Damping system, vehicle seat and adjusting method of vehicle seat

Abstract

The invention provides a damping system, a vehicle seat and an adjusting method of the vehicle seat, and relates to the technical field of engineering machinery. The damping system comprises a telescopic support, a positive stiffness elastic assembly, a negative stiffness elastic assembly, a detection assembly and a control system. The first end and the second end of the telescopic support get away from each other or get close to each other under the action of external force. The positive stiffness elastic assembly is used for providing system positive stiffness for the telescopic support. The negative stiffness elastic assembly is used for providing system negative stiffness for the telescopic support, and the system negative stiffness changes along with relative movement of the first end and the second end of the telescopic support. The detection assembly is used for detecting the relative position variation between the first end and the second end of the telescopic support. The control system is used for adjusting the system positive stiffness to enable the system total stiffness to be a target value. The low-frequency vibration isolation device overcomes the defect that in the prior art, an operation mechanical seat cannot effectively isolate vibration or even amplify the vibration under low-frequency vibration, the low-frequency vibration is effectively isolated, and the comfort of a driver is improved.

Description

Technical Field

[0001] This application relates to the field of engineering machinery technology, and in particular to a shock absorption system, a vehicle seat, and a method for adjusting the vehicle seat. Background Technology

[0002] In the field of engineering machinery, shock absorption systems, vehicle seats, and vehicle seat adjustment methods are widely used in seat structures to improve driver comfort, especially in equipment with harsh vibration environments. They reduce the vibration transmitted to the driver by absorbing and attenuating external vibration energy.

[0003] Currently, the vibration damping structure of seats typically integrates a horizontally placed coil spring or a vertically placed air spring and an obliquely placed damper to form a vibration damping unit.

[0004] Existing seat vibration damping structures cannot effectively isolate vibrations in low-frequency vibration scenarios, and may even amplify vibration energy, leading to a decrease in driver comfort. Summary of the Invention

[0005] This application provides a shock absorption system, a vehicle seat, and a method for adjusting the vehicle seat, in order to solve the defects of existing work machinery seats in that they cannot effectively isolate vibrations or even amplify vibrations under low-frequency vibrations, thereby achieving effective isolation of low-frequency vibrations and improving driver comfort.

[0006] This application provides a vibration damping system, including a telescopic bracket, a positive stiffness elastic component, a negative stiffness elastic component, a detection component, and a control system. A first end of the telescopic bracket is connected to a load-bearing component, and a second end is connected to a foundation support component. The first and second ends of the telescopic bracket move away from or towards each other under the action of an external force. The positive stiffness elastic component is disposed on the telescopic bracket to provide system positive stiffness. The negative stiffness elastic component is disposed on the telescopic bracket to provide system negative stiffness, and the system negative stiffness changes with the relative position between the first and second ends of the telescopic bracket. The detection component is disposed on the telescopic bracket to detect the amount of relative position change between the first and second ends of the telescopic bracket. The control system is disposed on the telescopic bracket and electrically connected to the positive stiffness elastic component and the detection component, and is used to calculate the system negative stiffness based on the relative position change, adjust the positive stiffness of the positive stiffness elastic component, and thus adjust the system positive stiffness to achieve a target system total stiffness.

[0007] In one possible implementation, the telescopic support includes a connecting frame, a connecting seat, and a scissor lift frame. The connecting frame is used to connect with the load-bearing component. The connecting seat is parallel to and spaced apart from the connecting frame, and is used to connect with the foundation support component. The upper and lower ends of the first side of the scissor lift frame are hinged to the connecting frame and the connecting seat, respectively, and the upper and lower ends of the second side are slidably connected to the connecting frame and the connecting seat, respectively. A hinge frame is fixedly provided at the upper or lower end of the first side of the scissor lift frame. In the initial state, the positive stiffness elastic component is arranged parallel to the connecting frame, and one end of the positive stiffness elastic component is hinged to the hinge frame, and the other end is hinged to the middle of the connecting frame or the connecting seat.

[0008] In one possible implementation, the positive stiffness elastic component includes a housing, a first magnetic element, and a second magnetic element. The housing has an interior cavity and a vent valve on its side wall, one end of which communicates with the outside and the other end with the cavity. The first magnetic element slides through one end of the housing, and its outer end is hinged to the hinge frame. The second magnetic element slides through the other end of the housing, and its outer end is hinged to the middle of the connecting frame or the connecting seat. The first and second magnetic elements are opposite each other at their interior ends and have the same magnetic properties. At least one of the first and second magnetic elements is an electromagnet, and the electromagnet is electrically connected to the control system.

[0009] In one possible implementation, a magnetic ring is sleeved around the outside of the first magnetic component and the second magnetic component, and the magnetic ring is located inside the cavity.

[0010] In one possible implementation, the scissor lift includes a first rotating frame and a second rotating frame. The first rotating frame is disposed between the connecting frame and the connecting seat, with a first end hinged to the connecting frame and a second end slidably connected to the connecting seat. The second rotating frame is X-shapedly rotatably connected to the first rotating frame via a central axis, with a first end hinged to the connecting seat and a second end slidably connected to the connecting frame. One end of the hinged frame is hinged to the positive stiffness elastic component, and the other end is fixedly connected to either the first end of the first rotating frame or the first end of the second rotating frame.

[0011] In one possible implementation, one end of both the connecting frame and the connecting seat is provided with a hinge hole, and the first rotating frame and the second rotating frame are hinged to the connecting frame and the connecting seat one-to-one through the hinge hole;

[0012] The other end of both the connecting frame and the connecting seat is provided with a slide rail, and the first rotating frame and the second rotating frame are slidably connected to the connecting frame and the connecting seat one-to-one through the slide rail.

[0013] In one possible implementation, a first pivot seat is provided in the middle of the connecting frame, and a second pivot seat is provided in the middle of the connecting seat; in the initial state, the first pivot seat, the second pivot seat, and the central shaft are located on the same plane; the negative stiffness elastic component includes at least one spring group, the spring group includes two springs, the two springs are symmetrically distributed on both sides of the central shaft; wherein, one end of one spring of the spring group is hinged to the first pivot seat, and the other end is hinged to the central shaft; one end of the other spring of the spring group is hinged to the second pivot seat, and the other end is hinged to the central shaft.

[0014] In one possible implementation, a folding shield is also included, which surrounds the outer periphery of the telescopic bracket.

[0015] Secondly, this application provides a vehicle seat, including a shock absorption system and a seat body as described in any of the above embodiments, wherein the seat body is disposed at the first end of the telescopic bracket.

[0016] Thirdly, embodiments of this application provide a method for adjusting a vehicle seat, based on the vehicle seat implementation described in the above embodiments, comprising: acquiring the relative position change between a first end and a second end of the telescopic bracket through the detection component, and transmitting the relative position change to the control system; the control system calculating the negative stiffness of the system based on the relative position change, and determining whether the relative position change is within a preset threshold; when the relative position change is within the preset threshold, the control system adjusting the positive stiffness of the positive stiffness elastic component to make the positive stiffness of the system equal to the negative stiffness of the system; when the relative position change exceeds the preset threshold, the control system adjusting the positive stiffness of the positive stiffness elastic component to make the positive stiffness of the system greater than or less than the negative stiffness of the system.

[0017] This application provides a vibration damping system, a vehicle seat, and a method for adjusting the vehicle seat. The vibration damping system incorporates a positive stiffness elastic component and a negative stiffness elastic component, wherein the negative stiffness characteristic of the negative stiffness elastic component dynamically changes with the actual vibration state. The positive stiffness elastic component, a detection component, and a control system together form a closed-loop control circuit. The detection component detects the negative stiffness value of the negative stiffness elastic component in real time, and the control system adjusts the positive stiffness of the positive stiffness elastic component in real time based on the detected value. When the external vibration frequency is low, the above control mechanism allows the positive stiffness provided by the positive stiffness elastic component and the negative stiffness generated by the negative stiffness elastic component to cancel each other out, so that the total system stiffness approaches zero. Therefore, the natural frequency of the vibration isolation system also approaches zero, resulting in good vibration isolation performance even at low external excitation frequencies. Since both the vehicle seat and the method for adjusting the vehicle seat include the vibration damping system, they also possess the aforementioned beneficial effects. Attached Figure Description

[0018] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application.

[0019] Figure 1 This is a structural schematic diagram of the vibration reduction system provided in this application;

[0020] Figure 2 Rear view of the shock absorption system provided in this application;

[0021] Figure 3 A partial structural schematic diagram of the vibration reduction system provided in this application;

[0022] Figure 4 for Figure 3 Side view of the structure shown;

[0023] Figure 5 A structural schematic diagram of the scissor lift frame for the shock absorption system provided in this application;

[0024] Figure 6 A schematic diagram of the connecting frame of the shock absorption system provided in this application;

[0025] Figure 7 A schematic diagram of the connection seat of the shock absorption system provided in this application;

[0026] Figure 8 A cross-sectional view of the positive stiffness elastic component of the damping system provided in this application;

[0027] Figure 9 This is a structural diagram of the vehicle seat provided in this application;

[0028] Figure 10A flowchart illustrating the method for adjusting the vehicle seat provided in this application;

[0029] Figure 11 A simplified structural comparison diagram of the scissor lift frame of the damping system provided in this application in the initial and compressed states;

[0030] Figure 12 A schematic diagram of the parameters of the normal stiffness elastic component of the scissor lift frame of the shock absorption system provided in this application in the initial state;

[0031] Figure 13 A schematic diagram of the parameters of the normal stiffness elastic component of the scissor lift frame of the shock absorption system provided in this application under compression.

[0032] Figure 14 A comparison diagram of the deformation of the scissor lift frame of the damping system provided in this application under the initial and compressed states, showing the deformation of the normal stiffness elastic component.

[0033] Figure 15 A schematic diagram of the parameters of the negative stiffness elastic component of the scissor lift frame of the shock absorption system provided in this application in the initial state;

[0034] Figure 16 A schematic diagram of the parameters of the negative stiffness elastic component of the scissor lift frame of the shock absorption system provided in this application under compression.

[0035] Figure 17 A comparison diagram of the deformation of the negative stiffness elastic component of the scissor lift frame of the damping system provided in this application in the initial and compressed states;

[0036] Figure 18 The schematic diagram shows the input current control principle of the positive stiffness elastic component of the damping system provided in this application.

[0037] Explanation of reference numerals in the attached figures:

[0038] 10: Shock absorption system; 20: Seat body;

[0039] 100: Telescopic support frame; 110: Connecting frame; 120: Connecting seat; 130: Scissor lift frame;

[0040] 111: Hinge hole; 112: Slide rail; 113: First pivot seat;

[0041] 121: Second pivot seat;

[0042] 131: First rotating frame; 132: Second rotating frame; 133: Central shaft; 134: Hinge frame; 135: Pulley;

[0043] 200: Positive stiffness elastic component; 210: Housing; 220: First magnetic component; 230: Second magnetic component; 240: Magnetic ring;

[0044] 211: Cavity; 212: Vent valve;

[0045] 300: Negative stiffness elastic component; 310: Spring assembly; 311: Spring;

[0046] 400: Detection component;

[0047] 500: Control system;

[0048] 600: Folding cover. Detailed Implementation

[0049] Exemplary embodiments will now be described in detail, examples of which are illustrated in the accompanying drawings. When the following description relates to the drawings, unless otherwise indicated, the same numbers in different drawings denote the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with this application. Rather, they are merely examples of apparatuses and methods consistent with some aspects of this application as detailed in the appended claims.

[0050] Frequency ratio (r): refers to the external vibration frequency (f) 外界 ) and the system's natural frequency (f 固有 The ratio of r to f, i.e., r=f 外界 / f 固有 .

[0051] Vibration isolation law: When r < 1.414, the vibration will be amplified, and in the worst case, when r = 1 (resonance), the amplification will be extreme. When r > 1.414, the system begins to isolate vibration, and the larger r is, the better the vibration isolation effect.

[0052] In summary, given a fixed external vibration frequency, a lower natural frequency results in better vibration isolation, while lower system stiffness leads to a lower natural frequency. This means that for some lower external vibration frequencies, the vibration damping structure needs to have lower stiffness. The existing seat vibration damping structures are too stiff to effectively isolate vibrations in low-frequency scenarios, and may even amplify vibration energy, leading to a decrease in driver comfort.

[0053] The technical solution of this application and how the technical solution of this application solves the above-mentioned technical problems are described in detail below with specific embodiments. These specific embodiments can be combined with each other, and the same or similar concepts or processes may not be described again in some embodiments. The embodiments of this application will be described below with reference to the accompanying drawings.

[0054] Reference Figure 1 and Figure 2The vibration damping system provided in this application includes a telescopic bracket 100, a positive stiffness elastic component 200, a negative stiffness elastic component 300, a detection component 400, and a control system 500. The first end of the telescopic bracket 100 is used to connect to a load-bearing component, and the second end of the telescopic bracket 100 is used to connect to a foundation support component. The first end and the second end of the telescopic bracket 100 move away from or towards each other under the action of an external force. The positive stiffness elastic component 200 is disposed on the telescopic bracket 100 and is used to provide the system's positive stiffness. The negative stiffness elastic component 300 is disposed on the telescopic bracket 100 and is used to provide the system's negative stiffness, and the system's negative stiffness increases with the first stiffness of the telescopic bracket 100. The relative position change between the first end and the second end of the telescopic bracket 100 changes; the detection component 400 is disposed on the telescopic bracket 100 and is used to detect the relative position change between the first end and the second end of the telescopic bracket 100; the control system 500 is disposed on the telescopic bracket 100 and is electrically connected to the positive stiffness elastic component 200 and the detection component 400, and is used to calculate the negative stiffness of the system based on the relative position change, adjust the positive stiffness of the positive stiffness elastic component 200 and thus adjust the positive stiffness of the system so that the total stiffness of the system is the target value.

[0055] Stiffness is the rate of change between the applied force and the displacement of the structure or component caused by that force, i.e., k = ΔF / ΔX. Here, k represents stiffness, ΔF is the change in applied force, and ΔX is the corresponding change in displacement.

[0056] Positive stiffness manifests as the restoring force generated when a structure deforms under stress, with the direction of the restoring force opposite to the direction of deformation, thus inhibiting further deformation. Specifically, when a displacement ΔX is applied to a component with positive stiffness characteristics along a certain direction, the component will generate an increment of restoring force ΔF opposite to the direction of displacement, resisting the action of external loads. For example, when compressing a conventional helical spring, a gradually increasing force must be applied to overcome its continuously increasing elastic restoring force.

[0057] Negative stiffness manifests as the equivalent "restoring force" generated by a component during deformation being in the same direction as the deformation, thus exacerbating the system's displacement. Specifically, when a displacement ΔX is applied to a structure with negative stiffness, the resulting additional force is in the same direction as the displacement, further promoting deformation. For example, when a slender rod in vertical equilibrium is subjected to a small disturbance and deviates from its equilibrium position, the torque generated by its gravity will cause the rod to tilt at an accelerated rate during the initial offset phase.

[0058] This application incorporates a positive stiffness elastic component 200 and a negative stiffness elastic component 300, where the negative stiffness characteristic of the negative stiffness elastic component 300 dynamically changes with the actual vibration state. The positive stiffness elastic component 200, together with the detection component 400 and the control system 500, form a closed-loop control circuit. The detection component 400 detects the negative stiffness value of the negative stiffness elastic component 300 in real time, while the control system 500 adjusts the system positive stiffness of the positive stiffness elastic component 200 in real time based on the detected value. When the external vibration frequency is low, the aforementioned control mechanism allows the system positive stiffness provided by the positive stiffness elastic component 200 and the system negative stiffness generated by the negative stiffness elastic component 300 to cancel each other out, causing the total system stiffness to approach zero. Consequently, the natural frequency of the vibration isolation system also approaches zero, ensuring that the system frequency ratio remains greater than 1.414 even at low external excitation frequencies. This structure achieves good vibration isolation performance even in low-frequency vibration environments.

[0059] Furthermore, when changes in operating conditions cause large longitudinal displacements (such as uphill), if the rate of change of position measured by the detection component 400 exceeds the preset range, the control system 500 will increase the stiffness of the positive stiffness elastic component 200, making the positive stiffness greater than the negative stiffness, and the system as a whole will exhibit positive stiffness characteristics. At this time, the first end of the telescopic bracket 100 will follow the second end of the telescopic bracket 100 to perform limited coordinated movement, maintaining a safe distance between the two ends and avoiding rigid collisions or instability caused by excessive amplitude.

[0060] Reference Figure 3 and Figure 4 In some embodiments of this application, the telescopic support 100 includes a connecting frame 110, a connecting seat 120, and a scissor lift frame 130. The connecting frame 110 is used to connect with the load-bearing component. The connecting seat 120 is parallel to and spaced apart from the connecting frame 110 and is used to connect with the foundation support component. The upper and lower ends of the first side of the scissor lift frame 130 are hinged to the connecting frame 110 and the connecting seat 120, respectively, and the upper and lower ends of the second side are slidably connected to the connecting frame 110 and the connecting seat 120, respectively. A hinge frame 134 is fixedly provided at the upper or lower end of the first side of the scissor lift frame 130. In the initial state, the positive stiffness elastic component 200 is arranged parallel to the connecting frame 110, and one end of the positive stiffness elastic component 200 is hinged to the hinge frame 134, and the other end is hinged to the middle of the connecting frame 110 or the connecting seat 120.

[0061] In the above structure, in the initial state, the positive stiffness elastic component 200 is arranged parallel to the connecting frame 110. In this embodiment, the positive stiffness elastic component 200 is arranged in two ways: in the first way, one end of the positive stiffness elastic component 200 is hinged to the upper end of the first side of the scissor lift frame 130, and the other end is hinged to the middle of the connecting frame 110; in the second way, one end of the positive stiffness elastic component 200 is hinged to the lower end of the first side of the scissor lift frame 130, and the other end is hinged to the middle of the connecting seat 120.

[0062] In this embodiment, the positive stiffness elastic component 200 is arranged in parallel and connected between the end of the scissor lift frame 130 and the middle of the connecting frame 110 or connecting seat 120 in the initial state. When the telescopic support 100 moves up and down, the lever arm between its two hinge points is relatively short. This shorter lever arm reduces the absolute deformation of the positive stiffness elastic component 200 during the support's movement. This reduction in deformation helps the positive stiffness elastic component 200 maintain a more stable stiffness coefficient within its operating range, thereby optimizing the nonlinear characteristics in its force-displacement response and resulting in higher linearity between the output of elastic force and displacement change. This provides a more linear and predictable elastic response in the vibration damping system, contributing to improved accuracy and system stability in vibration damping control.

[0063] Reference Figure 8 In some embodiments of this application, the positive stiffness elastic component 200 includes a housing 210, a first magnetic element 220, and a second magnetic element 230. The housing 210 has an interior cavity 211, and a vent valve 212 is provided on its side wall. One end of the vent valve 212 communicates with the outside, and the other end communicates with the cavity 211. The first magnetic element 220 slides through one end of the housing 210, and the end of the first magnetic element 220 located outside the housing 210 is hinged to the hinge frame 134. The second magnetic element 230 slides through the other end of the housing 210, and the end of the second magnetic element 230 located outside the housing 210 is hinged to the middle of the connecting frame 110 or the connecting seat 120. The first magnetic element 220 and the second magnetic element 230 are oppositely arranged at one end inside the housing 210 and have the same magnetism. At least one of the first magnetic element 220 and the second magnetic element 230 is an electromagnet, and the electromagnet is electrically connected to the control system 500.

[0064] Specifically, end caps are bolted to both ends of the housing 210, and each end cap has a precision through hole machined in its center. The first magnetic component 220 and the second magnetic component 230 slide through these two through holes, with the clearance between them controlled within a reasonable range. A sealing ring, made of wear-resistant rubber, is embedded in the through hole of each end cap, ensuring smooth sliding of the first and second magnetic components 220 and maintaining the airtightness of the cavity 211. A vent valve 212 is fixedly installed in a threaded hole on the side wall of the housing 210, and has a bidirectional valve core inside, ensuring communication between the inside of the housing 210 and the outside. In the configuration scheme of the first magnetic component 220 and the second magnetic component 230, one specific implementation is that the first magnetic component 220 is a permanent magnet and the second magnetic component 230 is an electromagnet; another implementation is that the first magnetic component 220 is an electromagnet and the second magnetic component 230 is a permanent magnet; and a third implementation is that both the first magnetic component 220 and the second magnetic component 230 are electromagnets. When an electromagnet is used, its power supply wire is led out from the sealed terminal block on the side of the end cover and connected to the control system 500. The housing 210 and the end cover are made of non-magnetic stainless steel, and the sliding rod surfaces of the first magnetic element 220 and the second magnetic element 230 are chrome-plated to improve wear resistance.

[0065] When the telescopic bracket 100 is compressed, the negative stiffness generated by the negative stiffness elastic component 300 increases. At this time, the first magnetic component 220 and the second magnetic component 230 approach each other within the housing 210, and the repulsive force generated between them due to their identical magnetism increases accordingly, causing the positive stiffness provided by the positive stiffness elastic component 200 to increase accordingly. When the telescopic bracket 100 is stretched, the negative stiffness generated by the negative stiffness elastic component 300 decreases, and at the same time, the first magnetic component 220 and the second magnetic component 230 move away from each other, and the decrease in magnetic force causes the positive stiffness to decrease accordingly. The vent valve 212 opens in a timely manner during the movement of the magnetic components to balance the air pressure inside and outside the cavity 211 and ensure smooth movement.

[0066] This embodiment uses at least one electromagnet as either the first magnetic element 220 or the second magnetic element 230. This allows the control system 500 to adjust the current of the electromagnet in real time based on the distance change detected by the detection component 400, thereby changing the magnetic force and achieving dynamic adjustment of the positive stiffness. This design ensures that when the telescopic support 100 is stretched, causing an increase in negative stiffness, the positive stiffness increases accordingly to match or exceed the negative stiffness; conversely, when the telescopic support 100 is compressed, causing an increase in negative stiffness, the positive stiffness decreases accordingly. This maintains precise control over the overall system stiffness, achieving zero-stiffness vibration isolation under stable operating conditions and providing sufficient support during severe vibrations.

[0067] Reference Figure 8In some embodiments of this application, a magnetic ring 240 is sleeved on the outside of the first magnetic element 220 and the second magnetic element 230, and the magnetic ring 240 is located inside the cavity 211.

[0068] Specifically, two magnetic rings 240 are respectively fixedly sleeved on the first magnetic element 220 and the second magnetic element 230, and are disposed together with the first magnetic element 220 and the second magnetic element inside the cavity 211 of the housing 210. The magnetic rings 240 adopt a U-shaped structure, with their open ends facing each other, respectively surrounding the outside of the corresponding first magnetic element 220 and the second magnetic element 230. The first magnetic element 220 passes through the U-shaped cavity of one of the magnetic rings 240, and the second magnetic element 230 passes through the U-shaped cavity of the other magnetic ring 240. The magnetic rings 240 are fixedly mounted on the corresponding magnetic elements by interference fit. The magnetic rings 240 can be made of laminated silicon steel sheets or soft magnetic composite materials. In the above structure, a gap is maintained between the outer wall of the magnetic ring 240 and the inner wall of the housing 210 to ensure that the moving parts remain in a non-contact state with the housing 210 during movement. The axial position of the magnetic ring 240 always corresponds to the first magnetic element 220 or the second magnetic element 230 to which it is fixed.

[0069] When the first magnetic component 220 and the second magnetic component 230 move relative to each other within the cavity 211, the two U-shaped magnetic rings 240 move together with their respective fixed magnetic components. As the first magnetic component 220 and the second magnetic component move closer to or further apart, the fixed magnetic rings 240 move together within the cavity 211. The vent valve 212 adjusts the air pressure inside and outside the cavity 211 during the movement of the first magnetic component 220 and the second magnetic component to ensure smooth movement.

[0070] In this embodiment, two U-shaped magnetic guide rings 240 are respectively positioned to correspond to the first magnetic component 220 and the second magnetic component 230, so that the magnetic field generated by each magnetic component is effectively constrained and guided by the corresponding U-shaped magnetic guide ring 240. The arrangement of the two U-shaped magnetic guide rings 240 with their openings facing each other forms a continuous magnetic circuit channel, improving the coupling efficiency of the magnetic field between the two magnetic components. This structure enhances the magnetic force between the first magnetic component 220 and the second magnetic component 230, enabling the generation of a larger magnetic force under the same current conditions, expanding the stiffness adjustment range of the positive stiffness elastic component 200, and making the relationship between magnetic force change and displacement more linear and controllable.

[0071] Reference Figure 4 and Figure 5 In some embodiments of this application, the scissor lift frame 130 includes a first rotating frame 131 and a second rotating frame 132; the first rotating frame 131 is disposed between the connecting frame 110 and the connecting seat 120, and the first end of the first rotating frame 131 ( Figure 5The right end shown is hinged to the connecting frame 110, and the second end of the first rotating frame 131 (shown on the right) is hinged to the connecting frame 110. Figure 5 The left end shown is slidably connected to the connecting seat 120; the second rotating frame 132 is X-shapedly rotatably connected to the first rotating frame 131 via the central shaft 133, and the first end of the second rotating frame 132 (shown on the left) is slidably connected to the connecting seat 120; the second rotating frame 132 is X-shapedly rotatably connected to the first rotating frame 131 via the central shaft 133 Figure 5 The right end shown is hinged to the connecting seat 120, and the second end of the second rotating frame 132 ( Figure 5 The left end shown is slidably connected to the connecting frame 110; wherein, one end of the hinge frame 134 is hinged to the positive stiffness elastic component 200, and the other end is fixedly connected to the first end of the first rotating frame 131 or the first end of the second rotating frame 132.

[0072] Specifically, the first end of the first rotating frame 131 is rotatably connected to the connecting frame 110 via a first hinge shaft, and the second end of the first rotating frame 131 is slidably connected to the connecting seat 120 via a pulley 135. The first end of the second rotating frame 132 is rotatably connected to the connecting seat 120 via a second hinge shaft, and the second end of the second rotating frame 132 is slidably connected to the connecting frame 110 via a pulley 135. The central shaft 133 passes through the intersection of the first rotating frame 131 and the second rotating frame 132, allowing them to rotate relative to each other.

[0073] When the hinge frame 134 is fixedly installed at the first end of the first rotating frame 131, the hinge frame 134 is hinged to one end of the positive stiffness elastic component 200, and at this time the other end of the positive stiffness elastic component 200 is hinged to the middle of the connecting frame 110.

[0074] When the hinge frame 134 is fixedly mounted at the first end of the second rotating frame 132, the hinge frame 134 is hinged to one end of the positive stiffness elastic component 200, and at this time, the other end of the positive stiffness elastic component 200 is hinged to the middle of the connecting seat 120. In the above structure, the hinge frame 134 is fixedly connected to the first rotating frame 131 or the second rotating frame 132 by welding.

[0075] When the connecting frame 110 undergoes longitudinal displacement relative to the connecting seat 120, the first rotating frame 131 and the second rotating frame 132 rotate relative to each other around the central axis 133. The second ends of the first rotating frame 131 and the second rotating frame 132 slide in a straight line via pulleys 135, causing the entire scissor lift frame 130 to extend and retract. The hinge frame 134 moves synchronously with the rotating frame it is connected to, driving the positive stiffness elastic component 200 to extend and retract.

[0076] In this embodiment, by placing the hinge frame 134 at the first end of the first rotating frame 131 or the second rotating frame 132, the positive stiffness elastic component 200 extends and retracts during the movement of the scissor lift frame 130. This arrangement optimizes the lever arm length of the positive stiffness elastic component 200 during the support movement, reduces the deformation of the component during operation, and thus improves the force-displacement response characteristics of the positive stiffness elastic component 200, making its stiffness output more stable and linear.

[0077] Reference Figure 5 and Figure 7 In some embodiments of this application, one end of the connecting frame 110 and the connecting seat 120 is provided with a hinge hole 111, and the first rotating frame 131 and the second rotating frame 132 are hinged to the connecting frame 110 and the connecting seat 120 one-to-one through the hinge hole 111; the other end of the connecting frame 110 and the connecting seat 120 is provided with a slide rail 112, and the first rotating frame 131 and the second rotating frame 132 are slidably connected to the connecting frame 110 and the connecting seat 120 one-to-one through the slide rail 112.

[0078] Specifically, one end of the connecting frame 110 and the connecting seat 120 is machined with a hinge hole 111, which can be press-fitted with a rolling bearing. The first end of the first rotating frame 131 is rotatably connected to the hinge hole 111 of the connecting frame 110 via a first hinge shaft, and the first end of the second rotating frame 132 is rotatably connected to the other hinge hole 111 of the connecting seat 120 via a second hinge shaft. The other end of the connecting frame 110 and the connecting seat 120 is machined with a slide rail 112, which is a straight channel with its inner surface hardened. The second end of the first rotating frame 131 is slidably connected to the slide rail 112 of the connecting seat 120 via a pulley 135, and the second end of the second rotating frame 132 is slidably connected to the slide rail 112 of the connecting frame 110 via a pulley 135. In the above structure, the slide rail 112 may be provided with a lubricating grease groove, and the pulley 135 may be provided with a ball retainer. The axis of the hinge hole 111 is parallel to the extension direction of the slide rail 112, ensuring that the first rotating frame 131 and the second rotating frame 132 maintain a stable geometric relationship during movement.

[0079] When the connecting frame 110 is displaced relative to the connecting seat 120, the first rotating frame 131 and the second rotating frame 132 rotate around their respective hinge holes 111, while their other ends slide along the slide rail 112 via pulleys 135. This combination of hinge and sliding motion allows the scissor lift frame 130 to extend and retract smoothly, while simultaneously driving the positive stiffness elastic component 200 to extend and retract.

[0080] This embodiment provides stable and reliable motion constraints for the first rotating frame 131 and the second rotating frame 132 by providing hinge holes 111 and slide rails 112 on the connecting frame 110 and the connecting seat 120, respectively. The hinge holes 111 ensure accurate positioning of the rotating frame's rotation center, and the slide rails 112 provide a precise linear motion trajectory for the ends of the rotating frame. This structure allows the scissor lift frame 130 to maintain a stable geometric shape during movement, ensuring that the positive stiffness elastic component 200 is always in its optimal working posture, thereby improving the accuracy and reliability of the damping system's stiffness adjustment.

[0081] Reference Figure 2 , Figure 5 , Figure 6 and Figure 7 In some embodiments of this application, the connecting frame 110 is provided with a first pivot seat 113 in the middle, and the connecting seat 120 is provided with a second pivot seat 121 in the middle; in the initial state, the first pivot seat 113, the second pivot seat 121 and the central shaft 133 are located on the same plane; the negative stiffness elastic component 300 includes at least one spring group 310, the spring group 310 includes two springs 311, the two springs 311 are symmetrically distributed on both sides of the central shaft 133; wherein, one end of one spring 311 of the spring group 310 is hinged to the first pivot seat 113 and the other end is hinged to the central shaft 133; one end of the other spring 311 of the spring group 310 is hinged to the second pivot seat 121 and the other end is hinged to the central shaft 133.

[0082] Specifically, the first rotating shaft seat 113 is fixed to the middle of the connecting frame 110 by welding, and the second rotating shaft seat 121 is fixed to the middle of the connecting seat 120 by welding. Figure 2 As shown: In the initial state, the axes of the first pivot seat 113, the second pivot seat 121, and the central shaft 133 are located in the same horizontal plane. The spring assembly 310 includes two springs 311 arranged on the upper and lower sides of the central shaft 133, respectively, with connecting rings at both ends of each spring 311. The connecting ring at one end of the spring 311 located on one side of the central shaft 133 is connected to the first pivot seat 113, and the connecting ring at the other end is connected to the central shaft 133; the connecting ring at one end of the spring 311 located on the other side of the central shaft 133 is connected to the second pivot seat 121, and the connecting ring at the other end is connected to the central shaft 133. The first pivot seat 113 and the second pivot seat 121 may be provided with mounting holes and fixedly connected to the connecting bracket 110 and the connecting seat 120 by bolts.

[0083] When the scissor lift frame 130 is compressed, the central shaft 133 is displaced due to the relative rotation of the first rotating frame 131 and the second rotating frame 132. At this time, the resultant force of the two springs 311 forms a negative stiffness characteristic during the displacement of the central shaft 133.

[0084] In this embodiment, two springs 311 are symmetrically arranged on both sides of the central shaft 133 and connected to the first pivot seat 113 and the second pivot seat 121, respectively. This arrangement causes the two springs 311 to generate opposite forces when the central shaft 133 deviates from its initial position. This arrangement generates a negative stiffness effect within a small displacement range of the central shaft 133. When this effect is canceled out by the positive stiffness of the positive stiffness elastic component 200, a quasi-zero stiffness state of the system can be achieved, thereby improving the isolation effect of the damping system against low-frequency vibrations.

[0085] Reference Figure 1 In some embodiments of this application, the shock absorption system further includes a folding shield 600, which surrounds the outer periphery of the telescopic bracket 100.

[0086] Specifically, the folding shield 600 adopts an accordion-like pleated structure, with an upper mounting edge and a lower mounting edge at its upper and lower ends, respectively. The upper mounting edge is fixedly connected to the periphery of the connecting frame 110 by bolts, and the lower mounting edge is fixedly connected to the periphery of the connecting seat 120 by bolts. The pleat direction of the folding shield 600 is consistent with the telescopic direction of the telescopic bracket 100, and its material is made of flexible rubber or waterproof canvas. In the above structure, the cross-sectional shape of the folding shield 600 can be set as circular or polygonal, and its pleat depth is adapted to the maximum telescopic stroke of the telescopic bracket 100. The inner side of the folding shield 600 can be provided with reinforcing ribs to improve structural stability.

[0087] When the telescopic bracket 100 extends or retracts, the folding cover 600 unfolds or folds accordingly, and its pleated structure changes accordingly with the extension stroke. When the telescopic bracket 100 is in its maximum extended state, the folding cover 600 is fully unfolded; when the telescopic bracket 100 is in its maximum compressed state, the folding cover 600 is tightly folded.

[0088] This embodiment effectively prevents external dust and foreign objects from entering the interior of the telescopic bracket 100 by providing a folding shield 600 on the outer periphery of the telescopic bracket 100, protecting internal components such as the positive stiffness elastic component 200 and the negative stiffness elastic component 300 from contamination. The pleated structure of the folding shield 600 allows it to deform freely with the movement of the telescopic bracket 100, without interfering with the normal operation of the shock absorption system, while maintaining the overall aesthetics.

[0089] Reference Figure 9 This application also provides a vehicle seat, including a shock absorption system 10 as described in any of the above embodiments and a seat body 20; the seat body 20 is disposed at the first end of the telescopic bracket 100. Since this application includes the shock absorption system 10 of any of the above embodiments, it also possesses the beneficial effects brought by the shock absorption system 10.

[0090] Reference Figure 10This application further provides a method for adjusting a vehicle seat, based on the vehicle seat implementation of the above embodiments, including the following steps:

[0091] S1. The relative position change between the first end and the second end of the telescopic support 100 is collected by the detection component 400 and transmitted to the control system 500. The relative position change can be the distance change between the first end and the second end of the telescopic support 100, the angle change of the scissor lift 130, or the length change of the positive stiffness elastic component 200 and the negative stiffness elastic component 300.

[0092] S2. The control system 500 calculates the negative stiffness based on the relative position change and determines whether the relative position change is within a preset threshold.

[0093] S3. When the relative position change is within a preset threshold, the control system 500 adjusts the positive stiffness of the positive stiffness elastic component 200 so that the positive stiffness is equal to the negative stiffness.

[0094] S4. When the relative position change exceeds the preset threshold, the control system 500 adjusts the positive stiffness of the positive stiffness elastic component 200 so that the positive stiffness is greater than or less than the negative stiffness.

[0095] This method uses a detection component 400 to collect the relative positional change between the first and second ends of the telescopic support 100 in real time and transmits this data to the control system 500. The control system 500 calculates the negative stiffness value generated by the negative stiffness elastic component 300 based on the positional change and simultaneously determines whether the rate of positional change is within a preset threshold range. When the rate of positional change is within the threshold range, the control system 500 adjusts the positive stiffness elastic component 200 so that its positive stiffness equals its negative stiffness. At this point, the total system stiffness approaches zero, effectively isolating vibration transmission. When the rate of positional change exceeds the threshold range, the control system 500 adjusts the positive stiffness elastic component 200 so that its positive stiffness is greater than or less than its negative stiffness. At this point, the system provides sufficient support force, ensuring that the first end of the telescopic support 100 moves in coordination with the second end, avoiding attitude changes or structural interference caused by excessive relative positional changes. This control method automatically adjusts the system stiffness characteristics according to the actual vibration state, providing excellent vibration isolation under stable operating conditions and ensuring system stability under severe vibration.

[0096] In the following embodiments, the working state of this application is up-and-down movement. Therefore, the positive stiffness of the system in this application is the longitudinal positive stiffness, and the negative stiffness of the system is mainly the longitudinal negative stiffness. The following provides the calculation of the longitudinal positive stiffness and the longitudinal negative stiffness of the system after the initial state and compression by a certain distance. The relative position change is detected by taking the distance between the first end and the second end of the telescopic bracket 100 as an example.

[0097] Reference Figures 11 to 14 The longitudinal stiffness of the system in this application is calculated as follows:

[0098] Formula 1.

[0099] In the formula, A is the initial distance (constant) between the first end and the second end of the telescopic bracket 100; B is the length of the first rotating frame 131 or the second rotating frame 132 (constant, both have the same length); C is the angle between segment E and the upper plane of the connecting frame 110 (constant); x0 is the change in distance between the first end and the second end of the telescopic bracket 100; and b is the angle between segment E and the first rotating frame 131.

[0100] Formula 2.

[0101] In the formula, x1 is the length change of the positive stiffness elastic component 200; E is the length of segment E (constant); F is the length of the hinge frame 134 (constant); a is the angle between the first rotating frame 131 and the hinge frame 134 (constant); and G is the length of the positive stiffness elastic component 200 in the initial state (constant).

[0102] Formula 3.

[0103] In the formula, k1 is the positive stiffness of the positive stiffness elastic component 200; k x0 This represents the longitudinal positive stiffness of the system.

[0104] Reference Figures 15 to 17 The longitudinal negative stiffness of the system in this application is calculated as follows:

[0105] Formula 4.

[0106] In the formula, x is the horizontal offset distance of one end of spring 311; A is the initial distance (constant) between the first end and the second end of telescopic bracket 100; B is the length of the first rotating frame 131 or the second rotating frame 132 (constant, both have the same length); x0 is the change in distance between the first end and the second end of telescopic bracket 100.

[0107] Formula 5.

[0108] In the formula, D represents the change in length of spring 311.

[0109] Formula Six.

[0110] In the formula, k x Let be the lateral stiffness of spring 311.

[0111] Formula 7.

[0112] In the formula, k x0 This represents the system's longitudinal negative stiffness.

[0113] Reference Figure 18 This embodiment provides the input current control principle of the positive stiffness elastic component 200.

[0114] When the driver sits in the vehicle seat and turns on the power, the system automatically inputs an initial current I0 and a stored current I2 to the positive stiffness elastic component 200. The initial current I0 and stored current I2 change the stiffness of the positive stiffness elastic component 200, thereby moving the vehicle seat to its initial height. When the driver wants to adjust the height of the vehicle seat, they can increase or decrease the current input to the positive stiffness elastic component 200 using adjustment buttons. That is, when a height is needed, a current I1 can be input. I1 is a vector value and can be increased or decreased. The height is changed by outputting I1. When the height is appropriate, inputting I1 stops, and the system records I1 as I2 and stores it. This setting enables the application to have a position memory function, and the default height will be used the next time it is turned on.

[0115] Furthermore, during operation, the detection component 400 continuously monitors x0. When the rate of change of x0 exceeds a preset threshold, the height-maintaining current I3 is increased, thereby increasing the longitudinal stiffness of the system. At this time, the first end of the telescopic bracket 100 will follow the second end of the telescopic bracket 100 in a limited coordinated movement to maintain a safe distance between the two ends and avoid rigid collisions or instability caused by excessive amplitude. When the rate of change of x0 does not exceed the preset threshold, I3 is zero, that is, the height-maintaining current is not increased, and the final output is I0+I2+I3.

[0116] Other embodiments of this application will readily occur to those skilled in the art upon consideration of the specification and practice of the invention disclosed herein. This application is intended to cover any variations, uses, or adaptations of this application that follow the general principles of this application and include common knowledge or customary techniques in the art not disclosed herein. The specification and examples are to be considered exemplary only, and the true scope and spirit of this application are indicated by the following claims.

[0117] It should be understood that this application is not limited to the precise structure described above and shown in the accompanying drawings, and various modifications and changes can be made without departing from its scope. The scope of this application is limited only by the appended claims.

Claims

1. A vibration damping system, characterized in that, include: A telescopic support, wherein the first end of the telescopic support is used to connect to a load-bearing component, and the second end of the telescopic support is used to connect to a foundation support component, and the first end and the second end of the telescopic support move away from each other or move closer to each other under the action of external force; A positive stiffness elastic component is provided on the telescopic support to provide system positive stiffness for the telescopic support. A negative stiffness elastic component is disposed on the telescopic bracket to provide system negative stiffness for the telescopic bracket, and the system negative stiffness varies with the relative position between the first end and the second end of the telescopic bracket. A detection component is provided on the telescopic bracket for detecting the relative positional change between the first end and the second end of the telescopic bracket; The control system is located on the telescopic support and electrically connected to the positive stiffness elastic component and the detection component. It is used to calculate the negative stiffness of the system based on the relative position change, adjust the positive stiffness of the positive stiffness elastic component, and thus adjust the positive stiffness of the system so that the total stiffness of the system is the target value.

2. The shock absorption system according to claim 1, characterized in that, The telescopic support includes: A connecting bracket is used to connect to the supporting component; A connecting seat, parallel and spaced apart from the connecting frame, is used to connect to the basic support component; The scissor lift has its upper and lower ends on the first side hinged to the connecting frame and the connecting seat, respectively, and its upper and lower ends on the second side slidably connected to the connecting frame and the connecting seat, respectively; a hinge frame is fixedly provided at the upper or lower end of the first side of the scissor lift. In the initial state, the positive stiffness elastic component is arranged parallel to the connecting frame, and one end of the positive stiffness elastic component is hinged to the hinge frame, while the other end is hinged to the middle of the connecting frame or the connecting seat.

3. The shock absorption system according to claim 2, characterized in that, The positive stiffness elastic component includes: The housing has an internal cavity and a vent valve on its side wall. One end of the vent valve is connected to the outside, and the other end is connected to the cavity. A first magnetic element slides through one end of the housing, and the end of the first magnetic element located outside the housing is hinged to the hinge frame. The second magnetic component slides through the other end of the housing, and the end of the second magnetic component located outside the housing is hinged to the middle of the connecting frame or the connecting seat; The first magnetic component and the second magnetic component are located opposite each other at one end inside the housing and have the same magnetic properties. At least one of the first magnetic component and the second magnetic component is an electromagnet, and the electromagnet is electrically connected to the control system.

4. The shock absorption system according to claim 3, characterized in that, A magnetic ring is sleeved on the outside of the first magnetic component and the second magnetic component, and the magnetic ring is located inside the cavity.

5. The shock absorption system according to claim 2, characterized in that, The scissor lift includes: A first rotating frame is disposed between the connecting frame and the connecting seat, with a first end of the first rotating frame hinged to the connecting frame and a second end of the first rotating frame slidably connected to the connecting seat; The second rotating frame is connected to the first rotating frame in an X-shaped cross rotation via a central axis. The first end of the second rotating frame is hinged to the connecting seat, and the second end of the second rotating frame is slidably connected to the connecting frame. One end of the hinged frame is hinged to the positive stiffness elastic component, and the other end is fixedly connected to the first end of the first rotating frame or the first end of the second rotating frame.

6. The shock absorption system according to claim 5, characterized in that, Both the connecting frame and the connecting seat have hinge holes at one end, and the first rotating frame and the second rotating frame are hinged to the connecting frame and the connecting seat one-to-one through the hinge holes; Both the connecting frame and the connecting seat are provided with slide rails at their other ends, and the first rotating frame and the second rotating frame are slidably connected to the connecting frame and the connecting seat one-to-one through the slide rails.

7. The shock absorption system according to claim 5 or 6, characterized in that, The connecting frame has a first rotating shaft seat in the middle, and the connecting seat has a second rotating shaft seat in the middle; in the initial state, the first rotating shaft seat, the second rotating shaft seat, and the central shaft are located on the same plane; The negative stiffness elastic component includes at least one spring assembly, the spring assembly including two springs, the two springs being symmetrically distributed on both sides of the central axis; In this configuration, one end of one spring in the spring assembly is hinged to the first rotating shaft seat, and the other end is hinged to the central shaft; one end of the other spring in the spring assembly is hinged to the second rotating shaft seat, and the other end is hinged to the central shaft.

8. The shock absorption system according to any one of claims 1-6, characterized in that, It also includes a folding shield, which surrounds the outer periphery of the telescopic bracket.

9. A vehicle seat, characterized in that, include: The shock absorption system as described in any one of claims 1-8; The seat body is located at the first end of the telescopic bracket.

10. A method for adjusting a vehicle seat, characterized in that, The vehicle seat implementation based on claim 9 includes: The detection component acquires the relative positional change between the first end and the second end of the telescopic bracket, and transmits the relative positional change to the control system. The control system calculates the negative stiffness of the system based on the relative position change and determines whether the relative position change is within a preset threshold. When the relative position change is within the preset threshold, the control system adjusts the positive stiffness of the positive stiffness elastic component so that the positive stiffness of the system is equal to the negative stiffness of the system. When the relative position change exceeds the preset threshold, the control system adjusts the positive stiffness of the positive stiffness elastic component so that the positive stiffness of the system is greater than or less than the negative stiffness of the system.

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