Bidirectional asymmetric damping characteristic adjustable dual-channel magnetorheological damper

Abstract

The invention discloses a bidirectional asymmetric damping characteristic adjustable dual-channel magneto-rheological damper which comprises a magneto-rheological damper body. The magnetorheological damper body comprises a working cylinder, a piston assembly which is arranged in the working cylinder and divides the working cylinder into an upper cavity and a lower cavity, and a piston rod which is connected with the piston assembly and can drive the piston assembly to reciprocate; the piston assembly is provided with a first damping channel and a second damping channel which are used for communicating the upper cavity and the lower cavity, and the first damping channel is provided with a first normally-closed valve assembly which can be opened under the action of magnetorheological fluid from the lower cavity to the upper cavity. The second damping channel is a normally open channel and is provided with a second normally closed valve assembly which can be opened under the action of the magnetorheological fluid from the upper cavity to the lower cavity; according to the magneto-rheological damper, the adjustable and controllable range of the damping characteristic of the magneto-rheological damper can be improved under the limited size design space; and the product cost can be reduced, so that market popularization and application are facilitated.

Description

Technical Field

[0001] The invention belongs to the technical field of vibration suppression and relates to a two-channel magnetorheological damper with adjustable bidirectional asymmetric damping characteristics. Background Art

[0002] The magnetorheological damper with asymmetric damping characteristics is an intelligent vibration damping device designed based on the controllable rheological characteristics of magnetorheological fluid. Its core is to adjust the damping force through a magnetic field to show different responses in the compression and recovery stages, which is beneficial to meeting the dynamic control requirements under complex working conditions. Among them, the double-channel design scheme realizes the asymmetric damping characteristics by independently controlling the liquid flow paths in the compression and recovery stages of the magnetorheological damper and combining magnetic field zoning adjustment. However, the existing structures of double-channel magnetorheological dampers are basically single-valve control structures. During the compression stroke of the damper, the double channels are opened and the damper provides small damping; during the recovery stroke, the single channel works and the damper provides large damping. During the recovery stroke, the damping forces at low and high speeds can only be adjusted through an active control system, and the adjustment range is limited. Especially in the scenario where the design space of the damper size is limited, it is difficult to meet the working condition requirements; or extremely precise active control is required, which has extremely high requirements for the response time, making the system complexity high and the overall cost high. In addition, the existing structures of double-channel magnetorheological dampers mainly adopt the scheme of uniformly arranging slender fluid channel holes around the central hole of the iron core, which has the problems of complex structure, high machining accuracy requirements, and large machining difficulty, resulting in a high overall cost and being not conducive to market promotion and application; and in this scheme, when the design space of the magnetorheological damper size is limited, the adjustable range of the asymmetric damping characteristics is small, and it is also difficult to meet the application requirements of the scenario where the design space of the magnetorheological damper size is limited.

[0003] Therefore, how to solve the problems of the existing double-channel magnetorheological damper, such as the small adjustable range of damping characteristics under a limited size design space, being difficult to meet the application requirements of the scenario where the design space of the magnetorheological damper size is limited, and the high cost, has become a technical problem to be solved. Summary of the Invention

[0004] In view of this, the purpose of the present invention is to provide a two-channel magnetorheological damper with adjustable bidirectional asymmetric damping characteristics, aiming to improve the adjustable range of the damping characteristics of the magnetorheological damper under a limited size design space, so as to be beneficial to meeting the application requirements of the scenario where the design space of the magnetorheological damper size is limited; and to reduce the cost of the product, so as to be beneficial to market promotion and application.

[0005] To achieve the above object, the present invention provides the following technical solution: A dual-channel magnetorheological damper with adjustable bidirectional asymmetric damping characteristics, comprising a magnetorheological damper body, the magnetorheological damper body including a working cylinder, a piston assembly disposed in the working cylinder and separating the working cylinder into an upper chamber and a lower chamber, and a piston rod connected to the piston assembly and capable of driving the piston assembly to reciprocate;

[0006] The piston assembly is provided with a first damping channel and a second damping channel for communicating the upper chamber and the lower chamber. The first damping channel is provided with a first normally closed valve assembly that can be opened under the action of the magnetorheological fluid flowing from the lower chamber to the upper chamber. The second damping channel is a normally open channel and is provided with a second normally closed valve assembly that can be opened under the action of the magnetorheological fluid flowing from the upper chamber to the lower chamber.

[0007] Further, the piston assembly includes a piston sleeve slidably disposed in the working cylinder and a piston core coaxially fixed in the piston sleeve. An excitation coil is provided on the piston core. The second damping channel includes a second annular channel formed between the outer peripheral surface of the piston core and the inner peripheral surface of the piston sleeve.

[0008] Further, the end of the piston sleeve is provided with an annular positioning boss protruding radially outward. The annular positioning boss is slidably and sealingly fitted in the inner cavity of the working cylinder. The first damping channel includes a first annular channel formed between the outer peripheral surface of the piston sleeve and the inner peripheral surface of the working cylinder, and a first communication hole provided on the annular positioning boss for communicating the first annular channel with the upper chamber.

[0009] Further, the piston assembly further includes an upper end plate and a lower end plate respectively fixed to the upper and lower ends of the piston sleeve. The upper and lower ends of the piston core respectively abut against the upper end plate and the lower end plate. The second damping channel further includes a second communication hole provided on the lower end plate for communicating the second annular channel with the lower chamber, and a third communication hole provided on the upper end plate for communicating the second annular channel with the upper chamber.

[0010] Further, a radial limiting hole for radially limiting the piston core is provided on the upper end surface of the lower end plate, and the lower end of the piston core is installed in the radial limiting hole.

[0011] Further, the upper end surface of the upper end plate is provided with a first guiding boss protruding upward. The piston rod axially penetrates through the first guiding boss and the upper end plate and is fixedly connected to the piston core.

[0012] Further, the first normally-closed valve assembly includes a first annular valve plate slidably disposed axially on the first guiding boss, and a first return spring for pressing the first annular valve plate against the annular positioning boss during the return stroke of the piston assembly. A fourth communication hole aligned with the port of the third communication hole is provided on the first annular valve plate. When the first annular valve plate is closed, the first annular valve plate seals the first communication hole.

[0013] Further, a second guiding boss protruding downward is provided on the lower end surface of the lower end plate. The second normally-closed valve assembly includes a second annular valve plate slidably disposed axially on the second guiding boss, a spring seat fixed to the lower end of the second guiding boss, and a second return spring disposed between the spring seat and the second annular valve plate. A throttling hole is provided on the second annular valve plate. When the second annular valve plate is completely closed, the second annular valve plate partially blocks the second communication hole.

[0014] Further, a positioning stepped hole is provided at the lower end of the piston sleeve. The lower end plate is fixed in the positioning stepped hole, and the lower end surface of the spring seat is flush with the lower end surface of the piston sleeve. An annular limiting boss protruding radially inward is provided at the upper end of the piston sleeve, and the upper end of the upper end plate abuts against the annular limiting boss.

[0015] Further, there are two sets of excitation coils, and the winding directions of the two sets of excitation coils are opposite. An excitation coil mounting groove is provided on the piston core, and the excitation coils are arranged in the excitation coil mounting groove.

[0016] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0017] The bidirectional asymmetric damping characteristic adjustable dual-channel magnetorheological damper provided by the present invention can help improve the adjustable range of the damping characteristics of the magnetorheological damper under the limited size design space, so as to meet the application requirements of the scenario where the size design space of the magnetorheological damper is limited. It can help reduce the cost of the product, thus facilitating market promotion and application. Specifically, compared with the structure of the traditional single-valve controlled magnetorheological damper, in the structure of this magnetorheological damper, by using the first normally-closed valve assembly and the second normally-closed valve assembly to throttle and control the first damping channel and the second damping channel respectively, the damping force magnitudes during the return and compression processes can be separately and passively controlled by the corresponding valve assemblies under the action of the magnetorheological fluid. The structure is simple, which is easy to simplify the difficulty of the active control system, thereby reducing the production cost. And due to the setting of the second normally-closed valve assembly, it can increase the adjustable upper limit value of the damping force at low speeds and reduce the adjustable lower limit value of the damping force at high speeds during the return stroke, effectively broadening the regulation range of the damping force of the damper at different speeds, that is, under the same size design space, the adjustable range of the damping characteristics of the magnetorheological damper is larger, which is conducive to meeting the application requirements of the scenario where the size design space of the magnetorheological damper is limited.

[0018] Other advantages, objectives, and features of the present invention will, to some extent, be elaborated in the subsequent description, and to some extent, will be obvious to those skilled in the art based on the study of the following text, or can be learned from the practice of the present invention. The objectives and other advantages of the present invention can be achieved and obtained through the following description. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 It is a schematic cross-sectional structure diagram of an embodiment of the present invention;

[0020] Figure 2 is Figure 1 a partially enlarged schematic diagram at position A in

[0021] Figure 3 is Figure 1 a partially enlarged schematic diagram at position B in

[0022] Figure 4 It is an axonometric sectional view of the lower end plate of an embodiment of the present invention;

[0023] Figure 5 It is an axonometric sectional view of the upper end plate of an embodiment of the present invention;

[0024] Figure 6 It is an axonometric sectional view of the piston sleeve of an embodiment of the present invention;

[0025] Figure 7 It is an axonometric structure diagram of the overall structure of an embodiment of the present invention;

[0026] Figure 8 It is a damper indicator diagram at different speeds of the piston assembly when the active control current is 0 A;

[0027] Figure 9 It is a damper indicator diagram at different speeds of the piston assembly when the active control current is 0.2 A;

[0028] Reference numerals: 1 - working cylinder; 101 - upper chamber; 102 - lower chamber; 2 - piston rod; 3 - piston assembly; 3a - first damping channel; 3b - second damping channel; 301 - piston sleeve; 301a - first annular channel; 3011 - annular positioning boss; 3011a - first communication hole; 3012 - positioning step hole; 3013 - annular limiting boss; 302 - piston core; 302a - second annular channel; 302b - excitation coil mounting groove; 303 - excitation coil; 304 - upper end plate; 304a - third communication hole; 304b - first guiding boss; 305 - lower end plate; 305a - second communication hole; 305b - radial limiting hole; 305c - second guiding boss; 4 - first normally closed valve assembly; 401 - first annular valve disc; 401a - fourth communication hole; 402 - first return spring; 5 - second normally closed valve assembly; 501 - second annular valve disc; 501a - throttle hole; 502 - spring seat; 503 - second return spring; 6 - protective sleeve; 7 - lifting lug. Detailed implementation mode

[0029] The following uses specific specific examples to illustrate the implementation mode of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. The present invention can also be implemented or applied through other different specific implementation modes. Each detail in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of the present invention. It should be noted that the drawings provided in the following embodiments are only used to illustrate the basic concept of the present invention. Without conflict, the following embodiments and the features in the embodiments can be combined with each other.

[0030] Please refer to Figure 1-7 , in this embodiment, a dual-channel magnetorheological damper with adjustable bidirectional asymmetric damping characteristics is disclosed, including a magnetorheological damper body. The magnetorheological damper body includes a working cylinder 1, a piston assembly 3 disposed in the working cylinder 1 and separating the working cylinder 1 into an upper chamber 101 and a lower chamber 102, and a piston rod 2 connected to the piston assembly 3 and capable of driving the piston assembly 3 to reciprocate; the piston assembly 3 is provided with a first damping channel 3a and a second damping channel 3b for communicating the upper chamber 101 and the lower chamber 102. The first damping channel 3a is provided with a first normally closed valve assembly 4 that can be opened under the action of the magnetorheological fluid from the lower chamber 102 to the upper chamber 101. The second damping channel 3b is a normally open channel and is provided with a second normally closed valve assembly 5 that can be opened under the action of the magnetorheological fluid from the upper chamber 101 to the lower chamber 102. Here, the "upper" and "lower" in the upper chamber 101 and the lower chamber 102 are based on the attached Figure 1The vertical direction therein. It can be understood that the magnetorheological fluid is provided in the working cylinder 1. The process of the magnetorheological fluid from the lower chamber 102 to the upper chamber 101 corresponds to the downward compression stroke of the damper, and the process of the magnetorheological fluid from the upper chamber 101 to the lower chamber 102 corresponds to the upward recovery stroke of the damper. In the compression stroke, the first normally closed valve assembly 4 is opened, and the first damping channel 3a and the always-open second damping channel 3b work in a dual-channel manner to provide a small damping. In the recovery stroke, the first normally closed valve assembly 4 is closed, and the always-open second damping channel 3b works in a single-channel manner to provide a large damping. Since the second normally closed valve assembly 5 is provided, it can remain closed at low speeds to increase the adjustable upper limit value of the damping force at low speeds, and open at high speeds to reduce the adjustable lower limit value of the damping force at high speeds.

[0031] The two-way asymmetric damping characteristic adjustable dual-channel magnetorheological damper provided in the above structure can help to improve the adjustable range of the damping characteristics of the magnetorheological damper under the limited size design space, so as to meet the application requirements of the scenario with limited size design space of the magnetorheological damper; it can help to reduce the cost of the product, so as to facilitate the market promotion and application. Specifically, compared with the traditional single-valve controlled magnetorheological damper structure, in this magnetorheological damper structure, by using the first normally closed valve assembly 4 and the second normally closed valve assembly 5 to perform unidirectional throttling control on the first damping channel 3a and the second damping channel 3b respectively, the damping force magnitudes in the recovery and compression processes can be separately and passively controlled by the corresponding valve assemblies under the action of the magnetorheological fluid. The structure is simple, which is easy to simplify the difficulty of the active control system, thus reducing the production cost; and due to the setting of the second normally closed valve assembly 5, it can realize the increase of the adjustable upper limit value of the damping force at low speeds and the reduction of the adjustable lower limit value of the damping force at high speeds during the recovery stroke, effectively broadening the adjustable range of the damping force of the damper at different speeds, that is, under the same size design space, the adjustable range of the damping characteristics of the magnetorheological damper is larger, which is conducive to meeting the application requirements of the scenario with limited size design space of the magnetorheological damper.

[0032] In this embodiment, the piston assembly 3 includes a piston sleeve 301 slidably disposed in the working cylinder 1 and a piston core 302 coaxially fixed in the piston sleeve 301. An excitation coil 303 is provided on the piston core 302. The second damping channel 3b includes a second annular channel 302a formed between the outer peripheral surface of the piston core 302 and the inner peripheral surface of the piston sleeve 301. The piston core 302 is usually a cylindrical iron core. An excitation coil 303 is provided on the iron core to generate a magnetic field to realize the active adjustment of the magnetorheological fluid damping characteristics. In order to facilitate wire threading, wire threading holes are respectively provided on the iron core and the piston rod 2 along the central axis direction. By forming the second annular channel 302a between the outer peripheral surface of the piston core 302 and the inner peripheral surface of the piston sleeve 301 to form the second damping channel 3b, it is possible to avoid directly opening slender damping channel holes on the piston core 302, effectively reducing the processing difficulty and the requirement for processing accuracy, so as to further reduce the production cost of the damper and be more conducive to the market promotion and application.

[0033] In this embodiment, an annular positioning boss 3011 protruding radially outward is provided at the end of the piston sleeve 301, and the annular positioning boss 3011 is slidably and sealingly arranged in the inner cavity of the working cylinder 1; the first damping channel 3a includes a first annular channel 301a formed between the outer peripheral surface of the piston sleeve 301 and the inner peripheral surface of the working cylinder 1, and a first communication hole 3011a provided on the annular positioning boss 3011 to communicate the first annular channel 301a with the upper cavity 101. Specifically, here the annular positioning boss 3011 is located at the upper end of the piston sleeve 301, and an annular sealing groove is provided on the outer peripheral surface of the annular positioning boss 3011 to complete the dynamic seal with the inner cavity wall surface of the working cylinder 1. The first communication holes 3011a are arranged in a circumferential and evenly distributed manner as multiple. By integrally arranging the annular positioning boss 3011 on the piston sleeve 301, not only can the movement guidance of the piston sleeve 301 be realized, but also it is beneficial to form the first annular channel 301a, which simplifies the structure of the first damping channel 3a, is beneficial to the processing of the first damping channel 3a, reduces the processing precision requirements for the first damping channel 3a, thereby can be beneficial to further reducing the production cost of the damper, and is more beneficial to the market promotion and application. At the same time, there is no need to set an additional movement guiding structure, and the overall axial dimension is small, which is beneficial to ensuring that the piston assembly 3 has a sufficient movement stroke under a limited length space. Since the first normally closed valve assembly 4 is used to control the first damping channel 3a, and the first annular channel 301a is located radially outside the second annular channel 302a in space, then under the same radial dimension, controlling the opening and closing of the first damping channel 3a can make the damping characteristics of the compression stroke and the recovery stroke of the damper differ more, that is, it is beneficial to further improve the regulation range of the damping force under a limited space dimension, and is more beneficial to meeting the application requirements of the magnetic rheological damper in the scenario of limited size design space, so that the overall axial and radial dimensions can be more compact.

[0034] In this embodiment, the piston assembly 3 further includes an upper end plate 304 and a lower end plate 305 respectively and fixedly disposed at the upper and lower ends of the piston sleeve 301. The upper and lower ends of the piston core 302 respectively abut against the upper end plate 304 and the lower end plate 305. The second damping channel 3b further includes a second communication hole 305a disposed on the lower end plate 305 to communicate the second annular channel 302a with the lower chamber 102, and a third communication hole 304a disposed on the upper end plate 304 to communicate the second annular channel 302a with the upper chamber 101. Both the upper end plate 304 and the lower end plate 305 are made of magnetic isolation plates to form a better magnetic field environment. The second communication holes 305a are uniformly arranged in a circumferential edge of the lower end plate 305 as a plurality of them, and the third communication holes 304a are uniformly arranged in a circumference of the upper end plate 304 as a plurality of them. Here, the second communication hole 305a is a straight through hole arranged axially, and the third communication hole 304a is an inclined through hole arranged obliquely with respect to its own axis. By providing the upper end plate 304 and the lower end plate 305, it is beneficial to realize the assembly limit of the piston core 302 and ensure the installation stability and assembly convenience of the piston core 302. By providing the second communication hole 305a and the third communication hole 304a, the force value change of the magnetorheological damper can be made smoother and no sudden change will occur.

[0035] In this embodiment, a radial limiting hole 305b for radially limiting the piston core 302 is provided on the upper end surface of the lower end plate 305, and the lower end of the piston core 302 is installed in the radial limiting hole 305b. By providing the radial limiting hole 305b on the lower end plate 305, it is beneficial to ensure the assembly accuracy of the piston core 302 and improve the product quality.

[0036] In this embodiment, a first guiding boss 304b protruding upward is provided on the upper end surface of the upper end plate 304. The piston rod 2 axially penetrates through the first guiding boss 304b and the upper end plate 304 and then is fixedly connected to the piston core 302. By providing the first guiding boss 304b, it can play a role in guiding the piston rod 2 and strengthening the strength, so as to reduce the working shaking problem caused by too large ratio of the shaft length to the shaft diameter.

[0037] In this embodiment, the first normally-closed valve assembly 4 includes a first annular valve disc 401 slidably disposed axially on the first guiding boss 304b, and a first return spring 402 that abuts the first annular valve disc 401 against the annular positioning boss 3011 during the return stroke of the piston assembly 3. A fourth communication hole 401a is provided on the first annular valve disc 401 and is aligned with the port of the third communication hole 304a. When the first annular valve disc 401a is closed, the first annular valve disc 401a closes the first communication hole 3011a. Specifically, the first annular valve disc 401 is movably sleeved on the first guiding boss 304b, and the first return spring 402 is a conical spring or a tower spring with a large compression amount. A tower spring installation groove is provided on the first guiding boss 304b, the small end of the tower spring is clamped in the tower spring installation groove, and the large end of the tower spring presses on the first annular valve disc 401. By providing the fourth communication hole 401a, the second damping channel 3b can be kept in a normally open state. The first normally-closed valve assembly 4 in this structural design is simple and reliable, which is conducive to cost control.

[0038] In this embodiment, a second guiding boss 305c protruding downward is provided on the lower end surface of the lower end plate 305. The second normally-closed valve assembly 5 includes a second annular valve disc 501 slidably disposed axially on the second guiding boss 305c, a spring seat 502 fixed to the lower end of the second guiding boss 305c, and a second return spring 503 disposed between the spring seat 502 and the second annular valve disc 501. A throttle hole 501a is provided on the second annular valve disc 501. When the second annular valve disc 501 is completely closed, the second annular valve disc 501 partially blocks the second communication hole 305a. Specifically, the second return spring 503 is a helical compression spring. The throttle holes 501a are uniformly distributed along the inner edge of the second annular valve disc 501. The outer diameter of the second annular valve disc 501 is smaller than the outer diameter of the lower end plate 305. When closed, it partially blocks the second communication hole 305a in the radial direction, so that the second damping channel 3b can be kept in a normally open state. During the return stroke, when the piston assembly 3 moves upward relative to the damper cylinder at a low speed, the impact of the magnetorheological fluid on the second annular valve disc 501 is not sufficient to push open the second annular valve disc 501, increasing the damping force of the damper at low speeds and broadening the upper limit value of the adjustable range of the damping force at low speeds. When the piston assembly 3 moves upward relative to the damper cylinder at a high speed, the second annular valve disc 501 is opened under the impact of the magnetorheological fluid, and the flow area increases, reducing the damping force of the damper at high speeds and broadening the lower limit value of the adjustable range of the damping force at high speeds, thereby realizing the regulation of the damper force value under different speed conditions. The second normally-closed valve assembly 5 in this structural design is simple and reliable, which is conducive to cost control.

[0039] In this embodiment, a positioning step hole 3012 is provided at the lower end of the piston sleeve 301, and the lower end plate 305 is fixedly arranged in the positioning step hole 3012; an annular limiting boss 3013 protruding radially inward is provided at the upper end of the piston sleeve 301, and the upper end of the upper end plate 304 abuts against the annular limiting boss 3013. Specifically, the lower end surface of the second guiding boss 305c is flush with the lower end surface of the piston sleeve 301. By providing the positioning step hole 3012 and the annular limiting boss 3013, it is beneficial to realize the stable and reliable installation of the lower end plate 305 and the upper end plate 304, ensure the assembly accuracy, improve the product quality, and at the same time, it is beneficial to save the axial dimension and ensure the piston stroke.

[0040] In this embodiment, there are two sets of exciting coils 303, and the winding directions of the two sets of exciting coils 303 are opposite; an exciting coil mounting groove 302b is provided on the piston core 302, and the exciting coils 303 are arranged in the exciting coil mounting groove 302b. Specifically, a central axis opening is provided on the piston core 302 to facilitate the threading of the exciting coils 303, and the top of the piston core 302 is threadedly connected to the piston rod 2. By providing two sets of exciting coils 303 to generate two opposite magnetic fields, and by providing the exciting coil mounting groove 302b, it is beneficial to ensure the structural compactness.

[0041] In this embodiment, a rigid protective sleeve 6 is further provided outside the working cylinder 1 to improve the service durability of the damper; lifting lugs 7 are respectively provided at the bottom end of the working cylinder 1 and the top end of the piston rod 2 to improve the use convenience.

[0042] To facilitate a better understanding of the damping characteristics of the damper in this embodiment by those skilled in the art, here in the attached Figure 8 and attached Figure 9 of the specification drawings, the indicator diagrams of the damper when the active control current is 0 A and 0.2 A are respectively provided at different moving speeds of the piston assembly 3. In the attached Figure 8 and attached Figure 9 , different colors respectively correspond to different running speeds of the piston assembly 3. Above the coordinate origin (in the positive direction of the force value axis) corresponds to the recovery stroke of the piston assembly 3, and below the coordinate origin (in the negative direction of the force value axis) corresponds to the compression stroke of the piston assembly 3; the origin of the displacement axis corresponds to the midpoint position of the compression or recovery stroke of the piston assembly. From the attached Figure 8 and attached Figure 9It can be clearly seen that in this embodiment, the compression stroke damper provides a small damping force, while the rebound stroke provides a large damping force. At the same running speed of the piston assembly 3, the force values exhibit obvious asymmetric characteristics. Especially after applying active current (such as changing from 0 A to 0.2 A), at the same positions in the rebound stroke and the compression stroke, the force values have a greater difference. In the rebound stroke, at different speeds, the force values show a large difference, effectively broadening the regulation range of the damping force of the damper at different speeds.

[0043] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit them. Although the present invention has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that the technical solutions of the present invention can be modified or equivalently replaced without departing from the purpose and scope of the technical solutions of the present invention, and they should all be covered within the scope of the claims of the present invention.

Claims

1. A two-way asymmetric damping characteristic adjustable two-channel magnetorheological damper, characterized in that: It includes a magnetorheological damper body, and the magnetorheological damper body includes a working cylinder (1), a piston assembly (3) disposed in the working cylinder (1) and separating the working cylinder (1) into an upper chamber (101) and a lower chamber (102), and a piston rod (2) connected to the piston assembly (3) and capable of driving the piston assembly (3) to reciprocate; The piston assembly (3) is provided with a first damping channel (3a) and a second damping channel (3b) for communicating the upper chamber (101) and the lower chamber (102). The first damping channel (3a) is provided with a first normally closed valve assembly (4) that can be opened under the action of magnetorheological fluid flowing from the lower chamber (102) to the upper chamber (101). The second damping channel (3b) is a normally open channel and is provided with a second normally closed valve assembly (5) that can be opened under the action of magnetorheological fluid flowing from the upper chamber (101) to the lower chamber (102).

2. The dual-channel magneto-rheological damper with adjustable bidirectional asymmetric damping characteristics according to claim 1, wherein: The piston assembly (3) includes a piston sleeve (301) slidably disposed in the working cylinder (1) and a piston core (302) coaxially fixed in the piston sleeve (301). An excitation coil (303) is provided on the piston core (302). The second damping channel (3b) includes a second annular channel (302a) formed between the outer peripheral surface of the piston core (302) and the inner peripheral surface of the piston sleeve (301).

3. The bidirectional asymmetric damping characteristic adjustable dual-channel magnetorheological damper according to claim 2, characterized in that: An annular positioning boss (3011) protruding radially outward is provided at the end of the piston sleeve (301), and the annular positioning boss (3011) is slidably and sealingly fitted in the inner cavity of the working cylinder (1); The first damping channel (3a) includes a first annular channel (301a) formed between the outer peripheral surface of the piston sleeve (301) and the inner peripheral surface of the working cylinder (1), and a first communication hole (3011a) provided on the annular positioning boss (3011) for communicating the first annular channel (301a) with the upper chamber (101).

4. The two-way asymmetric damping characteristic adjustable two-channel magnetorheological damper according to claim 3, characterized in that: The piston assembly (3) further includes an upper end plate (304) and a lower end plate (305) respectively fixed to the upper and lower ends of the piston sleeve (301). The upper and lower ends of the piston core (302) respectively abut against the upper end plate (304) and the lower end plate (305); The second damping channel (3b) further includes a second communication hole (305a) provided on the lower end plate (305) for communicating the second annular channel (302a) with the lower chamber (102), and a third communication hole (304a) provided on the upper end plate (304) for communicating the second annular channel (302a) with the upper chamber (101).

5. The two-way asymmetric damping characteristic adjustable two-channel magnetorheological damper according to claim 4, characterized in that: A radial limiting hole (305b) for radially limiting the piston core (302) is provided on the upper end surface of the lower end plate (305), and the lower end of the piston core (302) is installed in the radial limiting hole (305b).

6. The bi-directional asymmetric damping characteristic adjustable two-channel magneto-rheological damper according to claim 4, wherein: The upper end surface of the upper end plate (304) is provided with an upwardly protruding first guiding boss (304b). The piston rod (2) axially penetrates through the first guiding boss (304b) and the upper end plate (304) and is fixedly connected to the piston core (302).

7. The two-way asymmetric damping characteristic adjustable two-channel magnetorheological damper according to claim 6, wherein: The first normally closed valve assembly (4) includes a first annular valve disc (401) slidably arranged axially on the first guiding boss (304b), and a first return spring (402) for pressing the first annular valve disc (401) against the annular positioning boss (3011) during the return stroke of the piston assembly (3). A fourth communication hole (401a) aligned with the port of the third communication hole (304a) is provided on the first annular valve disc (401); when the first annular valve disc (401a) is closed, the first annular valve disc (401a) closes the first communication hole (3011a).

8. The bi-directional asymmetric damping characteristic adjustable two-channel magneto-rheological damper according to claim 4, wherein: A second guiding boss (305c) protruding downward is provided on the lower end surface of the lower end plate (305); The second normally closed valve assembly (5) includes a second annular valve disc (501) slidably arranged axially on the second guiding boss (305c), a spring seat (502) fixed to the lower end of the second guiding boss (305c), and a second return spring (503) arranged between the spring seat (502) and the second annular valve disc (501). A throttle hole (501a) is provided on the second annular valve disc (501), and when the second annular valve disc (501) is fully closed, the second annular valve disc (501) partially blocks the second communication hole (305a).

9. The bidirectional asymmetric damping characteristic adjustable two-channel magnetorheological damper according to claim 8, wherein: A positioning stepped hole (3012) is provided at the lower end of the piston sleeve (301), and the lower end plate (305) is fixed in the positioning stepped hole (3012); An annular limiting boss (3013) protruding radially inward is provided at the upper end of the piston sleeve (301), and the upper end of the upper end plate (304) abuts against the annular limiting boss (3013).

10. The dual-channel magneto-rheological damper with adjustable bidirectional asymmetric damping characteristics according to claim 2, wherein: There are two sets of exciting coils (303), and the winding directions of the two sets of exciting coils (303) are opposite; An exciting coil mounting groove (302b) is provided on the piston core (302), and the exciting coils (303) are arranged in the exciting coil mounting groove (302b).

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