Variable-frequency hydraulic type inerter vibration double-control system

Abstract

The invention relates to a variable-frequency hydraulic type inerter vibration double-control system. The variable-frequency hydraulic type inerter vibration double-control system comprises a variable-stiffness unit, a displacement triggering unit, a linkage unit and an inerter damping unit. The variable stiffness unit comprises a spring group comprising a long spring and a short spring; the displacement triggering unit comprises a displacement boundary module and a triggering plate between which a triggering gap is preset; the inerter damping unit comprises a hydraulic cylinder filled with viscous damping liquid and a spiral pipe. A piston is arranged in the hydraulic cylinder in a sliding mode and provided with a damping hole. When the relative displacement is smaller than the trigger gap, only the long spring provides elastic restoring force, and the viscous damping fluid flows through the damping hole and the spiral pipe to generate damping force and inertia force; and when the relative displacement exceeds the triggering gap, the triggering plate drives the short spring to participate in work so as to provide increased elastic restoring force. The rigidity can be automatically switched according to the displacement amplitude, and wind vibration and earthquake double control is achieved.

Description

Technical Field

[0001] This invention relates to the field of vibration control and energy dissipation reduction technology for civil engineering structures, and in particular to a variable frequency hydraulic inertial-capacitive vibration dual control system. Background Technology

[0002] With the increasing prevalence of high-rise and super high-rise buildings and large-span spatial structures, the threats posed by wind-induced vibrations and seismic forces are becoming increasingly prominent. To ensure structural safety and user comfort, various passive vibration control devices have been widely researched and applied. These devices require no external energy source and dissipate or transfer the energy of structural vibrations through additional damping, stiffness, or mass elements, thereby mitigating the dynamic response of the main structure. In passive control technology, inertial capacitive elements have attracted attention because they can provide apparent inertial forces far exceeding their physical mass. Hydraulic inertial capacitive elements, as one implementation, convert the linear motion of the structure into the rotational motion of the fluid within a closed loop, thus generating a significant inertial effect and typically also possessing viscous damping characteristics. Such devices exhibit good energy dissipation efficiency under a single type of dynamic load.

[0003] However, building structures may encounter different hazardous loads with vastly different characteristics throughout their life cycle. Wind-induced vibration typically induces high-frequency, low-amplitude reciprocating motions in the structure. In this case, the control device needs to provide sufficient initial stiffness to limit structural displacement and ensure normal functionality. Earthquakes, on the other hand, typically induce low-frequency, high-amplitude vibrations in the structure. In this case, the control device needs to have sufficient deformation capacity and energy dissipation capacity to absorb the huge seismic input energy and prevent damage to the main structure. In existing passive control devices, the stiffness, damping, and other performance parameters are usually fixed during design and manufacturing. Devices with single performance parameters are difficult to simultaneously optimize and adapt to wind-induced vibration and earthquakes, two conditions with almost opposite requirements in terms of frequency and displacement amplitude. Installing two separate control systems for wind-induced vibration and earthquakes would significantly increase cost and design complexity; if a compromise design is adopted, it is difficult to achieve optimal control performance under either condition. Summary of the Invention

[0004] Therefore, it is necessary to provide a variable frequency hydraulic inertial capacitive vibration dual control system that can adaptively adjust its dynamic characteristics according to the amplitude or frequency characteristics of external excitation in order to effectively cope with both wind-induced vibration and earthquake disasters.

[0005] This invention provides a variable frequency hydraulic inertial-capacitive vibration dual control system, including a first connector and a second connector for connecting a building structure, and further including a variable stiffness unit, a displacement triggering unit, a linkage unit, and an inertial-capacitive damping unit arranged in series. The variable stiffness unit includes an end plate and a set of springs, the spring set including a long spring and at least one short spring, one end of all springs being fixed to the end plate, and the free end length of the long spring being greater than the free end length of the short spring. The displacement triggering unit includes a displacement boundary module fixedly connected to the free end of the short spring, and a trigger plate fixedly connected to the free end of the long spring and housed within the displacement boundary module, with a pre-set trigger gap between the trigger plate and the inner wall of the displacement boundary module. The linkage unit includes a piston rod and a piston fixed to one end of the piston rod. The end plate is fixedly connected to the trigger plate; the inertial-capacitive damping unit includes a sealed liquid cylinder filled with viscous damping fluid, and a spiral tube with both ends communicating with the inside of the liquid cylinder and wound around its outside. The piston is sealed and slidably disposed in the liquid cylinder and divides its inner cavity into two working chambers. The piston has a damping hole connecting the two working chambers; the first connecting piece is connected to the end plate, and the second connecting piece is connected to the liquid cylinder; wherein, when the relative displacement between the first connecting piece and the second connecting piece is less than the trigger gap, only the long spring provides elastic restoring force, and at the same time, the piston is driven to move through the linkage unit, so that the viscous damping fluid flows through the damping hole to generate damping force, and part of it flows into the spiral tube to generate inertial force; when the relative displacement reaches and exceeds the trigger gap, the trigger plate contacts the displacement boundary module and drives the short spring to participate in the work to provide increased elastic restoring force.

[0006] In one embodiment, the spring assembly includes a wind-resistant spring as a long spring and two shock-resistant springs as short springs, the two shock-resistant springs being of the same length and arranged symmetrically about the center of the end plate.

[0007] In one embodiment, the stiffness of the wind-resistant spring is determined based on the stiffness required for the main control frequency of the system under wind-resistant conditions; the sum of the stiffnesses of the two seismic springs is determined based on the difference between the stiffness required for the main control frequency of the system under seismic conditions and the stiffness of the wind-resistant spring.

[0008] In one embodiment, the displacement boundary module is a cylindrical structure with openings at the top and bottom; the trigger plate is a circular plate with a diameter smaller than the inner diameter of the displacement boundary module to form an annular trigger gap, and when the system is in a balanced position, the trigger plate is located at the center of the displacement boundary module along its axial direction.

[0009] In one embodiment, when the relative displacement reaches and exceeds the trigger gap, the trigger plate contacts the inner wall of the end of the displacement boundary module, driving the displacement boundary module to compress or stretch the short spring, so that the short spring and the long spring together provide elastic restoring force.

[0010] In one embodiment, the piston has a plurality of through holes that serve as damping holes evenly distributed along its circumference.

[0011] In one embodiment, the ratio of the diameter of the helical tube to the diameter of the through hole is determined based on the ratio of the required inertial force to the viscous damping force of the system.

[0012] In one embodiment, the inertial-capacitive damping unit further includes a regulating valve disposed between the spiral tube and the liquid cylinder. The end of the spiral tube is connected to the interior of the liquid cylinder through the regulating valve. The regulating valve is a bidirectional valve that can control the flow rate of the viscous damping liquid flowing through the spiral tube by adjusting the opening degree.

[0013] In one embodiment, the cylinder includes an outer cylinder, a viscous damping fluid filled in the outer cylinder, and a sealing ring for sealing the piston rod. The side wall of the outer cylinder is provided with interfaces that communicate with the beginning and end of the spiral tube, respectively.

[0014] In one embodiment, the first connector is a first lug fixedly connected to the end plate, and the second connector is a second lug fixedly connected to the hydraulic cylinder; the center of the end plate, the center of the long spring, the center of the displacement boundary module, the center of the trigger plate, the center of the piston rod, the center of the piston, the center of the hydraulic cylinder, and the center of the connection surface between the second connector and the hydraulic cylinder are located on the same straight line.

[0015] The aforementioned variable frequency hydraulic inertial-capacitive vibration dual control system mechanically couples a variable stiffness unit containing long and short springs with a displacement triggering unit containing a displacement boundary module and a trigger plate. This allows the system to passively and automatically distinguish between small-displacement wind-induced vibration and large-displacement seismic vibration based on the direct physical signal of the building structure's own vibration displacement amplitude. Under wind-induced vibration, if the relative displacement does not reach the preset trigger gap, only the long spring provides the initial stiffness required to match the high-frequency small displacement. Simultaneously, the linkage unit drives the inertial-capacitive damping unit, and the viscous damping fluid flows through the piston damping orifice to generate damping force and partially flows into the helical tube to generate inertial force, jointly suppressing the micro-wind vibration of the structure. When the relative displacement exceeds the trigger gap under seismic action, the trigger plate and the displacement triggering unit... The boundary module contacts, mechanically forcing short springs to work in parallel, thereby significantly increasing the overall stiffness of the system to cope with large displacement requirements. At this time, the piston speed and acceleration driven by the linkage unit also change, and then the damping and inertial force output of the system are nonlinearly adjusted by redistributing the flow of viscous damping fluid in the damping orifice and helical tube. Finally, this scheme does not require external energy or active control, and only uses a purely mechanical structure to achieve passive and adaptive switching of the system's stiffness and dynamic response characteristics based on disaster load characteristics. This allows a single device to cope with two completely different working conditions, wind vibration and earthquake, in an optimized state, solving the problem that traditional passive damping devices have fixed parameters and cannot take into account the adaptability to multiple disaster conditions. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0017] Figure 1 This is a schematic diagram of the overall structure of the variable frequency hydraulic inertial-capacitive vibration dual control system according to an embodiment of the present invention; Figure 2 This is a cross-sectional structural schematic diagram of the variable frequency hydraulic inertial-capacitive vibration dual control system according to an embodiment of the present invention; Figure 3 This is a schematic diagram of the structure of the variable stiffness unit according to an embodiment of the present invention; Figure 4 This is a schematic diagram of the structure of the displacement triggering unit and the linkage unit in an embodiment of the present invention; Figure 5 This is a schematic diagram of the piston structure according to an embodiment of the present invention; Figure 6 This is a schematic diagram of the structure of the inertial-capacitive damping unit according to an embodiment of the present invention; Figure 7 This is a schematic diagram of the structure of the regulating valve according to an embodiment of the present invention.

[0018] Figure label: 1. First connecting piece; 2. End plate; 3. Spring assembly; 4. Displacement triggering unit; 5. Linkage unit; 6. Spiral tube; 7. Hydraulic cylinder; 8. Adjusting valve; 9. Second connecting piece; 31. Anti-vibration spring; 32. Anti-wind spring; 33. Anti-vibration spring; 41. Displacement boundary module; 42. Trigger plate; 51. Piston rod; 52. Piston; 53. Through hole; 71. Outer cylinder; 72. Viscous damping fluid; 73. Sealing ring; 81. Adjusting knob; 82. Valve. Detailed Implementation

[0019] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0020] It should be noted that when a component is referred to as being "fixed to" or "set on" another component, it can be directly on the other component or there may be an intermediate component. When a component is considered to be "connected to" another component, it can be directly connected to the other component or there may be an intermediate component present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used in this specification are for illustrative purposes only and do not represent the only possible implementation.

[0021] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0022] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature and the second feature are in indirect contact through an intermediate medium. Furthermore, "above," "over," and "on top" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0023] Unless otherwise defined, all technical and scientific terms used in this specification have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used in this specification includes any and all combinations of one or more of the associated listed items.

[0024] The following is combined Figures 1-7 The present invention describes a variable frequency hydraulic inertial-capacitive vibration dual control system.

[0025] like Figure 1 and Figure 2 As shown, in one embodiment, a variable frequency hydraulic inertial-capacitive vibration dual control system includes a first connector 1 and a second connector 9 for connecting a building structure, and also includes a variable stiffness unit, a displacement triggering unit 4, a linkage unit 5 and an inertial-capacitive damping unit arranged in series.

[0026] The first connector 1 and the second connector 9 are respectively located at both ends of the system, used to install and fix the entire system at the inter-story displacement points of the building structure or other locations requiring vibration damping control. The so-called series connection means that the excitation energy input from the first connector 1 flows sequentially through the variable stiffness unit for stiffness adjustment and energy storage, passes through the displacement triggering unit 4 for state judgment, and is then transmitted through the linkage unit 5 to the inertial-capacitive damping unit for energy dissipation and inertial control. Finally, the second connector 9 outputs a balancing force. The units are connected end-to-end in the mechanical transmission path, together forming a complete passive control loop.

[0027] The variable stiffness unit includes an end plate 2 and a set of springs 3. The springs 3 include a long spring and at least one short spring. One end of all the springs is fixed to the end plate 2, and the free end length of the long spring is greater than the free end length of the short spring.

[0028] End plate 2 serves as the base for the variable stiffness unit, providing a mounting foundation for spring assembly 3. Both the long and short springs are helical springs, where the free end length refers to the natural length of the spring when not subjected to external force. Since the free end length of the long spring is greater than that of the short spring, the long spring will extend further when the system is in equilibrium. This length difference provides the structural basis for the subsequent displacement triggering mechanism. It should be understood that although this embodiment shows spring assembly 3 containing one long spring and two short springs, in other embodiments, the number of short springs can be either only one or more than two, as long as the condition that the free end length of the long spring is greater than that of the short spring is met, the function of graded stiffness can be achieved.

[0029] The displacement triggering unit 4 includes a displacement boundary module 41 fixedly connected to the free end of the short spring, and a trigger plate 42 fixedly connected to the free end of the long spring and housed within the displacement boundary module 41. A trigger gap is preset between the trigger plate 42 and the inner wall of the displacement boundary module 41.

[0030] Specifically, the displacement boundary module 41 forms a limiting space, and the trigger plate 42 is located inside this space and can move with the extension and retraction of the long spring. The existence of the trigger gap allows the trigger plate 42 to move freely within a certain displacement range without contacting the displacement boundary module 41. This structural design cleverly transforms the displacement amplitude into a contact state: when the displacement is small, the trigger plate 42 is suspended and the short spring does not participate in the force; when the displacement is large, the trigger plate 42 touches the boundary, and the short spring intervenes to bear the force.

[0031] The linkage unit 5 includes a piston rod 51 and a piston 52 fixed to one end of it. The other end of the piston rod 51 is fixedly connected to the trigger plate 42.

[0032] Specifically, the piston rod 51, as a force transmission component, transmits the mechanical motion of the variable stiffness unit and the displacement triggering unit 4 to the inertial-capacitive damping unit. When the trigger plate 42 moves with the long spring, it drives the piston 52 to move synchronously within the hydraulic cylinder 7 via the piston rod 51.

[0033] The inertial-capacitive damping unit includes a sealed liquid cylinder 7 filled with viscous damping fluid 72, and a spiral tube 6 with both ends communicating with the inside of the liquid cylinder 7 and wound around its outside. The piston 52 is sealed and slidably disposed in the liquid cylinder 7 and its inner cavity is divided into two working chambers. The piston 52 has a damping hole that connects the two working chambers.

[0034] The cylinder 7 is filled with viscous damping fluid 72, and the piston 52 divides the interior of the cylinder 7 into two independent chambers, left and right. When the piston 52 moves, it squeezes the fluid in one chamber, causing it to flow through the damping orifice to the other chamber, while some fluid enters the spiral tube 6. The spiral tube 6 is wound around the outside of the cylinder 7, increasing the flow path length of the fluid. Utilizing the inertial effect generated by the fluid rotating and flowing inside the spiral tube, it achieves inertial volume function, that is, it generates an inertial force proportional to acceleration.

[0035] The first connector 1 is connected to the end plate 2, and the second connector 9 is connected to the hydraulic cylinder 7.

[0036] Specifically, the first connector 1 is fixed on the end plate 2, and the second connector 9 is fixed on the bottom or side of the hydraulic cylinder 7, so that the external excitation can directly act on the variable stiffness unit, and the damping reaction force can be transmitted back to the building structure through the hydraulic cylinder 7.

[0037] The system operates under two conditions: When the relative displacement between the first connector 1 and the second connector 9 is less than the trigger gap, only the long spring provides elastic restoring force. At the same time, the piston 52 is driven to move through the linkage unit 5, so that the viscous damping fluid 72 flows through the damping hole to generate damping force, and part of it flows into the spiral tube 6 to generate inertial force.

[0038] This operating condition corresponds to a small displacement scenario caused by wind vibration. Under wind load, the building structure experiences high-frequency, small-amplitude vibrations. At this time, the relative displacement between the first connector 1 and the second connector 9 is small, and the trigger plate 42 moves within the displacement boundary module 41 without contacting the inner wall of the boundary. Therefore, the short spring is in a free state and does not provide elastic force; only the long spring is subjected to force and extension, resulting in a low stiffness characteristic of the system to match the dominant frequency under wind vibration conditions. Simultaneously, the piston 52 moves with the trigger plate 42, forcing the viscous damping fluid 72 to flow through the damping orifice and the spiral tube 6, generating viscous damping force and inertial force, effectively dissipating wind vibration energy and limiting structural swaying.

[0039] When the relative displacement reaches and exceeds the trigger gap, the trigger plate 42 contacts the displacement boundary module 41 and drives the short spring to participate in the work, so as to provide increased elastic restoring force.

[0040] This operating condition corresponds to a large displacement scenario during an earthquake. Under earthquake action, the building structure experiences low-frequency, high-amplitude vibrations. When the relative displacement amplitude increases beyond the preset trigger gap, the trigger plate 42 impacts the inner wall of the end of the displacement boundary module 41. At this point, further deformation of the long spring transmits force to the short spring connected to the displacement boundary module 41 through the contact between the trigger plate 42 and the displacement boundary module 41, forcing the short spring to compress or stretch. Simultaneously, the long and short springs work together, instantly increasing the system's equivalent stiffness. This adaptive abrupt change in stiffness matches the requirements for high stiffness and large restoring force under earthquake conditions, preventing excessive plastic deformation of the structure. The entire switching process relies entirely on the geometric contact and force transmission of the mechanical structure, requiring no external energy or sensor control. This achieves a passive, adaptive dual-control function, significantly improving the system's reliability and adaptability in multi-hazard environments.

[0041] like Figure 3 As shown, in one embodiment, the spring assembly 3 includes a wind-resistant spring 32 as a long spring and two shock-resistant springs 31 and 33 as short springs. The two shock-resistant springs 31 and 33 are of the same length and are arranged symmetrically about the center of the end plate 2.

[0042] The length of the wind-resistant spring 32 is greater than that of the anti-vibration springs 31 and 33, and this length difference constitutes the physical basis for displacement triggering. In terms of arrangement, the two anti-vibration springs 31 and 33 are centrally symmetrical about the center of the end plate 2, for example, they can be located on either side of the wind-resistant spring 32. This symmetrical arrangement is not arbitrary but is designed to ensure the balance of force transmission. When the system triggers the anti-vibration springs 31 and 33 under large displacement conditions, the symmetrical arrangement allows the compressive force to be evenly distributed between the two springs, avoiding tilting of the end plate 2 or jamming of the piston rod 51 due to eccentric loads, thereby ensuring the mechanical stability and durability of the system under long-term reciprocating vibration.

[0043] Furthermore, the stiffness of the wind-resistant spring 32 is determined based on the stiffness required for the main control frequency of the system under wind-resistant conditions; the sum of the stiffnesses of the two seismic springs 31 and 33 is determined based on the difference between the stiffness required for the main control frequency of the system under seismic conditions and the stiffness of the wind-resistant spring 32.

[0044] This embodiment achieves adaptive matching for multiple disaster conditions through differentiated stiffness design. Under wind-induced vibration conditions, the structural vibration exhibits high-frequency, small-displacement characteristics. At this time, only the wind-resistant spring 32 is active, and the system stiffness is relatively small, which can effectively match the dominant wind-induced vibration frequency of the structure and provide appropriate elastic restoring force to limit structural sway and ensure comfort. Under earthquake conditions, the structural vibration changes to low-frequency, large-displacement characteristics. When the displacement exceeds the trigger gap, the seismic springs 31 and 33 intervene. At this time, the total stiffness of the system becomes the sum of the stiffness of the wind-resistant spring 32 and the stiffness of the two seismic springs 31 and 33. This total stiffness value is determined by back-calculation based on the structural dominant frequency requirement under earthquake conditions. Through this superposition design of basic stiffness and incremental stiffness, the system can achieve frequency characteristic switching from wind-resistant mode to earthquake-resistant mode without external sensors or control algorithms, relying solely on the physical matching of mechanical parameters. This solves the problem that traditional single-parameter devices cannot accommodate two completely different operating conditions.

[0045] like Figure 4 As shown, in one embodiment, the displacement boundary module 41 is a cylindrical structure with openings at the top and bottom; the trigger plate 42 is a circular plate with a diameter smaller than the inner diameter of the displacement boundary module 41 to form an annular trigger gap, and when the system is in a balanced position, the trigger plate 42 is located at the center of the displacement boundary module 41 along its axial direction.

[0046] The displacement boundary module 41 acts as a limiting container, and its cylindrical structure provides space for the trigger plate 42 to move. The diameter of the trigger plate 42 is slightly smaller than the inner diameter of the displacement boundary module 41, and the annular gap formed between them is the trigger gap. The size of this trigger gap directly determines the displacement threshold for the system to switch from wind-resistant mode to earthquake-resistant mode. It should be understood that the size of the trigger gap can be precisely designed and adjusted according to the maximum allowable displacement of the building structure under wind-induced vibration conditions, thereby ensuring that the system will not be falsely triggered under wind-induced vibration and can respond promptly under earthquake conditions. In addition, when the system is in equilibrium, the trigger plate 42 is located at the center of the displacement boundary module 41, which means that the trigger plate 42 has the same free travel in both the positive and negative directions. This symmetrical design ensures that the system can trigger stiffness switching with the same displacement threshold under both tensile and compressive stress states, adapting to the random reciprocating vibration characteristics of seismic waves and avoiding blind spots in unidirectional triggering.

[0047] Furthermore, when the relative displacement reaches and exceeds the trigger gap, the trigger plate 42 contacts the inner wall of the end of the displacement boundary module 41, driving the displacement boundary module 41 to compress or stretch the short spring, so that the short spring and the long spring together provide elastic restoring force.

[0048] This process describes the micromechanical transmission path of stiffness switching. When a building structure experiences a large displacement due to an earthquake, the first connector 1 drives the end plate 2 to move, causing the long spring to be compressed or stretched. As the displacement amplitude increases, the trigger plate 42, fixed to the free end of the long spring, moves inside the displacement boundary module 41. When the displacement reaches a preset trigger gap threshold, the trigger plate 42 makes hard contact with the top or bottom inner wall of the displacement boundary module 41. This hard contact is not a simple collision, but a turning point in force transmission. At the moment of contact, the trigger plate 42 directly applies the force transmitted from the long spring to the displacement boundary module 41. Since the displacement boundary module 41 is fixedly connected to the free end of the short spring, this force drives the short spring to undergo synchronous compression or stretching deformation. At this time, the short spring changes from its previous free and suspended state to a stressed working state, providing elastic restoring force in parallel with the long spring, and the total stiffness of the system increases instantaneously. This stiffness switching method achieved through mechanical contact has the characteristics of rapid response, high reliability, and no need for external energy drive, and can effectively cope with the suddenness of earthquake action.

[0049] like Figure 5 and Figure 6 As shown, in one embodiment, the piston 52 has a plurality of through holes 53, which serve as damping holes, evenly distributed along its circumference. Specifically, the through holes 53 are evenly spaced along the circumference of the piston 52, for example, eight through holes 53 of the same diameter can be provided. When the piston 52 reciprocates within the hydraulic cylinder 7, a pressure difference is generated between the two chambers separated by the piston 52 within the hydraulic cylinder 7. The viscous damping fluid 72 is forced to flow through the through holes 53 under the action of the pressure difference. Due to the small diameter of the through holes 53, the fluid is subjected to a strong throttling effect when passing through, thereby generating a viscous damping force related to the piston's movement speed, dissipating vibration energy. The design of the circumferentially uniform arrangement of the through holes 53 ensures that the flow resistance of the fluid in all directions of the piston 52 is consistent, avoiding tilting or jamming of the piston 52 due to uneven force caused by excessive flow resistance on one side, and ensuring the smoothness and stability of the piston 52's movement.

[0050] Furthermore, the ratio of the diameter of the helical tube 6 to the diameter of the through hole 53 is determined based on the ratio of the required inertial force to the viscous damping force of the system. Specifically, the helical tube 6 is wound around the outside of the hydraulic cylinder 7, with its two ends connected to the two working chambers of the hydraulic cylinder 7, respectively. When the piston 52 moves and compresses the viscous damping fluid 72, part of the fluid flows through the through hole 53 to generate damping force, while the other part of the fluid enters the helical tube 6. When the fluid flows inside the helical tube 6, it generates rotational motion due to the helical path. This rotational motion has a significant inertial effect, which can generate an inertial force proportional to the acceleration, thereby achieving the inertial-capacitance function, that is, obtaining a large apparent inertial mass with a small fluid physical mass. The ratio of the diameter of the helical tube 6 to the diameter of the through hole 53 directly determines the flow distribution ratio of the fluid between the damping channel and the inertial channel, and thus determines the ratio of the inertial force component to the damping force component in the system output force. By optimizing this diameter ratio, the system can obtain the best matching effect of inertial force and damping force under vibration loads with different frequency characteristics, thereby improving control efficiency.

[0051] Reference Figure 7 The inertial-capacitive damping unit also includes a regulating valve 8 located between the spiral tube 6 and the hydraulic cylinder 7. The end of the spiral tube 6 is connected to the interior of the hydraulic cylinder 7 via the regulating valve 8. The regulating valve 8 is a bidirectional valve that can control the flow rate of the viscous damping fluid 72 flowing through the spiral tube 6 by adjusting its opening. Specifically, the regulating valve 8 includes an adjusting knob 81 and a valve 82. By rotating the adjusting knob 81, the opening of the valve 82 can be changed, thereby changing the flow capacity of the spiral tube 6. When the opening of the valve 82 increases, more viscous damping fluid 72 enters the spiral tube 6 to participate in the rotational flow, increasing the apparent inertial mass of the system and enhancing the inertial force effect; conversely, when the opening of the valve 82 decreases, the inertial effect of the system weakens. This adjustment mechanism makes the variable frequency hydraulic inertial-capacitive vibration dual control system of the present invention widely adaptable. Engineers can adjust the inertial-capacitive parameters of the system on-site according to the dynamic characteristics of the actual building structure, achieving performance optimization without replacing hardware. At the same time, the bidirectional valve design ensures that the system can achieve consistent flow regulation in both the tensile and compressive motion directions.

[0052] Reference Figure 6The hydraulic cylinder 7 includes an outer cylinder 71, a viscous damping fluid 72 filled within the outer cylinder 71, and a sealing ring 73 for sealing the piston rod 51. The side wall of the outer cylinder 71 has interfaces that connect to the beginning and end of the spiral tube 6, respectively. Specifically, the outer cylinder 71, as a pressure vessel, is typically made of high-strength alloy steel, providing a sealed cavity space for the viscous damping fluid 72. The sealing ring 73 is located at an opening at the top of the outer cylinder 71, tightly wrapping the piston rod 51 to prevent leakage of the viscous damping fluid 72 under high pressure, and also to prevent external dust from entering the interior of the hydraulic cylinder 7. The interfaces on the side wall of the outer cylinder 71 connect to the beginning and end of the spiral tube 6, forming a fluid circulation loop. When the piston 52 moves, the viscous damping fluid 72 flows reciprocally between the inner cavity of the outer cylinder 71 and the spiral tube 6, realizing the mutual conversion of fluid kinetic energy and inertial potential energy. It should be understood that the viscous damping fluid 72 is usually selected from high-viscosity, chemically stable fluids, such as silicone oil, to ensure the stability of damping characteristics during long-term use.

[0053] In one embodiment, the connection method and assembly geometry of the system are further explained. (Refer to...) Figure 1 The first connecting piece 1 is a first earring that is fixedly connected to the end plate 2, and the second connecting piece 9 is a second earring that is fixedly connected to the liquid cylinder 7.

[0054] Specifically, the first and second lugs are located at opposite ends of the system, serving as interfaces for connection to the building structure. The lug-type connectors allow for slight oscillations within a certain angular range, accommodating minor angular displacements that may occur during building structure vibrations and preventing excessive bending stress at the connection points. It should be understood that while this embodiment demonstrates a lug connection, in other embodiments, the connectors may also employ flanges, hinged supports, or other forms of connection interfaces, as long as reliable anchoring of the system to the building structure is achieved.

[0055] Furthermore, the center of end plate 2, the center of long spring, the center of displacement boundary module 41, the center of trigger plate 42, the center of piston rod 51, the center of piston 52, the center of hydraulic cylinder 7, and the center of the connection surface between the second connector 9 and hydraulic cylinder 7 are located on the same straight line.

[0056] Specifically, this feature defines the coaxiality requirements of the core components within the system. Since this invention relates to the coordinated operation of a hydraulic inertial-capacitive and spring system, which includes the reciprocating motion of piston 52 within cylinder 7 and the extension and contraction of springs, the coaxiality of each moving component is crucial to the system's mechanical performance. If the centerlines of the components are not on the same straight line, i.e., there is an eccentric error, when the system is subjected to axial tensile and compressive loads, additional radial forces will be generated between piston rod 51 and sealing ring 73, and between piston 52 and the inner wall of cylinder 7. This radial force can cause piston 52 to tilt or wear unevenly during movement, increasing the wear rate of the sealing ring, and in severe cases, even causing piston jamming, preventing the system from responding properly to structural vibrations. By strictly limiting the centers of all the aforementioned components to be on the same straight line, it is ensured that external excitation loads can be uniformly transmitted along the axis, eliminating the adverse effects of eccentric loads. This coaxial arrangement effectively ensures the smoothness of piston movement, reduces internal mechanical friction resistance, thereby ensuring the system's reliability and durability under long-term reciprocating vibration conditions and extending the device's service life.

[0057] In a specific embodiment, taking the structural vibration control of a high-rise building as an example, the application and operational effect of the variable frequency hydraulic inertial-capacitive vibration dual control system provided by the present invention in a real engineering environment are illustrated. The system is installed at the inter-story displacement point of the high-rise building, specifically connected to the upper and lower floor slabs of the building structure through the first connector 1 and the second connector 9, respectively, making it a passive control element for inter-story deformation of the structure.

[0058] Under wind-induced vibration conditions, the building structure is subjected to random excitation by wind loads, typically exhibiting high-frequency, small-amplitude reciprocating vibrations. At this time, the relative displacement between the first connector 1 and the second connector 9 is small, with an amplitude less than the preset trigger gap. According to the design of this invention, when the relative displacement is less than the trigger gap, only the long spring provides elastic restoring force, while simultaneously driving the piston 52 through the linkage unit 5, causing the viscous damping fluid 72 to flow through the damping orifice to generate damping force, and partially flowing into the spiral tube 6 to generate inertial force. Specifically, at this time, only the wind-resistant spring 32 is subjected to force and extension, and the system exhibits low stiffness characteristics. This stiffness value is specially designed to match the dominant frequency of the structure under wind-induced vibration excitation, effectively limiting the inter-story displacement amplitude of the structure, reducing swaying, and ensuring the building's comfort in strong wind environments. Simultaneously, the viscous damping force generated by the inertial-capacitive damping unit works synergistically with the inertial force to dissipate some of the wind-induced vibration input energy, further suppressing the structural response.

[0059] Under seismic conditions, the building structure is subjected to strong impacts from seismic waves, resulting in low-frequency, high-amplitude vibrations. When the inter-story displacement caused by the earthquake increases, causing the relative displacement between the first connector 1 and the second connector 9 to reach and exceed the trigger gap, the trigger plate 42 contacts the displacement boundary module 41 and drives the short springs to participate in the work, providing increased elastic restoring force. Specifically, as the displacement amplitude exceeds the trigger threshold, the trigger plate 42 makes hard contact with the displacement boundary module 41, forcing the anti-seismic springs 31 and 33 to intervene. At this time, the equivalent stiffness of the system increases instantaneously, realizing an adaptive abrupt change in stiffness characteristics to match the requirements for high stiffness and large restoring force under seismic conditions, preventing excessive plastic deformation of the structure. At the same time, since the velocity and acceleration of seismic action are usually greater than those of wind vibration, the flow velocity of the viscous damping fluid 72 in the cylinder 7 and the spiral tube 6 increases, and the inertial force and viscous damping force generated by the inertial capacitive damping unit are significantly enhanced. Utilizing the mass amplification effect generated by the fluid rotation motion, the seismic input energy is efficiently absorbed and dissipated, protecting the safety of the main structure.

[0060] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0061] The above-described embodiments are merely illustrative of several implementations of the present invention, and while the descriptions are specific and detailed, they should not be construed as limiting the scope of the invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these modifications and improvements all fall within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the appended claims.

Claims

1. A variable frequency hydraulic inertial-capacitive vibration dual control system, comprising a first connector (1) and a second connector (9) for connecting a building structure, characterized in that, It also includes a series-connected variable stiffness unit, a displacement triggering unit (4), a linkage unit (5), and an inertial-capacitive damping unit; The variable stiffness unit includes an end plate (2) and a set of springs (3). The springs (3) include a long spring and at least one short spring. One end of all the springs is fixed to the end plate (2), and the free end length of the long spring is greater than the free end length of the short spring. The displacement triggering unit (4) includes a displacement boundary module (41) fixedly connected to the free end of the short spring, and a trigger plate (42) fixedly connected to the free end of the long spring and housed in the displacement boundary module (41). A trigger gap is preset between the trigger plate (42) and the inner wall of the displacement boundary module (41). The linkage unit (5) includes a piston rod (51) and a piston (52) fixed to one end thereon. The other end of the piston rod (51) is fixedly connected to the trigger plate (42). The inertial-capacitive damping unit includes a sealed liquid cylinder (7) filled with viscous damping fluid (72) and a spiral tube (6) with both ends connected to the inside of the liquid cylinder (7) and wound around its outside. The piston (52) is sealed and slidably disposed in the liquid cylinder (7) and its inner cavity is divided into two working chambers. The piston (52) has a damping hole connecting the two working chambers. The first connector (1) is connected to the end plate (2), and the second connector (9) is connected to the hydraulic cylinder (7); When the relative displacement between the first connector (1) and the second connector (9) is less than the trigger gap, only the long spring provides elastic restoring force, and at the same time, the piston (52) is driven to move through the linkage unit (5), so that the viscous damping fluid (72) flows through the damping hole to generate damping force, and partially flows into the spiral tube (6) to generate inertial force; when the relative displacement reaches and exceeds the trigger gap, the trigger plate (42) contacts the displacement boundary module (41) and drives the short spring to participate in the work to provide increased elastic restoring force.

2. The variable frequency hydraulic inertial-capacitive vibration dual control system according to claim 1, characterized in that, The spring assembly (3) includes a wind-resistant spring (32) as the long spring and two shock-resistant springs (31, 33) as the short springs. The two shock-resistant springs (31, 33) are of the same length and are arranged symmetrically about the center of the end plate (2).

3. The variable frequency hydraulic inertial-capacitive vibration dual control system according to claim 2, characterized in that, The stiffness of the wind-resistant spring (32) is determined based on the stiffness required for the main control frequency of the system under wind-resistant conditions; the sum of the stiffnesses of the two seismic springs (31, 33) is determined based on the difference between the stiffness required for the main control frequency of the system under seismic conditions and the stiffness of the wind-resistant spring (32).

4. The variable frequency hydraulic inertial-capacitive vibration dual control system according to claim 1, characterized in that, The displacement boundary module (41) is a cylindrical structure with openings at the top and bottom; the trigger plate (42) is a circular plate with a diameter smaller than the inner diameter of the displacement boundary module (41) to form an annular trigger gap, and when the system is in a balanced position, the trigger plate (42) is located at the center of the displacement boundary module (41) along its axial direction.

5. The variable frequency hydraulic inertial-capacitive vibration dual control system according to claim 4, characterized in that, When the relative displacement reaches and exceeds the trigger gap, the trigger plate (42) contacts the inner wall of the end of the displacement boundary module (41), driving the displacement boundary module (41) to compress or stretch the short spring, so that the short spring and the long spring together provide elastic restoring force.

6. The variable frequency hydraulic inertial-capacitive vibration dual control system according to claim 1, characterized in that, The piston (52) has a plurality of through holes (53) evenly distributed along its circumference as damping holes.

7. The variable frequency hydraulic inertial-capacitive vibration dual control system according to claim 6, characterized in that, The ratio of the diameter of the spiral tube (6) to the diameter of the through hole (53) is determined based on the ratio of the required inertial force to the viscous damping force of the system.

8. The variable frequency hydraulic inertial-capacitive vibration dual control system according to claim 1, characterized in that, The inertial-capacitive damping unit also includes a regulating valve (8) disposed between the spiral tube (6) and the liquid cylinder (7). The end of the spiral tube (6) is connected to the interior of the liquid cylinder (7) through the regulating valve (8). The regulating valve (8) is a bidirectional valve that can control the flow rate of the viscous damping fluid (72) flowing through the spiral tube (6) by adjusting the opening degree.

9. The variable frequency hydraulic inertial-capacitive vibration dual control system according to claim 1, characterized in that, The cylinder (7) includes an outer cylinder (71), a viscous damping fluid (72) filled in the outer cylinder (71), and a sealing ring (73) for sealing the piston rod (51). The side wall of the outer cylinder (71) is provided with interfaces that communicate with the beginning and end of the spiral tube (6) respectively.

10. The variable frequency hydraulic inertial-capacitive vibration dual control system according to any one of claims 1 to 9, characterized in that, The first connector (1) is a first earring fixedly connected to the end plate (2), and the second connector (9) is a second earring fixedly connected to the hydraulic cylinder (7); the center of the end plate (2), the center of the long spring, the center of the displacement boundary module (41), the center of the trigger plate (42), the center of the piston rod (51), the center of the piston (52), the center of the hydraulic cylinder (7), and the center of the connection surface between the second connector (9) and the hydraulic cylinder (7) are located on the same straight line.

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