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

Abstract

The invention 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, 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 present disclosure relates to the field of vehicle suspension research, engineering application and magneto-rheological technology, in particular to a magneto-rheological damper integrated with a nonlinear stiffness component, an adjustable air height function, a damping force stretching and compressing characteristic, an inverted anti-roll structure and a compact structure, which is an innovative application of magneto-rheological damper in mechanism. BACKGROUND

[0002] With the continuous progress of modern industrial technology, the requirements for damping technology are also constantly improving. In the field of automobile suspension research and engineering application engineering, there is a great demand for shock absorbers that meet the requirements of vehicle ride comfort, handling stability and road passability. And high-efficiency shock absorber, intelligent controllable and compact structure of damping device is essential to improve the safety, stability and comfort of the structure. Traditional magneto-rheological dampers mostly use single controllable electromagnetic rheological characteristics, but in actual application, vehicle suspensions often need to face complex road conditions, and traditional magneto-rheological dampers are not up to the task when dealing with these complex scenarios.

[0003] As an intelligent material damper, magneto-rheological damper has gradually become a research hotspot due to its fast response speed, adjustable damping force, simple structure and other advantages. The core material of magneto-rheological damper is magneto-rheological fluid, which is an intelligent material that changes in viscosity reversibly under the action of a magnetic field. By controlling the magnetic field strength, the viscosity of the magneto-rheological fluid can be adjusted in real time, thereby changing the damping characteristics of the damper and achieving effective control of vibration.

[0004] Although existing magneto-rheological dampers perform well in various applications, their structure is often single and cannot fully adapt to complex vibration environments. In addition, existing dampers are mostly positive type designs, and in some special application scenarios, more flexible damper forms are required for space arrangement. The present disclosure proposes an inverted magneto-rheological damper with anti-roll and compact structure. In actual operation, vehicles face complex road scenes, for example, when passing through a speed bump or other road conditions, the compression speed is greater than the stretching speed, in order to maintain good ride comfort of the vehicle suspension. SUMMARY

[0005] Therefore, the present disclosure provides an inverted magneto-rheological damper with linear stiffness characteristics and adjustable air height, which can meet the requirements of vehicle suspension for ride comfort, handling stability and road passability.

[0006] According to the inventive concept of one aspect of the present disclosure, an inverted magneto-rheological damper with nonlinear stiffness characteristics and adjustable air height is provided, comprising:

[0007] The upper connecting spring tray is suitable for connecting with the vehicle suspension;

[0008] an upper connecting spring tray connected to an upper end of the inner cylinder;

[0009] a piston rod guide mounted at a lower end of the inner cylinder, the piston rod guide having a through hole formed therein;

[0010] a floating piston assembly slidably disposed in the inner cylinder, the floating piston assembly dividing a space in the inner cylinder into an upper damper gas chamber and a lower magnetorheological fluid chamber;

[0011] an outer cylinder slidably and sealingly sleeved on an outer sidewall of the inner cylinder, the outer cylinder having an outer cylinder bottom cover provided at a bottom thereof, the outer cylinder and the piston rod guide together defining an inner-outer cylinder high-pressure gas chamber;

[0012] a piston rod having a lower end connected to the outer cylinder bottom cover and an upper end slidably and sealingly penetrating the piston rod guide and extending into the magnetorheological fluid chamber;

[0013] a piston ball valve provided at the upper end of the piston rod, the piston ball valve being a one-way piston ball valve configured to output a large damping force when stretched and a small damping force when compressed; and

[0014] a lower connecting spring tray mounted on the outer cylinder, the lower connecting spring tray being configured to support a load of a vehicle.

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

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

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

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

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

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

[0021] an inner magnet assembly mounted on the piston rod guide; and

[0022] an outer magnet assembly fixedly mounted on an inner sidewall of the outer cylinder.

[0023] Wherein, in response to the movement of the vehicle suspension, the inner magnet assembly and the inner cylinder simultaneously reciprocate axially relative to the outer cylinder and the outer magnet assembly, and the inner magnet assembly and the outer magnet assembly generate nonlinear negative stiffness force under the action of the axially magnetized magnetic field.

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

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

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

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

[0028] According to some embodiments of the present disclosure, an inner cylinder guide is further arranged inside the upper end of the outer cylinder, the inner cylinder guide and the outer cylinder are in static sealing through an inner cylinder guide O-ring, and the inner cylinder guide is in axial movement guiding and dynamic sealing with the inner cylinder through an inner cylinder guide dustproof oil seal, an inner cylinder guide bushing and an inner cylinder guide skeleton oil seal.

[0029] According to some embodiments of the present disclosure, the floating piston assembly comprises 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 one aspect of the present disclosure, an automobile suspension is further provided, which comprises the inverted magnetorheological damper as described above.

[0031] Compared with the prior art, the inverted magnetorheological damper and the automobile suspension provided by the present disclosure have the following characteristics:

[0032] (1) The inverted magnetorheological damper of the present disclosure can generate nonlinear negative stiffness force through the axial reciprocating movement of the inner-outer magnet assembly, realize the actuating force effect similar to the active suspension under certain control algorithm, and thus provide the damping performance similar to the active suspension for the vehicle.

[0033] (2) The air inflation height-adjustable mode is added 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 inner and outer magnet groups can be kept within a certain horizontal position range by adjusting the air pressure. The air inflation adjustable structure can also adjust the height of the vehicle body according to different road conditions. For example, in the off-road scene, 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.

[0034] (3) The one-way ball valve design in the inverted magnetorheological damper of the embodiment of the present disclosure makes the magnetorheological damper output large damping force when stretched and output small damping force when compressed, thereby improving the ride comfort. For example, when passing through a deceleration zone, the ride comfort of the vehicle suspension can be improved due to the compression speed being greater than the stretching speed.

[0035] (4) The above structure has the advantages of nonlinear stiffness, air inflation adjustable balance position, large damping force and small damping force, inverted anti-roll, and compact structure, which can meet the needs of ride comfort, handling stability and road passability of the vehicle suspension at the same time. BRIEF DESCRIPTION OF DRAWINGS

[0036] The above and other objects, features and advantages of the present disclosure will become more apparent from the following description of embodiments of the present disclosure taken in conjunction with the accompanying drawings, in which:

[0037] Figure 1 is a cross-sectional view of the inverted magnetorheological shock absorber of the present disclosure.

[0038] Figure 2 is a three-dimensional view of the nonlinear stiffness assembly of the present disclosure.

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

[0040] Figure 4 is a cross-sectional view of the piston with the large-stretching and small-compression characteristic of the present disclosure.

[0041] In the above drawings, the meanings of the reference signs are as follows:

[0042] 1- connecting rod;

[0043] 2- upper connecting nut;

[0044] 3- energy storage cavity air nozzle;

[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 supply wire harness;

[0060] 19-outer cylinder bottom cover;

[0061] 20-lower connecting nut;

[0062] 21-floating piston O-ring;

[0063] 22-floating piston guide belt;

[0064] 23-inner cylinder guide dustproof 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-magnetic coil;

[0072] 31-piston guide belt;

[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 - piston upper cover locking nut;

[0078] 37 - piston rod stop ring;

[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 fixed connecting piece;

[0084] 43 - inner and outer cylinder gas cavity gas nozzle;

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

[0086] 45 - inner magnet assembly;

[0087] 46 - inner magnet support;

[0088] 47 - inner and outer cylinder high-pressure gas cavity;

[0089] 48 - piston rod;

[0090] 49 - bottom cover O-ring;

[0091] 50 - magnetorheological fluid cavity;

[0092] 51 - damper energy storage gas cavity; DETAILED DESCRIPTION

[0093] In order to make the purpose, technical solutions and advantages of the present disclosure clearer, the present disclosure is further described in detail below with reference to specific embodiments and drawings.

[0094] The terms used herein are merely used to describe specific embodiments, and are not intended to limit the present disclosure. The terms "include", "contain" and the like used herein indicate the existence of the described features, steps, operations and / or components, but do not exclude the existence or addition of one or more other features, steps, operations or components.

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

[0096] In the event that expressions such as "at least one of A, B, and C, etc." are used herein, it generally should be understood that such phrases are used to provide an "and / or" perimeter to the listed items, e.g., the phrase "at least one of A, B, and C" should be interpreted to mean: "A alone; B alone; C alone; A and B together; A and C together; B and C together; or A, B, and C together." In the event that expressions such as "at least one of A or B" are used herein, it generally should be understood that such phrases are used to provide an "even more restrictive and / or" perimeter to the listed items, e.g., the phrase "at least one of A or B" should be interpreted to mean: "A alone and not B; B alone and not A; A and B together, etc."

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

[0098] The present disclosure proposes an inverted magnetorheological damper with nonlinear stiffness characteristics and adjustable air height function. The damper integrates an axially magnetized magnet group as a nonlinear stiffness component on the piston rod guide and the outer cylinder, so that the outer magnet group moves axially with the outer cylinder relative to the inner cylinder, achieving an actuating force effect similar to that of an active suspension under certain control algorithm, thereby providing a damping performance similar to that of an active suspension for a vehicle.

[0099] The present disclosure designs a piston ball valve with a large-damping-small-compression characteristic to improve the ride comfort of a vehicle. The introduction of the large-damping-small-compression characteristic of the damping force can effectively enhance the damping force of the damper in the stretching state and reduce the damping force in the compression state, thereby improving the damping effect and ride comfort. At the same time, the adjustable air height function 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 in space-limited and harsh installation conditions. In order to further improve the damping effect and application flexibility.

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

[0101] According to the inventive concept of one aspect of the present disclosure, an inverted magnetorheological damper with nonlinear stiffness characteristics and adjustable air height is provided, as shown in Figure 1As shown, it comprises: 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 suitable for connecting with the vehicle suspension. The inner cylinder 5 is connected with the upper connecting spring tray 4 at the upper end. The piston rod guide 39 is installed at the lower end of the inner cylinder 5, and a through hole is formed in the piston rod guide 39. The floating piston assembly 6 is slidably arranged in the inner cylinder 5, and the floating piston assembly 6 divides the space in the inner cylinder 5 into a damper energy storage gas cavity 51 located at the upper side and a magnetorheological fluid cavity 50 located at the lower side. The outer cylinder 9 is slidably and sealingly sleeved on the outer sidewall of the inner cylinder 5, and the bottom of the outer cylinder 9 is provided with an outer cylinder bottom cover 19. The outer cylinder 9 and the piston rod guide 39 jointly define an inner-outer cylinder high-pressure gas cavity 47. The piston rod 48 is connected with the outer cylinder bottom cover 19 at the lower end and extends into the magnetorheological fluid cavity 50 through the piston rod guide 39 at the upper end in a sliding and sealing manner. The piston ball valve 28 is arranged 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 when stretched and output a small damping force when compressed. 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 load of the vehicle.

[0102] In the embodiment, by integrating the axially magnetized magnet group as a nonlinear stiffness component on the piston rod guide 39 and the outer cylinder 9, the outer magnet group moves axially with the outer cylinder 9 relative to the inner cylinder 5, achieving an actuating force effect similar to that of an active suspension under a certain control algorithm, thereby providing the vehicle with a damping performance similar to that of an active suspension.

[0103] According to some embodiments of the present disclosure, the one-way ball valve design in the embodiment of the present disclosure enables the magnetorheological damper to output a large damping force when stretched and a small damping force when compressed, thereby improving the ride comfort. For example, when passing through a deceleration zone, the ride comfort of the vehicle suspension can be improved due to the compression speed being greater than the stretching speed. 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 damper and maintains the coaxiality of the inner and outer magnet groups during axial reciprocating movement.

[0104] According to some embodiments of the present disclosure, the inverted magnetorheological damper further comprises an electromagnetic coil 30 and a damper power supply wire harness 18. The electromagnetic coil 30 is sleeved on the piston ball valve. The damper power supply wire harness 18 is arranged inside the piston rod, and the damper power supply wire harness 18 is electrically connected with the electromagnetic coil 30 to generate an adjustable variable magnetic field, thereby changing the damping force of the damper.

[0105] In the embodiment, the magnetorheological piston part utilizes the characteristics of millisecond-level phase change and continuous controllable damping of the magnetorheological fluid under a magnetic field, so that the damper exhibits a continuously adjustable damping force.

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

[0107] According to some embodiments of the present disclosure, the inverted magnetorheological damper further comprises 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. In response to the movement of the vehicle suspension, the inner magnet assembly 45 and the inner cylinder 5 simultaneously move axially 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 nonlinear negative stiffness force under the action of the axially magnetized magnetic field.

[0108] According to some embodiments of the present disclosure, the inverted magnetorheological damper further comprises an energy storage cavity air nozzle 3, which is arranged on the inner cylinder 5 and is adapted to fill gas into the damper energy storage gas cavity 51.

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

[0110] In the present embodiment, high-pressure air can be filled between the outer cylinder 9 and the inner cylinder 5 through the inflation valve, and when the vehicle load changes, the inner-outer magnet assembly can be kept within a certain horizontal position range by adjusting the air pressure. The inflation adjustable structure can also adjust the vehicle body height according to different road conditions. For example, in the off-road scene, 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 disclosure, the inner cylinder guide 7 is arranged inside the upper end of the outer cylinder 9, and the inner cylinder guide 7 and the outer cylinder 9 are in static sealing with the outer cylinder 9 through the inner cylinder guide O-ring, and the inner cylinder guide 7 realizes axial movement guidance and dynamic sealing with the inner cylinder 5 through the inner cylinder guide dustproof oil seal 23, the inner cylinder guide bushing 25 and the inner cylinder guide skeleton oil seal 26.

[0112] According to some embodiments of the present disclosure, the floating piston comprises 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 one aspect of the inventive concept disclosed herein, an automotive suspension is also provided, including the aforementioned inverted magnetorheological damper.

[0114] The technical solutions of the embodiments of this disclosure will be further described below with reference to specific implementations and accompanying drawings. It should be understood that the specific embodiments are only for the purpose of enabling those skilled in the art to understand the technical solutions of this disclosure, and should not be construed as an inappropriate limitation on the scope of protection of this disclosure.

[0115] like Figure 1 As shown, the magnetorheological vibration damper, which features a nonlinear stiffness component, adjustable inflation height, high damping force with low compressive force, inverted anti-rollover design, and compact structure, comprises three parts: an inverted anti-rollover and compact structural body, a nonlinear stiffness component, and a piston assembly with a valve that allows for high damping force with low compressive force.

[0116] Specifically, the inverted magnetorheological damper consists of a connecting rod 1, an upper connecting nut 2, an energy 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 upper support for the outer magnet 8, an outer cylinder 9, an inner cylinder graphite guide bearing 10, a damper coil spring 11, a lower connecting spring tray 12, a lower support for the outer magnet 13, a connecting hole between the inner and outer cylinders 14, an outer magnet assembly 15, an outer magnet support 16, an inner magnet fixing component 17, a damper wiring harness 18, an outer cylinder bottom cover 19, a lower connecting nut 20, a floating piston O-ring 21, a floating piston guide belt 22, an inner cylinder guide dustproof oil seal 23, an inner cylinder guide O-ring 24, an inner cylinder guide bushing 25, and an inner cylinder guide frame. The system comprises: an oil seal 26, a piston bottom cover 27, a piston ball valve 28, a lower piston ball valve assembly 29, an electromagnetic coil 30, a piston guide band 31, an upper piston ball valve assembly 32, an outer piston cylinder 33, an upper piston end cover 34, a piston rod O-ring 35, a piston upper cover locking nut 36, a piston rod stop ring 37, a recovery buffer block 38, a piston rod guide 39, a piston rod guide bearing 40, a piston rod oil seal 41, an inner magnet fixing connector 42, an inner and outer cylinder air chamber 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 by the inner magnet support 46 and the inner magnet fixing member 17.

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

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

[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. The upper connecting spring tray 4 is connected to the upper part of the vehicle suspension.

[0121] Figure 2 A three-dimensional view of the nonlinear stiffness assembly of the present disclosure.

[0122] As shown in Figure 2 The outer magnet assembly 15 and the inner magnet assembly 45 are both axially magnetized magnets and are uniformly distributed along the circumference. When the vehicle suspension moves, the inner magnet assembly 45 and the inner cylinder 5 simultaneously reciprocate axially relative to the outer cylinder 9 and the outer magnet assembly 15. At this time, the inner magnet assembly 45 and the outer magnet assembly 15 exhibit nonlinear negative stiffness force due to the magnetic field interaction caused by the center line offset of the magnetic poles. The effect is similar to the actuating force effect of the active suspension under certain control algorithm, thereby providing the vehicle with a damping performance similar to that of the active suspension.

[0123] Further, when driving on unpaved roads and the like, the high-pressure gas entering through the inner and outer cylinder air chamber air nozzle 43 causes the inner cylinder 5 and the shock absorber coil spring 11 to rise to the appropriate position, thereby achieving the road passability of the vehicle suspension on non-paved and other extreme road conditions.

[0124] Further, 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 load of the vehicle. The inner and outer cylinder high-pressure air chamber 47 is inflated by the inner and outer cylinder air chamber air nozzle 43 to achieve the height-adjustable function of the damper. Figure 3As shown, in mode 1, when the vehicle load increases, the inner cylinder 5 and the shock absorber coil spring 11 will compress downwards, and the intermediate balance position of the inner magnet assembly 45 and the outer magnet assembly 15 will change, causing the maximum value of the nonlinear stiffness to shift. At this time, high-pressure air is injected through the air nozzle 43 of the inner and outer cylinder air chambers (internal pressure: P2>P1), and the gas is filled into the middle of the inner and outer cavities through the inner and outer cylinder connecting hole 14. At this time, the piston rod 48 is fixed to the bottom cover 19 of the outer cylinder by the lower connecting nut 20, and the bottom cover O-ring 49 is used to secure it. The piston rod and outer cylinder bottom cover 19 are statically sealed. The inner cylinder guide 7 achieves static sealing with the outer cylinder 9 through the inner cylinder guide O-ring 24. The inner cylinder guide 7 achieves axial movement guidance and dynamic sealing with the inner cylinder 5 through the inner cylinder guide dustproof oil seal 23, inner cylinder guide bushing 25 and inner cylinder guide skeleton oil seal 26. The high-pressure gas entering through the air nozzle 43 of the inner and outer cylinder air chambers causes the inner cylinder 5 and the damper coil spring 11 to return to the initial intermediate equilibrium position of the inner magnet assembly 45 and the outer magnet assembly 15, so as to obtain the maximum nonlinear stiffness value.

[0125] Figure 3 This is a two-dimensional schematic diagram illustrating the two adjustable inflation height modes disclosed herein.

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

[0127] Figure 4 This is a cross-sectional view of the piston with the characteristics of increased tension and decreased compression disclosed herein.

[0128] like Figure 4 As shown, the piston bottom cover 27, piston ball valve 28, piston ball valve lower assembly 29, electromagnetic coil 30, piston guide belt 31, piston ball valve upper assembly 32, piston outer cylinder 33, piston upper end cover 34, piston rod O-ring 35, piston upper cover locking nut 36, piston rod stop ring 37, and recovery buffer block 38 form a magnetorheological damper with the characteristic of large damping force when pulled and small damping force when compressed. A controllable current is passed through the damper's power supply 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 the magnetorheological fluid's millisecond-level phase change and continuous and controllable damping under the magnetic field to make the damper exhibit continuously adjustable damping force characteristics.

[0129] Meanwhile, the one-way piston ball valve 28 in the disclosed embodiment is designed to make the magneto-rheological damper output large damping force when stretched and small damping force when compressed, thereby improving the ride comfort. The specific implementation is that when the piston is stretched, the ball valve blocks the middle flow passage outlet of the valve core, and the liquid only passes through the peripheral magnetic control damping channel, which exhibits large damping force; when the piston is compressed, the ball valve releases the middle flow passage outlet, and the liquid can pass directly, which exhibits small damping force. For example, when passing through a deceleration zone, the compression speed is greater than the stretching speed, and this feature can improve the ride comfort of the damper. This structure can have good impact absorption and isolation of road vibration on the service life of the vehicle suspension and the vibration of the occupants.

[0130] Further, the piston rod 48 is fixed to the outer cylinder bottom cover 19 through the lower connecting nut 20, and the axial movement of the piston rod 48 and the magnet fixed connecting piece 42 is guided by the inner magnet fixed connecting piece 42 and the inner magnet piston rod guide 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 guide 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 guide bushing 25, the axial movement of the inner cylinder 5 and the outer cylinder 9 is guided by the inner cylinder graphite guide bearing 10, and the 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 of the axial reciprocating movement of the internal components of the shock absorber.

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

Claims

1. An inverted magnetorheological damper with nonlinear stiffness characteristics and adjustable inflation height, characterized in that, include: The upper connecting spring tray is suitable for connection with vehicle suspension; The inner cylinder is connected at its upper end to the upper connecting spring tray; A piston rod guide is installed at the lower end of the inner cylinder, and a through hole is provided on the piston rod guide; A floating piston is slidably disposed in the inner cylinder, which divides the space inside the inner cylinder into a damper energy storage gas chamber located above and a magnetorheological fluid chamber located below. The outer cylinder is slidably and sealed on the outer side wall of the inner cylinder. The bottom of the outer cylinder is provided with an outer cylinder bottom cover. The outer cylinder and the piston rod guide together define the high-pressure air chamber of the inner and outer cylinders. The piston rod is connected at its lower end to the bottom cover of the outer cylinder, and at its upper end, it extends through the piston rod guide and into the magnetorheological fluid chamber in a sliding seal. A 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 is configured to output a large damping force during tension and a small damping force during compression. as well as A lower connecting spring tray is mounted on the outer cylinder, and the lower connecting spring tray is configured to support the vehicle's load.

2. The inverted magnetorheological damper according to claim 1, characterized in that, Also includes: An electromagnetic coil is sleeved on the piston ball valve; as well as The damper wiring harness is located inside the piston rod. The damper wiring harness is electrically connected to the electromagnetic coil to generate an adjustable variable magnetic field, thereby changing the damping force of the damper.

3. The inverted magnetorheological damper according to claim 1, characterized in that, Also includes: A shock absorber coil spring is sleeved on the outside of the outer cylinder and the inner cylinder, and the 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, Also includes: The inner magnet assembly is mounted on the piston rod guide; as well as An external magnet assembly is fixedly installed on the inner wall of the outer cylinder; In response to the movement of the vehicle suspension, the inner magnet assembly and the inner cylinder simultaneously reciprocate axially relative to the outer cylinder and the outer magnet assembly. Under the action of the axially magnetized magnetic field, the inner magnet assembly and the outer magnet assembly exhibit a nonlinear negative stiffness force effect.

5. The inverted magnetorheological damper according to claim 1, characterized in that, Also includes: An energy storage chamber nozzle is disposed on the inner cylinder, and the energy storage chamber nozzle is used to fill the energy storage gas chamber of the damper with gas.

6. The inverted magnetorheological damper according to claim 1, characterized in that, Also includes: The inner and outer cylinder air chamber nozzles are installed on the outer cylinder and are used to fill the high-pressure air chambers of the inner and outer cylinders with gas.

7. The inverted magnetorheological damper according to claim 1, characterized in that, It also includes an inner cylinder guide, which is disposed inside the upper end of the outer cylinder. The inner cylinder guide and the outer cylinder are statically sealed by the inner cylinder guide O-ring. The inner cylinder guide is axially guided and dynamically sealed by the inner cylinder guide dustproof oil seal, the inner cylinder guide bushing and the inner cylinder guide skeleton 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 lower piston ball valve assembly, an electromagnetic coil, a piston guide band, an upper piston ball valve 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. A car suspension, characterized in that, Including the inverted magnetorheological damper as described in any one of claims 1 to 8.

Images