includes a configuration in which one end side and the other end side are linear when viewed from the stacking direction.
- the one end side and the other end side of the soft plate are linear when viewed from the laminating direction, that is, one end side and the other end side of the soft plate.
- the stress reducing portion can be configured.
- the stress reducing portion is configured such that the length from the one end side to the other end side of the hard plate is shorter than the length between the end portions at other positions. It is characterized by including.
- the vibration-proof structure according to the fifth aspect of the present invention is the vibration-proof structure according to the fourth aspect, wherein the composite laminated material is circular as viewed from the stacking direction, and the stress reducing portion is the hard plate. It includes a configuration in which one end side and the other end side are linear when viewed from the stacking direction.
- the one end side and the other end side of the hard plate are linear when viewed from the laminating direction, that is, one end side and the other end side of the hard plate.
- the stress reducing portion can be configured.
- the vibration-proof structure according to the sixth aspect of the present invention is characterized in that the stress reducing portion includes a hollow portion on the one end side and the other end side of the soft plate.
- the vibration-proof structure of the seventh aspect of the present invention has higher rigidity than the composite laminate with respect to the tensile load along the lamination direction, and can be deformed in a shearing direction perpendicular to the lamination direction.
- the first flange member and the second flange member hold the composite laminated material in a state compressed at a predetermined compression rate along the lamination direction, and the first flange member.
- the displacement limiting member has higher rigidity than the displacement limiting member with respect to the load in the tensile direction, even when a tensile load is applied to the composite laminate along with an external force along the shear direction, The deformation amount along the shear direction can be prevented from becoming excessive, and the deformation of the composite laminate in the tensile direction can be reduced.
- FIG. 2 is a cross-sectional view of the vibration isolating structure according to the first embodiment of the present invention taken along the line AA in FIG.
- FIG. 2 is a cross-sectional side view taken along the line BB in FIG. 1 of the vibration-proof structure according to the first embodiment of the present invention.
- It is side surface sectional drawing which shows the state which the vibration with a large amplitude input along the shear direction into the vibration isolator structure which concerns on 1st Embodiment of this invention, and the twist deformation
- FIG. 5 is a cross-sectional view of the vibration isolating structure according to the second embodiment of the present invention taken along the line AA in FIG.
- FIG. 6 is a cross-sectional view of the vibration isolating structure according to the second embodiment of the present invention taken along the line BB in FIG.
- It is side surface sectional drawing which shows the state which the vibration with a big amplitude input along the shear direction into the vibration isolating structure which concerns on 2nd Embodiment of this invention, and the twist deformation generate
- FIG. 8 is a cross-sectional view of the vibration isolating structure according to the third embodiment of the present invention taken along the line AA in FIG.
- FIG. 10 is a cross-sectional view of the vibration isolating structure according to the third embodiment of the present invention taken along the line BB in FIG. 7.
- It is side surface sectional drawing which shows the state which the vibration with a large amplitude input along the shear direction into the vibration isolator structure which concerns on 3rd Embodiment of this invention, and the twist deformation
- the vibration isolating structure 10 includes a laminated rubber 16 that is a composite laminated material in which hard plates 12 that can be regarded as substantially rigid bodies and rubber plates 14 having viscoelastic properties are alternately laminated.
- the laminated rubber 16 is formed in a substantially thick cylindrical shape, and a columnar cavity 17 penetrating in the laminating direction (arrow L direction) of the laminated rubber 16 is bored at the center of the laminated rubber 16.
- the laminated rubber 16 is configured by bonding the hard plate 12 and the rubber plate 14 together by vulcanization adhesion.
- the hard plate 12 has a disk shape.
- the rubber plate 14 has one end side 16 ⁇ / b> F and the other end side 16 ⁇ / b> B formed in a straight line when viewed from the lamination direction L of the laminated rubber 16, and the other outer edge is formed in an arc shape along the hard plate 12. That is, the rubber plate 14 has a two-sided width shape in which one end side 16F and the other end side 16B are cut off from a circle. Thereby, the laminated
- the anti-vibration structure 10 is coupled to the vibration generating section so that the direction connecting the one end side 16F and the other end side 16B (hereinafter referred to as “shear direction W”) is the amplitude direction of the input vibration.
- the coupling is performed so that the shearing direction W corresponds to the longitudinal direction of the vehicle.
- the distance S1 between the one end side 16F and the other end side 16B of the rubber plate 14 is shorter than the distance between the other end portions, that is, the diameter A of the hard plate 12.
- the hard board 12 constituting the laminated rubber 16 for example, metal, ceramics, plastics, FRP, polyurethane, wood, paper board, slate board, decorative board, and the like can be used.
- the rubber plate 14 is generally molded using various vulcanized rubbers as a raw material.
- the rubber ethylene propylene rubber (EPR, EPDM), nitrile rubber (NBR), butyl rubber, halogenated butyl rubber, chloroprene rubber (CR), natural rubber (NR), isoprene rubber (IR), styrene butadiene rubber (SBR), Examples include butadiene rubber (BR).
- the anti-vibration structure 10 is provided with a flange 18 and a flange 20 on the outer side of the laminated rubber 16 in the laminating direction, and the pair of flanges 18 and 20 are respectively added to the lower end surface and the upper end surface of the laminated rubber 16. It is fixed by sulfur or the like and sandwiches the laminated rubber 16 along the laminating direction.
- the flanges 18 and 20 are each formed of a rectangular metal plate.
- the flange 18 on the lower end side is formed with a circular opening 22 facing the cavity 17 of the laminated rubber 16 at the center thereof, and the bottom surface of the flange 18 is concave along the peripheral edge of the opening 22.
- the insertion part 24 is formed.
- the upper end side flange 20 is formed with an insertion hole 26 having a smaller diameter than the hollow portion 17 of the laminated rubber 16 at the center thereof.
- a metal link chain 28 which is a displacement limiting member, is disposed in the cavity 17 of the laminated rubber 16.
- the link chain 28 is arranged such that its longitudinal direction coincides with the lamination direction of the laminated rubber 16, and has sufficiently higher rigidity and strength than the laminated rubber 16 with respect to a tensile load along the lamination direction. ing.
- the link chain 28 is configured by connecting a plurality of (three in the present embodiment) link pieces 30, 31, 32 in a linear shape.
- the link chain 28 can be easily deformed in the shearing direction W as a whole orthogonal to the stacking direction by bending between the link pieces 30, 31 and 32.
- a circular plate-like lid member 34 is fixed to the lower end portion of the link piece 30 located at the lowermost portion of the link chain 28 by welding or the like.
- the bolt 32 is fixed to the upper end of the link piece 32 positioned at the top of the link chain 28 by welding or the like so as to protrude upward.
- the link chain 28 is inserted into the cavity 17 of the laminated rubber 16 through the opening 22 of the flange 18 on the lower end side.
- the bolt shaft 36 is inserted through the insertion hole 26 of the flange 20 to project the distal end side to the outside of the flange 20, and the lid member 34 closes the opening 22 of the flange 18, and its outer peripheral edge is flanged.
- 18 is inserted into the insertion portion 24.
- a washer 38 is fitted to the tip of the bolt shaft 36 protruding from the flange 20, and a nut 40 is further screwed.
- the link chain 28 disposed in the hollow portion 17 has its lower end connected and fixed to the flange 18 via the lid member 34 and its upper end connected and fixed to the flange 20 via the bolt shaft 36. Is done.
- the laminated rubber 16 is pressed along the lamination direction by a press device or the like and is compressed at a predetermined compression rate.
- the nut 40 screwed into the bolt shaft 36 protruding from the flange 20 is tightened until there is no play between the nut 20 and a predetermined fastening torque is generated.
- the laminated rubber 16 is held in a compressed state compressed at a predetermined compression rate along the laminating direction by the flanges 18 and 20, and the elastic restoration that the flanges 18 and 20 receive from the laminated rubber 16 in the compressed state.
- the force is supported by the link chain 28, and the link chain 28 is in a tensioned state (tensile state) by this restoring force.
- the laminated rubber 16 when it does not support the vibration generating part and receives a compressive load along the lamination direction from the vibration generating part, it exceeds 0% and 5% or less along the lamination direction. It is held in a compressed state at a compression ratio of preferably less than 0% along the laminating direction and is compressed at a compression rate of 2% or less, more preferably 0% along the laminating direction. And at a compression rate approximating 0% with an error range of + 0.5%.
- the laminated rubber 16 receives a load (compressive load) from the vibration generating part and is compressed in the laminating direction, so that a compressive load along the laminating direction is input from the vibration generating part.
- a load compressive load
- the vibration isolating structure 10 is disposed, for example, so as to be interposed between a vibration generating unit such as an engine or a motor and a vibration receiving unit such as a floor or a vehicle body. Support on top.
- the laminated rubber 16 is coupled to the vibration generating unit such that the shear direction W is the amplitude direction of the floor, the vehicle body, and the like. For example, if it is a vehicle body, it will be connected so that the shear direction W may correspond to the front-back direction of the vehicle.
- the laminated rubber 16 When the vibration is generated from the vibration generating portion, the laminated rubber 16 is mainly deformed in the shear direction W, and the vibration is attenuated and absorbed by internal friction or the like.
- the laminated rubber 16 is twisted and deformed as shown in FIG. 3, and one end side 16F and the other end side along the amplitude direction of the laminated rubber 16 are generated.
- a tensile load acts on 16B (the other end side 16B in FIG. 3).
- the link chain 28 is always stretched by the restoring force received from the laminated rubber 16 between the flanges 18 and 20 (tensile state)
- a tensile load acts on the laminated rubber 16 due to vibration.
- a part of this tensile load is supported by the link chain 28, and the tensile stress along the lamination direction generated in the laminated rubber 16 can be reduced.
- the distance S1 from the one end side 16F to the other end side 16B of the rubber plate 14 is shorter than the diameter A of the laminated rubber 16. Therefore, when the deformation of the laminated rubber 16 occurs (see FIG. 3), the hydrostatic pressure stress against the tensile load acting on the one end side 16F and the other end side 16B (the other end side 16B in FIG. 3) can be reduced. it can. As a result, damage to the rubber plate 14 can be effectively suppressed with respect to large amplitude vibration input along the shear direction W.
- the outer edges of the portions other than the one end side 16F and the other end side 16B of the rubber plate 14 are arcuate, so that the conventional rigidity can be maintained for the portions. , The decrease in rigidity can be reduced.
- the link chain 28 in which a plurality of link pieces 30, 31, 32 are linearly connected is used as the displacement limiting member.
- a metal wire, a metal wire knitted by a metal wire for example, a metal wire, a metal wire knitted by a metal wire, A linear member such as a string member made of a resin material such as an aramid fiber may be used.
- [Second Embodiment] (Configuration of anti-vibration structure) 4 to 6 show an anti-vibration structure according to the second embodiment of the present invention.
- the vibration isolating structure 50 according to the present embodiment the same parts as those in the vibration isolating structure 10 according to the first embodiment are denoted by the same reference numerals and description thereof is omitted.
- the anti-vibration structure 50 according to the present embodiment is different from the anti-vibration structure 10 according to the first embodiment in that the hard plate has the same shape as the rubber plate 14 of the first embodiment when viewed from the stacking direction L.
- the rubber plate has the same shape as the hard plate 12 of the first embodiment.
- the vibration-proof structure 50 includes a laminated rubber 56 that is a composite laminated material in which hard plates 52 and rubber plates 54 are alternately laminated.
- a laminated rubber 56 that is a composite laminated material in which hard plates 52 and rubber plates 54 are alternately laminated.
- the hard plate 52 of the present embodiment when viewed from the laminating direction L of the laminated rubber 16, one end side 56F and the other end side 56B are linear, and the other outer edges are arcuate. That is, the hard plate 52 has a two-sided width shape in which one end side 56F and the other end side 56B are cut off from a circle.
- the vibration isolating structure 50 is connected to the vibration generating portion so that the direction (shear direction W) connecting the one end side 56F and the other end side 56B is the amplitude direction of the input vibration.
- the coupling is performed so that the shearing direction W corresponds to the longitudinal direction of the vehicle.
- the distance S2 between the one end side 56F and the other end side 56B of the hard plate 52 is shorter than the distance between the other end portions, that is, the diameter A of the disc.
- the free surface area of the rubber plate 54 is increased, and when the laminated rubber 56 is twisted and deformed (see FIG. 6), the one end side 56F and the other end side 56B (the other end side in FIG. 6).
- the hydrostatic stress against the tensile load acting on 56B) is reduced.
- the distance S2 is preferably 65% to 90% of the diameter A.
- the rubber plate 54 of the present embodiment has a disk shape when viewed from the stacking direction L, and the one end side 56F and the other end side 56B are continuous in the stacking direction L so as to fill in the cut off portion of the hard plate 52. Is formed.
- the vibration isolating structure When vibration is generated from the vibration generating portion, the laminated rubber 56 is mainly deformed in the shear direction W, and the vibration is attenuated and absorbed by internal friction or the like. Further, when vibration having a large amplitude is input along the shearing direction W, the laminated rubber 56 is twisted and deformed as shown in FIG. 6, and one end side 56F and the other end side along the amplitude direction of the laminated rubber 56 are generated. A tensile load acts on 56B (the other end side 56B in FIG. 6).
- the distance S2 from the one end side 56F to the other end side 56B of the hard plate 52 is shorter than the diameter A of the laminated rubber 56. Accordingly, when the laminated rubber 56 is twisted (see FIG. 6), the hydrostatic stress against the tensile load acting on the one end side 56F and the other end side 56B (the other end side 56B in FIG. 6) can be reduced. it can. As a result, damage to the rubber plate 54 can be effectively suppressed against large amplitude vibration input along the shear direction W.
- the outer edges of the portions other than the one end side 56F and the other end side 56B of the rubber plate 54 are arcuate, so that the conventional rigidity can be maintained for the portions. , The decrease in rigidity can be reduced.
- the distance in the shearing direction W (distance S1, distance S2) is shorter than the diameter A for only one of the hard plate and the rubber plate. For both, the distance in the shear direction W may be shorter than the diameter A.
- FIG. 7 to 9 show a vibration isolating structure according to a third embodiment of the present invention.
- the same parts as those of the vibration isolating structures 10 and 50 according to the first and second embodiments are denoted by the same reference numerals, and the description thereof is omitted.
- the vibration isolating structure 60 according to the present embodiment is different from the anti-vibration structural body 10 according to the first embodiment in that the rubber plate has the same shape as the hard plate 12 of the first embodiment when viewed from the stacking direction L. And the point that the cavity is formed in the rubber plate.
- the vibration-proof structure 60 includes a laminated rubber 66 that is a composite laminated material in which hard plates 62 and rubber plates 64 are alternately laminated.
- the hard plate 52 and the rubber plate 64 of the present embodiment are disk-shaped.
- a cavity 68 is formed on one end side 66 ⁇ / b> F and the other end side 66 ⁇ / b> B in a direction perpendicular to the shearing direction W when viewed from the laminating direction L of the laminated rubber 66.
- the cavity 68 is configured to penetrate the rubber plate 64.
- the vibration isolating structure 60 is connected to the vibration generating portion so that the direction connecting the one end side 66F and the other end side 66B (shear direction W) is the amplitude direction of the input vibration.
- the coupling is performed so that the shearing direction W corresponds to the longitudinal direction of the vehicle.
- the position where the cavity 68 is formed is preferably within a range of 30% to 60% of the radius B from the outer periphery of the rubber plate 64 and a distance E from the outer periphery. This is because the hydrostatic stress cannot be effectively reduced when it is configured on the outer peripheral side with respect to 30% of the radius B and when it is configured on the inner peripheral side with respect to 60% of the radius B.
- the vibration isolating structure When vibration is generated from the vibration generating portion, the laminated rubber 66 is mainly deformed in the shear direction W, and the vibration is attenuated and absorbed by internal friction or the like. Further, when vibration having a large amplitude is input along the shearing direction W, the laminated rubber 66 is twisted and deformed as shown in FIG. 9, and one end side 66F and the other end side along the amplitude direction of the laminated rubber 66 are generated. A tensile load acts on 56B (the other end side 66B in FIG. 9).
- the cavity 68 is formed on one end side 66F and the other end side 66B of the rubber plate 64, when the twisted deformation occurs in the laminated rubber 66 (see FIG. 9).
- the hydrostatic stress against the tensile load acting on the one end side 66F and the other end side 66B (the other end side 66B in FIG. 9) can be reduced.
- damage to the rubber plate 64 can be effectively suppressed against large amplitude vibration input along the shear direction W.
- the rubber plate 64 of the present embodiment is also formed on the radially outer side than the cavity portion 68, it is possible to reduce the decrease in rigidity while reducing the hydrostatic stress as described above.
- the cavity portion 68 is formed along a direction orthogonal to the shearing direction W.
- the cavity portion is formed in another direction, for example, a direction along the shearing direction W, a radial direction, etc. The hydraulic stress may be reduced.
- the chain 28 is disposed between the flanges 18 and 20 and the laminated rubber 16, 56, and 66 are held in a compressed state. .
- FIG. 10 shows a graph of the result. In both the first and second embodiments, substantially the same result was obtained.
- the distance S1 and the distance S2 are expressed as a ratio with respect to the diameter A (distance S1 / diameter A, distance S2 / diameter A), the hydrostatic stress value, and the displacement expansion amount are circular for the rubber plate (hard plate).
- the hydrostatic stress value decreases by 10% and the displacement expansion amount increases by 10%. Further, the distance S1 / diameter A (distance S2 / diameter A) is 65% or less, and the increase in the displacement expansion amount exceeds 50%. Therefore, in order to reduce the hydrostatic stress while ensuring an appropriate amount of displacement, it is preferable to set the distance S1 / diameter A (distance S2 / diameter A) to 65% to 90%.
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Abstract
Description
(防振構造体の構成)
図1及び図2A、図2Bには、本発明の第1実施形態に係る防振構造体が示されている。この防振構造体10は、実質的に剛体とみなせる硬質板12と粘弾性的性質を有するゴム板14とが交互に積層された複合積層材である積層ゴム16を備えている。積層ゴム16は略肉厚円筒状に形成されており、その面央部には積層ゴム16の積層方向(矢印L方向)へ貫通する円柱状の空洞部17が穿設されている。積層ゴム16は、硬質板12とゴム板14とを加硫接着により貼り合わせることにより構成されている。
なお、距離S1は、直径Aの65%~90%であることが好ましい。
次に、本実施形態に係る防振構造体の作用について説明する。
本実施形態に係る防振構造体10は、例えば、エンジン、モータ等の振動発生部とフロア、車体等の振動受部との間に介在するように配設され、振動発生部を振動受部上に支持する。このとき、積層ゴム16は、剪断方向Wが、フロア、車体等の振幅方向になるように、振動発生部に連結される。例えば、車体であれば、剪断方向Wが車両の前後方向に対応するように、連結される。
(防振構造体の構成)
図4~図6には、本発明の第2実施形態に係る防振構造体が示されている。なお、本実施形態に係る防振構造体50において第1実施形態に係る防振構造体10と同一の部分については同一符号を付して説明を省略する。
なお、距離S2は、直径Aの65%~90%であることが好ましい。
次に、本実施形態に係る防振構造体の作用について説明する。
振動発生部からの振動発生時には、積層ゴム56が主として剪断方向Wに変形し内部摩擦等により振動が減衰吸収される。また、剪断方向Wに沿って振幅の大きい振動が入力すると、図6に示されるように積層ゴム56にこじり変形が発生し、この積層ゴム56の振幅方向に沿った一端側56F及び他端側56B(図6では他端側56B)に引張り荷重が作用する。このとき、第1実施形態と同様に、リンクチェーン28が張力状態となっているので、引張り荷重の一部をリンクチェーン28により支持し、積層ゴム16に生じる積層方向に沿った引張り応力を低減できる。
(防振構造体の構成)
図7~図9には、本発明の第3実施形態に係る防振構造体が示されている。なお、本実施形態に係る防振構造体60において第1、第2実施形態に係る防振構造体10、50と同一の部分については同一符号を付して説明を省略する。
次に、本実施形態に係る防振構造体の作用について説明する。
振動発生部からの振動発生時には、積層ゴム66が主として剪断方向Wに変形し内部摩擦等により振動が減衰吸収される。また、剪断方向Wに沿って振幅の大きい振動が入力すると、図9に示されるように積層ゴム66にこじり変形が発生し、この積層ゴム66の振幅方向に沿った一端側66F及び他端側56B(図9では他端側66B)に引張り荷重が作用する。このとき、第1実施形態と同様に、リンクチェーン28が張力状態となっているので、引張り荷重の一部をリンクチェーン28により支持し、積層ゴム66に生じる積層方向に沿った引張り応力を低減できる。
Claims (7)
- 複数の剛性を有する硬質板と粘弾性的性質を有する軟質板とが交互に積層された複合積層材と、
前記複合積層材を、その積層方向外側から挟持するように設けられると共に、振動発生部及び振動受部にそれぞれ連結される第1及び第2のフランジ部材と、
前記複合積層材の前記積層方向と直交する剪断方向の一端側及び他端側に対応する部分の前記積層方向に沿った引張り荷重に対する静水圧応力を前記複合積層材の他の部分の前記積層方向に沿った引張り荷重に対する静水圧応力よりも低減させる応力低減部と、
を備えた防振構造体。 - 前記応力低減部は、前記軟質板の前記一端側から他端側までの長さを他の位置の端部間の長さよりも短くする構成を含んでいること、を特徴とする請求項1に記載の防振構造体。
- 前記複合積層材は前記積層方向からみて円形とされ、
前記応力低減部は、前記軟質性板の前記一端側及び他端側を前記積層方向からみて直線状とする構成を含んでいること、を特徴とする請求項2に記載の防振構造体。 - 前記応力低減部は、前記硬質板の前記一端側から他端側までの長さを他の位置の端部間の長さよりも短くする構成を含んでいること、を特徴とする請求項1~3のいずれか1項に記載の防振構造体。
- 前記複合積層材は前記積層方向からみて円形とされ、
前記応力低減部は、前記硬質板の前記一端側及び他端側を、前記積層方向からみて直線状とする構成を含んでいること、を特徴とする請求項4に記載の防振構造体。 - 前記応力低減部は、前記軟質板の前記一端側及び他端側に空洞部を含んだ構成とされていること、を特徴とする請求項1に記載の防振構造体。
- 前記積層方向に沿った引張り荷重に対して前記複合積層材よりも高い剛性を有すると共に、該積層方向と直交する剪断方向へ変形可能とされ、前記積層方向に沿った両端部が前記第1のフランジ部材と前記第2のフランジ部材にそれぞれ連結固定され、前記複合積層材の前記積層方向及び前記剪断方向への変位を制限する変位制限部材を備え、
前記第1のフランジ部材と前記第2のフランジ部材とにより前記複合積層材を前記積層方向に沿って所定の圧縮率で圧縮した状態に保持すると共に、前記第1のフランジ部材及び前記第2のフランジ部材が圧縮状態とした前記前記複合積層材から受ける弾性的な復元力を前記変位制限部材により支持したことを特徴とする請求項1~6のいずれか1項に記載の防振構造体。
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EP11750706.1A EP2543908B1 (en) | 2010-03-04 | 2011-03-02 | Vibration isolation structure |
US13/582,665 US8864115B2 (en) | 2010-03-04 | 2011-03-02 | Vibration isolation structure |
CN201180012089.8A CN102782359B (zh) | 2010-03-04 | 2011-03-02 | 隔振结构体 |
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JP2010048381A JP5538957B2 (ja) | 2010-03-04 | 2010-03-04 | 防振構造体 |
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EP (1) | EP2543908B1 (ja) |
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JP6076849B2 (ja) | 2013-07-03 | 2017-02-08 | 株式会社ブリヂストン | 防振構造体 |
WO2015031983A1 (en) * | 2013-09-06 | 2015-03-12 | Tsai Jack Yiyo | Anchorage connector for a safety system |
JP2016061410A (ja) * | 2014-09-19 | 2016-04-25 | オイレス工業株式会社 | 構造物用振動減衰装置 |
CN106032829B (zh) * | 2015-03-10 | 2021-05-11 | 艾默生环境优化技术(苏州)有限公司 | 隔振垫以及包括该隔振垫的压缩机系统 |
DE102015109533B4 (de) * | 2015-06-15 | 2019-03-21 | Benteler Automobiltechnik Gmbh | Gummi-Feststofflager zur Anordnung an einer Kraftfahrzeugachse |
JP6613930B2 (ja) * | 2016-02-01 | 2019-12-04 | オイレス工業株式会社 | 免震装置 |
JP6579026B2 (ja) * | 2016-04-15 | 2019-09-25 | オイレス工業株式会社 | 橋梁用の免震支承及びそれを用いた橋梁 |
ES2840223T3 (es) * | 2017-09-20 | 2021-07-06 | Zhuzhou Times New Mat Tech Co | Dispositivo de soporte amortiguador de vibraciones |
TR201922885A2 (tr) * | 2019-12-31 | 2021-07-26 | Sem Lastik Sanayii Ve Ticaret Anonim Sirketi | Bağlanti takozu |
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CN102782359A (zh) | 2012-11-14 |
CN102782359B (zh) | 2015-08-26 |
CN103982583B (zh) | 2016-03-23 |
JP5538957B2 (ja) | 2014-07-02 |
JP2011185308A (ja) | 2011-09-22 |
EP2543908B1 (en) | 2017-08-16 |
US20120326366A1 (en) | 2012-12-27 |
EP2543908A4 (en) | 2015-10-28 |
CN103982583A (zh) | 2014-08-13 |
EP2543908A1 (en) | 2013-01-09 |
US8864115B2 (en) | 2014-10-21 |
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