Inverted magneto-rheological damper with nonlinear stiffness characteristic and adjustable inflation height and automobile suspension

Abstract

The utility model provides an inverted magneto-rheological damper with a nonlinear stiffness characteristic and an adjustable inflation height and an automobile suspension. The inverted magneto-rheological damper comprises an upper connecting spring tray, a lower connecting spring tray and an upper connecting spring tray, the upper end of the inner cylinder is connected with the upper connecting spring tray; the piston rod guider is mounted at the lower end of the inner cylinder, and a through hole is formed in the piston rod guider; the floating piston is arranged in the inner cylinder in a sliding mode and divides the inner space of the inner cylinder into a damper energy storage gas cavity and a magnetorheological fluid cavity; the outer cylinder sleeves the outer side wall of the inner cylinder in a sliding and sealing manner, an outer cylinder bottom cover is arranged at the bottom of the outer cylinder, and the outer cylinder and the piston rod guider jointly define an inner and outer cylinder high-pressure air cavity; the lower end of the piston rod is connected with the outer cylinder bottom cover, and the upper end of the piston rod penetrates through the piston rod guider in a sliding and sealing manner and extends into the magnetorheological fluid cavity; the piston ball valve is arranged at the upper end of the piston rod, and the piston ball valve is a one-way piston ball valve; and the lower connecting spring tray is arranged on the outer cylinder.

Description

Technical Field

[0001] The utility model relates to the technical fields of vehicle suspension research, engineering applications, and magnetorheological technology. In particular, it relates to a magnetorheological shock absorber that integrates a non-linear stiffness component, an inflatable height adjustment function, a characteristic of larger damping force in compression and smaller damping force in extension, an inverted anti-roll function, and a compact structure, which is an innovative application of magnetorheological shock absorbers in terms of mechanism. Background Art

[0002] With the continuous progress of modern industrial technology, the requirements for vibration damping technology are also constantly increasing. In the fields of automotive suspension research and engineering applications, there is a great demand for shock absorbers that can meet the requirements of vehicle ride comfort, handling stability, and road passing performance. Moreover, shock absorber devices with high efficiency, intelligent controllability, and compact structure are crucial for improving the safety, stability, and comfort of the structure. Traditional magnetorheological shock absorbers mostly adopt a single controllable electromagnetic rheological characteristic. However, in actual applications, vehicle suspensions often need to face complex road conditions, and traditional magnetorheological shock absorbers seem inadequate when dealing with these complex scenarios.

[0003] As an intelligent material shock absorber, magnetorheological shock absorbers have gradually become a research hotspot due to their advantages such as fast response speed, adjustable damping force, and simple structure. The core material of a magnetorheological shock absorber is magnetorheological fluid, which is an intelligent material whose viscosity changes reversibly under the action of a magnetic field. By controlling the magnetic field intensity, the viscosity of the magnetorheological fluid can be adjusted in real time, thereby changing the damping characteristics of the shock absorber and achieving effective control of vibration.

[0004] Although existing magnetorheological shock absorbers perform well in various applications, their structures are often single and cannot fully adapt to complex vibration environments. In addition, most existing shock absorbers are of a positive-mounted design, and in some special application scenarios, a shock absorber form with more flexible spatial layout is required. The present utility model proposes an inverted magnetorheological shock absorber with anti-roll and compact structure. When a vehicle is actually running, the road surface scenarios it faces are complex. For example, when passing through road conditions such as speed bumps, since the compression speed is greater than the stretching speed, in order to maintain good ride comfort of the vehicle suspension. Summary of the Utility Model

[0005] In view of this, the present utility model provides an inverted magnetorheological damper with linear stiffness characteristics and adjustable inflation height, as well as an automotive suspension, which can simultaneously meet the requirements of vehicle suspension for ride comfort, handling stability, and road passing performance.

[0006] According to the inventive concept of one aspect of the present utility model, there is provided an inverted magnetorheological damper with non-linear stiffness characteristics and adjustable inflation height, comprising:

[0007] An upper connecting spring tray, adapted to be connected to a vehicle suspension;

[0008] The inner cylinder is connected to the upper connecting spring tray at its upper end;

[0009] The piston rod guide is installed at the lower end of the inner cylinder, and a through hole is provided on the piston rod guide;

[0010] The floating piston assembly is slidably disposed in the inner cylinder, and the floating piston assembly divides the space inside the inner cylinder into a damper energy storage gas chamber located above and a magnetorheological fluid chamber located below;

[0011] The outer cylinder is slidably and sealingly sleeved on the outer side wall of the inner cylinder, and an outer cylinder bottom cover is provided at the bottom of the outer cylinder. The outer cylinder and the piston rod guide jointly define an inner and outer cylinder high-pressure gas chamber;

[0012] The piston rod is connected to the outer cylinder bottom cover at its lower end, and its upper end slidably and sealingly passes through the piston rod guide and extends into the magnetorheological fluid chamber;

[0013] The piston ball valve is disposed at the upper end of the piston rod. The piston ball valve is a one-way piston ball valve, and the piston ball valve is configured to output a large damping force during tension and a small damping force during compression; and

[0014] The lower connecting spring tray is installed on the outer cylinder, and the lower connecting spring tray is configured to support the vehicle load.

[0015] According to some embodiments of the present invention, the inverted magnetorheological damper further includes:

[0016] An electromagnetic coil is sleeved on the piston ball valve; and

[0017] The shock absorber power line harness is disposed inside the piston rod. The shock absorber power line harness is electrically connected to the electromagnetic coil to generate an adjustable variable magnetic field, thereby changing the damping force of the shock absorber.

[0018] According to some embodiments of the present invention, the inverted magnetorheological damper further includes:

[0019] The shock absorber coil spring is sleeved on the outer sides of the outer cylinder and the inner cylinder, and two ends of the shock absorber coil spring are respectively connected to the upper connecting spring tray and the lower connecting spring tray.

[0020] According to some embodiments of the present invention, the inverted magnetorheological damper further includes:

[0021] The inner magnet assembly is installed on the piston rod guide; and

[0022] The outer magnet assembly is fixedly installed on the inner side wall of the outer cylinder;

[0023] Wherein, in response to the movement of the vehicle suspension, the inner magnet assembly and the inner cylinder simultaneously perform axial reciprocating movements relative to the outer cylinder and the outer magnet assembly, and the inner magnet assembly and the outer magnet assembly exhibit the effect of non-linear negative stiffness force under the action of the axially magnetized magnetic field.

[0024] According to some embodiments of the present invention, the inverted magnetorheological damper further includes:

[0025] An energy storage chamber air nozzle, which is arranged on the inner cylinder, and the energy storage chamber air nozzle is suitable for filling gas into the damper energy storage gas chamber.

[0026] According to some embodiments of the present invention, the inverted magnetorheological damper further includes:

[0027] An inner and outer cylinder air chamber air nozzle, which is arranged on the outer cylinder, and the inner and outer cylinder air chamber air nozzle is suitable for filling gas into the inner and outer cylinder high-pressure air chamber.

[0028] According to some embodiments of the present invention, it further includes an inner cylinder guide. The inner cylinder guide is arranged inside the upper end of the outer cylinder. A static seal with the outer cylinder is achieved between the inner cylinder guide and the outer cylinder through an inner cylinder guide O-ring. Axial movement guiding and dynamic seal with the inner cylinder are achieved by the inner cylinder guide dust-proof oil seal, the inner cylinder guide bushing, and the inner cylinder guide skeleton oil seal.

[0029] According to some embodiments of the present invention, the floating piston assembly includes a piston bottom cover, a piston ball valve, a piston ball valve lower assembly, the electromagnetic coil, a piston guide belt, a piston ball valve upper assembly, a piston outer cylinder, a piston upper end cover, a piston rod O-ring, a piston upper cover locking nut, a piston rod stop ring, and a recovery buffer block.

[0030] According to the inventive concept of the first aspect of the present invention, there is also provided an automotive suspension, including the inverted magnetorheological damper as described above.

[0031] Compared with the prior art, the inverted magnetorheological damper and the automotive suspension provided by the present invention with linear stiffness characteristics and adjustable inflation height have the following characteristics:

[0032] (1) The inverted magnetorheological damper according to the embodiment of the present invention can generate non-linear negative stiffness force through the axial reciprocating movement of the inner and outer magnet groups, realizing the actuation effect similar to that of an active suspension under a certain control algorithm, thereby providing the vehicle with vibration damping performance similar to that of an active suspension.

[0033] (2)Add the air inflation adjustable height method to the shock absorber. Through the inflation valve, high-pressure air can be filled between the outer cylinder and the inner cylinder. When the vehicle load changes, the air pressure can be adjusted to keep the inner and outer magnet groups within a certain horizontal position range. This air inflation adjustable structure can also adjust the body height according to different road conditions. For example, in off-road scenarios, higher air pressure can be introduced between the inner and outer cylinders to raise the body and improve the vehicle's passability on unpaved roads.

[0034] (3)The one-way ball valve design in the inverted magnetorheological damper of the embodiment of the present utility model enables the magnetorheological damper to output a large damping force during stretching and a small damping force during compression, thereby improving the riding comfort. For example, when passing through road conditions such as speed bumps, due to the compression speed being greater than the stretching speed, this characteristic can improve the riding comfort of the vehicle suspension.

[0035] (4)The above-mentioned structure has the advantages of non-linear stiffness, adjustable air inflation at the equilibrium position, large damping force during compression and small damping force during stretching, inverted anti-roll, and compact structure, which can simultaneously meet the requirements of vehicle suspension for riding comfort, handling stability, and road passability. Description of the Drawings

[0036] Through the following description of the embodiments of the present utility model with reference to the drawings, the above and other objects, features, and advantages of the present utility model will become clearer. In the drawings:

[0037] Figure 1 is a sectional view of the inverted magnetorheological shock absorber of the present utility model.

[0038] Figure 2 is a three-dimensional view of the non-linear stiffness component of the present utility model.

[0039] Figure 3 is a two-dimensional principle schematic diagram of two air inflation height adjustable modes of the present utility model.

[0040] Figure 4 is a sectional view of the piston with the characteristic of large damping force during compression and small damping force during stretching of the present utility model.

[0041] In the above-mentioned drawings, the meanings of the reference numerals are specifically as follows:

[0042] 1 - connecting rod;

[0043] 2 - upper connecting nut;

[0044] 3 - air nozzle of the energy storage chamber;

[0045] 4 - upper connecting spring tray;

[0046] 5 - inner cylinder;

[0047] 6 - floating piston assembly;

[0048] 7 - Inner cylinder guide

[0049] 8 - Outer magnet upper support

[0050] 9 - Outer cylinder

[0051] 10 - Inner cylinder graphite guide bearing

[0052] 11 - Shock absorber coil spring

[0053] 12 - Lower connecting spring tray

[0054] 13 - Outer magnet lower support

[0055] 14 - Inner and outer cylinder communication hole

[0056] 15 - Outer magnet assembly

[0057] 16 - Outer magnet support

[0058] 17 - Inner magnet fixing part

[0059] 18 - Shock absorber power cord harness

[0060] 19 - Outer cylinder bottom cover

[0061] 20 - Lower connecting nut

[0062] 21 - Floating piston O - ring

[0063] 22 - Floating piston guide strip

[0064] 23 - Inner cylinder guide dust - proof oil seal

[0065] 24 - Inner cylinder guide O - ring

[0066] 25 - Inner cylinder guide bushing

[0067] 26 - Inner cylinder guide skeleton oil seal

[0068] 27 - Piston bottom cover

[0069] 28 - Piston ball valve

[0070] 29 - Piston ball valve lower assembly

[0071] 30 - Electromagnetic coil

[0072] 31 - Piston guide strip

[0073] 32 - Piston ball valve upper assembly

[0074] 33 - Piston outer cylinder

[0075] 34 - Piston upper end cover

[0076] 35 - Piston rod O-ring;

[0077] 36 - Locking nut for piston upper cover;

[0078] 37 - Stop ring for piston rod;

[0079] 38 - Recovery buffer block;

[0080] 39 - Piston rod guide;

[0081] 40 - Piston rod guide bearing;

[0082] 41 - Piston rod oil seal;

[0083] 42 - Inner magnet fixing connecting piece;

[0084] 43 - Air nozzle for air cavity between inner and outer cylinders;

[0085] 44 - Inner magnet piston rod guide bearing;

[0086] 45 - Inner magnet assembly;

[0087] 46 - Inner magnet support;

[0088] 47 - High-pressure air cavity between inner and outer cylinders;

[0089] 48 - Piston rod;

[0090] 49 - Bottom cover O-ring;

[0091] 50 - Magnetorheological fluid cavity;

[0092] 51 - Energy storage gas cavity of damper; Detailed implementation manners

[0093] To make the objectives, technical solutions and advantages of the present utility model clearer and more understandable, the following further elaborates on the present utility model in detail with reference to specific embodiments and the accompanying drawings.

[0094] The terms used herein are merely for describing specific embodiments and are not intended to limit the present utility model. The terms "including", "comprising", etc. used herein indicate the presence of the described features, steps, operations and / or components, but do not exclude the presence or addition of one or more other features, steps, operations or components.

[0095] All terms used herein, including technical and scientific terms, have the meanings commonly understood by those skilled in the art, unless otherwise defined. It should be noted that the terms used herein should be interpreted as having a meaning consistent with the context of this specification and should not be interpreted in an idealized or overly rigid manner.

[0096] In the case of using expressions such as "at least one of A, B, and C, etc.", generally, it should be interpreted according to the meaning that those skilled in the art usually understand this expression. For example, "a system having at least one of A, B, and C" should include, but not be limited to, a system having only A, only B, only C, having A and B, having A and C, having B and C, and / or having A, B, and C, etc. In the case of using expressions such as "at least one of A, B, or C, etc.", generally, it should be interpreted according to the meaning that those skilled in the art usually understand this expression. For example, "a system having at least one of A, B, or C" should include, but not be limited to, a system having only A, only B, only C, having A and B, having A and C, having B and C, and / or having A, B, and C, etc.

[0097] It should also be noted that the directional terms mentioned in the embodiments, such as "up", "down", "front", "rear", "left", "right", etc., are only references to the directions in the drawings and are not used to limit the protection scope of the present invention. Throughout the drawings, the same elements are represented by the same or similar reference numerals. When it may cause confusion in the understanding of the present invention, the conventional structures or configurations will be omitted.

[0098] The present invention provides an inverted magnetorheological damper with non-linear stiffness characteristics and adjustable inflation height. The damper integrates axially magnetized magnet groups on the piston rod guide and the outer cylinder as non-linear stiffness components, so that the outer magnet group reciprocates axially with respect to the inner cylinder of the outer cylinder, achieving a driving force effect similar to that of an active suspension under a certain control algorithm, thereby providing a damping performance similar to that of an active suspension for a vehicle.

[0099] The present invention designs a piston ball valve with the characteristic of larger damping force in extension and smaller damping force in compression to improve the ride comfort of the vehicle. The introduction of the characteristic of larger damping force in extension and smaller damping force in compression can effectively enhance the damping force of the damper in the extension state and reduce the damping force in the compression state, thereby improving the damping effect and ride comfort. At the same time, the function of adjustable inflation height not only improves the adjustment range and adaptability of the damper, but also enhances its damping performance under different working conditions. The inverted design provides more possibilities for its application scenarios with limited space and harsh installation conditions. In order to further improve the damping effect and application flexibility.

[0100] Figure 1 is a sectional view of the inverted magnetorheological damper of the present invention.

[0101] According to the inventive concept of one aspect of the present invention, there is provided an inverted magnetorheological damper with non-linear stiffness characteristics and adjustable inflation height, as Figure 1As shown in the figure, it includes: an upper connecting spring tray 4, an inner cylinder 5, a piston rod guide 39, a floating piston assembly 6, an outer cylinder 9, a piston rod 48, a piston ball valve 28, and a lower connecting spring tray 12. The upper connecting spring tray 4 is adapted to be connected to a vehicle suspension. The inner cylinder 5 is connected to the upper connecting spring tray 4 at its upper end. The piston rod guide 39 is installed at the lower end of the inner cylinder 5, and a through hole is provided on the piston rod guide 39. The floating piston assembly 6 is slidably disposed within the inner cylinder 5, and the floating piston assembly 6 divides the space within the inner cylinder 5 into a damper energy storage gas chamber 51 located above and a magnetorheological fluid chamber 50 located below. The outer cylinder 9 is slidably and sealingly sleeved on the outer side wall of the inner cylinder 5, and an outer cylinder bottom cover 19 is provided at the bottom of the outer cylinder 9. The outer cylinder 9 and the piston rod guide 39 jointly define an inner and outer cylinder high-pressure gas chamber 47. The piston rod 48 is connected to the outer cylinder bottom cover 19 at its lower end and extends into the magnetorheological fluid chamber 50 through the piston rod guide 39 in a slidable and sealed manner at its upper end. The piston ball valve 28 is provided at the upper end of the piston rod 48. The piston ball valve 28 is a one-way piston ball valve, and the piston ball valve 28 is configured to output a large damping force during stretching and a small damping force during compression. The lower connecting spring tray 12 is installed on the outer cylinder 9, and the lower connecting spring tray 12 is configured to support the vehicle load.

[0102] In this embodiment, by integrating an axially magnetized magnet group on the piston rod guide 39 and the outer cylinder 9 as a non-linear stiffness component, the outer magnet group reciprocates axially relative to the inner cylinder 5 along with the outer cylinder 9, realizing a driving force effect similar to that of an active suspension under a certain control algorithm, thereby providing the vehicle with a vibration damping performance similar to that of an active suspension.

[0103] According to some embodiments of the present invention, the one-way ball valve design in the embodiments of the present invention enables the magnetorheological damper to output a large damping force during stretching and a small damping force during compression, thereby improving the riding comfort. For example, when passing through road conditions such as speed bumps, due to the compression speed being greater than the stretching speed, this characteristic can improve the riding comfort of the vehicle suspension. The inverted structure not only meets the requirements of the compact installation space of the vehicle suspension, but also improves the anti-roll ability of the shock absorber and maintains the coaxiality when the inner and outer magnet groups reciprocate axially.

[0104] According to some embodiments of the present invention, the inverted magnetorheological damper further includes: an electromagnetic coil 30 and a shock absorber power cable harness 18. The electromagnetic coil 30 is sleeved on the piston ball valve. The shock absorber power cable harness 18 is disposed inside the piston rod, and the shock absorber power cable harness 18 is electrically connected to the electromagnetic coil 30 to generate an adjustable variable magnetic field, thereby changing the damping force of the shock absorber.

[0105] In this embodiment, the magnetorheological piston part utilizes the characteristics of the magnetorheological fluid undergoing phase change within milliseconds under a magnetic field and having continuously controllable damping, enabling the shock absorber to exhibit the characteristic of continuously adjustable damping force.

[0106] According to some embodiments of the present utility model, the inverted magnetorheological damper further includes a shock absorber coil spring 11, the shock absorber coil spring 11 is sleeved outside the outer cylinder 9 and the inner cylinder 5, and both ends of the shock absorber coil spring 11 are respectively connected to the upper connecting spring tray 4 and the lower connecting spring tray 12.

[0107] According to some embodiments of the present utility model, the inverted magnetorheological damper further includes: an inner magnet assembly 45 and an outer magnet assembly 15. The inner magnet assembly 45 is installed on the piston rod guide 39. The outer magnet assembly 15 is fixedly installed on the inner side wall of the outer cylinder 9. Wherein, in response to the movement of the vehicle suspension, the inner magnet assembly 45 and the inner cylinder 5 simultaneously perform axial reciprocating movements relative to the outer cylinder 9 and the outer magnet assembly 15, and the inner magnet assembly 45 and the outer magnet assembly 15 exhibit the effect of non-linear negative stiffness force under the action of the axially magnetized magnetic field.

[0108] According to some embodiments of the present utility model, the inverted magnetorheological damper further includes a storage cavity air nozzle 3, the storage cavity air nozzle 3 is arranged on the inner cylinder 5, and the storage cavity air nozzle 3 is adapted to fill gas into the damper storage gas cavity 51.

[0109] According to some embodiments of the present utility model, the inverted magnetorheological damper further includes an inner and outer cylinder air cavity air nozzle 43, the inner and outer cylinder air cavity air nozzle 43 is arranged on the outer cylinder 9, and the inner and outer cylinder air cavity air nozzle 43 is adapted to fill gas into the inner and outer cylinder high-pressure air cavity 47.

[0110] In this embodiment, high-pressure air can be filled between the outer cylinder 9 and the inner cylinder 5 through an air filling valve. When the vehicle load changes, the air pressure can be adjusted to keep the inner and outer magnet groups within a certain horizontal position range. This air filling adjustable structure can also adjust the vehicle body height according to different road conditions. For example, in an off-road scenario, higher air pressure can be introduced between the inner and outer cylinders to raise the vehicle body and improve the passability of the vehicle on unpaved roads.

[0111] According to some embodiments of the present utility model, it further includes an inner cylinder guide 7, the inner cylinder guide 7 is arranged inside the upper end of the outer cylinder 9, and the static seal between the inner cylinder guide 7 and the outer cylinder 9 is achieved through an inner cylinder guide O-ring, and the axial movement guidance and dynamic seal between the inner cylinder guide 7 and the inner cylinder 5 are achieved through an inner cylinder guide dust-proof oil seal 23, an inner cylinder guide bushing 25 and an inner cylinder guide skeleton oil seal 26.

[0112] According to some embodiments of the present utility model, the floating piston includes a piston bottom cover 27, a piston ball valve 28, a piston ball valve lower assembly 29, an electromagnetic coil 30, a piston guide belt 31, a piston ball valve upper assembly 32, a piston outer cylinder 9, a piston upper end cover 34, a piston rod O-ring 35, a piston upper cover locking nut 36, a piston rod stop ring 37 and a recovery buffer block 38.

[0113] According to the inventive concept of one aspect of the present utility model, there is also provided an automotive suspension, including the inverted magnetorheological damper as described above.

[0114] The technical solutions of the embodiments of the present utility model will be further elaborated below in conjunction with specific embodiments and the accompanying drawings. It should be understood that this specific embodiment is only for facilitating those skilled in the art to understand the technical solutions of the present utility model, and should not be regarded as an inappropriate limitation of the protection scope of the present utility model.

[0115] As Figure 1 shown, the magnetorheological shock absorber with non-linear stiffness components, adjustable inflation height function, characteristic of larger damping force in compression and smaller damping force in extension, inverted anti-roll and compact structure includes an inverted anti-roll and compact structure body, a non-linear stiffness component, and a piston assembly with a valve for larger damping force in compression and smaller damping force in extension, which are three parts.

[0116] Specifically, the inverted magnetorheological damper is composed of a connecting rod 1, an upper connecting nut 2, a storage chamber air nozzle 3, an upper connecting spring tray 4, an inner cylinder 5, a floating piston assembly 6, an inner cylinder guide 7, an outer magnet upper support 8, an outer cylinder 9, an inner cylinder graphite guide bearing 10, a shock absorber coil spring 11, a lower connecting spring tray 12, an outer magnet lower support 13, an inner and outer cylinder communication hole 14, an outer magnet assembly 15, an outer magnet support 16, an inner magnet fixing member 17, a shock absorber power cable harness 18, an outer cylinder bottom cover 19, a lower connecting nut 20, a floating piston O-ring 21, a floating piston guide strip 22, an inner cylinder guide dustproof oil seal 23, an inner cylinder guide O-ring 24, an inner cylinder guide bushing 25, an inner cylinder guide skeleton oil seal 26, a piston bottom cover 27, a piston ball valve 28, a piston ball valve lower assembly 29, an electromagnetic coil 30, a piston guide strip 31, a piston ball valve upper assembly 32, a piston outer cylinder 33, a piston upper end cover 34, a piston rod O-ring 35, a piston upper cover locking nut 36, a piston rod stop ring 37, a rebound buffer block 38, a piston rod guide 39, a piston rod guide bearing 40, a piston rod oil seal 41, an inner magnet fixing connecting member 42, an inner and outer cylinder air chamber air nozzle 43, an inner magnet piston rod guide bearing 44, an inner magnet assembly 45, an inner magnet support 46, an inner and outer cylinder high-pressure air chamber 47, a piston rod 48, a bottom cover O-ring 49, a magnetorheological fluid chamber 50, and a damper energy storage gas chamber 51.

[0117] The inner magnet assembly 45 is fixed to the piston rod guide 39 through the inner magnet support 46 and the inner magnet fixing member 17.

[0118] The piston rod guide bearing 40 and the piston rod oil seal 41 in the piston rod guide 39 are used for the dynamic sealing of the piston rod 48; the piston rod 48 is fixed to the outer cylinder bottom cover 19 through the lower connecting nut 20, and the static sealing between the piston rod and the outer cylinder bottom cover 19 is achieved by using the bottom cover O-ring 49.

[0119] The outer cylinder bottom cover 19 is connected to the outer cylinder 9 through circumferential seam welding to meet the requirements of sealing and tensile and compressive strength. The outer magnet assembly 15 is fixed by the outer magnet support 16, and is fixed inside the outer cylinder 9 through the outer magnet lower support 13, the inner cylinder graphite guide bearing 10 and the outer magnet upper support 8. The inner cylinder guide 7 is placed on the upper part of the outer magnet upper support 8 and fixed by a circlip.

[0120] The inner cylinder 5 and the connecting rod 1 are fixed to the upper connecting spring tray 4 by the upper connecting nut 2, and the upper connecting spring tray 4 is connected to the upper part of the vehicle suspension.

[0121] Figure 2 It is a three-dimensional view of the non-linear stiffness component of the present utility model.

[0122] As Figure 2 shown, both the outer magnet assembly 15 and the inner magnet assembly 45 are axially magnetized magnets, evenly distributed along the circumference. When the vehicle suspension moves, the inner magnet assembly 45 and the inner cylinder 5 simultaneously move axially back and forth relative to the outer cylinder 9 and the outer magnet assembly 15. At this time, due to the magnetic field interaction caused by the offset of the magnetic pole center line between the inner magnet assembly 45 and the outer magnet assembly 15, a non-linear negative stiffness force effect appears, and its effect is similar to the driving force effect of an active suspension under a certain control algorithm, thereby providing the vehicle with shock absorption performance similar to that of an active suspension.

[0123] Furthermore, when driving on unpaved roads such as off-road, the high-pressure gas introduced through the inner and outer cylinder air chamber nozzle 43 raises the inner cylinder 5 and the shock absorber coil spring 11 to a suitable position to achieve the road passing performance of the vehicle suspension under extreme road conditions such as unpaved roads.

[0124] Furthermore, the shock absorber coil spring 11 is connected by the upper connecting spring tray 4 and the lower connecting spring tray 12 to achieve the function of supporting the vehicle load. The inner and outer cylinder high-pressure air chamber 47 is inflated through the inner and outer cylinder air chamber nozzle 43 to achieve the function of adjustable damper height. As Figure 3As shown, in Mode 1, when the vehicle load increases, the inner cylinder 5 and the shock absorber coil spring 11 are compressed downward. The intermediate equilibrium position of the inner magnet assembly 45 and the outer magnet assembly 15 changes, causing the maximum value of the non-linear stiffness to shift. At this time, high-pressure inflation is carried out through the inner and outer cylinder air chamber nozzles 43 (internal pressure: P2 > P1), and the gas is filled into the middle of the inner and outer cavities through the inner and outer cylinder communication holes 14. At this time, the piston rod 48 is fixed to the bottom cover 19 of the outer cylinder through the lower connecting nut 20, and the bottom cover O-ring 49 is used to achieve the static seal between the piston rod and the bottom cover 19 of the outer cylinder. The inner cylinder guide 7 achieves the static seal with the outer cylinder 9 through the inner cylinder guide O-ring 24. The inner cylinder guide 7 achieves the axial movement guidance and dynamic seal with the inner cylinder 5 through the inner cylinder guide dust-proof oil seal 23, the inner cylinder guide bushing 25, and the inner cylinder guide skeleton oil seal 26. The high-pressure gas introduced through the inner and outer cylinder air chamber nozzles 43 causes the inner cylinder 5 and the shock absorber coil spring 11 to return to the initial intermediate equilibrium position of the inner magnet assembly 45 and the outer magnet assembly 15 to obtain the maximum non-linear stiffness value.

[0125] Figure 3 It is a two-dimensional principle schematic diagram of two inflatable height adjustable modes of the present utility model.

[0126] As Figure 3 shown, in Mode 2, when the vehicle suspension needs to achieve the road passing performance on extreme road conditions such as unpaved roads, higher-pressure gas inflation is carried out through the inner and outer cylinder air chamber nozzles 43 (internal pressure: P4 > P3 > P2 > P1). For example, when on off-road and other unpaved roads, the high-pressure gas introduced through the inner and outer cylinder air chamber nozzles 43 causes the inner cylinder 5 and the shock absorber coil spring 11 to rise to a suitable position, increasing the ground clearance of the vehicle suspension chassis to ensure that the vehicle suspension can smoothly pass through unpaved roads.

[0127] Figure 4 It is a cross-sectional view of the piston with a characteristic of increasing damping force during compression of the present utility model.

[0128] As Figure 4 shown, the piston bottom cover 27, the piston ball valve 28, the lower assembly of the piston ball valve 29, the electromagnetic coil 30, the piston guide belt 31, the upper assembly of the piston ball valve 32, the piston outer cylinder 33, the piston upper end cover 34, the piston rod O-ring 35, the locking nut of the piston upper cover 36, the piston rod stop ring 37, and the recovery buffer block 38 form a magnetorheological damper with the characteristic of increasing damping force during compression and decreasing damping force during extension. A controllable current is introduced through the shock absorber power line harness 18, and the electromagnetic coil 30 generates a magnetic field in the magnetorheological fluid chamber 50. The magnetorheological piston part utilizes the characteristics of millisecond-level phase change and continuously controllable damping of the magnetorheological fluid in the magnetic field, enabling the shock absorber to exhibit the characteristic of continuously adjustable damping force.

[0129] Meanwhile, the one-way piston ball valve 28 in the disclosed embodiment is designed to output a large damping force during stretching and a small damping force during compression of the magnetorheological damper, thereby improving the riding comfort. The specific implementation method is that when the piston is in the stretching stroke, the ball valve blocks the outlet of the middle flow channel of the valve core, and the liquid only passes through the peripheral magneto-controlled damping channel, showing a large damping force; when the piston is in the compression stroke, the ball valve releases the outlet of the middle flow channel, and the liquid can pass directly, showing a small damping force. For example, when passing through road conditions such as speed bumps, due to the compression speed being greater than the stretching speed, this characteristic can improve the riding comfort of the damper, and this structure can have better shock absorption and isolation of road vibrations from the vehicle suspension life and the vibrations of the passengers.

[0130] Furthermore, the piston rod 48 is fixed to the bottom cover 19 of the outer cylinder by the lower connecting nut 20, and the axial movement of the piston rod 48 and the magnet fixed connecting member 42 is guided by the inner magnet fixed connecting member 42 and the inner magnet piston rod guiding bearing 44. The axial movement of the piston rod 48 and the inner cylinder 5 is guided by the piston rod guide 39 and the piston rod guiding bearing 40. The axial movement of the inner cylinder 5 and the outer cylinder 9 is guided by the inner cylinder guide 7 and the inner cylinder guiding bushing 25, and the axial movement of the inner cylinder 5 and the outer cylinder 9 is guided by the inner cylinder graphite guiding bearing 10. The adoption of this inverted structure not only meets the requirements of the compact installation space of the vehicle suspension, but also greatly improves the anti-roll ability of the shock absorber and maintains the coaxiality during the axial reciprocating movement of the internal components of the shock absorber.

[0131] The embodiments of the present invention have been described above. However, these embodiments are only for illustrative purposes and not for limiting the scope of the present invention. Although the embodiments have been described separately above, this does not mean that the measures in each embodiment cannot be used advantageously in combination. The scope of the present invention is defined by the appended claims and their equivalents. Without departing from the scope of the present invention, those skilled in the art can make various substitutions and modifications, and these substitutions and modifications should all fall within the scope of the present invention.

Claims

1. An inverted magnetorheological damper with non-linear stiffness characteristics and adjustable inflation height, characterized in that, Comprising: An upper connecting spring tray, adapted to be connected to a vehicle suspension; An inner cylinder, the upper end of which is connected to the upper connecting spring tray; A piston rod guide, installed at the lower end of the inner cylinder, and a through hole is provided on the piston rod guide; A floating piston, slidably disposed in the inner cylinder, and the floating piston divides the inner space of the inner cylinder into a damper energy storage gas chamber located above and a magnetorheological fluid chamber located below; An outer cylinder, slidably and sealingly sleeved on the outer side wall of the inner cylinder, and an outer cylinder bottom cover is provided at the bottom of the outer cylinder, and the outer cylinder and the piston rod guide jointly define an inner and outer cylinder high-pressure gas chamber; A piston rod, the lower end of which is connected to the outer cylinder bottom cover, and the upper end of which slidably and sealingly passes through the piston rod guide and extends into the magnetorheological fluid chamber; A piston ball valve, provided at the upper end of the piston rod, the piston ball valve being a one-way piston ball valve, and the piston ball valve being configured to output a large damping force during tension and a small damping force during compression; And A lower connecting spring tray, installed on the outer cylinder, and the lower connecting spring tray is configured to support the vehicle load.

2. The inverted magnetorheological damper according to claim 1, wherein Further comprising: An electromagnetic coil, sleeved on the piston ball valve; And A shock absorber power supply wire harness, disposed inside the piston rod, and the shock absorber power supply wire harness is electrically connected to the electromagnetic coil to generate an adjustable variable magnetic field, thereby changing the damping force of the shock absorber.

3. The inverted magnetorheological damper according to claim 1, wherein Further comprising: A shock absorber coil spring, sleeved on the outer sides of the outer cylinder and the inner cylinder, and two ends of the shock absorber coil spring are respectively connected to the upper connecting spring tray and the lower connecting spring tray.

4. The inverted magnetorheological damper according to claim 1, characterized in that, Further comprising: An inner magnet assembly, installed on the piston rod guide; And An outer magnet assembly, fixedly installed on the inner side wall of the outer cylinder; Wherein, in response to the movement of the vehicle suspension, the inner magnet assembly and the inner cylinder simultaneously perform an axial reciprocating movement relative to the outer cylinder and the outer magnet assembly, and the inner magnet assembly and the outer magnet assembly exhibit an effect of non-linear negative stiffness force under the action of an axially magnetized magnetic field.

5. The inverted magnetorheological damper according to claim 1, characterized in that, Further comprising: An energy storage chamber air nozzle, provided on the inner cylinder, and the energy storage chamber air nozzle is adapted to fill the damper energy storage gas chamber with gas.

6. The inverted magnetorheological damper according to claim 1, characterized in that, Further comprising: An inner and outer cylinder air chamber air nozzle, provided on the outer cylinder, and the inner and outer cylinder air chamber air nozzle is adapted to fill the inner and outer cylinder high-pressure gas chamber with gas.

7. The inverted magnetorheological damper according to claim 1, characterized in that, Further comprising an inner cylinder guide, the inner cylinder guide is disposed inside the upper end of the outer cylinder, and a static seal between the inner cylinder guide and the outer cylinder is achieved through an inner cylinder guide O-ring, and an axial movement guide and a dynamic seal between the inner cylinder guide and the inner cylinder are achieved through an inner cylinder guide dust-proof oil seal, an inner cylinder guide bushing and an inner cylinder guide frame oil seal.

8. The inverted magnetorheological damper according to claim 1, characterized in that, The floating piston includes a piston bottom cover, a piston ball valve, a piston ball valve lower assembly, the electromagnetic coil, a piston guide band, a piston ball valve upper assembly, a piston outer cylinder, a piston upper end cover, a piston rod O-ring, a piston upper cover locking nut, a piston rod stop ring and a recovery buffer block.

9. An automotive suspension, characterized in that, Comprising an inverted magnetorheological damper according to any one of claims 1 to 8.

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