Ball screw type tuned mass damper inertial container

Abstract

The application discloses a ball screw type tuned mass damper inertial container and relates to the technical field of structural damping, which comprises a mass block, a ball screw element, a shaft coupling, a flywheel and a slide rail, wherein the ball screw element comprises a screw shaft, a ball nut and balls; the ball nut is in contact connection with the screw shaft; the balls slide between the screw thread of the screw shaft and the internal track of the ball nut; the mass block is fixedly connected with the ball nut; the screw shaft is connected with the shaft coupling; and the shaft coupling drives the flywheel to rotate. The ball screw type inertial container can realize greater equivalent inertia through smaller physical mass, has adjustability and can be applied to various scenes. The application also introduces a one-way rotation modulator, which can ensure one-way rotation of the flywheel, widen the vibration absorption frequency band, and improve the stability, reliability and vibration control performance of the device.

Description

Technical Field

[0001] This invention relates to the field of structural vibration reduction technology, and in particular to a ball screw type tuned mass damping inertial container. Background Technology

[0002] Dynamic vibration absorbers have wide applications in various fields, such as structural engineering, where they are used to reduce structural vibrations caused by external excitations like earthquakes, wind loads, and traffic loads. They can reduce the dynamic response of structures, improving their stability and durability. In vibration engineering, dynamic vibration absorbers are used to control and reduce the vibrations of systems such as machinery, engines, and motors. They can reduce the amplitude and energy of vibrations, improving system stability and reliability. A common type of dynamic vibration absorber is the tuned mass damper, which typically consists of components such as a mass block, springs, and dampers. To achieve optimal vibration reduction, these components require relatively large installation space. However, in certain applications, especially in space-constrained environments such as inside wind turbine towers, the installation and deployment of tuned mass dampers can be severely limited. Furthermore, the weight of the tuned mass damper itself must also be considered; typically, to achieve better vibration reduction, the mass block is quite heavy, which increases the load and bearing requirements of the structure. Furthermore, in large flexible structures such as wind power equipment, environmental excitations are multi-source, and the structural dynamic response is extremely complex, often exhibiting multi-frequency broadband characteristics. Traditional single-frequency narrowband vibration absorbers, such as tuned mass dampers, have limited performance. Therefore, there is an urgent need to develop vibration absorber designs that are more compact and efficient.

[0003] Therefore, considering the limitations of current vibration dampers, in order to improve the mass tuning capability of dampers, those skilled in the art are committed to developing a tuned mass damping inertial container that can be used within a limited structural space, has small mass and short stroke, and is adaptive under certain conditions, so as to improve the vibration characteristics and overall performance of the main structure. Summary of the Invention

[0004] In view of the above-mentioned deficiencies of the prior art, the technical problem to be solved by the present invention is how to design a tuned mass damped inertial container with small mass, short stroke and self-adaptive characteristics within a limited structural space.

[0005] To achieve the above objectives, the present invention provides a ball screw type tuned mass damping inertia container, characterized in that it includes a mass block, a ball screw element, a coupling, a flywheel, and a slide rail. The ball screw element includes a screw shaft, a ball nut, and balls. The ball nut is in contact with the screw shaft, and the balls slide between the threads of the screw shaft and the internal track of the ball nut. The mass block is fixedly connected to the ball nut and is connected to both the mass block, the ball nut, and the slide rail. The screw shaft is connected to the coupling, and the coupling drives the flywheel to rotate.

[0006] Furthermore, the flywheel rotates coaxially with the lead screw shaft, and the flywheel has a detachable multi-layer nested structure. The number of nested layers and the moment of inertia of the flywheel can be adjusted.

[0007] Furthermore, it also includes a device housing, which is connected to the fixed end of the ball screw type tuned mass damping inertia container, and one end of the ball screw element is connected to the fixed end.

[0008] Furthermore, it also includes a rigid spring, the mass block and the ball nut are mounted on the tray of the slide rail, and the rigid spring is detachably connected between the tray and the housing of the device.

[0009] Furthermore, the mass block has a detachable layered structure, and the number of layers and weight of the mass block can be adjusted.

[0010] Furthermore, it also includes a unidirectional rotation modulator, which is installed between the coupling and the flywheel, and the unidirectional rotation modulator causes the flywheel to rotate in only one direction.

[0011] Furthermore, the unidirectional rotary modulator includes a bevel gear, a fixed gear, a left shaft, and a right shaft. The bevel gear includes a left bevel gear, a right bevel gear, and a lower bevel gear. The left bevel gear, the right bevel gear, and the lower bevel gear mesh with each other. One end of the left shaft is connected to the coupling, and the other end of the left shaft is connected to the one-way bearing inside the fixed gear and the one-way bearing inside the left bevel gear. One end of the right shaft is connected to the outer end of the fixed gear and the one-way bearing inside the right bevel gear, and the other end of the right shaft is connected to the flywheel.

[0012] Furthermore, the bevel gear is made of resin.

[0013] Furthermore, the surface of the slide rail is treated with a chrome plating process.

[0014] Furthermore, the coupling is made of aluminum alloy, and the mass block is made of high carbon steel.

[0015] This invention introduces the concept and structure of inertial capacity, combining a tuned mass damper with a ball screw-type inertial container to propose a novel tuned mass damped inertial container. This design, based on a ball screw-type inertial container, achieves greater equivalent inertia with a smaller physical mass. The tuned mass damped inertial container uses a small mass block to drive the ball screw to rotate, which in turn drives the flywheel. The rotation of the flywheel provides additional inertial force, thereby improving the inertial characteristics of the damper.

[0016] The tuned mass-damped inertial container and the main structure constitute a two-degree-of-freedom system. According to the formula... Based on optimal tuning theory, the optimal frequency ratio, optimal damping ratio, and peak response of the tuned mass damped inertial container under different excitation methods can be determined. The weight of the mass block, rigid spring, flywheel, etc., can be changed according to the results to adapt to different requirements. Here, m1 represents the mass of the main structure, m2 represents the mass of the tuned mass damped inertial container, k1 represents the stiffness of the main structure, k2 represents the stiffness of the tuned mass damped inertial container, c1 represents the damping of the main structure, c2 represents the damping of the tuned mass damped inertial container, b represents the capacitance coefficient, ω1 represents the natural frequency of the main structure, ω2 represents the natural frequency of the tuned mass damped inertial container, ζ1 represents the damping ratio of the main structure, ζ2 represents the damping ratio of the tuned mass damped inertial container, μ represents the mass ratio of the tuned mass damped inertial container to the main structure, and β represents the mass ratio of the capacitance to the main structure. By increasing the rotational inertia of the flywheel, this invention can effectively reduce the vibration amplitude of the main structure and improve the vibration control effect. Furthermore, existing ball screw-type inertial capacitance systems require reciprocating forward and reverse rotations. Due to factors such as friction and clearance within the system, the effective inertial mass and damping effect of the damper are weakened. Therefore, this invention introduces a unidirectional rotation modulator, ensuring that the flywheel end maintains unidirectional rotation, thus improving the stability and reliability of the inertial capacitance assembly. Simultaneously, the introduction of the unidirectional rotation modulator effectively broadens the vibration absorption bandwidth of the tuned mass damped inertial capacitance system, overcoming the limitation of narrow control bandwidth in traditional linear vibration absorbers.

[0017] This tuned mass damping inertial device is widely used in various applications. For example, in scenario one, wind turbine towers experience horizontal vibrations due to wind force. However, due to limited internal space, traditional dampers are unsuitable for the vibration reduction requirements of wind turbine towers because of their large required mass and volume. This tuned mass damping inertial device can be applied to wind turbine towers. The parameters of the damper's mass block, rigid spring, and flywheel can be calculated based on relevant theories and formulas to meet the vibration reduction requirements of the wind turbine tower. By adjusting the characteristics of the damper's mass block, rigid spring, and flywheel, personalized vibration reduction effects can be achieved to suit different types of wind turbine towers. Scenario 2: Applying this tuned mass damped inertial device inside an aircraft. During takeoff and landing, aircraft experience roll and yaw motions, which significantly impact flight safety. However, due to aircraft weight design limitations, excessively large dampers cannot be used to mitigate these effects. Therefore, the damper scheme proposed in this paper offers significant advantages. This scheme allows for adjustments to the damper's mass, damping performance, and stiffness according to the requirements of different aircraft models to achieve optimal vibration reduction. Furthermore, this scheme can achieve greater inertia while maintaining a smaller mass, further improving vibration reduction efficiency. Scenario 3: In industrial production lines, mechanical components typically undergo high-speed rotation, reciprocating motion, or other processes during operation. These movements can cause vibrations and impacts, potentially posing problems for equipment and the working environment. Because these mechanical components are usually highly precise, vibration suppression requirements are extremely high. Therefore, highly precise tuned vibration reduction measures are necessary. By calculating the parameters based on the above formula, this damper can achieve accurate tuned vibration reduction effects to meet the high-precision vibration control requirements of mechanical components.

[0018] The tuned mass damped inertial container provided by this invention has the following beneficial technical effects:

[0019] 1. In existing ball screw-type inertial capacities, the flywheel rotates along with the ball screw, and its rotation direction is not fixed. When the rotation direction changes, its inertia causes a sudden change, resulting in impact force and vibration. This may cause other components of the system to be subjected to additional stress and pressure, leading to mechanical wear, breakage, or damage. Moreover, traditional linear vibration absorbers have a narrow control bandwidth and poor robustness. When there is an error in the vibration absorber tuning, the vibration control effect will be greatly reduced. This invention adds a unidirectional rotation modulator between the ball screw and the flywheel, so that the flywheel rotates in a fixed direction, improving system reliability, effectively widening the vibration control bandwidth, improving the overall performance of the tuned mass damped inertial capacities, reducing the impact force generated during flywheel turning, and improving the effective inertial mass of the inertial capacities and the vibration reduction effect of the dampers.

[0020] 2. Current traditional dampers typically rely on large physical masses for vibration control. However, this large mass addition can significantly impact the characteristics of the main structure, potentially leading to a series of problems. This invention employs a ball screw-type inertia container, achieving a large nominal inertia with a smaller physical mass, effectively reducing the required physical mass while achieving vibration reduction. The ball screw element consists of a screw shaft, a ball nut, and balls. The horizontal reciprocating motion of the mass block drives the ball nut to move on the ball screw element, causing the screw shaft to rotate under the action of the balls. Through the connection of a coupling and a unidirectional rotary modulator, the flywheel rotates, generating a large inertial mass. By converting the translational motion of the mass block into the rotational motion of the flywheel, the significant inertial mass generated by the flywheel rotation effectively reduces the actual weight of the tuning mass block.

[0021] 3. Traditional dampers have limited application ranges, and often require replacement when changing application scenarios. The damper of this invention is adjustable; the mass of the mass block, the wire diameter and number of springs, and the thickness, diameter, and number of flywheels can all be changed according to the actual application scenario. The tuned mass damped inertial container of this invention forms a two-degree-of-freedom system with the main structure. Based on optimal harmonicity theory, the optimal frequency ratio, optimal damping ratio, and peak response results of the tuned mass damped inertial container under different excitation methods can be obtained. Based on the results, the weight of the mass block, the rigidity of the springs, the flywheels, etc., can be changed to adapt to different requirements. The adjustability of this damper expands its application range, making it suitable for various scenarios.

[0022] The following will further explain the concept, specific structure, and technical effects of the present invention in conjunction with the accompanying drawings, so as to fully understand the purpose, features, and effects of the present invention. Attached Figure Description

[0023] Figure 1 This is a three-dimensional structural schematic diagram of a ball screw type tuned mass damping inertial container according to a preferred embodiment of the present invention.

[0024] Figure 2 This is a three-dimensional structural schematic diagram of a ball screw element in a ball screw type tuned mass damping inertial container according to a preferred embodiment of the present invention.

[0025] Figure 3 This is a schematic diagram of the planar structure of a unidirectional rotary modulator of a ball screw type tuned mass damped inertial container according to a preferred embodiment of the present invention.

[0026] Figure 4 This is a schematic diagram of the structural arrangement of the coupling, unidirectional rotary modulator and flywheel of a ball screw type tuned mass damping inertial container according to a preferred embodiment of the present invention.

[0027] Among them, 1-fixed end, 2-device housing, 3-slide rail, 4-tray, 5-mass block, 6-ball nut, 7-lead screw shaft, 8-rigid spring, 9-coupling, 10-bevel gear, 11-one-way bearing, 12-flywheel, 13-connecting shaft. Detailed Implementation

[0028] The following description, with reference to the accompanying drawings, illustrates several preferred embodiments of the present invention to make its technical content clearer and easier to understand. The present invention can be embodied in many different forms, and the scope of protection of the present invention is not limited to the embodiments mentioned herein.

[0029] In the accompanying drawings, components with the same structure are indicated by the same numerical designation, and components with similar structures or functions are indicated by similar numerical designations. The dimensions and thicknesses of each component shown in the drawings are arbitrary, and the present invention does not limit the dimensions and thicknesses of each component. To make the illustrations clearer, the thickness of some components has been appropriately exaggerated in the drawings.

[0030] like Figure 1The diagram illustrates a ball screw-type tuned mass damping inertial container. This device can be installed in confined spaces to reduce vibrations of the main structure, such as inside a wind turbine tower. It effectively reduces the impact of wind or wave loads on the tower, preventing resonance and excessive displacement, reducing fatigue damage to the wind turbine and tower, and improving the reliability and lifespan of the wind power generation system. When applied to aircraft and spacecraft structures, it can reduce vibration and impact during flight, improving stability and safety. Taking a wind turbine tower as an example, during the horizontal movement of the tower, the mass block 5 inside the inertial container automatically adjusts its position according to the tower's vibration frequency. The rigid spring 8 deforms, providing the required elastic force to the mass block 5. The mass block 5 moves linearly, causing the balls to move between the screw shaft 7 and the ball nut 6 via the ball nut 6, which in turn drives the screw shaft 7 and the flywheel 12 to rotate, generating inertial force. The flywheel 12 can be adjusted to achieve the required inertial force by changing the number, diameter, and thickness of the flywheels according to different inertial requirements. The stiffness of the rigid spring 8 and the moment of inertia of the flywheel 12 are functions of the natural frequency of the controlled object and the mass of the mass block 5, and can be calculated according to optimal tuning theory or optimization algorithms to achieve optimal vibration control. The rigid spring 8 can be adjusted according to different usage conditions, and its stiffness can be calculated based on the characteristic vibration frequency of the controlled object using fixed-point theory. The rigid spring 8 can achieve the required stiffness by changing the number, wire diameter, and length of the springs according to different scenarios. The mass block 5 is a detachable layered structure; the number of layers can be adjusted to adjust its dynamic mass according to different vibration control objects, achieving optimal vibration control. The mass block 5 can achieve the required mass by changing the number of mass blocks according to different scenarios. Through optimized design, when the weight and elastic force of the mass block 5 reach the optimal control parameters, the natural frequency of the inertial container is consistent with the first-order vibration frequency of the tower, thereby achieving precise suppression of the wind turbine tower's motion.

[0031] like Figure 1 , Figure 2 , Figure 3 and Figure 4As shown, a ball screw-type tuned mass damping inertia container includes a mass block 5, a ball screw element, a coupling 9, a one-way rotary modulator, a flywheel 12, a rigid spring 8, a slide rail 3, and a device housing 2. The mass block 5 is adjustable in weight and connected to the ball nut 6 of the ball screw element, while simultaneously mounted on the tray of the slide rail 3 to achieve reciprocating motion in the horizontal direction. The ball screw element consists of a screw shaft 7, a ball nut 6, and balls. The horizontal reciprocating motion of the mass block 5 drives the ball nut 6 to move on the ball screw element, thereby causing the screw shaft 7 to rotate under the action of the balls. One end of the ball screw element is fixed to a fixed end 1 connected to the device housing 2, and the other end is connected to the coupling 9. The coupling 9 allows the one-way rotary modulator to rotate coaxially with the screw shaft 7. The one-way rotary modulator consists of a one-way bearing 11 and a bevel gear 10, connected to the coupling 9 on the left and the flywheel 12 on the right. Through the cooperation of bearings and gear transmission, the flywheel 12 on the right side will rotate clockwise regardless of whether the left ball screw shaft 7 rotates clockwise or counterclockwise. The flywheel 12 is detachable and provides a large inertial force to the system through rotation. One end of the rigid spring 8 is connected to the tray below the mass block 5, and the other end is connected to the housing 2 of the device, providing elastic force. The adjustment of the mass block 5, the rotation of the ball screw element, and the inertial force of the flywheel 12 combine to effectively absorb and dissipate vibration energy.

[0032] like Figure 2 As shown, the tuned mass damping inertia container uses a ball screw type inertia capacitive element, in which the ball nut 6 is fixedly connected to the mass block 5. When the mass block 5 moves, it drives the ball nut 6 to move linearly, causing the balls to slide between the threads of the screw shaft 7 and the internal track of the ball nut 6, thereby driving the rotation of the screw shaft 7. When the screw shaft 7 rotates, the flywheel 12 is driven to rotate through the coupling 9 and the unidirectional rotation modulator, providing a certain inertial force for the entire system. This allows the tuned mass device to provide a large inertial force with a small weight, thereby reducing the added mass of the device and shortening the stroke of the mass block 5, more effectively reducing the overall motion amplitude in a confined space, and extending the service life of the equipment.

[0033] like Figure 3 and Figure 4As shown, a coupling 9 and a unidirectional rotary modulator are used inside the tuned mass damped inertial container. This unidirectional rotary modulator consists of a unidirectional bearing, three meshing bevel gears (left, right, and lower), one fixed gear, and two shafts (left and right shafts), with the bevel gears on both sides having identical specifications. The unidirectional rotary modulator introduces frictional damping with nonlinear dynamic factors by switching the bevel gear pair, thereby achieving a dynamic effect of widening the vibration absorption frequency band. When the left lead screw 7 rotates clockwise, the left one-way bearing rotates clockwise, while the left bevel gear remains stationary. Coupling 9 drives the left shaft to rotate clockwise. Through the shaft's transmission, the one-way bearing inside the middle fixed gear rotates clockwise, driving the middle gear to rotate clockwise. The outer end of the middle gear is connected to the right shaft of the one-way rotation modulator. The right shaft rotates clockwise, driving the flywheel 12 to rotate clockwise. When the left lead screw 7 rotates counterclockwise, the left one-way bearing rotates counterclockwise, driving the left bevel gear to rotate counterclockwise. Through the transmission of the lower bevel gear, the right bevel gear rotates clockwise, driving the right one-way bearing to rotate clockwise. This causes the right shaft connected to the right one-way bearing to rotate clockwise, ultimately achieving clockwise rotation of the flywheel 12. This reduces the impact force that may be generated during flywheel reversal. Because the flywheel can only rotate clockwise, instability and vibration that may occur during reversal are avoided, ensuring the smoothness and reliability of the system operation.

[0034] The present invention also includes the following features:

[0035] Preferably, the mass block 5 is made of high-carbon steel or other high-density alloy materials to ensure that the mass block has a large mass while maintaining a small volume, thereby saving the arrangement space of the tuned mass damper.

[0036] Preferably, all components of the ball screw element are made of high-strength alloy materials. The screw shaft 7 is in contact with the ball nut 6, which contains balls that move along tracks within the screw shaft 7 and the ball nut 6. Simultaneously, the internal tracks of the ball nut 6 remain smooth to ensure smooth ball movement. This design and material selection provide high strength and durability, ensuring the reliability and efficiency of the ball screw element during operation.

[0037] Preferably, the flywheel 12 rotates coaxially with the lead screw shaft 7. The flywheel 12 has a detachable multi-layer nested structure. The rotational inertia of the flywheel can be adjusted by increasing or decreasing the number of nested layers according to the characteristic vibration frequency of the controlled object. The mass and diameter of the flywheel 12 can be reasonably designed according to the calculated optimal inertial force requirements to ensure that the flywheel provides appropriate inertial effect in the system, thereby enhancing the performance and effectiveness of the damper.

[0038] Preferably, coupling 9 is made of high-strength aluminum alloy material, which has excellent strength and rigidity, can withstand high torque and speed, and ensures the reliability and durability of coupling 9.

[0039] Preferably, the bevel gear 10 is made of resin to reduce inertia generated during movement. The special tooth profile and precision manufacturing of the bevel gear 10 ensure high transmission efficiency, thereby reducing energy loss and heat generation.

[0040] Preferably, the surface of the slide rail 3 is treated with chrome plating to improve its surface hardness and wear resistance, reduce friction and wear between the slide rail 3 and other parts, and extend its service life.

[0041] The preferred embodiments of the present invention have been described in detail above. It should be understood that those skilled in the art can make numerous modifications and variations based on the concept of the present invention without creative effort. Therefore, all technical solutions that can be obtained by those skilled in the art based on the concept of the present invention through logical analysis, reasoning, or limited experimentation on the basis of existing technology should be within the scope of protection defined by the claims.

Claims

1. A ball screw type tuned mass damping inertial container, characterized in that, The system includes a mass block, a ball screw element, a coupling, a flywheel, and a slide rail. The ball screw element comprises a screw shaft, a ball nut, and balls. The ball nut is in contact with the screw shaft, and the balls slide between the threads of the screw shaft and the internal track of the ball nut. The mass block is fixedly connected to the ball nut and the slide rail. The screw shaft is connected to the coupling, which drives the flywheel to rotate. The system also includes a one-way rotation modulator installed between the coupling and the flywheel. The unidirectional rotation modulator causes the flywheel to rotate in only one direction. The unidirectional rotation modulator includes a bevel gear, a fixed gear, a left shaft, and a right shaft. The bevel gear includes a left bevel gear, a right bevel gear, and a lower bevel gear. The left bevel gear, the right bevel gear, and the lower bevel gear mesh with each other. One end of the left shaft is connected to the coupling, and the other end of the left shaft is connected to the one-way bearing inside the fixed gear and the one-way bearing inside the left bevel gear. One end of the right shaft is connected to the outer end of the fixed gear and the one-way bearing inside the right bevel gear, and the other end of the right shaft is connected to the flywheel.

2. The ball screw type tuned mass damping inertial container as described in claim 1, characterized in that, The flywheel rotates coaxially with the lead screw shaft. The flywheel has a detachable multi-layered nested structure, and the number of nested layers and the moment of inertia of the flywheel can be adjusted.

3. The ball screw type tuned mass damping inertial container as described in claim 1, characterized in that, It also includes a housing, which is connected to the fixed end of the ball screw type tuned mass damping inertia container, and one end of the ball screw element is connected to the fixed end.

4. The ball screw type tuned mass damping inertial container as described in claim 3, characterized in that, It also includes a rigid spring, the mass block and the ball nut are mounted on the tray of the slide rail, and the rigid spring is detachably connected between the tray and the housing of the device.

5. A ball screw type tuned mass damping inertial container as described in claim 1, characterized in that, The mass block has a detachable layered structure, and the number of layers and weight of the mass block can be adjusted.

6. The ball screw type tuned mass damping inertial container as described in claim 1, characterized in that, The bevel gear is made of resin.

7. A ball screw type tuned mass damping inertial container as described in claim 1, characterized in that, The surface of the slide rail is treated with chrome plating.

8. A ball screw type tuned mass damping inertial container as described in claim 1, characterized in that, The coupling is made of aluminum alloy, and the mass block is made of high carbon steel.

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