CN118686888B - Nonlinear stiffness vibration damper with inertial volume amplifying effect and using method thereof - Google Patents
Nonlinear stiffness vibration damper with inertial volume amplifying effect and using method thereof Download PDFInfo
- Publication number
- CN118686888B CN118686888B CN202410833009.4A CN202410833009A CN118686888B CN 118686888 B CN118686888 B CN 118686888B CN 202410833009 A CN202410833009 A CN 202410833009A CN 118686888 B CN118686888 B CN 118686888B
- Authority
- CN
- China
- Prior art keywords
- nonlinear stiffness
- vibration
- inertia
- damping
- connecting frame
- 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.)
- Active
Links
- 230000000694 effects Effects 0.000 title claims abstract description 44
- 238000000034 method Methods 0.000 title claims abstract description 15
- 238000013016 damping Methods 0.000 claims abstract description 74
- 230000003321 amplification Effects 0.000 claims abstract description 21
- 238000003199 nucleic acid amplification method Methods 0.000 claims abstract description 21
- 230000007246 mechanism Effects 0.000 claims abstract description 15
- 230000021715 photosynthesis, light harvesting Effects 0.000 claims abstract description 7
- 230000009467 reduction Effects 0.000 claims description 51
- 238000005452 bending Methods 0.000 claims description 42
- 238000005265 energy consumption Methods 0.000 claims description 10
- 229920002545 silicone oil Polymers 0.000 claims description 7
- 238000010521 absorption reaction Methods 0.000 abstract description 6
- 230000002708 enhancing effect Effects 0.000 abstract description 2
- 239000006096 absorbing agent Substances 0.000 description 29
- 230000035939 shock Effects 0.000 description 26
- 238000013461 design Methods 0.000 description 19
- 230000009471 action Effects 0.000 description 10
- 230000005540 biological transmission Effects 0.000 description 10
- 238000006073 displacement reaction Methods 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 230000004044 response Effects 0.000 description 6
- 230000008901 benefit Effects 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000001965 increasing effect Effects 0.000 description 4
- 239000000463 material Substances 0.000 description 3
- 238000007639 printing Methods 0.000 description 3
- 238000009434 installation Methods 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 206010017367 Frequent bowel movements Diseases 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000010485 coping Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 230000001934 delay Effects 0.000 description 1
- 239000006185 dispersion Substances 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000009776 industrial production Methods 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
- 238000006467 substitution reaction Methods 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
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/22—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper characterised by comprising also a dynamic damper
-
- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04B—GENERAL BUILDING CONSTRUCTIONS; WALLS, e.g. PARTITIONS; ROOFS; FLOORS; CEILINGS; INSULATION OR OTHER PROTECTION OF BUILDINGS
- E04B1/00—Constructions in general; Structures which are not restricted either to walls, e.g. partitions, or floors or ceilings or roofs
- E04B1/62—Insulation or other protection; Elements or use of specified material therefor
- E04B1/92—Protection against other undesired influences or dangers
- E04B1/98—Protection against other undesired influences or dangers against vibrations or shocks; against mechanical destruction, e.g. by air-raids
-
- 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
- F16F2222/00—Special physical effects, e.g. nature of damping effects
- F16F2222/08—Inertia
-
- 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
- F16F2230/0094—Magnifying a physical effect
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T90/00—Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation
Landscapes
- Engineering & Computer Science (AREA)
- Architecture (AREA)
- General Engineering & Computer Science (AREA)
- Environmental & Geological Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
本发明涉及一种具有惯容放大效果的非线性刚度减振器及其使用方法，减振器包括非线性刚度减振装置和惯容阻尼耗能装置；所述非线性刚度减振装置包括上连接架、下连接架和多组减振单元；所述减振单元包括上端面、下端面和多组弹性弯杆；上下两组非线性刚度减振装置中相对应的减振单元间通过转轴连接；所述惯容阻尼耗能装置包括柔顺放大机构、设在柔顺放大机构的上下两侧的惯量盘；所述柔顺放大机构包括中心轴和柔顺惯容放大结构；两组柔顺惯容放大结构上下镜像设置；所述转轴上设置有主动摆臂，主动摆臂与两组柔顺惯容放大结构连接。本发明的非线性刚度减振器具有惯容放大的作用，从而显著增强能量吸收和振动控制性能。
The present invention relates to a nonlinear stiffness vibration damper with inertia amplification effect and a method for using the same. The vibration damper comprises a nonlinear stiffness vibration damping device and an inertia damping energy dissipation device; the nonlinear stiffness vibration damping device comprises an upper connecting frame, a lower connecting frame and a plurality of vibration damping units; the vibration damping units comprise an upper end face, a lower end face and a plurality of elastic bent rods; the corresponding vibration damping units in the upper and lower groups of nonlinear stiffness vibration damping devices are connected by a rotating shaft; the inertia damping energy dissipation device comprises a compliant amplification mechanism and an inertia disk arranged on the upper and lower sides of the compliant amplification mechanism; the compliant amplification mechanism comprises a central axis and a compliant inertia amplification structure; the two groups of compliant inertia amplification structures are arranged in an upper and lower mirror image; an active swing arm is arranged on the rotating shaft, and the active swing arm is connected to the two groups of compliant inertia amplification structures. The nonlinear stiffness vibration damper of the present invention has the effect of inertia amplification, thereby significantly enhancing the energy absorption and vibration control performance.
Description
Technical Field
The invention relates to the technical field of vibration reduction, in particular to a nonlinear stiffness vibration absorber with an inertial volume amplifying effect and a using method thereof.
Background
A shock absorber is a device for controlling and reducing vibration and shock in a mechanical system, and is widely used in various fields including automobiles, construction, industrial production facilities, aerospace, and the like. The basic principle is to reduce or suppress vibrations and shocks in the system by absorbing and converting energy, thereby improving the stability, comfort and reliability of the system.
Inertial energy, also known as "inertial container", is a vibration damping device that uses inertia to store and transfer vibration energy. Based on the traditional spring-damping passive vibration reduction element, the inertia element is introduced, so that the natural frequency of the system can be effectively reduced, and the resonance peak value can be restrained. Therefore, the method is widely applied to the fields of vehicle vibration reduction, building vibration reduction, dynamic energy absorption and the like. The basic principle of inertial capacity can be more intuitively understood by comparing the action modes of the spring and the damping. The inertial capacity has the characteristics that the generated inertial force is in direct proportion to the relative acceleration of two ends, and the structure mainly comprises a transmission mechanism and a rotating mass, wherein the transmission mechanism can convert linear reciprocating motion in the vibration process into rotary motion of the mass.
Conventional shock absorbers have a number of limitations in facing complex impacts and vibrations. First, they generally employ a linear stiffness design, i.e., the damping force is proportional to displacement. Such linear characteristics are particularly inadequate in coping with different loads and impact strengths, failing to provide the desired nonlinear damping effect, resulting in reduced shock absorber performance at high-strength impacts or frequent vibrations, thereby affecting system stability and reliability. While a linear stiffness damper may perform well at low loads, at high loads or large changes in impact strength, it may not provide sufficient damping force to effectively control vibration, ultimately leading to fatigue and damage to the device. In addition, the traditional shock absorber is difficult to adapt to various complex working conditions in design, and the application range of the shock absorber is limited. More importantly, the conventional shock absorber is poor in inertial energy effect, and conventional design is difficult to realize effective inertial energy amplification. The inertial capacity effect refers to the capability of a system to absorb and disperse energy when facing vibration and impact, and a traditional shock absorber often lacks the characteristic, so that under the condition of severe vibration and impact, the traditional shock absorber has limited energy absorption and dispersion effect, so that the system is difficult to restore balance and further the working efficiency and service life are affected, in addition, the system is slow in response when being impacted due to insufficient inertial capacity, and cannot be quickly stabilized, and the risk and uncertainty of equipment operation are increased.
In view of the foregoing, conventional shock absorbers are particularly desirable for applications requiring high performance and high reliability, and improvements and innovations are needed.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a nonlinear stiffness vibration damper with an inertial volume amplifying effect, which has the inertial volume amplifying effect, so that the energy absorption and vibration control performance are obviously enhanced.
The second object of the invention is to provide a method for using the nonlinear stiffness vibration damper with the inertia capacity amplifying effect.
The technical scheme for solving the technical problems is as follows:
The nonlinear stiffness vibration damper with the inertial volume amplifying effect comprises nonlinear stiffness vibration dampers and inertial volume damping energy dissipation devices, wherein the nonlinear stiffness vibration dampers are two groups, the two groups of nonlinear stiffness vibration dampers are symmetrically arranged on the upper side and the lower side of the inertial volume damping energy dissipation devices, each group of nonlinear stiffness vibration dampers comprise an upper connecting frame, a lower connecting frame and a plurality of groups of vibration damper units arranged between the upper connecting frame and the lower connecting frame, each vibration damper unit comprises an upper end face, a lower end face and elastic bent rods arranged on the upper end face and the lower end face, the elastic bent rods are multiple groups, each group of elastic bent rods are obliquely arranged and can twist on a vertical face, the oblique directions and the twisting directions of the multiple groups of elastic bent rods are the same, and the corresponding vibration damper units in the upper group of nonlinear stiffness vibration dampers and the lower group of nonlinear stiffness vibration dampers are connected through rotating shafts;
The inertia damping energy consumption device comprises a flexible amplifying mechanism and damping inertia shells arranged on the upper side and the lower side of the flexible amplifying mechanism, wherein the flexible amplifying mechanism comprises a central shaft and flexible inertia amplifying structures arranged on the central shaft, the number of the flexible inertia amplifying structures is two, the two groups of flexible inertia amplifying structures are reversely arranged, the damping inertia shells are arranged on lower connecting frames of nonlinear stiffness vibration reduction devices on the upper side and the lower side, inertia discs are arranged in the damping inertia shells and are filled with silicone oil for damping, the inertia discs are coaxially arranged with the central shaft, and driving swing arms are arranged on the rotating shaft and are connected with the two groups of flexible inertia amplifying structures.
Preferably, the vibration reduction units are multiple groups, and the vibration reduction units are circumferentially arranged along the center of the upper connecting frame or the lower connecting frame.
Preferably, the inclination direction and the torsion direction of the elastic bending rod in the vibration damping unit in the upper and lower nonlinear stiffness vibration damping devices are opposite.
Preferably, bearings are arranged at the contact positions of the upper connecting frame and the lower connecting frame with the rotating shaft.
Preferably, the flexible inertial volume amplifying structure comprises a rotating sleeve and flexible hinges arranged on the outer side of the rotating sleeve, wherein the rotating sleeve is fixed on the central shaft, the number of the flexible hinges is the same as that of the vibration reduction units, and the driving swing arms are connected with the rotating sleeve through the flexible hinges.
Preferably, the upper end and the lower end of the central shaft are both rotatably connected with the central position of the lower connecting frame of the nonlinear rigidity vibration damper at the upper side and the lower side.
Preferably, the section of the elastic bending rod is rectangular.
Preferably, the compliant inertial amplifying structure is manufactured by 3d printing.
Preferably, the upper connecting frame and the lower connecting frame are of equilateral triangle structures, the vibration reduction units are in three groups, and the three groups of vibration reduction units are arranged on three corners of the upper connecting frame and the lower connecting frame.
A method of damping a nonlinear stiffness damper comprising the steps of:
s1, installing the nonlinear stiffness damper between an upper building structure and a lower building structure, so that an upper connecting frame in a nonlinear stiffness damper device at the upper side of the nonlinear stiffness damper is connected with the upper building structure, and an upper connecting frame in the nonlinear stiffness damper device at the lower side is connected with the lower building structure;
And S2, when the upper building structure or the lower building structure is subjected to vertical reciprocating vibration, impact force generated by the vertical reciprocating vibration is transmitted to an upper connecting frame of the nonlinear stiffness vibration damper at the upper side or the lower side of the nonlinear stiffness vibration damper, so that a plurality of groups of vibration damping units in the nonlinear stiffness vibration dampers at the upper side and the lower side are driven to rotate clockwise or anticlockwise on a horizontal plane, a rotating shaft and an active swing arm arranged on the rotating shaft are driven to rotate clockwise or anticlockwise, the active swing arm rotates and simultaneously drives a flexible inertia volume amplifying structure to work, the flexible inertia volume amplifying structure amplifies the input speed of the active swing arm and outputs the amplified speed to a central shaft, and an inertia disc arranged on the central shaft is driven to rotate anticlockwise or clockwise and is rubbed with silicone oil damping, so that vibration damping and energy consumption effects are realized.
Compared with the prior art, the invention has the following beneficial effects:
1. When the nonlinear stiffness vibration absorber is subjected to vertical reciprocating vibration, the vibration absorbing unit in the nonlinear stiffness vibration absorber converts linear impact force into rotary motion, meanwhile, the rotary shaft is driven to rotate, the driving swing arm is driven to rotate while the rotary shaft rotates, and the driving swing arm rotates and simultaneously drives the flexible inertial volume amplifying structure to reversely rotate, so that the central shaft and the inertia discs arranged on the upper side and the lower side of the central shaft are driven to reversely rotate, wherein the flexible inertial volume amplifying structure has the effect of inertial volume amplifying, and therefore, the rotation speed of the inertia discs is far greater than that of the driving swing arm, so that the inertial volume effect can be improved, the integral performance of the nonlinear stiffness vibration absorber can be enhanced, and the reliability and stability of the nonlinear stiffness vibration absorber under various complex working conditions are ensured.
2. The invention realizes the inertial volume amplifying effect through the flexible inertial volume amplifying structure, thereby remarkably enhancing the energy absorption and vibration control performance of the system, and the nonlinear stiffness shock absorber can not only maintain excellent performance under high-strength impact, but also maintain high precision and stability in micro vibration and frequent reciprocating motion by combining compact structural design and zero back clearance characteristics, thereby greatly improving the overall reliability and application range of the system.
3. Since conventional shock absorbers often have mechanical clearances in the reciprocating motion, these mechanical clearances can lead to response delays and reduced accuracy, particularly in small vibrations and high frequency reciprocating motion. By optimizing the mechanical structure and the manufacturing precision, the zero back clearance characteristic is realized, so that the system can keep continuous and close contact under any motion state. The design not only eliminates the negative influence caused by mechanical clearance, but also ensures accurate transmission of force and motion, and in the application occasions needing high-precision control and frequent motion, such as precise instruments and high-end mechanical equipment, the zero back clearance characteristic can obviously improve the response speed and control precision of the shock absorber, thereby ensuring the stability and reliability of the system, and the improvements ensure that the shock absorber can be excellent in various complex environments, and further expand the application field of the shock absorber.
Drawings
FIG. 1 is a schematic diagram of a nonlinear stiffness shock absorber with inertial amplification effect according to the present invention.
Fig. 2 is a cross-sectional view of a nonlinear stiffness damper with inertial amplification effect of the present invention.
Fig. 3 is a schematic structural diagram of an inertial damping energy dissipation device.
Fig. 4 and 5 are schematic structural views of two sets of compliant inertial amplifying structures and two different viewing angles of the active swing arm.
Fig. 6 and 7 are schematic structural views of a vibration damping unit from two different perspectives.
Fig. 8 is a horizontal projection view of the elastic bent rod.
FIG. 9 is a schematic transmission diagram of an active swing arm and compliant inertial amplifying structure.
FIG. 10 is a schematic structural view of two sets of compliant inertial amplifying structures.
Detailed Description
The present invention will be described in further detail with reference to examples and drawings, but embodiments of the present invention are not limited thereto.
Referring to fig. 1 to 10, the nonlinear stiffness vibration damper with the inertial volume amplifying effect of the present invention comprises a nonlinear stiffness vibration damper and an inertial volume damping energy consumption device.
The nonlinear stiffness vibration reduction devices are symmetrically arranged on the upper side and the lower side of the inertial damping energy consumption device, and each nonlinear stiffness vibration reduction device comprises an upper connecting frame 1, a lower connecting frame 3 and a plurality of groups of vibration reduction units 2 arranged between the upper connecting frame 1 and the lower connecting frame 3; the vibration reduction units 2 comprise an upper end face 201, a lower end face 202 and elastic bending rods 203 arranged on the upper end face 201 and the lower end face 202, wherein the elastic bending rods 203 are in multiple groups, each group of elastic bending rods 203 is obliquely arranged and can be twisted on a vertical surface for converting vertical acting force into rotary motion, the oblique directions and the twisting directions of the multiple groups of elastic bending rods 203 are the same, the oblique directions and the twisting directions of the elastic bending rods 203 in the vibration reduction units 2 in the upper and lower groups of nonlinear stiffness vibration reduction devices are opposite, the corresponding vibration reduction units 2 in the upper and lower groups of nonlinear stiffness vibration reduction devices are connected through a rotating shaft 8, and in order to reduce friction coefficients and ensure the rotary precision and the efficient operation of the nonlinear stiffness vibration reduction device, bearings are arranged at the contact positions of the upper connecting frame 1 and the lower connecting frame 3 and the rotating shaft 8;
the inertia damping energy consumption device comprises a flexible amplifying mechanism and damping inertia shells 4 arranged on the upper side and the lower side of the flexible amplifying mechanism, wherein the damping inertia shells 4 are arranged on a lower connecting frame 3 of a nonlinear stiffness vibration reduction device on the upper side and the lower side, the inside of the damping inertia shells 4 comprises an inertia disc 9 and silicone oil damping, the flexible amplifying mechanism comprises a central shaft 6 and a flexible inertia amplifying structure 7 arranged on the central shaft 6, wherein the upper end and the lower end of the central shaft 6 are both rotationally connected with the central position of the lower connecting frame 3 of the nonlinear stiffness vibration reduction device on the upper side and the lower side;
The flexible inertial volume amplifying structure 7 comprises a rotating sleeve 701 and flexible hinges 702 arranged on the outer side of the rotating sleeve 701, wherein the rotating sleeve 701 is fixed on the central shaft 6, the number of the flexible hinges 702 is the same as that of the vibration reduction units 2, in the embodiment, the flexible hinges 702 are three groups, and the driving swing arm 5 is connected with the rotating sleeve 701 through the flexible hinges 702.
When the nonlinear stiffness shock absorber is subjected to the acting force in the axial direction, the vibration reduction unit 2 in the nonlinear stiffness shock absorber is deformed so as to drive the driving swing arm 5 to rotate, and the motion of the driving swing arm 5 is further transmitted to the flexible inertial volume amplifying structure 7 to trigger the flexible inertial volume amplifying structure 7 to generate fine deformation, and the inertia disc 9 is finally driven to rotate by the series of actions, so that the inertial volume effect of the nonlinear stiffness shock absorber is remarkably enhanced.
Referring to fig. 1 to 10, the vibration damping units 2 are multiple groups, the multiple groups of vibration damping units 2 are circumferentially arranged along the center of the upper connecting frame 1 or the lower connecting frame 3, in this embodiment, the upper connecting frame 1 and the lower connecting frame 3 are both in an equilateral triangle structure, the vibration damping units 2 are three groups, and the three groups of vibration damping units 2 are arranged on three corners of the upper connecting frame 1 and the lower connecting frame 3.
Referring to fig. 1-10, the cross section of the elastic bending rod 203 is rectangular, which enables the elastic bending rod 203 to present different reaction forces according to displacement changes (i.e., the elastic bending rod 203 with a rectangular cross section has high-efficiency elastic deformation capability), so as to better adapt to various load changes and impact strengths, and further provide excellent vibration reduction effects under the condition of different load changes and impact strengths. In addition, by adjusting the aspect ratio of the rectangular section, the nonlinear rigidity characteristic of the elastic bent rod 203 can be further optimized, so that different reaction forces are provided at different displacement stages, the advantage of inertial expansion is further fully exerted, the performance of the shock absorber is greatly improved, and the nonlinear rigidity shock absorber can be suitable for various application scenes.
Therefore, the design can not only adapt to slight vibration and displacement with small amplitude, but also provide stronger vibration reduction effect under larger impact and load change, thereby remarkably improving the performance and adaptability of the nonlinear stiffness vibration damper. Therefore, the nonlinear stiffness damper can maintain high-efficiency damping performance in both micro-vibration environments and high-strength impact environments, so that the requirements of different application scenes are met.
In addition, by designing the sectional shape of the elastic bending rod 203 to be rectangular, it has a larger moment of inertia than the currently existing cylindrical elastic bending rod. The rectangular section of the elastic bending rod 203 can provide not only higher bending rigidity and bearing capacity but also more effective control of the direction of force, and thus can be supported more stably in the face of a complex vibration environment.
In addition, since the sectional area of the rectangular cross section is large, a special shape design can be performed, and the rectangular cross section elastic bending rod 203 can more effectively convert the linear motion into the rotational motion, so that the rotational angle generated by the elastic bending rod 203 when being stressed is larger, and the larger rotational angle means better inertial effect, thereby providing more excellent vibration control performance for the vibration damping unit 2. At the same time, the rectangular section of the elastic bending rod 203 also provides nonlinear stiffness, and can provide different reaction forces in different displacement stages, so as to better adapt to various load changes and impact strengths.
Referring to fig. 1-10, the vibration damper unit 2 provides nonlinear rigidity for the nonlinear rigidity vibration damper of the present invention, wherein the projection of the elastic bending rod 203 is an arc, the arc can be represented by a circle, an eccentric circle, an ellipse, an eccentric ellipse, etc., the height dimension of the elastic bending rod 203 is represented by a straight line, a diagonal line, etc., so that a three-dimensional curve is formed when the plane projection of the elastic bending rod 203 is unfolded, the rigidity of the vibration damper unit 2 can be increased by increasing the width and thickness of the elastic bending rod 203, the bearing capacity can be improved, but the nonlinear variation of the rigidity is reduced. Reducing the width and thickness of the elastic bending rod 203 can reduce the rigidity of the vibration damping unit 2 and reduce the bearing capacity, but the resonance frequency of the vibration damping unit 2 becomes lower, the vibration damping performance is improved, and the nonlinearity of the rigidity is more obvious. Therefore, the nonlinear rigidity of the vibration reduction unit 2 can be adjusted by adjusting the width and the thickness of the cross section of the elastic bent rod 203, and the nonlinear rigidity can be reasonably designed according to the vibration reduction requirement, so that the vibration reduction performance is improved.
Referring to fig. 8, fig. 8 shows a projection curve of an elastic bent rod 203 of rectangular cross section, assuming that the center of the projection curve is (x a,ya) and intersects (x b, 0) and (0, y b) on the x-axis and the y-axis, respectively, assuming that x a＝ya =a and x b＝yb =b >0, curvature k is the inverse of the radius of the projection curve, describing the degree of curvature of the projection curve, and thus, curvature k is:
If it is The center of the projection curve is located in the first quadrant (x a＝ya =a > 0);
If it is The center of the projection curve is in the third quadrant (x a＝ya = a < 0);
If it is The center of the projection curve is located on the origin;
Thus, the equation for the guide line of the elastic bending rod 203 is
Where h is the height of the resilient curved bar 203 and s.epsilon.0, 1.
The curvature k of two groups of different parameters and the coordinates of the projection center are set according to the equation to generate two three-dimensional curves, namely an inner curve 205 and an outer curve 204 of the elastic bending rod 203, the inner curve 205 and the outer curve 204 of the elastic bending rod 203 are respectively filled with curved surfaces and thickened to form the elastic bending rod 203, the thickness of the elastic bending rod 203 with a rectangular section is required to be adjusted according to the whole size and the hardness of the vibration reduction unit 2, so that the rigidity of the whole vibration reduction unit 2 is not too large or too small, the elastic bending rod 203 cannot be effectively deformed due to the too large rigidity, the vibration reduction unit 2 cannot be effectively converted into rotary motion, the vibration reduction unit 2 becomes unstable due to the too small rigidity, collapse is easy to occur when the vibration reduction unit is subjected to external vibration, and the thickness of the elastic bending rod 203 with the rectangular section is required to be determined to the optimal parameters according to real objects and through multiple experiments.
Referring to fig. 1-10, the compliant inertial volume amplifying structure 7 is manufactured by 3d printing, the hardness of the selected printing material is low, so that the compliant inertial volume amplifying structure 7 has high flexibility, and the compliant inertial volume amplifying structure 7 can generate larger deformation when stressed by utilizing the characteristics of the flexible material, thereby absorbing and relieving impact. The high flexibility not only helps to reduce vibration and isolate vibration, but also can protect other elements in the system from being damaged by excessive stress, and improves the durability and service life of the system. Zero backlash is a great advantage of the compliant inertial amplifying structure 7, meaning that there is no looseness or delay in the motion transfer process, which is critical for high precision drive systems. The zero back clearance structure can effectively control micro-vibration. The flexible inertial amplification structure 7 can play a role in good vibration isolation, and the flexible material has good vibration reduction performance, so that the micro-vibration transmitted to the inside of the system from the external environment can be effectively isolated, and the precise element is protected from vibration interference.
Referring to fig. 9, fig. 9 shows a schematic diagram of the compliant inertial volume amplifying structure 7 working in cooperation with the driving swing arm 5, and when the driving swing arm 5 rotates, the compliant inertial volume amplifying structure 7 is driven to deform. Particularly, when the three groups of driving swing arms 5 rotate clockwise, the flexible inertial accommodating and amplifying structure 7 is driven to rotate anticlockwise. Because the ratio of the radius 10 of the driving swing arm 5 to the radius 11 of the compliant inertial volume amplifying structure 7 is 3:1, when the driving swing arm 5 rotates by one unit angle, the compliant inertial volume amplifying structure 7 rotates by three corresponding unit angles, thereby realizing a transmission ratio of 1:3. The design skillfully utilizes the lever principle, and realizes the amplification and transmission of the motion through the difference of radius proportions. Under the mechanism, the rotation angle of the smaller driving swing arm 5 can be converted into a larger output angle through the amplification effect of the flexible inertial volume amplifying structure 7, so that the response sensitivity and the response efficiency of the system are effectively improved. In addition, the design of the high transmission ratio ensures that the whole system can still maintain high stability and reliability in a complex working environment, and ensures that the whole system can achieve optimal performance under various working conditions. In this way, the whole system not only improves the inertial effect, but also enhances the overall mechanical advantage and dynamic performance.
Referring to fig. 1-10, the present invention achieves efficient vibration damping through a unique mechanical design, specifically:
(1) The elastic bending rod 203 with a rectangular section can bend under the action of external force, so that linear motion is converted into rotary motion, impact energy is effectively absorbed and dispersed, and the nonlinear rigidity characteristic of the elastic bending rod 203 can be optimized by adjusting the length-width ratio of the rectangular section, so that different reaction forces can be provided at different displacement stages, and the elastic bending rod is suitable for various load changes and impact strength, thereby improving the vibration reduction effect. The design ensures that the nonlinear stiffness damper can flexibly adjust the stiffness characteristic under the action of external impact force, and can provide the optimal damping effect when facing impacts with different intensities.
(2) The compliant inertial volume amplifying structure 7 in the invention realizes the inertial volume amplifying effect of 1:3 through accurate design, and obviously enhances the energy absorption and vibration control performance of the system, which means that the input motion quantity can be amplified three times, thereby greatly improving the vibration reduction capability and response speed of the system.
In addition, the compact structural design not only enables the system to be suitable for application scenes with limited space, but also reduces the whole volume and the difficulty of installation and maintenance, so that the design is particularly suitable for equipment and occasions with high-performance vibration reduction but limited installation space.
In addition, the zero back clearance design ensures the high precision and stability of the nonlinear stiffness shock absorber in the reciprocating motion, and is particularly suitable for precision instruments and high-end mechanical equipment with small vibration and frequent reciprocating motion. The zero backlash feature also ensures that the nonlinear stiffness damper of the present invention can always maintain high precision motion control in a small vibration environment without degradation or instability of motion due to backlash problems, which is particularly important for precision instruments and equipment, which typically require high frequency reciprocating motion within a very small error range. The connecting frame, the central shaft 6, the inertia disc 9, the driving swing arm 5 and other components in the nonlinear stiffness damper play important roles respectively to ensure correct relative positions and motion paths, wherein the lower connecting frame 3 is used for supporting and positioning all the components to ensure that all the components keep correct relative positions and motion paths in the working process, the central shaft 6 is a core supporting structure of the nonlinear stiffness damper, is used for connecting and transmitting motion and force of all the components, provides structural stability and is a key channel for motion transmission, the design and the mass of the inertia disc 9 directly influence the inertial capacity characteristics of a system, the inertial capacity effect of the nonlinear stiffness damper can be optimized by adjusting the mass and the position of the inertia disc 9 (for example, increasing the number of the inertia discs 9), the optimal damping performance is achieved, the driving swing arm 5 is connected between the damping unit 2 and the inertia disc 9 and is responsible for transmitting and converting motion, and the design and the motion characteristics have direct influence on the system performance. In the nonlinear stiffness shock absorber, the external linear impact force is converted into rotary motion through the bending of the elastic bending rod 203 with a rectangular section, and the motion is amplified by utilizing the 1:3 transmission ratio of the compliant inertial volume amplifying structure 7, so that the inertial volume effect is obviously enhanced. Under the action of the inertia disc 9 and the driving swing arm 5, the motion is further converted and transmitted, and efficient vibration reduction is realized. The process not only enhances the overall performance of the nonlinear stiffness shock absorber, but also ensures the reliability and stability of the nonlinear stiffness shock absorber under various complex working conditions. The zero back clearance design ensures high precision and high efficiency vibration reduction in micro vibration environment, greatly improves the reliability and application range of the system, and is particularly suitable for scenes requiring high performance and high reliability. Therefore, the nonlinear stiffness damper has remarkable advantages in the aspects of improving the damping effect of the system, optimizing the structural design and improving the overall performance, and can be widely applied to various high-end equipment and complex application scenes needing high-efficiency damping.
Referring to fig. 1 to 10, the vibration damping method for a nonlinear stiffness vibration damper having an inertial amplification effect of the present invention includes the steps of:
S1, installing the nonlinear stiffness damper between an upper building structure and a lower building structure, so that an upper connecting frame 1 in a nonlinear stiffness damper device on the upper side of the nonlinear stiffness damper is connected with the upper building structure, and an upper connecting frame 1 in the nonlinear stiffness damper device on the lower side is connected with the lower building structure;
s2, when the upper building structure or the lower building structure generates vertical reciprocating vibration, impact force generated by the vertical reciprocating vibration is transmitted to an upper connecting frame 1 of the nonlinear stiffness vibration damper at the upper side or the lower side of the nonlinear stiffness vibration damper, so that a plurality of groups of vibration damper units 2 in the nonlinear stiffness vibration damper at the upper side and the lower side are driven to rotate clockwise or anticlockwise on a horizontal plane, thereby driving a rotating shaft 8 and a driving swing arm 5 arranged on the rotating shaft 8 to rotate clockwise or anticlockwise, driving an inertia disc 9 to rotate anticlockwise or rotate clockwise through a flexible inertia amplifying structure 7, and friction is generated between the inertia disc 9 and silicone oil damping when the inertia disc 9 rotates, and further achieving vibration damping and energy consumption effects;
When the upper building structure or the lower building structure generates vertical reciprocating vibration, impact force generated by the vertical reciprocating vibration is transmitted to an upper connecting frame 1 of a nonlinear stiffness vibration damper at the upper side or the lower side of the nonlinear stiffness vibration damper, so that a plurality of groups of vibration damping units 2 in the nonlinear stiffness vibration damper at the upper side and the lower side are driven to rotate clockwise or anticlockwise on a horizontal plane, a rotating shaft 8 and a driving swing arm 5 arranged on the rotating shaft 8 are driven to rotate clockwise or anticlockwise, the driving swing arm 5 rotates and drives a flexible inertia capacity amplifying structure 7 to work, the flexible inertia capacity amplifying structure 7 amplifies the input speed of the driving swing arm 5 and outputs the amplified speed to a central shaft 6, and an inertia disc 9 arranged on the central shaft 6 is driven to rotate anticlockwise or clockwise, and friction is generated between the inertia disc 9 and silicone oil damping when the inertia disc rotates, so that vibration damping and energy consumption effects are realized.
Taking the vertical reciprocating vibration of a lower building structure (such as the ground) as an example, when the lower building structure generates the vertical reciprocating vibration, a plurality of groups of vibration damping units 2 in the nonlinear stiffness vibration damping device in the nonlinear stiffness vibration damper can be vertically compressed and vertically stretched.
In the vertical compression process, the lower end surface of the lower vibration reduction unit 2 rotates clockwise under the action of the acting force of the lower building structure on the lower vibration reduction unit 2, the acting force is the extending direction of the elastic bent rod 203, and the lower end surface of the lower vibration reduction unit 2 is decomposed to obtain a vertical component force and a horizontal component force, wherein the vibration reduction unit compresses downwards under the action of the vertical component force, and the lower end surface of the vibration reduction unit 2 rotates clockwise under the action of the horizontal component force;
In the vertical stretching process, the lower vibration reduction unit 2 rotates anticlockwise under the action force of the lower building structure on the lower vibration reduction unit, the inclination direction and the torsion direction of the elastic bending rod 203 in the upper vibration reduction unit 2 are opposite to those of the elastic bending rod 203 in the lower vibration reduction unit 2, so that the lower vibration reduction unit can also rotate anticlockwise under the action force of the upper building structure, the rotating shaft 8 and the driving swing arm 5 arranged on the rotating shaft 8 are driven to rotate anticlockwise, and similarly, the driving swing arm 5 rotates to drive the compliant inertial navigation amplifying structure 7 to rotate clockwise, and the center shaft 6 and the inertia discs 9 arranged on two sides of the center shaft 6 are driven to rotate clockwise through the compliant inertial navigation amplifying structure 7.
In the above process, since the upper and lower groups of compliant hinges 702 are staggered, when the compliant inertial capacitance amplifying structure 7 rotates clockwise or anticlockwise, one group of compliant hinges always bear tensile force (the other group bears compressive force), so that stable zero-backlash transmission is realized.
The foregoing is illustrative of the present invention and is not to be construed as limiting thereof, but rather as various changes, modifications, substitutions, combinations, and simplifications which may be made therein without departing from the spirit and principles of the invention are intended to be included within the scope of the invention.
Claims (8)
1. The nonlinear stiffness vibration damper with the inertial volume amplifying effect is characterized by comprising nonlinear stiffness vibration dampers and inertial volume damping energy dissipation devices, wherein the nonlinear stiffness vibration dampers are two groups, the two groups of nonlinear stiffness vibration dampers are symmetrically arranged on the upper side and the lower side of the inertial volume damping energy dissipation devices, each group of nonlinear stiffness vibration dampers comprises an upper connecting frame, a lower connecting frame and a plurality of groups of vibration dampers arranged between the upper connecting frame and the lower connecting frame, each vibration damper comprises an upper end face, a lower end face and elastic bending rods arranged on the upper end face and the lower end face, the elastic bending rods are multiple groups, each group of elastic bending rods are obliquely arranged and can twist on a vertical face, the oblique directions and the twisting directions of the multiple groups of elastic bending rods are the same, and the corresponding vibration dampers in the upper group of nonlinear stiffness vibration dampers and the lower group of vibration dampers are connected through a rotating shaft;
The inertia damping energy consumption device comprises a flexible amplifying mechanism and inertia discs arranged on the upper side and the lower side of the flexible amplifying mechanism, wherein the flexible amplifying mechanism comprises a central shaft and flexible inertia amplifying structures arranged on the central shaft, two groups of flexible inertia amplifying structures are arranged in opposite directions, and the inertia discs are coaxially arranged with the central shaft;
the inertia capacity damping energy consumption device further comprises a damping inertia shell, wherein the damping inertia shell is arranged on a lower connecting frame of the nonlinear stiffness vibration reduction device at the upper side and the lower side, the inertia disc is positioned in the damping inertia shell, and silicone oil damping is filled in the damping inertia shell;
The flexible inertial volume amplifying structure comprises a rotating sleeve and flexible hinges arranged on the outer side of the rotating sleeve, wherein the rotating sleeve is fixed on the central shaft, the number of the flexible hinges is the same as that of the vibration reduction units, and the driving swing arms are connected with the rotating sleeve through the flexible hinges.
2. The nonlinear stiffness vibration damper with inertial amplification effect according to claim 1, wherein the vibration damper units are in a plurality of groups, and the plurality of groups of vibration damper units are circumferentially arranged along the center of the upper or lower connecting frame.
3. The nonlinear stiffness vibration damper with inertial amplification effect according to claim 1, wherein the inclination direction and the torsion direction of the elastic bending rod in the vibration damping unit in the upper and lower sets of nonlinear stiffness vibration damping devices are opposite.
4. The nonlinear stiffness vibration damper with inertial amplification effect according to claim 1, wherein bearings are provided at positions where the upper and lower connection frames are in contact with the rotating shaft.
5. The nonlinear stiffness vibration damper with inertial amplification effect according to claim 4, wherein the upper and lower ends of the center shaft are both rotatably connected at the center position of the lower connecting frame of the nonlinear stiffness vibration damper at the upper and lower sides.
6. The nonlinear stiffness vibration damper with inertial amplification effect according to claim 1, wherein the elastic bending rod has a rectangular cross section.
7. The nonlinear stiffness vibration damper with the inertial volume amplifying effect according to claim 1, wherein the upper connecting frame and the lower connecting frame are of equilateral triangle structures, the vibration damper units are three groups, and the three groups of vibration damper units are arranged on three corners of the upper connecting frame and the lower connecting frame.
8. A vibration damping method for a nonlinear stiffness vibration damper having an inertial amplification effect according to any one of claims 1 to 7, characterized by comprising the steps of:
s1, installing the nonlinear stiffness damper between an upper building structure and a lower building structure, so that an upper connecting frame in a nonlinear stiffness damper device at the upper side of the nonlinear stiffness damper is connected with the upper building structure, and an upper connecting frame in the nonlinear stiffness damper device at the lower side is connected with the lower building structure;
And S2, when the upper building structure or the lower building structure is subjected to vertical reciprocating vibration, impact force generated by the vertical reciprocating vibration is transmitted to an upper connecting frame of the nonlinear stiffness vibration damper at the upper side or the lower side of the nonlinear stiffness vibration damper, so that a plurality of groups of vibration damping units in the nonlinear stiffness vibration dampers at the upper side and the lower side are driven to rotate clockwise or anticlockwise on a horizontal plane, a rotating shaft and an active swing arm arranged on the rotating shaft are driven to rotate clockwise or anticlockwise, the active swing arm rotates and simultaneously drives a flexible inertia volume amplifying structure to work, the flexible inertia volume amplifying structure amplifies the input speed of the active swing arm and outputs the amplified speed to a central shaft, and an inertia disc arranged on the central shaft is driven to rotate anticlockwise or clockwise and is rubbed with silicone oil damping, so that vibration damping and energy consumption effects are realized.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410833009.4A CN118686888B (en) | 2024-06-25 | 2024-06-25 | Nonlinear stiffness vibration damper with inertial volume amplifying effect and using method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410833009.4A CN118686888B (en) | 2024-06-25 | 2024-06-25 | Nonlinear stiffness vibration damper with inertial volume amplifying effect and using method thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN118686888A CN118686888A (en) | 2024-09-24 |
| CN118686888B true CN118686888B (en) | 2024-12-13 |
Family
ID=92764347
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202410833009.4A Active CN118686888B (en) | 2024-06-25 | 2024-06-25 | Nonlinear stiffness vibration damper with inertial volume amplifying effect and using method thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN118686888B (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109163047A (en) * | 2018-10-25 | 2019-01-08 | 华北水利水电大学 | A kind of non-linear current vortex is used to matter damper and design method |
| CN112554360A (en) * | 2020-11-30 | 2021-03-26 | 同济大学 | Self-resetting self-balancing inertial container based on rhombic transmission mechanism |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2528757A1 (en) * | 2010-01-25 | 2012-12-05 | Lotus F1 Team Limited | Fluid inerter |
| CN114321249B (en) * | 2022-01-14 | 2022-11-29 | 华南农业大学 | Three-dimensional spiral unit with inertial volume effect, mechanical metamaterial and application of three-dimensional spiral unit |
| CN117780841A (en) * | 2023-12-21 | 2024-03-29 | 同济大学 | A propeller through-type hydraulic inertia-inertia mass coupling type tuned vibration absorption system |
-
2024
- 2024-06-25 CN CN202410833009.4A patent/CN118686888B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109163047A (en) * | 2018-10-25 | 2019-01-08 | 华北水利水电大学 | A kind of non-linear current vortex is used to matter damper and design method |
| CN112554360A (en) * | 2020-11-30 | 2021-03-26 | 同济大学 | Self-resetting self-balancing inertial container based on rhombic transmission mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| CN118686888A (en) | 2024-09-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP5831734B2 (en) | Inertia mass damper | |
| US20140048989A1 (en) | Vibration isolation systems | |
| US6084329A (en) | Vibration mechanism having a magnetic spring | |
| Chen et al. | A variable positive-negative stiffness joint with low frequency vibration isolation performance | |
| JP5387123B2 (en) | Friction damper | |
| US5549270A (en) | Vibration isolation system | |
| CN113565922B (en) | Integrated quasi-zero stiffness vibration isolation buffering element and vibration isolation buffering assembly | |
| US3066905A (en) | Vibration isolator | |
| CN111156283A (en) | Crank-piston inertial damping dynamic isolator | |
| JP2019019849A (en) | Seismic isolation damper and seismic isolation system | |
| CN118686888B (en) | Nonlinear stiffness vibration damper with inertial volume amplifying effect and using method thereof | |
| CN108035598B (en) | Semi-active/passive hybrid damping device | |
| CN117889184A (en) | A multi-stage vibration isolation device | |
| JP2023044961A (en) | Vibration suppression device | |
| CN113503336A (en) | Constant-quasi-zero-stiffness vibration isolator | |
| JPH11351318A (en) | Damper for base isolation device | |
| CN114673758B (en) | Drilling device based on positive and negative rigidity vibration reduction technology | |
| EP1241371A2 (en) | Vibration isolation system | |
| CN113503332B (en) | Quasi-zero stiffness vibration isolator | |
| CN118462745B (en) | Load self-adaptive continuous multistage quasi-zero stiffness vibration isolator | |
| CN222811136U (en) | Nonlinear combined shock absorbing device | |
| JPH0776951A (en) | Steel bending damper | |
| WO1994013999A1 (en) | Vibration isolation system | |
| CN116181848B (en) | Vertical-torsional nonlinear vibration absorber | |
| CN221647478U (en) | A nonlinear self-balancing inertia container with cubic stiffness |
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 |