A magnetorheological damping device

Abstract

The utility model discloses a kind of magnetorheological damper devices, provide a kind of maintenance-free, no environmental pollution, leakage risk low and the magnetorheological damper device of big resistance. Including cylinder, sealing cavity formed by sealing and its inside magnetorheological fluid, piston is equipped in cylinder;Key improvement lies in: setting external convection pipe intercommunication two capacity cavity, and elastic member is set on damping pull rod, and permanent magnet is set at the end of cylinder and generates magnetic field.When ship is impacted, piston compression stroke forces magnetorheological fluid to flow through permanent magnetic field and generate high damping. Whole process does not need power, leakage risk is low, solve traditional hydraulic damper device oil pollution, hydraulic damper device size limit and the defect that electromagnetic type needs continuous power supply, realize buffer system maintenance-free operation.

Description

TECHNICAL FIELD

[0001] The utility model relates to a damping device, especially a magneto-rheological damping device.

BACKGROUND

[0002] In the connection and buffering application scenarios of large equipment or structures, the severe pulling or extrusion force between the connecting bodies due to external load seriously threatens the equipment structural integrity and operation safety. To resolve such problems, traditional hydraulic damping devices have long been used as the mainstream buffering scheme. However, the valve core will face irreversible wear and corrosion failure in continuous vibration or harsh working conditions with high humidity and high corrosion, resulting in a gradual decline in sealing performance. If hydraulic oil leaks, not only will the environment be polluted, but also high operating costs and forced interruption of work will be caused. Moreover, the maximum resistance of the hydraulic damping device depends on the system oil pressure and the size of the valve core. A large-size valve core needs to be configured to withstand the huge impact kinetic energy generated by large equipment, causing maintenance difficulties. With the update of technology, some hydraulic damping devices are gradually replaced by traditional electromagnetic magneto-rheological damping devices. However, the electromagnetic magneto-rheological damping device needs to be powered continuously to maintain the work of the excitation coil. The coil lead will still cause liquid leakage risk under long-term high-frequency impact. Moreover, the supporting precision circuit control system is easily corroded or short-circuited in harsh environments such as humidity, salt spray, and dust.

[0003] The above industry pain points highlight the urgent need for a intrinsically safe buffering device in the market. A product that can completely eliminate the ecological pollution hazard of oil leakage, limit the size of the hydraulic damping device, and eliminate the dependence on power, and work reliably for decades without any active maintenance.

[0004] In addition, the traditional buffering system faces a fundamental contradiction between the demand for damping force and the bearing capacity of the external fixed base. When a single damping device is impacted, the reaction force generated will be completely applied to the fixed base. The repeated impact load forces the base to bear periodic large unidirectional forces, which may cause damage to the fixed base in the long term. Moreover, for large equipment, the required damping force is larger, and the bearing capacity requirement of the fixed base is also higher.

[0005] Therefore, the utility model is proposed to solve the above problems.

UTILITARY MODEL CONTENT

[0006] The utility model aims at overcoming the prior art's insufficient, provide a kind of magneto-rheological damper, provide a kind of maintenance-free, no environmental pollution, leakage risk low and the magneto-rheological damper of big resistance. Including cylinder, sealing cavity formed by sealing and its inside magneto-rheological fluid, cylinder is equipped with piston;Key improvement lies in: setting external convection pipe intercommunication two capacity cavities, and the first elastic member is set on damping pull rod, and permanent magnet is set at the end of cylinder and generates magnetic field.When equipment is impacted, piston compression stroke forces magneto-rheological fluid to flow through permanent magnetic field and generates high damping. Whole process does not need power, leakage risk is low, solve the defects that traditional hydraulic damping device leaks and pollutes, hydraulic damping device size limit and electromagnetic type need continuous power supply, realize the maintenance-free operation of buffer system.

[0007] In order to solve the above technical problems, the utility model provides a kind of magneto-rheological damper, comprising:

[0008] Cylinder, the cylinder both ends are sealed and have sealing cavity filled with magneto-rheological fluid;

[0009] Piston head, the piston head is reciprocatingly slidably arranged in sealing cavity, and the sealing cavity is divided into first capacity cavity and second capacity cavity by piston head;

[0010] Damping pull rod, one end of the damping pull rod extends into the first capacity cavity and is fixedly connected with the piston head, and the other end of the damping pull rod extends out of one end of the cylinder and is connected with the first expansion connecting assembly;

[0011] Convection pipe, the convection pipe is respectively communicated with the first capacity cavity and the second capacity cavity at both ends, so that the magneto-rheological fluid is extruded by the piston head and flows between the first capacity cavity and the second capacity cavity;

[0012] Permanent magnet, the permanent magnet is fixedly arranged at the end of the cylinder and close to the first capacity cavity;

[0013] First elastic member, the first elastic member is arranged in the first capacity cavity, one end of the first elastic member is elastically abutted to the piston head, and the other end of the first elastic member is elastically abutted to the end of the cylinder close to the first capacity cavity.

[0014] As described above, a kind of magneto-rheological damper, the cylinder both ends are respectively provided with first interface and second interface communicated with the first capacity cavity, the second capacity cavity, the convection pipe both ends are respectively connected with first interface and second interface.

[0015] As described above, a kind of magneto-rheological damper, the convection pipe both ends are respectively connected with first interface and second interface by shock-absorbing liquid pipe.

[0016] As described above, a kind of magneto-rheological damper, the piston head is located at the second capacity cavity side and is protrudedly formed with blocking part, and when the blocking part abuts the corresponding end of the cylinder, the second capacity cavity is always communicated with the second interface.

[0017] The magnetic rheological damping device as claimed in any one of the preceding claims, wherein the convection pipe is arranged outside the cylinder barrel, and an adjusting valve is arranged on the convection pipe between the first interface and the second interface.

[0018] The magnetic rheological damping device as claimed in any one of the preceding claims, wherein the cylinder barrel is connected with a port flange at the end of the first cavity, the port flange is provided with an annular groove, and the permanent magnet is embedded in the annular groove.

[0019] The magnetic rheological damping device as claimed in any one of the preceding claims, wherein the cylinder barrel is connected with the port flange at the end of the first cavity through internal threads and external threads, the annular groove is arranged between the end surface of the port flange and the threaded connection part of the port flange, and the cylinder barrel is abutted to the inner side of the end surface of the port flange to cover and seal the annular groove.

[0020] The magnetic rheological damping device as claimed in any one of the preceding claims, wherein the permanent magnet is composed of a plurality of non-circular magnetic rings and embedded in the annular groove, or the permanent magnet is composed of a plurality of magnetic columns and embedded in the annular groove.

[0021] The magnetic rheological damping device as claimed in any one of the preceding claims, wherein the permanent magnet is arranged in a Halbach array.

[0022] The magnetic rheological damping device as claimed in any one of the preceding claims, further comprising a second elastic member, the second elastic member is arranged in the second cavity, one end of the second elastic member is elastically abutted to the piston head, and the other end of the second elastic member is elastically abutted to the end of the cylinder barrel close to the second cavity.

[0023] The magnetic rheological damping device as claimed in any one of the preceding claims, wherein the other end of the cylinder barrel away from the first expansion connection assembly is connected with a second expansion connection assembly.

[0024] The magnetic rheological damping device as claimed in any one of the preceding claims, wherein the first elastic member is a disc spring assembly and sleeved on the damping pull rod.

[0025] The magnetic rheological damping device as claimed in any one of the preceding claims, wherein the other end of the cylinder barrel away from the first expansion connection assembly is connected with another cylinder barrel of the same configuration as the cylinder barrel, and the outer end of the damping pull rod of the other cylinder barrel is connected with a damping rod joint.

[0026] The magnetic rheological damping device as claimed in any one of the preceding claims, wherein the two cylinder barrels are fixedly connected through a connecting flange, and the two cylinder barrels and the connecting structure thereof are symmetrically arranged.

[0027] The magnetic rheological damping device as claimed in any one of the preceding claims, wherein the first expansion connection assembly comprises a damping rod joint fixedly connected with the outer end of the damping pull rod, a universal ball head hingedly connected with the damping rod joint, and a universal ball head seat hingedly connected with the universal ball head, and the universal ball head seat is provided with an expansion connection part for external connection.

[0028] As described above, a magnetorheological damping device further includes a docking cylinder. The end of the cylinder away from the first extended connection assembly is connected to the end of the docking cylinder. The other end of the docking cylinder is connected to another cylinder configured identically to the cylinder. The outer end of the damping rod on the other cylinder is connected to a damping rod connector. The end of the damping rod near the piston head extends to form an extension portion, which is movably inserted through the docking cylinder.

[0029] As described above, in a magnetorheological damping device, the ends of the two cylinders are fixedly connected to a connecting cylinder via a connecting flange, and the two cylinders and their connecting structure are arranged symmetrically.

[0030] Compared with the prior art, the present invention has the following advantages:

[0031] 1. The magnetic field of the permanent magnet is precisely positioned at the connection between the convection tube and the first cavity. When the damping device is subjected to tensile force, the magnetorheological fluid must flow through the magnetic field region into the convection tube. The flow resistance increases dramatically, efficiently dissipating the kinetic energy under tension. After the external force disappears, the first elastic element pushes the piston back to its original position. At this time, the magnetorheological fluid in the second cavity flows to the first cavity through the convection tube. The influence of the magnetic field is smaller than that of the compression stroke, allowing for rapid reset and preparation to withstand the next tensile force.

[0032] 2. A closed magnetorheological fluid system is adopted. The magnetorheological fluid is sealed in the first cavity, the second cavity and the external convection pipe, which avoids the risk of environmental pollution caused by leakage of traditional hydraulic oil and meets environmental protection requirements.

[0033] 3. The magnetic field is provided by a permanent magnet, not an electromagnetic coil, so there is no need for a continuous power supply to maintain the magnetic field, saving energy and simplifying the system.

[0034] 4. The permanent magnet is sealed between the port flange and the cylinder, and is not sensitive to corrosive water environments such as high humidity and salt spray, and can resist harsh environments.

[0035] 5. The permanent magnet has a stable and long-lasting magnetic field, and the disc spring is fatigue-resistant, so it can work reliably without active maintenance.

[0036] 6. A mechanical regulating valve is installed on the convection pipe, which can change the effective flow area of ​​the flow channel through a purely mechanical means, thereby adjusting the flow resistance of the magnetorheological fluid and providing manual adjustment capability of damping force within a certain range, suitable for different working conditions or different equipment tonnage requirements.

[0037] 7. A shock-absorbing liquid passage is installed between the convection pipe and the first and second interfaces to reduce the impact of external vibration on the damping device, while also buffering the fluid impact inside the convection pipe and extending its service life.

[0038] 8. The permanent magnets are arranged in a Halbach array, which can greatly optimize the magnetic field utilization and enhance the magnetic field in a specific direction, namely, enhance the magnetic field at the convection tube and the first interface.

[0039] 9. A second elastic element is installed in the second cavity to construct a double-sided elastic reset and support mechanism, thereby enhancing bidirectional load-bearing capacity, reset stability, and impact resistance.

[0040] 10. The combined magnetorheological damping device is composed of two magnetorheological damping devices. The first impact can simultaneously drive the pistons of the two damping devices to compress, significantly increasing the total damping force and easily coping with ultra-large impact kinetic energy. Furthermore, by utilizing the symmetrical and opposite piston movements, the reaction forces generated by the impact cancel each other out at the flange, thereby transforming the traditional unidirectional impact load into a balanced force system inside the damping device, significantly reducing the load on the external structure. [Attached Image Description]

[0041] The specific embodiments of this utility model will be further described in detail below with reference to the accompanying drawings, wherein:

[0042] Figure 1 This is a schematic diagram of the overall structure of a magnetorheological damping device according to the present invention;

[0043] Figure 2 This is a cross-sectional view of a magnetorheological damping device of this utility model under stress.

[0044] Figure 3 This is a cross-sectional view of a magnetorheological damping device of this utility model during resetting;

[0045] Figure 4 for Figure 3 A magnified view of part A;

[0046] Figure 5 This is an exploded view of a magnetorheological damping device according to this utility model;

[0047] Figure 6 This is a schematic diagram of the overall structure of a magnetorheological damping device according to the present invention;

[0048] Figure 7 This is a cross-sectional view of a magnetorheological damping device according to the present invention;

[0049] Figure 8 This is an exploded view of a magnetorheological damping device according to this utility model;

[0050] Figure 9 This is a schematic diagram of the overall structure of a magnetorheological damping device according to the present invention;

[0051] Figure 10 for Figure 9a cross-sectional view of the B-B section of figure 1 ;

[0052] Figure 11 is Figure 9 a cross-sectional view of the C-C section of figure 1 ;

[0053] Figure 12 is an exploded view of a magnetorheological damping device of the utility model.

DETAILED DESCRIPTION

[0054] The embodiments of the utility model will be described below in detail in combination with the drawings.

[0055] As Figures 1 to 9As shown, in an embodiment of the magnetorheological damping device of this utility model, it includes a cylinder 1, which is sealed at both ends and has a sealed cavity 10 filled with magnetorheological fluid; a piston head 41, which is reciprocally slidably disposed in the sealed cavity 10, and the sealed cavity 10 is divided into a first cavity 11 and a second cavity 12 by the piston head 41; a damping rod 4, one end of which extends into the first cavity 11 and is fixedly connected to the piston head 41, and the other end of which extends out of one end of the cylinder 1 and is connected to a first extension link. The convection tube 5 is connected to the first cavity 11 and the second cavity 12 at both ends, so that the magnetorheological fluid is squeezed by the piston head 41 and flows between the first cavity 11 and the second cavity 12 accordingly; the permanent magnet 7 is relatively fixedly disposed at the end of the cylinder 1 and close to the first cavity 11; the first elastic member 61 is placed in the first cavity 11, with one end of the first elastic member 61 elastically abutting against the piston head 41 and the other end elastically abutting against the end of the cylinder 1 close to the first cavity 11. Specifically, the system includes a cylinder 1, with both ends sealed by a port flange 2 and a second end cap 3, forming a sealed cavity 10 inside the cylinder 1. Preferably, the second end cap 3 can be integrally formed with the cylinder 1. The sealed cavity 10 is filled with magnetorheological fluid. A damping rod 4 passes through the port flange 2, and a first dynamic sealing mechanism 42 is provided between the damping rod 4 and the port flange 2. The damping rod 4 can reciprocate along the axis of the cylinder 1 within the sealed cavity 10. A piston head 41 is disposed inside the cylinder 1 and fixed to the end of the damping rod 4. A second dynamic sealing mechanism 43 is provided between the piston head 41 and the inner wall of the cylinder 1. The piston head 41 divides the sealed cavity 10 into a first cavity 11 near the port flange 2 and a second cavity 12 near the second end cap 3. A convection pipe 5 is disposed outside the cylinder 1 and passes through a first interface 13 and a second interface 14 opened on the cylinder 1. The first cavity 11 and the second cavity 12 are connected respectively; the first elastic element 61 is sleeved on the damping rod 4, one end of which acts on the piston head 41 and the other end acts on the port flange 2; the permanent magnet 7 is set in the area of ​​the port flange 2 or the cylinder 1 near the port flange 2, and is configured to generate a constant magnetic field in the connection section between the convection pipe 5 and the first cavity 11; when the damping rod 4 is subjected to external force and the piston head 41 moves toward the port flange 2: the piston head 41 compresses the first elastic element 61 and drives the magnetorheological fluid in the first cavity 11 to flow into the convection pipe 5 after passing through the magnetic field generated by the permanent magnet 7. At this time, the flow resistance of the magnetorheological fluid increases significantly under the action of the magnetic field; when the external force disappears: the first elastic element 61 pushes the piston head 41 to move toward the second end cap 3, driving the magnetorheological fluid in the second cavity 12 to flow through the convection pipe 5 to the first cavity 11. At this time, the flow resistance of the magnetorheological fluid is relatively small. Preferably, the piston head 41 has a blocking portion 44 protruding from the side of the second cavity 12, and when the blocking portion 44 abuts against the corresponding end of the cylinder 1, the second cavity 12 is always in communication with the second interface 14, such as... Figure 2As shown, the blocking part 44 is a protrusion on the piston head 41, and the outer diameter of the blocking part is smaller than the outer diameter of the piston head. More specifically, the cylinder 1 is cylindrical and integrally machined from a high-strength corrosion-resistant alloy material. The two ends of the cylinder 1 are respectively connected to the port flange 2 and the second end cap 3 via precision-machined threaded connections, and rubber sealing rings are provided on the connecting surfaces to achieve static sealing, forming a completely closed sealed cavity 10. The sealed cavity 10 is filled with magnetorheological fluid, which is composed of ferromagnetic particles, surfactants, and a suspension. The size of the ferromagnetic particles is generally in the range of 1-10 μm, and they are generally made of magnetic materials such as iron, cobalt, and nickel; the carrier fluid is usually silicone oil, kerosene, or mineral oil, which has good flame retardancy and temperature stability, and does not pollute the environment, nor does it cause corrosion when in contact with common materials. Magnetorheological fluid is a smart material; when a magnetic field exists in the magnetorheological fluid, the shear strength of the fluid changes dramatically, which is the so-called magnetorheological effect. The damping rod 4 is made of stainless steel and passes through the center hole of the port flange 2. A first dynamic sealing mechanism 42 is provided between the damping rod 4 and the port flange 2. Preferably, the first dynamic sealing mechanism 42 includes a dustproof ring, two anti-wear rings, and a V-shaped sealing ring arranged in sequence to ensure that the damping rod 4 is leak-free when the cylinder 1 reciprocates axially. One end of the damping rod 4 that extends into the sealing cavity 10 is threadedly fixed to a piston head 41. The outer edge of the piston head 41 and the inner wall of the cylinder 1 form a second dynamic sealing mechanism 43. Preferably, the second dynamic sealing mechanism 43 includes an anti-wear ring, a support ring, a V-shaped sealing ring, a support ring, and an anti-wear ring nested in sequence on the outer edge of the piston head 41. This divides the sealing cavity 10 into a first cavity 11 adjacent to the port flange 2 and a second cavity 12 adjacent to the second end cover 3. A U-shaped convection pipe 5 is installed outside the cylinder 1. This convection pipe 5 is formed by bending a seamless steel pipe. One end of the pipe connects to the side wall interface of the first cavity 11 near the port flange 2 via a pipe connector 52, and the other end connects to the side wall interface of the second cavity 12 near the second end cap 3 via the same pipe connector 52. Preferably, both ends of the convection pipe 5 are connected to the first interface 13 and the second interface 14 respectively via shock-absorbing liquid-passing pipes 53. The shock-absorbing liquid-passing pipes 53 can be made of flexible metal bellows. This flexible shock-absorbing connection effectively isolates vibration transmission, reduces operating noise, and mitigates damage to the pipeline from fluid impact, thereby improving the stability, reliability, and user comfort of the device. A mechanical regulating valve 51 is installed in the middle of the convection pipe 5. Preferably, the regulating valve 51 is a throttle valve, providing manual adjustment capability of damping force within a certain range, suitable for different working conditions or different equipment tonnage requirements.

[0056] In some embodiments, the other end of the cylinder 1 away from the first extended connection component 8 is connected to a second extended connection component 9.

[0057] like Figure 5 and Figure 6As shown, in some embodiments, the first elastic element 61 is a disc spring assembly, which includes multiple coaxially stacked disc springs. The disc spring assembly is fitted with the damping rod 4 in the section of the first cavity 11. One end of the disc spring assembly abuts against the piston head 41, and the other end presses against the inner side of the port flange 2. Preferably, the disc springs are made of chromium vanadium alloy spring steel and are heat-treated to enhance fatigue resistance. Preferably, in some embodiments, a second elastic element 62 is also included. The second elastic element 62 is placed in the second cavity 12, with one end elastically abutting against the piston head 41 and the other end elastically abutting against the end of the cylinder 1 near the second cavity 12. By adding the second elastic element 62 on the second cavity 12 side, a bilaterally symmetrical elastic reset and support structure is constructed, significantly enhancing the static stiffness, bidirectional load-bearing capacity, reset stability, and impact protection capability of the device. Preferably, the second elastic element 62 is also a disc spring assembly, which includes multiple coaxially stacked disc springs.

[0058] like Figure 5 and Figure 6 As shown, in some embodiments, the permanent magnet 7 is machined into an annular structure. A coaxial annular groove 21 is machined on the mounting surface of the port flange 2 facing the cylinder 1. The permanent magnet 7 is embedded in the annular groove 21, and a sealing structure 71 for sealing the permanent magnet 7 is provided at the connection between the port flange 2 and the cylinder 1. The end of the cylinder 1 near the first cavity 11 is sealed to the external thread of the port flange 2 through an internal thread. The annular groove 21 is located between the end face of the port flange 2 and the threaded connection part of the port flange 2. The end of the cylinder 1 near the first cavity 11 abuts against the inner side of the end face of the port flange 2, thus covering and sealing the annular groove 21. Preferably, the sealing structure is a threaded structure between the port flange 2 and the cylinder 1 and an O-ring rubber seal. The installation position of the permanent magnet 7 precisely covers the inlet area of ​​the flow channel from the first cavity 11 to the convection pipe 5 interface, allowing the magnetorheological fluid flowing through this area to pass through the magnetic field generated by the permanent magnet 7. In other embodiments, the permanent magnet 7 can also be installed on the outer wall of the cylinder 1, and the position is close to the port flange 2. Preferably, the permanent magnet 7 is composed of several non-circular magnetic rings embedded in the annular groove 21, or the permanent magnet 7 is composed of several magnetic pillars embedded in the annular groove 21. Preferably, in some embodiments, such as Figure 12 As shown, the permanent magnet 7 is arranged in a Halbach array, which greatly optimizes the magnetic field utilization and enhances the magnetic field in a specific direction. The magnetic field in a specific direction refers to the magnetic field on the side of the convection tube 5 and the first interface 13.

[0059] The working process is as follows: When a tensile impact load is applied to the damping rod 4, the damping rod 4 drives the piston head 41 to move towards the port flange 2. During this process: 1. The piston head 41 compresses the disc spring assembly 61 to store mechanical energy, while simultaneously reducing the volume of the first cavity 11; 2. After the magnetorheological fluid in the first cavity 11 is pressurized, it is forced to flow through the outlet channel covered by the magnetic field of the permanent magnet 7; 3. Under the action of the magnetic field, the magnetic particles in the magnetorheological fluid instantly form a chain structure, and the fluid viscosity increases sharply, generating extremely high flow resistance; 4. The high-pressure fluid then enters the convection pipe 5, and the high resistance characteristics dissipate the tensile kinetic energy. When the tensile load disappears: 1. The disc spring assembly 61 releases elastic potential energy, pushing the piston head 41 to move towards the second end cap 3; 2. The volume of the second cavity 12 decreases, and the magnetorheological fluid inside it is pressurized and flows back to the first cavity 11 through the convection tube 5; 3. Since this return path flows from the convection tube 5 to the first cavity 11, and the first cavity 11 tends to increase in volume under the action of the disc spring assembly 61, the influence of the magnetic field is much smaller than when the tension damping rod 4 is stretched; 4. The magnetorheological fluid flows back rapidly under low resistance, prompting the piston to reset in preparation for the next impact.

[0060] like Figures 7-9 As shown, this utility model also discloses a magnetorheological damping device. Specifically, to achieve double damping force while eliminating reaction force, two individual magnetorheological damping devices are assembled together via flange 30. The second end cap 3 of the first damping device is directly and rigidly connected to the second end cap 3 of the second damping device to form flange 30. Specifically, the other end of the cylinder 1 away from the first extended connection assembly 8 is connected to another cylinder 1 with the same configuration as the first cylinder 1. The outer end of the damping rod 4 on the other cylinder 1 is connected to a damping rod connector 22. The ends of the cylinders 1 are fixedly connected to each other via connecting flange 30, and the two cylinders 1 and their connection structure are symmetrically arranged. The first extended connection assembly 8 includes a damping rod connector 22 fixedly connected to the outer end of the damping rod 4, a universal ball joint 81 hinged to the damping rod connector 22, and a universal ball joint seat 82 ball-hinged to the universal ball joint 81. The universal ball joint seat 82 is provided with an extended connection part 83 for external connection. An integrally formed flange 30 connects the first damping device and the second damping device respectively; the damping rod 4 of the first damping device and the damping rod 4 of the second damping device are coaxial and move in opposite directions. By utilizing the symmetrical and opposite piston movements, the reaction forces generated by the impact cancel each other out at the flange 30, thereby transforming the traditional unidirectional impact load into a balanced force system inside the damping device, significantly reducing the load on the external structure.

[0061] In some embodiments, a magnetorheological damping device is provided, further comprising a docking cylinder 31. The end of the cylinder 1 furthest from the first extended connection assembly 8 is connected to the end of the docking cylinder 31. The other end of the docking cylinder 31 is connected to another cylinder 1 configured identically to the first cylinder 1. The outer end of a damping rod 4 on this other cylinder 1 is connected to a damping rod connector 22. An extension 45 extends from the end of the damping rod 4 near the piston head 41, and the extension 45 movably passes through the docking cylinder 31. The ends of the two cylinders 1 are fixedly connected to the docking cylinder 31 via a connecting flange 30. The two cylinders 1 and their connecting structure are symmetrically arranged. Figure 11 As shown, two second elastic elements 62 are provided. One end of the second elastic element 62 abuts against the piston head 41, and the other end abuts against the connecting flange 30. This constructs a bilaterally symmetrical elastic reset and support structure, significantly enhancing the static structural strength, bidirectional load-bearing capacity, reset stability, and impact protection capability of the device. Furthermore, the extension 45 slides within the docking cylinder 31, achieving synchronized movement of the piston assembly in the dual-cylinder structure, ensuring magnetorheological fluid sealing, and improving structural rigidity.

Claims

1. A magnetorheological damping device, characterized in that... include: Cylinder (1), the cylinder (1) is sealed at both ends and has a sealed cavity (10) filled with magnetorheological fluid; A piston head (41) is reciprocally slidably disposed in a sealed cavity (10), and the sealed cavity (10) is divided into a first cavity (11) and a second cavity (12) by the piston head (41). Damping rod (4), one end of which extends into the first cavity (11) and is fixedly connected to the piston head (41), and the other end of which extends out of the cylinder (1) and is connected to the first extension connection assembly (8); The convection tube (5) is connected at both ends to the first cavity (11) and the second cavity (12) respectively, so that the magnetorheological fluid is squeezed by the piston head (41) and flows between the first cavity (11) and the second cavity (12). A permanent magnet (7) is fixedly disposed at the end of the cylinder (1) and close to the first cavity (11); The first elastic element (61) is placed in the first cavity (11). One end of the first elastic element (61) elastically abuts against the piston head (41), and the other end elastically abuts against the end of the cylinder (1) near the first cavity (11).

2. The magnetorheological damping device as described in claim 1, characterized in that... The cylinder (1) has a first interface (13) and a second interface (14) at both ends, which are connected to the first cavity (11) and the second cavity (12), respectively. The convection pipe (5) is connected to the first interface (13) and the second interface (14) at both ends, respectively.

3. The magnetorheological damping device as described in claim 2, characterized in that... The two ends of the convection pipe (5) are connected to the first interface (13) and the second interface (14) respectively through the shock-absorbing liquid passage pipe (53).

4. The magnetorheological damping device as described in claim 2, characterized in that... The piston head (41) has a blocking part (44) protruding from the side of the second cavity (12), and when the blocking part (44) abuts against the corresponding end of the cylinder (1), the second cavity (12) is always in communication with the second interface (14).

5. The magnetorheological damping device as described in claim 2, characterized in that... The convection pipe (5) is externally located on the side of the cylinder (1), and a regulating valve (51) is provided on the convection pipe (5) and located between the first interface (13) and the second interface (14).

6. The magnetorheological damping device as described in claim 1, characterized in that... The cylinder (1) is connected to a port flange (2) through which a damping rod (4) extends from the end of the first cavity (11). The port flange (2) is provided with an annular groove (21), and the permanent magnet (7) is embedded in the annular groove (21).

7. The magnetorheological damping device as described in claim 6, characterized in that... The cylinder (1) is sealed to the external thread of the port flange (2) by the internal thread near the end of the first cavity (11). The annular groove (21) is located between the end face of the port flange (2) and the threaded connection part of the port flange (2). The cylinder (1) is abutted against the inner side of the end face of the port flange (2) to cover the annular groove (21).

8. The magnetorheological damping device as described in claim 7, characterized in that... The permanent magnet (7) is composed of several non-circular magnetic rings embedded in the annular groove (21), or the permanent magnet (7) is composed of several magnetic pillars embedded in the annular groove (21).

9. The magnetorheological damping device as described in claim 8, characterized in that... The permanent magnets (7) are arranged in a Halbach array.

10. The magnetorheological damping device as described in claim 1, characterized in that... It also includes a second elastic element (62), which is placed in the second cavity (12). One end of the second elastic element (62) elastically abuts against the piston head (41), and the other end elastically abuts against the end of the cylinder (1) near the second cavity (12).

11. The magnetorheological damping device as described in claim 1, characterized in that... The cylinder (1) is connected to a second extension connection assembly (9) at the other end away from the first extension connection assembly (8).

12. The magnetorheological damping device as described in claim 1, characterized in that... The first elastic element (61) is a disc spring assembly and is sleeved on the damping rod (4).

13. A magnetorheological damping device as described in any one of claims 1-10, characterized in that... The other end of the cylinder (1) away from the first extended connection assembly (8) is connected to another cylinder (1) configured the same as the cylinder (1), and the outer end of the damping rod (4) on the other cylinder (1) is connected to a damping rod connector (22).

14. The magnetorheological damping device as described in claim 13, characterized in that... The two cylinders (1) are fixedly connected at their ends by a connecting flange (30), and the two cylinders (1) and their connecting structure are arranged symmetrically.

15. The magnetorheological damping device as described in claim 13, characterized in that... The first extended connection assembly (8) includes a damping rod joint (22) fixedly connected to the outer end of the damping rod (4), a universal ball joint (81) hinged to the damping rod joint (22), and a universal ball joint seat (82) ball-jointed to the universal ball joint (81). The universal ball joint seat (82) is provided with an extended connection part (83) for connecting to the outside.

16. A magnetorheological damping device as described in any one of claims 1-10, characterized in that... It also includes a docking cylinder (31), the other end of the cylinder (1) away from the first extended connection assembly (8) is connected to the end of the docking cylinder (31), the other end of the docking cylinder (31) is connected to another cylinder (1) configured the same as the cylinder (1), the outer end of the damping rod (4) on the other cylinder (1) is connected to a damping rod connector (22); the end of the damping rod (4) near the piston head (41) extends to form an extension (45), the extension (45) is movably inserted through the docking cylinder (31).

17. The magnetorheological damping device as described in claim 16, characterized in that... The two cylinders (1) are fixedly connected to the docking cylinder (31) at their ends by a connecting flange (30), and the two cylinders (1) and their connecting structure are arranged symmetrically.

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