Inerter and active suspension

Abstract

The invention discloses an inerter which comprises a chuck, a flywheel mass block and a shell. The chuck is arranged in the shell, and a plurality of sliding grooves are circumferentially distributed in the chuck with the circle center as the center. A plurality of flywheel mass blocks are arranged, and sliding blocks are arranged at the bottoms of the flywheel mass blocks and are arranged in the sliding grooves of the chuck in a sliding manner; a fixing frame is arranged on the back of the shell, a worm is arranged in the fixing frame in a sliding mode, a worm gear is fixed to the back of the chuck and meshed with the worm, and flywheel mass blocks can be driven to synchronously move in the same direction or back to back in the radial direction by controlling rotation of the worm, so that the rotational inertia of the flywheel mass blocks is adjusted. Through the structure of the worm gear, the worm and the chuck, the position of the flywheel mass block can be adjusted in the radial direction, so that the flywheel mass block can keep excellent dynamic balance and operation stability in any working posture so as to cope with different loads and vibration environments.

Description

Technical Field

[0001] This invention relates to an automotive shock absorption device, and more particularly to an inertial container and an active suspension. Background Technology

[0002] A linear active suspension typically consists of actuators, springs, and shock absorbers. Springs are responsible for adjusting vehicle height and suspension stiffness to ensure good ride comfort; shock absorbers are used to adjust damping force; and actuators dynamically adjust the suspension stiffness and damping characteristics according to control commands.

[0003] An inertial container is a device that can absorb and reduce vibration and shock in a machine system. However, the existing inertial containers have the following problems: because the radial position of the flywheel mass is fixed, the flywheel mass cannot maintain good dynamic balance when facing different loads and vibration environments, and its operation is unstable and has poor adaptability. Therefore, in order to cope with different loads and vibration environments, the flywheel mass needs to be replaced according to the corresponding load and vibration environment, which is not convenient to use. Summary of the Invention

[0004] To address the aforementioned technical problems, this invention provides an inertial container and an active suspension system, which enables the flywheel mass block to maintain good dynamic balance and operate stably when facing different loads and vibration environments.

[0005] To solve the above-mentioned technical problems, the present invention adopts the following technical solution: an inertia container, comprising a chuck, a flywheel mass block, and a housing; the chuck is disposed inside the housing, and multiple sliding grooves are distributed circumferentially around the center of the chuck; multiple flywheel mass blocks are provided, each with a slider at its bottom, which is slidably disposed in the sliding groove of the chuck; a fixing frame is provided on the back of the housing, and a worm gear is slidably disposed within the fixing frame; a worm wheel is fixed on the back of the chuck, and the worm wheel meshes with the worm gear. By controlling the rotation of the worm gear, the flywheel mass blocks can be driven to move synchronously in opposite directions or in the radial direction, thereby adjusting the rotational inertia of the flywheel mass blocks.

[0006] Furthermore, the moment of inertia of the flywheel mass block can be continuously adjusted between I_min and I_max, and the inertia coefficient b can be adjusted accordingly.

[0007] The moment of inertia of the flywheel mass is: I = Σ m r²

[0008] Where: m: mass of the mass block; r: radius of the mass block's center of mass from the center of rotation;

[0009] The inertia coefficient b = (2π / L)² × I, where L is the lead screw.

[0010] Furthermore, the housing is provided with an adjusting screw, which is connected to the worm gear.

[0011] Furthermore, in this invention, the flywheel mass block is an elongated arc shape, and four of them are provided.

[0012] Furthermore, this invention also provides an active suspension, including a linear actuator, a spring assembly, a damper, and a mounting bracket; it also includes any of the aforementioned inertia containers; the linear actuator is a ball screw assembly with a hollow structure, driven by a motor to perform linear motion; the upper end of the spring assembly is connected to the housing of the linear actuator, and the lower end of the spring assembly is connected to the mounting bracket, the spring assembly being stretched or compressed as the linear actuator moves; the damper is disposed inside the hollow structure of the linear actuator, and a damper piston is located at the front end of the damper; the inertia container is fixed to the upper end of the ball nut of the ball screw and rotates synchronously with the nut; the upper end of the mounting bracket is connected to the damper piston, and the bottom of the mounting bracket moves up and down with the stretching and compression of the spring assembly; when the mounting bracket is squeezed by the vehicle body, it pushes the damper piston upward and compresses the spring assembly.

[0013] Furthermore, in this invention, the inertial container is connected to the ball screw and then strung between the vehicle body and the wheel, which is mechanically equivalent to adding an interferometer element between (z_s) and (z_u);

[0014] The formula for the inertia coefficient b is as follows:

[0015]

[0016]

[0017] Where L is the lead screw; (I) is the equivalent moment of inertia of the flywheel;

[0018] Body mass, i.e., sprung mass: displacement (z_s(t));

[0019] Wheel / suspension assembly unsprung mass: displacement (z_u(t));

[0020] The axial force generated by the linear actuator is denoted as (F_a(t)), which is positive upwards for the vehicle body and opposite in direction for the wheels.

[0021] Furthermore, the ball screw has multiple ball spline grooves evenly distributed around its circumference, and the ball spline connects the screw to the housing.

[0022] Furthermore, the linear actuator is provided with a top connecting shell on its upper part, and a position sensor is provided inside the linear actuator. The position sensor is connected to the damper piston through a position sensor rod, which extends downward into the mounting bracket. A load sensor is provided on the top connecting shell.

[0023] Furthermore, in this invention, the spring assembly is a helical spring, with the upper end of the helical spring connected to the outer shell via an upper spring mounting seat, and the lower end of the helical spring connected to a mounting bracket via a lower spring mounting seat.

[0024] The beneficial effects of adopting the above technical solution are as follows: by integrating the flywheel and ball bearing nut into an "inertia container," the automotive shock absorption system achieves an upgrade from the traditional "mass-spring-damping" system to a "mass-spring-damping-inertia container" system. This design, through the inertial effect of the flywheel, endows the shock absorber with the ability to intelligently identify and respond to road input frequencies, thereby achieving a breakthrough balance between comfort and handling.

[0025] The worm gear and chuck structure allows for radial adjustment of the flywheel mass block's position, ensuring that the flywheel's center of mass always coincides perfectly with the axis of rotation, both in static and high-speed rotating states. This symmetry fundamentally counteracts the centrifugal force and inertial coupling effects caused by mass eccentricity, enabling the flywheel mass block to maintain excellent dynamic balance and operational stability in any working posture, thus coping with different loads and vibration environments. This adjustable mechanism provides broad adaptability to the core inertial capacitance component without requiring replacement of the flywheel itself, greatly enhancing the system's integration and ease of maintenance. Attached Figure Description

[0026] Figure 1 This is a schematic diagram of the structure of the inertial container of the present invention;

[0027] Figure 2 This is a schematic diagram of the flywheel mass block of the present invention. Figure 1 (Remove the casing)

[0028] Figure 3 This is a schematic diagram of the rear structure of the inertial container of the present invention;

[0029] Figure 4 This is a schematic diagram of the adjusting screw of the inertial container of the present invention;

[0030] Figure 5 This is a cross-sectional structural schematic diagram of the active suspension of the present invention;

[0031] Figure 6 This is a schematic diagram of the active suspension system of the present invention;

[0032] Figure 7 This is a schematic diagram of the inertial container connection of the present invention;

[0033] Figure 8 This is a schematic diagram of the active suspension system of the present invention;

[0034] In the diagram: 1. Sensor rod, 2. Load sensor, 3. Top connecting shell, 4. Housing, 5. Upper isolator, 6. Lower isolator, 7. Spring, 8. Mounting bracket, 9. Piston, 10. Position sensor, 11. Ball spline, 12. Damper, 13. Ball screw, 14. Lower bearing assembly, 15. Steel ball, 16. Stator, 17. Rotor, 18. Ball nut, 19. Upper bearing assembly, 20. Inertia container, 201. Slide groove, 202. Chuck, 203. Flywheel mass block, 204. Housing, 205. Slider, 206. Fixing bracket, 207. Worm gear, 208. Worm wheel, 209. Adjusting screw, 21. Controller, 22. Vehicle body at the wheel. Detailed Implementation

[0035] The present invention will now be described in further detail with reference to the accompanying drawings.

[0036] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0037] One embodiment of the present invention: as follows Figure 1 , Figure 2 and Figure 3 As shown, an inertia container includes a chuck 202, a flywheel mass block 203, and a housing 204. The chuck 202 is disposed inside the housing 204, and multiple grooves 201 are distributed circumferentially around the center of the chuck 202. There are multiple flywheel mass blocks 203, and each flywheel mass block 203 has a slider 205 at its bottom, which is slidably disposed in the grooves 201 of the chuck 202. A fixing frame 206 is provided on the back of the housing 204, and a worm gear 207 is slidably disposed inside the fixing frame 206. A worm wheel 208 is fixed on the back of the chuck 202, and the worm wheel 208 meshes with the worm gear 207. By controlling the rotation of the worm gear 207, the flywheel mass blocks 203 can be driven to move synchronously in opposite directions or in the radial direction, thereby adjusting the rotational inertia of the flywheel mass blocks.

[0038] The flywheel can change its moment of inertia during operation by controlling the rotation of the worm 207. The rotational input of the worm 207 is converted into the rotation of the worm wheel 208, and the chuck 202, which is fixed to the worm wheel 208, rotates together, thereby driving the flywheel mass block 203 to move synchronously in opposite directions or radially. The inherent reverse self-locking characteristic of the worm gear mechanism is key to the reliability of this design. It ensures that once the adjustment is complete, the position of the flywheel mass block 203 will remain absolutely fixed under any complex dynamic load, without the need for continuous power supply locking. This operating mode allows the system to flexibly and precisely adjust the mass distribution moment of the entire rotating body, effectively offsetting the initial mass eccentricity caused by manufacturing tolerances or material inhomogeneity, as well as the dynamic imbalance that may occur due to wear and thermal deformation during long-term operation. The moment of inertia of the flywheel mass block 203 can be continuously adjusted between I_min and I_max, and the inertia coefficient b is adjusted accordingly.

[0039] The moment of inertia of the flywheel mass is: I = Σ m r²

[0040] Where: m: mass of the mass block; r: radius of the mass block's center of mass from the center of rotation;

[0041] The inertia coefficient b = (2π / L)² × I, where L is the lead screw.

[0042] When the flywheel mass is close to the center: r is small → I is small → weak inertia; when the flywheel mass moves to the outer periphery: r is large → I is large → strong inertia.

[0043] This embodiment employs a precise and evenly distributed configuration of the flywheel mass blocks 203 around the flywheel shaft. This installation design ensures that the flywheel's center of mass always coincides with the axis of rotation, whether in a static or high-speed rotating dynamic state. This symmetry fundamentally counteracts the centrifugal force and inertial coupling effects caused by mass eccentricity, enabling the flywheel to maintain excellent dynamic balance and operational stability in any operating posture.

[0044] Therefore, by adjusting the mass m and radial position r of the mass block, a precise match can be achieved to the system's inertial-compression characteristics to cope with different loads and vibration environments. This adjustable mechanism provides broad adaptability for the core inertial-compression component.

[0045] like Figure 4 As shown, based on the above embodiment, the housing 204 is provided with an adjusting screw 209, which is connected to the worm gear 207. The worm gear 207 can be rotated by the screw, which facilitates operation.

[0046] like Figure 2As shown, based on the above embodiment, the flywheel mass block 203 is an elongated arc shape, and four of them are provided. The shape and number of the flywheel mass blocks 203 can be adjusted according to actual needs.

[0047] like Figure 5 and Figure 6 As shown, based on the above embodiments, the present invention also provides an active suspension, including a linear actuator, a spring assembly, a damper, a mounting bracket, and an inertia container 20 as described in any of the above embodiments; the linear actuator is a ball screw assembly with a hollow structure, driven by a motor to perform linear motion; the upper end of the spring assembly 7 is connected to the housing 4 of the linear actuator, and the lower end of the spring assembly 7 is connected to the mounting bracket 8, and the spring assembly 7 is stretched or compressed with the movement of the linear actuator; the damper 12 is disposed in the hollow structure inside the linear actuator, and the front end of the damper 12 has a damper piston 9; the inertia container is fixed to the upper end of the ball nut of the ball screw and rotates synchronously with the nut; the upper end of the mounting bracket 8 is connected to the damper piston 9, and the bottom of the mounting bracket 8 moves up and down with the stretching and compression of the spring assembly 7; when the mounting bracket 8 is squeezed by the vehicle body, it pushes the damper piston 9 upward and compresses the spring assembly 7. In this embodiment, the linear actuator includes a ball screw 13, which is engaged with the ball nut 18 through a threaded pair. When the system is in normal condition, the linear actuator remains stationary. When the mounting bracket 8 moves upward under the pressure of the vehicle body, it first compresses the damper 12. After the damper is compressed to a specific stroke, the mounting bracket 8 begins to push the ball screw 13 upward. The linear motion of the ball screw 13 is converted into the rotation of the ball nut 18 through the threaded engagement, which in turn drives the inertial container fixed to it to rotate synchronously. At this time, the inertial capacitance effect is achieved by the ball nut 18 and the inertial container together. The principle is that in the non-working stationary state, the center of gravity of these flywheel mass blocks 203 converges at the center of the chuck 202;

[0048] When the mounting bracket 8 is compressed upwards by the vehicle body, it drives the ball screw 13 to generate axial (linear) motion. This linear motion is converted into the rotational motion of the ball nut 18 through the threaded connection. Since the inertia container 20 is fixed to the ball nut 18, the inertia container 20 rotates synchronously. As the inertia container 20 rotates with the ball nut 18, the flywheel mass block 203 slides radially outwards under the centrifugal effect, and its overall center of gravity moves to the periphery of the inertia container 20. This dynamic process significantly increases the system's moment of inertia, thereby enabling more efficient absorption and dissipation of vibration energy and enhancing the vehicle's shock absorption performance. The rotating inertia container 20, due to its own moment of inertia I, generates a counter-torque when the rotational speed changes. This counter-torque, through the nut-screw transmission relationship, ultimately manifests as a damping force proportional to the relative acceleration in the axial direction of the screw, thus realizing the mechanical effect of the "inertia container".

[0049] Based on the above embodiments, such as Figure 5 As shown, this embodiment uses a reverse-type ball screw assembly as the core transmission mechanism. This assembly includes steel balls 15, a ball nut 18, a screw 13 that also serves as the output shaft, a rotor 17, and a stator 16. Specifically, the inner surface of the ball nut 18 is machined with an open helical raceway, and the nut 18 is fitted onto the outside of the screw 13. The outer surface of the rear end of the screw 13 is provided with a circulating bearing raceway. Multiple steel balls 15 are evenly arranged circumferentially between the nut raceway and the circulating bearing raceway, together forming a highly efficient ball screw transmission mechanism. In terms of support and drive, the ball nut 18 is connected to the stator 16 via an upper bearing assembly 19 and a lower bearing assembly 14. The rotor 17 is located in the annular space between the stator 16 and the ball nut 18, forming the motor drive section. During operation, the motor directly drives the ball nut 18 to rotate, and then, through the cyclic movement of the steel balls 15, the rotation is converted into a linear output from the screw 13. An inertial container 20 is also connected to the upper end of the ball nut 18. The core of this reverse design lies in integrating the circulating structure onto the lead screw 13. A motor drives the ball nut 18 to rotate, directly converting its motion into linear motion of the lead screw 13. The steel ball 15, as a key rolling element, greatly reduces friction between the lead screw and the nut, thereby significantly improving transmission efficiency.

[0050] like Figure 7 As shown, the inertial container 20 is connected to the ball screw and then strung between the vehicle body and the wheel. Mechanically equivalent, it is the addition of an interferometer element between (z_s) and (z_u).

[0051] The formula for the inertia coefficient b is as follows:

[0052]

[0053]

[0054] Where L is the lead screw; (I) is the equivalent moment of inertia of the flywheel;

[0055] Body mass, i.e., sprung mass: displacement (z_s(t));

[0056] Wheel / suspension assembly unsprung mass: displacement (z_u(t));

[0057] The axial force generated by the linear actuator is denoted as (F_a(t)), which is positive upwards for the vehicle body and opposite in direction for the wheels.

[0058] The adjustment mechanism on this inertial container 20 achieves an active, closed-loop controllable dynamic balancing method. It transcends the static limitations of traditional fixed counterweight methods, and through precise mechanical adjustments, the center of gravity deviation can be brought close to zero during system assembly or maintenance, thereby suppressing harmful vibrations at the source and significantly improving the rotational accuracy, operational smoothness, and mechanical life of the flywheel system and the connected ball screw transmission system.

[0059] In other specific embodiments of the present invention, the remainder is the same as the embodiments described above, except that, as follows: Figure 5 As shown, this invention employs a shell vibration isolation and reinforcement structure. Specifically, a rigid shell 4 covers the stator 16, and an upper isolator 5 and a lower isolator 6 are respectively installed between the upper and lower ends of the stator 16 and the shell 4. This design achieves a dual purpose: firstly, the rigid shell 4, as a robust load-bearing structure, significantly improves the mechanical strength and durability of the actuator assembly; secondly, the internal upper and lower isolators effectively block and absorb the transmission path of vibration energy. Ultimately, this solution not only enhances the structural reliability and lifespan of the system but also directly improves the ride comfort of the vehicle under complex road conditions through excellent vibration isolation performance.

[0060] In other specific embodiments of the present invention, the remaining parts are the same as those described above, except that, for example... Figure 5 As shown, the outer circumferential surface of the lead screw 13 has multiple axial ball splines 11 evenly distributed. The lead screw 13 is connected to the external rigid housing 4 via a ball spline 11. The core function of this ball spline 11 is to provide reliable anti-rotation constraint, effectively limiting the degree of freedom of the lead screw 13 to rotate circumferentially relative to the housing 4, thereby ensuring that the lead screw 13 only produces precise axial linear motion under drive. The layout of the ball splines 11 is independent of the thread raceway of the ball screw 13, allowing the guiding function of the splines 11 and the transmission function of the lead screw 13 to work together without interference. This embodiment significantly improves the overall performance of the system: on the one hand, it enhances the efficiency of torque transmission and the rigidity of the entire transmission chain; on the other hand, it reduces sliding friction through rolling contact, thereby reducing wear and helping to extend the service life of the entire suspension system. The key structure of this invention is that the ball screw 13 can only move axially; the ball spline 11 structure prevents the lead screw 13 from rotating. Therefore, the counter-torque generated by the rotation of nut 18 will not be transmitted to the fixed end of screw 13; fatigue caused by large torque at the joint can be avoided; and the housing does not need to bear large counter-torque.

[0061] In other specific embodiments of the present invention, the remainder is the same as the embodiments described above, except that the sensing and control system is further enhanced, such as... Figure 1As shown, the position sensor 10 and load sensor 2 are integrated within the connecting housing 3 located on top of the linear actuator. The position sensor 10 is connected to the moving piston 9 via its retractable sensor rod 1, thereby directly capturing the vertical displacement of the wheel. The load sensor 2 is mounted on the top connecting housing 3, a key load-bearing point, to sense the load from the vehicle body in real time. These two types of sensors provide crucial real-time status parameters for the suspension system. They feed back the collected displacement and force signals to the central controller, which then accurately calculates and issues commands to drive the linear actuator to make a fast and accurate response, thus forming an efficient and precise active control closed loop, significantly improving the vehicle's adaptability to different road conditions.

[0062] In other specific embodiments of the present invention, the remaining parts are the same as those described above, except that, for example... Figure 5 As shown, the spring assembly 7 specifically employs a coil spring. The upper and lower ends of this coil spring 7 are reliably connected to the housing 4 and mounting bracket 8 via upper and lower spring mounting seats, respectively. The coil spring 7, with its classic structural form, exhibits core advantages such as simple structure, mature technology, low manufacturing cost, and high reliability. This solution utilizes the inherent linear elastic properties of metallic materials to provide stable and predictable stiffness for the suspension system. Based on its wide application base and mature manufacturing process, this solution effectively reduces the manufacturing and maintenance complexity of the system while ensuring excellent suspension performance, providing an ideal choice for applications seeking high economy and high durability.

[0063] like Figure 8As shown, in application, this invention involves four sets of active suspensions independently positioned below the vehicle body 22 at each of the four wheels, connected to the corresponding wheel hubs via mounting brackets 8, forming a complete four-wheel independent controllable suspension system. Each active suspension structure in the system is equipped with high-precision sensors, which establish a high-speed data connection with the central controller 21, forming a real-time monitoring and feedback loop. Sensors at each tire continuously collect key parameters such as the relative height between the wheel and the vehicle body, acceleration, and load changes, providing a data basis for system decision-making. The linear actuator, as the core execution unit of the system, precisely adjusts the suspension state according to controller commands. By controlling the compression state of the coil spring, the actuator can dynamically change the distance between the wheel and the vehicle body and adjust the equivalent stiffness of the spring in real time. This active intervention mechanism achieves adaptive matching between vehicle height adjustment and suspension stiffness, providing hardware assurance for comfort optimization. The spring assembly 7 and damper 12 perform passive adjustment functions in the system. Based on their own physical characteristics, they naturally respond to road unevenness, vehicle acceleration, braking, and other operating conditions, providing basic support and shock absorption functions for the vehicle, ensuring basic driving stability. Controller 21, acting as the system's intelligent hub, processes real-time information uploaded from various sensors using multi-channel data fusion technology to accurately analyze the vehicle's dynamic attitude. Based on its built-in advanced control strategy, the controller generates optimized commands and sends them to each linear actuator, achieving active closed-loop control of vehicle height and suspension stiffness. Simultaneously, the system continuously monitors the passive response status of the spring assembly and dampers, ensuring optimal driving stability and ride comfort under any road conditions through a coordinated active and passive control strategy. This active suspension system, through its distributed sensing, centralized decision-making, and independent execution architecture, achieves precise and independent control of the four-wheel suspension characteristics, demonstrating excellent overall performance.

[0064] The equilibrium equation for vehicle body mass (m_s)

[0065] The vehicle body is subjected to forces from the suspension springs, suspension dampers, inertia container, and active actuators:

[0066] Suspension spring force: (-k s (z s - z u ))

[0067] Suspension damping force: (-c s (dot z s - dot z u ))

[0068] Inertial container force: (-F) b = -b(dot z s - dot z u ))

[0069] Active actuator: (+F a )

[0070] Equations of motion for the vehicle body:

[0071]

[0072] After organizing the inertial container terms, we get:

[0073]

[0074] The equilibrium equation for the mass (mu) of the wheel

[0075] The wheel / unsprung mass is subject to:

[0076]

[0077] Equation of motion of the wheel:

[0078]

[0079] After organizing the inertial container terms, we get:

[0080]

[0081] Based on the above detailed description, the active inertial-capacity suspension provided by the present invention has the following technical effects:

[0082] 1. The core components, such as the linear actuator, spring assembly, damper, and inertia container, are highly integrated into a compact, independent module. This modular design not only significantly saves installation space and facilitates layout and maintenance within the vehicle, but also improves the overall integrity and reliability of the system.

[0083] 2. The system employs a reverse-type ball screw pair design, integrating the circulation structure into the screw. The nut is directly driven by the motor, causing the screw to move linearly, resulting in high transmission efficiency. The addition of a ball spline mechanism ensures that the screw performs only precise axial movement, avoiding the transmission of harmful torque and improving the system's rigidity, precision, and durability.

[0084] 3. The flywheel's inertia generates a counter-torque when its rotational speed changes, which is converted into a damping force proportional to the relative acceleration (F = b × a) via the leadscrew. This introduces a third mechanical relationship into the system, in addition to the spring (force related to displacement) and the damper (force related to velocity). This upgrades the suspension from a traditional "mass-spring-damping" system to a "mass-spring-damping-inertia" system, adding a dimension for optimizing dynamic characteristics. The inertia container and damper work together to dissipate mid-to-high frequency vibration energy more quickly and efficiently, significantly enhancing ride comfort, especially when dealing with instantaneous impacts and continuous bumps.

[0085] 4. Continuously adjustable moment of inertia: Through a worm gear mechanism, the radial position of the mass block inside the inertia container can be adjusted symmetrically, thereby continuously changing the flywheel's moment of inertia I and the system's inertia coefficient b. Without replacing hardware, it can match the optimal inertia characteristics in real time according to different loads, road conditions, or driving modes (such as comfort / sport), achieving intelligent functionality and wide adaptability.

[0086] 5. Active dynamic balancing design: The mass blocks are symmetrically arranged and always move symmetrically, ensuring that the flywheel's center of gravity remains strictly on the axis of rotation in any adjustment position. This eliminates harmful vibrations caused by mass eccentricity during high-speed rotation, guaranteeing smooth operation and component reliability under extreme conditions. Mechanical self-locking stability: The worm gear used in the adjustment mechanism has reverse self-locking characteristics, maintaining an absolutely fixed position after adjustment without the need for additional locking devices, providing strong anti-interference capabilities.

[0087] Note that the above description is merely a preferred embodiment of the present invention. Those skilled in the art will understand that the present invention is not limited to the specific embodiments described herein, and various obvious changes, readjustments, and substitutions can be made without departing from the scope of protection of the present invention. Therefore, although the present invention has been described in detail through the above embodiments, the present invention is not limited to the above embodiments, and may include many other equivalent embodiments without departing from the concept of the present invention, the scope of which is determined by the scope of the appended claims.

Claims

1. An inertial container, characterized in that, Includes chuck, flywheel mass, and housing; The chuck is disposed inside the housing, and multiple sliding grooves are distributed around the circumference of the chuck with the center as the center. The flywheel mass blocks are multiple, and each flywheel mass block has a slider at its bottom, which is slidably set in the groove of the chuck. A fixed frame is provided on the back of the housing, and a worm gear is slidably arranged inside the fixed frame. A worm wheel is fixed on the back of the chuck, and the worm wheel meshes with the worm gear. By controlling the rotation of the worm gear, the flywheel mass block can be driven to move synchronously in opposite directions or in the radial direction, thereby adjusting the rotational inertia of the flywheel mass block.

2. The inertial container according to claim 1, characterized in that, The moment of inertia of the flywheel mass block can be continuously adjusted between I_min and I_max, and the inertia coefficient b can be adjusted accordingly. The moment of inertia of the flywheel mass is: I = Σ m r² Where: m: mass of the mass block; r: radius of the mass block's center of mass from the center of rotation; The inertia coefficient b = (2π / L)² × I, where L is the lead screw.

3. An inertial container according to claim 1 or 2, characterized in that, The housing is equipped with an adjusting screw, which is connected to the worm gear.

4. An inertial container according to claim 1 or 2, characterized in that, The flywheel mass block is a long, arc-shaped block, and there are four of them.

5. An active suspension system, comprising a linear actuator, a spring assembly, a damper, and a mounting bracket; characterized in that, It also includes the inertial container as described in any one of claims 1 to 4 above; The linear actuator is a ball screw assembly with a hollow structure, driven by a motor to perform linear motion. The upper end of the spring assembly is connected to the housing of the linear actuator, and the lower end is connected to the mounting bracket. The spring assembly is stretched or compressed as the linear actuator moves. The damper is located inside the hollow structure of the linear actuator, and a damper piston is located at the front end of the damper. The inertia container is fixed to the upper end of the ball nut of the ball screw and rotates synchronously with the nut. The upper end of the mounting bracket is connected to the damper piston, and the bottom of the mounting bracket moves up and down with the stretching and compression of the spring assembly. When the mounting bracket is squeezed by the vehicle body, it pushes the damper piston upward and compresses the spring assembly.

6. An active suspension according to claim 5, characterized in that, The inertial container is connected to the ball screw and strung between the vehicle body and the wheel. Mechanically equivalent, it is the addition of an interferometer element between (z_s) and (z_u). The formula for the inertia coefficient b is as follows: ； ； Where L is the lead screw; (I) is the equivalent moment of inertia of the flywheel; Body mass, i.e., sprung mass: displacement (z_s(t)); Wheel / suspension assembly unsprung mass: displacement (z_u(t)); The axial force generated by the linear actuator is denoted as (F_a(t)), which is positive upwards for the vehicle body and opposite in direction for the wheels.

7. The active suspension structure according to claim 5, characterized in that, The ball screw has multiple ball spline grooves evenly distributed around its circumference, and the ball spline connects the screw to the housing.

8. An active suspension according to claim 5, characterized in that, The linear actuator is provided with a top connecting shell on its upper part. A position sensor is provided inside the linear actuator. The position sensor is connected to the damper piston through a position sensor rod, which extends downward into the mounting bracket. A load sensor is provided on the top connecting shell.

9. An active suspension structure according to claim 5, characterized in that, The spring assembly is a helical spring. The upper end of the helical spring is connected to the outer shell through an upper spring mounting seat, and the lower end of the helical spring is connected to the mounting bracket through a lower spring mounting seat.

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