CN115370693A

CN115370693A - Magnetorheological shock absorber with wide damping adjustable range and magnetorheological suspension

Info

Publication number: CN115370693A
Application number: CN202211174247.6A
Authority: CN
Inventors: 徐涵欧
Original assignee: Shenzhen Chaoshang Technology Co ltd
Current assignee: Shenzhen Chaoshang Technology Co ltd
Priority date: 2022-09-26
Filing date: 2022-09-26
Publication date: 2022-11-22

Abstract

The present disclosure describes a magnetorheological damper and a magnetorheological suspension having a wide damping adjustable range, the damper comprising: an outer cylinder body; an inner cylinder body; the first base and the second base are respectively wound on a first coil in the first base and a second coil in the second base; a piston head slidably disposed in the inner cylinder; one end of the piston rod is connected with the piston head, and the other end of the piston rod extends out of the outer cylinder body; and the magnetorheological fluid is filled in the working cavity, wherein the piston head comprises a piston main body, a first leakage flow through hole and a second leakage flow through hole which are formed in the piston main body, a first pressure release valve arranged at one end of the piston main body and a second pressure release valve arranged at the other end of the piston main body. In this case, when the frequency of movement of the piston head exceeds the limit, the first relief valve and the second relief valve operate alternately and cause the first drain hole and the second drain hole to open alternately, whereby the viscous damping due to the velocity can be reduced, and the controllable range of the output damping can be increased.

Description

Magnetorheological shock absorber with wide damping adjustable range and magnetorheological suspension

Technical Field

The present disclosure generally relates to the field of intelligent manufacturing equipment industry, and more particularly to a magnetorheological damper and a magnetorheological suspension having a wide damping adjustable range.

Background

The magneto-rheological shock absorber is a semi-active shock absorber taking a magneto-rheological intelligent material as a medium, and can achieve the optimal vibration isolation effect by adaptively adjusting self parameters (such as damping or rigidity) in real time under the drive of a small current according to the change of an external environment. The semi-active magneto-rheological shock absorber has the advantages of low energy consumption, strong controllability, high response speed, good reliability and the like, so that the semi-active magneto-rheological shock absorber has a huge application prospect in the buffer shock absorption of the intelligent suspension.

However, in the existing magnetorheological damper, under high-frequency reciprocating motion, the unadjustable viscous damping force caused by the speed is obviously increased, so that the change of the whole output damping force of the damper is limited when the coulomb damping is regulated (the output damping of the damper is the sum of the coulomb damping and the viscous damping), the adjustable range is lowered, and the application range and the application effect of the magnetorheological intelligent suspension are greatly reduced.

Disclosure of Invention

The present disclosure has been made in view of the above-mentioned state of the art, and an object thereof is to provide a magnetorheological damper and a magnetorheological suspension having a wide damping adjustable range.

To this end, the present disclosure provides in a first aspect a magnetorheological damper having a wide damping adjustable range, comprising: an outer cylinder body; the inner cylinder body is arranged in the working cavity in the outer cylinder body and is fixedly connected with the outer cylinder body; the first base and the second base are arranged at two ends of the outer cylinder body, and a first coil in the first base and a second coil in the second base are wound respectively; a piston head slidably disposed in the inner cylinder; one end of the piston rod is connected with the piston head, and the other end of the piston rod extends out of the outer cylinder body; and fill in the magnetorheological suspensions of working chamber, wherein, the piston head includes the piston main part, open first earial drainage through-hole and second earial drainage through-hole in the piston main part, install the first relief valve of piston main part one end and install the second relief valve of the piston main part other end, the working chamber quilt first cavity and second cavity are separated to the piston head, the outer cylinder body first base the second base and the damping channel that the inner cylinder body formed communicates respectively first cavity with the second cavity.

In the disclosure, a first leakage through hole and a second leakage through hole are formed in a piston main body, and a first pressure release valve for controlling the conduction of the first leakage through hole and a second pressure release valve for controlling the conduction of the second leakage through hole are correspondingly arranged at two ends of the piston main body, so that when the piston rod drives the movement speed or the movement frequency of a piston head in a working cavity to reach a certain threshold value, the nonadjustable viscous damping force caused by the flow speed of magnetorheological fluid can be regulated and controlled through the first pressure release valve and the second pressure release valve.

In addition, in the magnetorheological shock absorber according to the first aspect of the present disclosure, optionally, when the motion frequency of the piston rod driving the piston main body is less than a preset threshold, the first pressure release valve blocks the first leakage through hole and unblocks the second leakage through hole, and the second pressure release valve blocks the second leakage through hole and unblocks the first leakage through hole; when the movement frequency of the piston rod driving the piston main body is larger than the preset threshold value, the first pressure release valve is used for dredging the first drainage through hole, or the second pressure release valve is used for dredging the second drainage through hole. From this, can make first relief valve and second relief valve control respectively switching on of first earial drainage through-hole and second earial drainage through-hole conveniently according to the frequency of motion size of piston main part.

In addition, in the magnetorheological shock absorber according to the first aspect of the present disclosure, optionally, the first pressure relief valve includes a first plug movably disposed at one end of the piston main body, a first fixing plate fixedly connected to one end of the piston rod, and a first elastic element for connecting the first plug and the first fixing plate; the second pressure release valve comprises a second plug movably arranged at the other end of the piston main body, a second fixing plate fixedly connected to the other end of the piston rod, and a second elastic element used for connecting the second plug and the second fixing plate. Therefore, the movement control of the first plug and the second plug can be conveniently realized.

In addition, in the magnetorheological shock absorber according to the first aspect of the disclosure, optionally, when the piston rod drives the piston main body to move into the working chamber at a movement frequency greater than the preset threshold, the pressure in the first chamber causes the first plug of the first pressure release valve to plug the first flow release through hole, and the second plug of the second pressure release valve unblocks the second flow release through hole; when the piston rod drives the piston main body to move towards the outside of the working cavity under the movement frequency larger than the preset threshold value, the pressure in the second cavity enables the second plug of the second pressure release valve to plug the second flow release through hole, and meanwhile, the first plug in the first pressure release valve dredges the first flow release through hole. From this, can conveniently make first relief valve and second relief valve control respectively according to the motion frequency size and the direction of motion of piston main part and lead to of first earial drainage through-hole and second earial drainage through-hole.

In addition, in the magnetorheological shock absorber according to the first aspect of the present disclosure, optionally, when the piston rod drives the piston main body to move toward the working chamber at a movement frequency greater than the preset threshold, the magnetorheological fluid in the first chamber flows into the second chamber from the damping channel and the second drain through hole, respectively; when the piston rod drives the piston main body to move towards the outside of the working cavity under the movement frequency larger than the preset threshold value, magnetorheological fluid in the second cavity flows into the first cavity from the damping channel and the first leakage through hole respectively. Therefore, when the piston rod drives the piston main body to move towards the working cavity or outside under the movement frequency larger than the preset threshold value, the magnetorheological fluid can conveniently circulate in the first cavity and the second cavity through the damping channel and the first leakage through hole or the second leakage through hole.

In addition, in the magnetorheological damper relating to the first aspect of the present disclosure, optionally, the first plug is provided with an opening for dredging the second drain hole. From this, can conveniently dredge second earial drainage through-hole.

In addition, in the magnetorheological damper according to the first aspect of the present disclosure, optionally, two ends of the inner cylinder are respectively provided with a first "convex" shaped port and a second "convex" shaped port, the first base is provided with a first groove matching the first "convex" shaped port, and the second base is provided with a second groove matching the second "convex" shaped port. Therefore, the damping channel can be conveniently formed.

In addition, in the magnetorheological shock absorber according to the first aspect of the present disclosure, optionally, a compensation air bag is further included, which is disposed at one end of the first chamber of the outer cylinder. Therefore, the volume change of the working cavity can be conveniently compensated by gas.

In addition, in the magnetorheological damper according to the first aspect of the disclosure, optionally, the first bleed through holes are a plurality of arc-shaped through holes that are provided in the outer periphery of the piston main body and are located in the same circumference, and the second bleed through holes are a plurality of arc-shaped through holes that are provided in the inner periphery of the piston main body and are located in the same circumference. Thereby, the first drain through hole and the second drain through hole can be formed.

In addition, in the magnetorheological damper according to the first aspect of the present disclosure, optionally, the first coil is wound in a first base space formed by the first base, and the second coil is wound in a second base space formed by the second base. Therefore, the first coil and the second coil can be protected conveniently.

The second aspect of the present disclosure also provides a magnetorheological suspension, which includes the magnetorheological damper.

According to the magnetorheological damper and the magnetorheological suspension, when the viscous resistance force caused by the overhigh flowing speed of the magnetorheological fluid in the damping channel is overlarge, the magnetorheological damper and the magnetorheological suspension with wide damping adjustable range can be adjusted and controlled.

Drawings

Embodiments of the present disclosure will now be explained in further detail, by way of example only, with reference to the accompanying drawings, in which:

fig. 1 is a schematic view illustrating an overall structure of a magnetorheological shock absorber having a wide damping adjustable range according to an embodiment of the present disclosure.

Fig. 2 is a schematic view showing the structure of a piston head according to an embodiment of the present disclosure.

Fig. 3 is a schematic view showing one example of the flowing direction of a magnetorheological fluid according to an embodiment of the present disclosure.

Fig. 4 is a schematic view showing another example of the flowing direction of the magnetorheological fluid according to the embodiment of the present disclosure.

Fig. 5 is a schematic structural view showing a piston main body according to an embodiment of the present disclosure.

Fig. 6 is a schematic structural view illustrating a first plug fitted to a piston body according to an embodiment of the present disclosure.

Fig. 7 is a schematic structural view showing a base and an inner cylinder according to an embodiment of the present disclosure.

Fig. 8 is a schematic diagram illustrating a magnetic path formed by the coil according to the embodiment of the present disclosure.

Fig. 9 is a schematic diagram showing functional modules of a magnetorheological suspension according to an embodiment of the present disclosure.

A schematic diagram illustrating the functional blocks of a magnetorheological suspension control system according to an embodiment of the present disclosure is shown at 10.

Description of the symbols:

1 … external cylinder, 2 … internal cylinder, 3 … first base, 4 … second base, 5 … piston head, 6 … piston rod, 7 … magnetorheological fluid, 8 … compensation bladder, 10 … working chamber, 11 … external cylinder, 12 … first endcap, 13 … second endcap, 21 … first "male" font port, 22 … second "male" font port, 31 58 zxft 6258 first coil, 32 first groove, 42 second groove, 41 … second coil, 51 … piston body, 52 … first relief valve, 53 … second relief valve, 102 … damping channel, 110 … first chamber, 120 … second chamber, 511 … first relief through hole, 512 … second relief through hole, 521 … first plug, 521 … first fixing plate, 523 … first resilient element, 531 … second plug, 532 … second fixing plate, 533 … second resilient element, 625211 … open hole.

Detailed Description

All references cited in this disclosure are incorporated by reference in their entirety as if fully set forth. Unless defined otherwise, technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure belongs. General guidance for many of the terms used in this application is provided to those skilled in the art. Those of skill in the art will recognize many methods and materials similar or equivalent to those described herein that can be used in the practice of the present disclosure. Indeed, the disclosure is in no way limited to the methods and materials described.

Hereinafter, preferred embodiments of the present disclosure will be described in detail with reference to the accompanying drawings. In the following description, the same components are denoted by the same reference numerals, and redundant description thereof is omitted. In addition, the drawings are only schematic, and the ratio of the sizes of the components to each other, the shapes of the components, and the like may be different from actual ones.

It is noted that the terms "comprises," "comprising," and "having," and any variations thereof, in this disclosure, for example, a process, method, system, article, or apparatus that comprises or has a list of steps or elements is not necessarily limited to those steps or elements expressly listed, but may include or have other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.

In addition, the subtitles and the like referred to in the following description of the present disclosure are not intended to limit the content or the scope of the present disclosure, and serve only as a hint in reading. Such a subtitle should neither be understood as a content for segmenting an article, nor should the content under the subtitle be limited to only the scope of the subtitle.

Fig. 1 is a schematic view illustrating an overall structure of a magnetorheological shock absorber having a wide damping adjustable range according to an embodiment of the present disclosure. Fig. 2 is a schematic view showing the structure of a piston head according to an embodiment of the present disclosure.

Referring to fig. 1 and 2, the magnetorheological damper having a wide damping adjustable range according to the present embodiment (hereinafter, may be simply referred to as a magnetorheological damper or a damper) may be a damper provided in a suspension of an aircraft or an automobile, and an automobile will be described below as an example. The damper may comprise an outer cylinder 1, an inner cylinder 2, a first base 3, a second base 4, a piston head 5, a piston rod 6 and a magnetorheological fluid 7.

Specifically, the inner cylinder 2 may be disposed in the working chamber 10 inside the outer cylinder 1 and fixedly connected to the outer cylinder 1. The first base 3 and the second base 4 may be respectively installed and fixed at both ends of the external cylinder 1, the first coil 31 may be wound in the first base 3, and the second coil 41 may be wound in the second base 4. The piston head 5 may be slidably provided in the inner cylinder 2. One end of the piston rod 6 may be connected to the piston head 5 and the other end may extend out of the outer cylinder 1. The magnetorheological fluid 7 may be filled in a working chamber 10 formed in the outer cylinder body 1.

The piston head 5 may further include a piston main body 51, a first and a second vent through

holes

511 and 512 opened in the piston main body 51, a first relief valve 52 installed at one end of the piston main body 51, and a second relief valve 53 installed at the other end of the piston main body 51. The working chamber 10 may be divided into a first chamber 110 and a second chamber 120 by the piston head 5, and the damping passage 102 formed by the outer cylinder 1, the first base 3, the second base 4, and the inner cylinder 2 may communicate with the first chamber 110 and the second chamber 120, respectively.

In the present disclosure, the first leakage through hole 511 and the second leakage through hole 512 are opened in the piston main body 51, and the first pressure relief valve 52 for controlling the conduction of the first leakage through hole 511 and the second pressure relief valve 53 for controlling the conduction of the second leakage through hole 512 are correspondingly arranged at two ends of the piston main body 51, so that when the movement speed or the movement frequency of the piston rod 6 driving the piston head 5 in the working chamber 10 reaches a certain threshold value, the non-adjustable viscous damping force caused by the flow speed of the magnetorheological fluid 7 can be adjusted and controlled by the first pressure relief valve 52 and the second pressure relief valve 53.

In some examples, the inner cylinder 2 and the outer cylinder 1 may be partially connected, and reserve a damping passage 102 communicating the first chamber 110 and the second chamber 120.

In some examples, the first base 3 may be fixedly installed at a bottom end of the external cylinder 1, and the second base 4 may be fixedly installed at a top end of the external cylinder 1.

In some examples, the piston head 5 and the inner cylinder 2 may have a gap of a certain distance therebetween. This facilitates sliding of the piston head 5 in the inner cylinder 2.

In some examples, the other end of the piston rod 6 extending out of the outer cylinder 1 may abut a wheel or an axle. Therefore, the shock absorber can sense and regulate the vibration of the vehicle caused by the uneven road surface conveniently.

In this embodiment, when the piston rod 6 drives the piston main body 51 to move at a frequency lower than the preset threshold, the first pressure release valve 52 may be attached to one end of the piston main body 51 to block the first leakage through hole 511 and unblock the second leakage through hole 512 (that is, the magnetorheological fluid 7 in the first chamber 110 may flow into the second leakage through hole 512 through the first pressure release valve 52 in real time); the second pressure release valve 53 may be attached to the other end of the piston main body 51 to block the second leakage through hole 512 and unblock the first leakage through hole 511 (that is, the magnetorheological fluid 7 in the second chamber 120 may flow into the first leakage through hole 511 through the second pressure release valve 53 in real time). When the movement frequency of the piston rod 6 driving the piston main body 51 is greater than the preset threshold, the first pressure relief valve 52 may be disengaged from one end of the piston main body 51 to dredge the first drainage hole 511, or the second pressure relief valve 53 may be disengaged from the other end of the piston main body 51 to dredge the second drainage hole 512. Therefore, the operation modes of the first relief valve 52 and the second relief valve 53 can be reasonably regulated according to the movement condition that the piston rod 6 drives the piston main body 51.

In addition, in some examples, the first relief valve 52 may include a first plug 521 movably disposed at one end of the piston main body 51, a first fixing plate 522 fixedly connected to one end of the piston rod 6, and a first elastic element 523 for connecting the first plug 521 and the first fixing plate 522. The second relief valve 53 may include a second stopper 531 movably disposed at the other end of the piston main body 51, a second fixing plate 532 fixedly connected to the other end of the piston rod 6, and a second elastic member 533 for connecting the second stopper 531 and the second fixing plate 532. Accordingly, the movement control of the first and

second fixing plates

522 and 532 can be easily performed.

In some examples, the first fixing plate 522 may be fixedly coupled to an end position of one end of the piston rod 6, and the second fixing plate 532 may be fixedly coupled to the piston rod 6 spaced apart from the other end of the piston body 51.

In some examples, the first resilient element 523 may be a first spring and the second resilient element 533 may be a second spring.

In this embodiment, the first fixing plate 522 may be attached to one end of the piston main body 51 by the biasing force of the first spring, and the second fixing plate 532 may be attached to the other end of the piston main body 51 by the biasing force of the second spring. And when the frequency of the movement of the piston rod 6 with the piston body 51 is too high, the first fixing plate 522 or the second fixing plate 532 is disengaged from the piston body 51 (described in detail later).

In some examples, the spring rates of the first and second springs may be adjustable, or the first and second springs may be preselected or replaced at any time with a certain spring rate. This enables the threshold value, the default threshold value, to be set accordingly.

In addition, in the present embodiment, when the piston rod 6 drives the piston main body 51 to move (leftward) into the working chamber 10 at a movement frequency greater than the preset threshold, the pressure in the first chamber 110 increases to block the first plug 521 of the first relief valve 52 from the first relief through hole 511, and the second plug 531 of the second relief valve 53 disengages from the other end of the piston main body 51 to open the second relief through hole 512. When the piston rod 6 drives the piston main body 51 to move outward (rightward) of the working chamber 10 at a movement frequency greater than the preset threshold, the pressure in the second chamber 120 increases to block the second plug 531 of the second pressure release valve 53 to block the second vent hole 512, and the first plug 521 of the first pressure release valve 52 disengages from one end of the piston main body 51 to unblock the first vent hole 511. In this case, the corresponding vent hole can be conveniently dredged according to the movement direction of the piston rod 6 driving the piston main body 51 under the movement frequency larger than the preset threshold value.

In some examples, a frequency less than the preset threshold may be a medium to low frequency of movement of the piston rod 6, and a frequency greater than the preset threshold may be a high frequency of movement of the piston rod 6.

Fig. 3 is a schematic view showing one example of the flowing direction of a magnetorheological fluid according to an embodiment of the present disclosure. Fig. 4 is a schematic view showing another example of the flowing direction of the magnetorheological fluid according to the embodiment of the present disclosure.

In addition, in the present embodiment, when the piston rod 6 drives the piston main body 51 to move towards the inside of the working chamber 10 (towards the left direction) at a movement frequency greater than the preset threshold, the magnetorheological fluid 7 in the first chamber 110 may flow into the second chamber 120 from the damping channel 102 and the second drain through hole 512 in the first direction (towards the right direction), respectively. When the piston rod 6 drives the piston main body 51 to move out of the working chamber 10 (to the right) at a movement frequency greater than the preset threshold, the magnetorheological fluid 7 in the second chamber 120 flows into the first chamber 110 from the damping channel 102 and the first drain through hole 511 in the second direction (to the left), respectively. Therefore, when the piston rod 6 drives the piston main body 51 to move at a movement frequency larger than a preset threshold value and a viscous damping force caused by an excessively high flow speed of the magnetorheological fluid 7 in the damping channel 102 is excessively large, damping regulation and control of the shock absorber are achieved through the flow of the magnetorheological fluid 7 in the first leakage through hole 511 or the second leakage through hole 512, and therefore the regulation and control range of the shock absorber on the damping force can be enlarged.

Fig. 5 is a schematic configuration diagram showing a piston main body according to an embodiment of the present disclosure, and further, fig. 5 is a plan view showing a piston main body 51 according to an embodiment of the present disclosure. Fig. 6 is a schematic configuration diagram illustrating a first plug adapted to a piston main body according to an embodiment of the present disclosure, and further, fig. 6 is a plan view illustrating the first plug 521 adapted to the piston main body 51 according to the embodiment of the present disclosure.

Referring to fig. 5, in some examples, the outer circumference of the piston main body 51 may be uniformly opened with four arc-shaped first drain through holes 511, and the inner circumference of the piston main body 51 may be uniformly opened with four arc-shaped second drain through holes 512.

In other examples, the number of the first and second vent through

holes

511 and 512 may also be 1, 2, 3, 5, etc., and the shape of the first and second vent through

holes

511 and 512 may also be rectangular, triangular, or other irregular shapes, etc.

In some examples, the first plug 521 may be opened with an opening 5211 for opening the second vent hole 512.

In some examples, the position of the opening 5211 may correspond to the position of the second vent through hole 512, and the number and shape of the openings 5211 may be the same as the number and shape of the second vent through holes 512, respectively. In this case, the magnetorheological fluid 7 in the first chamber 110 may enter the second drain hole 512 through the first plug 521 in real time.

In some examples, the number of the first plugs 521 may also be 1, 2, 3, 5, etc., and the shape of the first plugs 521 may also be rectangular, triangular, or other irregular shapes, etc., as long as the number, shape, and position of the first plugs are the same as those of the second drain through holes 512.

In some examples, the first plug 521, the piston body 51, and the second plug 531 may be all cylinders, which may be axisymmetrically disposed with respect to an axis of the piston rod 6.

In some examples, the radius of the bottom circle of the first plug 521 may be smaller than the radius of the bottom circle of the piston main body 51 and larger than the radius of the circle of the piston main body 51 where the first vent through hole 511 is located. This allows the first vent hole 511 to be sealed when the first plug 521 is attached to the piston main body 51.

In some examples, the radius of the bottom circle of second plug 531 may be located between the radius of the circle of piston body 51 where second vent hole 512 is located and the radius of the circle where first vent hole 511 is located. This facilitates the closing of the second vent hole 512 and the opening of the first vent hole 511 when the second plug 531 is attached to the other end of the piston main body 51.

Referring to fig. 7, in some examples, both ends of the inner cylinder 2 may be respectively provided as a first port 21 and a second port 22, and the first port 21 and the second port 22 may be identical. The first base 3 may be provided with a first groove 32 matching the first port 21, the second base 4 with a second groove 42 matching the second port 22, and the first groove 32 and the second groove 42 may be identical. Thereby, a damping channel 102 through which the magnetorheological fluid 7 can flow between the first chamber 110 and the second chamber 120 can be conveniently formed between the outer cylinder 1, the first base 3, the second base 4 and the inner cylinder 2.

In some examples, the shock absorber may further include a compensation bladder 8 disposed at one end of the first chamber 110 of the outer cylinder 1. In some examples, the compensation bladder 8 may be filled with high pressure nitrogen. In this case, the change in volume of the working chamber 10 caused when the piston rod 6 pushes the piston head 5 can be compensated by the change in volume of the high-pressure nitrogen gas in the compensation balloon 8.

In some examples, the first vent holes 511 are arc-shaped through holes opened on the outer circumference of the piston main body 51 and on the same circumference, and the second vent holes 512 are arc-shaped through holes opened on the inner circumference of the piston main body 51 and on the same circumference. Thus, first and second drain through

holes

511 and 512 can be formed easily.

In some examples, the first coil 31 may be wound in a first base space formed by the first base 3, and the second coil 41 may be wound in a second base space formed by the second base 4. Thereby, corrosion and damage of the first coil 31 and the second coil 41 by the magnetorheological fluid 7 can be avoided.

In some examples, the magnetic core may be disposed in a sandwich in the first and second bases 3 and 4.

In some examples, the outer cylinder block 1 may include an outer cylinder 11 and first and second end caps 12 and 13 disposed at both ends of the outer cylinder 11. In some examples, the first end cap 12 may be a bottom end cap and the second end cap 13 may be a top end cap.

In some examples, the outer cylinder 1 may have a cylindrical shape.

In some examples, the piston rod 6 may be threadedly fixed with the first fixing plate 522, the second fixing plate 532, and the piston main body 51, respectively.

In some examples, the second end cap 13 and the second base 4 may be centrally provided with a through hole through which the piston rod 6 passes.

Fig. 9 is a schematic diagram showing functional modules of a magnetorheological suspension according to an embodiment of the present disclosure. A schematic diagram illustrating the functional blocks of a magnetorheological suspension control system according to an embodiment of the present disclosure is shown at 10.

With reference to fig. 9 and 10, the present disclosure also provides a magnetorheological suspension a, which may include the above-mentioned damper a1, and an elastic element a2 and a guide mechanism a3 connected to the damper.

The present disclosure also provides a magnetorheological suspension control system, which may include the magnetorheological suspension a, a wheel b, a vehicle body c, a controller d, and a sensing element e, where the magnetorheological suspension a may be connected between the wheel b and the vehicle body c, the magnetorheological suspension a may be electrically connected to the controller d through an outgoing line of a coil (the first coil 31 and the second coil 41), and the sensing element e may be disposed on the wheel b and/or the vehicle body c for sensing a state change of the wheel b or the vehicle body c. Specifically, the other end of the piston rod 6 in the shock absorber can abut against a wheel (or an axle), and the first end cover 12 of the shock absorber can be connected with the vehicle body c through corresponding parts.

In some examples, the sensing element e may include a sprung acceleration sensor e1 mounted between the magnetorheological suspension a and the vehicle body c and a wheel acceleration sensor e2 mounted on the wheel b. The sprung acceleration sensor e1 can be used for measuring the acceleration of the vehicle body c and sending the signal to the central controller d in real time, the wheel acceleration sensor e2 can be used for measuring the acceleration of the wheel in real time and sending the signal to the central controller d, and the central controller can be used for receiving the signal to judge the running state or the road surface state of the vehicle and then outputting current to control the output damping of the shock absorber. This is mainly coulomb damping regulation.

Of course, the wheels may be aircraft wheels, and the body may be a fuselage.

The working principle of the shock absorber related by the disclosure is as follows:

in the using process, when the tire of the airplane or the automobile is vibrated to trigger the piston rod 6 in the magnetorheological shock absorber of the device to move towards the inside or the outside of the working cavity 10 at a medium-low frequency, the first plug 521 and the second plug 531 are tightly attached to the two ends of the piston main body 51 under the pretightening force of the first elastic element 523 and the second elastic element 533, and at the moment, the magnetorheological fluid 7 in the first chamber 110 and the second chamber 120 cannot flow through the piston head 5 but only flows through the damping channel 102. At this time, after the central controller d applies the current to the coils (the first coil 31 and the second coil 41), the magnetic field lines formed by the magnetic cores of the coils may be distributed as the magnetic circuit shown in fig. 8, and magnetic force control is applied to the magnetorheological fluid 7 near the first base 3 and the second base 4, and the viscosity of the magnetorheological fluid 7 changes along with the change of the magnitude of the current applied in the coils, thereby realizing the control of the output damping of the shock absorber a 1. The shock absorber a1 now primarily controls the output of coulomb damping.

When the tire of the airplane or the automobile is vibrated to trigger the piston rod 6 in the magnetorheological shock absorber of the device to move in the working chamber 10 at a high frequency, the pressure in the first chamber 110 is increased to enable the first plug 521 of the first pressure relief valve 52 to block the first leakage through hole 511, meanwhile, the second plug 531 of the second pressure relief valve 53 is separated from the other end of the piston main body 51 to unblock the second leakage through hole 512, and the magnetorheological fluid 7 in the first chamber 110 can respectively flow into the second chamber 120 from the damping channel 102 and the second leakage through hole 512 in a first direction (rightward direction in fig. 3). Meanwhile, the output of coulomb damping is controlled by the central controller d for the shock absorber a1 (as described above).

When the tire of the airplane or the automobile is vibrated to trigger the piston rod 6 in the magnetorheological shock absorber of the device to move out of the working chamber 10 at a high frequency, the pressure in the second chamber 120 is increased to enable the second plug 531 of the second pressure relief valve 53 to block the second leakage through hole 512, meanwhile, the first plug 521 of the first pressure relief valve 52 is separated from one end of the piston main body 51 to dredge the second leakage through hole 512, and the magnetorheological fluid 7 in the second chamber 120 flows into the first chamber 110 from the damping channel 102 and the first leakage through hole 511 in a second direction (leftward direction in fig. 4). At the same time, the shock absorber a1 will control the output of coulomb damping by the central controller d (as described above).

In summary, under the high-frequency reciprocating motion of the piston rod 6, the first pressure relief valve 52 and the second pressure relief valve 53 are alternately opened, and the first flow-discharging through hole 511 and the second flow-discharging through hole 512 are alternately conducted, so that the viscous damping caused by the flowing speed of the magnetorheological fluid 7 can be greatly reduced, and the purpose of improving the controllable range of the output damping (the sum of the coulomb damping and the viscous damping) can be achieved.

Therefore, the regulation and control of the increase of the viscous damping of the magnetorheological fluid 7 caused by the too fast movement of the piston rod 6 can be completed.

According to the magnetorheological damper and the magnetorheological suspension, when viscous resistance caused by overhigh flowing speed of the magnetorheological fluid 7 in the damping channel is overlarge, the magnetorheological damper and the magnetorheological suspension with wide damping adjustable range can be adjusted and controlled.

While the present disclosure has been described in detail in connection with the drawings and the examples, it should be understood that the above description is not intended to limit the present disclosure in any way. Those skilled in the art can make modifications and variations to the present disclosure as needed without departing from the true spirit and scope of the disclosure, which fall within the scope of the disclosure.

Claims

1. A magneto-rheological shock absorber with wide damping adjustable range is characterized in that,

the method comprises the following steps:

an outer cylinder body;

the inner cylinder body is arranged in the working cavity in the outer cylinder body and is fixedly connected with the outer cylinder body;

the first base and the second base are arranged at two ends of the outer cylinder body, and a first coil in the first base and a second coil in the second base are wound respectively;

a piston head slidably disposed in the inner cylinder;

one end of the piston rod is connected with the piston head, and the other end of the piston rod extends out of the outer cylinder body; and

magnetorheological fluid filled in the working cavity, wherein,

the piston head comprises a piston body, a first drainage through hole and a second drainage through hole which are formed in the piston body, a first pressure release valve arranged at one end of the piston body and a second pressure release valve arranged at the other end of the piston body, the working cavity is divided into a first cavity and a second cavity by the piston head, and the outer cylinder body, the first base, the second base and a damping channel formed by the inner cylinder body are respectively communicated with the first cavity and the second cavity.

2. The magnetorheological damper of claim 1,

when the movement frequency of the piston rod driving the piston main body is smaller than a preset threshold value, the first pressure release valve blocks the first flow discharge through hole and dredges the second flow discharge through hole, and the second pressure release valve blocks the second flow discharge through hole and dredges the first flow discharge through hole;

when the movement frequency of the piston rod driving the piston main body is larger than the preset threshold value, the first pressure release valve is used for dredging the first drainage through hole, or the second pressure release valve is used for dredging the second drainage through hole.

3. The magnetorheological damper of claim 2,

the first pressure release valve comprises a first plug movably arranged at one end of the piston main body, a first fixing plate fixedly connected to one end of the piston rod and a first elastic element used for connecting the first plug and the first fixing plate;

the second pressure release valve comprises a second plug movably arranged at the other end of the piston main body, a second fixing plate fixedly connected to the other end of the piston rod, and a second elastic element used for connecting the second plug and the second fixing plate.

4. The magnetorheological damper of claim 3,

when the piston rod drives the piston main body to move towards the working cavity under the movement frequency which is greater than the preset threshold value, the pressure in the first cavity enables the first plug of the first pressure release valve to plug the first flow discharge through hole, and meanwhile, the second plug of the second pressure release valve dredges the second flow discharge through hole;

when the piston rod drives the piston main body to move towards the outside of the working cavity under the movement frequency larger than the preset threshold value, the pressure in the second cavity enables a second plug of the second pressure release valve to plug the second flow release through hole, and meanwhile, a first plug in the first pressure release valve dredges the first flow release through hole.

5. The magnetorheological damper of claim 4,

when the piston rod drives the piston main body to move towards the working cavity under the movement frequency which is greater than the preset threshold value, magnetorheological fluid in the first cavity respectively flows into the second cavity from the damping channel and the second leakage through hole;

when the piston rod drives the piston main body to move towards the outside of the working cavity under the movement frequency larger than the preset threshold value, magnetorheological fluid in the second cavity flows into the first cavity from the damping channel and the first leakage through hole respectively.

6. The magnetorheological damper of claim 4,

and the first plug is provided with an opening for dredging the second drainage through hole.

7. The magnetorheological damper of claim 1,

the two ends of the inner cylinder body are respectively provided with a first convex port and a second convex port, the first base is provided with a first groove matched with the first convex port, and the second base is provided with a second groove matched with the second convex port.

8. The magnetorheological damper of claim 1,

the air-cooling cylinder further comprises a compensation air bag arranged at one end of the first chamber of the outer cylinder body.

9. The magnetorheological damper of claim 1,

the first leakage through holes are a plurality of arc-shaped through holes which are arranged on the periphery of the piston main body and are positioned on the same circumference, and the second leakage through holes are a plurality of arc-shaped through holes which are arranged on the periphery of the piston main body and are positioned on the same circumference.

10. A magneto-rheological suspension is characterized in that,

comprising the magnetorheological damper of any one of claims 1 to 9.