CN114017467A - A Magneto-Rheological Damper with Negative Stiffness - Google Patents
A Magneto-Rheological Damper with Negative Stiffness Download PDFInfo
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- CN114017467A CN114017467A CN202111366034.9A CN202111366034A CN114017467A CN 114017467 A CN114017467 A CN 114017467A CN 202111366034 A CN202111366034 A CN 202111366034A CN 114017467 A CN114017467 A CN 114017467A
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- 238000013016 damping Methods 0.000 claims abstract description 35
- 230000000694 effects Effects 0.000 claims abstract description 18
- 230000005284 excitation Effects 0.000 claims abstract description 14
- 238000009434 installation Methods 0.000 claims abstract description 7
- 230000033001 locomotion Effects 0.000 claims abstract description 7
- 238000007667 floating Methods 0.000 claims abstract description 5
- 230000009467 reduction Effects 0.000 claims abstract description 4
- 239000012530 fluid Substances 0.000 claims description 14
- 230000009471 action Effects 0.000 claims description 7
- 238000006073 displacement reaction Methods 0.000 claims description 4
- 239000007788 liquid Substances 0.000 claims description 3
- 230000009286 beneficial effect Effects 0.000 claims description 2
- 239000000725 suspension Substances 0.000 description 14
- 238000000034 method Methods 0.000 description 9
- 230000001133 acceleration Effects 0.000 description 3
- 238000011161 development Methods 0.000 description 3
- 238000005265 energy consumption Methods 0.000 description 3
- 230000007547 defect Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000003137 locomotive effect Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000001228 spectrum Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
- F16F15/027—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means comprising control arrangements
- F16F15/0275—Control of stiffness
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
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- General Engineering & Computer Science (AREA)
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- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Abstract
本发明公开了一种具有负刚度特性的磁流变阻尼器，包括磁流变阻尼单元和负刚度生成组件；磁流变阻尼单元包括外部的阻尼器缸体、内部的蓄能器、浮动活塞、活塞头、励磁线圈、中心轴、活塞杆端盖以及活塞杆等；负刚度生成组件由一对环形永磁铁组成；其中内环形永磁铁固定于中心轴上，外环形永磁铁固定在活塞杆内壁上；两个永磁铁之间可发生相对运动。本发明将负刚度特性引入磁流变阻尼器中，可实现接近主动控制的减振效果，同时规避了主动控制稳定性差、功耗大、成本高的缺点。以及将负刚度组件安装在活塞杆内部，大幅减小了新型阻尼器的尺寸，可以满足高速列车上二系横向阻尼器紧凑空间的安装要求。
The invention discloses a magnetorheological damper with negative stiffness characteristics, comprising a magnetorheological damping unit and a negative stiffness generating component; the magnetorheological damping unit includes an external damper cylinder, an internal accumulator, and a floating piston , piston head, excitation coil, central shaft, piston rod end cap and piston rod, etc.; the negative stiffness generating component is composed of a pair of annular permanent magnets; the inner annular permanent magnet is fixed on the central shaft, and the outer annular permanent magnet is fixed on the piston rod. On the inner wall; relative motion can occur between the two permanent magnets. The invention introduces the negative stiffness characteristic into the magnetorheological damper, which can realize the vibration reduction effect close to the active control, and simultaneously avoid the disadvantages of poor stability, high power consumption and high cost of the active control. And the negative stiffness component is installed inside the piston rod, which greatly reduces the size of the new damper, which can meet the installation requirements of the second-series transverse damper on high-speed trains in the compact space.
Description
Technical Field
The invention belongs to the field of vibration control, particularly relates to the technical field of high-speed rail suspensions, and particularly relates to a magnetorheological damper with negative stiffness characteristic.
Background
The rapid development of Chinese high-speed rail highlights the advantages of high transportation efficiency, safety, environmental protection and low unit transportation cost. At present, the highest speed per hour of the China railway is increased to 350km/h, which marks that the development of the China high-speed railway takes a new step. The high-speed rail acceleration is an effective way for further improving the railway passenger and freight transportation capacity and reducing the transportation cost of enterprises. However, the running speed of the train is increasing, and simultaneously, higher requirements are also put on the stability and safety of the high-speed running of the train. The results of the actual measurement of the Japan new mainline show that when the speed of the train is increased from 160km/h to 270km/h, the power spectrum density of the acceleration of the train body as the vibration strength judging condition is increased by 7 times. Therefore, the improvement of the train running speed brings great challenges to the safety and comfort of train running. The most fundamental method for solving the problem is to develop an effective novel transverse vibration control method while accelerating the speed of the high-speed rail, so that the transportation efficiency and the high-speed stability of the high-speed rail are ensured at the same time.
At present, the method for improving the dynamic performance of the suspension system of the train is an effective damping method. As one of the most important parts in a train suspension structure, various parameters of a secondary transverse damper directly affect the stability and riding comfort of a train, and play an important role in suppressing the transmission of vibration between a train body and a bogie and improving the motion stability of the bogie and the train body. Currently, active control and semi-active control are two typical methods which are superior to passive control and can be used for improving the damping performance of the high-speed rail secondary transverse damper.
The active control has better effect in the aspect of vibration reduction. However, the active control depends on a complex control algorithm and has the disadvantages of poor stability, large power consumption, high cost and the like, which greatly limits the wide application of the active control. Semi-active control has received much attention in recent years due to its advantages of good performance, low power consumption, low hardware cost, etc. Currently, it has become a mainstream way to realize semi-active control by filling a smart fluid in a damper. The damper is filled with the intelligent fluid, and no redundant movable part is needed to be installed, so that the damper based on the magnetorheological fluid has the advantages of simple overall structure, stability and reliability. In addition, the magnetorheological fluid can be converted from a free flow state to a semi-solid state only by exciting a magnetic field by a low voltage source, which means that the semi-active control of the magnetorheological fluid material is safer and more practical. In the aspect of railway locomotives, a great deal of work focuses on the application of a semi-active control technology based on a magnetorheological damping device in the aspect of railway vehicles, such as patents named as 'a transverse semi-active suspension fault-tolerant control system and method of a high-speed train' and 'a transverse vibration control method of the high-speed train based on a magnetorheological damping model'. Although the vibration damping performance of the proposed semi-active suspension is greatly improved compared with a passive system, the vibration control effect is only effective near a resonance region, and when the excitation frequency is higher than the resonance frequency, the vibration control effect is not obviously improved compared with the passive suspension.
Disclosure of Invention
The invention solves the problems: the negative stiffness component is combined with the magneto-rheological damping unit, the negative stiffness force generated by the negative stiffness component can play a role of an active force in an active system, the semi-active vibration reduction effect is improved on the premise of not introducing the active unit, and the stability and the safety of a high-speed train in the speed-up process are improved.
The invention is realized by the following technical scheme: a magnetorheological damper having negative stiffness characteristics, comprising: the magneto-rheological damping unit and the negative stiffness generating assembly are adopted, the magneto-rheological controllable unit can provide controllable damping force and simultaneously acts together with the negative stiffness force, and the vibration damping performance of the magneto-rheological damper is further improved;
the magneto-rheological damping unit comprises: the damper comprises a piston rod (1), a damper cylinder body (4), a central shaft (5), a piston head (6), a magnet exciting coil (7), a piston rod end cover (8), a floating piston (9), an internal energy accumulator (10) and a bottom plate (11); the negative rigidity generating assembly consists of an inner annular permanent magnet (2) and an outer annular permanent magnet (3);
the piston rod (1) is inserted into the damper cylinder body (4), the magnet exciting coil (7) is wound at the groove of the piston head (6), and magnetorheological fluid is filled in the damper cylinder body (4); one end of the central shaft (5) is fixedly connected with the bottom plate (11), the other end of the central shaft is inserted into the piston rod (1), and under the action of external excitation, the central shaft (5) moves relative to the piston rod (1) along with the damper cylinder body (4); the inner annular permanent magnet (2) and the outer annular permanent magnet (3) are arranged inside the piston rod (1), the inner annular permanent magnet (2) is fixed on the central shaft (5), and the outer annular permanent magnet (3) is fixed on the inner wall of the piston rod (1); the axial installation positions of the inner annular permanent magnet (2) and the outer annular permanent magnet (3) are on the same plane, and the centers of the inner annular permanent magnet and the outer annular permanent magnet are superposed;
the piston rod end cover (8) is connected with the piston rod (1), the piston head (6) is also fixed on the piston rod (1), the internal energy accumulator (10) is a spiral spring, precompression is carried out during installation, and the liquid pressure of magnetorheological fluid in the damper cylinder body (4) is increased;
under the action of external excitation, when the piston rod (1) is subjected to pulling force, the piston rod (1) moves towards one end relative to the damper cylinder body (4), the outer annular permanent magnet (3) on the inner wall of the piston rod (1) also moves towards the relative displacement of the one end relative to the inner annular permanent magnet (2), at the moment, the inner annular permanent magnet (2) has a relative acting force towards the one end towards the outer annular permanent magnet (3), the direction of the relative acting force is the same as the direction of the relative movement, and the negative stiffness generating assembly generates an active force effect; when the piston rod (1) is stressed, the negative stiffness generating assembly also generates a main force effect which is beneficial to the movement of the piston rod (1).
The piston rod (1) is hollow inside so as to install the central shaft (5), the inner annular permanent magnet (2) and the outer annular permanent magnet (3).
The inner annular permanent magnet (2) and the outer annular permanent magnet (3) are different in diameter and same in height, wherein the diameter of the outer annular permanent magnet (3) is larger than that of the inner annular permanent magnet (2).
The invention has the advantages and positive effects that:
(1) the invention provides a theory basis of expressing negative stiffness characteristics by active control, introduces the negative stiffness characteristics into a novel magnetorheological damper, is applied to a secondary transverse damper used on a high-speed rail, avoids the defects of low stability, high cost and high energy consumption of active control, and further improves the vibration control effect of a semi-active suspension system in a full frequency range.
(2) The piston rod is hollow inside and is used for mounting the central shaft and the inner and outer annular permanent magnet pairs, the structure is compact, the design is novel, and the actual situation that the mounting space of the secondary transverse damper of the train is narrow is fully considered. One end of the central shaft is fixed with the damper cylinder body through the bottom plate, the other end of the central shaft is inserted into the piston rod in a penetrating mode, and under the external excitation effect, the central shaft can move relative to the piston rod along with the damper cylinder body. The inner ring-shaped permanent magnet and the outer ring-shaped permanent magnet have different diameters and the same height. Wherein, the outer annular permanent magnet with large diameter is arranged on the inner wall of the piston rod, and the inner annular permanent magnet with small diameter is fixed on the outer wall of the central shaft. The end faces of the two annular permanent magnets are in the same plane, the centers of the two annular permanent magnets are overlapped, and under the action of external excitation, the two annular permanent magnets can move relatively, the centers of the two annular permanent magnets deviate, so that mutual repulsive force, namely negative rigidity force is generated. Under external excitation, the negative stiffness force generated between the two annular permanent magnets can play the role of active control force. The invention can reach the active control effect and avoid the defects of low stability, high cost and high energy consumption of the active control.
(3) The negative stiffness force based on the annular magnet pair is effective in the full frequency range, and the limitation that the current semi-active control is only effective near the resonant frequency can be effectively overcome.
(4) According to the invention, the negative stiffness component is arranged in the piston rod, so that the outer diameter of the secondary transverse damper is greatly reduced, and the problem of limited installation space of a high-speed train is solved.
(5) The method can meet the increasingly severe requirements of vibration and stability control of the high-speed train, ensures the running safety of the high-speed train, ensures that the high-speed train technology in China is in the leading position in the world, promotes the further development and internationalization of the high-speed train, and has important scientific significance and practical value.
(6) Through adding the magneto rheological damper who has the burden rigidity characteristic in suspension system, compare passive suspension can be better promotion damping effect, overcome the limitation that traditional semi-active suspension only has damping effect near resonant frequency simultaneously, promote the damping effect of semi-active system to initiative damping level to solve the problem of the transverse vibration aggravation that high speed train produced because the speed-raising, improve stability and the security of high speed train after the speed-raising.
Drawings
FIG. 1 is a schematic view of the overall structure of a magnetorheological damper with negative stiffness characteristics according to the present invention;
FIG. 2 is a schematic view of the mounting position of the magnetorheological damper with negative stiffness characteristic on the high-speed rail suspension according to the invention;
wherein, 1 is a piston rod, 2 is an inner annular permanent magnet, 3 is an outer annular permanent magnet, 4 is a damper cylinder, 5 is a central shaft, 6 is a piston head, 7 is an excitation coil, 8 is a piston rod end cover, 9 is a floating piston, 10 is an energy accumulator, and 11 is a bottom plate.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly described below with reference to the drawings of the embodiments, and it is obvious that the described embodiments are some embodiments of the present invention, but not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
As shown in FIG. 1, the magneto-rheological damper with negative stiffness characteristic of the invention is composed of a magneto-rheological damping unit and a negative stiffness generating assembly; the magnetorheological damping unit comprises a piston rod 1, a damper cylinder 4, a central shaft 5, a piston head 6, an excitation coil 7, a piston rod end cover 8, a floating piston 9, an internal energy accumulator 10 and a bottom plate 11; the negative rigidity generating assembly consists of an inner annular permanent magnet 2 and an outer annular permanent magnet 3;
the piston rod 1 is inserted into the damper cylinder body 4 in a penetrating mode, the magnet exciting coil 7 is wound on the groove of the piston head 6, and magnetorheological fluid is filled in the damper cylinder body 4; one end of the central shaft 5 is fixedly connected with the bottom plate 11, the other end is inserted into the piston rod 1, and the piston rod 1 can move relative to the central shaft 5. The piston rod end cover 8 is connected with the piston rod 1 through a screw, the piston head 6 is also fixed on the piston rod 1, the internal energy accumulator 10 is a spiral spring, and precompression is performed during installation to increase the liquid pressure of magnetorheological fluid in the damper cylinder body 4. The piston rod 1 is connected with the vehicle body as a moving part, and the bottom plate 11 is connected with the bogie frame.
The inner ring-shaped permanent magnet 2 is fixed on the central shaft 5, and the outer ring-shaped permanent magnet 3 is fixed on the inner wall of the piston rod 1; the two permanent magnets have different diameters and the same height, the end faces of the inner annular permanent magnet 2 and the outer annular permanent magnet 3 are arranged on the same plane, the centers of the inner annular permanent magnet 2 and the outer annular permanent magnet 3 are overlapped, and under the action of external excitation, the inner annular permanent magnet 2 and the outer annular permanent magnet 3 can move relatively and deviate from the centers of the inner annular permanent magnet and the outer annular permanent magnet, so that mutual repulsive force, namely negative rigidity force, can be generated, and the effect of active control force can be achieved.
The controllable component is realized by the magneto-rheological damping unit, and the magneto-rheological damping unit can provide controllable damping force, so that the controllability of the suspension system is realized. The magnetorheological fluid shows a magnetorheological effect under the action of a magnetic field generated by the magnet exciting coil 7, when a large current is applied, the magnetorheological fluid shows large damping, and conversely, the magnetorheological fluid shows small damping, so that a controllable semi-active damping force is output.
The negative stiffness force and the semi-active controllable damping force act together, so that the overall vibration damping performance of the suspension system can be improved, and the following description specifically shows that: the mounting position of the magnetorheological damper with the negative rigidity characteristic on a high-speed rail suspension is shown in figure 2. One end of the damper is connected with the bogie, and the other end of the damper is connected with a high-speed rail vehicle body. When the high-speed rail runs at a high speed, the high-speed rail is influenced by transverse vibration from a track, a vibration signal is transmitted to the damper through the bogie, and the piston rod 1 and the central shaft 5 generate relative displacement under the action of vibration excitation, so that the outer annular permanent magnet 3 and the inner annular permanent magnet 2 which are respectively fixed on the piston rod 1 and the central shaft 5 generate relative displacement, and negative stiffness force is generated. The exciting coil 7 wound on the piston head 6 is energized to generate a magnetic field, thereby outputting a controllable semi-active damping force. The negative stiffness force and the semi-active controllable damping force act together, the negative stiffness force is effective in a full frequency range, the vibration damping effect of active control can be achieved, the problems of poor stability, large energy consumption and high cost in the active control are solved, and the semi-active damping force is controllable in a large range, so that the real-time controllability of the damper can be achieved. Meanwhile, signals such as vibration acceleration or vibration amplitude of the vehicle body are fed back to the controller through the sensor, and the controller outputs current control signals according to control rules and transmits the current control signals to the damper, so that real-time control of semi-active damping force is achieved. And the semi-active damping force can be adjusted and controlled in real time according to the instant response of the vehicle body, so that the vibration of the vehicle body is controlled.
The above examples are provided only for the purpose of describing the present invention, and are not intended to limit the scope of the present invention. The scope of the invention is defined by the appended claims. Various equivalent substitutions and modifications can be made without departing from the spirit and principles of the invention, and are intended to be within the scope of the invention.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111366034.9A CN114017467A (en) | 2021-11-18 | 2021-11-18 | A Magneto-Rheological Damper with Negative Stiffness |
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| CN202111366034.9A CN114017467A (en) | 2021-11-18 | 2021-11-18 | A Magneto-Rheological Damper with Negative Stiffness |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115392069A (en) * | 2022-07-28 | 2022-11-25 | 河南濮泽高速公路有限公司 | Damping control method for long-span continuous bridge |
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Application publication date: 20220208 |