CN109505914A - Stiffness variable adaptive damping semi-active suspension - Google Patents
Stiffness variable adaptive damping semi-active suspension Download PDFInfo
- Publication number
- CN109505914A CN109505914A CN201811590284.9A CN201811590284A CN109505914A CN 109505914 A CN109505914 A CN 109505914A CN 201811590284 A CN201811590284 A CN 201811590284A CN 109505914 A CN109505914 A CN 109505914A
- Authority
- CN
- China
- Prior art keywords
- damping
- value
- damper
- main
- acceleration
- 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.)
- Granted
Links
- 238000013016 damping Methods 0.000 title claims abstract description 77
- 239000000725 suspension Substances 0.000 title claims abstract description 31
- 230000003044 adaptive effect Effects 0.000 title claims abstract description 13
- 230000001133 acceleration Effects 0.000 claims abstract description 39
- 238000000034 method Methods 0.000 claims description 8
- 239000000203 mixture Substances 0.000 claims 1
- 230000000694 effects Effects 0.000 abstract description 5
- 238000005265 energy consumption Methods 0.000 description 2
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 238000011217 control strategy Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 229910001873 dinitrogen Inorganic materials 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
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
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/005—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper
- F16F13/007—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper the damper being a fluid damper
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
- B60G17/018—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the use of a specific signal treatment or control method
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/06—Characteristics of dampers, e.g. mechanical dampers
- B60G17/08—Characteristics of fluid dampers
-
- 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
- F16F9/32—Details
- F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
- F16F9/535—Magnetorheological [MR] fluid dampers
-
- 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
- F16F2224/00—Materials; Material properties
- F16F2224/04—Fluids
- F16F2224/045—Fluids magnetorheological
-
- 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
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
- F16F2228/066—Variable stiffness
-
- 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
- F16F2230/18—Control arrangements
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
A kind of stiffness variable adaptive damping semi-active suspension provided by the invention, including main MR damper, secondary MR damper, main spring and auxiliary spring；The main MR damper and main spring are in parallel, the pair MR damper and auxiliary spring are in parallel, the main MR damper and secondary MR damper are coaxially connected, the main spring and auxiliary spring are coaxially connected, pass through above structure, it can accurately be adjusted according to rigidity and damping force of the acceleration signal in vertical direction to semi-active suspension, to play good damping effect for automobile, effectively promote the comfort that vehicle is driven.
Description
Technical field
The present invention relates to a kind of automobile component more particularly to a kind of stiffness variable adaptive damping semi-active suspensions.
Background technique
With the development of economy, requirement of the people to vehicle riding comfort is higher and higher, and the passive suspension of tradition is comfortable
Property the potentiality very little that is promoted, though Active suspension has preferable comprehensive performance, cost and price are high, and energy consumption is high.Half actively
Suspension is since structure is simple, energy consumption is small, performance is but substantially favored better than passive suspension.
MR damper be with provide movement resistance, the device of depletion kinergety, when in coil electric current increase,
Magnetic field will enhance in throttle orifice, and the resistance that magnetic current and liquid flow crosses throttle orifice increases with it, so that the damping force of damper output
Increase, conversely, electric current reduces, damping force also reduces.Therefore by the adjusting to input current, i.e., controllable damper damping force
Size.
Most of research about semi-active suspension all concentrates on the control strategy to semi-active suspension mostly, at present also
There is no the research of stiffness variable and the semi-active suspension of adaptive damping structure.
Therefore, in order to solve the above-mentioned technical problem, need to propose a kind of stiffness variable adaptive damping semi-active suspension.
Summary of the invention
In view of this, the object of the present invention is to provide a kind of stiffness variable adaptive damping semi-active suspension, can according to
The acceleration signal of vertical direction accurately adjusts the rigidity and damping force of semi-active suspension, to play well for automobile
Damping effect, effectively promoted vehicle drive comfort.
A kind of stiffness variable adaptive damping semi-active suspension provided by the invention, including main MR damper, secondary magnetic current
Variable damping device, main spring and auxiliary spring；
The main MR damper and main spring are in parallel, and the pair MR damper and auxiliary spring are in parallel, the master
MR damper and secondary MR damper are coaxially connected, and the main spring and auxiliary spring are coaxially connected.
Further, the damping and rigidity of the suspension are controlled according to lower method:
Establish the equivalent damping and equivalent stiffness model of the suspension, wherein equivalent damping model are as follows:
Equivalent stiffness model are as follows:
Wherein, k1For the rigidity value of main spring, k2For the rigidity value of auxiliary spring, c1For the damping value of main MR damper,
c2The damping value of secondary MR damper, ω are the intrinsic frequency of the suspension；
Obtain the expectation rigidity value a and desired damping value b of vehicle, and by desired rigidity value a and desired damping value b generation respectively
Enter into equivalent stiffness model and equivalent damping model and simultaneous forms the damping value c that equation group finds out main MR damper1
With the damping value c of secondary MR damper2；
According to damping value c1With damping value c2Search damping value-current relationship table of comparisons, determine main MR damper and
The driving current value of secondary MR damper, according to the driving current value of acquisition to main MR damper and secondary magnetorheological damping
Device provides operating current.
Further, the expectation rigidity value a and desired damping value b of vehicle are obtained according to the following method:
Acquire the acceleration signal of the vertical direction of vehicle；
Calculate the acceleration of vehicle vertical direction and the difference and rate of acceleration change of acceleration desired value；
The difference of acceleration and acceleration desired value is input in PLC controller, ratio tune is obtained using fuzzy algorithmic approach
Save coefficient, differential adjustment factor and integral adjustment coefficient；
Establish the computation model of expectation rigidity value a:
Wherein: a=Kd1·ε+KP1·ε+Ki1ε, Kd1、KP1And Ki1The respectively difference of acceleration and acceleration desired value
It is input to the differential adjustment factor, proportional control factor and integral adjustment coefficient obtained in PLC controller by fuzzy algorithmic approach, ε
For the difference of acceleration and acceleration desired value；
Rate of acceleration change signal is input in PLC controller, proportional control factor K is obtained using fuzzy algorithmic approachP2, product
Divide adjustment factor Ki2With differential adjustment factor Kd2, establish the computation model of expectation damping value b:
B=Kd2·δ+KP2·δ+Ki2δ, wherein δ is rate of acceleration change.
Further, the main MR damper is identical with the secondary structure of MR damper.
Beneficial effects of the present invention: by means of the invention it is possible to half-and-half actively outstanding according to the acceleration signal in vertical direction
The rigidity and damping force of frame are accurately adjusted, to play good damping effect for automobile, effectively promote what vehicle was driven
Comfort.
Detailed description of the invention
The invention will be further described with reference to the accompanying drawings and examples:
Fig. 1 is the structural diagram of the present invention.
Fig. 2 is control flow chart of the invention.
Specific embodiment
Further description is made to the present invention below in conjunction with Figure of description:
A kind of stiffness variable adaptive damping semi-active suspension provided by the invention, including main MR damper, secondary magnetic current
Variable damping device, main spring 8 and auxiliary spring 10；
The main MR damper and main spring are in parallel, and the pair MR damper and auxiliary spring are in parallel, the master
MR damper and secondary MR damper are coaxially connected, and the main spring and auxiliary spring are coaxially connected, by above structure,
It can accurately be adjusted according to rigidity and damping force of the acceleration signal in vertical direction to semi-active suspension, to be vapour
Vehicle plays good damping effect, effectively promotes the comfort that vehicle is driven.
Specifically: so the main MR damper is identical with the secondary structure of MR damper；Main magnetorheological damping
It coaxially connects between device and the connecting rod of secondary MR damper, two MR dampers include connecting rod (6,9), cylinder body, nitrogen
Gas reducing transformer 1, line valve 2, magnetorheological fluid 3, coil lead 4 and restriction 5, main MR damper and secondary MR damper
Connecting rod is fixedly connected by support plate 7.
In the present embodiment, the damping and rigidity of the suspension are controlled according to lower method:
Establish the equivalent damping and equivalent stiffness model of the suspension, wherein equivalent damping model are as follows:
Equivalent stiffness model are as follows:
Wherein, k1For the rigidity value of main spring, k2For the rigidity value of auxiliary spring, c1For the damping value of main MR damper, c2It is secondary
The damping value of MR damper, ω are the intrinsic frequency of the suspension；
Obtain the expectation rigidity value a and desired damping value b of vehicle, and by desired rigidity value a and desired damping value b generation respectively
Enter into equivalent stiffness model and equivalent damping model and simultaneous forms the damping value c that equation group finds out main MR damper1
With the damping value c of secondary MR damper2；
According to damping value c1With damping value c2Search damping value-current relationship table of comparisons, determine main MR damper and
The driving current value of secondary MR damper, according to the driving current value of acquisition to main MR damper and secondary magnetorheological damping
Device provides operating current.
Specifically, the expectation rigidity value a and desired damping value b of vehicle are obtained according to the following method:
Acquire the acceleration signal of the vertical direction of vehicle；
Calculate the acceleration of vehicle vertical direction and the difference and rate of acceleration change of acceleration desired value；Wherein, accelerate
Spending the general value of desired value is 0, still, according to actual road conditions environment, can be configured to desired value, when setting, is more connect
Nearly 0 is better；
The difference of acceleration and acceleration desired value is input in PLC controller, ratio tune is obtained using fuzzy algorithmic approach
Save coefficient, differential adjustment factor and integral adjustment coefficient；
Establish the computation model of expectation rigidity value a:
Wherein: a=Kd1·ε+KP1·ε+Ki1ε, Kd1、KP1And Ki1The respectively difference of acceleration and acceleration desired value
It is input to the differential adjustment factor, proportional control factor and integral adjustment coefficient obtained in PLC controller by fuzzy algorithmic approach, ε
For the difference of acceleration and acceleration desired value；
Rate of acceleration change signal is input in PLC controller, proportional control factor K is obtained using fuzzy algorithmic approachP2, product
Divide adjustment factor Ki2With differential adjustment factor Kd2, establish the computation model of expectation damping value b:
B=Kd2·δ+KP2·δ+Ki2δ, wherein δ is rate of acceleration change；Wherein, fuzzy PID algorithm is existing skill
Art, not in this to go forth, by the above method, can accurately determine the required work electricity of major and minor MR damper
Stream, so as to play good damping effect for automobile, effectively promote the comfort that vehicle is driven.
Finally, it is stated that the above examples are only used to illustrate the technical scheme of the present invention and are not limiting, although referring to compared with
Good embodiment describes the invention in detail, those skilled in the art should understand that, it can be to skill of the invention
Art scheme is modified or replaced equivalently, and without departing from the objective and range of technical solution of the present invention, should all be covered at this
In the scope of the claims of invention.
Claims (4)
1. a kind of stiffness variable adaptive damping semi-active suspension, it is characterised in that: including main MR damper, secondary magnetic current variable resistance
Buddhist nun's device, main spring and auxiliary spring；
The main MR damper and main spring are in parallel, and the pair MR damper and auxiliary spring are in parallel, the main magnetic current
Variable damping device and secondary MR damper are coaxially connected, and the main spring and auxiliary spring are coaxially connected.
2. stiffness variable adaptive damping semi-active suspension according to claim 1, it is characterised in that: control institute according to lower method
State the damping and rigidity of suspension:
Establish the equivalent damping and equivalent stiffness model of the suspension, wherein equivalent damping model are as follows:
Equivalent stiffness model are as follows:
Wherein, k1For the rigidity value of main spring, k2For the rigidity value of auxiliary spring, c1For the damping value of main MR damper, c2It is secondary
The damping value of MR damper, ω are the intrinsic frequency of the suspension；
The expectation rigidity value a and desired damping value b of vehicle are obtained, and desired rigidity value a and desired damping value b are updated to respectively
In equivalent stiffness model and equivalent damping model and simultaneous composition equation group finds out the damping value c of main MR damper1And pair
The damping value c of MR damper2；
According to damping value c1With damping value c2Damping value-current relationship table of comparisons is searched, determines main MR damper and secondary magnetic
The driving current value of rheological damper is mentioned according to the driving current value of acquisition to main MR damper and secondary MR damper
For operating current.
3. stiffness variable adaptive damping semi-active suspension according to claim 2, it is characterised in that: obtain according to the following method
The expectation rigidity value a of vehicle and desired damping value b:
Acquire the acceleration signal of the vertical direction of vehicle；
Calculate the acceleration of vehicle vertical direction and the difference and rate of acceleration change of acceleration desired value；
The difference of acceleration and acceleration desired value is input in PLC controller, proportion adjustment system is obtained using fuzzy algorithmic approach
Number, differential adjustment factor and integral adjustment coefficient；
Establish the computation model of expectation rigidity value a:
Wherein: a=Kd1·ε+KP1·ε+Ki1ε, Kd1、KP1And Ki1Respectively the difference of acceleration and acceleration desired value inputs
Differential adjustment factor, proportional control factor and the integral adjustment coefficient obtained into PLC controller by fuzzy algorithmic approach, ε are to add
The difference of velocity and acceleration desired value；
Rate of acceleration change signal is input in PLC controller, proportional control factor K is obtained using fuzzy algorithmic approachP2, integral adjust
Save COEFFICIENT Ki2With differential adjustment factor Kd2, establish the computation model of expectation damping value b:
B=Kd2·δ+KP2·δ+Ki2δ, wherein δ is rate of acceleration change.
4. stiffness variable adaptive damping semi-active suspension according to claim 1, it is characterised in that: the main magnetorheological damping
Device is identical with the secondary structure of MR damper.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811590284.9A CN109505914B (en) | 2018-12-25 | 2018-12-25 | Variable-rigidity variable-damping semi-active suspension |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811590284.9A CN109505914B (en) | 2018-12-25 | 2018-12-25 | Variable-rigidity variable-damping semi-active suspension |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109505914A true CN109505914A (en) | 2019-03-22 |
| CN109505914B CN109505914B (en) | 2020-11-03 |
Family
ID=65754530
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811590284.9A Active CN109505914B (en) | 2018-12-25 | 2018-12-25 | Variable-rigidity variable-damping semi-active suspension |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109505914B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110939678A (en) * | 2019-12-07 | 2020-03-31 | 佛山市鼎科科技发展有限公司 | Intelligent air damper for front suspension of automobile |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20020185347A1 (en) * | 1997-04-26 | 2002-12-12 | Andreas Pohl | Spring/mass vibratory force coupler |
| DE10236514A1 (en) * | 2002-08-30 | 2004-03-18 | Bundesrepublik Deutschland, vertreten durch das Bundesministerium der Verteidigung, dieses vertreten durch das Bundesamt für Wehrtechnik und Beschaffung | Large displacement spring damper system for mine explosion protection of shipboard antennas has shock sensor and amplifier controlled magnetorheological damping with end stop |
| CN103241095A (en) * | 2013-05-31 | 2013-08-14 | 山东理工大学 | Control algorithm of automotive magneto-rheological semi-active suspension system and real-time optimal current |
| CN105172511A (en) * | 2015-07-15 | 2015-12-23 | 西南交通大学 | Automobile suspension shock absorber control system and method |
| CN105584310A (en) * | 2016-01-07 | 2016-05-18 | 江苏大学 | Variable-rigidity semi-active suspension |
| CN106246796A (en) * | 2016-08-10 | 2016-12-21 | 安徽工程大学 | A kind of automotive suspension self-supplied magnetic current damper device |
-
2018
- 2018-12-25 CN CN201811590284.9A patent/CN109505914B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20020185347A1 (en) * | 1997-04-26 | 2002-12-12 | Andreas Pohl | Spring/mass vibratory force coupler |
| DE10236514A1 (en) * | 2002-08-30 | 2004-03-18 | Bundesrepublik Deutschland, vertreten durch das Bundesministerium der Verteidigung, dieses vertreten durch das Bundesamt für Wehrtechnik und Beschaffung | Large displacement spring damper system for mine explosion protection of shipboard antennas has shock sensor and amplifier controlled magnetorheological damping with end stop |
| CN103241095A (en) * | 2013-05-31 | 2013-08-14 | 山东理工大学 | Control algorithm of automotive magneto-rheological semi-active suspension system and real-time optimal current |
| CN105172511A (en) * | 2015-07-15 | 2015-12-23 | 西南交通大学 | Automobile suspension shock absorber control system and method |
| CN105584310A (en) * | 2016-01-07 | 2016-05-18 | 江苏大学 | Variable-rigidity semi-active suspension |
| CN106246796A (en) * | 2016-08-10 | 2016-12-21 | 安徽工程大学 | A kind of automotive suspension self-supplied magnetic current damper device |
Non-Patent Citations (3)
| Title |
|---|
| 张庆庆: "基于MR阻尼器可变刚度和阻尼半主动悬架控制研究", 《江苏大学硕士学位论文》 * |
| 范方强等: "变刚度和阻尼半主动悬架的模糊控制研究", 《重庆交通大学学报》 * |
| 郭耀辉: "磁流变阻尼器等效阻尼建模及其控制系统研究", 《合肥工业大学硕士学位论文》 * |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110939678A (en) * | 2019-12-07 | 2020-03-31 | 佛山市鼎科科技发展有限公司 | Intelligent air damper for front suspension of automobile |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109505914B (en) | 2020-11-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| WO2020224231A1 (en) | Semi-active coordination control method for vibration reduction and power generation of magnetorheological energy-regenerative suspension | |
| CN106515348B (en) | Intelligent acceleration damping semi-active control method for vehicle suspension system | |
| CN107825930B (en) | A kind of intelligent fuzzy mixing canopy semi-active control method for vehicle suspension system | |
| US6721641B1 (en) | Electromagnetic damper for vehicle suspension | |
| CN102678808A (en) | Shock absorbing system with combined rigidity and damping adjusting function and shock absorbing method | |
| CN109334378B (en) | Vehicle ISD suspension active control method based on single neuron PID control | |
| Avesh et al. | Modeling simulation and control of active suspension system in Matlab Simulink environment | |
| CN109532510B (en) | Maglev train vibration control device and method and maglev train | |
| CN109505914A (en) | Stiffness variable adaptive damping semi-active suspension | |
| CN110341413B (en) | Method and system for controlling limited time of vehicle body height of electric control air suspension system | |
| CN105946496A (en) | Suspension control system based on skyhook control algorithm | |
| CN104648073A (en) | Electromagnetic variable suspension and regulating method thereof | |
| CN206344652U (en) | A kind of hydro-pneumatic suspension system of achievable active and half active switching control | |
| CN109515104A (en) | A kind of wheel hub driving electric car airsuspension system with multilayer auxiliary chamber | |
| CN116080326A (en) | Semi-active suspension control method and system | |
| CN103419591B (en) | High-pressure air source self-stabilization device of air suspension vehicle body height adjustment system | |
| CN106678253A (en) | Damper provided with matrix series capillary tubes and variable system natural frequency | |
| Tang et al. | Sliding Mode Control of Vehicle Semi-active Suspension System Based on Magnetorheological Damper | |
| CN202418392U (en) | Air spring with static rigidity adjustment based on liquid charging and dynamic rigidity adjustment based on floating throttle plate | |
| CN102401074A (en) | Air spring for adjusting dynamic stiffness along with displacement of air bag | |
| CN111273543A (en) | PID optimization control method based on strategy iteration | |
| CN117021870A (en) | Dynamic inertia suspension control method based on power flow | |
| Zhang et al. | Double closed—Loop control of high—Regulation of electronically controlled air suspension | |
| CN111923679B (en) | Stability switching theory-based PID time-lag switching compensation control method for vehicle ISD semi-active suspension | |
| CN109130758A (en) | A kind of suspension system dual feed can control system and method |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20240122 Address after: 230000 floor 1, building 2, phase I, e-commerce Park, Jinggang Road, Shushan Economic Development Zone, Hefei City, Anhui Province Patentee after: Dragon totem Technology (Hefei) Co.,Ltd. Country or region after: China Address before: 402247 No. 1 Fuxing Road, Shuang Fu New District, Jiangjin District, Chongqing. Patentee before: CHONGQING JIAOTONG University Country or region before: China |