CN111005970A - Rotary mixing magnetorheological fluid high-speed damper and magnetorheological fluid rotary mixing method thereof - Google Patents
Rotary mixing magnetorheological fluid high-speed damper and magnetorheological fluid rotary mixing method thereof Download PDFInfo
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- CN111005970A CN111005970A CN202010005493.3A CN202010005493A CN111005970A CN 111005970 A CN111005970 A CN 111005970A CN 202010005493 A CN202010005493 A CN 202010005493A CN 111005970 A CN111005970 A CN 111005970A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
- F16F9/535—Magnetorheological [MR] fluid dampers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
- F16F9/535—Magnetorheological [MR] fluid dampers
- F16F9/537—Magnetorheological [MR] fluid dampers specially adapted valves therefor
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Abstract
The invention discloses a rotary mixing magnetorheological fluid high-speed shock absorber and a rotary mixing method of the magnetorheological fluid, wherein the rotary mixing magnetorheological fluid high-speed shock absorber comprises a damping cylinder filled with the magnetorheological fluid, a piston and a push rod, the piston is positioned in the damping cylinder and divides the damping cylinder into a forward pressure cavity at the front part and a backward pressure cavity at the rear part, one end of the piston, which is positioned in the backward pressure cavity, is provided with a rotary flow spray plate, and the edge of the rotary flow spray plate is provided with a tangential spray hole; a one-way valve control flow channel is arranged in the piston, and a liquid inlet of the one-way valve control flow channel is positioned at one end of the piston in the forward pressure cavity; the outlet of the one-way valve control flow channel is communicated with the tangential spray hole of the rotational flow spray disk; when the magnetorheological fluid is impacted, the push rod pushes the piston to extrude the magnetorheological fluid in the forward pressure cavity, so that a part of the magnetorheological fluid is directly sprayed out from the tangential spray holes of the rotational flow spray disk through the one-way valve control flow channel, and the magnetorheological fluid forms rotational flow in the reverse pressure cavity. The advantages are that: the magnetic induction particles of the magnetorheological fluid in the buffer are uniformly in the magnetorheological fluid, so that the buffer is always in the optimal vibration reduction state.
Description
Technical Field
The invention relates to a rotary mixing magnetorheological fluid high-speed damper, belonging to the technical field of mechanical damping.
Background
Under the high-speed impact environment, the mechanical system can resist the instantaneous large impact force of the structure, and the buffer plays a great role all the time. The basic principle of the buffer is that the two-way reciprocal damping stroke enables impact kinetic energy to be converted into heat energy, namely a forward impact damping stroke and a reverse reset damping stroke. When the damping cylinder is impacted, the push rod pushes the piston to instantly slide forward for a stroke in the damping liquid of the damping cylinder by strong impact force, one part of the strong kinetic energy of the piston is absorbed by the damping liquid in the damping cylinder and converted into heat energy, and the other part of the strong kinetic energy is stored by the return spring in a mode that the return spring is compressed and converted into elastic potential energy; when the impact is finished, the compressed reset spring makes the push rod push the damping liquid of the piston in the damping cylinder to return to the reset state according to the original stroke, and most of the stored elastic potential energy is absorbed by the damping liquid in the reset stroke and is converted into heat energy to be released.
Some high-speed buffers of the device have to travel a forward stroke in a short time before the damping fluid absorbs too much energy when the high-speed buffer is subjected to high-speed impact, and need to store more energy in a form of compressing a return spring, and after the impact is completed, the return spring outputs force to convert the stored energy in a reverse stroke. That is, the amount of heat energy that is converted by the damping fluid on the forward stroke of the damper is less than the amount of heat energy that is converted by the damping fluid on the reverse stroke of the damper. In order to meet the requirement, the prior art adopts a magnetorheological damping mode, and the main measures of the magnetorheological damping mode include: magnetorheological damping fluid is used in the damping cylinder, an electromagnetic coil is arranged on the periphery of the piston, and a magnetorheological one-way valve control flow channel (22) is arranged outside the piston or the cylinder body of the damping cylinder. The principle of the magnetorheological fluid damper is that a piston is positioned in a damping cylinder, the damping cylinder is divided into a forward pressure cavity and a backward pressure cavity which are positioned in front of the piston and behind the piston, a gap through the magnetorheological fluid is formed between the piston and the inner wall of the damping cylinder, and during impact, the piston extrudes the magnetorheological fluid in the forward pressure cavity in a forward impact stroke to force the magnetorheological fluid to flow to the backward pressure cavity in the gap between the piston and the inner wall of the damping cylinder. When the magnetorheological fluid passes through the magnetic field range of the electromagnetic coil, the magnetorheological fluid is instantly converted from a water sample liquid state into a viscous liquid state with greatly increased resistance, the kinetic energy of the piston is continuously absorbed in the forward propulsion process of the piston, the temperature of the magnetorheological fluid in the viscous liquid state is increased, and the forward attenuation of the impact kinetic energy is realized. However, this forward damping is only a fraction, even a small fraction, of the impact energy, the other fraction being stored by the return spring during the constant compression. Conversely, when the impact is finished, the force of the return spring pushes the piston to perform a reverse damping stroke, and the energy conversion principle of the return spring is consistent with that of a forward damping stroke. In order to realize that the amount of heat energy converted by the damping fluid in the forward stroke is smaller than that of heat energy converted by the damping fluid in the reverse stroke, a part of magnetorheological fluid in the forward pressure cavity directly enters the reverse pressure cavity along the one-way valve control flow channel (22), namely the part of magnetorheological fluid does not play a damping role, and thus the purpose of reducing the conversion energy of the magnetorheological fluid in the forward pressure cavity is realized. However, when the part of the magnetorheological fluid entering the counter-pressure cavity from the one-way valve control flow channel (22) returns to the forward-pressure cavity in the reverse damping stroke, the part of the magnetorheological fluid and the magnetorheological fluid in the whole counter-pressure cavity pass through a gap between the piston and the inner wall of the damping cylinder and are converted into viscous liquid through the magnetorheological action of the magnetic field of the electromagnetic coil to participate in energy conversion of retarding the piston resetting stroke, so that the aim of improving the conversion energy of the magnetorheological fluid in the counter-pressure cavity is fulfilled.
As can be seen from the arrangement and the working principle of the buffer, in order to realize that the amount of heat energy converted by the damping fluid in the forward stroke is less than that of heat energy converted by the damping fluid in the reverse stroke, the damping fluid is not separated from the one-way valve control flow channel (22) and the like, and is also not separated from the damping fluid, namely the magnetorheological fluid. However, in practical application, the magnetorheological fluid used as the damping fluid contains magnetic particles formed by mixing silicon oil and iron ions, and the magnetic particles are easy to precipitate in the magnetorheological fluid, so that excessive magnetic particles are gathered at the bottom of the damping cylinder in an impact process, and the magnetorheological fluid in a lower gap becomes too thick and the magnetorheological fluid in an upper gap is obviously thin when the magnetorheological fluid receives the magnetic field magnetorheological action from the gap between the piston and the damping cylinder in the damping process, so that the stress of the piston in the motion process is not uniform, thereby not only directly reducing the vibration damping effect, but also obviously reducing the service life of the buffer.
Disclosure of Invention
The technical problems to be solved by the invention are mainly as follows: the buffer of the magnetorheological fluid is needed to finish the forward stroke in a short time for bearing high-speed impact, and the magnetically-induced particles suspended by the magnetorheological fluid are easy to precipitate.
Aiming at the problems, the technical scheme provided by the invention is as follows:
a rotary mixing magnetorheological fluid high-speed shock absorber comprises a damping cylinder filled with magnetorheological fluid, a piston and a push rod, wherein the piston is positioned in the damping cylinder and divides the damping cylinder into a forward pressure cavity at the front part and a backward pressure cavity at the rear part; a one-way valve control flow channel is arranged in the piston, and a liquid inlet of the one-way valve control flow channel is positioned at one end of the piston in the forward pressure cavity; the outlet of the one-way valve control flow channel is communicated with the tangential spray hole of the rotational flow spray disk; when the magnetorheological fluid is impacted, the push rod pushes the piston to extrude the magnetorheological fluid in the forward pressure cavity, so that a part of the magnetorheological fluid is directly sprayed out from the tangential spray holes of the rotational flow spray disk through the one-way valve control flow channel, and the magnetorheological fluid forms rotational flow in the reverse pressure cavity.
Furthermore, the end surfaces of two opposite sides of the rotational flow spraying disc are respectively a slotted surface and a closed surface; the sealing surface is connected with the push rod, and the slotting surface is attached to the end surface of the piston; the slotted surface is provided with a diversion trench communicated with the tangential spray hole, and the outlets of the one-way valve control flow channels in the diversion trench piston are communicated.
Furthermore, a tangential jet flow position is arranged at the edge of the rotational flow jet disc; the tangential jet flow position is formed by intersecting a radial surface of a disk center and an eccentric cambered surface; the tangential spray holes are formed in the radial surface of the disc center.
Further, the radial surface of the disk center is provided with an axial large diameter side and an axial small diameter side, the distance between the axial large diameter side and the central axis of the rotational flow spraying disk is larger than the distance between the axial small diameter side and the central axis of the rotational flow spraying disk, the axial large diameter sides of all the radial surfaces of the disk center are all on the same circle with the disk center of the rotational flow spraying disk as the center of circle, and the axial small diameter sides of all the radial surfaces of the disk center are all on the same circle with the disk center of the rotational flow spraying disk as the center of circle.
Further, the circle center of the eccentric cambered surface deviates from the disk center of the rotational flow spray disk and is provided with two axial sides; one axial side of the eccentric cambered surface is coincided with the axial small diameter side of the radial surface of one disc center, and the other axial side of the eccentric cambered surface is coincided with the axial large diameter side of the radial surface of the adjacent disc center.
Furthermore, the edge of the rotational flow spray disk is provided with 3 tangential spray positions.
Furthermore, the one-way valve control flow channel arranged on the piston comprises a liquid flow cavity channel, the liquid flow cavity channel comprises a pressure spring cavity, a liquid inlet groove arranged on the inner wall of the pressure spring cavity, a throat pipe communicated with the pressure spring cavity, a valve cavity communicated with the throat pipe and an outlet pipe communicated with the valve cavity, and the pressure spring cavity is positioned at one end, close to the forward pressure cavity, of the piston; the magnetorheological fluid in the pressure chamber can sequentially pass through the liquid inlet groove, the pressure spring chamber, the throat pipe, the valve chamber and the outlet pipe and then enter the diversion groove of the rotational flow spray disk.
Furthermore, the one-way valve control flow passage arranged on the piston further comprises a one-way valve assembly, the one-way valve assembly comprises a pressure spring, a pressing handle, a pull rod and a conical surface valve, the pressure spring is installed in a pressure spring cavity, one end of the pressure spring facing the pressing cavity is attached to the pressing handle and is compressed and controlled by the pressing handle, one end of the pull rod is fixedly connected with the pressing handle, and the other end of the pull rod penetrates through the pressure spring and the throat pipe to be fixedly connected with the conical surface valve in the valve cavity.
Furthermore, the conical surface valve is provided with a conical outer surface, the opening of the throat pipe in the valve cavity is a conical surface throat with a conical inner surface, and the conical outer surface of the conical surface valve is matched with the conical inner surface of the conical surface throat; when the piston moves towards the counter-pressure cavity or is in a static state, the pressure spring in a pre-pressing state pulls the conical valve into the conical throat through the pressing handle and the pull rod fixed with the pressing handle, and the conical throat is sealed unidirectionally.
A rotational flow mixing method for the magneto-rheological fluid of high-speed damper features that part of the magneto-rheological fluid is directly sprayed out from the tangential nozzle of rotational flow spraying disk via one-way valve controlled flow channel to form a rotational flow in counter-pressure cavity, so mixing the magnetic particles easily deposited in the magneto-rheological fluid.
The invention has the advantages that: under the high-speed impact environment, the magnetic induction particles of the magnetorheological fluid in the buffer uniformly exist in the magnetorheological fluid, so that the buffer is always in the optimal vibration reduction state, and meanwhile, the service life of the buffer is also obviously prolonged.
Drawings
FIG. 1 is a schematic axial sectional view of a rotary mixing magnetorheological fluid high-speed damper;
FIG. 2 is a schematic axial sectional view of the damping cylinder;
FIG. 3 is a schematic structural view of a slotted surface of a swirl flow spray disk;
FIG. 4 is a schematic structural view of a closed surface of a swirl spray disk;
FIG. 5 is a perspective view of a swirl flow nozzle plate;
FIG. 6 is a schematic axial cross-sectional view of the piston;
FIG. 7 is a schematic perspective view of the piston, the swirl flow nozzle plate and the push rod;
fig. 8 is a schematic one-way flow diagram of rheological fluid passing through the one-way valve control flow channel and the flow guide groove of the rotational flow spray disk communicated with the one-way valve control flow channel, wherein the arrow direction is the fluid flow direction.
In the figure: 1. a shock absorber body; 2. a damping cylinder; 3. a piston; 4. a push rod; 5. a return spring; 6. a pressure chamber; 7. a counter-pressure chamber; 8. embedding a groove; 9. an electromagnetic coil; 10. a damping gap; 11. a rotational flow spray plate; 12. tangentially spraying holes; 13. grooving surface; 14. a closed face; 15. a diversion trench; 16. a tangential jet position; 17. a disc center radial plane; 18. an eccentric arc surface; 19. an axial large-diameter side; 20. an axial minor diameter; 21. an axial edge; 22. a one-way valve controlled flow channel; 23. a pressure spring cavity; 24. a liquid inlet tank; 25. a throat; 26. a conical surface throat; 27. a valve cavity; 28. an outlet pipe; 29. a pressure spring; 30. pressing the handle; 31. a conical surface valve; 32. a pull rod.
Detailed Description
The invention is further described with reference to the accompanying drawings in which:
as shown in fig. 1, 2 and 7, the rotary mixing magnetorheological fluid high-speed shock absorber comprises a shock absorber body 1, a damping cylinder 2, a piston 3, a push rod 4 and a return spring 5; the shock absorber body is provided with a damping cylinder 2, and a piston 3 is positioned in the damping cylinder 2 to divide the damping cylinder 2 into a forward pressure cavity 6 at the front part and a backward pressure cavity 7 at the rear part; an embedded groove 8 embedded with an electromagnetic coil is arranged on the piston, and an electromagnetic coil 9 is arranged in the embedded groove 8; a damping gap 10 is arranged between the piston 3, the electromagnetic coil 9 embedded on the piston and the inner wall of the damping cylinder 2; one end of the push rod 4 is connected with the piston 3 in the damping cylinder 2, and the other end extends out of the damping cylinder 2; a return spring 5 is sleeved on a push rod 4 outside the damping cylinder 2, a rotational flow spray disk 11 is arranged at one end of the piston 3, which is positioned in the counter pressure cavity 7, and a tangential spray hole 12 is formed in the edge of the rotational flow spray disk 11; a one-way valve control flow channel 22 is arranged in the piston 3, and a liquid inlet of the one-way valve control flow channel 22 is positioned at one end of the piston 3 in the forward pressure cavity 6; the outlet of the one-way valve control flow passage 22 is communicated with the tangential spray holes 12 of the swirl spray disk 11.
The working principle of the arrangement is as follows: when high-speed impact is encountered, the push rod pushes the piston to start a forward impact stroke to extrude the magnetorheological fluid in the forward pressure cavity, most of the magnetorheological fluid is forced to flow into the backward pressure cavity from the damping gap 10, in the process of flowing through the damping gap 10, the rheological fluid is instantly converted into viscous liquid with greatly increased resistance from a water sample dilute liquid state under the action of a magnetic field generated by the electromagnetic coil 9, the kinetic energy of the piston is continuously absorbed in the forward propulsion process of the piston, the temperature of the viscous liquid magnetorheological fluid is increased, and therefore forward attenuation of impact kinetic energy is achieved. However, this forward damping is only a part, even a small part, of the impact energy, and the other part is stored by the return spring 5 during the continuous compression process. In order to adapt to high-speed impact, rheological fluid in the forward pressure cavity 6 is intentionally reduced to participate in rheological damping in a forward impact stroke, and a part of magnetorheological fluid is designed to directly enter the counter pressure cavity from the forward pressure cavity 6 through the one-way valve control flow passage 22. After the high-speed impact is finished, the piston is pushed to perform a reverse damping stroke by the aid of the force of the return spring, and the energy conversion principle of the piston is consistent with that of a forward damping stroke. Different from the forward damping stroke, the magnetorheological fluid entering the counter-pressure cavity from the one-way valve control flow passage 22 passes through the damping gap 10 between the piston and the inner wall of the damping cylinder when the reverse damping stroke returns to the forward pressure cavity 6, and is converted into viscous liquid through the magnetorheological action of the magnetic field of the electromagnetic coil 9 to participate in energy conversion of the reset stroke of the retarded piston, so that the impact kinetic energy stored when the reset spring 5 is compressed is greatly attenuated.
Because rheological fluid contains a large amount of easily precipitated magnetic induction particles, in order to ensure that the magnetic induction particles are always uniformly distributed in rheological fluid under the high-speed impact environment of the shock absorber, the invention makes the special arrangement for the one-way valve control flow channel, and can ensure that rheological fluid entering the counter-pressure cavity 7 through the one-way valve control flow channel is sprayed out from the tangential spray hole 12 of the swirl spray disk 11, so that the magnetorheological fluid forms swirl in the counter-pressure cavity 7, and the magnetic induction particles are uniformly mixed by swirl in the rheological fluid.
In the above arrangement, as shown in fig. 2-8, the opposite end surfaces of the swirl spray disk 11 are respectively a slotted surface 13 and a closed surface 14; the closed surface 14 is fixedly connected with the push rod 4, and the slotted surface 13 is attached to the end surface of the piston 3; the connection can be bolt fastening or welding; the slotted surface 13 is provided with a diversion trench 15 communicated with the tangential spray hole 12, and the diversion trench 15 is communicated with an outlet of a one-way valve control flow passage 22 in the piston 3. Thus, the magnetorheological fluid one-way channel from the forward pressure cavity 6 to the backward pressure cavity 7 is formed by the one-way valve control flow channel 22 in the piston 3, the guide groove 15 on the rotational flow spray disk 11 and the tangential spray holes 12.
The edge of the rotational flow spray disk 11 is provided with a tangential spray position 16; the tangential jet position 16 is formed by intersecting a radial surface 17 of a disk center and an eccentric cambered surface 18, so that the tangential jet position 16 is in a V shape; the tangential orifices 12 are provided in the radial surface 17 of the hub. The purpose of this is to provide a tangential mounting position for the tangential nozzle 12.
The hub radial surfaces 17 have an axial large diameter side 19 and an axial small diameter side 20, the distance between the axial large diameter side 19 and the central axis of the swirl flow nozzle plate 11 is greater than the distance between the axial small diameter side 20 and the central axis of the swirl flow nozzle plate 11, and the axial small diameter sides 20 of all the hub radial surfaces 17 are on the same small diameter circle with the hub of the swirl flow nozzle plate 11 as the center of the circle.
The center of the eccentric cambered surface 18 deviates from the center of the swirl spray disk 11 and is provided with two axial sides 21; one axial side 21 of the eccentric arc surface 18 coincides with the axial small diameter side 20 of one hub radial surface 17, and the other axial side 21 coincides with the axial large diameter side 19 of the adjacent hub radial surface 17. This arrangement ensures that the stream exiting from the tangential orifices 12 is not obstructed by the edge of the swirl disk 11 in front of the tangential orifices 12.
The edge of the swirl spray disk 11 is provided with 3 tangential spray positions 16 at equal intervals. This is preferable, and too much arrangement will increase the difficulty of processing the swirl-flow spray plate 11, and will also cause the sprayed liquid to be blocked by the eccentric arc surface 18 with too large front angle. Obviously, one tangential jet position 16 is certainly not sufficient, and 2 tangential jet positions 16 with equal arc distances are also desirable.
The one-way valve control flow channel 22 arranged on the piston 3 comprises a liquid flow channel, the liquid flow channel comprises a pressure spring cavity 23, a liquid inlet groove 24 arranged on the inner wall of the pressure spring cavity 23, a throat pipe 25 communicated with the pressure spring cavity 23, a valve cavity 27 communicated with the throat pipe 25 and an outlet pipe 28 communicated with the valve cavity 27, and the pressure spring cavity 23 is positioned at one end of the piston 3 close to the forward pressure cavity 6; the magnetorheological fluid in the pressure chamber 6 can sequentially pass through the liquid inlet groove 24, the pressure spring chamber 23, the throat pipe 25, the valve chamber 27 and the outlet pipe 28 and then enter the diversion groove 15 of the swirl spray disk 11. The cavity is arranged in a complex and tortuous manner, so that a liquid flow cavity is not only constructed, but also a position is reserved for arranging a one-way valve mechanism below.
The one-way valve control flow passage 22 arranged on the piston 3 further comprises a one-way valve assembly, the one-way valve assembly comprises a pressure spring 29, a pressure handle 30, a pull rod 32 and a conical valve 31, the pressure spring 29 is arranged in the pressure spring cavity 23, one end of the pressure spring 29 facing the pressure cavity 6 is attached to the pressure handle 30 and is compressed and controlled by the pressure handle 30, one end of the pull rod 32 is fixedly connected with the pressure handle 30, and the other end of the pull rod passes through the pressure spring 29 and the throat pipe 25 and is fixedly connected with the conical valve 31 in a valve cavity 27. The arrangement is that the one-way valve is completely arranged in the piston 3, which is beneficial to realizing the one-way flow control of the liquid flow in the liquid flow cavity channel, and compared with the prior art that the one-way control pressure spring 29 is arranged outside the piston 3, the invention leads the outside of the piston to be simpler.
The conical surface valve 31 is provided with a conical outer surface, the opening of the throat pipe 25 in the valve cavity 27 is a conical surface throat 26 with a conical inner surface, and the conical outer surface of the conical surface valve 31 is matched with the conical inner surface of the conical surface throat 26; when the piston 3 moves towards the counter-pressure cavity 7 or is in a static state, the pressure spring 29 in a pre-pressing state pulls the conical valve 31 into the conical throat 26 through the pressure handle 30 and the pull rod 32 fixed with the pressure handle 30, and therefore the conical throat 26 is sealed in a one-way mode. Such a profile arrangement is more beneficial to the conical valve 31 to have a better reverse closing effect.
A magnetorheological fluid rotational flow mixing method of a magnetorheological fluid high-speed shock absorber utilizes a part of magnetorheological fluid to be directly sprayed out from a tangential spray hole 12 of a rotational flow spray disk 11 through a one-way valve control flow passage 22, so that the magnetorheological fluid forms rotational flow in a counter pressure cavity 7, and magnetic induction particles which are easy to precipitate in the magnetorheological fluid are obviously mixed and mixed.
Claims (10)
1. The utility model provides a high-speed shock absorber of magnetorheological suspensions soon, is including pouring damping cylinder (2) of magnetorheological suspensions, piston (3), push rod (4), and piston (3) are located damping cylinder (2), separate damping cylinder (2) for anterior in the same direction as pressure chamber (6) and the adverse pressure chamber (7) at rear portion, and the one end of push rod is connected with piston (3) in damping cylinder (2), and the other end stretches out outside damping cylinder (2), its characterized in that: a rotational flow spray disk (11) is arranged at one end, located in the counter-pressure cavity (7), of the piston (3), and tangential spray holes (12) are formed in the edge of the rotational flow spray disk (11); a one-way valve control flow channel (22) is arranged in the piston (3), and a liquid inlet of the one-way valve control flow channel (22) is positioned at one end of the piston (3) in the forward pressure cavity (6); the outlet of the one-way valve control flow channel (22) is communicated with the tangential spray hole (12) of the rotational flow spray disk (11); when the magnetorheological fluid is impacted, the push rod pushes the piston to extrude the magnetorheological fluid in the forward pressure cavity (6), so that a part of the magnetorheological fluid is directly sprayed out from the tangential spray holes (12) of the rotational flow spray disk (11) through the one-way valve control flow channel (22), and the magnetorheological fluid forms rotational flow in the reverse pressure cavity (7).
2. The rotary-mixing magnetorheological fluid high-speed damper according to claim 1, wherein: the end surfaces of two opposite sides of the rotational flow spray disk (11) are respectively a slotted surface (13) and a closed surface (14); the closed surface (14) is connected with the push rod, and the slotted surface (13) is attached to the end surface of the piston (3); the grooving surface (13) is provided with a diversion trench (15) communicated with the tangential spray hole (12), and outlets of a one-way valve control flow passage (22) in the diversion trench (15) and the piston (3) are communicated.
3. The rotary-mixing magnetorheological fluid high-speed damper according to claim 2, wherein: the edge of the rotational flow spray disk (11) is provided with a tangential spray position (16); the tangential jet flow position (16) is formed by intersecting a disc center radial surface (17) and an eccentric cambered surface (18); the tangential spray holes (12) are formed in the radial surface (17) of the disc center.
4. The rotary mixing magnetorheological fluid high-speed damper according to claim 3, wherein: the disc center radial surface (17) is provided with an axial large-diameter side (19) and an axial small-diameter side (20), the distance between the axial large-diameter side (19) and the central axis of the swirl spray disc (11) is larger than the distance between the axial small-diameter side (20) and the central axis of the swirl spray disc (11), the axial large-diameter sides (19) of all the disc center radial surfaces (17) are all on the same circle with the disc center of the swirl spray disc (11) as the circle center, and the axial small-diameter sides (20) of all the disc center radial surfaces (17) are all on the same circle with the disc center of the swirl spray disc (11) as the circle center.
5. The rotary mixing magnetorheological fluid high-speed damper according to claim 4, wherein: the circle center of the eccentric cambered surface (18) deviates from the disk center of the swirl spray disk (11) and is provided with two axial sides (21); one axial side (21) of the eccentric cambered surface (18) is superposed with the axial small-diameter side (20) of one disc center radial surface (17), and the other axial side (21) is superposed with the axial large-diameter side (19) of the adjacent disc center radial surface (17).
6. The rotary mixing magnetorheological fluid high-speed damper according to claim 5, wherein: the edge of the rotational flow spray disk (11) is provided with 3 tangential spray positions (16).
7. The rotary-mixing magnetorheological fluid high-speed damper according to claim 2, wherein: the one-way valve control flow channel (22) arranged on the piston (3) comprises a liquid flow cavity channel, the liquid flow cavity channel comprises a pressure spring cavity (23), a liquid inlet groove (24) arranged on the inner wall of the pressure spring cavity (23), a throat pipe (25) communicated with the pressure spring cavity (23), a valve cavity (27) communicated with the throat pipe and an outlet pipe (28) communicated with the valve cavity (27), and the pressure spring cavity (23) is positioned at one end, close to the forward pressure cavity (6), of the piston (3); the magnetorheological fluid in the forward pressure cavity (6) can sequentially pass through the liquid inlet groove (24), the pressure spring cavity (23), the throat pipe (25), the valve cavity (27) and the outlet pipe (28) and then enter the flow guide groove (15) of the rotational flow spray disc (11).
8. The rotary-mixing magnetorheological fluid high-speed damper according to claim 7, wherein: the check valve control flow passage (22) arranged on the piston (3) further comprises a check valve assembly, the check valve assembly comprises a pressure spring (29), a pressing handle (30), a pull rod (32) and a conical valve (31), the pressure spring (29) is arranged in a pressure spring cavity (23), one end, facing the forward pressure cavity (6), of the pressure spring (29) is attached to the pressing handle (30) and is controlled by the compression of the pressing handle (30), one end of the pull rod (32) is fixedly connected with the pressing handle (30), and the other end of the pull rod penetrates through the pressure spring (29) and the throat pipe (25) to be fixedly connected with the conical valve (31) in a valve cavity (27).
9. The rotary-mixing magnetorheological fluid high-speed damper according to claim 8, wherein: the conical surface valve (31) is provided with a conical outer surface, the opening of the throat pipe (25) in the valve cavity (27) is a conical surface throat (26) with a conical inner surface, and the conical outer surface of the conical surface valve (31) is matched with the conical inner surface of the conical surface throat (26); when the piston (3) moves towards the counter-pressure cavity (7) or is in a static state, the pressure spring (29) in a pre-pressing state pulls the conical valve (31) into the conical throat (26) through the pressure handle (30) and the pull rod (32) fixed with the pressure handle (30), and the conical throat (26) is sealed unidirectionally.
10. A magnetorheological fluid cyclone blending method for the magnetorheological fluid high-speed damper according to any one of the claims 1 to 9, which is characterized in that: a part of magnetorheological fluid is directly sprayed out from a tangential spray hole (12) of a swirl spray disk (11) through a one-way valve control flow channel (22), so that the magnetorheological fluid forms a swirl in a counter-pressure cavity (7), and magnetic induction particles which are easy to precipitate in the magnetorheological fluid are mixed and uniformly mixed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010005493.3A CN111005970B (en) | 2020-01-03 | 2020-01-03 | Rotary mixing magnetorheological fluid high-speed damper and magnetorheological fluid rotary mixing method thereof |
Applications Claiming Priority (1)
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| KR100935179B1 (en) * | 2008-07-29 | 2010-01-06 | 주식회사 브이원 | One direction viscos damper |
| CN102654167A (en) * | 2012-05-09 | 2012-09-05 | 杭州电子科技大学 | Magnetorheological damper capable of preventing magnetorheological fluid from precipitating |
| CN202833832U (en) * | 2012-10-24 | 2013-03-27 | 成都市翻鑫家科技有限公司 | Magneto-rheological fluid shock absorber capable of preventing magneto-rheological fluid sediment |
| CN203685963U (en) * | 2014-02-05 | 2014-07-02 | 吉林大学 | Multistage spiral magneto-rheological shock absorber piston assembly |
| CN108533665A (en) * | 2018-06-04 | 2018-09-14 | 清华大学 | Can quick redisperse sedimented particle magneto-rheological vibration damper |
| CN109723750A (en) * | 2019-02-13 | 2019-05-07 | 重庆大学 | A kind of MR damper piston component of band sedimentation Active dispersion devices |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100935179B1 (en) * | 2008-07-29 | 2010-01-06 | 주식회사 브이원 | One direction viscos damper |
| CN102654167A (en) * | 2012-05-09 | 2012-09-05 | 杭州电子科技大学 | Magnetorheological damper capable of preventing magnetorheological fluid from precipitating |
| CN202833832U (en) * | 2012-10-24 | 2013-03-27 | 成都市翻鑫家科技有限公司 | Magneto-rheological fluid shock absorber capable of preventing magneto-rheological fluid sediment |
| CN203685963U (en) * | 2014-02-05 | 2014-07-02 | 吉林大学 | Multistage spiral magneto-rheological shock absorber piston assembly |
| CN108533665A (en) * | 2018-06-04 | 2018-09-14 | 清华大学 | Can quick redisperse sedimented particle magneto-rheological vibration damper |
| CN109723750A (en) * | 2019-02-13 | 2019-05-07 | 重庆大学 | A kind of MR damper piston component of band sedimentation Active dispersion devices |
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