CN108895111B - Shock absorber with variable damping and adjustable rigidity - Google Patents
Shock absorber with variable damping and adjustable rigidity Download PDFInfo
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- CN108895111B CN108895111B CN201811101299.4A CN201811101299A CN108895111B CN 108895111 B CN108895111 B CN 108895111B CN 201811101299 A CN201811101299 A CN 201811101299A CN 108895111 B CN108895111 B CN 108895111B
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- Prior art keywords
- damper
- spring
- end cover
- piston
- shock absorber
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Classifications
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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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
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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
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
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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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
- F16F9/3235—Constructional features of cylinders
- F16F9/3242—Constructional features of cylinders of cylinder ends, e.g. caps
Abstract
The invention discloses a shock absorber with variable damping and adjustable rigidity. The spring pressing end cover is positioned at the opening of the spring fixing barrel, and the size of the spring pressing end cover is matched with that of the opening of the spring fixing barrel; the diaphragm spring is arranged below the spring pressing end cover, and the damper outer cylinder is arranged inside the spring fixing cylinder; the damper upper end cover is positioned at the opening of the damper outer cylinder, and the size of the damper upper end cover is matched with that of the opening of the damper outer cylinder; the damper upper end cover is arranged below the diaphragm spring, through holes with the same size are formed in the centers of the spring pressing end cover, the diaphragm spring and the damper outer cylinder, the piston rod penetrates through the through holes of the damper upper end cover, the diaphragm spring and the damper outer cylinder, the piston rod is fixed to the bottom of the damper outer cylinder and penetrates through the piston, a plurality of inner grooves which penetrate through the damper upper end cover and the damper lower end cover are formed in the piston, the inner grooves are formed in the piston in the radial direction, the positioning pole. The invention can realize real-time adjustment of damping and rigidity.
Description
Technical Field
The invention relates to the technical field of shock absorbers, in particular to a shock absorber with variable damping and adjustable rigidity.
Background
Currently, there are three main modes of shock absorbers: passive control mode, active control mode, semi-active control mode. The vibration damper based on the passive control mode has the advantages of most extensive application, simple structure and low cost, but the natural frequency of the vibration damper is not adjustable, and when the natural frequency is the same as or has a small difference with the excitation frequency, a good vibration damping effect can be achieved; when the natural frequency of the damper is greatly different from the excitation frequency, the damping effect is poor and even the vibration is deteriorated. The vibration absorber based on the active control mode directly provides force to counteract the force generated by vibration by acquiring the information of a vibrating object in real time through a sensor, but has the advantages of quick response, external energy support and higher cost. The vibration absorber based on semi-active mode control collects vibration object information in real time through a sensor to change the natural frequency of the vibration absorber, so that a great deal of energy is not consumed, a good vibration absorbing effect can be achieved, and the application has certain limitation.
With the increasingly strict requirements of the shock absorber in many occasions, the shock absorbers in the three modes cannot meet the shock absorbing requirements in specific occasions. Theories and experiments show that: in practical engineering, a shock absorber capable of changing both the stiffness (increasing the vibration isolation frequency band range) and the damping (optimizing the vibration attenuation effect of the high-frequency part) is further required, that is, the shock absorber is required to be capable of changing both the stiffness characteristic and the damping characteristic. However, the above characteristics are not found in the prior art shock absorbers.
Disclosure of Invention
The invention aims to provide a shock absorber with variable damping and adjustable rigidity, so that the damping and the rigidity can be adjusted in real time.
in order to achieve the purpose, the invention provides the following scheme:
A variable damping, adjustable stiffness shock absorber, said shock absorber comprising: the device comprises a piston rod, a spring pressing end cover, a diaphragm spring, a spring fixing cylinder, a damper outer cylinder, a damper upper end cover, a piston, a fixed polar plate and giant electrorheological fluid;
The spring pressing end cover is positioned at the opening of the spring fixing barrel, and the size of the spring pressing end cover is matched with that of the opening of the spring fixing barrel; the diaphragm spring is arranged below the spring pressing end cover, the damper outer cylinder is arranged inside the spring fixing cylinder, the upper end cover of the damper is located at an opening of the damper outer cylinder, and the size of the upper end cover of the damper is matched with the size of the opening of the damper outer cylinder; the damper upper end cover is arranged below the diaphragm spring, through holes with the same size are formed in the centers of the spring pressing end cover, the diaphragm spring and the damper outer cylinder, the piston rod penetrates through the through holes in the centers of the spring pressing end cover, the diaphragm spring and the damper outer cylinder, the piston is fixed to the bottom of the damper outer cylinder, the piston rod penetrates through the piston, the piston rod is matched with the piston, a plurality of inner grooves which penetrate through the piston up and down are formed in the piston, the inner grooves are formed in the piston in the radial direction, the positioning polar plate is located in the inner grooves, and the giant electrorheological fluid is filled in the spring fixing cylinder.
Optionally, the shock absorber further comprises a sealing ring, and the sealing ring is located at the joint of the damper outer cylinder and the damper upper end cover.
Optionally, the shock absorber further comprises a linear bearing, a groove is formed at a joint of the upper end cover of the damper and the piston rod, and the linear bearing is located at the groove.
Optionally, the diaphragm spring is connected with the spring pressing end cover through a hexagon socket head cap bolt.
Optionally, the spring fixing cylinder is connected with the damper outer cylinder through an inner hexagonal bolt.
Optionally, the linear bearing is connected with the upper end cover of the damper through a hexagon socket head cap screw.
Optionally, the position where the diaphragm spring contacts the piston rod includes a hexagonal nut.
Optionally, the interval between the fixed pole plate and the groove wall of the inner groove is 2 mm.
According to the specific embodiment provided by the invention, the invention discloses the following technical effects: the invention provides a shock absorber with variable damping and adjustable rigidity, which has the advantages of compact structure, large relative area, good damping effect and capability of realizing damping adjustment by adopting a polar plate in a planar form; by adopting the diaphragm spring and utilizing the nonlinear stiffness characteristic of the diaphragm spring, the rigidity of the spring is adjusted by changing the size and the position of the inner processing hole groove of the diaphragm spring.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed to be used in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings without inventive exercise.
FIG. 1 is a schematic structural diagram of a variable damping, stiffness adjustable shock absorber in accordance with an embodiment of the present invention;
FIG. 2 is a top view of a variable damping, adjustable stiffness shock absorber;
FIG. 3 is a diaphragm spring and shaft assembly;
FIG. 4 is a diagram showing the relative position of the fixed pole plate and the piston;
Fig. 5 is an isometric view of the relative relationship of the stationary plate and the piston.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the 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.
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in further detail below.
An electrorheological fluid is a suspension liquid formed by dispersing small particles of high dielectric constant in a solvent of low dielectric constant. The suspension liquid can polarize solid particles at millisecond-level moment under the action of an external electric field to interact with each other to form a chain or columnar structure parallel to the electric field, so that the liquid is in a solid-like constitutive state with certain yield stress, and the apparent viscosity is increased by several orders of magnitude. This effect of causing the fluid to change state is called the electrorheological effect.
the current variable damper is an energy dissipation and vibration reduction control device with wide application, and can be used in the fields of machinery, buildings and the like. The control mechanism is that partial vibration energy of the structure is dissipated through damping materials by means of the electro-rheological effect in the damper, so that the aims of relieving the impact of external load, reducing the vibration of the structure and protecting the safety of the structure are fulfilled.
giant electrorheological fluid is a suspension formed by uniformly dispersing polarizable dielectric particles in base liquid of the giant electrorheological fluid, when an electric field is applied to the giant electrorheological fluid, the viscosity, the shearing strength and the like of the giant electrorheological fluid can be instantly changed, the viscosity, the strength and the like can be adjusted along with the electric field, the giant electrorheological fluid can be continuously adjusted in a large range and can reach several orders of magnitude, and low-viscosity fluid can be converted into high-viscosity fluid or even solid. When the external electric field is removed, the fluid state can be recovered within millisecond time, the property between liquid and solid can be instantly changed in a controllable, reversible and continuous manner, the controllable transmission of torque and the online stepless and reversible control of a mechanism can be realized through the electric field, the traditional electrode mechanical conversion component can be replaced, the electromechanical integrated self-adaptive control mechanism has wide application prospect in the industrial field, particularly has wider application foundation and application requirements in the fields of national defense construction, transportation tools, hydraulic equipment, mechanical manufacturing industry, sensor technology and the like, and is one of key materials urgently needed in the field of damping vibration reduction.
according to the research work of the professor Wenweijia of hong Kong university of science and technology, the yield strength of the novel giant electrorheological fluid developed at present can reach more than 130kPa under the electric field strength of 5KV/mm, and the engineering requirements can be completely met. However, the viscosity coefficient of the novel giant electrorheological fluid is only 1/10 of that of the common electrorheological fluid, and is only 0.1 pas, while the viscosity coefficient of the common electrorheological fluid is 1 pas. Therefore, under the same condition, the viscous damping force provided by the common electrorheological fluid is far greater than that provided by the novel giant electrorheological fluid.
During the service process of various building or mechanical structures, the safety and the service life of the structures are seriously influenced by vibration or impact load. The installation of a damping device capable of dissipating energy and damping vibration on the structure is an effective means for reducing the vibration or impact response and increasing the safety and stability of the structure. The traditional passive control damper (such as a hydraulic damper) can only provide non-adjustable damping force, and the vibration control effect is not ideal. The intelligent damper prepared by the electro/magnetic rheological body can continuously adjust the damping force in real time according to the working condition by adjusting the intensity of the electro/magnetic field, thereby realizing the active and semi-active control of the structural vibration or impact and better preventing the failure and the damage of the structure. Compared with a magneto-rheological damper, the magneto-rheological damper taking the giant electro-rheological body as a core material has the advantages of high stability, simple structure, large damping force adjusting range, quick response and the like.
The diaphragm spring has ideal nonlinear elastic characteristic, high rigidity, strong buffering and vibration absorbing capacity, capacity of bearing large load with small deformation and suitability for occasions with small requirement on axial space. Diaphragm springs have a variable stiffness characteristic, and such springs have a wide range of non-linear characteristics.
To a large extent, diaphragm springs are replacing cylindrical coil springs. Are commonly used in heavy machinery (e.g., presses), as strong cushioning and dampening springs, as compression springs for automobile and tractor clutches and safety valves, and as energy storage elements for automotive equipment. The diaphragm springs can be divided into three types according to different cross-sectional shapes, including common diaphragm springs (the cross-sectional shape of which is rectangular), diaphragm springs with radial grooves and diaphragm springs with trapezoidal cross-sections. The common diaphragm spring is divided into two types, namely a supported surface and an unsupported surface; the diaphragm spring with the radial grooves is characterized in that a plurality of uniformly distributed grooves are formed in the radial direction on the basis of a common diaphragm spring, and the grooves can be formed from an inner hole to an outer circle or from the outer circle to an inner control direction; the diaphragm spring with trapezoidal section can be divided into two types, i.e. the inner edge thickness is larger than the outer thickness and the inner edge thickness is smaller than the outer thickness.
Compared with a cylindrical spiral spring, the diaphragm spring has the following characteristics: firstly, the load deformation characteristic curve is in a nonlinear relation. And secondly, the diaphragm spring is in a sheet shape, so that an assembly is easy to form, and building block type assembly and replacement can be carried out, thereby bringing convenience to maintenance. And thirdly, the disc spring with the radial groove has zero rigidity. This feature can be used in applications where the spring force is required to remain substantially constant over a range of deformation.
FIG. 1 is a schematic structural diagram of a variable damping, stiffness adjustable shock absorber in accordance with an embodiment of the present invention. As shown in fig. 1, a variable damping, adjustable stiffness shock absorber comprising: the device comprises a piston rod 1, a spring pressing end cover 2, a diaphragm spring 3, a spring fixing cylinder 4, a damper outer cylinder 5, a linear bearing 8, a damper upper end cover 9, a piston 10, a fixed polar plate 11, an O-shaped sealing ring 12 and giant electrorheological fluid; wherein 6a, 6b and 6c are inner hexagon bolts, and 7a, 7b and 7c are hexagon nuts;
The spring pressing end cover 2 is positioned at the opening of the spring fixing barrel 4, and the size of the spring pressing end cover 2 is matched with that of the opening of the spring fixing barrel 4; the diaphragm spring 3 is arranged below the spring pressing end cover 2, the damper outer cylinder 5 is arranged inside the spring fixing cylinder 4, the damper upper end cover 9 is positioned at an opening of the damper outer cylinder 5, and the size of the damper upper end cover 9 is matched with that of the opening of the damper outer cylinder 5; the damper upper end cover 9 is arranged below the diaphragm spring 3, through holes with the same size are formed in the centers of the spring pressing end cover 2, the diaphragm spring 3 and the damper outer cylinder 5, the piston rod 1 penetrates through the through holes in the centers of the spring pressing end cover 2, the diaphragm spring 3 and the damper outer cylinder 5, the piston 10 is fixed to the bottom of the damper outer cylinder 5, the piston rod 1 penetrates through the piston 10, the piston rod 1 is matched with the piston 10, a plurality of inner grooves which penetrate through the piston 1 from top to bottom are formed in the piston 1, the inner grooves are formed in the piston in the radial direction, the fixed pole plate 11 is located in the inner grooves, and the giant electrorheological fluid is filled in the spring fixing cylinder 4.
the sealing ring is an O-shaped sealing ring 12, and the O-shaped sealing ring 12 is positioned at the joint of the damper outer cylinder 5 and the damper upper end cover 9. The damper upper end cover 9 and the piston rod 1 are connected through a groove, and the linear bearing 2 is located in the groove. The diaphragm spring 3 and the spring pressing end cover 2 are connected through an inner hexagon bolt. The spring fixing cylinder 4 is connected with the damper outer cylinder 5 through an inner hexagonal bolt. The linear bearing 8 is connected with the damper upper end cover 9 through an inner hexagon bolt. The position where the diaphragm spring 3 contacts the piston rod 1 comprises a hexagonal nut. The interval between the fixed polar plate 11 and the wall of the inner groove is 2 mm. The matching part of the piston rod 1 and the spring pressing end cover 2 is not circular, which is used for ensuring the radial position of the piston and ensuring the position and the clearance between an inner groove of the piston 10 and the fixed pole plate 11. The piston rod 1 may be connected to a load by means of a coupling or other mechanical part. Before the piston rod 1 is loaded, giant electrorheological fluid is injected through a liquid injection hole on the upper end cover 9 of the damper. The giant electrorheological fluid is filled in a cavity formed by compressing the damper outer cylinder 5 and the damper upper end cover 9. The positive power supply positive electrode is applied to the piston 10, and the negative power supply negative electrode is applied to the fixed electrode plate 11. Thus, an electric field is formed between the gap between the inner groove of the piston 10 and the fixed pole plate 11. When the piston rod 1 moves, the two polar plates move mutually, so that the giant electrorheological fluid damper can generate damping force.
The working principle of the vibration damping device is that vibration damping is realized according to the damping effect of giant electrorheological fluid and the nonlinear stiffness action of the diaphragm spring. The variable damping of the giant electrorheological fluid is realized by changing the external voltage, and the adjustable rigidity of the diaphragm spring is realized by changing the size and the position of an inner processing hole groove of the diaphragm spring. The piston rod 1 can be connected with a device needing vibration reduction through parts such as bolts and the like. Giant electrorheological fluid is arranged in the damper outer cylinder 5, and the piston rod 1 mainly moves up and down. Under the action of an external electric field, the rheological property of the liquid between the two polar plates is changed, the viscosity is increased, and the damping coefficient is increased. Thus, the giant electrorheological fluid can generate certain damping effect. The damping can be changed along with the change of the voltage, and semi-active control and active control can be realized. The rigidity of the diaphragm spring can be adjusted, and the load of the vibration damping device can be changed as required, so that the vibration damping effect is optimized.
FIG. 2 is a top view of a variable damping, adjustable stiffness shock absorber; FIG. 3 is a diaphragm spring and shaft assembly; FIG. 4 is a diagram showing the relative position of the fixed pole plate and the piston; fig. 5 is an isometric view of the relative relationship of the stationary plate and the piston.
the invention has the following advantages:
1. The polar plates adopt a plane form to form an electrode gap. When the size of the outer cylinder is determined, the positive and negative polar plates adopt a plurality of plane polar plate shapes, the structure is compact, the relative area is large, and the damping effect is good;
2. The giant electrorheological fluid is adopted as a novel material, the giant electrorheological fluid has quick response along with the change of voltage, the damping of the shock absorber device can change along with the change of the voltage, and the shock absorption effect is better than that of the common passive rubber;
3. The pitting treatment of the surfaces of the upper and lower polar plates increases the area of the damping channel in a limited space, obviously reduces the slippage between the giant electrorheological fluid and the surfaces of the polar plates, and has the advantages of simple structure, high response speed, light weight, small volume, large output and the like.
4. The diaphragm spring is adopted, and the nonlinear stiffness characteristic of the diaphragm spring is good for the vibration reduction of a small-displacement precision instrument. The adjustable rigidity of the diaphragm spring can be realized by changing the size and the position of an inner processing hole groove of the diaphragm spring.
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
the principles and embodiments of the present invention have been described herein using specific examples, which are provided only to help understand the method and the core concept of the present invention; meanwhile, for a person skilled in the art, according to the idea of the present invention, the specific embodiments and the application range may be changed. In view of the above, the present disclosure should not be construed as limiting the invention.
Claims (8)
1. A variable damping, adjustable stiffness shock absorber, said shock absorber comprising: the device comprises a piston rod, a spring pressing end cover, a diaphragm spring, a spring fixing cylinder, a damper outer cylinder, a damper upper end cover, a piston, a fixed polar plate and giant electrorheological fluid;
the spring pressing end cover is positioned at the opening of the spring fixing barrel, and the size of the spring pressing end cover is matched with that of the opening of the spring fixing barrel; the diaphragm spring is arranged below the spring pressing end cover, the damper outer cylinder is arranged inside the spring fixing cylinder, the upper end cover of the damper is located at an opening of the damper outer cylinder, and the size of the upper end cover of the damper is matched with the size of the opening of the damper outer cylinder; the damper upper end cover is arranged below the diaphragm spring, through holes with the same size are formed in the centers of the spring pressing end cover, the diaphragm spring and the damper outer barrel, the piston rod penetrates through the through holes in the centers of the spring pressing end cover, the diaphragm spring and the damper outer barrel, the fixed pole plate is fixed to the bottom of the damper outer barrel, the piston rod penetrates through the piston, the piston rod is matched with the piston, a plurality of inner grooves which penetrate through the piston up and down are formed in the piston, the inner grooves are formed in the piston in the radial direction, the fixed pole plate is located in the inner grooves, and the giant electrorheological fluid is filled in the spring fixing barrel.
2. The variable damping, adjustable stiffness shock absorber according to claim 1 further comprising a seal ring located at the junction of the damper outer tube and the damper upper end cap.
3. The variable damping, adjustable stiffness shock absorber according to claim 1 further comprising a linear bearing, wherein the damper upper end cap and piston rod interface is a groove, and wherein the linear bearing is located in the groove.
4. The variable damping, adjustable rate shock absorber according to claim 1 wherein said diaphragm spring is connected to said spring hold down end cap by a socket head cap.
5. The variable damping, adjustable rate shock absorber of claim 1 wherein said spring mount cylinder is connected to said damper outer cylinder by a socket head cap screw.
6. The variable damping, adjustable stiffness shock absorber according to claim 3 wherein the linear bearing is connected to the damper upper end cap by a socket head cap.
7. the variable damping, variable stiffness shock absorber according to claim 1 wherein the location where the diaphragm spring contacts the piston rod comprises a hex nut.
8. the variable damping, adjustable stiffness shock absorber according to claim 1 wherein the fixed plate is spaced 2mm from the walls of the inner tank.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811101299.4A CN108895111B (en) | 2018-09-20 | 2018-09-20 | Shock absorber with variable damping and adjustable rigidity |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201811101299.4A CN108895111B (en) | 2018-09-20 | 2018-09-20 | Shock absorber with variable damping and adjustable rigidity |
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| CN108895111A CN108895111A (en) | 2018-11-27 |
| CN108895111B true CN108895111B (en) | 2019-12-13 |
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| CN109752235B (en) * | 2019-03-27 | 2020-04-24 | 上海大学 | Giant electrorheological fluid extrusion force testing device |
| CN111779790B (en) * | 2020-07-24 | 2021-09-28 | 上海大学 | Vibration damper |
| CN112161017B (en) * | 2020-09-22 | 2022-08-16 | 汕头大学 | Quick response magneto-rheological damper |
| CN112901703B (en) * | 2021-01-29 | 2022-12-09 | 重庆大学 | Prevent subsiding formula multilayer spiral polar plate attenuator based on huge electrorheological fluids |
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| DE69309302T2 (en) * | 1992-10-15 | 1997-07-03 | Gomma C F Spa | VALVE FOR CONTROLLING ELECTRO-RHEOLOGICAL FLUIDS IN HYDROELASTIC BEARINGS |
| CN104214267B (en) * | 2014-08-22 | 2017-02-01 | 华中科技大学 | Combined type short-stroke buffer device |
| CN205315597U (en) * | 2015-07-24 | 2016-06-15 | 南京航空航天大学 | Diaphragm formula molecule spring vibration -isolation buffer |
| CN106763441B (en) * | 2016-12-14 | 2018-09-21 | 长安大学 | A kind of resistance adjustable automobile absorber automatically |
| CN108006147B (en) * | 2017-12-04 | 2019-11-12 | 上海大学 | A kind of hybrid giant electro-rheological fluid damper of multilayer shear extrusion |
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