CN113006305A - Additional damping type nonlinear gas spring - Google Patents
Additional damping type nonlinear gas spring Download PDFInfo
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- CN113006305A CN113006305A CN202110217435.1A CN202110217435A CN113006305A CN 113006305 A CN113006305 A CN 113006305A CN 202110217435 A CN202110217435 A CN 202110217435A CN 113006305 A CN113006305 A CN 113006305A
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
- E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
- E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
- E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
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Abstract
The invention discloses an additional damping type nonlinear gas spring which is used for tuning mass damping and comprises a gas spring cavity and a damping cavity, wherein a piston and a piston rod are respectively arranged in the gas spring cavity and the damping cavity and are connected with a damping sliding mass block through the piston rod, and a piston hole in the damping cavity is formed in the piston. The gas spring can realize the function of integrating rigidity and damping, simplifies the configuration of TMD, greatly reduces the maintenance cost of a later system, has a wider vibration reduction frequency band, has shorter working stroke and obvious advantages, and can make up the defect of space limitation of the traditional TMD.
Description
Technical Field
The invention belongs to the field of vibration control of civil engineering, and particularly relates to an additional damping type nonlinear gas spring.
Background
Tuned Mass Dampers (TMD) are widely used for damping of actual engineering structures as a mature quantitative design method. However, the conventional tuned mass damping technology has its own defects, which are mainly reflected in a narrow vibration damping frequency band and a large working stroke, which also greatly limits the practical engineering application. Accordingly, the related scholars have introduced a non-linear mechanism into the conventional TMD to overcome the inherent disadvantages thereof, such as SMA-TMD, sounding-TMD, etc., which all exhibit good damping performance. Therefore, the nonlinear mechanism is introduced into the linear TMD system, the control performance of the damping system can be effectively improved, and the reliability is good.
The gas spring is widely applied to the fields of machinery, aerospace and the like. A gas spring is a sealed container filled with compressed gas and relies primarily on a non-linear restoring force to achieve its spring effect. Currently, gas springs are commonly used as cushioning and isolating elements in machinery and the like, for example, to improve the comfort of automotive suspension systems, to dampen vibrations of precision instruments and machinery, and in these respects exhibit excellent nonlinear properties.
Therefore, the gas spring is introduced into the field of structural vibration control, and the research and development of a novel damping system by combining the traditional tuned mass damping technology is a very potential work. However, the existing gas spring often does not have additional damping performance, and the use requirement of the tuned mass damper is difficult to meet.
Disclosure of Invention
The invention aims to solve the problems and provide an additional damping type nonlinear gas spring, the gas spring is a gas spring with integrated stiffness and damping functions, the spring stiffness has strong nonlinear characteristics, and the gas spring is used in a nonlinear damper and can suppress earthquake and wind vibration.
The purpose of the invention is realized by the following technical scheme:
the utility model provides an additional damping formula nonlinear gas spring for harmonious mass damping, this nonlinear gas spring includes air spring cavity and damping cavity, be equipped with piston and piston rod in air spring cavity and the damping cavity respectively to be connected with damping sliding mass piece through the piston rod, the piston foraminiferous in the damping cavity.
Furthermore, the air spring is a concentric cylinder, the damping cavity is sleeved outside the air spring cavity, the middle cylinder cavity is the air spring, and the outer circular cavity is the damping cavity.
Further, the gas inside the gas spring cavity can be air, nitrogen or helium.
Further, the damping medium inside the damping cavity comprises an oily medium.
Further, the piston rods in the gas spring cavity and the damping cavity are arranged in parallel.
Further, the gas spring cavity and a piston rod in the damping cavity are connected with the damping sliding mass block.
Furthermore, the end parts of the piston rods of the gas spring cavity and the damping cavity are connected through a sleeve connecting piece to perform synchronous motion.
Furthermore, the gas springs are provided with a pair of gas springs which are symmetrically arranged on two sides of the damping sliding mass block.
The gas spring disclosed by the invention can realize the function of integrating rigidity and damping, simplifies the configuration of TMD (tuned mass damper), greatly reduces the maintenance cost of a later system, has a two-stage vibration damping mechanism, has a wider vibration damping frequency band, is shorter in working stroke and remarkable in advantage compared with the traditional TMD, and overcomes the defect of space limitation of the traditional TMD.
The invention provides a novel piston type gas spring with integrated rigidity and damping, which utilizes the novel gas spring to replace the original steel spring and viscous damper to form a novel combined damping technology, namely a Nonlinear Gas Spring Tuned Mass Damper (NGSTMD). The mechanical characteristics of the gas spring have strong nonlinearity, and the nonlinearity becomes stronger and stronger as the working distance of the spring increases.
The working state of the tuned mass damper of the nonlinear gas spring is flexibly converted between two stages of damping mechanisms along with the change of the excitation intensity. Specifically, the method comprises the following steps: 1) when the response of the damping system is small, the gas spring is in an approximately linear working state, the working mechanism of the gas spring is basically consistent with that of a traditional steel spring, vibration energy is transmitted to the damping system from the main structure through the tuning function, and then the energy is dissipated by the damping unit. 2) When the response is larger, the working distance of the mass block is increased sharply, and the tuning mass damper of the nonlinear gas spring enters a nonlinear working stage. Since the non-linear stiffness of the gas spring provides a non-linear restoring force, the proposed damper system has a non-constant natural frequency, and the damper can resonate with a series of primary modes of the structure, thereby expanding its damping band, the so-called "transient resonance catch" effect.
The gas spring simplifies the configuration of the TMD, greatly reduces the maintenance cost of a system at the later stage, has a two-stage vibration reduction mechanism, has a wider vibration reduction frequency band, a shorter working stroke and obvious advantages compared with the traditional TMD, and overcomes the defect of space limitation of the traditional TMD.
Compared with the prior art, the invention has the following advantages:
1) the air spring greatly simplifies the configuration of TMD, and effectively reduces the maintenance cost of a later system;
2) the gas spring has strong nonlinear characteristics, the damper system has non-constant natural frequency, the transient resonance capture effect can be realized, and the damping frequency band is wider than TMD;
3) the damper has good control effect on wind load or/and earthquake action and the like, is flexible in installation position, reduces noise in the working process of the damper by using the air spring to replace the original common steel spring, is suitable for high-rise buildings and high-rise structures, and can generate better social benefit and economic benefit.
Drawings
FIG. 1 is a schematic structural view of an additional damping type nonlinear gas spring according to the present invention;
FIGS. 2 and 3 are schematic cross-sectional views A-A and B-B of FIG. 1, respectively;
FIG. 4 is a schematic diagram of an application structure of an additional damping type nonlinear gas spring according to the present invention;
in the figure: 1 is an air spring, 2 is a mass block, 3 is a slide rail, 4 is a middle support, and 5 is an edge support; 1-1 is a gas spring cavity, 1-2 is a piston and a piston rod of the gas spring, 1-3 is a damping cavity, 1-4 is a piston and a piston rod of the damping cavity, and 1-5 is a sleeve connecting piece at the end part of the piston rod.
Detailed Description
The invention is described in detail below with reference to the figures and specific embodiments.
The additional damping type nonlinear gas spring 1 has a mechanism integrating rigidity and damping, and is constructed into concentric cylinders, as shown in figures 1-3, a middle cylinder cavity 1-1 is a gas spring, 1-2 is a piston and a piston rod of the gas spring, a circular ring cavity 1-3 is a damping cavity, 1-4 is a piston and a piston rod of the damping cavity, and 1-5 at the end part of the piston rod is a sleeve connecting piece.
Referring to fig. 2, a tuned mass damper for a non-linear gas spring with additional damping comprises a gas spring 1, a mass block 2, a slide rail 3, a middle support 4 and an edge support 5. The mass block 2 is constructed by I-shaped steel and integrally milled, a middle web plate is provided with a hole and is connected with the air spring 1, and a lower flange plate is provided with a bolt hole and is connected with the slide rail 3; the slide rail 3 consists of a slide block and a guide rail; the middle bracket 4 consists of an upper cover plate, a hollow U-shaped plate and a bottom plate, the lower end of the bottom plate is provided with a hole, and the bottom plate is provided with a bolt hole; the edge support 5 is similar to the middle support 4 in structure, and is different from the middle support in that an upper cover plate is not arranged, a U-shaped groove is formed in the middle plate, the depth of the groove is half of the thickness of the plate, and a hole is not formed in the bottom plate.
In the embodiment, the gas spring 1 can provide the rigidity required by the system and viscous damping, the rigidity is strong nonlinear, the whole structure is a concentric cylinder, wherein the middle cylinder cavity 1-1 is the gas spring, one side of the piston is filled with gas (nitrogen, helium or air), and the other side is communicated with the outside; the annular cavity 1-3 is a damping cavity filled with damping medium, the piston 1-4 is an annular piston with holes, and the medium can flow through the holes when the piston moves; the bushing connectors 1-5 are mainly used for connecting the piston rods.
In this embodiment, the shape of quality piece 2 is the I shape, and open the circular port in the middle of the web, can imbed the tailpiece of the piston rod of air spring 1, and the oblique symmetry trompil of bottom plate reduces the mass loss for connect slide rail 3.
In this embodiment, the slide rail 3 comprises slider and guide rail, and there is the bolt hole slider upper portion, is convenient for install quality piece 2.
In this embodiment, middle support 4 comprises upper cover plate, cavity U template and bottom plate, and the upper cover plate is used for fixed air spring 1, and air spring 1 card is in the middle of the U template, and the bottom plate is opened the rectangle hole, can put up the bolt hole that has on slide rail 3 upper plate for it is fixed.
In this embodiment, the edge support 5 is composed of a slotted U-shaped plate and a bottom plate, the slot depth is 1/2 of the plate thickness, and the bottom plate is provided with bolt holes for fixing.
During the specific use, with slide rail 3, middle support 4 and edge support 5 assembly in the bottom plate, utilize support 4 and 5 to fix gas spring 1 in preset position, mass block 2 is installed in the slider top with the bolt, after gas spring 1 carries out the pre-compaction with the tip embedding mass block 2's intermediate position.
When earthquake and wind load are excited, the nonlinear damping system starts to work, the energy of the main structure is transferred to the damping system, and the mass block 2 slides back and forth along the slide rail 3 to drive the piston rod of the gas spring 1 to move left and right. Wherein, the piston and the piston rod 1-2 of the gas spring compress the gas in the cavity 1-1 of the gas spring to generate the elastic restoring force required by the system; meanwhile, the piston and the piston rod 1-4 of the damping cavity move back and forth in the damping cavity 1-3, and damping media in the cavity flow through the round hole in the piston to generate damping force. That is to say, the damping system transmits the vibration energy of the main structure to the damping system through the tuning function, drives the mass block 2 to move, further damps the piston movement of the cavities 1-3, and further dissipates the energy by using the viscous damping of the flowing damping medium.
The embodiments described above are described to facilitate an understanding and use of the invention by those skilled in the art. It will be readily apparent to those skilled in the art that various modifications to these embodiments may be made, and the generic principles described herein may be applied to other embodiments without the use of the inventive faculty. Therefore, the present invention is not limited to the above embodiments, and those skilled in the art should make improvements and modifications within the scope of the present invention based on the disclosure of the present invention.
Claims (8)
1. The utility model provides an additional damping formula nonlinear gas spring for harmonious mass damping, its characterized in that, this nonlinear gas spring includes air spring cavity and damping cavity, be equipped with piston and piston rod in air spring cavity and the damping cavity respectively to be connected with damping sliding mass piece through the piston rod, piston foraminiferous in the damping cavity.
2. The additional damping type nonlinear gas spring as set forth in claim 1 wherein said gas spring is a concentric cylinder, said damping cavity is nested outside said gas spring cavity, the middle cylinder cavity is a gas spring, and the outer annular cavity is a damping cavity.
3. An additionally damped non-linear gas spring as set forth in claim 2 wherein said gas within said gas spring chamber is air, nitrogen or helium.
4. An additionally damped non-linear gas spring as set forth in claim 2 wherein said damping medium within said damping chamber comprises an oil based medium.
5. An additionally damped non-linear gas spring as set forth in claim 1 wherein said piston rods in said gas spring chamber and said damping chamber are disposed in parallel.
6. An additionally damped non-linear gas spring as set forth in claim 5 wherein said gas spring chamber and said piston rod within said damping chamber are connected to a damping sliding mass.
7. An additionally damped non-linear gas spring as set forth in claim 5 wherein said gas spring chamber and said damping chamber piston rod ends are connected for synchronous movement by a sleeve connection.
8. An additionally damped non-linear gas spring as set forth in claim 1 wherein said gas spring is provided in a pair symmetrically disposed on opposite sides of said damping sliding mass.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110217435.1A CN113006305A (en) | 2021-02-26 | 2021-02-26 | Additional damping type nonlinear gas spring |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110217435.1A CN113006305A (en) | 2021-02-26 | 2021-02-26 | Additional damping type nonlinear gas spring |
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| CN113006305A true CN113006305A (en) | 2021-06-22 |
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| CN202110217435.1A Pending CN113006305A (en) | 2021-02-26 | 2021-02-26 | Additional damping type nonlinear gas spring |
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| JP2002021918A (en) * | 2000-06-30 | 2002-01-23 | Ohbayashi Corp | Vibration isolation device |
| CN2811665Y (en) * | 2005-05-26 | 2006-08-30 | 江苏大学 | Single-chamber oil-gas separation type oil-gas spring with nonlinear characteristics |
| US20110037209A1 (en) * | 2009-08-11 | 2011-02-17 | Ruentex Engineering & Construction Co., Ltd. | Vibration Damping Construction System |
| CN102174948A (en) * | 2011-02-28 | 2011-09-07 | 张红辉 | Decoupling-type constant-pressure oil chamber double-cylinder pneumatic spring |
| CN202392036U (en) * | 2011-11-17 | 2012-08-22 | 东南大学 | Large-damping vertical viscoelastic vibration isolating and damping device |
| US20130257011A1 (en) * | 2012-03-27 | 2013-10-03 | Showa Corporation | Damping force generator for hydraulic shock absorber |
| CN103510636A (en) * | 2013-10-15 | 2014-01-15 | 北京工业大学 | Assembled viscous double-sub-energy-dissipation device |
| US20140138887A1 (en) * | 2011-07-08 | 2014-05-22 | Rafael Knobloch | Gas spring with dampening |
| CN104373495A (en) * | 2014-11-13 | 2015-02-25 | 常州市华贤五金厂 | Double parallel connection gas-liquid damping cylinder |
| CN105402302A (en) * | 2015-12-21 | 2016-03-16 | 吉林大学 | Magneto-rheological sliding column integrated with air spring |
| CN106704439A (en) * | 2016-11-21 | 2017-05-24 | 大连理工大学 | Tuned mass damper based on symmetrical combination-type air springs |
| CN208907433U (en) * | 2018-06-12 | 2019-05-28 | 重庆商务职业学院 | Variable damping formula turning gear with gas spring |
-
2021
- 2021-02-26 CN CN202110217435.1A patent/CN113006305A/en active Pending
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002021918A (en) * | 2000-06-30 | 2002-01-23 | Ohbayashi Corp | Vibration isolation device |
| CN2811665Y (en) * | 2005-05-26 | 2006-08-30 | 江苏大学 | Single-chamber oil-gas separation type oil-gas spring with nonlinear characteristics |
| US20110037209A1 (en) * | 2009-08-11 | 2011-02-17 | Ruentex Engineering & Construction Co., Ltd. | Vibration Damping Construction System |
| CN102174948A (en) * | 2011-02-28 | 2011-09-07 | 张红辉 | Decoupling-type constant-pressure oil chamber double-cylinder pneumatic spring |
| US20140138887A1 (en) * | 2011-07-08 | 2014-05-22 | Rafael Knobloch | Gas spring with dampening |
| CN202392036U (en) * | 2011-11-17 | 2012-08-22 | 东南大学 | Large-damping vertical viscoelastic vibration isolating and damping device |
| US20130257011A1 (en) * | 2012-03-27 | 2013-10-03 | Showa Corporation | Damping force generator for hydraulic shock absorber |
| CN103510636A (en) * | 2013-10-15 | 2014-01-15 | 北京工业大学 | Assembled viscous double-sub-energy-dissipation device |
| CN104373495A (en) * | 2014-11-13 | 2015-02-25 | 常州市华贤五金厂 | Double parallel connection gas-liquid damping cylinder |
| CN105402302A (en) * | 2015-12-21 | 2016-03-16 | 吉林大学 | Magneto-rheological sliding column integrated with air spring |
| CN106704439A (en) * | 2016-11-21 | 2017-05-24 | 大连理工大学 | Tuned mass damper based on symmetrical combination-type air springs |
| CN208907433U (en) * | 2018-06-12 | 2019-05-28 | 重庆商务职业学院 | Variable damping formula turning gear with gas spring |
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Application publication date: 20210622 |