WO2006060956A1 - Amortisseur - Google Patents

Amortisseur Download PDF

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Publication number
WO2006060956A1
WO2006060956A1 PCT/CN2005/002099 CN2005002099W WO2006060956A1 WO 2006060956 A1 WO2006060956 A1 WO 2006060956A1 CN 2005002099 W CN2005002099 W CN 2005002099W WO 2006060956 A1 WO2006060956 A1 WO 2006060956A1
Authority
WO
WIPO (PCT)
Prior art keywords
damper
chamber
cylinder
damping
damper according
Prior art date
Application number
PCT/CN2005/002099
Other languages
English (en)
Chinese (zh)
Inventor
Xuejun Yin
Original Assignee
Gerb (Qingdao) Vibration Control Co., Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gerb (Qingdao) Vibration Control Co., Ltd. filed Critical Gerb (Qingdao) Vibration Control Co., Ltd.
Priority to JP2007544718A priority Critical patent/JP2008523324A/ja
Publication of WO2006060956A1 publication Critical patent/WO2006060956A1/fr

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Classifications

    • 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein

Definitions

  • the present invention relates to a vibration control device, a damper, particularly a shock absorber for a vehicle suspension system, and a vibration absorbing damper for a building structure.
  • the damper is a widely used basic component of vibration control for vibration damping, cushioning, and energy consumption of machinery, vehicles, bridges, and building structures.
  • the common damper is a hydraulic cylinder type.
  • the piston only moves axially relative to the cylinder. It is called a single-axis damper. It consists of a moving body, a moving rod, a cylinder block and a seal.
  • the moving body is generally cylindrical.
  • the moving body is provided with a plurality of small holes or a proper radial gap is left between the moving body, and the moving body divides the oil cylinder into two moving body chambers, and the moving body cavity is filled with hydraulic oil or a slightly higher viscosity viscous liquid, such as silicone oil.
  • the object of the present invention is to overcome the above drawbacks and to provide a single-axis damper adopting a novel principle and a novel structure, which has the advantages of soft damping characteristics, simple structure, low cost, stable performance, long service life, and the like, and is easy to regenerate. Environmentally friendly features.
  • the invention is implemented as follows:
  • the damper comprises a cylinder body and a moving body, the movable body is at least partially located in the cylinder body, and the cylinder body is provided with at least one axially extending chamber filled with a viscous damping liquid to form a damping
  • the chamber is composed of moving blades correspondingly disposed in the damper chamber, and the moving blades and the damper chamber wall constitute a shearing chamber, and the thickness of the shearing chamber is much smaller than the axial dimension.
  • At least one axially extending stator blade is disposed in the damper chamber of the cylinder block, and the damper chamber is divided into a plurality of sub-damper chambers that are connected to each other or not connected to each other, and the rotor blades are correspondingly disposed in the sub-damper chamber, the moving blades
  • the shear chamber is formed with the sub-damper chamber wall or the stationary vane, and the thickness of the shear chamber is much smaller than the axial dimension.
  • an axial guiding device is arranged between the moving body and the cylinder block, and the axial guiding device is sliding guiding Or flexible orientation.
  • damping chambers or shearing chambers arranged in parallel with each other, or arranged concentrically, or a plurality of chambers are arranged concentrically and then arranged in parallel; Concavities, through holes, purlins, or ring pieces are provided on the blades for adjusting the damping fluid flow disturbance.
  • the shape of the blade is tubular, columnar, or plate-like, and the shape of the outer surface cross section may be a circle, an ellipse, or a polygon, wherein a concentric tube or a square tube is most preferred.
  • the damper does not necessarily need to be sealed. If the damper is basically working in the vertical direction, the damper chamber opening is upward, or the angle of inclination is not large, it may not be sealed, or only a dust seal. If the damper chamber opening is downward, or the angle of inclination is large, a sealing device should be provided between the moving body and the cylinder; the sealing device can be a sliding seal, such as an elastic sealing ring, a 0-type sealing circumference, or a flexible one. Sealed, such as rubber seals, metal bellows seals;
  • the net volume of the damper chamber changes as the moving body moves, so that at least one damper is provided with a volume compensating device.
  • the volume compensating device is at least one elastic compensating body disposed in the damper chamber; the volume compensating device includes a volume compensating chamber connected to the damper chamber, and the volume compensating chamber is provided One or several elastic compensating bodies; the elastic compensating body is an inflatable gas crucible, or an elastic foam having an airtight elastic layer on the outer surface; the volume compensating device is an elastic gas cylinder, and one side and the damping chamber Connected, the other side is filled with compressed gas, or is provided with an elastic foam, or is provided with a compression spring.
  • a damping liquid level adjustment device and a damping liquid perfusion ⁇ L are provided.
  • a viscous shear damper can also be integrated with a hydraulic damper, that is, a piston is provided on one blade, and a sliding seal is arranged between the piston and its adjacent blade to form two Piston chamber; a suitable gap between the piston and its adjacent vanes, or a plurality of intercepting orifices.
  • the damper is provided with flange connection, pin hole connection at both ends, or anchoring ribs on the outer surfaces of the cylinder and the moving body.
  • the viscous damping liquid is a magnetron-controlled fluid, or a voltage-controlled rheological liquid, or a viscosity-reducing liquid such as silicone oil, or a silicone oil, or polyisobutylene, or a modified asphalt which is liquid at normal temperature.
  • the moving body moves axially relative to the cylinder under external load, and the moving blade moves relative to the cylinder and the stationary blade, and shears the viscous liquid in the chamber inside the moving blade, due to sticking
  • the viscosity of the liquid lags, creating a viscous resistance that hinders the movement of the moving blade.
  • the viscous resistance is always opposite to the direction of motion, and the greater the speed of motion, the greater the resistance, thereby consuming external force to work and converting mechanical energy into heat.
  • the damper of the present invention Compared with the hydraulic damper, the damper of the present invention generates motion resistance without the pressure difference formed by the orifice or the gap throttling, but forms the viscous force generated by the high viscosity damping liquid in the shearing chamber on the moving blade. Movement resistance, therefore the pressure in the damper chamber is lower than n.
  • the damper chamber opening higher than the highest position of the damping liquid the damper does not need to be sealed, only the damper chamber opening is lower than the highest position of the damping fluid, or the damper is dust-proof.
  • DRAWINGS 1 is a schematic structural view of Embodiment 1 of the present invention.
  • Figure 2 is a cross-sectional view taken along line A-A of Figure 1;
  • Embodiment 2 of the present invention is a schematic structural view of Embodiment 2 of the present invention.
  • Figure 4 is one of the A-A cross-sectional views of Figure 3;
  • Figure 5 is a second sectional view taken along line A-A of Figure 3;
  • Figure 6 is a third cross-sectional view taken along line A-A of Figure 3;
  • Figure 7 is a schematic structural view of Embodiment 3 of the present invention.
  • Figure 8 is one of the A-A cross-sectional views of Figure 7;
  • Figure 9 is a second sectional view taken along line A-A of Figure 7;
  • Figure 10 is a schematic structural view of Embodiment 4 of the present invention.
  • Figure 1 1 is one of the A-A cross-sectional views of Figure 10;
  • Figure 12 is a second cross-sectional view taken along line A-A of Figure 10;
  • Figure 13 is a schematic structural view of Embodiment 5 of the present invention.
  • Figure 14 is a schematic structural view of Embodiment 6 of the present invention.
  • Figure 15 is a schematic structural view of Embodiment 7 of the present invention.
  • Figure 16 is a cross-sectional view taken along line A-A of Figure 15. detailed description
  • the movable body 1 and the cylinder block 2 are partially located in the cylindrical cylinder block 2, and are axially movable relative to the cylinder block 2.
  • the cylinder body is provided with an axial extension.
  • Damping chamber the damping chamber is filled with a viscous damping liquid 3, here is a modified emulsified asphalt which is viscous liquid at normal temperature
  • the moving body 1 is composed of a cylindrical moving blade, and the moving blade is located in the damping chamber
  • the shear chamber is formed with the damper chamber wall, and the radial dimension of the shear chamber is much smaller than the axial dimension.
  • the cylinder head is provided with a cylinder head 2a, and the cylinder head is slidably engaged with the moving blade.
  • the cylinder head is embedded with a sliding sealing ring 5, and the end of the moving blade is fixed to the sliding guiding block 4b, which has a cross shape, allowing the damping liquid to flow through.
  • the damper chamber is provided with a volume compensating body 6a, which is an inflatable gas raft.
  • a volume compensating body 6a which is an inflatable gas raft.
  • the moving blade 1 moves axially relative to the cylinder block 2, and the viscous liquid in the shearing chamber around the moving blade 1 is sheared, and due to the viscosity of the viscous liquid, a viscous resistance that hinders the movement of the moving blade is generated.
  • the viscous resistance is always opposite to the direction of motion, and the greater the speed of motion, the greater the resistance, thereby consuming external forces to perform work, converting mechanical energy into heat.
  • the damper of the present invention does not rely on the pressure difference formed by the orifice or the gap to form the motion resistance, but relies on the high viscosity of the damping liquid in the shearing chamber to form the viscous force generated by the moving blade.
  • the resistance of the movement so the pressure in the damper chamber is low, so the friction between the moving body and the cylinder is small, the starting resistance is small, and the damping force and speed are a continuous smooth exponential function.
  • the design can be calculated accurately and realistically.
  • a cylindrical stationary vane 2a is provided in the center of the cylinder block 2, and the damper chamber is changed into an annular damper chamber.
  • the moving blade of the moving body 1 is tubular.
  • the moving blade is located in the damper chamber, and forms a shearing chamber with the damper chamber wall and the stationary blade 2a.
  • the damper chamber and the shear chamber are filled with sulfhydryl silicone oil, and the transverse dimension of the shearing chamber is much smaller than the axial dimension.
  • the lower part of the damper chamber is provided with an annular elastic compensating body 6b, and the top damper chamber of the moving body is provided with an elastic compensating body 6b, and the elastic compensating body 6b is an elastic foaming polyurethane provided with an airtight elastic layer externally.
  • the moving blade of the embodiment has two viscous shear chambers inside and outside, and the blade has two viscous shear planes when moving, which increases the viscous resistance;
  • the same guiding block 4b has a cross-sectional shape of a spline shape, the spline teeth are used for guiding, the inter-tooth gap allows the damping liquid to flow, and the ring between the teeth can also flow through the resistance of the appropriate liquid, thereby increasing the damping. .
  • the cylinder head is not provided with a sliding seal, but a flexible hermetic seal is provided.
  • the flexible seal is a rubber ring vulcanized on the cylinder head, and the inner side is vulcanized with a metal ring, the metal ring is welded with the moving body, and the cylinder is welded.
  • the cover is coupled with the cylinder bolt, and a sealing gasket is arranged between the coupling faces to ensure that the damping liquid does not leak. Since the rubber has good shear elasticity, it can allow the moving body to move axially while sealing the damping liquid well, so there is no sealing friction resistance and no wear; the guiding device no longer needs to meet the sealing requirements.
  • the damper has simple structure, no precision parts and strong robustness. Therefore, it has low cost, stable performance and reliable operation. It has no wear parts, so it basically requires no maintenance and long service life. It can be used after maintenance. It has renewable characteristics and is environmentally friendly.
  • the sealing structure is suitable for working conditions with small amplitude and stroke. If the stroke is large or the amplitude is large, a metal bellows can be used instead of the rubber ring.
  • the cross section of the cylinder block and the moving blade are concentric circles, and the cross section of the stator blade is a circle; in practice, referring to FIG. 5 and 6, the cross-sectional shape may also be a section of the cylinder and the moving blade adopting a concentric six-pipe, and the cross section of the stator blade is one. Or flat plate; or, the cross section of the cylinder block and the moving blade adopts a steel pipe having a cross-section of a concentric racetrack shape, and the cross section of the static blade is a flat plate.
  • the structure can make the width of the damper large and easy to be hidden in the wall body. This damper is therefore particularly suitable for building energy dampers because of the limited thickness of the wall.
  • the stationary blade in the damper chamber in the cylinder 2 is a tubular tube 2c
  • the moving body 1 is composed of two circular tubular moving blades to form three concentric shears.
  • the lower part of the damper chamber is provided with an annular elastic compensating body 6b
  • the elastic compensating body is an elastic foaming polyurethane which is provided with an airtight elastic layer.
  • the top of the moving body is provided with a compensation chamber, and the compensation chamber is provided with a gas-tight elastic film 6c, one side is filled with compressed air, one side is filled with damping liquid, and is connected with the damping chamber to compensate for the volume change of the damping chamber.
  • the end of the inner moving blade is also provided with a flanging spoiler ring.
  • cross section of the above-mentioned cylinder block, moving blade and stator vane is concentric; in practice, referring to Fig. 9, the cross-sectional shape may also be a concentric rectangle.
  • the damper is provided with a flexible hermetic seal
  • the flexible seal is a rubber corrugated sleeve 5c, which is vulcanized with flanges at both ends, and the flanges are respectively bolted to the movable body and the cylinder head 2d, and the joint surface is A gasket is provided to ensure that the damping fluid does not leak; the guiding device does not need to be particularly precise, and a proper radial clearance is allowed, so that the friction between the moving body and the cylinder is small, and the starting resistance of the damper is also small.
  • Example 4 Referring to FIG.
  • the damper chamber in the cylinder 2 is divided into four sub-damper chambers by a cross-shaped stator vane 2e, and four moving blades having a rectangular cross section are respectively located at the sub-section. Inside the damper chamber, four plate-shaped stationary blades 2b are respectively distributed in the moving blades. Thus, eight viscous shear chambers are formed, which can generate a larger damping force; the cylinder body is provided with a filling hole and a drain hole for adjusting the liquid level of the damping liquid, and a wire plug is provided.
  • stator blades and the moving blades are alternately arranged in the moving blades of the rectangular tube, and constitute a plurality of parallel shear chambers, and the structure is simple and easy to manufacture.
  • the embodiment is suitable for assembling into a large damper. As long as the number of groups of damper chambers side by side is increased, a corresponding multiple damping force can be obtained.
  • the damper chamber opening is upward, and the liquid level of the damping liquid is located at the upper edge of the cylinder. Underneath, there is no seal and will not leak, work as usual, the seal shown is mainly used for dust prevention purposes.
  • the damping liquid in the damping chamber is a magnetron-controlled liquid
  • the cylinder and the moving blade are made of a magnetic conductive material
  • an electromagnetic wire ⁇ 8 is arranged on the outer wall of the cylinder.
  • the damping liquid in the damping chamber is a voltage-controlled rheological liquid
  • the positive electrode 9 is arranged on the central stationary vane of the cylinder body
  • the negative electrode 10 is disposed on the inner wall of the cylinder, and the positive and negative electrodes are respectively
  • the exposed part of the damper is insulated.
  • the viscosity of the voltage-controlled rheological liquid can be adjusted to adjust the magnitude of the damping force.
  • This embodiment is suitable for applications requiring adjustment of damping according to road conditions, especially dampers for automotive suspension systems.
  • a piston 11 is provided on the stationary blade 2a, and a sliding sealing guide ring 4c is provided between the stationary blade and its adjacent moving blade 1 to constitute two piston chambers. Since the viscosity of the damping fluid is much higher than that of a conventional hydraulic damper, the sealing guide fit does not have to be as precise as the seal of a conventional hydraulic damper, and a gap can be left, the piston and the bucket There may also be a suitable gap between the sheets and a plurality of throttling holes.
  • the pressure difference between the two piston chambers forms a damping force, and the moving blades shear the damping liquid of the outer shear chamber. A viscous motion damping force is generated, and the viscous shear force of the viscous liquid in the static vane and the damper chamber also generates a damping force, so the damper can generate a larger damping force in the same volume.
  • a flexible hermetic seal 5b is also provided between the moving body and the cylinder block. Since the rubber ring has a large length and has a guiding effect itself, a guiding block 4b can be omitted.
  • Anchoring bars 12 are welded to the outer surfaces of the cylinder block 2 and the movable body 1, respectively.
  • the damper Because the damper has no precision parts, it is very robust, has strong anti-destruction and overload resistance, and adopts flexible hermetic sealing and anchoring steel. Therefore, the damper can be embedded in the reinforced concrete structure, for example It is embedded in the structural joint between the dam section of the reservoir dam. It can fully absorb the seismic energy during the earthquake, reduce the amplitude of the dam and the cracking degree of the structural joint, and ensure the safety of the dam.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

La présente invention concerne un amortisseur pour réduire les vibrations et absorber de l’énergie, qui comprend un cylindre et un corps mobile, au moins une partie du corps mobile se trouve dans le cylindre. Le cylindre comprend au moins une chambre qui s’étend le long de l’axe du cylindre et est remplie de liquide amortisseur visqueux ; ainsi une chambre d’amortissement est formée. Le corps mobile est constitué d’un élément mobile qui se trouve dans la chambre d’amortissement. L’élément mobile avec la chambre d’amortissement constitue une chambre de cisaillement dont l’épaisseur est inférieure à la taille de son axe. L’amortisseur possède une action d’amortissement flexible et une construction simple, de faible coût, des performances stables et une durée de vie prolongée.
PCT/CN2005/002099 2004-12-11 2005-12-06 Amortisseur WO2006060956A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2007544718A JP2008523324A (ja) 2004-12-11 2005-12-06 減衰器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN200410075501.2 2004-12-11
CNB2004100755012A CN100425860C (zh) 2004-12-11 2004-12-11 阻尼器

Publications (1)

Publication Number Publication Date
WO2006060956A1 true WO2006060956A1 (fr) 2006-06-15

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PCT/CN2005/002099 WO2006060956A1 (fr) 2004-12-11 2005-12-06 Amortisseur

Country Status (3)

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JP (1) JP2008523324A (fr)
CN (1) CN100425860C (fr)
WO (1) WO2006060956A1 (fr)

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JP2008267494A (ja) * 2007-04-20 2008-11-06 Kyoei Ind Co Ltd 流体ダンパ
CN102912881A (zh) * 2012-11-06 2013-02-06 沈阳建筑大学 可调液体粘滞阻尼器

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CN101457554B (zh) * 2007-12-14 2011-01-19 尹学军 阻尼比可调式调谐质量减振器
CN101526119B (zh) * 2008-03-04 2010-09-01 尹学军 阻尼与位移相关型阻尼器
CN102644689B (zh) * 2011-02-22 2014-05-14 中国矿业大学 一种叶轮式馈能减振器
CN102352906A (zh) * 2011-07-16 2012-02-15 西南交通大学 自由膜式防倾斜空气弹簧
CN102410335A (zh) * 2011-08-19 2012-04-11 谭晓婧 单出杆板式磁流变阻尼器
CN102561173B (zh) * 2011-12-19 2014-07-16 北京工业大学 内含剪切增稠液的速度型结构连接锁定装置
CN103266679B (zh) * 2013-05-23 2015-08-05 北京工业大学 一种活塞型颗粒阻尼器
CN103541459B (zh) * 2013-11-08 2015-07-29 同济大学 一种混合消能减振装置
CN103615492B (zh) * 2013-11-29 2016-05-18 重庆材料研究院有限公司 悬挂式磁流变阻尼器及系统
CN103939517B (zh) * 2013-12-06 2016-05-18 重庆材料研究院有限公司 抗冲击磁流变缓冲器的抗过冲击的方法
CN103867629B (zh) * 2014-03-24 2016-03-30 北京京西重工有限公司 一种对动能进行液压耗散的方法和用于实施该方法的装置
CN103938750B (zh) * 2014-04-08 2016-06-15 同济大学 耗能支撑减震装置
CN104895253B (zh) * 2015-04-20 2017-04-26 北京工业大学 一种阻尼钢筋连接器
CN104963424B (zh) * 2015-07-15 2017-10-13 大连理工大学 一种阻尼耗能抗风装置
CN105090334A (zh) * 2015-07-20 2015-11-25 常州大学 单杆变节流孔无源单控变阻尼磁流变阻尼器
CN105065556A (zh) * 2015-07-20 2015-11-18 常州大学 单杆变节流孔无源双控变阻尼磁流变阻尼器
CN105546034B (zh) * 2016-03-04 2018-02-27 江苏大学 一种叶轮式惯性和阻尼设备
CN106013492B (zh) * 2016-06-28 2018-04-20 南京工业大学 一种建筑物防震系统及其感应控制方法
CN109307033B (zh) * 2017-07-28 2021-07-23 青岛海尔洗涤电器有限公司 用于衣物处理装置的减震器和衣物处理装置
US10696336B2 (en) * 2017-10-17 2020-06-30 GM Global Technology Operations LLC Actuation system having a magnetorheological damper
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CN110388404A (zh) * 2019-08-27 2019-10-29 华东交通大学 一种剪切型磁流变液阻尼器
CN110671460A (zh) * 2019-09-24 2020-01-10 南京大德减震科技有限公司 一种剪切式粘滞阻尼器
CN113969952B (zh) * 2021-11-17 2022-09-16 长沙理工大学 一种车用柔性活塞减振器
CN116857313B (zh) * 2023-09-01 2023-11-14 中国科学院长春光学精密机械与物理研究所 可调节阻尼的减振耗能机构

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CN102912881A (zh) * 2012-11-06 2013-02-06 沈阳建筑大学 可调液体粘滞阻尼器
CN102912881B (zh) * 2012-11-06 2015-01-14 沈阳建筑大学 可调液体粘滞阻尼器

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Publication number Publication date
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CN100425860C (zh) 2008-10-15
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