Double-cylinder magnetorheological damper

Abstract

The utility model relates to a double-cylinder magneto-rheological shock absorber which comprises a base. The inner cylinder barrel is sleeved on the step of the base; the outer cylinder barrel is arranged on the periphery of the inner cylinder barrel in a sleeving manner; the bottom end of the outer cylinder barrel is fixed on the base and is communicated with the inner cylinder barrel through the through hole; the guide sealing seat is mounted at the top of the outer cylinder barrel, and a step of the guide sealing seat is inserted into the inner cylinder barrel; a cavity formed among the inner cylinder barrel, the guide sealing seat and the floating piston is an inner cavity; the piston rod is axially and movably mounted in a middle hole of the guide sealing seat; the damping piston is installed at the end of the piston rod and located in the inner cylinder barrel. And the floating piston is located in the inner cylinder barrel and located between the damping piston and the base. The heat dissipation performance and the stability of the shock absorber are improved, so that the shock absorber can keep a good shock absorption effect under different working conditions.

Description

Technical Field

[0001] This utility model relates to the field of vibration damper technology, and specifically to a dual-cylinder magnetorheological vibration damper. Background Technology

[0002] Magnetorheological dampers are intelligent dampers with rapidly adjustable damping, made by utilizing the rheological effect of magnetorheological fluid when it encounters a magnetic field. They have excellent application prospects in vibration control and motion control in active fields such as vehicles, civil engineering, medical devices, and robots.

[0003] Existing magnetorheological dampers, exemplified by patent US6874603B2, are monotube structures, which have numerous problems:

[0004] Because the cylinder barrel is prone to deformation due to thermal stress during welding, single-cylinder magnetorheological dampers usually cannot weld accessories such as spring trays, brackets, and fasteners onto the cylinder barrel outer wall. Spring trays are usually fixed axially using snap rings, but cannot be fixed circumferentially, making them unsuitable for some applications with circumferential torsional forces.

[0005] When subjected to lateral forces or external impacts, the cylinder of a single-tube magnetorheological damper is prone to deformation, which can cause piston movement to become stuck or even completely damage the damper and render it inoperable.

[0006] The air chambers of single-tube magnetorheological dampers occupy a certain axial space. In some cases where the axial dimensions are constrained but the damper is required to have a large stroke, it is difficult to meet the design requirements of magnetorheological dampers.

[0007] In view of this, a dual-cylinder magnetorheological vibration damper is provided to solve the above-mentioned technical problems of the single-cylinder magnetorheological vibration damper. Utility Model Content

[0008] This utility model addresses the technical problems existing in the prior art by providing a dual-cylinder magnetorheological vibration damper.

[0009] The technical solution of this utility model to solve the above-mentioned technical problems is as follows:

[0010] A twin-tube magnetorheological vibration damper includes:

[0011] A base, wherein several through holes are provided on the base;

[0012] Inner cylinder, which is fitted onto the step of the base;

[0013] An outer cylinder is sleeved around the outer periphery of the inner cylinder, and the cavity formed between the inner wall of the outer cylinder and the outer wall of the inner cylinder is the outer cavity; the bottom end of the outer cylinder is fixed to the base and communicates with the inner cylinder through the through hole.

[0014] A guide seal seat is installed on the top of the outer cylinder, and the step of the guide seal seat is inserted into the inner cylinder.

[0015] A piston rod, which is axially movably mounted in the central hole of the guide seal seat;

[0016] A damping piston, which is mounted at the end of the piston rod and located in the inner cylinder;

[0017] A floating piston is located in the inner cylinder and between the damping piston and the base; the cavity formed between the inner cylinder, the guide seal, and the floating piston is the inner chamber.

[0018] The inner chamber between the floating piston and the guide seal is filled with magnetorheological fluid, the inner chamber between the floating piston and the base and a part of the outer chamber are filled with heat-conducting oil, and the other part of the outer chamber is filled with high-pressure inert gas.

[0019] In some embodiments, the damping piston is provided with a plurality of coils, and the wires of the coils are led out through the central hole of the piston rod.

[0020] In some embodiments, a plurality of sealing rings are provided in the central hole of the guide sealing seat.

[0021] In some embodiments, sealing elements are provided between the guide sealing seat and the outer cylinder, and between the guide sealing seat step and the inner cylinder;

[0022] In some embodiments, the seal is an O-ring.

[0023] In some embodiments, the heat-conducting oil is damper oil or silicone oil.

[0024] In some embodiments, the high-pressure inert gas is nitrogen.

[0025] Compared with the existing single-tube magnetorheological vibration damper solution, the double-tube magnetorheological vibration damper provided by this utility model has the following advantages:

[0026] 1. The inner cylinder of the double-cylinder magnetorheological damper provided by this utility model is used for piston sliding guidance and damping generation of magnetorheological fluid. The inner cylinder has high processing requirements such as roundness and straightness, while the outer cylinder is only used for sealing heat transfer oil and gas. The processing requirements are lower. Spring plates, brackets, fixing seats, etc. can be welded on the outer wall of the outer cylinder, which solves the problem that the single-cylinder magnetorheological damper cannot weld accessories on the cylinder.

[0027] 2. The twin-cylinder structure gives the shock absorber better resistance to deformation. When the shock absorber is subjected to large lateral forces or external impacts, the inner cylinder is protected by the outer cylinder and is not easily deformed, thus preventing piston jamming and improving the reliability and service life of the shock absorber.

[0028] 3. The twin-tube magnetorheological damper has a larger working stroke; the single-tube magnetorheological damper has its air chamber and damping working chamber set in one cylinder, and the air chamber needs to occupy a certain axial length. When the axial dimension of the damper is limited, but a certain working stroke is required, it is often difficult to meet the design requirements; in the solution provided in this application, the floating piston can be compressed to the bottom of the cylinder. Therefore, under the same axial length conditions, the twin-tube magnetorheological damper can be designed to have a larger stroke.

[0029] 4. The gas rebound force of the twin-cylinder magnetorheological damper is more stable. In the single-cylinder magnetorheological damper design, when the gas chamber volume is too small, the piston rod entering and exiting the main cylinder causes a relatively large rate of change in the gas chamber volume, resulting in a large variation in the gas rebound force of the damper. However, this design places the gas chamber between the inner and outer cylinders, resulting in a larger gas chamber volume. The rate of change in the gas chamber volume caused by the piston rod movement is relatively small, thus the variation in the gas rebound force of the damper is smaller. Attached Figure Description

[0030] Figure 1 This is a schematic diagram of the structure of the double-cylinder magnetorheological vibration damper provided by this utility model.

[0031] The attached diagram lists the components represented by each number as follows:

[0032] 1. Base; 2. Inner cylinder; 3. Outer cylinder; 4. Guide seal seat; 5. Piston rod; 6. Damping piston; 7. Floating piston; 8. Magnetorheological fluid; 9. Heat transfer oil; 10. High-pressure inert gas; 11. Coil; 12. Wire; 13. Through hole; 14. Spring plate; 15. Bracket. Detailed Implementation

[0033] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0034] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the stated features. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0035] In the description of this application, the term "for example" is used to mean "used as an example, illustration, or description." Any embodiment described as "for example" in this application is not necessarily to be construed as being more preferred or advantageous than other embodiments. The following description is provided to enable any person skilled in the art to implement and use the present invention. Details are set forth in the following description for purposes of explanation. It should be understood that those skilled in the art will recognize that the present invention can be implemented without using these specific details. In other instances, well-known structures and processes will not be described in detail to avoid obscuring the description of the present invention with unnecessary detail. Therefore, the present invention is not intended to be limited to the embodiments shown, but is consistent with the broadest scope of the principles and features disclosed in this application.

[0036] Reference Figure 1The dual-cylinder magnetorheological vibration damper provided by this utility model includes a base 1, an inner cylinder 2, an outer cylinder 3, a guide sealing seat 4, a piston rod 5, a damping piston 6, and a floating piston 7. The base 1 has several through holes 13. The inner cylinder 2 is fitted onto the step of the base 1. The outer cylinder 3 is fitted around the outer periphery of the inner cylinder 2. The cavity formed between the inner wall of the outer cylinder 3 and the outer wall of the inner cylinder 2 is the outer cavity. The bottom end of the outer cylinder 3 is fixed to the base 1 and communicates with the inner cylinder 2 through the through holes 13. The guide sealing seat 4 is installed on the top of the outer cylinder 3, and the step of the guide sealing seat 4 is inserted into the inner cylinder. 2; The cavity formed between the inner cylinder 2, the guide seal seat 4, and the base 1 is the inner cavity. The piston rod 5 is axially movably installed in the middle hole of the guide seal seat 4. The damping piston 6 is installed at the end of the piston rod 5 and is located in the inner cylinder 2. The floating piston 7 is located in the inner cylinder 2 and is located between the damping piston 6 and the base 1. The inner cavity between the floating piston 7 and the guide seal seat 4 is filled with magnetorheological fluid 8. The inner cavity between the floating piston 7 and the base 1 and a part of the space of the outer cavity are filled with heat-conducting oil 9. The other part of the space of the outer cavity is filled with high-pressure inert gas 10.

[0037] In this way, by setting magnetorheological fluid 8 and heat-conducting oil 9 in the inner chamber and filling the outer chamber with high-pressure inert gas 10, the damping force of the vibration damper can be effectively adjusted, while improving the heat dissipation performance and stability of the vibration damper, so that it can maintain a good vibration damping effect under different working conditions.

[0038] In some embodiments, the damping piston 6 is provided with a plurality of coils 11, and the wires 12 of the coils 11 are led out through the central hole of the piston rod 5. Thus, by providing coils 11 on the damping piston 6, magnetic field control of the magnetorheological fluid 8 can be achieved, thereby precisely adjusting the damping force of the shock absorber and improving the adaptability and control accuracy of the shock absorber. It is understood that the coils 11 can adopt other structures capable of generating magnetic fields, such as electromagnets or permanent magnets; the lead-out method of the coils 11 can be replaced with other reliable electrical connection methods, such as through external wires 12 or wireless transmission modules.

[0039] The guide sealing seat 4 has several sealing rings installed in its central hole. This effectively prevents leakage of the magnetorheological fluid 8, improving the sealing performance and reliability of the vibration damper. The sealing rings can be replaced with other sealing structures, such as gaskets or sealant. The number and arrangement of the sealing rings can be adjusted according to actual needs to meet different sealing requirements.

[0040] Sealing elements are provided between the guide sealing seat 4 and the outer cylinder 3, and between the step of the guide sealing seat 4 and the inner cylinder 2. By providing sealing elements between the guide sealing seat 4 and the outer cylinder 3, and between the step of the guide sealing seat 4 and the inner cylinder 2, the sealing performance of the shock absorber is ensured, liquid and gas leakage is prevented, and the normal operation of the shock absorber is ensured.

[0041] Furthermore, the heat-conducting oil 9 is preferably, but not limited to, damper oil or silicone oil. Damper oil and silicone oil have good thermal conductivity and stability, and can effectively absorb and conduct the heat generated during the operation of the damper, prevent the damper from overheating, and extend its service life.

[0042] Specifically, the high-pressure inert gas 10 is preferably, but not limited to, nitrogen. Nitrogen has stable chemical properties and good compressibility, which can provide stable gas pressure for the shock absorber, ensure the normal operation of the shock absorber, and at the same time avoid chemical reactions between the gas and the liquid, thereby improving the safety and reliability of the shock absorber.

[0043] To facilitate understanding, the overall technical solution of this utility model is briefly described below through a specific embodiment.

[0044] The dual-cylinder magnetorheological vibration damper provided by this utility model includes an inner cylinder 2 and an outer cylinder 3. A base 1 is welded to the bottom of the outer cylinder 3, and the inner cylinder 2 is fitted onto the step of the base 1. The base 1 has several through holes 13 that connect the bottoms of the inner and outer cylinders. A guide sealing seat 4 is fitted onto the upper part of the outer cylinder 3. The step of the guide sealing seat 4 is inserted into the inner cylinder 2 to ensure the coaxiality of the inner and outer cylinders 3. The upper end of the outer cylinder 3 is rolled to press against the guide sealing seat 4, or other methods of fixing the guide can be used (such as snap rings, rolled ring grooves, multi-point riveting, etc., which are not specifically limited in this embodiment). Sealing elements are provided between the guide sealing seat 4 and the outer cylinder 3, and between the step of the guide sealing seat 4 and the inner cylinder 2. O-rings are recommended. The piston rod 5 passes through the middle hole of the guide sealing seat 4. The end of the piston rod 5 inside the inner cylinder 2 has a damping piston 6, which is usually provided with several coils 11. The coils 11 on the piston are led out through the center hole of the piston rod 5. The guide sealing seat 4 has several sealing rings in the middle hole to achieve dynamic sealing of the piston rod 5.

[0045] The chamber formed between the inner cylinder and the outer cylinder 3 is the outer chamber, and the chamber formed between the inner cylinder 2, the guide seal seat 4, and the base 1 is the inner chamber. A floating piston 7 is installed between the damping piston 6 and the base 1. The inner chamber between the floating piston 7 and the guide seal seat 4 is filled with magnetorheological fluid 8 and is the damping working chamber; the inner chamber between the floating piston 7 and the base 1, as well as part of the outer chamber, is filled with oil with good thermal conductivity (such as damper oil, silicone oil, etc.). The floating piston 7 is equipped with a sealing ring to isolate the magnetorheological fluid 8 from the heat-conducting oil. A certain space needs to be left in the outer chamber to be filled with high-pressure inert gas 10 (commonly nitrogen) to act as a gas spring to compensate for the volume change caused by the piston rod 5 moving in and out.

[0046] When the piston rod 5 pushes the piston to slide within the inner cylinder 2 under the action of an external force, a current is applied to the coil 11 on the piston through a guide. The coil 11 generates a magnetic field, which induces a change in the viscosity of the magnetorheological fluid 8 flowing through the piston, thereby controlling the damping force of the piston rod 5. The heat generated by the piston damping force is transferred to the outer cylinder through the heat transfer oil in the outer chamber and dissipated.

[0047] The outer wall of the outer cylinder can be welded with spring disc 14, bracket 15, fasteners, etc. as needed; this embodiment does not impose specific limitations.

[0048] Compared with the existing single-tube magnetorheological vibration damper solution, the double-tube magnetorheological vibration damper provided by this utility model has the following advantages:

[0049] 1. The inner cylinder 2 of the double-cylinder magnetorheological damper provided by this utility model is used for piston sliding guidance and damping generation of magnetorheological fluid 8. The inner cylinder has high requirements for roundness, straightness and other processing, while the outer cylinder 3 is only used for sealing heat transfer oil and gas. The processing shape and position requirements are low. Spring plates, brackets, fixed seats and other components can be welded on the outer wall of the outer cylinder 3, which solves the problem that the single-cylinder magnetorheological damper cannot weld accessories on the cylinder.

[0050] 2. The twin-cylinder structure gives the shock absorber better resistance to deformation. When the shock absorber is subjected to large lateral forces or external impacts, the inner cylinder 2 is protected by the outer cylinder 3 and is not easily deformed, so as to avoid piston jamming and improve the reliability and service life of the shock absorber.

[0051] 3. The twin-tube magnetorheological damper has a larger working stroke; the single-tube magnetorheological damper has its air chamber and damping working chamber set in one cylinder, and the air chamber needs to occupy a certain axial length. When the axial dimension of the damper is limited, but a certain working stroke is required, it is often difficult to meet the design requirements; in the solution provided in this application, the floating piston 7 can be compressed to the bottom of the cylinder. Therefore, under the same axial length conditions, the twin-tube magnetorheological damper can be designed to have a larger stroke.

[0052] 4. The gas rebound force of the twin-cylinder magnetorheological damper is more stable. In the single-cylinder magnetorheological damper design, when the gas chamber volume is too small, the piston rod 5 entering and exiting the main cylinder will cause a relatively large rate of change in the gas chamber volume, resulting in a large change in the gas rebound force of the damper. However, in this design, the gas chamber is located between the inner and outer cylinders, resulting in a larger gas chamber volume. The rate of change in the gas chamber volume caused by the movement of the piston rod 5 is relatively small, thus the change in the gas rebound force of the damper is smaller.

[0053] Although preferred embodiments of the present invention have been described, those skilled in the art, upon learning the basic inventive concept, can make other changes and modifications to these embodiments. Therefore, the appended claims are intended to be interpreted as including the preferred embodiments as well as all changes and modifications falling within the scope of the present invention.

[0054] Obviously, those skilled in the art can make various modifications and variations to this utility model without departing from its spirit and scope. Therefore, if these modifications and variations fall within the scope of the claims of this utility model and their equivalents, this utility model also intends to include these modifications and variations.

Claims

1. A twin-cylinder magnetorheological vibration damper, characterized in that, include: A base, wherein several through holes are provided on the base; Inner cylinder, which is fitted onto the step of the base; An outer cylinder is sleeved around the outer periphery of the inner cylinder, and the cavity formed between the inner wall of the outer cylinder and the outer wall of the inner cylinder is the outer cavity; the bottom end of the outer cylinder is fixed to the base and communicates with the inner cylinder through the through hole. A guide seal seat is installed on the top of the outer cylinder, and the step of the guide seal seat is inserted into the inner cylinder. A piston rod, which is axially movably mounted in the central hole of the guide seal seat; A damping piston, which is mounted at the end of the piston rod and located in the inner cylinder; A floating piston is located in the inner cylinder and between the damping piston and the base; the cavity formed between the inner cylinder, the guide seal, and the floating piston is the inner chamber. The inner chamber between the floating piston and the guide seal is filled with magnetorheological fluid, the inner chamber between the floating piston and the base and a part of the outer chamber are filled with heat-conducting oil, and the other part of the outer chamber is filled with high-pressure inert gas.

2. The twin-cylinder magnetorheological vibration damper according to claim 1, characterized in that, The damping piston is provided with several coils, and the wires of the coils are led out through the central hole of the piston rod.

3. The twin-cylinder magnetorheological vibration damper according to claim 1, characterized in that, Several sealing rings are provided in the middle hole of the guide sealing seat.

4. The twin-cylinder magnetorheological vibration damper according to claim 1, characterized in that, Sealing elements are provided between the guide sealing seat and the outer cylinder, and between the guide sealing seat step and the inner cylinder.

5. The twin-cylinder magnetorheological vibration damper according to claim 4, characterized in that, The sealing element is an O-ring.

6. The twin-cylinder magnetorheological vibration damper according to claim 1, characterized in that, The heat-conducting oil is either vibration damper oil or silicone oil.

7. The twin-cylinder magnetorheological vibration damper according to claim 1, characterized in that, The high-pressure inert gas is nitrogen.

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