CN102678808A - Shock absorbing system with combined rigidity and damping adjusting function and shock absorbing method - Google Patents
Shock absorbing system with combined rigidity and damping adjusting function and shock absorbing method Download PDFInfo
- Publication number
- CN102678808A CN102678808A CN2012101911667A CN201210191166A CN102678808A CN 102678808 A CN102678808 A CN 102678808A CN 2012101911667 A CN2012101911667 A CN 2012101911667A CN 201210191166 A CN201210191166 A CN 201210191166A CN 102678808 A CN102678808 A CN 102678808A
- Authority
- CN
- China
- Prior art keywords
- damping
- pneumatic spring
- magneto
- vibration damper
- valve
- Prior art date
- Legal status (The legal status 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 status listed.)
- Pending
Links
Images
Landscapes
- Vehicle Body Suspensions (AREA)
Abstract
The invention discloses a shock absorbing system with a combined rigidity and damping adjusting function and a shock absorbing method. An air spring with an additional air chamber and a magnetorheological shock absorber which are connected in parallel are arranged between an upper connecting plate of a suspension frame and a bottom plate of the suspension frame; and the air spring is connected with the additional air chamber via a positioning control valve. The shock absorbing method comprises the following steps that a controller performs Fourier transformation on automobile body response acceleration time domain signals at a specified time interval, and outputs control signals to the positioning control valve according to the biggest excitation frequency of vertical energy, the opening of an orifice between the air spring and the additional air chamber is controlled and adjusted in real time, so that the rigidity of the suspension frame is changed, the purpose of avoiding the excitation frequency is achieved, the damping of the suspension frame is adjusted by changing input current of the magnetorheological shock absorber, and shock is attenuated further. The combined rigidity and damping adjusting function can be realized, an adjusting range is expanded, the shock absorbing system adapts to complex and changeable running work conditions of automobiles, and the shock absorbing property is increased.
Description
Technical field
The present invention relates to the vehicle suspension system field, be specifically related to the damping technology of vehicle suspension system.
Background technique
In the vehicle driving process, the vibration of Vehicular system can cause the uncomfortable of occupant, jeopardizes occupant's physical and mental health, also can cause the tired and destruction of institute's bearing goods and the structure member of vehicle own, influences the durability and the travelling comfort of vehicle.Therefore, but the vibration insulating system that an effective attenuation vibrational energy is provided to safeguarding that the occupant is physically and mentally healthy, improving vehicle durability etc. and have very great help.
At present, the vehicle chassis vibration insulating system helical spring of deciding rigidity and the dydraulic shock absorber of the deciding damping of adopting as damping element more, and its rigidity and damping design to specific operation; System vibration performance immobilizes, and can not adapt to the driving cycle of variation, and the adjustable dydraulic shock absorber throttle valve complex structure of orifice size; Energy consumption is big; And only on several levels, realized Adjustable Damping, regulation range is narrower, has limited the further raising of vehicle performance; Still be difficult to adapt to vehicle driving cycle complicated and changeable, effectiveness in vibration suppression is undesirable.
Summary of the invention
The objective of the invention is for overcoming the deficiency of above-mentioned existing technology the vibration insulating system and the oscillation damping method that provide a kind of rigidity and damping to unite adjusting.
1, the vibration insulating system of adjusting is united in a kind of rigidity and damping, it is characterized in that:
Pneumatic spring with the band auxiliary chamber is an elastic element; With the magneto-rheological vibration damper is damping member; Set up the continuously adjustable semi-active suspension system of rigidity and damping, the pneumatic spring upper bracket is fixedly connected with the suspension upper junction plate, and the pneumatic spring lower support frame is connected with the suspension base plate; Pneumatic spring is connected with air supply system through levelling valve, and levelling valve is controlled by controlling rod, controls an end and is connected with levelling valve, the other end and suspension base plate hinged; Pneumatic spring links to each other with auxiliary chamber through the positioning control valve; An output port of the signaling line of positioning control valve and controller joins; Magneto-rheological vibration damper is parallelly connected with pneumatic spring; Magneto-rheological vibration damper upper bracket and suspension upper junction plate are hinged, magneto-rheological vibration damper lower support frame and suspension base plate hinged; Another output port of lead that field coil is drawn in the magneto-rheological vibration damper and controller joins.
The initial mounting point of above-mentioned pneumatic spring is by levelling valve control adjustment; When pneumatic spring is in compression or extended state; Levelling valve is opened gas charging valve or the outlet valve in it under the controlling rod effect; Air supply system is to pneumatic spring inflation or exhaust, when pneumatic spring returns to its equilibrium position, valve closing.
2, the oscillation damping method of adjusting is united in a kind of rigidity and damping, and its characteristic is may further comprise the steps:
(1), the positioning control valve is initially set to full-shut position; The every interval of controller certain hour just carries out Fourier transformation to vehicle body response acceleration time-domain signal; Calculate the maximum energizing frequency of vertical vibration energy, export control signal to the positioning control valve, in real time throttle orifice aperture between regulating and controlling pneumatic spring and the auxiliary chamber by controller; Thereby change the rigidity of suspension, reach the purpose of avoiding energizing frequency;
(2), when throttle orifice is adjusted to certain aperture, the pneumatic spring of band auxiliary chamber also has certain damping function, can satisfy under the better operating mode of vehicle the demand to damping, and under relatively poor operating mode, still need magneto-rheological vibration damper to come attenuation vibration;
(3), utilize the rheological effect of magnetic flow liquid under the different exciting electric current to change the damping size of magneto-rheological vibration damper; The size of field coil input current is controlled by controller in real time in the magneto-rheological vibration damper; The realization damping force is regulated continuously, and it is simple in structure, and energy consumption is low.
The beneficial effect that the present invention reached: the method that adopts rigidity and damping to unite adjusting reaches the vibration damping purpose, at first utilizes restriction aperture between positioning control valve regulation pneumatic spring and the auxiliary chamber, has avoided resonant frequency, and system can not resonate like this.Then,, control the magneto-rheological vibration damper input current in real time, for system provides different big or small dampings, further attenuation vibration through controller according to the needs of different operating modes to damping.This vibration insulating system does not need the electromechanical control valve, has simplified system architecture.With respect to traditional vibration insulating system, the present invention can realize the adjusting of uniting of rigidity and damping, adapts to driving cycle complicated and changeable, improves damping property.
Description of drawings
Fig. 1 is a general structure schematic representation of the present invention.
Fig. 2 is under certain spring carried mass, the corresponding relation of throttle orifice aperture and air spring rigidity.
Fig. 3 is under certain spring carried mass, the corresponding relation of throttle orifice aperture and pneumatic spring damping.
Fig. 4 is under certain spring carried mass, the distribution map in suspension damping compares between rigidity and damping regulatory region.
Among Fig. 1: 1-suspension base plate; 2-magneto-rheological vibration damper lower support frame; The 3-magneto-rheological vibration damper; The 4-auxiliary chamber; 5 suspension upper junction plates; 6-magneto-rheological vibration damper upper bracket; 7 leads; The 8-controller; 9 signaling lines; 10-positioning control valve; The 11-pneumatic spring; 12-pneumatic spring upper bracket; 13 levelling valves; The 14-controlling rod; 15-pneumatic spring lower support frame; The 16-air supply system.
Embodiment
Referring to Fig. 1; Vibration insulating system of the present invention is an elastic element with the pneumatic spring (11) of band auxiliary chamber (4); With magneto-rheological vibration damper (3) is damping member; Pneumatic spring (11) is parallelly connected with magneto-rheological vibration damper (3) to be arranged between suspension upper junction plate (5) and the suspension base plate (1), and pneumatic spring upper bracket (12) is fixedly connected with suspension upper junction plate (5), and pneumatic spring lower support frame (15) is connected with suspension base plate (1); Magneto-rheological vibration damper upper bracket (6) is hinged with suspension upper junction plate (5), and magneto-rheological vibration damper lower support frame (2) is hinged with suspension base plate (1).Pneumatic spring (11) links to each other with auxiliary chamber (4) through positioning control valve (10), and pneumatic spring (11) is connected with air supply system (16) through levelling valve (13); Levelling valve (13) is controlled by controlling rod (14); Controlling rod (14) one ends are connected with levelling valve (13), and the other end and suspension base plate (1) are hinged, under the different bearer operating mode; The initialization position of pneumatic spring (11) is by levelling valve (13) control adjustment, and when pneumatic spring (11) was in compression or extended state, levelling valve (13) was opened gas charging valve or the outlet valve in it under controlling rod (14) effect; Air supply system (16) is to pneumatic spring (11) inflation or exhaust; When pneumatic spring (1) returns to its equilibrium position, valve closing, the working stroke that can guarantee pneumatic spring (11) like this is near its equilibrium position; Make full use of its stiffness characteristics, and guarantee its working stability.
Oscillation damping method of the present invention is:
Referring to Fig. 2; Positioning control valve (10) is initially set to full-shut position; The every interval of controller (8) certain hour just carries out Fourier transformation to vehicle body response acceleration time-domain signal, calculates the maximum energizing frequency of vertical vibration energy, according to the corresponding relation of the rigidity and the throttle orifice aperture of pneumatic spring shown in Figure 2 (11); Export control signal by controller (8) to positioning control valve (10); Throttle orifice aperture between real-time regulating and controlling pneumatic spring (11) and the auxiliary chamber (4), thus the rigidity of change suspension reaches the purpose of avoiding energizing frequency.
Referring to Fig. 3; When throttle orifice is adjusted to certain aperture; The pneumatic spring (11) of band auxiliary chamber (4) also has certain damping function; The damping that pneumatic spring (11) produces can be satisfied under the better operating mode of vehicle the demand to damping, and under relatively poor operating mode, still needs magneto-rheological vibration damper (3) to come attenuation vibration;
Referring to Fig. 4, confirmed the throttle orifice aperture under certain operating mode, set suitable damping ratio then, thereby the damping of rational Match magneto-rheological vibration damper (3) meets the demands damping ratio.The damping size of magneto-rheological vibration damper (3) is regulated by the field coil input current, and the size of coil input current is controlled by controller in real time, and the realization damping force is regulated continuously.The present invention is simple in structure; Energy consumption is low, in conjunction with certain control strategy, adjusts throttle orifice aperture between input current and the pneumatic spring (11) and the auxiliary chamber (4) of magneto-rheological vibration damper (3) field coil in real time; Realized the adjusting of uniting of rigidity and damping, effectiveness in vibration suppression is better.
The above only is a preferred implementation of the present invention; For those skilled in the art; Under the prerequisite that does not break away from know-why of the present invention, can also make some improvement and distortion, these improvement and distortion also should be regarded as protection scope of the present invention.
Claims (2)
1. the vibration insulating system of adjusting is united in rigidity and damping, it is characterized in that:
Pneumatic spring (11) with band auxiliary chamber (4) is an elastic element; With magneto-rheological vibration damper (3) is damping member; Set up the continuously adjustable semi-active suspension system of rigidity and damping; Pneumatic spring upper bracket (12) is fixedly connected with suspension upper junction plate (5), and pneumatic spring lower support frame (15) is connected with suspension base plate (1); Pneumatic spring (11) is connected with air supply system (16) through levelling valve (13), and levelling valve (13) is by controlling rod (14) control, and controlling rod (14) one ends are connected with levelling valve (13), and the other end and suspension base plate (1) are hinged; Pneumatic spring (11) links to each other with auxiliary chamber (4) through positioning control valve (10); The signaling line (9) of positioning control valve (10) joins with an output port of controller (8); Magneto-rheological vibration damper (3) is parallelly connected with pneumatic spring (11); Magneto-rheological vibration damper upper bracket (6) is hinged with suspension upper junction plate (5), and magneto-rheological vibration damper lower support frame (2) is hinged with suspension base plate (1); The lead (7) that field coil is drawn in the magneto-rheological vibration damper (3) joins with another output port of controller (8);
The initial mounting point of above-mentioned pneumatic spring (11) is by levelling valve (13) control adjustment; When pneumatic spring (11) is in compression or extended state; Levelling valve (13) is opened gas charging valve or the outlet valve in it under controlling rod (14) effect; Air supply system (16) is to pneumatic spring (11) inflation or exhaust, when pneumatic spring (11) returns to its equilibrium position, valve closing.
2. the oscillation damping method of adjusting is united in rigidity and damping, and its characteristic is may further comprise the steps:
(1), positioning control valve (10) is initially set to full-shut position; The every interval of controller (8) certain hour just carries out Fourier transformation to vehicle body response acceleration time-domain signal; Calculate the maximum energizing frequency of vertical vibration energy, export control signal to positioning control valve (10), in real time throttle orifice aperture between regulating and controlling pneumatic spring (11) and the auxiliary chamber (4) by controller (8); Thereby change the rigidity of suspension, reach the purpose of avoiding energizing frequency;
(2), when throttle orifice is adjusted to certain aperture, the pneumatic spring (11) of band auxiliary chamber (4) also has certain damping function, can satisfy under the better operating mode of vehicle the demand to damping, and under relatively poor operating mode, still need magneto-rheological vibration damper (3) to come attenuation vibration;
(3), utilize the rheological effect of magnetic flow liquid under the different exciting electric current to change the damping size of magneto-rheological vibration damper (3); The size of field coil input current is by controller (8) control in real time in the magneto-rheological vibration damper (3); The realization damping force is regulated continuously, and it is simple in structure, and energy consumption is low.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012101911667A CN102678808A (en) | 2012-06-12 | 2012-06-12 | Shock absorbing system with combined rigidity and damping adjusting function and shock absorbing method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012101911667A CN102678808A (en) | 2012-06-12 | 2012-06-12 | Shock absorbing system with combined rigidity and damping adjusting function and shock absorbing method |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102678808A true CN102678808A (en) | 2012-09-19 |
Family
ID=46811183
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012101911667A Pending CN102678808A (en) | 2012-06-12 | 2012-06-12 | Shock absorbing system with combined rigidity and damping adjusting function and shock absorbing method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102678808A (en) |
Cited By (30)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103225668A (en) * | 2013-04-02 | 2013-07-31 | 江苏大学 | Load-sensing variable-damping electromagnetic shock absorption system |
| CN103727171A (en) * | 2012-10-16 | 2014-04-16 | 义乌市黑白矿山机械有限公司 | Shock absorption machine base |
| CN103727170A (en) * | 2012-10-16 | 2014-04-16 | 义乌市黑白矿山机械有限公司 | Resonance-resisting damping machine base |
| CN104401200A (en) * | 2014-10-31 | 2015-03-11 | 北京新能源汽车股份有限公司 | Suspension device |
| US9205717B2 (en) | 2012-11-07 | 2015-12-08 | Polaris Industries Inc. | Vehicle having suspension with continuous damping control |
| CN105172511A (en) * | 2015-07-15 | 2015-12-23 | 西南交通大学 | Automobile suspension shock absorber control system and method |
| CN105459753A (en) * | 2015-12-03 | 2016-04-06 | 安徽农业大学 | Electronic control air suspension spring stiffness adjusting structure |
| CN106012807A (en) * | 2016-07-29 | 2016-10-12 | 浙江大学建筑设计研究院有限公司 | Low-frequency self-adaption tuned mass damper |
| CN106151357A (en) * | 2016-07-30 | 2016-11-23 | 江苏师范大学 | A kind of rigidity and damp adjustable bullet train half active air suspension arrangement |
| US9662954B2 (en) | 2012-11-07 | 2017-05-30 | Polaris Industries Inc. | Vehicle having suspension with continuous damping control |
| CN106763411A (en) * | 2016-11-09 | 2017-05-31 | 上海卫星装备研究所 | A kind of isolation mounting for the in-orbit weightlessness simulation of spacecraft |
| CN107815954A (en) * | 2017-12-06 | 2018-03-20 | 哈尔滨市市政工程设计院 | The overpass or steel suspension bridge of Vibration Active Control are realized based on pneumatic muscles |
| US10124709B2 (en) | 2015-05-15 | 2018-11-13 | Polaris Industries Inc. | Utility vehicle |
| CN109655225A (en) * | 2019-01-29 | 2019-04-19 | 吉林大学 | A kind of adjustable wind-tunnel testing stand and test method for the test of car model fluid structurecoupling |
| CN109703423A (en) * | 2019-01-07 | 2019-05-03 | 唐昕 | The control method of vehicle seat suspension system based on ER fluid |
| CN109760708A (en) * | 2019-03-25 | 2019-05-17 | 中车青岛四方车辆研究所有限公司 | Empty spring upper cover, air spring and rail vehicle |
| US10406884B2 (en) | 2017-06-09 | 2019-09-10 | Polaris Industries Inc. | Adjustable vehicle suspension system |
| CN110228343A (en) * | 2019-05-15 | 2019-09-13 | 江苏师范大学 | A kind of magnetorheological air suspension control system of partly active and its control method |
| CN110641502A (en) * | 2019-11-06 | 2020-01-03 | 中车株洲电力机车有限公司 | Dynamic adjusting method for train bogie suspension system |
| CN111120561A (en) * | 2018-11-01 | 2020-05-08 | 株洲中车机电科技有限公司 | Damping device and damping method for electric cabinet |
| CN112172436A (en) * | 2020-10-12 | 2021-01-05 | 中车株洲电力机车有限公司 | Air spring height adjusting system and method for medium-low speed maglev train |
| US10946736B2 (en) | 2018-06-05 | 2021-03-16 | Polaris Industries Inc. | All-terrain vehicle |
| US10987987B2 (en) | 2018-11-21 | 2021-04-27 | Polaris Industries Inc. | Vehicle having adjustable compression and rebound damping |
| CN112937411A (en) * | 2019-12-10 | 2021-06-11 | 长沙智能驾驶研究院有限公司 | Multi-stage damping linkage control method and system for refrigeration device |
| US11110913B2 (en) | 2016-11-18 | 2021-09-07 | Polaris Industries Inc. | Vehicle having adjustable suspension |
| CN113898290A (en) * | 2021-10-09 | 2022-01-07 | 龙岩学院 | Ground source heat pump building construction device based on control of making an uproar falls in driving system |
| US11285964B2 (en) | 2014-10-31 | 2022-03-29 | Polaris Industries Inc. | System and method for controlling a vehicle |
| CN116044949A (en) * | 2022-12-21 | 2023-05-02 | 珠海格力电器股份有限公司 | Adjusting device, adjusting method and equipment of adjusting device |
| CN116292740A (en) * | 2023-03-24 | 2023-06-23 | 大连地拓电子工程技术有限公司 | Quasi-zero rigidity three-degree-of-freedom active anti-micro-vibration platform |
| US11904648B2 (en) | 2020-07-17 | 2024-02-20 | Polaris Industries Inc. | Adjustable suspensions and vehicle operation for off-road recreational vehicles |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20020020594A1 (en) * | 2000-08-14 | 2002-02-21 | Ward Michael C. | Suspension strut |
| JP2004301271A (en) * | 2003-03-31 | 2004-10-28 | Tokico Ltd | Damping force adjustment type shock absorber |
| CN201042978Y (en) * | 2007-04-27 | 2008-04-02 | 张西航 | Steering room air spring vibration reduction suspending device |
| CN201679901U (en) * | 2009-11-26 | 2010-12-22 | 重庆师范大学 | Precise vibration isolation device |
| CN202046381U (en) * | 2011-01-20 | 2011-11-23 | 南京农业大学 | Vibration absorber for cab |
-
2012
- 2012-06-12 CN CN2012101911667A patent/CN102678808A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20020020594A1 (en) * | 2000-08-14 | 2002-02-21 | Ward Michael C. | Suspension strut |
| JP2004301271A (en) * | 2003-03-31 | 2004-10-28 | Tokico Ltd | Damping force adjustment type shock absorber |
| CN201042978Y (en) * | 2007-04-27 | 2008-04-02 | 张西航 | Steering room air spring vibration reduction suspending device |
| CN201679901U (en) * | 2009-11-26 | 2010-12-22 | 重庆师范大学 | Precise vibration isolation device |
| CN202046381U (en) * | 2011-01-20 | 2011-11-23 | 南京农业大学 | Vibration absorber for cab |
Non-Patent Citations (2)
| Title |
|---|
| 《科学技术与工程》 20111130 柳伟等 "半主动悬架座椅的设计及振动特性实验研究" 第11卷, 第31期 * |
| 柳伟等: ""半主动悬架座椅的设计及振动特性实验研究"", 《科学技术与工程》 * |
Cited By (53)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103727170A (en) * | 2012-10-16 | 2014-04-16 | 义乌市黑白矿山机械有限公司 | Resonance-resisting damping machine base |
| CN103727171A (en) * | 2012-10-16 | 2014-04-16 | 义乌市黑白矿山机械有限公司 | Shock absorption machine base |
| US9662954B2 (en) | 2012-11-07 | 2017-05-30 | Polaris Industries Inc. | Vehicle having suspension with continuous damping control |
| US10005335B2 (en) | 2012-11-07 | 2018-06-26 | Polaris Industries Inc. | Vehicle having suspension with continuous damping control |
| US11400786B2 (en) | 2012-11-07 | 2022-08-02 | Polaris Industries Inc. | Vehicle having suspension with continuous damping control |
| US9205717B2 (en) | 2012-11-07 | 2015-12-08 | Polaris Industries Inc. | Vehicle having suspension with continuous damping control |
| US11970036B2 (en) | 2012-11-07 | 2024-04-30 | Polaris Industries Inc. | Vehicle having suspension with continuous damping control |
| US11400785B2 (en) | 2012-11-07 | 2022-08-02 | Polaris Industries Inc. | Vehicle having suspension with continuous damping control |
| US11400787B2 (en) | 2012-11-07 | 2022-08-02 | Polaris Industries Inc. | Vehicle having suspension with continuous damping control |
| US11124036B2 (en) | 2012-11-07 | 2021-09-21 | Polaris Industries Inc. | Vehicle having suspension with continuous damping control |
| US11400784B2 (en) | 2012-11-07 | 2022-08-02 | Polaris Industries Inc. | Vehicle having suspension with continuous damping control |
| CN103225668B (en) * | 2013-04-02 | 2015-08-26 | 江苏大学 | Mutative damp electromagnetic vibration damping system is carried in a kind of sense |
| CN103225668A (en) * | 2013-04-02 | 2013-07-31 | 江苏大学 | Load-sensing variable-damping electromagnetic shock absorption system |
| US11285964B2 (en) | 2014-10-31 | 2022-03-29 | Polaris Industries Inc. | System and method for controlling a vehicle |
| CN104401200A (en) * | 2014-10-31 | 2015-03-11 | 北京新能源汽车股份有限公司 | Suspension device |
| US11919524B2 (en) | 2014-10-31 | 2024-03-05 | Polaris Industries Inc. | System and method for controlling a vehicle |
| US11752860B2 (en) | 2015-05-15 | 2023-09-12 | Polaris Industries Inc. | Utility vehicle |
| US10124709B2 (en) | 2015-05-15 | 2018-11-13 | Polaris Industries Inc. | Utility vehicle |
| CN105172511B (en) * | 2015-07-15 | 2017-09-26 | 西南交通大学 | A kind of shock absorber of automobile suspension control system and method |
| CN105172511A (en) * | 2015-07-15 | 2015-12-23 | 西南交通大学 | Automobile suspension shock absorber control system and method |
| CN105459753A (en) * | 2015-12-03 | 2016-04-06 | 安徽农业大学 | Electronic control air suspension spring stiffness adjusting structure |
| CN106012807A (en) * | 2016-07-29 | 2016-10-12 | 浙江大学建筑设计研究院有限公司 | Low-frequency self-adaption tuned mass damper |
| CN106151357B (en) * | 2016-07-30 | 2018-01-26 | 江苏师范大学 | A kind of rigidity and the active air suspension arrangement of damp adjustable bullet train half |
| CN106151357A (en) * | 2016-07-30 | 2016-11-23 | 江苏师范大学 | A kind of rigidity and damp adjustable bullet train half active air suspension arrangement |
| CN106763411A (en) * | 2016-11-09 | 2017-05-31 | 上海卫星装备研究所 | A kind of isolation mounting for the in-orbit weightlessness simulation of spacecraft |
| US11878678B2 (en) | 2016-11-18 | 2024-01-23 | Polaris Industries Inc. | Vehicle having adjustable suspension |
| US11110913B2 (en) | 2016-11-18 | 2021-09-07 | Polaris Industries Inc. | Vehicle having adjustable suspension |
| US11479075B2 (en) | 2017-06-09 | 2022-10-25 | Polaris Industries Inc. | Adjustable vehicle suspension system |
| US10406884B2 (en) | 2017-06-09 | 2019-09-10 | Polaris Industries Inc. | Adjustable vehicle suspension system |
| US10987989B2 (en) | 2017-06-09 | 2021-04-27 | Polaris Industries Inc. | Adjustable vehicle suspension system |
| US11912096B2 (en) | 2017-06-09 | 2024-02-27 | Polaris Industries Inc. | Adjustable vehicle suspension system |
| CN107815954B (en) * | 2017-12-06 | 2023-11-10 | 哈尔滨市市政工程设计院 | Pedestrian overpass or steel temporary bridge realizing active vibration control based on pneumatic muscles |
| CN107815954A (en) * | 2017-12-06 | 2018-03-20 | 哈尔滨市市政工程设计院 | The overpass or steel suspension bridge of Vibration Active Control are realized based on pneumatic muscles |
| US10946736B2 (en) | 2018-06-05 | 2021-03-16 | Polaris Industries Inc. | All-terrain vehicle |
| CN111120561A (en) * | 2018-11-01 | 2020-05-08 | 株洲中车机电科技有限公司 | Damping device and damping method for electric cabinet |
| US11884117B2 (en) | 2018-11-21 | 2024-01-30 | Polaris Industries Inc. | Vehicle having adjustable compression and rebound damping |
| US10987987B2 (en) | 2018-11-21 | 2021-04-27 | Polaris Industries Inc. | Vehicle having adjustable compression and rebound damping |
| US11975584B2 (en) | 2018-11-21 | 2024-05-07 | Polaris Industries Inc. | Vehicle having adjustable compression and rebound damping |
| CN109703423A (en) * | 2019-01-07 | 2019-05-03 | 唐昕 | The control method of vehicle seat suspension system based on ER fluid |
| CN109655225A (en) * | 2019-01-29 | 2019-04-19 | 吉林大学 | A kind of adjustable wind-tunnel testing stand and test method for the test of car model fluid structurecoupling |
| CN109655225B (en) * | 2019-01-29 | 2024-03-29 | 吉林大学 | Adjustable wind tunnel test bed and test method for fluid-solid coupling test of automobile model |
| CN109760708A (en) * | 2019-03-25 | 2019-05-17 | 中车青岛四方车辆研究所有限公司 | Empty spring upper cover, air spring and rail vehicle |
| CN110228343A (en) * | 2019-05-15 | 2019-09-13 | 江苏师范大学 | A kind of magnetorheological air suspension control system of partly active and its control method |
| CN110641502A (en) * | 2019-11-06 | 2020-01-03 | 中车株洲电力机车有限公司 | Dynamic adjusting method for train bogie suspension system |
| CN112937411A (en) * | 2019-12-10 | 2021-06-11 | 长沙智能驾驶研究院有限公司 | Multi-stage damping linkage control method and system for refrigeration device |
| US11904648B2 (en) | 2020-07-17 | 2024-02-20 | Polaris Industries Inc. | Adjustable suspensions and vehicle operation for off-road recreational vehicles |
| CN112172436A (en) * | 2020-10-12 | 2021-01-05 | 中车株洲电力机车有限公司 | Air spring height adjusting system and method for medium-low speed maglev train |
| CN113898290B (en) * | 2021-10-09 | 2023-09-22 | 龙岩学院 | Ground source heat pump building construction device based on power system noise reduction control |
| CN113898290A (en) * | 2021-10-09 | 2022-01-07 | 龙岩学院 | Ground source heat pump building construction device based on control of making an uproar falls in driving system |
| CN116044949A (en) * | 2022-12-21 | 2023-05-02 | 珠海格力电器股份有限公司 | Adjusting device, adjusting method and equipment of adjusting device |
| CN116044949B (en) * | 2022-12-21 | 2024-08-06 | 珠海格力电器股份有限公司 | Adjusting device, adjusting method and equipment of adjusting device |
| CN116292740B (en) * | 2023-03-24 | 2023-09-05 | 大连地拓电子工程技术有限公司 | Quasi-zero rigidity three-degree-of-freedom active anti-micro-vibration platform |
| CN116292740A (en) * | 2023-03-24 | 2023-06-23 | 大连地拓电子工程技术有限公司 | Quasi-zero rigidity three-degree-of-freedom active anti-micro-vibration platform |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102678808A (en) | Shock absorbing system with combined rigidity and damping adjusting function and shock absorbing method | |
| US11926368B2 (en) | Cab suspension systems and associated methods of manufacture and use | |
| EP2236326B1 (en) | Active suspension and adaptive damping configuration | |
| CN104309438B (en) | A kind of multi-state vehicle suspension | |
| CN101968097B (en) | Magneto-rheological hydraulic rubber air spring | |
| CN105522906B (en) | The bypass flow path ON/OFF formula driving engine of gas chamber has been used to suspend equipment | |
| CN106763441A (en) | A kind of automatic adjustable automobile absorber of resistance | |
| CN205136453U (en) | Variably be used to dual circuit liquid of matter coefficient and be used to container | |
| CN103225668B (en) | Mutative damp electromagnetic vibration damping system is carried in a kind of sense | |
| CN102829121A (en) | Variable gas spring with magnetorheological fluid stiffness damper | |
| CN102582389A (en) | Vehicle suspension control method based on virtual damper | |
| CN109606055A (en) | A kind of airsuspension system and method and the vehicle for installing the system | |
| CN203627631U (en) | Semi-active parallel air spring | |
| CN202914611U (en) | Stiffness and damping united adjusting vibration-reducing device | |
| CN103775554B (en) | The stepless adjustable hydro-pneumatic spring of double bolloon formula rigidity | |
| CN203623320U (en) | Air suspension closed-loop control system with additional air chamber | |
| CN106134403B (en) | A kind of controllable damping hydro-pneumatic spring | |
| CN206344652U (en) | A kind of hydro-pneumatic suspension system of achievable active and half active switching control | |
| CN202046381U (en) | Vibration absorber for cab | |
| CN102107683A (en) | Vibration damping device for cab | |
| CN104385874B (en) | A kind of ultra-magnetic telescopic vehicle suspension vibration absorber of resonant frequency autotracking | |
| CN101975241B (en) | Mgnetorheological hydraulic rubber spring | |
| CN202628925U (en) | Gas compensation type double-barrel magneto-rheological damper | |
| CN104455140B (en) | Vehicle suspension vibration damper | |
| CN103921646A (en) | Adjustable suspension temperature compensation system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20120919 |