A semi-active control TMD based on fluid spring

Abstract

A kind of semi-active control TMD based on fluid spring relates to damper technical field, including mass, fluid spring, damper, bottom plate, accessory parts;Mass is opposite to bottom plate, fluid spring and damper are installed between mass and bottom plate, fluid spring includes to be connected with the upper connecting plate of mass, to be connected with the lower connecting plate of bottom plate, sleeve fixed at the top of lower connecting plate, cover plate sealingly fixed to the top of sleeve, piston shaft is slidably connected through cover plate, piston is fixedly connected to the bottom end of piston shaft, the top of piston shaft is fixedly connected with the bottom end of upper connecting plate, damping spring is arranged between the lower end of piston and the upper end of lower connecting plate and located in sleeve, sleeve is connected with variable stiffness control mechanism by accessory parts.The present application has simple structure, low installation and maintenance cost, high stiffness linearity, wide frequency domain control structure vibration, and can effectively improve the damping energy dissipation performance of device in the face of complex working conditions.

Description

Technical Field

[0001] This invention relates to the field of damper technology, and more specifically to a semi-active control TMD based on a fluid spring. Background Technology

[0002] The impact of earthquakes on buildings is primarily caused by vibration, with damage often occurring as dynamic failure, meaning the building collapses due to insufficient strength of the main structure or loss of structural stability. Traditional earthquake-resistant structures mainly utilize the plastic deformation of structural members during yielding to dissipate energy; however, due to the limited energy dissipation capacity of these members, the structure is prone to severe damage under strong earthquakes and is difficult to repair post-earthquake. To address these issues, installing tuned mass dampers on the exterior of the structure can reduce structural vibration and effectively mitigate post-earthquake damage. Furthermore, due to the advantages of easy maintenance and replacement and low repair costs, tuned mass dampers have been increasingly used in recent years and have attracted widespread attention in the industry.

[0003] Due to the limitations of traditional seismic design, many scholars have proposed new seismic design methods—structural vibration control methods. These methods involve arranging energy-dissipating or vibration-damping devices on the building structure to reduce or suppress its dynamic response. One approach is to install large dampers throughout the structure to increase its damping ratio during vibrations, thereby reducing the amplitude of vibrations under load and dissipating vibrational energy through the damper's movement. The most widely used device is the tuned mass damper (TMD), which comes in various types with different application theories and system optimizations, but is generally recognized as an effective way to reduce structural vibration. Variable stiffness TMD devices can achieve broadband vibration control of the structure and offer better stability compared to ATMDs.

[0004] Once installed, the dynamic characteristics of common TMD devices, such as their frequency range, remain fixed. TMD devices with active control systems increase maintenance costs and are more sensitive to time delays. TMD devices with semi-active control systems suffer from stiffness nonlinearity, making their performance unstable under complex excitations. Furthermore, existing TMD frequency domain control ranges are relatively narrow, making it difficult to achieve effective vibration damping at frequencies outside the design range. Summary of the Invention

[0005] This invention discloses a semi-active control TMD based on fluid springs. The device has a relatively simple structure, low installation and maintenance costs, high stiffness linearity, and wide frequency domain control of structural vibration, which can effectively improve the device's performance when facing complex working conditions.

[0006] To achieve the above objectives, the present invention adopts the following technical solution:

[0007] A semi-active control TMD based on a fluid spring includes a mass block, a fluid spring, a damper, a base plate, and auxiliary components. The mass block and the base plate are vertically opposite each other. A fluid spring and a damper are installed between the mass block and the base plate. The fluid spring includes an upper connecting plate for connecting to the mass block, a lower connecting plate for connecting to the base plate, a sleeve fixedly disposed at the top of the lower connecting plate, a cover plate fixedly and sealed to the top of the sleeve, a piston shaft passing through the cover plate and slidably connected to the cover plate, and a piston fixedly connected to the bottom of the piston shaft. The top of the piston shaft is fixedly connected to the bottom of the upper connecting plate. A damping spring is disposed between the lower end of the piston and the upper end of the lower connecting plate and inside the sleeve. The sleeve is connected to a variable stiffness control mechanism through auxiliary components.

[0008] Preferably, a first connecting seat is provided on one side of the lower end of the mass block, and a second connecting seat is fixedly provided on the upper surface of the base plate opposite to the first connecting seat. The two ends of the damper are respectively connected to the first connecting seat and the second connecting seat.

[0009] Preferably, the fluid spring is located between the mass block and the base plate and on the side away from the damper, and the upper connecting plate and the lower connecting plate are respectively fixedly connected to the mass block or the base plate by bolts.

[0010] Preferably, the variable stiffness control mechanism adjusts the damping capacity of the fluid spring by changing the gas pressure or liquid pressure inside the sleeve; the bottom of both sides of the sleeve is provided with an input hole and an output hole, and the input hole and the output hole are respectively provided with electromagnetic flow regulating valves.

[0011] Preferably, when the variable stiffness control mechanism adjusts the damping capacity of the fluid spring by changing the gas pressure inside the sleeve, the variable stiffness control mechanism includes a high-pressure air pump fixedly mounted on the upper end of the base plate and a first controller. The high-pressure air pump is connected to the input hole through a pipeline, and a through hole penetrating the inside of the sleeve is also provided on the cover plate.

[0012] Preferably, when the variable stiffness control mechanism adjusts the damping capacity of the fluid spring by changing the liquid pressure inside the sleeve, the variable stiffness control mechanism includes a fluid storage chamber fixedly mounted on the upper end of the base plate, a high-pressure pump, and a second controller. The auxiliary components include pipe one, pipe two, and pipe three. The fluid storage chamber has an outlet and an inlet at its bottom. The inlet is connected to the output port through pipe one, the outlet is connected to the input end of the high-pressure pump through pipe three, and the output end of the high-pressure pump is connected to the input port through pipe two.

[0013] Preferably, the auxiliary components further include an acceleration sensor, which is fixedly connected to the middle of the lower surface of the mass block. The acceleration sensor is signal-connected to a first controller or a second controller via a wire. The first controller is electrically connected to an electromagnetic flow regulating valve and a high-pressure air pump via a wire. The second controller is electrically connected to the electromagnetic flow regulating valve and the high-pressure pump via a wire.

[0014] Preferably, the damping fluid is a Group III base oil, with 0.1% of a composite antifoaming agent and high-viscosity silicone oil added to the base oil to improve its defoaming ability and damping effect; to increase the fluid density and improve the damping effect of the fluid spring, 0.2% of cuprous bromide is added to the base oil; since TMD is used in the external environment, good shear stability and low-temperature performance will also affect the damping effect of TMD, so a viscosity index improver PMA is added to the base oil.

[0015] A method for using a semi-active control TMD based on a fluid spring includes the following steps:

[0016] The mass block and base plate are connected to the upper and lower structures respectively. Vibration reduction is achieved by connecting the upper and lower structures. When vibration begins, the acceleration sensor transmits vibration data to the controller. The controller determines whether the vibration is within the controllable range of the current state. If it is, no action is taken, and vibration reduction is achieved through the fluid spring and damper. If not, the variable stiffness control mechanism is activated. That is, when the vibration frequency or amplitude is greater than the controllable range of the current state, the controller opens the electromagnetic flow regulating valve (i.e., the pressurizing valve) on the input port side to pressurize the damping gas or damping liquid in the sleeve. If the vibration frequency or amplitude is less than the controllable range of the current state, the controller opens the electromagnetic flow regulating valve (i.e., the pressure relief valve) on the output port side to release the pressure of the damping gas or damping liquid in the sleeve. The variable stiffness control mechanism is adjusted until the value of the acceleration sensor returns to the set safe range.

[0017] The beneficial effects of the semi-active control TMD based on fluid springs in this invention are as follows:

[0018] This invention has a simple structure, low installation and maintenance costs, high stiffness linearity, and wide frequency domain control of structural vibration, which can effectively improve the vibration reduction and energy dissipation performance of the device when facing complex working conditions. Attached Figure Description

[0019] To more clearly illustrate the technical solution of the present invention, the accompanying drawings used in the embodiments are briefly described below, which constitute a part of the specification and are used together with the embodiments of the present invention to explain the present invention, but do not constitute a limitation on the present invention.

[0020] Figure 1 : A side view of the structure of the present invention;

[0021] Figure 2 This invention Figure 1 A cross-sectional view of the structure along the AA direction;

[0022] Figure 3 : A top view of the structure of the present invention;

[0023] Figure 4 : A three-dimensional structural schematic diagram of the present invention;

[0024] Figure 5 : A bottom view of the mass block of the present invention;

[0025] Figure 6 : A side view of the mass block of the present invention;

[0026] Figure 7 : A three-dimensional structural diagram of the mass block of the present invention;

[0027] Figure 8 : A top view of the fluid spring of the present invention;

[0028] Figure 9 This invention Figure 8 A cross-sectional view of the structure along the AA direction;

[0029] Figure 10 : A three-dimensional structural schematic diagram of the fluid spring of the present invention;

[0030] Figure 11 : A top view of the base plate of this invention;

[0031] Figure 12 : A side view of the base plate of the present invention;

[0032] Figure 13 This invention Figure 12 A cross-sectional view of the structure along the AA direction;

[0033] Figure 14 1. Structural diagram of the auxiliary components of this invention;

[0034] Figure 15 A schematic diagram illustrating the implementation principle of the present invention;

[0035] 1. Mass block; 101. First bolt hole for connection to the superstructure; 102. Second bolt hole for connection to the upper connecting plate; 103. First connecting seat; 104. Bolt hole for mounting the acceleration sensor; 2. Fluid spring; 201. Upper connecting plate; 20101. First threaded hole for connection to the mass block; 20102. Second threaded hole for connection to the mass block; 202. Piston shaft; 203. Cover plate; 20301. Through hole; 20302. Sliding hole; 204. Sleeve; 20401. Input hole; 20402. Output hole; 205. Lower connecting plate ; 20501, First threaded hole for connection with the base plate; 20502, Second threaded hole for connection with the base plate; 206, Vibration damping spring; 3, Damper; 4, Base plate; 401, Bolt hole for connection with the lower connecting plate; 402, Controller reserved position (for installing the first controller or the second controller); 403, High-pressure pump or high-pressure air pump reserved position; 404, Fluid storage chamber; 405, Second connecting seat; 406, Bolt hole for connection with the lower structure; 5, Auxiliary components; 501, Pipeline 1; 502, Pipeline 2; 503, Pipeline 3; 504, Accelerometer sensor. Detailed Implementation

[0036] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present invention, and 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.

[0037] Example 1

[0038] A semi-active control TMD based on fluid springs, such as Figure 1-14 As shown, the device includes a mass block 1, a fluid spring 2, a damper 3, a base plate 4, and an auxiliary component 5. The mass block 1 and the base plate 4 are vertically opposite each other. The fluid spring 2 and the damper 3 are installed between the mass block 1 and the base plate 4. The fluid spring 2 includes an upper connecting plate 201 for connecting to the mass block 1, a lower connecting plate 205 for connecting to the base plate 4, a sleeve 204 fixedly disposed at the top of the lower connecting plate 205, a cover plate 203 sealed and fixedly connected to the top of the sleeve 204, a piston shaft 202 passing through the cover plate 203 and slidably connected to the cover plate 203, and a piston fixedly connected to the bottom end of the piston shaft 202. The top end of the piston shaft is fixedly connected to the bottom end of the upper connecting plate 201. A damping spring 206 is provided between the lower end of the piston and the upper end of the lower connecting plate 205 and inside the sleeve 204. The sleeve 204 is connected to a variable stiffness control mechanism through the auxiliary component 5.

[0039] Example 2

[0040] Based on Example 1, this example discloses:

[0041] like Figure 5 , 6 As shown, a first connecting seat 103 is provided on one side of the lower end of the mass block 1, such as... Figure 11 As shown, a second connecting seat 405 is fixedly provided on the upper surface of the base plate 4, which is vertically opposite to the first connecting seat 103. The two ends of the damper 3 are respectively connected to the first connecting seat 103 and the second connecting seat 405.

[0042] The damper 3 of the present invention can be any type of existing damper structure, and its function is to provide vibration reduction and energy dissipation within the conventional range for the structure.

[0043] Example 3

[0044] Based on Example 2, this example discloses:

[0045] like Figure 1 , 2 As shown in Figure 4, the fluid spring 2 is located between the mass block 1 and the base plate 4 and on the side away from the damper 3. The upper connecting plate 201 and the lower connecting plate 205 are respectively fixedly connected to the mass block 1 or the base plate 4 by bolts.

[0046] The fluid spring 2 and damper 3 of the present invention are respectively arranged on both sides between the base plate and the mass block, and together undertake the work of vibration reduction and energy dissipation of the structure.

[0047] Example 4

[0048] Based on Example 3, this example discloses:

[0049] like Figure 1-14 As shown, the variable stiffness control mechanism adjusts the damping capacity of the fluid spring 2 by changing the gas pressure or damping liquid pressure inside the sleeve 204. The bottom of both sides of the sleeve 204 is provided with an input port 20401 and an output port, respectively, and each of the input and output ports is equipped with an electromagnetic flow regulating valve. This electromagnetic flow regulating valve can also be installed in pipes one, two, or three of the auxiliary components to achieve the same purpose.

[0050] The electromagnetic flow regulating valve located on the input port side of this invention functions as a pressurizing valve, while the electromagnetic flow regulating valve on the output port side functions as a pressure relief valve. By changing the pressure of the damping gas or damping liquid within the sleeve to regulate the frequency domain of the fluid spring, this invention can be applied to complex vibration scenarios.

[0051] Example 5

[0052] Based on Example 4, this example discloses:

[0053] like Figure 1-14 As shown, when the variable stiffness control mechanism adjusts the damping capacity of the fluid spring 2 by changing the gas pressure inside the sleeve 204, the variable stiffness control mechanism includes a high-pressure air pump (not shown in the figure, but the position of the high-pressure pump can be referenced) fixed on the upper end of the base plate 4 and a first controller. The high-pressure air pump is connected to the input hole 20401 through a pipeline, and a through hole 20301 penetrating the inside of the sleeve is also provided on the cover plate.

[0054] This embodiment discloses one implementation of the present invention, in which the fluid spring provides damping through gas, the sleeve is pressurized by a high-pressure air pump to improve the damping capacity of the gas, and the damping capacity of the damping gas is reduced by opening the pressure relief valve to release the pressure of the damping gas in the sleeve, thereby achieving the purpose of bidirectional adjustment.

[0055] Example 6

[0056] Based on Example 4, this example discloses:

[0057] like Figure 1-14 As shown, when the variable stiffness control mechanism adjusts the damping capacity of the fluid spring 2 by changing the liquid pressure inside the sleeve 204, the variable stiffness control mechanism includes a fluid storage chamber 404 fixedly mounted on the upper end of the base plate 4, a high-pressure pump, and a second controller. The auxiliary components include pipe 1 501, pipe 2 502, and pipe 3 503. The fluid storage chamber 404 has an outlet and an inlet at its bottom. The inlet is connected to the output hole through pipe 1 501, and the outlet is connected to the input end of the high-pressure pump through pipe 3 503. The output end of the high-pressure pump is connected to the input hole through pipe 2.

[0058] This embodiment provides a scheme for adjusting the damping frequency domain of the fluid spring 2 by filling and discharging liquid. The specific principle is the same as that of embodiment 5. It should be noted that the through hole 20301 is not provided in this embodiment.

[0059] Example 7

[0060] Based on the above embodiments, this embodiment discloses:

[0061] like Figure 1 , 2 As shown in Figures 5 and 14, the auxiliary component 5 also includes an acceleration sensor 504, which is fixedly connected to the middle of the lower surface of the mass block 1. The acceleration sensor 504 is connected to the first controller or the second controller via a wire. The first controller is electrically connected to the electromagnetic flow regulating valve and the high-pressure air pump via a wire. The second controller is electrically connected to the electromagnetic flow regulating valve and the high-pressure pump via a wire.

[0062] This embodiment describes the control methods for two implementations of the present invention (gas and liquid regulating damping force). The controller uses electronic components programmed according to the dynamic characteristics of the structure, with code provided by the electronic component manufacturer. The electromagnetic flow regulating valve, acceleration sensor, high-pressure air pump, and high-pressure pump can all be commercially available products.

[0063] Example 8

[0064] Based on the above embodiments, this embodiment discloses:

[0065] The damping fluid uses Group III base oils. 0.1% composite antifoaming agent and high-viscosity silicone oil are added to the base oils to improve their defoaming ability and damping effect. To increase the fluid density and improve the damping effect of the fluid spring, 0.2% cuprous bromide is added to the base oils. Since TMDs are used in external environments, good shear stability and low-temperature performance also affect their damping effect; therefore, a viscosity index improver, PMA, is added to the base oils. This fluid oil has good viscosity and antifoaming properties; however, when applied to specific scenarios, the fluid should be modified according to different operating environments.

[0066] Example 9

[0067] Based on the above embodiments, this embodiment discloses:

[0068] A method for using a semi-active control TMD based on a fluid spring, such as Figure 15 As shown, it includes the following steps:

[0069] The mass block and base plate are connected to the upper and lower structures respectively. Vibration reduction is achieved by connecting the upper and lower structures. When vibration begins, the acceleration sensor transmits vibration data to the controller. The controller determines whether the vibration is within the controllable range of the current state. If it is, no action is taken, and vibration reduction is achieved through the fluid spring and damper. If not, the variable stiffness control mechanism is activated. That is, when the vibration frequency or amplitude is greater than the controllable range of the current state, the controller opens the electromagnetic flow regulating valve (i.e., the pressurizing valve) on the input port side to pressurize the damping gas or damping liquid in the sleeve. If the vibration frequency or amplitude is less than the controllable range of the current state, the controller opens the electromagnetic flow regulating valve (i.e., the pressure relief valve) on the output port side to release the pressure of the damping gas or damping liquid in the sleeve. The variable stiffness control mechanism is adjusted until the value of the acceleration sensor returns to the set safe range.

Claims

1. A semi-active control TMD based on fluid springs, characterized by: The device includes a mass block, a fluid spring, a damper, a base plate, and auxiliary components. The mass block and the base plate are positioned vertically opposite each other. A fluid spring and a damper are installed between the mass block and the base plate. The fluid spring includes an upper connecting plate for connecting to the mass block, a lower connecting plate for connecting to the base plate, a sleeve fixedly mounted on the top of the lower connecting plate, a cover plate fixedly and sealed to the top of the sleeve, a piston shaft passing through the cover plate and slidably connected to the cover plate, and a piston fixedly connected to the bottom of the piston shaft. The top of the piston shaft is fixedly connected to the bottom of the upper connecting plate. A damping spring is provided between the lower end of the piston and the upper end of the lower connecting plate, located inside the sleeve. The sleeve is connected to a variable stiffness control mechanism through auxiliary components. The variable stiffness control mechanism adjusts the damping capacity of the fluid spring by changing the gas pressure or damping liquid pressure inside the sleeve; the bottom of both sides of the sleeve is provided with an input hole and an output hole, and the input hole and the output hole are respectively provided with electromagnetic flow regulating valves; the auxiliary components also include an acceleration sensor, which is fixedly connected to the middle of the lower surface of the mass block.

2. The semi-active control TMD based on a fluid spring as described in claim 1, characterized in that: A first connecting seat is provided on one side of the lower end of the mass block, and a second connecting seat is fixed on the upper surface of the base plate opposite to the first connecting seat. The two ends of the damper are respectively connected to the first connecting seat and the second connecting seat.

3. The semi-active control TMD based on a fluid spring as described in claim 2, characterized in that: The fluid spring is located between the mass block and the base plate and on the side away from the damper. The upper connecting plate and the lower connecting plate are respectively fixedly connected to the mass block or the base plate by bolts.

4. The semi-active control TMD based on a fluid spring as described in claim 3, characterized in that: When the variable stiffness control mechanism adjusts the damping capacity of the fluid spring by changing the gas pressure inside the sleeve, the variable stiffness control mechanism includes a high-pressure air pump and a first controller fixed on the upper part of the base plate. The high-pressure air pump is connected to the input hole through a pipeline, and a through hole penetrating the inside of the sleeve is also provided on the cover plate.

5. A semi-active control TMD based on a fluid spring as described in claim 3, characterized in that: When the variable stiffness control mechanism adjusts the damping capacity of the fluid spring by changing the damping fluid pressure inside the sleeve, the variable stiffness control mechanism includes a fluid storage chamber fixedly mounted on the upper part of the base plate, a high-pressure pump, and a second controller. The auxiliary components include pipe one, pipe two, and pipe three. The bottom of the fluid storage chamber is provided with an outlet and an inlet. The inlet is connected to the output hole through pipe one, the outlet is connected to the input end of the high-pressure pump through pipe three, and the output end of the high-pressure pump is connected to the input hole through pipe two.

6. A semi-active control TMD based on a fluid spring as described in claim 4 or 5, characterized in that: The acceleration sensor is connected to the first controller or the second controller via a wire. The first controller is electrically connected to the electromagnetic flow regulating valve and the high-pressure air pump via a wire. The second controller is electrically connected to the electromagnetic flow regulating valve and the high-pressure pump via a wire.

7. A semi-active control TMD based on a fluid spring as described in claim 6, characterized in that: The damping fluid uses Group III base oils. 0.1% of a composite antifoaming agent and high-viscosity silicone oil are added to the base oil to improve its defoaming ability and damping effect. To increase the fluid density and improve the damping effect of the fluid spring, 0.2% of cuprous bromide is added to the base oil. Since TMD is used in the external environment, good shear stability and low-temperature performance will also affect the damping effect of TMD. Therefore, a viscosity index improver PMA is added to the base oil.

8. The method of using a semi-active control TMD based on a fluid spring as described in claim 7, characterized in that: Includes the following steps: The mass block and base plate are connected to the upper and lower structures respectively. Vibration reduction is achieved by connecting the upper and lower structures. When vibration begins, the acceleration sensor transmits vibration data to the controller. The controller determines whether the vibration is within the controllable range of the current state. If it is, no action is taken, and vibration reduction is achieved through the fluid spring and damper. If not, the variable stiffness control mechanism is activated. That is, when the vibration frequency or amplitude is greater than the controllable range of the current state, the controller opens the electromagnetic flow regulating valve on the input port side to pressurize the damping gas or damping liquid in the sleeve. If the vibration frequency or amplitude is less than the controllable range of the current state, the controller opens the electromagnetic flow regulating valve on the output port side to depressurize the damping gas or damping liquid in the sleeve. The variable stiffness control mechanism is adjusted until the value of the acceleration sensor returns to the set safe range.

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