A tuned inertial mass damper

Abstract

The present invention belongs to the field of vibration control technology and discloses a tuned inertia mass damper, comprising an outer frame, an elastic device, an inertia damping device and a mass block; the mass block is suspended in the outer frame by the elastic device and the inertia damping device; the inertia damping device comprises a viscous damping unit, an inertia flywheel, a screw and a nut; the viscous damping unit comprises an outer cylinder connected to the outer frame and an inner roller rotatably arranged in the outer cylinder; a viscous material is provided between the inner roller and the outer cylinder; the inner roller and the inertia flywheel are both fixedly connected to the nut; the nut is threadedly connected to the screw, and one end of the screw is connected to the mass block. The present invention achieves effective control of multi-order frequency vibration by adjusting the inertia coefficient, and has a wide adjustable range. It is suitable for multi-frequency vibration control of structures such as multi-order vortex vibration control of suspension bridges, is simple to install and maintain, has little additional effect on the structure, and has high vibration reduction efficiency.

Description

Technical Field

[0001] The invention belongs to the technical field of vibration control, and in particular relates to a tuned inertia mass damper. Background Art

[0002] As bridge structures become larger and more flexible, they often experience vibration responses across multiple frequency ranges under complex natural and social environments. This not only accelerates structural fatigue and reduces service life, but also affects structural safety and user comfort.

[0003] Traditional tuned mass dampers (TMDs) primarily provide effective vibration reduction at a single frequency and are unable to meet the control requirements for structures vibrating at multiple frequencies. While multi-tuned mass dampers (MTMDs) can control multiple frequencies, they are bulky, difficult to install and maintain, and their non-operating components can easily interfere with structural control, making them less practical.

[0004] Semi-active systems can adjust damper characteristics by driving actuators through external energy sources, thereby adjusting the damper's operating frequency in real time. Currently, adaptive vibration damping systems primarily achieve stiffness changes by driving complex mechanical devices to modify the constraints of the tuned mass damper (TMD) or the length of the elastic member. These systems are typically more complex and less durable, requiring more maintenance to ensure long-term performance.

[0005] Therefore, we propose a tuned inertia mass damper to solve the above problems existing in the prior art. Summary of the Invention

[0006] The object of the present invention is to provide a tuned inertia mass damper, which can adjust the operating frequency of the tuned inertia mass damper by adjusting the inertia coefficient, thereby achieving effective control of multiple modal vibrations within a wide frequency range.

[0007] The specific technical solutions are as follows:

[0008] A tuned inertia mass damper comprises an outer frame, an elastic device, an inertia damping device and a mass block;

[0009] The mass block is suspended in the outer frame through an elastic device and an inertia damping device;

[0010] The inertia-capacitance damping device includes a viscous damping unit, an inertial flywheel, a screw, and a nut; the viscous damping unit includes an outer cylinder connected to the outer frame and an inner roller rotatably disposed within the outer cylinder; a viscous material is further disposed between the inner roller and the outer cylinder to provide resistance when the inner roller rotates relative to the outer cylinder;

[0011] The internal drum and the inertia flywheel are both fixedly connected to a nut; the nut is threadedly connected to a screw rod, one end of the screw rod is movably arranged in the internal drum, and the other end thereof is connected to the mass block.

[0012] Preferably, the inertia flywheel comprises a flywheel disc with grooves, a wheel cover and a flywheel mass block;

[0013] The grooved flywheel disc is provided with a plurality of linear slide grooves along the radial direction, the wheel cover is rotatably arranged on the grooved flywheel disc, and the wheel cover is provided with curved slide grooves corresponding to the linear slide grooves;

[0014] The flywheel mass block is slidably arranged in the linear slide groove and the curved slide groove at the same time, so as to push the flywheel mass block to slide along the linear slide groove through the curved slide groove when the wheel cover rotates relative to the grooved flywheel disc;

[0015] The grooved flywheel disc is also fixedly connected to the nut.

[0016] Preferably, the device further comprises a control device, wherein the control device comprises a receiver, a processor and a drive motor;

[0017] The receiver is connected to an external vibrating structure and is used to collect the vibration frequency of the vibrating structure and transmit it to a processor; the processor is also connected to a drive motor; the processor is used to calculate the actual operating frequency of the tuned inertia mass damper, the inertia coefficient of the inertia damping device, and the radius of the flywheel mass block in the slotted flywheel disc;

[0018] The drive motor is used to control the rotation angle of the wheel cover relative to the slotted flywheel disc according to the signal from the processor, thereby pushing the flywheel mass block to a specified position;

[0019] Preferably, the flywheel mass is made of cast iron.

[0020] Preferably, the inner drum is rotatably arranged in the outer cylinder through a tapered roller bearing; and the wheel cover is rotatably arranged on the grooved flywheel disc through two angular contact ball bearings.

[0021] Preferably, the nut is a ball nut.

[0022] Preferably, the elastic device includes a plurality of springs, one end of each spring is connected to the outer frame, and the other end of each spring is connected to the mass block.

[0023] Preferably, the mass block is further provided with an ear plate; the spring is connected to the mass block via the ear plate.

[0024] Compared with the prior art, the present invention has the following beneficial effects:

[0025] The present invention adjusts the inertia coefficient of the inertia damping device by adjusting the radius of the flywheel mass block to match multi-order frequency vibrations, and cooperates with the mass block to effectively control the vibration. It has a wide adjustable range, better versatility, and a controllable frequency band wider than that of existing semi-active tuned inertia mass dampers.

[0026] Further features and advantages of the present invention will become apparent from the following detailed description of exemplary embodiments of the present invention with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 is a schematic structural diagram of a tuned inertia mass damper according to an embodiment of the present invention;

[0028] Figure 2 for Figure 1 Schematic diagram of the structure of the medium inertia damping device;

[0029] Figure 3 for Figure 2 Schematic diagram of the connection between the middle screw and the nut;

[0030] Figure 4 for Figure 2 Schematic diagram of the structure of the medium inertia flywheel and control device;

[0031] Figure 5 for Figure 4 Schematic diagram of the connection relationship of the flywheel with grooves in the middle;

[0032] Figure 6 for Figure 4 Schematic diagram of the structure of the flywheel mass block and wheel cover;

[0033] Figure 7 for Figure 4 Schematic diagram of the motion conversion method of the middle wheel cover and the flywheel mass block, where: Figure 7 (a) is a schematic diagram before the wheel cover rotates. Figure 7 (b) is a schematic diagram of the wheel cover after rotation;

[0034] In the figure: 1. Outer frame; 2. Spring; 3. Outer cylinder; 4. Viscous material; 5. Inner roller; 6. Inertia flywheel; 7. Screw; 8. Nut; 9. Mass block; 10. Control device; 11. Ball; 12. Angular contact ball bearing; 13. Grooved flywheel disc; 14. Flywheel mass block; 15. Wheel cover; 16. Linear slide; 17. Curved slide; 18. Tapered roller bearing. DETAILED DESCRIPTION

[0035] The embodiments of the present invention are described in detail below with reference to the accompanying drawings. However, the present invention can be implemented in many different ways as defined and covered by the claims.

[0036] Example:

[0037] A tuned inertial mass damper, see Figures 1 to 3 , including an outer frame 1, an elastic device, an inertia damping device and a mass block 9; the outer frame is a square frame, and the mass block 9 is suspended in the outer frame 1 through the elastic device and the inertia damping device; the inertia damping device includes a viscous damping unit, an inertia flywheel 6, a screw 7 and a nut 8; the viscous damping unit includes an outer cylinder 3 connected to the outer frame 1 and an inner roller 5 rotatably arranged in the outer cylinder 3; a viscous material 4 is also provided between the inner roller 5 and the outer cylinder 3 to provide resistance when the inner roller 5 rotates relative to the outer cylinder 3; the inner roller 5 and the inertia flywheel 6 are both fixedly connected to the nut 8; the nut 8 is threadedly connected to the screw 7, one end of the screw 7 is movably arranged in the inner roller 5 as a free end, and the other end is connected to the mass block 9. When the mass block vibrates up and down, it drives the screw to move linearly and horizontally up and down. At this time, the nut rotates and drives the inner roller and the inertia flywheel to rotate.

[0038] The tuned inertia mass damper of this embodiment adopts a ball screw inertia mechanism, which allows the device and the structure to transmit dynamic loads through only a single connection point. This can more effectively control and limit the distribution of additional stress on the main structure, protect the integrity and safety of the main structure, and facilitate installation, maintenance and replacement. At the same time, the use of balls can significantly reduce the friction effect, and compared with the gear rack inertia mechanism, it reduces the influence of gap nonlinearity and noise.

[0039] See also Figures 4 to 7 ,in, Figure 7 (a) is a schematic diagram before the wheel cover rotates. Figure 7 (b) is a schematic diagram after the wheel cover rotates; the inertial flywheel 6 includes a slotted flywheel disc 13, a wheel cover 15, and a flywheel mass 14; the slotted flywheel disc 13 is provided with a plurality of linear slots 16 in the radial direction, the wheel cover 15 is rotatably mounted on the slotted flywheel disc 13, and the wheel cover 15 is provided with curved slots 17 corresponding to the linear slots 16; the flywheel mass 14 is slidably mounted within both the linear slots 16 and the curved slots 17, so that when the wheel cover 15 rotates relative to the slotted flywheel disc 13, the curved slots 17 push the flywheel mass 14 along the linear slots 16; the slotted flywheel disc 13 is also fixedly connected to the nut 8. The number of the flywheel mass, linear slots, and curved slots is consistent, ranging from three to nine, with nine being preferred in this embodiment.

[0040] The tuned inertia mass damper of this embodiment adjusts the damper's inertia coefficient by changing the radius of the flywheel mass block or the size of the mass hammer in the inertial flywheel, thereby achieving effective control of multi-order frequency vibrations. It also has a wide adjustable range and a controllable frequency band that is wider than that of existing semi-active tuned inertia mass dampers.

[0041] The system further includes a control device 10, comprising a receiver, a processor, and a drive motor. The receiver is connected to an external vibrating structure to collect the vibration frequency of the vibrating structure and transmit it to the processor. The processor is also connected to the drive motor. The processor is configured to calculate the actual operating frequency of the tuned inertia mass damper, the inertia coefficient of the inertia damper, and the radius of the flywheel mass 14 within the slotted flywheel disc 13. The drive motor is configured to control the rotation angle of the wheel cover 15 relative to the slotted flywheel disc 13 based on signals from the processor, thereby driving the flywheel mass 14 to a specified position.

[0042] The tuned inertia mass damper of this embodiment realizes automatic control of the rotation angle of the wheel cover through the control device, that is, the inertia coefficient can be automatically adjusted as needed, realizing the adaptability of the damper to the multi-order modal vibration control of the structure; and only a small motor is needed to control the radial position of multiple flywheel mass blocks, which is lower in cost and higher in reliability.

[0043] The flywheel mass 14 is made of cast iron and is removable, allowing replacement of masses of different sizes. In situations where dynamic characteristics significantly change, such as due to unusual environmental conditions or structural fatigue damage, the flywheel mass's weight can be manually replaced, allowing for a wider range of adjustment of the TID's inertia coefficient, achieving effective vibration control.

[0044] The inner drum 5 is rotatably mounted within the outer drum 3 via a tapered roller bearing 18. The wheel cover 15 is rotatably mounted on the grooved flywheel disc 13 via two angular contact ball bearings 12. The bearings must withstand the weight of the inner drum 5 and nut 8, preventing the inertia flywheel 6 and the inner drum from moving up and down.

[0045] The nut 8 is a ball nut. The balls 11 inside can convert rotational friction into rolling friction, thereby significantly reducing the friction between the nut 8 and the screw rod 7.

[0046] The elastic device includes multiple springs 2, one end of each of which is connected to the outer frame 1 and the other end to the mass 9. In this embodiment, four springs are preferably provided, with two lugs on each side of the mass 9, symmetrically mounted. One end of each spring is connected to the top plate of the outer frame 1, keeping the springs vertical to ensure stability when the mass vibrates up and down, and to prevent excessive static deformation of the springs.

[0047] The mass block 9 is further provided with a lug plate; the spring 2 is connected to the mass block 9 via the lug plate.

[0048] In a further embodiment, when the mass 9 vibrates up and down, it drives the screw 7 in translation. At this point, the nut 8 rotates at high speed, driving the internal drum 5 and the flywheel 6 in rotation. The viscous material 4 undergoes shear deformation, generating a damping force. The flywheel 6 generates an inertial force far greater than its physical mass, achieving both inertial and energy efficiency gains. The height of the entire viscous damping unit should account for the amplitude of the mass 9's vibration, ensuring that the screw 7 remains within the internal drum 5 during translation and does not escape from the nut 8. The lugs of the mass 9 should be designed so that the distance between the springs 2 on either side covers the length of the flywheel at its maximum radius, i.e., greater than twice the maximum radius of the flywheel.

[0049] The control unit's receiver includes a vibration sensor. The drive motor is connected to the wheel cover 15 via a rocker lever, controlling its rotation. The vibration sensor monitors the dynamic response of the bridge structure. The vibration frequency is processed by the corresponding module in the control unit and used to calculate the required radial extension of the flywheel mass and the motor rotation angle. The required motor rotation angle is input to the drive motor, at which point the radial extension of the flywheel mass reaches the desired control value.

[0050] The actual operating frequency of the tuned inertial mass damper is:

[0051]

[0052] Where, k is the total spring stiffness; m s is the physical mass of the mass block; m in is the inertia coefficient of the inertia container;

[0053] The inertia container is a screw-type inertia container, and its inertia coefficient is the product of the square of the transmission ratio and the moment of inertia of the inertia flywheel:

[0054]

[0055] Among them, L d is the lead of the screw; J is the total moment of inertia of the flywheel and J=J s +J v ,J s is the total moment of inertia of the slotted flywheel disc and the wheel cover, J v is the moment of inertia of the flywheel mass:

[0056]

[0057] Where n is the number of flywheel masses or slideways; m i is the physical mass of each mass block; r o is the radius of the inertial flywheel; r vis the radial extension of the flywheel mass block. When the masses of the flywheel mass blocks are equal, that is, m i =m(i=1,2,…n), J v =nm(r o +r v ) 2 ;

[0058] Therefore, the required flywheel mass radius extension can be calculated based on the structural vibration frequency:

[0059]

[0060] The adjustable range of the flywheel mass block radius extension is (0, r m ), r m is the maximum extendable length of the mass block and r m Slightly smaller than r o , the corresponding wheel cover angle range is (0, θ) and

[0061] The drive motor is arranged between any two adjacent chute / mass blocks on the upper surface of the slotted flywheel disc 13, and the ratio of the distance to the center of the flywheel disc to the radius of the flywheel disc is:

[0062]

[0063] At this time, the driving motor can rotate in an angle range of (0, 2θ). When the radius extension of the mass block required for vibration control is r v When , the required motor rotation angle is (this formula assumes that the radius extension and the wheel cover rotation angle are linearly related, which is actually a complex trigonometric function relationship. In practical applications, a parabola or cubic function can be used for approximation):

[0064]

[0065] The rotation angle of the wheel cover 15 of the control device rocker adjustable should be the same as the angle between two adjacent flywheel mass blocks, so as to maximize the adjustable radius range of the flywheel mass block 14 of the inertia flywheel 6, which is zero to the inertia flywheel radius.

[0066] In another embodiment, a gear transmission is used instead of the rocker to rotate the wheel cover 15 to adjust the radial extension of the flywheel mass 14, thereby achieving precise adjustment of the rotation angle of the wheel cover 15.

[0067] Since structures may experience multimodal vibrations, and the vibration frequency is related to external excitations such as the environment and the structure's own stiffness, the tuned inertia mass damper provided in this embodiment can adapt to vibration control over a large frequency range and requires less energy input. In special circumstances, the mass hammer can also be replaced to adjust the inertia coefficient, thus having a wide range of applications.

[0068] The foregoing description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Those skilled in the art will readily appreciate that various modifications and variations of the present invention are possible. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention shall be included within the scope of protection of the present invention.

Claims

1. A tuned inertia mass damper, characterized in that: It includes an outer frame (1), an elastic device, an inertia damping device, and a mass block (9); The mass block (9) is suspended in the outer frame (1) via an elastic device and an inertia damping device; one end of the elastic device is connected to the outer frame (1), and the other end is connected to the mass block (9); The inertial capacity damping device comprises a viscous damping unit, an inertial flywheel (6), a screw (7) and a nut (8); the viscous damping unit comprises an outer cylinder (3) connected to the outer frame (1) and an inner roller (5) rotatably arranged in the outer cylinder (3); a viscous material (4) is further provided between the inner roller (5) and the outer cylinder (3) for providing resistance when the inner roller (5) rotates relative to the outer cylinder (3); The inner roller (5) and the inertia flywheel (6) are both fixedly connected to a nut (8); the nut (8) is threadedly connected to a screw rod (7); one end of the screw rod (7) is movably arranged in the inner roller (5), and the other end thereof is connected to a mass block (9); The inertia flywheel (6) comprises a grooved flywheel disc (13), a wheel cover (15) and a flywheel mass block (14); a plurality of linear slide grooves (16) are radially provided on the grooved flywheel disc (13); the wheel cover (15) is rotatably arranged on the grooved flywheel disc (13), and a curved slide groove (17) corresponding to the linear slide groove (16) is opened on the wheel cover (15); the flywheel mass block (14) is slidably arranged in the linear slide groove (16) and the curved slide groove (17) at the same time, so as to push the flywheel mass block (14) to slide along the linear slide groove (16) through the curved slide groove (17) when the wheel cover (15) rotates relative to the grooved flywheel disc (13); the grooved flywheel disc (13) is also fixedly connected to the nut (8).

2. The tuned inertia mass damper according to claim 1, characterized in that: Also included is a control device (10), wherein the control device (10) includes a receiver, a processor, and a drive motor; The receiver is connected to an external vibrating structure and is used to collect the vibration frequency of the vibrating structure and transmit it to a processor; the processor is also connected to a drive motor; the processor is used to calculate the actual operating frequency of the tuned inertia mass damper, the inertia coefficient of the inertia damping device, and the radius of the flywheel mass block (14) in the slotted flywheel disc (13); The drive motor is used to control the rotation angle of the wheel cover (15) relative to the slotted flywheel disc (13) according to a signal from a processor, thereby pushing the flywheel mass block (14) to a specified position.

3. The tuned inertia mass damper according to claim 1, characterized in that: The flywheel mass (14) is made of cast iron.

4. The tuned inertia mass damper according to claim 1, characterized in that: The inner roller (5) is rotatably arranged in the outer cylinder (3) via a tapered roller bearing (18); and the wheel cover (15) is rotatably arranged on the grooved flywheel disc (13) via two angular contact ball bearings (12).

5. The tuned inertia mass damper according to claim 1, characterized in that: The nut (8) is a ball nut.

6. The tuned inertia mass damper according to claim 1, characterized in that: The elastic device comprises a plurality of springs (2).

7. The tuned inertia mass damper according to claim 6, characterized in that: The mass block (9) is also provided with a lug plate; the spring (2) is connected to the mass block (9) via the lug plate.

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