A nonlinear vibration damping device

Abstract

The application provides a nonlinear damping device, which comprises a frame, a sliding block, a transverse linear expansion component and a longitudinal linear expansion component; the frame is provided with a longitudinal sliding rail, the sliding block is slidingly arranged on the longitudinal sliding rail, one end of the longitudinal linear expansion component is connected with the frame, and the other end of the longitudinal linear expansion component is connected with the sliding block; the frame is symmetrically provided with a guide track groove on both sides of the longitudinal sliding rail, the sliding block is symmetrically provided with the transverse linear expansion component on both sides in the longitudinal direction; one end of the transverse linear expansion component is connected with the sliding block, and the other end of the transverse linear expansion component is movably arranged in the guide track groove; the guide track groove comprises a curve groove section one and a curve groove section two which are symmetrically arranged in the transverse direction, and the track lines of the curve groove section one and the curve groove section two are both quadratic functions. The damping device has a polynomial stiffness form, has better robustness, and can realize efficient damping of the structure in a wide frequency and wide amplitude range.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of vibration reduction, in particular to a nonlinear vibration reduction device. BACKGROUND

[0002] Vibration problems exist widely in aerospace, machinery, civil engineering and other engineering fields. For example, in the field of bridge engineering, with the use of new lightweight high-strength materials, the development of construction and design technology, and the improvement of people's aesthetic appreciation of buildings, bridge structures tend to be more flexible. Flexible bridges have the characteristics of small structural stiffness, so their vibration problems are obvious (such as wind vibration, human-induced vibration, etc.), and how to ensure the safety and vibration comfort of the structure is a problem that needs to be solved in the industry. Therefore, it is of great significance to take effective measures for vibration control.

[0003] Currently, vibration control theory is mainly divided into passive control, active control and semi-active control. Among them, active control measures and semi-active control measures both involve external energy input process, and the device maintenance cost is high and the reliability is general; in comparison, passive control measures do not require external energy, and have the advantages of simple structure, low cost and easy maintenance. Therefore, adding passive control vibration reduction devices to the structure is the most widely used vibration control measure at present.

[0004] Linear frequency modulation vibration reduction devices (such as TMD) are the most commonly used passive control devices at present, but they only have vibration reduction effect in a relatively narrow frequency band near the target modal frequency, and have poor robustness to frequency changes. The non-linear energy sink (NES) that has emerged in recent years has vibration reduction effect in a wide frequency band, and has good adaptability, but has poor robustness to external load amplitude changes.

[0005] Therefore, it is an urgent problem in the field to develop a vibration reduction device that can achieve efficient vibration reduction in a wide frequency and wide amplitude range.

[0006] In summary, there is an urgent need for a nonlinear vibration reduction device to solve the problems in the prior art. SUMMARY

[0007] The present application aims to provide a nonlinear vibration reduction device, which aims to achieve efficient vibration reduction of the structure in a wide frequency and wide amplitude range, and the specific technical solutions are as follows:

[0008] The nonlinear damping device comprises a frame, a sliding block, a transverse linear expansion component and a longitudinal linear expansion component; the frame is provided with a longitudinal sliding rail, the sliding block is slidingly arranged on the longitudinal sliding rail, one end of the longitudinal linear expansion component is connected with the frame, and the other end of the longitudinal linear expansion component is connected with the sliding block; the frame is symmetrically provided with a guide track groove on the two sides of the longitudinal sliding rail, and the sliding block is symmetrically provided with the transverse linear expansion component on the two sides in the longitudinal direction; one end of the transverse linear expansion component is connected with the sliding block, and the other end of the transverse linear expansion component is movably arranged in the guide track groove; the guide track groove comprises a curve groove section one and a curve groove section two which are symmetrically arranged in the transverse direction, and the track lines of the curve groove section one and the curve groove section two are quadratic functions.

[0009] In the above technical solution, preferably:

[0010] The track line of the curve groove section one is f(u)=au 2 -bu(u<0),

[0011] The track line of the curve groove section two is f(u)=au 2 +bu(u>0),

[0012] Wherein, a is a quadratic term coefficient, b is a linear term coefficient, u is a coordinate value on a longitudinal coordinate axis, and f(u) is a coordinate value on a transverse coordinate axis; u=0 is the intersection of the curve groove section one and the curve groove section two.

[0013] In the above technical solution, preferably, the restoring force of the longitudinal linear expansion component and the transverse linear expansion component acting on the sliding block is:

[0014] F m =k1u+k2u·|u|+k3u 3 ,

[0015] F m is the restoring force of the sliding block, k1, k2 and k3 are respectively a linear stiffness coefficient, a square stiffness coefficient and a cubic stiffness coefficient of the nonlinear damping system, wherein: k1=2k l1 b 2 +k l2 , k2=6k l1 ab, k3=4k l1 a 2 ; k l1 and k l2 are respectively stiffness coefficients of the transverse linear expansion component and the longitudinal linear expansion component.

[0016] In the above technical solution, preferably, the frame is provided with a guide plate on the two sides of the longitudinal sliding rail, and the guide track groove is arranged on the guide plate.

[0017] Preferably, the damping device further comprises a damper arranged along the longitudinal direction, one end of the damper being connected to the frame and the other end of the damper being connected to the sliding block.

[0018] Preferably, the longitudinal linear extension component is a longitudinal linear spring.

[0019] Preferably, the transverse extension component comprises a movable part and a transverse linear spring, one end of the transverse linear spring being connected to the sliding block and the other end of the transverse linear spring being arranged with the movable part, the movable part being arranged in the guide track slot to move along the guide track slot.

[0020] Preferably, the movable part comprises a connecting seat and a roller, the connecting seat being connected to the end of the transverse linear spring, the roller being rotatably arranged on the connecting seat, and the roller being arranged in the guide track slot.

[0021] Preferably, the transverse extension component further comprises a hollow tube, one end of the hollow tube being fixedly arranged on the sliding block, the transverse linear spring being arranged inside the hollow tube, and the transverse linear spring being capable of freely extending and contracting in the transverse direction inside the hollow tube.

[0022] Preferably, a gap is left between the inner wall of the hollow tube and the outer periphery of the transverse linear spring.

[0023] The technical scheme of the present application has the following beneficial effects:

[0024] 1) The damping device provided by the present application is a passive control device, which does not require external energy input, has simple device structure, low cost and low maintenance cost, and relatively high system reliability.

[0025] 2) The damping device provided by the present application has a polynomial stiffness form, has better frequency robustness than a linear frequency damping device, and has better amplitude robustness than a traditional nonlinear energy sink device, and the damping device provided by the present application can realize efficient damping of a structure in a wide frequency and wide amplitude range.

[0026] 3) The damping device provided by the present application can accurately realize the stiffness nonlinearity of the polynomial form through the sliding track of the roller, while the traditional nonlinear stiffness is realized through the geometric nonlinearity of the spring, and the high-order nonlinearity term is often omitted. In addition, the linear stiffness coefficient, the square stiffness coefficient and the cubic stiffness coefficient in the polynomial stiffness of the present application can be individually set, which can better meet the actual damping requirements.

[0027] In addition to the purposes, features and advantages described above, the present application has other purposes, features and advantages. The present application will be further described below with reference to the drawings. BRIEF DESCRIPTION OF DRAWINGS

[0028] The accompanying drawings, which form a part of this application, are intended to provide further understanding of the application and are incorporated herein in their entirety. The drawings include an exemplary embodiment of the application and its description is used to explain the application, and is not intended to limit the application.

[0029] Figure 1 is a schematic diagram of the overall structure of the nonlinear damping device;

[0030] Figure 2 is a schematic diagram of the overall structure of the nonlinear damping device; Figure 1 is a schematic diagram of the structure of the guide plate;

[0031] Figure 3 is a schematic diagram of the overall structure of the nonlinear damping device; Figure 1 is a schematic diagram of the structure of the transverse linear expansion component;

[0032] Figure 4 is a schematic diagram of the overall structure of the nonlinear damping device; Figure 1 is a schematic diagram of the structure of the hidden hollow tube of the transverse linear expansion component;

[0033] Figure 5 is a schematic diagram of the overall structure of the nonlinear damping device;

[0034] Figure 6 is a schematic diagram of the overall structure of the nonlinear damping device;

[0035] Wherein, 1, frame bottom plate, 2, frame side plate, 3, longitudinal slide rail, 4, sliding block, 5, guide plate, 5.1, guide track groove, 5.1.1, curve groove segment one, 5.1.2, curve groove segment two, 6, transverse linear expansion component, 6.1, hollow tube, 6.2, roller, 6.3, connecting plate, 6.4, first end plate, 6.5, second end plate, 6.6, transverse linear spring, 7, longitudinal linear expansion component, 8, damper. DETAILED DESCRIPTION

[0036] In order to facilitate the understanding of the present application, the present application will be described more fully below, and preferred embodiments of the present application will be given. However, the present application can be realized in many different forms and is not limited to the embodiments described herein. On the contrary, the purpose of providing these embodiments is to make the disclosure of the present application more thorough and comprehensive.

[0037] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used in the description of the application herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the application.

[0038] Embodiment:

[0039] Referring to Figures 1-4The nonlinear damping device, i.e. a nonlinear energy sink damping device, comprises a frame, a sliding block 4, a transverse linear expansion component 6 and a longitudinal linear expansion component 7. The frame is provided with a longitudinal sliding rail 3, the sliding block 4 is slidingly arranged on the longitudinal sliding rail 3, one end of the longitudinal linear expansion component 7 is connected to the frame, and the other end is connected to the sliding block 4. The frame is symmetrically provided with a guide track groove 5.1 on both sides of the longitudinal sliding rail 3, and the sliding block 4 is symmetrically provided with the transverse linear expansion component 6 on both sides in the longitudinal direction. One end of the transverse linear expansion component is connected to the sliding block 4, and the other end is movably arranged in the corresponding guide track groove (i.e. in the guide track groove on the same side). The guide track groove 5.1 comprises a curve groove segment one 5.1.1 and a curve groove segment two 5.1.2 arranged in sequence, and the curve groove segment one and the curve groove segment two are symmetrically arranged about the transverse direction and the track lines of both are quadratic functions. Specifically, when the sliding block 4 slides on the longitudinal sliding rail, the end of the transverse linear expansion component moves along the guide track groove, and expands and contracts with the change of the guide track groove. In this embodiment, the expansion amount of the transverse linear expansion component and the transverse elastic force generated thereby are linearly changed; the expansion amount of the longitudinal linear expansion component and the longitudinal elastic force generated thereby are linearly changed; and the combination of the two and the supporting force provided by the curve groove make the elastic force acting on the sliding block and the displacement of the sliding block have a nonlinear relationship.

[0040] Further, the nonlinear damping device further comprises a damper 8 arranged in the longitudinal direction, one end of the damper 8 is connected to the frame, and the other end is connected to the sliding block 4. The damper is used to provide a damping force in the longitudinal direction, and the damping coefficient of the damper is c.

[0041] Preferably, the number of the damper and the longitudinal linear expansion component 7 can be multiple. Further, in this embodiment, the longitudinal linear expansion component 7 is a longitudinal linear spring.

[0042] Referring to Figure 1 In this embodiment, the frame comprises a frame bottom plate 1 and a frame side plate 2, both ends of the frame bottom plate 1 in the longitudinal direction are provided with the frame side plate 2, and the longitudinal sliding rail 3 is arranged on the frame bottom plate 1 and abuts against the two frame side plates 2 at both ends.

[0043] Referring to Figure 2 In this embodiment, the frame is provided with a guide plate 5 on both sides of the longitudinal sliding rail 3, and the guide plate 5 is provided with the guide track groove 5.1. Specifically, in this embodiment, both ends of the guide plate 5 are connected to the two frame side plates 2. Those skilled in the art can understand that Figure 2Only one kind of guide plate and guide track groove setting mode is shown, and the person skilled in the art can improve the structure setting, for example, it is also possible to make the guide plate into a guide track groove towards the side of the longitudinal sliding rail 3, in which case the end of the transverse linear extension assembly slides along the side of the guide plate.

[0044] Referring to Figure 3 and Figure 4 , the transverse extension assembly 6 comprises a movable part and a transverse linear spring 6.6, one end of the transverse linear spring 6.6 is connected to the sliding block 4, and the other end is provided with a movable part; the movable part is arranged in the guide track groove 5.1 to realize the movement of the movable part along the guide track groove 5.1, and the transverse linear spring is stretched and contracted according to the change of the guide track groove.

[0045] Further, the movable part comprises a connecting seat and a roller 6.2, the connecting seat is connected with the end of the transverse linear spring, and the roller 6.2 is rotatably arranged on the connecting seat, and the roller 6.2 is arranged in the guide track groove 5.1.

[0046] Specifically, the connecting seat in the embodiment comprises a first end plate 6.4 and two connecting plates 6.3, one side of the first end plate is fixedly connected with the transverse linear spring 6.6, and the other side is provided with two parallel connecting plates 6.3, and the two ends of the roller 6.2 are rotatably connected with the two connecting plates respectively; the roller 6.2 is arranged in the guide track groove, and the two connecting plates are located on the upper and lower sides of the guide plate respectively, and the upper end face and the lower end face of the roller protrude from the upper surface and the lower surface of the guide plate respectively, so as to avoid unnecessary friction resistance between the connecting plate and the guide plate.

[0047] Referring to Figure 3 and Figure 4 , the transverse extension assembly 6 further comprises a hollow tube 6.1, one end of the hollow tube 6.1 is fixedly arranged on the sliding block 4, and the end of the transverse linear spring 6.6 is arranged on the sliding block through a second end plate 6.5, and the transverse linear spring and the second end plate 6.5 are arranged in the hollow tube 6.1, the transverse linear spring 6.6 can freely stretch and contract in the transverse direction in the hollow tube 6.1, and the hollow tube 6.1 makes the transverse linear spring 6.6 only stretch or compress in the direction perpendicular to the vibration of the sliding block 4.

[0048] Further, the first end plate 6.4 in the embodiment is also located in the hollow tube and moves in the hollow tube along with the stretching and contraction of the transverse linear spring 6.6.

[0049] Specifically, a gap is left between the inner wall of the hollow tube 6.1 and the outer periphery of the transverse linear spring 6.6, preferably a gap of 1-10mm, so that the transverse linear spring can freely stretch and contract in the hollow tube.

[0050] Further, in order to avoid excessive friction force affecting the entire vibration system, the contact surface of the sliding block 4 and the longitudinal sliding rail 3, the contact surface of the roller 6.2 and the guide track groove 5.1, and the contact surface of the first end plate 6.4 and the hollow tube 6.1 should be kept smooth.

[0051] Specifically, the trajectory line of the curve groove segment one 5.1.1 in the embodiment is:

[0052] f(u)=au 2 -bu(u<0) (1),

[0053] The trajectory line of the curve groove segment two 5.1.2 is:

[0054] f(u)=au 2 +bu(u>0) (2),

[0055] Wherein, a is the coefficient of the quadratic term, b is the coefficient of the linear term, u is the coordinate value on the longitudinal coordinate axis, and f(u) is the coordinate value on the transverse coordinate axis; u=0 is the intersection of the curve groove segment one and the curve groove segment two, which is the equilibrium position. At this position, the transverse linear spring and the longitudinal linear expansion piece (i.e. the longitudinal linear spring) do not stretch or compress, and no elastic force is generated.

[0056] Referring to Figure 5 and Figure 6 When the sliding block 4 is in a static state, the transverse linear spring 6.6 and the longitudinal linear expansion piece 7 do not deform and do not generate elastic force. At this time, the sliding block 4 is in the equilibrium position (i.e. the static state). When the sliding block 4 is in a vibration state, the transverse linear spring 6.6 and the longitudinal linear expansion piece 7 stretch or compress, and the sliding block 4 is subjected to an elastic restoring force directed to the equilibrium position. The specific principle analysis is as follows:

[0057] A coordinate system is established, the sliding block 4 is limited to reciprocate in the direction of the u-axis, and the curve groove segment one and the curve groove segment two are symmetrical about the v-axis. The mass of the sliding block 4 is m.

[0058] When the roller 6.2 moves to the position as shown in Figure 6 , the slope of the tangent line at the position of the roller is:

[0059]

[0060] The force in the v-direction on a single roller 6.2 is:

[0061] F v =k l1 ·f(u) (4),

[0062] Let the reaction force of the inner wall of the guiding track groove 5.1 to the roller 6.2 be R, then the relationship between the component forces of the single roller 6.2 in the u direction and the v direction and the reaction force is:

[0063]

[0064] Therefore, the relationship between the component forces of the single roller 6.2 in the u direction and the v direction can be expressed as:

[0065] F u =F v ·tanθ (6),

[0066] Therefore, the resultant force of the sliding block 4 in the vibration process is obtained by combining the nonlinear restoring force transmitted by the movement of the rollers 6.2 on both sides and the linear restoring force generated by the longitudinal linear expansion component 7:

[0067]

[0068] Therefore, the polynomial nonlinear restoring force of the longitudinal linear expansion component and the transverse linear expansion assembly acting on the sliding block 4 is obtained:

[0069] F m =k1u+k2u·|u|+k3u 3 (8),

[0070] F m is the restoring force of the sliding block; k1, k2 and k3 are the linear stiffness coefficient, the square stiffness coefficient and the cubic stiffness coefficient of the nonlinear damping system, respectively;

[0071] The relationship between the linear, square and cubic stiffness coefficients of the system and the geometric parameters of the guiding track groove 5.1 and the stiffness coefficients of the transverse linear spring 6.6 and the longitudinal linear expansion component 7 (i.e. the longitudinal linear spring) is as follows:

[0072] k1=2k l1 b 2 +k l2 (9),

[0073] k2=6k l1 ab (10),

[0074] k3=4k l1 a 2 (11),

[0075] where k l1 and k l2 are the stiffness coefficients of the transverse linear expansion assembly and the longitudinal linear expansion component, respectively.

[0076] Therefore, the damping device provided by the embodiment can realize efficient damping in a wide frequency and wide amplitude range, effectively overcome the defects of the prior art, and has great practical value.

[0077] The technical scheme of the present application has the following effects:

[0078] The nonlinear damping device with a polynomial stiffness form of the embodiment provides a stable and reliable sliding track for the roller 6.2 by arranging the guide track groove in the guide plate 5. The polynomial stiffness accurately containing linear, square and cubic terms is realized by the sliding of the roller 6.2 in the guide track groove 5.1. The coupling relationship between the linear stiffness coefficient and the square stiffness coefficient is eliminated by adding the longitudinal linear expansion piece 7. The linear stiffness coefficient, the square stiffness coefficient and the cubic stiffness coefficient can be independently set, which can better meet the actual damping requirements. Efficient damping in a wide frequency and wide amplitude range can be realized, the defects of the prior art are effectively overcome, and the damping device has great practical value.

[0079] The above description is only preferred embodiments of the present application and is not used to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A nonlinear vibration damping device, characterized in that, The system includes a frame, a sliding block (4), a transverse linear telescopic component (6), and a longitudinal linear telescopic component (7). The frame is provided with a longitudinal slide rail (3), and the sliding block (4) is slidably disposed on the longitudinal slide rail (3). One end of the longitudinal linear telescopic component (7) is connected to the frame, and the other end is connected to the sliding block (4). The frame is symmetrically provided with guide track grooves (5.1) on both sides of the longitudinal slide rail (3). The sliding block (4) is symmetrically provided with transverse linear telescopic components (6) on both sides in the longitudinal direction. One end of the transverse linear telescopic component is connected to the sliding block (4), and the other end is movably disposed in the guide track groove. The guide track groove (5.1) includes a first curved groove segment (5.1.1) and a second curved groove segment (5.1.2) symmetrically disposed in the transverse direction. The trajectory lines of the first curved groove segment and the second curved groove segment are both quadratic functions. The trajectory of the first curved groove segment (5.1.1) is as follows: , The trajectory of the second curved groove segment (5.1.2) is as follows: , in, The coefficient of the quadratic term, The coefficient of the linear term, These are the coordinate values ​​on the vertical axis. These are the coordinate values ​​on the horizontal coordinate axis; It is the intersection of curved groove segment one and curved groove segment two; The longitudinal linear telescopic component (7) is a longitudinal linear spring; the transverse linear telescopic assembly (6) includes a transverse linear spring (6.6).

2. The nonlinear vibration reduction device according to claim 1, characterized in that, The restoring forces exerted by the longitudinal linear telescopic component and the transverse linear telescopic assembly on the sliding block (4) are: ， The restoring force acting on the slider. k 1. k 2 and k 3 represents the linear stiffness coefficient, square stiffness coefficient, and cubic stiffness coefficient of the nonlinear vibration reduction system, where: , , ; and These are the stiffness coefficients of the transverse linear expansion joint and the longitudinal linear expansion joint, respectively.

3. The nonlinear vibration reduction device according to claim 1, characterized in that, The frame has guide plates (5) on both sides of the longitudinal slide rail (3), and the guide plates (5) have guide track grooves (5.1).

4. The nonlinear vibration damping device according to claim 1, characterized in that, It also includes a damper (8) arranged longitudinally, one end of which is connected to the frame and the other end of which is connected to the sliding block (4).

5. The nonlinear vibration damping device according to claim 1, characterized in that, The transverse linear telescopic assembly (6) also includes a movable part, one end of the transverse linear spring (6.6) is connected to the sliding block (4), and the other end is provided with a movable part; the movable part is provided in the guide track groove (5.1) to move along the guide track groove (5.1).

6. The nonlinear vibration damping device according to claim 5, characterized in that, The movable part includes a connecting seat and a roller (6.2). The connecting seat is connected to the end of a transverse linear spring. The roller (6.2) is rotatably mounted on the connecting seat and is located in a guide track groove (5.1).

7. The nonlinear vibration reduction device according to claim 6, characterized in that, The transverse linear telescopic assembly (6) also includes a hollow tube (6.1), one end of which is fixedly mounted on a sliding block (4), and a transverse linear spring (6.6) is disposed inside the hollow tube (6.1), which can freely extend and retract laterally inside the hollow tube (6.1).

8. The nonlinear vibration damping device according to claim 7, characterized in that, A gap is left between the inner wall of the hollow tube (6.1) and the outer periphery of the transverse linear spring (6.6).

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