Nonlinear bidirectional active anti-impact damper

Abstract

The invention belongs to the technical field of dampers, and particularly discloses a nonlinear bidirectional active anti-impact damper which comprises a cylinder body, a load connecting plate, an elastic supporting piece and a magnetic damping assembly, the load connecting plate is installed at one axial end of the cylinder body in a floating mode through the elastic supporting piece, the load connecting plate is connected with a piston rod, and the end of the piston rod extends into the cylinder body; the magnetic damping assembly comprises a magnet and a coil, one of the magnet and the coil is connected to the end of the piston rod, and the other one is connected into the cylinder body. The damper further comprises a displacement sensor and a controller, the displacement sensor is used for detecting displacement data of the load connecting plate, the controller is connected with the displacement sensor and the coil, and the controller is used for controlling the current of the coil so that the coil can cut magnetic lines of force of the magnet to generate magnetic damping force changing nonlinearly along with displacement. The damper can effectively restrain vibration impact, gentle impact resistance is achieved, and the influence of sudden impact force on the service performance of equipment is reduced.

Description

Technical Field

[0001] The present application belongs to the technical field of dampers, and more specifically, relates to a nonlinear bidirectional active anti-impact damper. Background Art

[0002] Whether in the service of dynamic carrier equipment or in precision manufacturing, the impact phenomenon is ubiquitous and is a key factor restricting the service performance of equipment and the precision of precision manufacturing. For example, during aircraft takeoff and landing, and artillery recoil suppression, instantaneous high speed and large impact will occur, reducing the working life of the structure; especially low-voltage products inside ships will be accidentally touched under impact vibration, resulting in the system being unable to continuously power supply. In order to effectively absorb and dissipate the energy of external impact and reduce the adverse effects of impact vibration on equipment, various types of impact resistance devices have been developed and applied to actual engineering, playing a very important role in ensuring system performance and improving safety.

[0003] In the related technology, common anti-impact devices include liquid dampers, air dampers, and permanent magnet dampers. These dampers often generate excessive damping force when facing instantaneous high-speed impacts, causing serious impacts on the equipment and are in urgent need of improvement. Summary of the invention

[0004] In response to the defects or improvement needs of the prior art, the present application provides a nonlinear bidirectional active anti-impact damper, the damping force of which changes smoothly and is not likely to cause serious impact on the equipment.

[0005] The present application provides a nonlinear bidirectional active anti-impact damper, which specifically includes a cylinder, a load connecting plate, an elastic support member and a magnetic damping assembly, wherein: The load connecting plate is floatingly mounted on one axial end of the cylinder body through an elastic support member, and the load connecting plate is connected to a piston rod, the end of the piston rod extends into the cylinder body; The magnetic damping assembly comprises a magnet and a coil, one of which is connected to the end of the piston rod, and the other is connected to the cylinder body; The damper also includes a displacement sensor and a controller. The displacement sensor is used to detect the displacement data of the load connecting plate. The controller is connected to the displacement sensor and the coil respectively. The controller is used to control the current of the coil according to the displacement data detected by the displacement sensor, so that the magnetic damping coefficient of the damper is linearly related to the displacement of the load connecting plate, so that when the load connecting plate moves with the force difference between the external force and the elastic force of the elastic support, the coil cuts the magnetic lines of force of the magnet to generate a magnetic damping force that changes nonlinearly with the displacement.

[0006] Through the above technical scheme conceived by the present application, compared with the prior art, the damper introduces a feedback control mechanism, and realizes variable damping control by actively changing the current in the coil, so that the damping characteristic is a nonlinear function that changes with the displacement. In the initial displacement section under impact, the speed is large, but the corresponding magnetic damping coefficient is small, and no excessive instantaneous magnetic damping force is generated. Then, as the displacement increases, the damping coefficient also increases, and the speed continues to decrease, thereby ensuring that the magnetic damping force changes smoothly during the buffering process and the smoothness of the anti-impact process. At the same time, due to the floating setting of the load connection plate, the load connection plate can actively and smoothly resist the impact through the magnetic damping force generated by the magnetic damping component when it is subjected to forward or reverse impact, reducing the impact of sudden impact force on the service performance of the equipment and ensuring the safety of the equipment.

[0007] As a further preference, the piston rod is slidingly sealed with the open end of the cylinder body, and the cylinder body is filled with a damping fluid.

[0008] As a further preference, two positioning bushings are arranged in the cylinder body along the axial direction at intervals, and the magnet or coil is connected to the cylinder body through the two positioning bushings.

[0009] As a further preferred embodiment, two buffer limit structures are arranged in the cylinder body, and the two buffer limit structures are arranged at the two axial ends of the cylinder body, and the end of the piston rod is located between the two buffer limit structures. The end of the piston rod can move to abut against any one of the buffer limit structures.

[0010] As further preferred, the buffer limit structure comprises a limit plate and an elastic member, the limit plate is connected to the cylinder body via the elastic member, and the limit plate has a limit surface for the piston rod to abut against.

[0011] As a further preference, a plurality of elastic members are provided, and the plurality of elastic members are evenly distributed in the cylinder along the circumference of the cylinder.

[0012] As a further preferred embodiment, a guide structure for guiding the limit plate is fixed in the cylinder body.

[0013] As a further preference, the stiffness of the elastic member is greater than the stiffness of the elastic supporting member.

[0014] As a further preference, the damping fluid can flow through the buffer limiting structure and the end of the piston rod.

[0015] As a further preference, the open end of the cylinder body is sealedly connected with a sealing end cover with a perforation, the piston rod extends into the inner cavity of the cylinder body along the perforation, and a sealing structure is provided between the inner wall of the perforation and the circumferential surface of the piston rod.

[0016] In general, the above technical solutions conceived by this application have the following technical advantages compared with the prior art: 1. This damper introduces a feedback control mechanism, which realizes variable damping control by actively changing the current in the coil, so that the damping characteristic is a nonlinear function that changes with the displacement. When the initial load velocity is large, it will not produce excessive damping force to ensure the smoothness of the anti-impact process; under continuous impact, the damper can trigger the limit and produce an effective limit with high stiffness and high damping, effectively suppressing vibration impact, reducing the impact of sudden impact force on the service performance of the equipment, and ensuring the safety of the equipment.

[0017] 2. The damping fluid can not only realize the low stiffness and low damping vibration isolation performance of the damper under non-impact working conditions with the wide gap damping structure and the low stiffness support spring, but also can generate a large damping force through the extrusion and shearing movement of the damping fluid when the piston rod contacts the buffer limit structure, thereby assisting the buffer limit structure to realize the limit function. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 is a cross-sectional view of the overall structure of a nonlinear bidirectional active anti-impact damper provided in an embodiment of the present application; Figure 2 is a control block diagram of magnetic damping force of a nonlinear bidirectional active anti-shock damper with displacement variation provided by an embodiment of the present application; Figure 3 is a schematic diagram showing the variation of magnetic damping characteristics of a nonlinear bidirectional active anti-shock damper with displacement provided by an embodiment of the present application; Figure 4 is a schematic diagram of a magnetic damping assembly provided in an embodiment of the present application; Figure 5 is a structural schematic diagram of a first buffer limiting structure provided in an embodiment of the present application; Figure 6 It is a structural schematic diagram of the second buffer limiting structure provided in an embodiment of the present application.

[0019] Throughout the drawings, the same reference numerals are used to denote the same elements or structures, wherein: 1. Cylinder body; 2. Load connecting plate; 3. Elastic support member; 4. Piston rod; 5. Magnet; 6. Coil; 7. Displacement sensor; 8. Positioning bushing; 9. Damping fluid; 10. Sealing end cover; 11. Sealing ring; 12. Guide bearing; 13. First limit plate; 14. First elastic member; 15. Second limit plate; 16. Second elastic member; 17. Guide rod. DETAILED DESCRIPTION

[0020] In order to make the purpose, technical solution and advantages of the present application more clearly understood, the present application is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

[0021] The following is combined with Figure 1-6 This application is described in further detail.

[0022] The present application embodiment discloses a nonlinear bidirectional active anti-impact damper. Figure 1 The nonlinear bidirectional active anti-impact damper comprises a cylinder body 1, a load connecting plate 2, an elastic support 3 and a magnetic damping assembly, wherein: the load connecting plate 2 is floatingly mounted on one end of the cylinder body 1 through the elastic support 3, the load connecting plate 2 is connected to a piston rod 4, and the end of the piston rod 4 extends into the cylinder body 1; the magnetic damping assembly is located in the cylinder body 1, and the magnetic damping assembly comprises a magnet 5 and a coil 6, one of the magnet 5 and the coil 6 is connected to the end of the piston rod 4, and the other is connected to the cylinder body 1; the damper also comprises a displacement sensor 7 and a controller (not shown in the figure), the displacement sensor 7 is used to detect the displacement data of the load connecting plate 2, the controller is connected to the displacement sensor 7 and the coil 6 respectively, and the controller is used to control the current of the coil 6 according to the displacement data detected by the displacement sensor 7, so that the magnetic damping coefficient of the damper is linearly related to the displacement of the load connecting plate 2, so that when the load connecting plate 2 moves axially with the force difference between the external force and the elastic force of the elastic support 3, the coil 6 cuts the magnetic force lines of the magnet 5 to generate a magnetic damping force that changes nonlinearly with the displacement.

[0023] In practical applications, the magnetic damping force is in a linear function relationship with the speed. The controller actively controls the current value of the coil 6 based on the monitoring value (i.e., displacement data) of the displacement sensor 7 to realize the magnetic damping force control at different positions of the damper, thereby realizing the nonlinear change of the magnetic damping characteristics with the displacement. In the initial stage of displacement, the speed is relatively large, but the corresponding magnetic damping coefficient is relatively small, and no excessive instantaneous magnetic damping force will be generated; then the displacement increases, the damping coefficient also increases, and at the same time, the speed continues to decrease, and the magnetic damping force will not be too large, thereby ensuring that the magnetic damping force changes smoothly during the buffering process.

[0024] Furthermore, two detachable positioning bushings 8 are arranged in the cylinder body 1 along the axial direction, and the magnet 5 or the coil 6 is connected to the cylinder body 1 through the two positioning bushings 8. In some embodiments, the positioning bushing 8 includes but is not limited to being installed at the open end of the cylinder body 1 (i.e. Figure 1 The top end of the cylinder body 1 shown in FIG. Figure 1 The bottom of the cylinder 1 described in FIG.

[0025] Further, in some specific embodiments, the cross section of the coil 6 is circular and is wound in a ring shape on the end of the piston rod 4. The magnet 5 is in a ring shape and is coaxially positioned inside the cylinder body 1 by two positioning bushings 8. Preferably, a large radial gap is left between the coil 6 and the magnet 5. Under this design, the two form a damping structure with a wide gap to ensure that the damper has a small damping vibration isolation characteristic under non-impact conditions.

[0026] In other embodiments, when the coil 6 is connected in the cylinder body 1 and the magnet 5 is installed on the piston rod 4, the coil 6 is preferably also sleeved on the outer circumference of the magnet 5. It should be noted that no matter whether the coil 6 or the magnet 5 is connected in the cylinder body 1, the installation position and setting size of the coil 6 and the magnet 5 should satisfy that the coil 6 can cut the magnetic field lines of the magnet 5 when the load connecting plate 2 moves.

[0027] Further, such as Figure 4 In the illustrated scheme, when the coil 6 is fixed to the end of the piston rod 4, wiring holes are preferably reserved inside the load connecting plate 2 and the piston rod 4, and the control line of the coil 6 is connected to the controller through the wiring hole to realize current control of the coil 6, wherein the outlet of the wiring hole is preferably sealed by a rubber ring.

[0028] Further, the elastic support member is preferably a support spring, and further preferably a support spring with low stiffness characteristics.

[0029] For ease of understanding, Figure 2 A control scheme of a controller is shown. In this scheme, when the load connecting plate 2 is subjected to an instantaneous impact, the displacement signal sampled by the displacement sensor 7 is discretely converted into a long string of digital signals by an ADC (i.e., an analog-to-digital converter), and then the ADC inputs the digital signal into the processor, and the long string of digital signals is intercepted by the resolver in the processor. Then, the differentiator in the controller differentiates the digital signal intercepted by the resolver to obtain the speed of the damper (i.e., the moving speed of the load connecting plate 2), and the control law pre-constructed in the controller gives the desired magnetic damping coefficient (e.g., Figure 3 As shown, when impacted, the magnetic damping coefficient given is a linear function that changes with displacement), and then the damping force function is obtained according to the speed and damping coefficient. Then the controller combines the damping force function with the pre-constructed thrust function of the current and magnetic field strength, and reversely solves to obtain the real-time current change law. Then the solver solves based on the current change law and generates a control signal through the digital-to-analog conversion of the DAC. The controller then controls the current change of the coil 6 (generally an alternating current) through this control signal, so that the movement of the coil 6 causes the alternating current to cut the magnetic lines of force of the magnet 5, and obtains the expected magnetic damping force that changes with displacement, and realizes the damping characteristics that change with displacement. Among them, the operation and construction principles of the differentiator, control law, etc. are existing technologies, and will not be elaborated here.

[0030] Furthermore, the piston rod 4 is slidably sealed with the open end of the cylinder body 1, and the cylinder body 1 is filled with a damping fluid 9 (i.e. Figure 1 The damping fluid 9 can provide constant damping. Furthermore, in order to achieve sliding sealing between the piston rod 4 and the open end of the cylinder body 1, a sealing unit is provided at the open end of the cylinder body 1.

[0031] Specifically, the sealing unit includes a sealing end cover 10, which is sealed and connected to the open end of the cylinder body 1, and has a through hole for the piston rod 4 to pass axially. A sealing structure is provided between the inner peripheral wall of the through hole and the circumferential surface of the piston rod 4, and the sealing structure includes but is not limited to the use of a sealing ring 11. When the sealing ring 11 is selected, the sealing ring 11 is preferably fixedly sleeved in the inner cavity of the sealing end cover 10, and the inner peripheral wall of the sealing ring 11 is sealed and fitted with the circumferential surface of the rod body of the piston rod 4.

[0032] Under this design, the sealing end cover 10 and the sealing ring 11 limit the overflow of the damping fluid 9 in the inner cavity of the cylinder body 1, while preventing foreign matter from entering the working section of the damper, reducing the number of times the damping fluid 9 needs to be replaced and improving the reliability of the damper operation.

[0033] Furthermore, a guide bearing 12 can be installed in the sealing end cover 10. The sealing end cover 10, the sealing ring 11 and the guide bearing 12 are coaxial with the piston rod 4. The inner walls of the sealing ring 11 and the guide bearing 12 are in a hole-shaft matching state with the piston rod 4. The guide bearing 12 can provide a guiding function for the axial movement of the piston rod 4.

[0034] Furthermore, the inner end surface of the sealing end cover 10 fits with the end surface of the positioning bushing 8 at the open end of the cylinder body 1, and the inner end of the sealing end cover 10 protrudes to form a boss extending into the inner cavity of the cylinder body 1, and the circumferential outer side wall of the boss can fit closely with the inner circumferential wall edge of the positioning bushing 8.

[0035] Furthermore, in this embodiment, the displacement sensor 7 is installed between the load connecting plate 2 and the sealing end cover 10 to monitor the relative displacement between the two. In this design, by using the displacement of the damper as the input of the control processor and the magnetic damping force as the final output, the magnetic damping force that changes with the displacement can be obtained.

[0036] Furthermore, the damper is also provided with a bidirectional limit unit, which has the characteristics of high rigidity and high damping, and can provide impact protection for the piston rod 4.

[0037] Specifically, if Figure 1As shown, the bidirectional limit unit includes two buffer limit structures, which are arranged in the cylinder body 1, and the two buffer limit structures are arranged at the axial ends of the end of the piston rod 4. When the load connecting plate 2 is not subjected to external force (such as external impact force), the end of the piston rod 4 forms an axial gap with the two buffer limit structures; when the load connecting plate 2 is subjected to positive or negative external force (such as impact force), the end of the piston rod 4 can move to contact one of the buffer limit structures to form a bidirectional buffer protection. Generally speaking, the positive direction is the direction from the load connecting plate 2 to the cylinder body 1 along the axis of the cylinder body 1, and the reverse direction is the opposite.

[0038] Furthermore, the buffer limit structure includes a limit plate and an elastic member, the limit plate is connected to the cylinder body through the elastic member, and the limit plate has a limit surface for the piston rod to resist. Furthermore, the rigidity of the elastic member is greater than the rigidity of the elastic support member.

[0039] In some embodiments, in order to improve performance, multiple elastic members in the buffer limit structure can be provided, and the multiple elastic members should be evenly spaced and distributed in the cylinder body 1 along the circumference of the cylinder body 1. In some embodiments, in order to improve the stability of the limit plate, a guide structure for guiding the limit plate is also fixed in the cylinder body 1.

[0040] For ease of understanding, in this embodiment, the two buffer limit structures are subdivided into a first buffer limit structure and a second buffer limit structure, and their composition and layout positions are as follows: like Figure 1 and Figure 5 As shown, the first buffer limit structure includes a first limit plate 13 and a first elastic member 14. The first limit plate 13 and the first elastic member 14 are distributed along the axial direction of the cylinder body 1. The first limit plate 13 is connected to the open end of the cylinder body 1 through the first elastic member 14. The first limit plate 13 has a first limit surface for the piston rod 4 to contact.

[0041] When the load connecting plate 2 is not subjected to external force (such as external transient impact force), there is a large axial gap between the first limiting surface of the first limiting plate 13 and the head of the piston rod 4, and the two are not in contact.

[0042] Further, a plurality of first elastic members 14 may be provided, and the plurality of first elastic members 14 are preferably evenly spaced and distributed in the cylinder body 1 along the circumference of the cylinder body 1. The first elastic member 14 includes but is not limited to a spring; when a spring is used, one end of the spring is preferably connected to the sealing end cover 10 connected to the open end of the cylinder body 1, and the other end is preferably connected to the first limit plate 13. Under the connection of the spring, the first limit plate 13 is located in the positioning bushing 8 at the open end of the cylinder body 1.

[0043] Generally speaking, mounting holes can be set on the first limiting plate 13 and the sealing end cover 10, and a certain length is reserved at both ends of the spring as a joint. By assembling and fixing the joint into the mounting holes, the spring and the sealing end cover 10 and the first limiting plate 13 can be connected and installed.

[0044] like Figure 6 As shown, the second buffer limit structure includes a second limit plate 15 and a second elastic member 16. The second limit plate 15 is connected to the bottom wall end of the cylinder body 1 through the second elastic member 16, and is located in the positioning sleeve 8 near the bottom wall end of the cylinder body 1. The second limit plate 15 has a second limit surface for the piston rod 4 to resist.

[0045] When the load connecting plate 2 is not subjected to external force, there is a large axial gap between the second limiting surface of the second limiting plate 15 and the piston rod 4, and the two are not in contact. The first elastic member 14 and the second elastic member 16 are preferably high-rigidity springs.

[0046] Furthermore, a guide structure for guiding the second limit plate 15 is fixed in the cylinder body 1. The guide structure is preferably a guide rod 17 installed at the center of the bottom wall end of the cylinder body 1. Correspondingly, the second limit plate 15 has a perforation, and the second limit plate 15 is sleeved on the peripheral side of the guide rod 17 through the perforation, so that the guide rod 17 provides an axial movement guiding function for the second limit rod. The second elastic member 16 includes but is not limited to a spring sleeved on the outer periphery of the guide rod 17.

[0047] The guide rod 17 is preferably connected to the cylinder body 1 by screws. When the installation position of the guide rod 17 is selected at the center line of the cylinder body 1, the head of the piston rod 4 has a corresponding avoidance hole for avoiding the guide rod 17.

[0048] It can be known that, in some other embodiments, a plurality of second elastic members 16 may be arranged along the circumference of the cylinder body 1 , and the first elastic member 14 and the second elastic member 16 may also be other feasible elastic structures such as spring sheets and spring washers.

[0049] Furthermore, in some embodiments, the damper can replace positioning bushings 8 with different axial lengths and support springs with different specifications to obtain different damping working displacement sections; or by replacing positioning bushings 8 with different inner diameters and support springs with different specifications, the bidirectional limit unit can replace the first elastic member 14 and the second elastic member 16 with different specifications to obtain different impact resistance strokes.

[0050] In general, under this design, the damper is in an enabled state, and under non-impact conditions, low-stiffness and low-damping vibration isolation is performed through a wide-gap damping structure, damping fluid 9, a low-stiffness support spring, and a nonlinear magnetic damping force based on displacement control.

[0051] When impacted, the load connecting plate 2 drives the piston rod 4 to move, and the controller actively changes the current in the coil 6 to achieve variable damping control, so that when the initial load velocity is large, excessive damping force will not be generated to ensure the smoothness of the anti-impact process. Under continuous action, the load connecting plate 2 moves until the bidirectional limit unit is triggered, generating an effective limit with high stiffness and high damping.

[0052] When the bidirectional limiting unit is triggered, the end of the piston rod 4 contacts the first limiting plate 13 or the second limiting plate 15. When the piston rod 4 moves to contact the first limiting plate 13, the piston rod 4 can drive the first limiting plate 13 to move toward the open end of the cylinder body 1, and is subject to the restoring force of the first elastic member 14, so as to achieve axial limiting at one end; when the piston rod 4 moves to contact the second limiting plate 15, the piston rod 4 can drive the second limiting plate 15 to move toward the bottom wall end of the cylinder body 1, and is subject to the restoring force of the second elastic member 16, so as to achieve axial limiting at the other end. At the same time, when the piston rod 4 contacts the first limiting plate 13 or the second limiting plate 15, the inner cavity flow channel of the cylinder body 1 becomes narrower, and the extrusion and shearing motion of the damping fluid 9 generates a large damping force, which assists the first elastic member 14 or the second elastic member 16 to achieve the limiting function.

[0053] After the impact is over, the damper uses the elastic restoring force of the support spring to restore the damper to its initial working position.

[0054] It should be understood that the non-impact working condition mentioned in this application means: there is no instantaneous large impact, but there may be a relatively gentle external disturbance. When there is a relatively gentle external disturbance, the load connecting plate 2 still has displacement, and compared with the impact disturbance, the initial velocity of the load subjected to the non-impact disturbance changes more slowly.

[0055] It should be understood that expressions such as "include" and "may include" used in this application indicate the existence of the disclosed functions, operations or constituent elements, and do not limit one or more additional functions, operations and constituent elements. In this application, terms such as "include" and / or "have" may be interpreted as indicating specific characteristics, numbers, operations, constituent elements, components or combinations thereof, but may not be interpreted as excluding the existence or possibility of adding one or more other characteristics, numbers, operations, constituent elements, components or combinations thereof.

[0056] It should be understood that the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

[0057] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of this application, the meaning of "plurality" is two or more, unless otherwise clearly and specifically defined.

[0058] In this application, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be an indirect connection through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0059] It will be easily understood by those skilled in the art that the above description is only a preferred embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present application shall be included in the scope of protection of the present application.

Claims

1. A nonlinear bidirectional active anti-impact damper, characterized in that: It comprises a cylinder body (1), a load connecting plate (2), an elastic support member (3) and a magnetic damping component, wherein: The load connecting plate (2) is floatingly mounted on one axial end of the cylinder body (1) via an elastic support member (3); the load connecting plate (2) is connected to a piston rod (4), and the end of the piston rod (4) extends into the cylinder body (1); The magnetic damping assembly comprises a magnet (5) and a coil (6), one of the magnet (5) and the coil (6) being connected to the end of the piston rod (4), and the other being connected to the inside of the cylinder body (1); The damper further comprises a displacement sensor (7) and a controller, wherein the displacement sensor (7) is used to detect displacement data of the load connection plate (2), and the controller is connected to the displacement sensor (7) and the coil (6) respectively, and the controller is used to control the current of the coil (6) according to the displacement data detected by the displacement sensor (7), so that the magnetic damping coefficient of the damper is linearly related to the displacement of the load connection plate (2), so that when the load connection plate (2) moves with the force difference between the external force and the elastic force of the elastic support member (3), the coil (6) cuts the magnetic lines of force of the magnet (5) to generate a magnetic damping force that changes nonlinearly with the displacement.

2. The nonlinear bidirectional active anti-impact damper according to claim 1, characterized in that: The piston rod (4) is slidably sealed with the open end of the cylinder body (1), and the cylinder body (1) is filled with a damping fluid (9).

3. The nonlinear bidirectional active anti-impact damper according to claim 1, characterized in that: Two positioning bushings (8) are arranged in the cylinder body (1) at intervals along the axial direction, and the magnet (5) or the coil (6) is connected to the cylinder body (1) via the two positioning bushings (8).

4. The nonlinear bidirectional active anti-impact damper according to claim 2, characterized in that: Two buffer limit structures are arranged in the cylinder body (1), and the two buffer limit structures are arranged at two axial ends of the cylinder body (1). The end of the piston rod (4) is located between the two buffer limit structures, and the end of the piston rod (4) can move to abut against any one of the buffer limit structures.

5. The nonlinear bidirectional active anti-shock damper according to claim 4, characterized in that: The buffer limit structure comprises a limit plate and an elastic member, the limit plate is connected to the cylinder body (1) via the elastic member, and the limit plate has a limit surface for the piston rod (4) to abut against.

6. The nonlinear bidirectional active anti-shock damper according to claim 5, characterized in that: A plurality of elastic members are provided, and the plurality of elastic members are evenly spaced and distributed in the cylinder body (1) along the circumference of the cylinder body (1).

7. The nonlinear bidirectional active anti-shock damper according to claim 5, characterized in that: A guide structure for guiding the limit plate is also fixed in the cylinder body (1).

8. The nonlinear bidirectional active anti-shock damper according to claim 5, characterized in that: The rigidity of the elastic member is greater than the rigidity of the elastic support member (3).

9. The nonlinear bidirectional active anti-shock damper according to claim 5, characterized in that: The damping fluid (9) is capable of flowing through the buffer limiting structure and the end of the piston rod (4).

10. The nonlinear bidirectional active shock damper according to any one of claims 1 to 9, characterized in that: The open end of the cylinder body (1) is sealed with a sealing end cover (10) with a perforation, the piston rod (4) extends into the inner cavity of the cylinder body (1) along the perforation, and a sealing structure is provided between the inner wall of the perforation and the circumferential surface of the piston rod (4).

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