Tuned inerter mass damper

Abstract

The invention belongs to the technical field of vibration control, and discloses a tuning inerter mass damper which comprises an outer frame, an elastic device, an inerter damping device and a mass block. The mass block is suspended in the outer frame through the elastic device and the inerter damping device; the inerter damping device comprises a viscous damping unit, an inertia flywheel, a screw rod and a nut; the viscous damping unit comprises an outer cylinder connected with the outer frame and an inner roller rotationally arranged in the outer cylinder. A viscous material is arranged between the inner roller and the outer cylinder; the internal roller and the inertia flywheel are fixedly connected with the nut; the nut is in threaded connection with the lead screw, and one end of the lead screw is connected with the mass block. By adjusting the inerter coefficient, effective control over multi-order frequency vibration is achieved, the adjustable range is wide, the vibration damper is suitable for structural multi-frequency vibration control such as multi-order vortex vibration control of a suspension bridge, installation and maintenance are easy, the additional effect on the structure is small, and the vibration damping efficiency is high.

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 develop towards larger and more flexible directions, under complex natural conditions and social environments, structures often experience vibration responses in multiple frequency ranges, which not only accelerates structural fatigue and reduces service life, but also affects structural safety and comfort.

[0003] Traditional tuned mass dampers (TMDs) are mainly effective at reducing vibration at a single frequency and cannot meet the control requirements of structures vibrating at multiple frequencies. Although multi-tuned mass dampers (MTMDs) can control multiple frequencies, they are bulky, difficult to install and maintain, and their non-working parts easily interfere with the control of the structure, making them less applicable.

[0004] Semi-active systems can adjust the damper characteristics by driving the actuator through external energy to adjust the damper's operating frequency in real time. At present, adaptive vibration reduction systems mainly change the stiffness by driving complex mechanical devices to change the constraints of the tuned mass damper (TMD) or the length of the elastic component. The system is usually 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 working frequency of the tuned inertia mass damper by adjusting the inertia coefficient, thereby achieving effective control of multiple modal vibrations within a wider 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 capacity damping device comprises a viscous damping unit, an inertial flywheel, a screw and a nut; the viscous damping unit comprises an outer cylinder connected to the outer frame and an inner cylinder rotatably arranged in the outer cylinder; a viscous material is also arranged between the inner cylinder and the outer cylinder to provide resistance when the inner cylinder rotates relative to the outer cylinder;

[0011] The internal roller 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 roller, and the other end thereof is connected to a mass block.

[0012] Preferably, the inertial 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 in 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 with the nut.

[0016] Preferably, it 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 vibration structure to collect the vibration frequency of the vibration 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 driving motor is used to control the rotation angle of the wheel cover relative to the grooved flywheel disc according to the signal of the processor, so as to push the flywheel mass block to a specified position;

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

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

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

[0022] Preferably, the elastic device comprises 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. The invention has a wide adjustable range, better versatility, and a wider controllable frequency band than the existing semi-active tuned inertia mass damper.

[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 attached drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 is a schematic structural diagram of a tuned inertia mass damper in 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 the control device;

[0031] Figure 5 for Figure 4 Schematic diagram of the connection relationship of the flywheel disc with a groove 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 mode 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, but 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 arranged 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, which is 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, so that the device and the structure can transfer dynamic loads only through a single connection point, which 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, 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 grooved flywheel disc 13, a wheel cover 15 and a flywheel mass block 14; the grooved flywheel disc 13 is provided with a plurality of linear slide grooves 16 in the radial direction, the wheel cover 15 is rotatably arranged on the grooved flywheel disc 13, and the wheel cover 15 is provided with a curved slide groove 17 corresponding to the linear slide groove 16; the flywheel mass block 14 is slidably arranged in the linear slide groove 16 and the curved slide groove 17 at the same time, and is used for pushing 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. The flywheel mass block and the number of linear slide grooves and curved slide grooves are consistent, and are all three to nine. In this embodiment, nine are preferably arranged.

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

[0041] The invention also includes a control device 10, which includes a receiver, a processor and a drive motor; the receiver is connected to an external vibration structure to collect the vibration frequency of the vibration structure and transmit it to the processor; the processor is also connected to the 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 grooved flywheel disc 13; the drive motor is used to control the rotation angle of the wheel cover 15 relative to the grooved flywheel disc 13 according to the signal of the processor, so as to push the flywheel mass block 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, thereby realizing the adaptability of the damper to the multi-order modal vibration control of the structure; and only one small motor is needed to control the radial position of multiple flywheel mass blocks, which has lower cost and higher reliability.

[0043] The flywheel mass block 14 is made of cast iron and can be detachably installed to replace mass blocks of different sizes. When the dynamic characteristics change greatly under special environmental conditions or when the structure is damaged by fatigue, the mass hammer of the flywheel mass block can be replaced manually, thereby adjusting the inertia coefficient of the tuned inertia mass damper in a wider range to achieve effective vibration control.

[0044] The inner drum 5 is rotatably arranged in the outer drum 3 through a tapered roller bearing 18; the wheel cover 15 is rotatably arranged on the grooved flywheel disc 13 through two angular contact ball bearings 12. The bearing needs to bear the gravity of the inner drum 5 and the nut 8, etc., so that the inertial flywheel 6 and the inner drum will not move up and down.

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

[0046] The elastic device includes a plurality of springs 2, one end of the spring 2 is connected to the outer frame 1, and the other end is connected to the mass block 9. In this embodiment, preferably there are four springs, two ear plates are respectively provided on the left and right sides of the mass block 9 and are symmetrically installed, one end of the spring is connected to the top plate of the outer frame 1 and the spring is kept vertical to ensure the stability of the mass block when it vibrates up and down, and the spring should not have excessive static deformation.

[0047] 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.

[0048] In a further embodiment, when the mass block 9 vibrates up and down, it drives the screw 7 to move up and down. At this time, the nut 8 rotates at high speed and drives the internal drum 5 and the inertia flywheel 6 to rotate. The viscous material 4 undergoes shear deformation to generate damping force, and the inertia flywheel 6 generates an inertia force far greater than its physical mass, thereby achieving inertia efficiency and energy efficiency. The height of the entire viscous damping unit should take into account the amplitude of the mass block 9, so that the screw 7 is always located in the internal drum 5 when it moves horizontally, and does not separate from the nut 8. The ear plate of the mass block 9 should be such that the distance between the springs 2 on both sides can cover the length of the maximum radius of the inertia flywheel, that is, greater than twice the maximum radius of the inertia flywheel.

[0049] The receiver of the control device includes a vibration sensor. The drive motor is connected to the wheel cover 15 through a rocker to control the rotation of the wheel cover 15. The vibration sensor is used to monitor the dynamic response of the bridge structure. The vibration frequency of the structure is obtained through processing by the corresponding module in the control device, and the required radial extension of the flywheel mass block and the motor rotation angle are calculated. The required motor rotation angle is input into the drive motor, and at this time, the radial extension of the flywheel mass block reaches the required value for control.

[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 rotational 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 each flywheel mass block are equal, that is, m i =m(i=1,2,…n), J v =nm(r o +r v ) 2 ;

[0058] Therefore, the required radial extension of the flywheel mass block 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 driving motor is arranged between any two adjacent slide grooves / mass blocks on the upper surface of the grooved 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 rotation angle of the motor is (this formula assumes that the radius extension and the rotation angle of the wheel cover 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 inertial flywheel 6, which is zero to the inertial 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, so as to achieve precise adjustment of the rotation angle of the wheel cover 15.

[0067] Since the structure may experience multi-modal vibration, and the vibration frequency is related to external excitations such as the environment and the stiffness of the structure itself, the tuned inertia mass damper provided in this embodiment can adapt to vibration control in a larger frequency range and requires less energy input; in special circumstances, the mass hammer can also be replaced to adjust the inertia coefficient, and the scope of application is wide.

[0068] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A tuned inertia mass damper, characterized in that: It comprises 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; The inertia 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 cylinder (5) rotatably arranged inside the outer cylinder (3); a viscous material (4) is further arranged between the inner cylinder (5) and the outer cylinder (3) for providing resistance when the inner cylinder (5) rotates relative to the outer cylinder (3); The internal 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 internal roller (5), and the other end thereof is connected to a mass block (9).

2. A tuned inertia mass damper according to claim 1, characterized in that: The inertial flywheel (6) comprises a flywheel disc with grooves (13), a wheel cover (15) and a flywheel mass block (14); The grooved flywheel disc (13) is provided with a plurality of linear slide grooves (16) along the radial direction, the wheel cover (15) is rotatably arranged on the grooved flywheel disc (13), and the wheel cover (15) is provided with curved slide grooves (17) corresponding to the linear slide grooves (16); The flywheel mass block (14) is slidably arranged in the linear slide groove (16) and the curved slide groove (17) at the same time, and is used 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).

3. A tuned inertia mass damper according to claim 2, 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 the external vibration structure and is used to collect the vibration frequency of the vibration structure and transmit it to the processor; the processor is also connected to the 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 grooved flywheel disc (13); The driving motor is used to control the rotation angle of the wheel cover (15) relative to the grooved flywheel disc (13) according to the signal of the processor, thereby pushing the flywheel mass block (14) to reach a specified position.

4. A tuned inertia mass damper according to claim 2, characterized in that: The flywheel mass block (14) is made of cast iron.

5. The tuned inertia mass damper according to claim 2, characterized in that: The inner drum (5) is rotatably arranged in the outer cylinder (3) via a tapered roller bearing (18); the wheel cover (15) is rotatably arranged on the grooved flywheel disc (13) via two angular contact ball bearings (12).

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

7. The tuned inertia mass damper according to claim 1, characterized in that: The elastic device comprises a plurality of springs (2), one end of each spring (2) being connected to the outer frame (1) and the other end of each spring (2) being connected to the mass block (9).

8. A tuned inertia mass damper according to claim 7, 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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