An adaptive dual-channel magnetorheological damper

Abstract

The application discloses a self-adaptive double-channel magneto-rheological damper with a wide adjustment range, and belongs to the technical field of automobile suspension systems, and comprises a self-adaptive double-channel piston assembly, a working cylinder assembly, a compensation piston assembly and a guide assembly, the self-adaptive double-channel piston assembly internally comprises a main channel that is always open and a self-adaptive auxiliary channel that is guided by a one-way mechanism, and a coil winding is arranged between the two channels to realize synchronous control. When the self-adaptive double-channel piston assembly is forced to vibrate, the channel flow distribution can be adaptively adjusted according to the generated fluid damping force, and then the impact resistance and the damping force adjustment range of the damper are improved; the exciting magnetic field generated by the coil winding can vertically pass through the main channel and the auxiliary channel at the same time, and then the utilization rate of the magnetic field is effectively improved. The application can be applied to vehicle suspensions of different vehicle models, and the riding comfort and the control stability of the vehicle are improved.

Description

Technical Field

[0001] This invention belongs to the technical field of automotive suspension systems, specifically relating to an adaptive dual-channel magnetorheological damper. Background Technology

[0002] With the continuous development of automotive suspension systems, the performance requirements for suspension dampers are increasing, especially in the contradictory aspects of ride comfort and handling stability. Magnetorheological dampers, as a highly efficient damping control device, possess advantages such as high response speed, simple structure, and high robustness, and have been widely used in automotive suspension systems, providing relatively ideal dynamic response control. However, existing magnetorheological dampers still face several technical bottlenecks in practical applications. Due to design limitations, the damping force adjustment range of traditional magnetorheological dampers is quite limited, resulting in insufficient adjustment capability for handling stability. Furthermore, when a magnetorheological damper experiences a sudden large displacement or impact load during high-speed impacts, the flow velocity of the magnetorheological fluid flowing through the damper increases rapidly, leading to a sharp increase in fluid pressure difference. This results in an excessively large minimum damping force (zero-field damping force), which may be directly transmitted to the occupants, significantly reducing ride comfort under impact conditions. This limitation prevents existing dampers from adapting to the complex and varied vibration requirements under different driving conditions, affecting the overall comfort and handling stability of the vehicle.

[0003] Existing technical solutions mainly employ methods such as increasing the cross-sectional area of ​​the channel or using multiple channels to reduce the minimum damping force under impact conditions. However, these solutions also reduce the maximum damping force of the magnetorheological damper, thereby affecting the adjustment range of its handling stability and thus hindering the improvement of the overall performance of the suspension. On the other hand, using electronically controlled valves to improve the adjustment range of handling stability significantly increases system cost and the difficulty of system control, thereby affecting the robustness of the suspension system. Summary of the Invention

[0004] To solve the above-mentioned technical problems, the present invention adopts the following technical solution: an adaptive dual-channel magnetorheological damper, comprising: an adaptive dual-channel piston assembly, a working cylinder assembly, a compensating piston assembly, and a guide assembly. The outer cylinder guide band of the adaptive dual-channel piston assembly and the inner wall of the working cylinder assembly form a coaxial fit through surface contact, thereby placing the adaptive dual-channel piston assembly in the chamber inside the working cylinder 39 of the working cylinder assembly. Inside the working cylinder, in the upper chamber above the adaptive dual-channel piston assembly, the piston rod of the adaptive dual-channel piston assembly coaxially passes through the guide assembly to achieve radial multi-degree-of-freedom constraint of the piston rod. In the lower chamber below the adaptive dual-channel piston assembly, a compensating piston assembly coaxial with the adaptive dual-channel piston assembly is provided; the compensating piston assembly divides the lower chamber into two chambers, wherein the chamber below the compensating piston assembly constitutes a volume compensation chamber; the adaptive dual-channel piston assembly includes a damping main channel, a damping auxiliary channel, and a coil winding, and the synchronous control of the damping main channel and the damping auxiliary channel is achieved through the arrangement of the coil winding.

[0005] The present invention has the following beneficial effects: The adaptive dual-channel magnetorheological damper of the present invention includes an adaptive dual-channel piston assembly. This assembly adds an adaptively adjustable auxiliary damping channel to the piston assembly of a traditional magnetorheological damper, allowing the damper to adaptively adjust the channel flow distribution according to the magnitude of the fluid damping force. When the damping force is low, the dual-channel magnetorheological damper of the present invention has a dual-channel pressure relief function, thereby increasing the effective cross-sectional area of ​​the channels to reduce the flow-induced pressure difference (fluid pressure difference), and thus reducing the minimum damping force of the magnetorheological damper. It can also lock the auxiliary channel when the damping force is high, forming a single-channel flow concentration, increasing the maximum damping force of the magnetorheological damper. Correspondingly, the coil winding configuration of the present invention enables synchronous control of the main damping channel and the auxiliary damping channel. The coordinated operation of the dual-channel structure and the coil winding gives the damper a wide adaptive adjustment range, thereby improving vehicle ride comfort and handling stability. Attached Figure Description

[0006] Figure 1This is an axonometric sectional view of the adaptive dual-channel magnetorheological damper of the present invention, wherein: 1-floating compensating piston, 2-compensating piston guide band, 3-bottom end cap, 4-first positioning pin, 5-second positioning pin, 6-lower magnetic guide plate, 7-first plug guide band, 8-first helical spring, 9-insulating covering layer, 10-second helical spring, 11-upper magnetic guide plate, 12-second plug guide band, 13-piston inner core, 14-piston rod O-ring, 15-shaft retaining ring, 16-outer lead wire, 17-magnetorheological fluid, 18-nylon buffer pad, 19-guide skeleton. 20-Guide bushing, 21-First snap ring, 22-Skeleton O-ring, 23-First skeleton oil seal, 24-Second skeleton oil seal, 25-Second snap ring, 26-Piston rod, 27-Retaining ring pad, 28-Top end cap, 29-Second one-way plug, 30-Coil winding, 31-Coil skeleton, 32-Lead plug, 33-First one-way plug, 34-Outer cylinder guide strip, 35-Wire groove, 36-Guide outer cylinder, 37-Winding lead, 38-Compensating piston O-ring, 39-Working cylinder, 40-Cap, 41-Lifting lug, 42-Bushing;

[0007] Figure 2 The figures show a bottom view and two sectional views of the adaptive dual-channel piston assembly of the present invention, wherein: 3-bottom end cap, 4-first positioning pin, 5-second positioning pin, 6-lower magnetic guide plate, 11-upper magnetic guide plate, 13-piston inner core, 14-piston rod O-ring, 15-shaft retaining ring, 16-outer lead wire, 26-piston rod, 27-retaining ring pad, 28-top end cap, 30-coil winding, 31-coil skeleton, 32-lead wire plug, 34-outer cylinder guide strip, 35-wire groove, 36-guide outer cylinder, 37-winding lead wire, 301-inner annular channel groove, 302-outer annular channel groove, 303-annular positioning boss, 304-extension boss;

[0008] Figure 3 The images show a front view and multiple sectional views of the piston core and related parts of the present invention, wherein: 7-first plug guide band, 8-first helical spring, 10-second helical spring, 12-second plug guide band, 13-piston core, 29-second one-way plug, 33-first one-way plug, 305-inner annular platform, 306-outer annular platform, 307-first annular channel groove, 308-second annular channel groove;

[0009] Figure 4This is a cross-sectional view of the adaptive dual-channel piston assembly of the present invention when it operates under a low damping force, wherein 3-bottom end cap, 7-first plug guide band, 8-first helical spring, 10-second helical spring, 12-second plug guide band, 13-piston inner core, 28-top end cap, 29-second one-way plug, 33-first one-way plug, 307-first annular channel groove, 308-second annular channel groove;

[0010] Figure 5 This is a cross-sectional view of the auxiliary flow channel in the adaptive dual-channel piston assembly of the present invention when it is working under a large damping force, wherein 3-bottom end cap, 7-first plug guide band, 8-first helical spring, 10-second helical spring, 12-second plug guide band, 13-piston inner core, 28-top end cap, 29-second one-way plug, 33-first one-way plug, 308-second annular channel groove;

[0011] Figure 6 This is a cross-sectional view of the auxiliary flow channel in the adaptive dual-channel piston assembly of the present invention when it is working under moderate damping force, wherein 3-bottom end cap, 7-first plug guide band, 8-first helical spring, 10-second helical spring, 12-second plug guide band, 13-piston inner core, 28-top end cap, 29-second one-way plug, 33-first one-way plug, 308-second annular channel groove. Detailed Implementation

[0012] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention. Furthermore, the technical features involved in the various embodiments of this invention described below can be combined with each other as long as they do not conflict with each other.

[0013] The adaptive dual-channel magnetorheological damper of this invention includes an adaptive dual-channel piston assembly. This assembly adds an adaptively adjustable auxiliary damping channel to the piston assembly of a traditional magnetorheological damper, allowing the damper to adaptively adjust the channel flow distribution according to the magnitude of the fluid damping force. When the damping force is low, the dual-channel magnetorheological damper of this invention has a dual-channel pressure relief function, thereby increasing the effective cross-sectional area of ​​the channels to reduce the flow-induced pressure difference (fluid pressure difference), and thus reducing the minimum damping force of the magnetorheological damper. It can also lock the auxiliary channel when the damping force is high, forming a single-channel flow concentration and increasing the maximum damping force of the magnetorheological damper. Correspondingly, the coil winding configuration of this invention enables synchronous control of the main damping channel and the auxiliary damping channel. The coordinated operation of the dual-channel structure and the coil winding gives the damper a wide adaptive adjustment range, thereby improving vehicle ride comfort and handling stability.

[0014] like Figure 1 As shown, the adaptive dual-channel magnetorheological damper provided by the present invention includes an adaptive dual-channel piston assembly, a working cylinder assembly, a compensating piston assembly, and a guide assembly. The outer cylinder guide band 34 of the adaptive dual-channel piston assembly forms a coaxial fit with the inner wall of the working cylinder assembly through surface contact, thereby placing the adaptive dual-channel piston assembly in the chamber inside the working cylinder 39 of the working cylinder assembly. Inside the working cylinder 39, in the upper chamber above the adaptive dual-channel piston assembly, the piston rod 26 of the adaptive dual-channel piston assembly coaxially passes through the guide assembly to achieve radial multi-degree-of-freedom constraint of the piston rod 26. In the lower chamber below the adaptive dual-channel piston assembly, a compensating piston assembly coaxial with the adaptive dual-channel piston assembly is provided; the compensating piston assembly divides the lower chamber into two chambers, wherein the chamber below the compensating piston assembly constitutes a volume compensation chamber.

[0015] The components of its assembly are as follows:

[0016] Working cylinder assembly: includes bushing 42, lifting lug 41, cover 40 and working cylinder 39. The lifting lug 41 is coaxially installed inside the bushing 42 and welded to the bottom of the cover 40. The cover 40 is fixed to the bottom of the working cylinder 39 by gas welding.

[0017] Compensating piston assembly: includes a floating compensating piston 1, a compensating piston O-ring 38, and a compensating piston guide band 2. The compensating piston O-ring 38 and the compensating piston guide band 2 are installed in corresponding grooves on the floating compensating piston 1.

[0018] The guide assembly includes a guide frame 19, a first frame oil seal 23, a second frame oil seal 24, a first retaining ring 21, a second retaining ring 25, a frame O-ring 22, a guide bushing 20, and a nylon buffer pad 18. The guide bushing 20 is installed between the first frame oil seal 23 and the guide frame 19. The first frame oil seal 23 and the second frame oil seal 24 are respectively fixed to the stepped grooves of the guide frame 19 via the first retaining ring 21 and the second retaining ring 25. The frame O-ring 22 is installed in a groove on the outer side of the guide frame 19. The nylon buffer pad 18 is fixed to a groove at the bottom of the guide frame 19 via a top boss structure.

[0019] Adaptive dual-channel piston assembly: including bottom end cap 3, top end cap 28, piston inner core 13, lower magnetic guide plate 6, first positioning pin 4, second positioning pin 5, coil frame 31, upper magnetic guide plate 11, coil winding 30, piston rod 26, piston rod O-ring 14, shaft retaining ring 15, retaining ring pad 27, guide outer cylinder 36, outer cylinder guide strip 34, first helical spring 8, second helical spring 10, first plug guide strip 7, second plug guide strip 12, first one-way plug 33, second one-way plug 29, winding lead wire 37, wire groove 35, lead wire plug 32, outer lead wire 16, and insulation covering layer 9.

[0020] The following describes the composition and operation of the adaptive dual-channel piston assembly.

[0021] like Figure 2 As shown, the adaptive dual-channel piston assembly includes: a guide outer cylinder 36, a piston inner core 13, a lead wire plug 32, a piston rod 26, a bottom end cap 3, a top end cap, and a coil frame 31. In the guide outer cylinder 36, the piston inner core 13 is the main body. The lead wire plug 32 is fixed in a groove at the bottom end of the piston inner core 13. The piston rod 26 is located in a groove at the top end of the piston inner core 13. The bottom end cap 3 is coaxially located on the lower end face of the piston inner core 13. The lower magnetic plate 6 is coaxially located on the upper end face of the bottom end cap 3. The coil frame 31 is coaxially located in a fixing groove on the inner surface of the lower magnetic plate 6 and the upper magnetic plate 11 for connection. The bottom end of the guide outer cylinder 36 is fixed to the bottom end cap 3 via its external thread, and the top end of the guide outer cylinder 36 is fixed to the top end cap 28 via its external thread. Alternatively, it can be fixed in other ways. The guide outer cylinder 36, bottom end cap 3, and top end cap 28 are assembled as described above to lock the internal parts of the adaptive dual-channel piston assembly.

[0022] The bottom end cap 3 is provided with two sets of circumferentially distributed annular channel grooves: an inner annular channel groove 301 and an outer annular channel groove 302. Since the material of the bottom end cap 3 is not magnetic, the magnetic field has little effect on the regulation of the magnetorheological fluid 17 flowing in the two sets of annular channel grooves of the bottom end cap 3. Therefore, the outer annular channel groove 302 needs a larger groove width to further reduce the minimum damping force of the damper. In order to realize the adaptive locking function of the auxiliary channel, the inner annular channel groove 301 needs a smaller groove width to ensure that the channel can be completely locked. Therefore, the groove width of the outer annular channel groove 302 is greater than the gap width of the main channel of the damper, and the groove width of the inner annular channel groove 301 is smaller than the gap width of the auxiliary channel of the damper. An annular positioning boss is provided on the upper surface of the bottom end cover 3. The inner annular channel groove 301 passes through the annular positioning boss 303 to ensure the coaxial assembly relationship between the piston inner core 13, the lower magnetic guide plate 6, and the upper magnetic guide plate 11. An extension boss 304 is provided on the lower surface of the bottom end cover 3. A wrench groove is provided on the outer circular surface of the extension boss 304 to facilitate threaded assembly. In addition, two positioning pin holes are provided on the upper surface between the two sets of annular channel grooves to prevent the winding lead 37 from being cut due to relative rotation during movement. A wire guide hole and a wire embedding groove are provided on the upper surface of the bottom end cover 3 at the opposite position of the horizontal line connecting the two positioning pin holes for the lead-out of the winding lead 37. The top end cover 28 and the bottom end cover 3 are provided with two sets of annular channel grooves, annular positioning bosses, and extension bosses with the same structure and function. The piston core 13 and the lower magnetic plate 6 are positioned by the inner and outer surfaces of the annular positioning boss 303 of the bottom end cover 3 and by the first positioning pin 4 and the second positioning pin 5, respectively. The upper end face of the lower magnetic plate 6, the lower end face of the upper magnetic plate 11, and the outer circular surface of the coil frame 31 axially arranged between the lower magnetic plate 6 and the upper magnetic plate 11 form a winding groove, and the coil winding 30 is wound in the aforementioned winding groove. The combination of the lower magnetic plate 6, the upper magnetic plate 11, the coil frame 31, and the coil winding 30 serves as a magnetic circuit control assembly. The coil frame 31 is not manufactured as a single piece with the lower magnetic plate 6 and the upper magnetic plate 11. The coil frame 31 is made of a non-magnetic material to reduce magnetic leakage in the magnetic circuit.

[0023] Similarly, the retaining ring 15 and the piston rod O-ring 14 are positioned by the inner and outer surfaces of the annular positioning boss of the top end cover 28. The piston rod O-ring 14 and the retaining ring 15 are respectively disposed in grooves at different positions in the lower circumferential direction of the piston rod 26 and in the axial downward direction (piston rod O-ring 14 is in the axial downward part, and retaining ring 15 is in the axial upward part), respectively used for sealing the piston inner core 13 and limiting the piston rod 26; the retaining ring pad 27 is disposed on the radial inner surface of the top end cover 28 and extends to contact the retaining ring 15; the bottom end cover 3 and the top end cover 28 are respectively fixed to the bottom and top of the guide outer cylinder 36 by threads or other means, and the outer cylinder guide band 34 is disposed in the guide groove on the outer surface of the guide outer cylinder 36.

[0024] like Figure 2 As shown, the outer surface of the magnetic circuit control assembly and the inner surface of the guide outer cylinder 36 form the main channel of the damper, and the position of the main channel of the damper corresponds to the outer annular channel groove of the bottom end cover 3 and the top end cover 28; the inner surface of the magnetic circuit control assembly and the outer surface of the piston inner core 13 form the auxiliary channel of the damper, and the position of the auxiliary channel of the damper corresponds to the inner annular channel groove of the bottom end cover 3 and the top end cover 28.

[0025] like Figure 2 and Figure 3 As shown, the piston inner core 13 has a double-stage fixed annular platform on its radial center and circumferential outer surface. The double-stage fixed annular platform includes an inner annular platform 305 and an outer annular platform 306. The inner annular platform 305 has multiple circumferentially distributed first annular channel grooves 307, and the outer annular platform 306 has multiple circumferentially distributed second annular channel grooves 308. The first annular channel grooves 307 are provided to ensure that the magnetorheological fluid 17 can flow smoothly through the middle position of the damper auxiliary channel under any circumstances. The second annular channel grooves 308 are provided to allow more fluid pressure to act on the first one-way plug 33 and the second one-way plug 29, facilitating the damping. The locking of the auxiliary channel of the damper is achieved by fixing the first helical spring 8 and the second helical spring 10 to the upper and lower end faces of the outer ring platform, respectively. The first one-way plug 33 and the second one-way plug 29 are fixed to the other side of the outer ring platform where the first helical spring 8 and the second helical spring 10 are not fixed. A number of circumferentially distributed annular channel grooves are correspondingly provided on the axial projection position of the first annular channel groove 307 of the inner ring platform 305 of the first one-way plug 33 and the second one-way plug 29. At this time, even if the first one-way plug 33 and the second one-way plug 29 are in contact with the double-stage fixed ring platform of the piston inner core 13, the flow of magnetorheological fluid 17 can be guaranteed. Furthermore, the first annular channel groove 307 has no overlapping area with the inner annular channel grooves of the bottom end cap 3 and the top end cap 28, thereby achieving auxiliary channel locking when the first one-way plug 33 or the second one-way plug 29 contacts the bottom end cap 3 or the top end cap 28; the first plug guide strip 7 and the second plug guide strip 12 are respectively disposed in the circumferential outer guide grooves of the first one-way plug 33 and the second one-way plug 29.

[0026] The functions of the inner and outer channels in this invention are interchangeable. The outer channel can be used as an auxiliary channel for the damper, and the inner channel as the main channel. In this case, the double-stage fixed ring platform needs to be placed on the inner surface of the guide outer cylinder 36, and other settings need to be adjusted accordingly to achieve the interchangeability of the main and auxiliary channels. The coil winding 30 is led outwards through two winding leads 37. The two winding leads 37 pass through two through holes in the through groove 35 made of insulating material on the lower magnetic guide plate 6, then through the through hole of the bottom end cover 3 to the lower end face of the bottom end cover 3, then through the embedded wire groove on the lower end face of the bottom end cover 3, and then welded to the metal connecting fork at the lower end of the lead plug 32. Finally, it is led outwards through the outer lead 16 at the upper end of the lead plug 32 via the inner through hole of the piston rod 26 to the outside of the damper. Both the coil winding 30 and the winding leads 37 are covered with insulating material to ensure that the coil winding 30 and the winding leads 37 will not short-circuit or be cut off.

[0027] like Figure 4 As shown, when the adaptive dual-channel piston assembly is subjected to downward displacement excitation, the damper enters the compression stroke. The fluid pressure pushes the first one-way plug 33 and the second one-way plug 29 upward, i.e., the first helical spring 8 is compressed and the second helical spring 10 is stretched. Without applying magnetic field excitation to the adaptive dual-channel piston assembly, the damper outputs its minimum damping force. At this time, the fluid pressure of the magnetorheological fluid 17 is relatively low, so the stretching stroke of the second helical spring 10 is insufficient to make the second one-way plug 29 contact the top end cap 28, and the compression stroke of the first helical spring 8 is also insufficient to make the first one-way plug 33 contact the double-stage fixed ring platform on the piston inner core 13 or cause the first helical spring 8 to fully coil. At this time, the auxiliary channel of the damper flows normally, and both the first annular channel groove 307 and the second annular channel groove 308 are open. The adaptive dual-channel piston assembly operates in a dual-channel pressure relief manner, which can obtain a larger effective channel cross-sectional area, thereby reducing the minimum damping force of the damper.

[0028] like Figure 5 As shown, when the damper is subjected to the maximum magnetic field excitation, the damper outputs the maximum damping force. At this time, the fluid pressure is relatively large, so the extension stroke of the second helical spring 10 can make the second one-way plug 29 contact with the top end cap 28, locking the auxiliary channel of the damper. At this time, the adaptive dual-channel piston assembly works in the form of single-channel flow concentration, thus obtaining a smaller effective cross-sectional area of ​​the channel, thereby increasing its maximum damping force.

[0029] like Figure 6As shown, when a low magnetic field excitation is applied to the damper, the extension stroke of the second helical spring 10 may be insufficient to make the second one-way plug 29 contact the top end cap 28. However, the compression stroke of the first helical spring 8 will make the first one-way plug 33 contact the double-stage fixed ring platform on the piston inner core 13 or cause the first helical spring 8 to be completely coiled. At this time, the second annular channel groove 308 of the outer ring platform of the piston inner core 13 will be locked, but the channel groove on the inner ring platform can still flow normally, so it will not affect the normal working state of the dual-channel pressure relief.

[0030] In this invention, when the adaptive dual-channel piston assembly is subjected to upward displacement excitation, the damper enters the stretching phase stroke, and its working principle is exactly the same as that of the compression phase. Therefore, the damper can achieve a bidirectional adjustment range expansion.

[0031] This invention provides an adaptive dual-channel magnetorheological damper, whose adaptive dual-channel piston assembly includes two damping channels: a normally open main channel and an adaptive auxiliary channel related to the damping force, formed by an elastic element and a one-way plug. A coil winding is arranged between the two channels to achieve synchronous control of the two channels. When the adaptive dual-channel piston assembly is subjected to forced vibration, this invention can adaptively adjust the channel flow distribution according to the magnitude of the generated fluid damping force. When the damping force is small, the minimum damping force of the magnetorheological damper is reduced by depressurization through the dual channels, and the maximum damping force of the magnetorheological damper is increased by flow concentration through the single channel when the damping force is large. This improves the damper's shock resistance and the adjustment range of the damping force. In addition, the excitation magnetic field generated by the coil winding located between the two damping channels can simultaneously pass perpendicularly through both the main and auxiliary channels, effectively improving the magnetic field utilization rate. This invention can be widely applied to the suspensions of various vehicle models to improve vehicle ride comfort and handling stability.

[0032] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit it. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all such modifications or substitutions should be covered within the scope of the claims of the present invention.

Claims

1. An adaptive dual-channel magnetorheological damper, characterized in that, The adaptive double-channel piston assembly, the working cylinder assembly, the compensation piston assembly and the guide assembly, the outer cylinder guide belt (34) of the adaptive double-channel piston assembly is in contact with the inner wall of the working cylinder assembly to form a coaxial fitting relationship, so that the adaptive double-channel piston assembly is arranged in the chamber inside the working cylinder (39) of the working cylinder assembly; the piston rod (26) of the adaptive double-channel piston assembly is coaxially arranged in the upper chamber above the adaptive double-channel piston assembly inside the working cylinder (39) to realize the radial multi-degree-of-freedom constraint of the piston rod (26); the compensation piston assembly coaxial with the adaptive double-channel piston assembly is arranged in the lower chamber below the adaptive double-channel piston assembly; the compensation piston assembly divides the lower chamber into two chambers, wherein the chamber below the compensation piston assembly constitutes a volume compensation chamber; the adaptive double-channel piston assembly comprises a damping main channel, a damping auxiliary channel and a coil winding, and the synchronous control of the damping main channel and the damping auxiliary channel is realized through the arrangement of the coil winding. The adaptive double-channel piston assembly comprises a guide outer cylinder (36), a piston inner core (13), a lead plug (32), a piston rod (26), a bottom end cover (3), a top end cover (28) and a coil former (31); the piston inner core (13) is arranged in the guide outer cylinder (36), the lead plug (32) is fixed in the groove at the bottom end of the piston inner core (13), the piston rod (26) is arranged in the groove at the top end of the piston inner core (13), the bottom end cover (3) is coaxially arranged at the lower end surface of the piston inner core (13), the lower magnetic plate (6) is coaxially arranged at the upper end surface of the bottom end cover (3), the coil former (31) is coaxially arranged in the fixed groove on the inner surfaces of the lower magnetic plate (6) and the upper magnetic plate (11) and is used for connecting the lower magnetic plate (6) and the upper magnetic plate (11); the bottom end of the guide outer cylinder (36) is fixed with the bottom end cover (3), and the top end is fixed with the top end cover (28). The bottom end cover (3) comprises an inner annular channel groove (301) and an outer annular channel groove (302), the groove width of the outer annular channel groove (302) is greater than the gap width of the damper main channel, and the groove width of the inner annular channel groove (301) is less than the gap width of the damper auxiliary channel; the upper end surface of the bottom end cover (3) is provided with an annular positioning boss (303), and the inner annular channel groove (301) penetrates through the annular positioning boss (303); the lower end surface of the bottom end cover (3) is provided with an extension boss (304); the top end cover (28) and the bottom end cover (3) are provided with two groups of annular channel grooves, annular positioning bosses (303) and extension bosses (304) which have the same structure and function; the piston inner core (13) and the lower magnetic plate (6) are positioned by the inner and outer surfaces of the annular positioning boss (303) of the bottom end cover (3) and the first positioning pin (4) and the second positioning pin (5), respectively; the piston inner core (13) and the upper magnetic plate (11) are positioned by the inner and outer surfaces of the annular positioning boss (303) of the top end cover (28). ​ The upper end surface of the lower magnetic conducting plate (6), the lower end surface of the upper magnetic conducting plate (11), and the outer circular surface of the coil former (31) axially arranged between the lower magnetic conducting plate (6) and the upper magnetic conducting plate (11) form a winding groove, and the coil winding (30) is wound in the winding groove; the combination of the lower magnetic conducting plate (6), the upper magnetic conducting plate (11), the coil former (31), and the coil winding (30) serves as a magnetic circuit regulation component; the coil former (31) is not made in one piece with the lower magnetic conducting plate (6) and the upper magnetic conducting plate (11), and is made of a non-magnetic conducting material to reduce the magnetic circuit leakage; The outer surface of the magnetic circuit regulation component and the inner surface of the guide outer cylinder (36) form an outer passage as the main passage of the damper, and the position of the main passage of the damper corresponds to the outer annular passage groove of the bottom end cover (3) and the top end cover (28); the inner surface of the magnetic circuit regulation component and the outer surface of the piston inner core (13) form an inner passage as the auxiliary passage of the damper, and the position of the auxiliary passage of the damper corresponds to the inner annular passage groove of the bottom end cover (3) and the top end cover (28); The radial middle part and the circumferential outer surface of the piston inner core (13) are provided with a double-stage fixing ring platform, which includes an inner ring platform (305) and an outer ring platform (306); the inner ring platform (305) is provided with a plurality of circumferentially distributed first annular passage grooves (307), and the outer ring platform (306) is provided with a plurality of circumferentially distributed second annular passage grooves (308); the first helical spring (8) and the second helical spring (10) are respectively fixed to the upper and lower end surfaces of the outer ring platform; the first one-way plug (33) and the second one-way plug (29) are respectively fixed to the other sides of the outer ring platforms not fixed with the first helical spring (8) and the second helical spring (10), and are respectively provided with a plurality of circumferentially distributed annular passage grooves at the axial projection positions of the first one-way plug (33) and the second one-way plug (29) on the first annular passage grooves (307) of the inner ring platform (305); the first annular passage grooves (307) have no intersection area with the inner annular passage grooves of the bottom end cover (3) and the top end cover (28); the first plug guide belt (7) and the second plug guide belt (12) are respectively arranged in the circumferential guide grooves of the first one-way plug (33) and the second one-way plug (29).

2. The adaptive dual-channel magnetorheological damper of claim 1, wherein, The shaft stop ring (15) and the piston rod O-ring (14) are respectively arranged in the grooves at different axial lower and upper positions of the lower part of the piston rod (26), and are respectively used for sealing the piston inner core (13) and limiting the piston rod (26); the stop ring pad (27) is arranged on the radial inner surface of the top end cover (28) and extends to contact the shaft stop ring (15).

3. The adaptive dual-channel magnetorheological damper of claim 1, wherein, The coil winding (30) is led out to the outside through two winding leads (37), which pass through two wire passing holes in the wire passing slots (35) on the lower magnetic conducting plate (6) respectively, then pass through the wire passing holes of the bottom end cover (3) to the lower end face of the bottom end cover (3), then are welded to the metal connecting prongs at the lower end of the lead plug (32) after passing through the wire embedding slots at the lower end face of the bottom end cover (3), and finally are led out to the outside of the damper through the outer lead (16) at the upper end of the lead plug (32) via the inner through hole of the piston rod (26).

4. The adaptive dual-channel magnetorheological damper of claim 3, wherein, Two positioning pin holes are arranged at the upper end face between the inner annular channel groove (301) and the outer annular channel groove (302), which are used to prevent the winding lead (37) from being cut off due to relative rotation during movement.

5. The adaptive dual-channel magnetorheological damper of claim 4, wherein, A wire passing hole and a wire embedding slot are arranged at the opposite position of the horizontal line connecting the upper end face of the bottom end cover (3) and the two positioning pin holes, which are used for leading out the winding lead (37).

6. The adaptive dual-channel magnetorheological damper of claim 3, wherein, The coil winding (30) and the winding lead (37) are both covered with insulating materials, so as to ensure that the coil winding (30) and the winding lead (37) will not be short-circuited or cut off.

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