Parameter-adaptive displacement amplification type Maxwell inertial damper

Abstract

The invention belongs to the technical field of vibration reduction, and particularly discloses a parameter-adaptive displacement amplification type Maxwell inertial damper which comprises a Maxwell unit and a displacement amplification inertial unit, and the Maxwell unit comprises a spring unit and a viscous damping unit which are connected in series; the displacement amplification inertial mass unit comprises a displacement amplification assembly and a mass block, one side of the displacement amplification assembly is connected with the spring unit, and the other side is provided with the mass block; the displacement amplification assembly is used for amplifying the movement of the spring unit and transmitting the amplified movement to the mass block. When the damper generates displacement under the action of an external load, the upper part of the Maxwell unit generates displacement, and the displacement is transmitted to the mass block after being amplified by the displacement amplification assembly, so that an equivalent mass effect of several times to dozens of times is generated, and the inertial damping force of the whole system is improved; and meanwhile, the inertial unit and the Maxwell unit enable equivalent parameters of the damper to change along with the change of the vibration frequency, and the self-adaptive characteristic is brought to the passive damper.

Description

Technical Field

[0001] This invention belongs to the field of vibration reduction technology, and more specifically, relates to a parameter-adaptive displacement-amplified Maxwell mass damper. Background Technology

[0002] In the field of structural vibration control, the introduction of inertial mass units can effectively improve the performance of dampers. In particular, for structures that require multimodal vibration control, the introduction of inertial mass units can effectively extend the control frequency range of the damper.

[0003] However, conventional inertial mass dampers currently have two major problems: First, the structure of commonly used inertial mass units is highly complex. Currently, ball screws and similar structures are commonly used as inertial mass units. These devices achieve effective inertial effects by converting rotational and translational motion to rotate components such as flywheels. However, this type of structure still faces several engineering challenges. Firstly, ball screw mechanisms are typically complex in structure and have a large number of parts, leading to high processing difficulty, high manufacturing costs, and difficult maintenance. Secondly, although rolling friction can improve energy efficiency, the balls are prone to wear or derailment during long-term operation, significantly reducing reliability and service life. In addition, the lubrication and maintenance requirements for ball components are high, and problems such as jamming and increased backlash occur during long-term use, affecting the stability of system performance.

[0004] Secondly, conventional passive dampers have fixed parameters, making it difficult to adapt to situations with a wide range of controlled frequencies. Because of their fixed parameters, conventional passive dampers cannot achieve adaptive changes in equivalent parameters with varying vibration frequencies. However, practical engineering often requires consideration of wideband and multimodal vibration control of structures, which is beyond the capabilities of dampers with fixed parameters. Summary of the Invention

[0005] In view of the above-mentioned defects or improvement needs of the existing technology, the present invention provides a displacement amplification Maxwell inertial mass damper with adaptive parameters. Its purpose is to construct a simpler and more reliable inertial mass unit and achieve adaptive damper equivalent parameters.

[0006] To achieve the above objectives, this invention proposes a parameter-adaptive displacement-amplified Maxwell mass damper, comprising Maxwell elements and displacement-amplified mass elements, wherein: The Maxwell unit includes a spring unit and a viscous damping unit connected in series; The displacement amplification inertial mass unit includes a displacement amplification component and a mass block. One side of the displacement amplification component is connected to the spring unit, and the other side is equipped with the mass block. The displacement amplification component is used to amplify the movement of the spring unit and transmit it to the mass block.

[0007] As a further preferred embodiment, the spring unit includes an ear plate and a spring, with an upper connector and a lower connector fixed to the upper and lower ends of the spring, respectively, and the ear plate fixed to the upper connector.

[0008] As a further preferred embodiment, the viscous damping unit includes a piston rod and a viscous damper, with one end of the piston rod fixed to the lower connector and the other end movably mounted in the viscous damper.

[0009] As a further preferred embodiment, both the viscous damper and the displacement amplification assembly are fixed on the base.

[0010] As a further preferred embodiment, the displacement amplification component employs a hinged connecting rod.

[0011] As a further preferred embodiment, the displacement amplification assembly includes four connecting rods, wherein the first connecting rod has its first end fixed to the base and its last end hinged to the first end of the second connecting rod, and a mass block is fixed to the last end of the second connecting rod; the third connecting rod has its first end hinged to the second connecting rod and its last end hinged to the first end of the fourth connecting rod, and the last end of the fourth connecting rod is fixed to the upper connecting member.

[0012] As a further preferred embodiment, the hinge position of the third connecting rod and the second connecting rod is closer to the side of the first connecting rod.

[0013] As a further preferred embodiment, the ear plate is used to connect to the controlled structure.

[0014] In summary, compared with the prior art, the above-described technical solutions conceived by this invention mainly possess the following technical advantages: 1. This invention replaces the ball screw inertial mass structure with a displacement amplification inertial mass unit. The ball screw structure uses small metal balls arranged in the thread as the transmission structure. This structure requires high machining precision, and the friction of the inertial mass unit increases with wear of the balls. In contrast, this invention uses a displacement amplification structure combined with a mass block, making wear negligible. Furthermore, it avoids any complex mechanisms that convert translational motion into rotation, thus significantly reducing friction. This invention greatly simplifies the structure of the inertial mass unit, achieving a simpler and more reliable unit, and reducing production and maintenance costs.

[0015] 2. When the damper is subjected to an external load and undergoes displacement, the upper part of the Maxwell unit also experiences displacement. This displacement is amplified through lever transmission and transmitted to the mass block, resulting in an equivalent mass effect several to tens of times greater. The displacement amplification component designed in this invention effectively amplifies the mass effect of the mass block. This structure can provide a larger inertial force, increasing the inertial-mass damping force of the entire system and further improving energy dissipation efficiency. Simultaneously, the inertial-mass unit, together with the Maxwell unit, causes the equivalent parameters of the damper to change with the vibration frequency, bringing adaptive characteristics to the passive damper. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of a displacement-amplified Maxwell inertial-mass damper with adaptive parameters according to an embodiment of the present invention. Figure 2 This is a test diagram of a prototype of a displacement-amplified Maxwell inertial-mass damper with adaptive parameters according to an embodiment of the present invention. Figure 3 This is a force-displacement hysteresis curve of an embodiment of the present invention under 0.25Hz excitation; Figure 4 This is a force-velocity hysteresis curve of an embodiment of the present invention under 0.25Hz excitation; Figure 5 This is a force-displacement hysteresis curve of an embodiment of the present invention under 0.5Hz excitation; Figure 6 This is a force-velocity hysteresis curve of an embodiment of the present invention under 0.5Hz excitation; Figure 7 This is a graph showing the variation of equivalent stiffness with vibration frequency in an embodiment of the present invention. Figure 8 This is a graph showing the variation of equivalent damping with vibration frequency in an embodiment of the present invention.

[0017] In all the accompanying drawings, the same reference numerals are used to denote the same elements or structures, wherein: 1-ear plate, 2-connector, 3-spring, 4-displacement amplification assembly, 5-mass block, 6-piston rod, 7-viscous damper, 8-base. Detailed Implementation

[0018] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention. Furthermore, the technical features involved in the various embodiments of this invention described below can be combined with each other as long as they do not conflict with each other.

[0019] This invention provides a parameter-adaptive displacement-amplified Maxwell inertial-mass damper, such as... Figure 1 As shown, it includes parallel Maxwell units and displacement-amplified inertial mass units, wherein: The Maxwell unit consists of spring units and viscous damping units connected in series.

[0020] The spring unit includes a lug 1, a connector 2, and a spring 3. The connector 2 includes an upper connector and a lower connector, and the spring 3 is fixed between the upper connector and the lower connector. The lug 1 is fixed on the upper connector and is generally connected to the controlled structure.

[0021] The viscous damping unit includes a piston rod 6, a viscous damper 7, and a base 8. One end of the piston rod 6 is fixed to the lower connector, and the other end is connected to the viscous damper 7. The viscous damper 7 is fixed to the base 8.

[0022] The displacement amplification inertial mass unit includes a displacement amplification component 4 and a mass block 5. The upper part of the displacement amplification component 4 is fixed on the upper connector as the input end of the displacement, and the lower part is fixed on the base 8 as a support. The mass block 5 is fixed at the tail end of the displacement amplification component 4.

[0023] When the damper generates relative displacement, the ear plate 1 moves, causing the spring 3 to deform, which in turn drives the piston rod 6, allowing the liquid (such as silicone oil) in the viscous damper 7 to pass through the piston hole. At the same time, the movement of the ear plate 1 is also amplified by the displacement amplification component 4 and transmitted to the mass block 5. The displacement amplification component 4, through the displacement amplification mechanism, makes the movement amplitude of the mass block 5 fixed at the end much greater than the displacement amplitude generated at the ear plate 1, thereby generating a mass effect much greater than the mass of the mass block 5 itself. This makes the equivalent mass effect of the damper dozens of times the mass of the mass block 5 itself.

[0024] Furthermore, the displacement amplification component 4 forms a lever through connecting rods, and the internal connections are hinged, allowing the internal connecting rods to rotate relative to each other. Specifically, the displacement amplification component 4 includes four connecting rods. The first connecting rod's head is vertically fixed to the base 8, and its tail is hinged to the head of the second connecting rod, with the mass block 5 fixed to the tail of the second connecting rod. The third connecting rod's head is hinged to the second connecting rod, and its tail is hinged to the head of the fourth connecting rod, with the tail of the fourth connecting rod fixed to the upper connecting member. The hinge position A between the third and second connecting rods is closer to the first connecting rod and further away from the mass block. The displacement amplification coefficient can be changed by adjusting the hinge position A, and its specific position can be determined according to actual needs.

[0025] like Figure 2 The prototype test diagram shown illustrates a cyclic loading test performed on a displacement-amplified Maxwell inertial-mass damper prototype with adaptive test parameters, using either a fixed displacement or a fixed velocity. When the upper part of the damper experiences an upward or downward displacement, spring 3 first undergoes tensile or compressive deformation, transmitting this force to the viscous damper 7 via piston rod 6. Simultaneously, the displacement amplification assembly 4, fixed to the connector, amplifies the displacement of the damper and transmits it to the mass block 5. In this example, the displacement direction of mass block 5 is consistent with the displacement direction of ear plate 1, but this may differ depending on the lever transmission mechanism used. Figure 2 It is clear from the data that the upper part of the damper has a very small displacement, while the motion of mass block 5 is very large.

[0026] Figures 3 to 6The test results of the prototype hysteresis curves under different loading frequencies were compared with the theoretical values. It can be clearly seen that the experimental data and theoretical predictions are in good agreement, which strongly proves that the displacement amplification inertial mass unit mentioned above can effectively reduce the internal friction of the damper.

[0027] Figure 7 and Figure 8 The study presents the variation of the prototype's equivalent parameters with the test frequency, which closely matches theoretical predictions. It is evident that within 1 Hz, the equivalent stiffness of the parameter-adaptive displacement-amplified Maxwell inertial-mass damper continuously increases with increasing vibration frequency, while its equivalent damping continuously decreases. This trend of "high damping at low frequencies and low damping at high frequencies" is highly beneficial for the multimodal vibration control needs of various structures.

[0028] Those skilled in the art will readily understand that the above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A parameter-adaptive displacement-amplified Maxwell mass-inertia damper, characterized in that, Includes Maxwell elements and displacement-amplified inertial mass elements, wherein: The Maxwell unit includes a spring unit and a viscous damping unit connected in series; The displacement amplification inertial mass unit includes a displacement amplification component (4) and a mass block (5). One side of the displacement amplification component (4) is connected to the spring unit, and the other side is equipped with the mass block (5). The displacement amplification component (4) is used to amplify the movement of the spring unit and transmit it to the mass block (5).

2. The parameter-adaptive displacement-amplified Maxwell inertial-mass damper as described in claim 1, characterized in that, The spring unit includes an ear plate (1) and a spring (3). The upper and lower ends of the spring (3) are respectively fixed with an upper connector and a lower connector. The ear plate (1) is fixed on the upper connector.

3. The parameter-adaptive displacement-amplified Maxwell inertial-mass damper as described in claim 2, characterized in that, The viscous damping unit includes a piston rod (6) and a viscous damper (7). One end of the piston rod (6) is fixed on the lower connector, and the other end is movably installed in the viscous damper (7).

4. The parameter-adaptive displacement-amplified Maxwell inertial-mass damper as described in claim 3, characterized in that, The viscous damper (7) and the displacement amplification assembly (4) are both fixed on the base (8).

5. The parameter-adaptive displacement-amplified Maxwell inertial-mass damper as described in claim 4, characterized in that, The displacement amplification component (4) uses a hinged connecting rod.

6. The parameter-adaptive displacement-amplified Maxwell inertial-mass damper as described in claim 4, characterized in that, The displacement amplification component (4) includes four connecting rods, wherein the first connecting rod is fixed at the beginning of the base (8) and the end of the first connecting rod is hinged to the beginning of the second connecting rod, and the end of the second connecting rod is fixed to the mass block (5); the third connecting rod is hinged at the beginning of the second connecting rod and the end of the third connecting rod is hinged to the beginning of the fourth connecting rod, and the end of the fourth connecting rod is fixed to the upper connecting member.

7. The parameter-adaptive displacement-amplified Maxwell inertial-mass damper as described in claim 6, characterized in that, The hinge position of the third connecting rod and the second connecting rod is close to the side of the first connecting rod.

8. The parameter-adaptive displacement-amplified Maxwell inertial-mass damper as described in any one of claims 1-7, characterized in that, The ear plate (1) is used to connect the controlled structure.

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