Radial multi-coil magnetorheological damper

Abstract

The utility model discloses a radial multi-coil magneto-rheological damper mainly is composed of piston rod, damper end cover, damper cylinder body, piston head, excitation coil, floating baffle, check valve etc, processes a plurality of radial distribution's excitation coil in the piston head inside, through the current intensity of independent control each group coil, utilizes the principle of magnetic field superposition, realizes that magnetic field intensity, direction, gradient can be adjusted, and increases the floating baffle in the cylinder body inside, and the magneto-rheological fluid work area in the cylinder body is divided into three chambers, through the closure state of control floating baffle on check valve, forms dynamic flow distribution mode, realizes the step or continuous formula extension of damping force, widens the damping force regulation range, the utility model discloses on the basis of traditional magneto-rheological damper has more control mode, increases the output of damping force, can realize the fine multistage damping adjustment, can adapt to the scene of vibration control precision requirement extremely high, is applicable to the damping system of automobile, railway etc. industry.

Description

Technical Field

[0001] This utility model relates to a magnetorheological damper, and more particularly to a radial multi-coil magnetorheological damper. Background Technology

[0002] Magnetorheological dampers are widely used in vibration reduction and absorption devices in vehicles, construction, and military industries. Their core advantage lies in the efficient integration of dynamic response and control performance. Magnetorheological fluids, under the influence of a magnetic field, can achieve millisecond-level response speeds, rapidly adapting to external vibration changes, far exceeding traditional hydraulic dampers. Simultaneously, by continuously varying the input current, the damping force can be precisely controlled, achieving a wide adjustable range from minimum viscous resistance to maximum damping to meet the precision requirements of different scenarios. Magnetorheological dampers have an effective operating frequency range covering 0.1-1000Hz, suppressing low-frequency resonant displacement and reducing high-frequency vibration transmission. Furthermore, they require only low voltage and low current for operation, resulting in low energy consumption and significantly reduced operating costs.

[0003] Traditional magnetorheological dampers have limited damping adjustment ranges, making it difficult to meet vibration control requirements under various complex operating conditions. Regarding magnetic field control, traditional single-coil designs have limitations; the magnetic field distribution is not flexible enough, preventing precise multi-level damping adjustment. The single-cavity structure results in a fixed amount of liquid participating in the rheological process, leading to a narrow damping force adjustment range, making it unsuitable for scenarios with extremely high vibration control precision requirements. Summary of the Invention

[0004] To overcome the problems existing in the background technology, this utility model proposes a radially multi-coil magnetorheological damper. Multiple sets of radially distributed excitation coils are machined inside the piston head, allowing independent current control. A variable composite magnetic field is formed by superimposing magnetic fields, expanding the damping force adjustment range, achieving fine-tuning, and improving response speed. Simultaneously, a dual-cavity flow-splitting structure is adopted, and the amount of liquid participating in the rheological operation is dynamically adjusted through a controllable one-way valve, further widening the damping force adjustment range and significantly improving damping performance and service life. This meets current market demands and is suitable for vibration reduction systems in industries such as automobiles and railways.

[0005] A radial multi-coil magnetorheological damper, characterized by comprising: a piston rod, a sealing ring I, a damper left end cap, a screw I, a screw II, a sealing ring II, an excitation coil, a screw III, a piston head right end cap, a nut, a floating partition, a floating piston, a sealing ring III, a right lifting lug, a damper right end cap, a screw IV, a sealing ring IV, a damper cylinder, a magnetorheological fluid channel, a sealing ring V, a one-way valve, a piston head, a piston head left end cap, a sealing ring VI, and a left lifting lug. The left end of the piston rod is fastened to the left lifting lug by a thread. A circular through hole is machined in the center of the left end cap of the damper. The piston rod is clearance-fitted with the inner surface of the circular through hole of the left end cap of the damper. The piston rod is sealed with the inner surface of the circular through hole of the left end cap of the damper by sealing ring I. The left end cap of the damper is clearance-fitted with the left end face of the damper cylinder. The left end cap of the damper is tightly connected to the damper cylinder by screw I. The left end cap of the damper is sealed with the damper cylinder by sealing ring VI. The right end of the piston rod is machined with an external thread. A circular through hole is machined in the center of the left end cap of the piston head. The left end of the piston head... The circular through-hole of the end cap is machined with internal threads. The right end of the piston rod is interference-fitted with the threaded hole of the left end cap of the piston head. The left end cap of the piston head is tightly connected to the piston head by screw II. The piston rod is threadedly fastened to the piston head through the threaded hole. The piston head is sealed to the damper cylinder by sealing ring II. The right end cap of the piston head is tightly connected to the piston head by screw III. The right end of the piston head is machined with external threads. The piston head is fastened to the right end cap of the piston head by a nut. The floating baffle and the outer surface of the floating piston are clearance-fitted with the inner surface of the damper cylinder. The diaphragm and damper cylinder are sealed by sealing ring V. The floating piston and damper cylinder are sealed by sealing ring IV. The right end cover of the damper is clearance-fitted to the right end face of the damper cylinder. The right end cover of the damper is tightly connected to the damper cylinder by screw IV. The right end cover of the damper is also sealed to the damper cylinder by sealing ring III. The right end cover of the damper has an external thread machined on its right end, and the right lifting lug has an internal thread machined on its right end. The right end cover of the damper is fastened to the right lifting lug through the machined external thread. Three sets of radially distributed excitation coils are machined inside the piston head. The two leads of the excitation coils... The lead wires are led out through the lead wire holes in the piston head and the left end cover of the piston head, and through the lead wire holes in the piston rod. The left end cover of the damper, the left end cover of the piston head, and the damper cylinder form a sealed chamber I. The right end cover of the piston head, the damper cylinder, and the floating partition form a sealed chamber II. The floating partition, the damper cylinder, and the floating piston form a sealed chamber III. The floating piston, the damper cylinder, and the right end cover of the damper form a sealed chamber IV. The sealed chambers I, II, and III are filled with magnetorheological fluid, and the sealed chamber IV is filled with compressed gas.When the piston rod is stretched axially, the magnetorheological fluid in sealed chamber I enters sealed chamber II through the fluid flow channel. When the piston rod is compressed axially, the magnetorheological fluid in sealed chamber II enters sealed chamber I through the magnetorheological fluid channel. As the piston rod moves axially, the volumes of sealed chambers I and II change accordingly. At this time, the floating baffle and floating piston achieve volume compensation by floating left and right in the axial direction. During this process, the amount of fluid participating in the rheological process in sealed chamber III is dynamically adjusted by the opening and closing state of the controllable one-way valve, achieving the purpose of multi-stage damping regulation.

[0006] Compared with the prior art, the advantages of this utility model are:

[0007] (1) This utility model processes three sets of radially distributed excitation coils inside the piston head. By independently controlling the current intensity of each set of coils, a dynamically variable composite magnetic field is formed using the principle of magnetic field superposition. The magnetic field intensity, direction, and gradient are all adjustable. By adjusting the current ratio of the three sets of coils, the spatial distribution of the magnetic field in the piston working area can be changed. It can generate a uniform magnetic field (when the three sets of currents are equal) or a gradient magnetic field (when the currents are unequal), thus realizing multi-level damping adjustment.

[0008] (2) This utility model divides the working area of ​​the magnetorheological fluid inside the cylinder into three chambers by adding a floating baffle inside the cylinder. The sealed chamber II and the sealed chamber III are connected by a controllable one-way valve. The sealed chamber II is responsible for providing the basic damping force to ensure the stability of the system under normal operating conditions. The sealed chamber III dynamically adjusts the amount of fluid participating in the rheology by controlling the opening and closing state (fully open, half open, closed) of the controllable one-way valve, thereby realizing the step-like or continuous expansion of the damping force and widening the damping force adjustment range. Attached Figure Description

[0009] Figure 1 This is a schematic diagram of the structure of this utility model.

[0010] Figure 2 This is a cross-sectional view of the arrangement of the excitation coil inside the piston head of this utility model.

[0011] Figure 3 This is a schematic diagram of the floating partition structure of this utility model. Detailed Implementation

[0012] The present invention will be further described below with reference to the accompanying drawings and embodiments:

[0013] like Figure 1As shown, this utility model includes: piston rod 1, sealing ring I 2, damper left end cover 3, screw I 4, screw II 5, sealing ring II 6, excitation coil 7, screw III 8, piston head right end cover 9, nut 10, floating partition 11, floating piston 12, sealing ring III 13, right lifting lug 14, damper right end cover 15, screw IV 16, sealing ring IV 17, damper cylinder 18, magnetorheological fluid channel 19, sealing ring V 20, one-way valve 21, piston head 22, piston head left end cover 23, sealing ring VI 24, and left lifting lug 25.

[0014] The left end of piston rod 1 is fastened to the left lifting lug 25 by threads. A circular through hole is machined in the middle of the left end cover 3 of the damper. The piston rod 1 is clearance-fitted with the inner surface of the circular through hole of the left end cover 3 of the damper. The piston rod 1 is sealed with the inner surface of the circular through hole of the left end cover 3 of the damper by sealing ring I2. The left end cover 3 of the damper is clearance-fitted with the left end face of the damper cylinder 18. The left end cover 3 of the damper is tightly connected to the damper cylinder 18 by screw I4. The left end cover 3 of the damper is sealed with the damper cylinder 18 by sealing ring VI24. The piston rod 1 has an external thread on its right end, and the piston head left end cap 23 has a circular through hole in its center. The circular through hole in the piston head left end cap 23 has an internal thread. The right end of the piston rod 1 is interference-fitted with the threaded hole in the piston head left end cap 23. The piston head left end cap 23 is tightly connected to the piston head 22 by screw II5. The piston rod 1 is threadedly fastened to the piston head 22 through the threaded hole. The piston head 22 is sealed to the damper cylinder 18 by sealing ring II6. The piston head right end cap 9 is connected to the piston head by screw III8. Piston head 22 is tightly connected to piston head 12. The right end of piston head 22 is machined with external threads. Piston head 22 is fastened to right end cap 9 of piston head by nut 10. Floating baffle 11 and the outer surface of floating piston 12 are clearance-fitted with the inner surface of damper cylinder 18. Floating baffle 11 and damper cylinder 18 are sealed by sealing ring V20. Floating piston 12 and damper cylinder 18 are sealed by sealing ring IV17. Right end cap 15 of damper cylinder 18 is clearance-fitted with the right end face of damper cylinder 18. Right end cap 15 of damper cylinder 18 is secured by screws. IV16 is tightly connected to the damper cylinder 18. The right end cover 15 of the damper is sealed to the damper cylinder 18 through the sealing ring III13. The right end cover 15 of the damper has an external thread, and the right lifting lug 14 has an internal thread. The right end cover 15 of the damper is fastened to the right lifting lug 14 through the external thread. Three sets of radially distributed excitation coils 7 are machined inside the piston head 22. The two leads of the excitation coils 7 pass through the lead holes in the piston head 22 and the left end cover 23 of the piston head, and are led out through the lead holes in the piston rod 1.

[0015] The left end cover 3 of the damper, the left end cover 23 of the piston head, and the damper cylinder 18 form a sealed chamber I. The right end cover 15 of the piston head, the damper cylinder 18, and the floating partition 11 form a sealed chamber II. The floating partition 11, the damper cylinder 18, and the floating piston 12 form a sealed chamber III. The floating piston 12, the damper cylinder 18, and the right end cover 15 of the damper form a sealed chamber IV. The sealed chambers I, II, and III are filled with magnetorheological fluid, and the sealed chamber IV is filled with compressed gas. When piston rod 1 is stretched in the axial direction, the magnetorheological fluid in sealed chamber I enters sealed chamber II through the fluid flow channel. When piston rod 1 is compressed in the axial direction, the magnetorheological fluid in sealed chamber II enters sealed chamber I through the magnetorheological fluid channel. When piston rod 1 moves in the axial direction, the volumes of sealed chamber I and sealed chamber II will change accordingly. At this time, floating partition 11 and floating piston 12 will achieve volume compensation by floating left and right in the axial direction.

[0016] Figure 2 This is a cross-sectional view of the excitation coil arrangement inside the piston head of this utility model. Three sets of radially distributed excitation coils 7 are machined inside the piston head 23. By independently controlling the current intensity of each set of coils, a dynamically variable composite magnetic field is formed using the principle of magnetic field superposition. The magnetic field strength, direction, and gradient are all adjustable. When a single set of coils works, a magnetic field of a certain intensity is generated; when two or three sets of coils work simultaneously, the magnetic field strength is enhanced through superposition. Simultaneously, by adjusting the current ratio of the three sets of coils, the spatial distribution of the magnetic field in the piston's working area can be changed, generating either a uniform magnetic field (when the three sets of currents are equal) or a gradient magnetic field (when the currents are unequal), achieving multi-level damping adjustment.

[0017] Figure 3 This is a schematic diagram of the floating baffle structure of this utility model. A floating baffle 11 is added inside the cylinder, dividing the working area of ​​the magnetorheological fluid inside the cylinder into three chambers. Sealed chamber II and sealed chamber III are connected by a controllable one-way valve 21. Sealed chamber II is responsible for providing the basic damping force, ensuring the stability of the system under normal operating conditions. The amount of fluid participating in the rheological process in sealed chamber III is dynamically adjusted by the on / off state (fully open, partially open, closed) of the controllable one-way valve 21. When a smaller damping force is required, the controllable one-way valve 21 is closed, and only the magnetorheological fluid in sealed chamber II participates in the work, providing basic damping. When a larger damping force is required, the controllable one-way valve 21 is opened, and the magnetorheological fluid in sealed chamber III enters sealed chamber II, participating in the rheological process together with the magnetorheological fluid in sealed chamber II, thereby increasing the damping force. Through this dynamic flow distribution, a stepped or continuous expansion of the damping force is achieved, widening the damping force adjustment range.

[0018] The above description is merely a preferred embodiment of the present utility model and is not intended to limit the present utility model in any way. Although the present utility model has been disclosed above with reference to a preferred embodiment, it is not intended to limit the present utility model. Any person skilled in the art can make some modifications or alterations to the above-disclosed technical content to create equivalent embodiments without departing from the scope of the present utility model. Any simple modifications, equivalent changes and alterations made to the above embodiments based on the technical essence of the present utility model without departing from the scope of the present utility model shall still fall within the scope of the present utility model.

Claims

1. A radial multi-coil magnetorheological damper, characterized in that include: Piston rod (1), sealing ring I (2), damper left end cap (3), screw I (4), screw II (5), sealing ring II (6), excitation coil (7), screw III (8), piston head right end cap (9), nut (10), floating partition (11), floating piston (12), sealing ring III (13), right lifting lug (14), damper right end cap (15), screw IV (16), sealing ring IV (17), damper cylinder (18), magnetorheological fluid channel (19), sealing ring V (20), one-way valve (21), piston head (22), piston head left end cap (23), sealing ring VI (24), left lifting lug (25), the left end of piston rod (1) and the left lifting lug (25) are fastened together by threads. A circular through hole is machined in the middle of the left end cap (3) of the damper. The piston rod (1) is clearance-fitted with the inner surface of the circular through hole of the left end cap (3) of the damper. The piston rod (1) is sealed with the inner surface of the circular through hole of the left end cap (3) of the damper through sealing ring I (2). The left end cap (3) of the damper is clearance-fitted with the left end face of the damper cylinder (18). The left end cap (3) of the damper is tightly connected to the damper cylinder (18) through screw I (4). The left end cap (3) of the damper is sealed with the damper cylinder (18) through sealing ring VI (24). The right end of the piston rod (1) is machined with external threads. A circular through hole is machined in the center of the left end cap (23) of the piston head. The circular through hole machined in the left end cap (23) of the piston head is machined with internal threads. The piston rod (1) The right end of the piston head is interference-fitted with the threaded hole of the left end cap (23) of the piston head. The left end cap (23) of the piston head and the piston head (22) are tightly connected by screw II (5). The piston rod (1) is threadedly fastened to the piston head (22) through the threaded hole. The piston head (22) is sealed to the damper cylinder (18) through sealing ring II (6). The right end cap (9) of the piston head is tightly connected to the piston head (22) through screw III (8). The right end of the piston head (22) is machined with external threads. The piston head (22) is fastened to the right end cap (9) of the piston head through nut (10). The outer surface of the floating partition (11) and the floating piston (12) is clearance-fitted with the inner surface of the damper cylinder (18). The floating partition (11) and the damper cylinder (18) are clearance-fitted. The damper cylinder (18) is sealed by sealing ring V (20), the floating piston (12) is sealed with the damper cylinder (18) by sealing ring IV (17), the damper right end cover (15) is clearance-fitted with the right end face of the damper cylinder (18), the damper right end cover (15) is tightly connected to the damper cylinder (18) by screw IV (16), the damper right end cover (15) is sealed with the damper cylinder (18) by sealing ring III (13), the right end of the damper right end cover (15) is machined with external thread, the right lifting lug (14) is machined with internal thread, the damper right end cover (15) is fastened to the right lifting lug (14) by the machined external thread, and the piston head (22) has 3 sets of radially distributed excitation coils (7) machined inside.The two leads of the excitation coil (7) pass through the lead holes in the piston head (22) and the left end cap (23) of the piston head, and are led out through the lead hole in the piston rod (1).

2. A radial multi-coil magneto-rheological damper according to claim 1, wherein: Three sets of radially distributed excitation coils (7) are machined inside the piston head. The current intensity of each set of coils can be controlled independently. A dynamic and variable composite magnetic field is formed by using the principle of magnetic field superposition. The magnetic field intensity, direction and gradient can be adjusted. At the same time, by adjusting the current ratio of the three sets of coils, a uniform magnetic field is generated when the three sets of currents are equal and a gradient magnetic field is generated when the three sets of currents are unequal, so as to realize multi-level damping adjustment.

3. The radial multi-coil magneto-rheological damper according to claim 1, wherein: Two control modes are formed by controlling the closing state of the one-way valve (21) on the floating baffle (11). In mode 1, the one-way valve is closed, and only the magnetorheological fluid in the sealed chamber II participates in the work to provide basic damping force. In mode 2, the one-way valve is open, and the magnetorheological fluid in the sealed chamber III and the sealed chamber II participate in the rheological action together, increasing the amount of liquid participating in the work, thereby increasing the damping force. When the opening and closing state of the one-way valve is controllable, a dynamic flow distribution mode is formed to realize the step-like or continuous expansion of the damping force and broaden the damping force adjustment range.

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