CN114934953A

CN114934953A - Magnetic fluid bearing

Info

Publication number: CN114934953A
Application number: CN202210586980.2A
Authority: CN
Inventors: 王政玉; 王超颖; 岑陈; 张玉芹
Original assignee: Individual
Current assignee: Individual
Priority date: 2021-12-01
Filing date: 2022-05-27
Publication date: 2022-08-23
Also published as: CN113958608A

Abstract

The present invention relates to a magnetic fluid bearing comprising: the bearing comprises an outer shell sleeve and an inner sleeve, wherein the inner sleeve is a rotatable disc or a ring, the outer shell sleeve is a shell sleeved on the periphery of the disc or the ring, a gap is reserved between the outer shell sleeve and the inner sleeve, the outer shell sleeve or the inner sleeve is respectively or simultaneously provided with a magnetic potential source, magnetic yokes or magnetic conducting pole plates are arranged on two sides of a magnetic pole surface of the magnetic potential source, a magnetic isolation bushing is arranged on a non-magnetic pole surface of the magnetic potential source, annular tooth grooves or wear-resistant bushings are respectively or simultaneously arranged on the inner surface of the outer shell sleeve or the outer surface of the inner sleeve, magnetic fluid lubricants are injected in the gap and the annular tooth grooves, and when lubricant runners are arranged on the inner sleeve and the outer shell sleeve, the heat dissipation capacity of the bearing can be improved. The bearing has self-sealing capacity, axial and radial bearing capacity, strong heat dissipation capacity, high reliability and long service life; the self-sealing bearing not only can be used as a self-sealing bearing, but also can be used as a rotary sealing device with self-supporting capacity or a collecting ring.

Description

Magnetic fluid bearing

Technical Field

The invention relates to the field of bearings, in particular to a magnetic fluid bearing and application of the magnetic fluid bearing as a self-supporting rotating collecting ring or a self-supporting sealing element.

Background

At present, in a mechanical rotation supporting system, improvement of reliability and life of a bearing is still an important subject. Besides factors related to external environment, working conditions, bearing materials and the like, the lubricating, sealing and cooling effects of the bearing are all key factors influencing the reliability and the service life, and the factors are related and influenced mutually.

When the bearing lubrication is poor, partial oil film lubrication or dry friction occurs and the bearing is quickly damaged.

When the bearing is sealed badly, the lubricant can be leaked, the bearing is dried up, the loss is increased, the temperature is increased, the sliding surface or the rolling surface of the shaft sleeve is stripped, and the bearing fails. For example: in the existing bearing with the sealing cover, a gap is formed between the outer sleeve and the sealing end cover, and high-viscosity lubricating grease needs to be adopted for lubrication, and leakage can be generated if low-viscosity lubricating oil is adopted for lubrication.

When the heat transfer or cooling of the bearing is poor, the temperature of the lubricant is continuously increased, the viscosity is continuously reduced, the thickness of an oil film is continuously reduced, the bearing capacity is continuously reduced, the dry friction degree is continuously increased, and finally the bearing fails.

When the bearing adopts lubricating grease with high viscosity, the friction loss of the lubrication and the sealing of the bearing is increased, the temperature of the lubricating agent is continuously increased, the viscosity is continuously reduced, the thickness of an oil film is continuously reduced, the bearing capacity is continuously reduced, the dry friction degree is continuously increased, and finally the bearing fails.

Therefore, the selection of a proper bearing structure, a proper sealing structure, a proper lubricant and a good heat transfer cooling mode is important for improving the reliability and the service life of the bearing.

According to the related theory and practical experience of the tribology, the bearing is lubricated by a low-viscosity lubricant and sealed in a non-contact way as much as possible from the viewpoint of adapting to high-speed operation and reducing loss. Under the same size, environment and working condition, the friction loss of the bearing lubricated by the lubricating oil is about one order of magnitude smaller than that of the bearing lubricated by the lubricating grease. In addition, the friction loss of the contact bearing seal is sometimes much greater than the friction loss of the bearing body. However, when lubricating oil is adopted for lubrication, the lubricating oil with low viscosity is adopted and contact type sealing is adopted, so that the contact type sealing has large friction loss, the sealing abrasion is easy to lose efficacy, and the lubricating oil is easy to leak. Therefore, for small bearings, grease which is large in loss but not suitable for leakage is generally adopted; for large bearings or small and medium bearings requiring high reliability and long life, bearings of "no-seal oil return structure" of low-viscosity lubricating oil with low loss are used, for example: the static pressure sliding bearing, the bearing with the oil throwing rope (ring), the oil spray lubricated bearing and the like are adopted, and the bearings lubricated by low-viscosity lubricating oil have small friction loss and good cooling and radiating effects; in order to eliminate the loss caused by sealing and sealing, an oil pumping, oil returning and oil receiving system is required to be arranged outside the bearing body. The oil pumping, oil returning and oil receiving systems are complex, large in occupied space, high in cost, and capable of increasing the energy consumption of oil pumping.

In order to reduce the volume and the cost of a light-load and low-speed common bearing, the common rolling bearing and the sliding bearing are generally lubricated by high-viscosity lubricating grease at present, the bearing lubricated by the high-viscosity lubricating grease is simple in structure, small in volume and low in cost, the lubricating grease is not easy to leak and throw under the working conditions of low speed and low temperature, and the friction loss of the lubricating grease is greatly increased. How to realize the non-leakage, low friction loss and long service life of the bearing is still an important task.

Since the 1960 s a magnetic fluid bearing was developed, which is a bearing using a magnetic fluid lubricant, having lubrication, load-bearing and certain self-sealing capabilities.

A magnetic fluid is a stable suspension that has both the properties of a liquid fluid and the electromagnetic properties of some solid magnetic material. The magnetic fluid consists of magnetic particles, a surfactant and base carrier liquid, and is divided into a water base, an organic carrier liquid base, a liquid metal base and the like according to different carrier liquids of the magnetic fluid, wherein the liquid metal base is divided into a mercury base, a gallium base alloy base and the like. One sometimes simply refers to the magnetic fluid as a magnetic fluid.

The existing magnetic fluid bearing generally comprises an inner bearing sleeve, an outer sleeve, an excitation magnet, magnetic fluid poured between a shaft sleeve and a rotating shaft and the like, wherein the outer sleeve is arranged on the inner sleeve, the excitation magnet is arranged on the outer sleeve, and the diameter of the inner sleeve, namely the diameter of a shaft neck, is basically the same as that of the rotating shaft. The authors in Jinshuai on China Zhi network point out in the current research situation of magnetic fluid bearings and the application prospect thereof in the field of high-speed railways: the radial size of the magnetic particles is only 5-10 nanometers and is 3-4 orders of magnitude smaller than the bearing gap, so that the magnetic particles cannot be abraded, and the magnetic fluid lubricant has extremely small friction factor and extremely small friction loss; due to the action between the magnetic field of the excitation magnet and the magnetic fluid, the magnetofluid bearing has certain self-sealing performance at rest and low speed, leakage cannot occur, meanwhile, external pollutants generally cannot enter a gap inside the bearing, oil film lubrication can be kept, and an external lubricating oil supply subsystem and other mechanical sealing subsystems are not needed. The experimental results in another paper "research on the development and performance of magnetic fluid lubrication sliding bearings" on the Chinese knowledge network indicate that: the thickness of the oil film of the magnetic fluid lubrication bearing in the horizontal direction and the vertical direction is larger than that of No. 30 engine oil under the action of the magnetic field, which shows that the bearing capacity of the magnetic fluid lubrication bearing is larger than that of the No. 30 engine oil lubrication bearing under the same condition, and the friction force of the magnetic fluid lubrication is smaller than that of the traditional bearing under the same condition. Therefore, the magnetic fluid bearing has the characteristics of good sealing performance, less loss, small volume, strong shockproof capability, high rotation precision, low noise and suitability for high-speed operation.

In recent years, the application of the magnetic fluid technology in the aspects of rotary support, sealing, lubrication and cooling is continuously developed, but the existing magnetic fluid bearing still has structural problems, and a rotating shaft or a shaft sleeve can generate great centrifugal force on the magnetic fluid under the conditions of high speed and heavy load, so that the magnetic fluid generates the problems of throwing leakage, oil film damage, temperature rise, bearing capacity reduction, sealing capacity reduction, demagnetization of a permanent magnet exciter and the like at two end faces of a shaft neck. Thus, there are still a number of problems to be solved by magnetic fluid bearings and their related applications:

(1) in the aspects of bearing and lubrication of the magnetic fluid bearing, in order to improve the bearing capacity and the lubricating performance, people adopt the magnetic fluid as a lubricant and simultaneously utilize the aggregation action of an excitation magnetic field on magnetic particles in the magnetic fluid to improve the bearing capacity. In the "magnetic fluid bearing" of reference 1 (CN 202010343564.0), because the magnetic circuit short circuit is generated to the excitation permanent magnet by the journal in the bearing, the magnetizing and adsorbing action of the magnetic field of the permanent magnet on the magnetic fluid is greatly reduced, and the bearing capacity is greatly reduced, the cooling and heat dissipation of the magnetic fluid bearing is mainly performed by the turbofan, but the position where the turbofan is installed cannot form air commutation, so that the improvement of the heat dissipation effect is extremely limited; at high speed and high temperature, the oil film is damaged, the viscosity of the magnetic fluid is reduced, the permanent magnet loses efficacy after demagnetization, and the bearing capacity and the lubricating performance of the permanent magnet are reduced or lost. In the "magnetic fluid sliding bearing" of the reference 2 (CN 201711483127.3), because the inner sleeve and the outer sleeve of the conical bearing are made of magnetic conductive materials, the direction of the magnetic field generated by the excitation coil is axial, and the magnetic force lines passing through the magnetic fluid are few, the excitation effect of the magnetic field on the magnetic fluid is small, and the bearing capacity is low. To improve the excitation effect on the magnetic fluid, i.e. to improve the carrying capacity, a very large excitation current must be used, which in turn causes an increase in energy consumption and an increase in bearing temperature. In addition, when the lip-shaped sealing rings and the rotating shaft on the two sides of the conical bearing inner sleeve adopt ceramic materials, a large magnetic resistance can be generated to the magnetic loop.

(2) In the sealing aspect of the magnetic fluid bearing, the sealing of the bearing is generally to arrange a sealing device on one side or two sides of the bearing, and the sealing device comprises a sealing device for lubricant in the bearing and an isolation sealing device for isolating the bearing. The "a magnetic fluid sealed bearing" of the reference 3 (CN 202110098974.8) is a typical structure, the magnetic fluid sealed part of the bearing is on one side of the bearing, the bearing and lubricating part of the bearing is on the other side, and the bearing area and the sealing area are separated; the invention has the advantages of realizing non-contact zero-leakage sealing and having the defect of larger axial dimension. The 'novel stepped magnetic fluid sealing device' of the reference 4 (patent No. CN 201711031588.7) can effectively prevent magnetic fluid from throwing and leaking, and ensure the sealing effect, but the invention is only used for sealing and has no bearing function, purpose and effect. In terms of the existing contactless dynamic seal, the sealing device does not bear load, and the sealing device also needs to be provided with a supporting bearing independently, namely, the existing magnetic fluid sealing device body has no bearing capacity due to a large gap between the sealing device body and a rotating shaft, and cannot be used as a magnetic fluid bearing.

In addition, the bearing technology and the sealing technology belong to two different technical fields, and although the magnetofluid seal and the magnetofluid bearing mainly comprise an outer sleeve, an inner sleeve or a shaft neck and a magnetic potential source, the functions and the use purposes of the magnetofluid seal and the magnetofluid bearing are different. And the bearing needs to be provided with a wear-resistant bushing or a bearing bush, and the seal needs to be provided with a supporting device. The gap size between the outer sleeve and the inner sleeve of the magnetic fluid sealing device is different, the sealing capacity is good when the average gap size of the magnetic fluid sealing is 0.05 mm-0.2 mm, the sealing capacity is reduced along with the increase of the gap, the size relation between the sealing gap and the shaft neck is not large, and the sealing gap is related to the magnetic field intensity, the shaft neck fluctuation deformation, the related size of the tooth socket and the assembling condition. The average gap c between the inner sleeve and the outer sleeve of the magnetofluid bearing is related to the size of the journal radius r, and is generally defined by a gap ratio psi = c/r, psi ranges from 0.0001 to 0.003, and generally the larger the radius r is, the larger the psi value is, the larger the rotating speed is, the larger the psi value is, the higher the bearing precision requirement is, the smaller the psi value is, the larger the load is, and the smaller the psi value is.

(3) In the aspect of cooling of the magnetic fluid bearing, under the conditions of high speed and heavy load, the magnetic fluid bearing can seriously heat, and when the magnetic fluid bearing is not cooled, the permanent magnet can generate demagnetization, and the magnetic fluid can be thinned, so that the bearing capacity, the sealing capacity and the lubricating performance are greatly reduced. In order to solve the problem of cooling and heat dissipation of the magnetic fluid bearing, various methods are adopted, such as: in the "magnetofluid sliding bearing heat dissipation fan" of reference 5 (patent No. CN 03228086.6), cooling and heat dissipation are performed by a fan attached to the hub. For another example: the "magnetohydrodynamic plain bearing" of the above-mentioned reference 2 (patent No. CN 201711483127.3) and the "magnetohydrodynamic plain bearing" of the reference 6 (patent No. CN 201810312388.7) have no cooling heat dissipation structure and measure, and heat is conducted by the oil-based magnetic fluid, so that the coefficient of thermal conductivity is low, and the cooling effect is poor. The following steps are repeated: the "magnetic fluid cooling structure and the corresponding magnetic fluid sealing device" of reference 7 (patent application No. 200820155225.4) cools the magnetic fluid and the permanent magnet by pumping a cooling liquid from the outside.

(4) In the aspect of collecting rings required by motors and electric appliances, the collecting rings bear large current and have high linear speed under the conditions of high power and high speed. The allowable linear velocity of the solid-state electric brush is adopted, the linear velocity is below 40-90 m/s according to different materials, and the current density is below 12-47A/cm 2. The allowable linear speed of the liquid metal collector can reach 150 m/s at most, and the current density is 300-40000A/cm ^ 2. The best way to do this is to use a liquid metal collector. However, due to the influence of centrifugal force and frictional heating at high speed, leakage prevention and cooling of the collector ring liquid metal become critical problems, and the solution proposed in reference 8 (the chinese informed network paper), the research on the collector device of the liquid metal of the unipolar motor, has a very complicated structure and does not have self-supporting capability. In order to solve the problems of lubrication, sealing, support and the like of the collecting ring, a comprehensive solution is required.

Disclosure of Invention

The invention aims to provide a novel magnetic fluid bearing which integrates bearing, lubrication, sealing and cooling; the problems of lubricant leakage, poor heat dissipation effect and the like during high-speed running of the magnetic fluid bearing are solved, and meanwhile the service life and the reliability of the bearing are improved. The technical scheme provided by the invention is as follows:

a magnetic fluid bearing comprising: the magnetic fluid lubricant filling device comprises an outer shell sleeve and an inner sleeve, wherein the inner sleeve is located in the inner space of the outer shell sleeve, a gap is reserved between the outer shell sleeve and the inner sleeve, a magnetic potential source is arranged on the outer shell sleeve, a lubricant filling air release valve is further arranged on the outer shell sleeve and is communicated with the gap, and a magnetic fluid lubricant is filled in the gap.

The inner sleeve is at least one rotatable magnetic conductive disc or ring, and the center of the disc or ring is provided with a shaft hole; the contour shape of the section of the disc or the ring with the radius of the axial sectioning is a rectangle, a trapezoid, a triangle, a step, an M shape, an inverted W shape and the like which are bilaterally symmetrical, or a rectangle, a trapezoid, a triangle, a step, an M shape, an inverted W shape and the like which are bilaterally asymmetrical.

The outer shell is a cavity sleeved outside the disc or the ring, the outer shell is composed of at least one group of outer shell magnetic potential source, a first outer shell magnetic isolation bushing, a second outer shell magnetic isolation bushing, a first magnetic yoke and a second magnetic yoke, the outer shell magnetic potential source is an annular body, the first outer shell magnetic isolation bushing and the second outer shell magnetic isolation bushing are annular bodies and are arranged on two non-magnetic pole faces of the outer shell magnetic potential source respectively, the first magnetic yoke and the second magnetic yoke are circular bodies made of magnetic conductive materials and are arranged on the two magnetic pole faces of the magnetic potential source and outside the outer surface of the disc or the ring respectively, the first outer shell magnetic isolation bushing and the second outer shell magnetic isolation bushing are made of diamagnetic or paramagnetic substances, and the first outer shell magnetic isolation bushing or the second outer shell magnetic isolation bushing which directly correspond to the outer surface of the disc or the ring are made of materials which are used for both magnetic isolation and wear resistance.

The contour surface of the inner surface or the inner surface of the cavity of the outer shell is matched with the contour surface of the outer surface or the outer surface of the disc or the ring in shape, and a gap is reserved between the contour surfaces.

The first magnetic yoke is a circular body with no hole in the center or a circular body with a through hole or a blind hole in the center, and the second magnetic yoke is a circular body with a through hole in the center. The round body comprises a round plate body or a round barrel body.

The diameter of the excircle surface of the disc or the ring is larger than the diameter of the central through holes of the first magnetic yoke and the second magnetic yoke, and the diameter of the shaft hole of the disc or the ring is smaller than the diameter of the central through holes of the first magnetic yoke and the second magnetic yoke.

At least one group of annular tooth grooves taking the axle center of the axle hole of the disc or the ring as the circle center are respectively or simultaneously arranged on the outer surface of the inner sleeve or the inner surface of the outer shell. When at least one group of annular tooth sockets taking the axis of the shaft hole of the disc or the ring as the center of a circle are simultaneously arranged on the outer surface of the inner sleeve or the inner surface of the outer shell, the tooth surfaces of the two groups of corresponding tooth sockets can be spaced, or the teeth of one group of tooth sockets are embedded into the grooves of the other group of tooth sockets and are in clearance fit with each other.

The magnetic circuit breaker comprises an inner sleeve, a first magnetic yoke, a second magnetic yoke, a disc or a ring, a magnetic fluid lubricant, a lubricant oil and a lubricant oil. The technical scheme can improve the axial sealing capability.

The outer sleeve magnetic potential source is a permanent magnet magnetic potential source or a direct current electromagnetic magnetic potential source or a mixed magnetic potential source combining permanent magnet and direct current electromagnetism. The outer sleeve magnetic potential source can be axial excitation or radial excitation, and axial excitation is preferentially recommended.

When the end cover material of the excircle where the bearing is installed is a non-magnetic material, the non-magnetic material of the end cover can replace the first outer sleeve magnetic isolation bushing.

Another technical solution of a magnetic fluid bearing is: a magnetic fluid bearing comprising: the magnetic fluid lubricant filling device comprises an outer shell sleeve and an inner sleeve, wherein the inner sleeve is located in the inner space of the outer shell sleeve, a gap is reserved between the outer shell sleeve and the inner sleeve, a lubricant filling air release valve is arranged on the outer shell sleeve and communicated with the gap, and a magnetic fluid lubricant is filled in the gap.

The inner sleeve is a disc or a ring which consists of at least one group of inner sleeve magnetic potential source, a first magnetic conductive pole plate, a second magnetic conductive pole plate, a first inner sleeve magnetism isolating bush and a second inner sleeve magnetism isolating bush, the center of the disc or the ring is provided with a shaft hole, the inner sleeve magnetic potential source is an annular permanent magnet with a circular hole in the center, the first magnetic conductive pole plate and the second magnetic conductive pole plate are annular magnetic conductive plate bodies with inner circular holes, the first magnetic conductive pole plate and the second magnetic conductive pole plate are respectively positioned on two magnetic pole surfaces of the inner sleeve magnetic potential source, the first inner sleeve magnetism isolating bush and the second inner sleeve magnetism isolating bush are circular ring bodies, the first inner sleeve magnetism isolating bush and the second inner sleeve magnetism isolating bush are respectively positioned on two non-magnetic pole surfaces of the inner sleeve magnetic potential source and on the outer circular pole surfaces of the first magnetic conductive pole plate and the second magnetic conductive pole plate, the first inner sleeve magnetism isolating bush and the second inner sleeve magnetism isolating bush are made of diamagnetic or paramagnetic substances, the first inner sleeve magnetism-isolating bush or the second inner sleeve magnetism-isolating bush which directly corresponds to the inner circle surface of the outer shell is made of magnetism-isolating and wear-resisting materials; the contour shape of the section of the disc or the ring with the radius of the axial sectioning is a rectangle, a trapezoid, a triangle, a step, an M shape, an inverted W shape and the like which are bilaterally symmetrical, or a rectangle, a trapezoid, a triangle, a step, an M shape, an inverted W shape and the like which are bilaterally asymmetrical.

The outer shell is a shell arranged outside the disc or the ring, and consists of a first magnetic yoke, a second magnetic yoke and a magnetic conductive cylinder, wherein the first magnetic yoke and the second magnetic yoke are round bodies made of magnetic conductive materials and are respectively positioned outside two lateral surfaces of the disc or the ring, the magnetic conductive cylinder is a cylindrical shell made of ferromagnetic substances, an abrasion-resistant layer or a bearing bush is laid on the inner circular surface of the magnetic conductive cylinder, and the magnetic conductive cylinder is arranged on the outer circular surfaces of the first magnetic yoke and the second magnetic yoke.

The diameter of the outer circular surface of the disc or the circular ring is larger than the diameter of the central through holes of the first magnetic yoke and the second magnetic yoke, and the diameter of the inner circular surface of the shaft hole of the disc or the circular ring is smaller than the diameter of the central through holes of the first magnetic yoke and the second magnetic yoke.

At least one group of annular tooth grooves taking the axle center of the axle hole of the disc or the ring as the circle center are respectively or simultaneously arranged on the outer surface of the inner sleeve or the inner surface of the outer shell; when at least one group of annular tooth sockets taking the axis of the shaft hole of the disc or the ring as the center of a circle are simultaneously arranged on the outer surface of the inner sleeve or the inner surface of the outer shell, the tooth surfaces of the two groups of corresponding tooth sockets can be spaced, or the teeth of one group of tooth sockets are embedded in the grooves of the other group of tooth sockets and are in clearance fit with each other.

The inner sleeve magnetic potential source can be axial excitation or radial excitation, and axial excitation is preferentially recommended.

When the end cover material of the excircle of the bearing installation position is magnetic conductivity material, the magnetic conductivity material of the end cover can replace the magnetic conductivity cylinder.

Still another technical solution of a magnetic fluid bearing is: a magnetic fluid bearing comprising: the magnetic fluid lubricant filling device comprises an outer shell sleeve and an inner sleeve, wherein the inner sleeve is positioned in the inner space of the outer shell sleeve, a gap is reserved between the outer shell sleeve and the inner sleeve, a magnetic potential source is arranged on the outer shell sleeve, a lubricant filling air release valve is further arranged on the outer shell sleeve and is communicated with the gap between the outer shell sleeve and the inner sleeve, and a magnetic fluid lubricant is filled in the gap.

The inner sleeve is a disc or a ring which consists of at least one group of inner sleeve magnetic potential source, a first magnetic conductive pole plate, a second magnetic conductive pole plate, a first inner sleeve magnetism isolating bush and a second inner sleeve magnetism isolating bush, the center of the disc or the ring is provided with a shaft hole, the inner sleeve magnetic potential source is an annular permanent magnet with a circular hole in the center, the first magnetic conductive pole plate and the second magnetic conductive pole plate are annular magnetic conductive plate bodies with inner circular holes, the first magnetic conductive pole plate and the second magnetic conductive pole plate are respectively positioned on two magnetic pole surfaces of the inner sleeve magnetic potential source, the first inner sleeve magnetism isolating bush and the second inner sleeve magnetism isolating bush are circular ring bodies, the first inner sleeve magnetism isolating bush and the second inner sleeve magnetism isolating bush are respectively positioned on two non-magnetic pole surfaces of the inner sleeve magnetic potential source and on the outer circular pole surfaces of the first magnetic conductive pole plate and the second magnetic conductive pole plate, the first inner sleeve magnetism isolating bush and the second inner sleeve magnetism isolating bush are made of diamagnetic or paramagnetic substances, the first inner magnetism isolating bush or the second inner magnetism isolating bush which directly corresponds to the inner circle surface of the outer shell is made of materials which are magnetism isolating and wear resistant; the contour shape of the axially-cut radius section of the disc or the ring is a bilaterally symmetrical rectangle, trapezoid, step, triangle, M-shaped, inverted W-shaped or the like, or a bilaterally asymmetrical triangle, rectangle, trapezoid, step, M-shaped, inverted W-shaped or the like.

The utility model discloses a magnetic field strength measuring device, including disk or ring, shell cover, first overcoat magnetism bush, second overcoat magnetism bush, first yoke and second yoke, the shell cover is the cavity of set outside disk or ring, and the shell cover separates the magnetism bush by at least a set of overcoat magnetism potential source, first overcoat magnetism potential source, second overcoat magnetism potential source, the overcoat magnetism potential source separates the magnetism bush and constitutes, first yoke and second yoke, the overcoat magnetism potential source is the ring body and sets up respectively on the two non-magnetic pole faces in overcoat magnetism potential source, first yoke, second yoke are the circular body that magnetic conductivity material made and set up respectively on the two magnetic pole faces in magnetism potential source and outside the surface of disk or ring, first overcoat magnetism bush, second overcoat magnetism bush are made by diamagnetic or paramagnetic substance, and the first overcoat magnetism bush or the second overcoat magnetism bush that separates that directly corresponds outside the surface of disk or ring separates by both magnetism, and wear-resistant material is made again.

The inner sleeve magnetic potential source and the outer sleeve magnetic potential source are excited in series on the magnetic loop.

The outer sleeve magnetic potential source is a permanent magnet magnetic potential source or a direct current electromagnetic magnetic potential source or a mixed magnetic potential source combining permanent magnet and direct current electromagnetism. The inner sleeve magnetic potential source and the outer sleeve magnetic potential source are excited in series on the magnetic loop.

The inner sleeve magnetic potential source and the outer sleeve magnetic potential source can be axial excitation or radial excitation, and axial excitation is preferentially recommended.

When the end cover material of the excircle where the bearing is installed is non-magnetic conductive material, the non-magnetic conductive material of the end cover can replace the first outer sleeve magnetic isolation bushing.

The first characteristic of the structure of the above technical scheme and the existing common lubricant sliding bearing and magnetic fluid lubricant sliding bearing is that: the disc or the ring in the technical scheme replaces the journal of the existing sliding bearing, and the diameter of the outer circular surface of the disc or the ring is larger than that of the journal of the existing common lubricant sliding bearing or magnetic fluid lubricant sliding bearing. When the same kind of common lubricant and the same shaft neck width-diameter ratio are adopted, the friction power consumption of the lubricant is increased due to the fact that the surface area of the disc or the ring is larger and the equivalent shaft neck is increased in the technical scheme. But the friction power consumption of the disc or the ring is not only in direct proportion to the surface area of the disc or the ring and the equivalent journal size, but also in direct proportion to the viscosity of the lubricant, the load size and the rotating speed. However, because the diameter of the disc or the ring in the above technical solution is increased, the outer circle area thereof is also increased, that is, the bearing area is increased, and the thickness or width-to-diameter ratio of the disc or the ring can be reduced, that is, the outer circle surface area of the disc or the ring is reduced when the disc or the ring bears the same load. Therefore, under the condition of the same rotating speed, the bearing adopting the technical scheme adopts a smaller width-diameter ratio and a nano-scale magnetic fluid lubricant with extremely small viscosity coefficient, and simultaneously omits an external sealing device with larger friction power consumption, and the bearing can realize full oil film lubrication, so that the overall friction resistance moment of the bearing and the seal thereof can be greatly reduced, and the overall friction power consumption can be greatly reduced. For example, gallium-based alloy is used as the carrier liquid of the liquid metal magnetofluid: sn is equal to Sn In mass fraction =67 percent to 20.5 percent to 12.5 percent, the melting point is-20 ℃, the boiling point is 2300 ℃, the density is 6.440g/cm ^2, the resistivity is 0.435 ohm/m, when the temperature is 100 ℃, the thermal conductivity is 16.5W/m.K, the viscosity is 0.0024Pa.s, and the proportion of adding iron powder and gallium-based alloy is 1: 8, the thermal conductivity is 132 times that of No. 46 lubricating oil, 0.125W/m.K. Lubricating oil number 46 has a viscosity of 0.025pa.s which is about 10 times that of the liquid metal lubricant, and the frictional resistance torque for rotation of the disc or ring will be lower than or equal to that of lubricating oil number 46. The liquid metal magnetofluid lubricant is incompatible with organic solvent and most of inorganic solvent, and has the advantages of good heat conductivity, low viscosity, low magnetofluid power consumption, large surface tension, no toxicity and the like. In addition, when some equipment requires high reliability, high stability, and long life of the bearing as main indicators, the loss, even if a little, does not become a major problem.

In addition, in the above technical scheme, when the diameter of the outer circular surface of the disc or the ring is larger than the journal of the existing sliding bearing, the disc or the ring has two outer side surfaces and one outer circular surface, both the two outer side surfaces and the one outer circular surface have functional effects, both the two outer side surfaces of the disc or the ring have axial thrust effects, the outer circular surface of the disc or the ring has a radial bearing effect, and when the disc or the ring is static, the annular tooth grooves on the inner side surfaces of the first magnetic yoke and the second magnetic yoke or the annular tooth grooves on the outer surface of the disc or the ring and the magnetic fluid lubricant play a sealing role together under the action of the excitation magnetic field; when the disc or the ring rotates, the magnetofluid lubricant on the two sides of the disc or the ring facing the gap also plays a certain pumping role of the pump wheel, so that the magnetofluid lubricant on the two sides of the disc or the ring tends to the gap outside the outer circular surface of the disc or the ring, and the magnetofluid lubricant is prevented from axially leaking in the gap between the inner through hole of the first magnetic yoke and the second magnetic yoke and the rotating shaft. The gap between the inner surface of the outer sleeve and the outer surface of the inner sleeve has the function of a magnetic fluid lubricant flow channel.

The existing common bearing with the sealing cover plate on both sides can only be lubricated by high-viscosity lubricating grease, a gap is reserved between the bearing outer sleeve and the sealing cover plate, and leakage can be generated by adopting low-viscosity lubricating grease for lubrication. When high-viscosity lubricating grease is adopted for lubrication, the lubricating grease can be thinned and leakage can be generated under the high-speed and high-temperature working condition. The technical scheme is also a gap seal, but almost has no gap and no leakage under the action of the magnetic fluid and the magnetic field.

The second characteristic of the above technical scheme is that: when the outer sleeve magnetic potential source or the inner sleeve magnetic potential source is excited axially, unipolar excitation can be realized, and the unipolar excitation means that all magnetic fluxes passing through the whole area of a gap at one side between the inner circle surface of the outer sleeve and the outer circle of the inner sleeve are in the same polarity, which is also called like-polarity excitation. When the disk or the ring rotates, induced potentials can be generated on two side surfaces of the disk or the ring along the radial direction, or induced electromotive forces are generated on the inner side surfaces of the first magnetic yoke and the second magnetic yoke, but the induced potentials generated in the radius ranges of the two sides of the disk or the ring or the first magnetic yoke and the second magnetic yoke are equal in size and same in the radial direction, like a unipolar generator, but because no electric brush is arranged to connect an electric loop, and permanent magnet or direct current excitation is adopted, no loop induced current or eddy current is formed in the radius ranges of the disk or the ring or the first magnetic yoke and the second magnetic yoke, and no electric loss or electric temperature rise is generated. In the conventional magnetofluid bearing (for example, a multipolar direct-current excitation magnetofluid bearing structure provided in the magnetofluid lubrication sliding bearing lubricating film bearing characteristic analysis, which is derived from the bearing journal 2015 of the 9 th period in the traditional Chinese knowledge network, because the N pole and the S pole of the outer sleeve magnetic potential source are alternately arranged and form a multipolar magnetic pole, when the rotating shaft rotates, an alternating induced potential and an alternating induced current or eddy current are formed on the surface of the circular shaft, so that the electrical loss and the electrical temperature rise are generated, the higher the rotating speed is, the larger the induced current or eddy current is, the higher the electrical loss is, and the higher the temperature rise is.

The third characteristic of the above technical scheme is that: the bearing, lubrication and sealing of the bearing are all in the same area range, and the inner circular surface of the outer shell and the outer circular surface of the inner sleeve are provided with annular tooth grooves which can bear and seal through magnetic fluid. Namely: the magnetic fluid lubricant plays roles of lubrication and bearing in the same area in the bearing, and plays roles of sealing and heat conduction at the same time; namely, the bearing, lubrication, sealing and heat dissipation of the magnetic fluid bearing are integrated into a whole. Different from a single magnetic fluid sealing device, the magnetic fluid sealing device only plays a role in sealing, does not need to be provided with a wear-resistant lining or a bearing bush and cannot bear load, and when in engineering application, the magnetic fluid sealing device also needs an additional supporting bearing; and the bearing is different from a common magnetic fluid bearing, and a sealing device is additionally arranged under the high-speed operation working condition to prevent the lubricant from being thrown and leaked.

The fourth characteristic of the above technical solution is: the bearing has both axial and radial bearing capacity. Because the disc or the ring of the inner sleeve is surrounded in the inner space of the outer sleeve, the diameter of the disc or the ring is larger than that of a shaft neck of the existing bearing, the axial projection area of the disc or the ring bears radial load, and the radial projection area of the disc or the ring bears axial load.

The fifth characteristic of the above technical solution is: in the technical scheme, under the condition of the same shaft neck, the average gap dimension between the profile surface of the inner surface of the outer shell of the bearing and the profile surface of the outer surface of the inner sleeve is smaller than the average gap dimension between the tooth surface of the tooth groove of the existing magnetic fluid sealing element only with the sealing function and the rotating shaft. In the technical scheme, the average gap between the profile surface of the inner surface of the outer sleeve of the bearing and the profile surface of the outer surface of the inner sleeve is about one half to one fifteen times of the average gap between the tooth surface of the tooth groove of the existing magnetic fluid sealing element only with sealing effect and the rotating shaft.

According to the technical scheme, when the bearing is static, under the excitation action of the magnetic potential source, the magnetic fluid lubricant is adsorbed and stored in the gap between the outer shell and the inner sleeve, and leakage cannot be generated. After the inner sleeve rotates, an adhesion boundary layer effect can be generated between the magnetic fluid lubricant and the surfaces on two sides of the disc or the circular ring, so that the magnetic fluid lubricant generates an outward centrifugal movement tendency along the radial direction of the disc or the circular ring, and leakage along the axial direction can not be generated.

According to the technical scheme, when the disc or the ring rotates and bears load, the oil wedge and the oil film can be automatically formed between the inner circular surface of the outer shell and the outer circular surface of the inner sleeve, and the condition of the dynamic pressure bearing is met.

In the above technical scheme: the outer casing comprises various shells which are similar and equivalent to the outer casing and can be assembled and provided with inner cavities. Such as: the first magnetic yoke and the magnetic conductivity cylinder are integrated, and the second magnetic yoke can be independently installed.

The outer casing can be a cavity with radiating fins on the outer surface or a cooling liquid channel on the outer casing.

The outer casing can be an integrated structure with a mounting seat, and can also be a split type casing structure.

The outer circle profile surface of the outer shell can also be an arc surface or an arc surface and the like along the axial direction, and the shape of the inner circle surface of the bearing seat arranged outside the outer shell is matched with the shape of the inner circle surface of the bearing seat to adapt to radial fluctuating load to form the joint bearing.

The cross-sectional profile shapes of the teeth of the annular tooth socket arranged on the outer circular surface of the inner sleeve or the inner circular surface of the outer shell are symmetrical or asymmetrical triangles, rectangles or trapezoids and the like.

The magnetic lubricant includes: water-based, organic carrier liquid-based, liquid metal-based, and the like magnetic fluid lubricating oils and magnetic greases; liquid metal-based magnetic fluid lubricants are preferred.

The overall contour shape of the inner surface of the outer shell corresponding to the outer circular surface of the disc or the ring includes a cylindrical inner circular surface or a circular surface in a bearing area, a non-circular surface in a non-bearing area, or the surface shape of a bush or a sleeve of various conventional sliding bearings.

The inner surface of the outer shell sleeve corresponding to the outer circular surface of the disc or the ring can be provided with oil wedges or oil cavities with different structures adopted by the existing hydrodynamic lubrication bearing.

The outer magnetic potential source can be arranged between the first magnetic yoke and the second magnetic yoke, or equivalently arranged on the first magnetic yoke or the second magnetic yoke, or arranged on the first magnetic yoke and the second magnetic yoke, or arranged at the inner circular surfaces of the through holes of the first magnetic yoke and the second magnetic yoke, or arranged on the inner side surfaces of the first magnetic yoke and the second magnetic yoke, and the non-polar surface of the magnetic potential source is provided with a non-magnetic conductive body; the non-conductive magnet includes a space formed of a gas.

The magnetic isolation material is a diamagnetic material or a paramagnetic material, and when the positions of the first outer sleeve magnetic isolation bushing, the second outer sleeve magnetic isolation bushing, the first inner sleeve magnetic isolation bushing and the second inner sleeve magnetic isolation bushing do not play a supporting role or bear no force, the magnetic isolation bushings can be replaced by air gaps.

The lubricant filling air release valve is a valve which can not only fill lubricant, but also release gas in a pipeline and a flow passage. The lubricant filling air release valve can also be formed by directly arranging a lubricant filling hole on the shell sleeve, and a cock is arranged at the outer port of the filling hole. The number and the positions of the lubricant filling air release valves are set, and the selection and the configuration can be carried out according to the working condition requirements, the lubricant variety and the size of the bearing. The lubricant filling and air release valve is positioned higher than the upper part of the disc or the circular ring so as to ensure that the lubricant can fill all gaps and flow passages under the action of gravity. When the magnetic fluid lubricant is injected into the annular tooth groove from the gap between the through hole of the first magnetic yoke and the disk or the ring and the gap between the through hole of the second magnetic yoke and the disk or the ring by using the injection needle, the lubricant filling deflation valve is not needed.

The bearing area refers to an area with a small gap between the outer edge rotating surface of the disc or the circular ring and the inner circle surface of the outer shell after the load is applied, and the non-bearing area refers to an area with a large gap between the outer edge rotating surface of the disc or the circular ring and the inner circle surface of the outer shell after the load is applied.

In the present application:

the at least one set of annular gullets refers to at least one annular tooth and one annular groove.

The two outer side surfaces of the disc or the ring are two annular planes which are perpendicular to the rotating central axis of the disc or the ring and are arranged on the two sides of the rotating surface on the outermost edge of the disc or the ring.

The inner side surface of the magnetic yoke faces to the side surface of the disc or the ring, and the outer side surface of the magnetic yoke is the other side surface of the magnetic yoke corresponding to the inner side surface of the magnetic yoke.

The inner surface of the outer shell refers to all surfaces in the cavity of the outer shell, including the surfaces of teeth or grooves and the like on the inner surface of the outer shell; the outer surface of the inner sleeve or the disc or the ring refers to all surfaces on the outer surface of the inner sleeve or the disc or the ring, including the surfaces of teeth or grooves and the like on the surface of the inner sleeve or the disc or the ring.

The inner contour surface of the outer shell is the integral surface of the inner edge surface of the inner surface of the cavity of the outer shell formed by a plurality of elements, and does not comprise the surface of a concave groove or hole or groove on the inner surface of the outer shell; the outer contour surface of the inner sleeve or the disc or the ring refers to the whole surface of the outer edge of the outer surface of the inner sleeve or the circular disc body formed by a plurality of elements, and does not comprise the surface of a groove or a hole or a groove which is recessed on the outer surface of the disc or the ring.

The magnetism isolating bushing is a bushing and has a magnetism isolating function.

The term "on a surface" means "on a surface or on a body".

The term "in vivo" includes "in vivo" or "on a surface".

The term "outside a certain surface" means outside a certain surface, and has a certain gap or distance from the certain surface.

The term "somewhere" is included in a small range on or near the body of "somewhere". Both meanings of the "magnetic fluid" simply referred to as "magnetic fluid" are the same.

The disk with the central axial hole is generally identical to the circular ring. The radial thickness of the disk with the axial bore is generally greater than the radial thickness of the ring.

The above magnetic fluid bearing can be selected as follows: and a shaft sleeve or a rotating shaft is arranged in the shaft hole of the disc or the ring, the axial length of the shaft sleeve or the rotating shaft is equal to or greater than the distance between the outer side surface of the first magnetic yoke and the outer side surface of the second magnetic yoke, and an annular tooth groove or a spiral tooth groove or an oblique tooth groove or a combination of the annular tooth groove and the oblique tooth groove or the spiral tooth groove is arranged on the outer circumferential surface of the shaft sleeve or the rotating shaft in the range corresponding to the first magnetic yoke and the second magnetic yoke.

The above magnetic fluid bearing can be selected as follows: and dustproof rings are arranged on the outer side wall surfaces of the central through holes of the first magnetic yoke and the second magnetic yoke.

The above magnetic fluid bearing can be selected as follows: and a hub is arranged on the shaft hole of the disc or the circular ring or the inner circular surface of the shaft sleeve.

The above magnetic fluid bearing can be selected as follows: rolling grooves are arranged on the outer surface of the disc or the ring and the inner surface of the outer shell corresponding to the outer surface of the disc or the ring, and at least two rolling bodies which are symmetrically arranged are arranged in the rolling grooves. The rolling grooves comprise integral continuous annular grooves taking the axle center of the axle hole of the disc or the ring as the circle center, and meanwhile, a retainer is arranged between the rolling bodies; or discontinuous independent grooves or ball bowls are uniformly distributed on the inner surface of the outer shell and the outer surface of the disc or the circular ring, and no retainer is arranged between the rolling bodies. The groove or the spherical bowl comprises a rolling groove or a spherical bowl arranged on the outer circular surface of the disc or the ring and on the inner circular surface of the outer shell corresponding to the outer circular surface of the disc or the ring, and also comprises a rolling groove or a spherical bowl arranged on one outer side surface or two outer sides of the disc or the ring and on the inner side surfaces of the corresponding first magnetic yoke and the second magnetic yoke.

The above magnetic fluid bearing can be selected as follows: a rolling bearing is arranged between the outer circular surface of the disc or the circular ring and the inner circular surface of the outer sleeve; the rolling bearing comprises a ball bearing, a roller bearing, a cross rolling bearing and the like. In the technical scheme, the second outer sleeve magnetism isolating bush of the outer sleeve and the first inner sleeve magnetism isolating bush of the inner sleeve are not arranged during implementation.

The above magnetic fluid bearing can be selected as follows: a rolling bearing is arranged between the outer side surface of the disc or the ring and the inner side surface of the cavity of the outer sleeve; the rolling bearing comprises a ball bearing, a roller bearing, a cross rolling bearing and the like.

The above magnetic fluid bearing can be selected as follows: the outer sleeve body is provided with at least one magnetofluid lubricant storage cavity, and the magnetofluid lubricant storage cavity is communicated with the gap between the outer sleeve and the inner sleeve. Air is contained in the storage cavity when the bearing is static in the magnetic fluid lubricant storage cavity, and when the bearing rotates, part of centrifugally thrown lubricant can be stored in the storage cavity.

The above magnetic fluid bearing can be selected as follows: at least two linear or arc-shaped disc or ring flow channels which are symmetrically and uniformly distributed are arranged on the body of the disc or the ring along the circumference, a flow inlet and a flow outlet are arranged on the disc or the ring flow channel, the flow inlet of the disc or the ring flow channel is arranged at the position close to the shaft hole of the disc or the ring, the flow inlet of the disc or the ring flow channel is communicated with a gap at one side or two sides between the inner sleeve and the outer shell, the flow outlet of the disc or the ring flow channel is arranged on the outer circle surface of the disc or the ring or one side surface or two side surfaces close to the outer circle surface of the disc or the ring, and a magnetic fluid lubricant is filled in the disc or the ring flow channel.

The disc or ring runner may equivalently consist of an axial runner and a radial runner, the axial runner being in communication with the corresponding radial runner.

According to the technical scheme, when the disc or the ring rotates, the magnetic fluid lubricant can be pumped, so that the magnetic fluid circulates in the bearing through the disc or the ring flow channel and a gap between the outer shell and the inner sleeve, and the heat transfer capacity is improved. The wall surface of the disc or the circular ring flow passage plays the role of a pump impeller blade and a pump impeller cover plate.

The above magnetic fluid bearing can be selected as follows: the flow passage of the disc or the ring is provided with a one-way valve, and the flow inlet direction of the one-way valve faces to the flow inlet of the flow passage of the disc or the ring. The function of the one-way valve is as follows: when the disc or the ring is static or rotates at low speed, the retaining spring and the valve core of the one-way valve seal the flow passage of the disc or the ring, so as to prevent the reduction of the axial sealing capability at static or low speed; when the disc or the ring rotates at high speed, the check valve is opened under the suction action of the centrifugal force of the magnetic fluid lubricant in the flow passage of the disc or the ring, the magnetic fluid can form circulation, and the heat transfer capacity at high speed is improved.

The above magnetic fluid bearing can be selected as follows: the magnetic fluid lubricant magnetic fluid of the magnetic fluid of the magnetic fluid of the magnetic fluid of magnetic field of the magnetic field of magnetic fluid of the magnetic fluid of the magnetic fluid of magnetic field of magnetic fluid of the magnetic fluid of magnetic field of magnetic fluid of magnetic field of the magnetic fluid of magnetic field of the magnetic field of the magnetic field of the magnetic. The opening degree of the throttle valves at different positions can be adjusted to adjust the oil film pressure at different positions and the convection heat dissipation capacity of the magnetic fluid lubricant. According to the technical scheme, when the disc or the ring rotates, the magnetic fluid lubricant can be pumped, so that the magnetic fluid circulates in the bearing through the disc or ring flow channel and the outer sleeve flow channel, and the heat transfer capacity is improved. When the outer sleeve flow passage is arranged in the non-bearing area or the throttle valve on the inner sleeve flow passage and the outer sleeve flow passage in the bearing area is closed, the outflow port of the disc or the circular ring flow passage is arranged on the outer circular surface of the disc or the circular ring, the magnetic fluid lubricant generates a pressure relief effect in the non-bearing area due to the outer sleeve flow passage, a pumping and boosting effect is generated in the bearing area, and the disc or the circular ring can be jacked up in the bearing area due to the boosting effect of the magnetic fluid lubricant in the bearing area, so that the oil film thickness is increased, and the bearing capacity is improved.

This technical scheme still can be equipped with the check valve in the runner of disc or ring, and the effect of check valve is: when the disc or the ring is static or rotates at low speed, the retaining spring and the valve core of the one-way valve seal the flow passage of the disc or the ring, so as to prevent the reduction of the axial sealing capability at static or low speed; when the disc or the ring rotates at a high speed, the check valve is opened under the suction action of the centrifugal force of the magnetic fluid lubricant in the flow passage of the disc or the ring, the magnetic fluid forms circulation, and the heat transfer capacity at the high speed is improved.

In the technical scheme, the power for generating circulation for the magnetic fluid lubricant is the power generated when a disc or a circular ring of a bearing inner sleeve rotates, and the pumping effect of the static pressure bearing is different from the pumping effect of an externally-mounted circulating pump of the existing static pressure bearing, and the difference is that: when a circulating pump is installed outside, when the pumping pressure is too high, lubricant is generated at the gap between the two end faces of the bearing and leaks along the axial direction; in the technical scheme, the disc or the ring is enclosed inside the outer shell sleeve, the pumping force is generated inside, according to the continuity principle of hydrodynamics, the lubricant in the bearing can continuously and circularly flow in the gap between the disc or the ring flow channel and the outer shell sleeve and the inner sleeve, a low-pressure or negative-pressure area is generated at the flow inlet of the disc or the ring flow channel, and the magnetic fluid lubricant cannot be thrown to the outside at the outer end faces of the central through holes of the first magnetic yoke and the second magnetic yoke. Meanwhile, the high-pressure magnetic fluid lubricant can generate Bernoulli effect when flowing through the gap between the inner circular surface of the outer shell and the outer circular surface of the inner shell in the non-bearing area at high speed, so that the radial pressure in the non-bearing area is reduced. The higher the rotation speed, the better the bearing and sealing effect. The technical scheme is particularly suitable for large, heavy-load and high-speed bearings.

The above magnetic fluid bearing can be selected as follows: at least one jacket flow channel is arranged on the pipeline arranged outside the jacket sleeve, and a throttle valve, a filter and a radiator are connected in series on the arranged pipeline.

The above magnetic fluid bearing can be selected as follows: the outer sleeve magnetic potential source is a permanent magnetic outer sleeve magnetic potential source, and the thickness of the permanent magnetic outer sleeve magnetic potential source in the area corresponding to the bearing area is larger than that of the non-bearing area. The thicker the axial thickness of the permanent magnetic jacket magnetic potential source is, the stronger the excitation magnetic field intensity is, the thicker the oil film thickness is, the stronger the bearing capacity is, and the better the lubricating performance is.

The above magnetic fluid bearing can be selected as follows: the magnetic fluid lubricant is a liquid metal-based magnetic fluid lubricant. The heat conductivity coefficient of the liquid metal-based magnetic fluid lubricant is about 100 times that of the lubricating oil-based magnetic fluid lubricant, so that the heat transfer and heat dissipation effects of the bearing can be greatly improved; the viscosity of the liquid metal-based magnetic fluid lubricant is about one tenth to one twentieth of that of the lubricating oil-based magnetic fluid lubricant, so that the friction loss and the temperature rise of the bearing can be greatly reduced.

The above magnetic fluid bearing can be selected as follows: in the bearing area of the bearing, at least one energy storage pipeline is connected to a gap between the outer shell and the inner sleeve through the outer shell, one port of the energy storage pipeline is communicated with the gap in the bearing area, the other port of the energy storage pipeline is communicated with an energy storage one-way valve, an energy storage switch valve and an energy accumulator, a flow inlet of the energy storage one-way valve is communicated with the other port of the energy storage pipeline, a flow outlet of the energy storage one-way valve is communicated with a flow inlet of the energy accumulator, the flow outlet and the flow inlet of the energy storage switch valve are connected in parallel to the flow inlet and the flow outlet of the energy storage one-way valve, and magnetic fluid lubricants are filled in the energy accumulator pipeline and the energy accumulator. The energy accumulator and the matched energy storage one-way valve and the energy storage switch valve have the following functions: high-pressure lubricant formed when the disc or the ring runs at high speed can be injected into the energy accumulator through the energy storage one-way valve for storage and energy storage, and the energy storage one-way valve can be automatically closed when the machine is stopped or at low speed; when the bearing is restarted or at low speed, the energy storage switch valve is opened, the stored high-pressure lubricant flows back to the gap of the bearing area of the bearing, and the hard collision friction between the outer circular surface of the disc or the circular ring and the inner circular surface of the outer sleeve is prevented. The energy storage switch valve can be a manual or an electromagnetic valve or a pneumatic or hydraulic valve which is automatically controlled by various sensors and a programmable controller. The bearing of the technical scheme is particularly suitable for a rotary supporting system with heavy load, high speed and frequent starting.

The above magnetic fluid bearing can be selected as follows: and annular confluence grooves are arranged on the inner side surface of the magnetic yoke at the outflow port of the outer sleeve flow passage of the first magnetic yoke and the second magnetic yoke or the outer side surface of the corresponding disc or the corresponding ring at the inflow port of the disc or the corresponding ring along the circumference.

The above magnetic fluid bearing can be selected as follows: at least two screw holes are formed in the outer side face of the first magnetic yoke or the second magnetic yoke or the end face of the outer shell, and screws are mounted during disassembly, so that disassembly is convenient.

The magnetic fluid bearing has the following alternative technical scheme: a magnetic conductivity annular gasket is arranged in a gap between the inner side surface of the first magnetic yoke or the second magnetic yoke and the outer side surface of the disc or the ring, and the inner diameter of the annular gasket is smaller than the diameter of the shaft hole of the disc or the ring. The two side surfaces or one side surface of the annular gasket can be provided with an annular tooth groove; the annular gasket can be provided with radial grooves or through holes, the gasket is used for adjusting axial clearance, and the grooves or the through holes on the gasket can form a lubricant flow passage.

The above magnetic fluid bearing can be selected as follows: and a flange is arranged on one side of the shell sleeve and is used for connecting and sealing the bearing and the equipment.

The magnetic fluid bearing has the following alternative technical scheme: and a bearing bush, an inner bushing or a lining is arranged on the inner circular surface of the outer shell, the outer circular surface of the inner sleeve or the end surfaces of the inner sides of the first magnetic yoke and the second magnetic yoke, and oil wedges or oil cavities with different structures adopted by the traditional hydrodynamic lubrication bearing or hydrostatic bearing can be arranged on the bearing bush, the inner bushing or the lining according to the requirements of different working conditions.

The magnetic fluid bearing has the following alternative technical scheme: the bearings are filled with lubricant of different properties at different locations. For example: organic carrier liquid-based magnetic fluid lubricant can be injected into the clearance between the inner circular surfaces of the inner through holes of the first magnetic yoke and the second magnetic yoke of the outer shell sleeve and the outer circular surface of the shaft sleeve or the rotating shaft, and liquid metal-based magnetic fluid lubricant or low-viscosity lubricating oil can be injected into other clearances between the outer shell sleeve and the inner sleeve and the disc or circular flow channel.

The above magnetic fluid bearing can be selected as follows: the outer casing is connected with an electrode, the rotating shaft or the shaft sleeve connected with the disc or the ring or an element arranged on the rotating shaft or the shaft sleeve is connected with another electrode, and a space gap between the disc or the ring and the outer casing is filled with liquid metal magnetic fluid. The technical scheme can be used as a rotary collecting ring bearing and a self-supporting collecting ring.

The above magnetic fluid bearing can be selected as follows: the bearing can be used alone as a sealing component with self-support.

Various runners on each part in the technical scheme can be drilled and provided with process holes, and the process holes are blocked or directly realized in a 3D printing mode.

Has the advantages that: (1) the sealing effect is good. When the bearing is static, the magnetic fluid lubricant is absorbed in the gap between the outer sleeve and the inner sleeve under the excitation action of the outer sleeve magnetic potential source or the inner sleeve magnetic potential source respectively or jointly, and leakage cannot be generated. When the bearing rotates, particularly when the inner sleeve rotates at a high speed, the disc or the ring has adhesion and centrifugal action on the magnetic fluid lubricant, so that the magnetic fluid lubricant tends to the outer circular surface of the disc or the ring, the magnetic fluid lubricant at the gap between the two ends of the bearing tends to gather towards the symmetrical center of the bearing, and the magnetic fluid lubricant is not easy to leak. For the bearing provided with the magnetic fluid lubricant circulation flow passage, a low-pressure or negative-pressure area can be formed at the flow inlet of the axial flow passage of the disc or the ring when the bearing rotates at a high speed, and the magnetic fluid lubricant is less prone to leakage at the gap at the two ends of the bearing. Because the lubricant does not leak, the bearing is always in a good lubricating state, and the stability, the reliability and the long service life of the bearing are ensured. (2) The heat transfer and cooling effects are good. The bearing adopting the liquid metal magnetofluid lubricant with high heat conductivity coefficient greatly improves the heat transfer efficiency. For the bearing provided with various magnetofluid lubricant circulation flow passages, when the liquid metal magnetofluid lubricant circulates in the outer sleeve flow passage, the inner sleeve flow passage and the gap between the inner sleeve and the outer sleeve of the bearing outer sleeve due to the rotation of the disc or the ring, the heat transfer of the bearing is mainly completed by heat conduction and heat convection together, and the cooling effect of the bearing is better than that of pure heat conduction. (3) The function is multiple. The bearing has both axial and radial bearing capacity. Because the disc or the ring of the inner sleeve is surrounded in the inner space of the outer sleeve, the outer circle surface and the end surfaces at two sides of the disc or the ring can bear load. (4) The energy consumption is low. The invention adopts non-contact lubricating sealing structure, uses magnetic fluid with low viscosity as lubricating sealing agent, and uses unipolar excitation structure without eddy current loss, to reduce friction loss and electric loss. In particular, the existing bearing adopting lubricating grease with high friction loss can be changed into a liquid metal magnetofluid lubricating oil bearing with low friction loss, so that a large amount of energy consumption can be reduced. (5) Has multiple purposes. The bearing not only can be used as a bearing, but also can be independently used as a rotary sealing device with self-supporting capacity; when the liquid metal magnetofluid lubricant with better electrical conductivity is adopted, the rotating shafts of the outer shell sleeve and the inner sleeve are respectively connected with an electrode, and the bearing can be used as a rotating electrode or an electrical appliance rotating joint or a motor collecting ring with the capabilities of bearing, lubricating and sealing.

The invention is further described with reference to the following figures and detailed description.

Drawings

FIG. 1 is a schematic diagram showing the basic structure of a magnetic fluid bearing in which a magnetic potential source is provided on a housing cover according to the present invention.

Fig. 2 is a schematic diagram showing the basic structure of a magnetic fluid bearing with a magnetic potential source arranged on an inner sleeve according to the present invention.

Fig. 3 is a schematic diagram of a basic structure of a magnetic fluid bearing with a magnetic potential source arranged on an inner sleeve and an outer sleeve.

Fig. 4 is a schematic structural view of a magnetic fluid bearing with an internal and external circulation flow passage, a radiator, a restrictor and an energy accumulator according to the present invention.

FIG. 5 is a schematic structural view of a magnetic fluid bearing in which magnetic potential sources are respectively disposed at inner circumferential surfaces of through holes of first and second yokes according to the present invention.

Fig. 6 is a structural schematic diagram of a radial axial sectioning section of an asymmetric trapezoidal disk or ring of the present invention.

FIG. 7 is a schematic structural diagram of a radial axial sectioning section of a rectangular symmetrical disc or ring provided with double flow channels according to the present invention.

FIG. 8 is a schematic structural diagram of a radial axial sectioning section of an inverted W-shaped symmetrical disc or ring of the present invention.

The reference numbers and corresponding designations in the drawings are as follows:

in the attached figure 1: 100-an outer shell comprising: 110 a-a second outer sleeve magnetism-isolating bush, 120 a-an outer sleeve magnetic potential source, 150-a first outer sleeve magnetism-isolating bush, 130-a first magnetic yoke, 140-a second magnetic yoke, 131-a first annular tooth space, 141-a second annular tooth space, 132-a first connecting hole, 142-a second connecting hole, 160-a first lubricant filling and air-releasing valve, 161-a second lubricant filling and air-releasing valve, 133-a first magnetic yoke through hole, 143-a second magnetic yoke through hole, 134-a first magnetic yoke through hole tooth space and 144-a second magnetic yoke through hole tooth space. 200-an inner sleeve comprising: 201-disc or ring, 210-shaft hole.

In the attached fig. 2: 100-an outer shell comprising: 150 b-a magnetic conductive cylinder body, 130-a first magnetic yoke, 140-a second magnetic yoke, 131-a first annular tooth space, 141-a second annular tooth space, 132-a first through hole, 142-a second through hole, 160-a first lubricant filling and air-release valve, 161-a second lubricant filling and air-release valve, 133-a first magnetic yoke through hole, 143-a second magnetic yoke through hole, 134-a first magnetic yoke through hole tooth space, and 144-a second magnetic yoke through hole tooth space. 200-inner sleeve, comprising 201-disc or ring, 210-shaft hole, 200 a-first magnetic guide plate, 200 b-second magnetic guide plate, 120 b-inner sleeve magnetic potential source, 110 b-first inner sleeve magnetism isolating bush, 110c second inner sleeve magnetism isolating set.

In FIG. 3: 100-an outer shell comprising: 110 a-a second outer sleeve magnetism-isolating bush, 120 a-an outer sleeve magnetic potential source, 150-a first outer sleeve magnetism-isolating bush, 130-a first magnetic yoke, 140-a second magnetic yoke, 131-a first annular tooth space, 141-a second annular tooth space, 132-a first connecting hole, 142-a second connecting hole, 160-a first lubricant filling and air-releasing valve, 161-a second lubricant filling and air-releasing valve, 133-a first magnetic yoke through hole, 143-a second magnetic yoke through hole, 134-a first magnetic yoke through hole tooth space and 144-a second magnetic yoke through hole tooth space. 200-an inner sleeve comprising: 201-disc or ring, 210-shaft hole. The disc or ring 201 comprises: 200 a-a first magnetic conducting pole plate, 200 b-a second magnetic conducting pole plate, 120 b-an inner sleeve magnetic potential source, 110 b-a first inner sleeve magnetism isolating bush and 110 c-a second inner sleeve magnetism isolating set.

In fig. 4: 100-an outer shell comprising: 110 a-second outer sleeve magnetic isolation bush, 120 a-outer sleeve magnetic potential source, 150-first outer sleeve magnetic isolation bush, 130-first magnetic yoke, 140-second magnetic yoke, 134-first magnetic yoke through hole tooth space, 144-second magnetic yoke through hole tooth space, 160 a-first throttle valve and 160 b-second throttle valve. 200-an inner sleeve comprising: 201-disc or ring, 213 a-left annular tooth space, 213 b-right annular tooth space, 212 e-first disc or ring radial flow channel, 212 a-first left disc or ring axial flow channel, 212 b-first right disc or ring axial flow channel, 211 a-first left check valve, 211 b-first right check valve, 211 e-first spring, 212 f-second disc or ring radial flow channel, 212 c-second left disc or ring axial flow channel, 212 d-second right disc or ring axial flow channel, 211 c-second left check valve, 211 d-second right check valve, 211 f-second spring; 210 d-shaft sleeve, 210 a-first shaft collar shaped spline, 210 b-second shaft collar shaped spline. 160 c-a third throttle valve, 160 d-a fourth throttle valve, 21 a-a first radiator, 21 b-a second radiator, 22 a-a first magnetic fluid filling air release valve, 22 b-a second magnetic fluid filling air release valve, 23 a-a first jacket flow channel, 23 b-a second jacket flow channel, 24 a-a third jacket flow channel, and 24 b-a fourth jacket flow channel; 30-energy storage pipeline, 31-energy storage one-way valve, 32-energy storage switch valve and 33-energy storage device.

In fig. 5: 100-an outer shell comprising: 110 a-a third inner liner, 120 a-a first outer sleeve magnetic potential source, 120 b-a second outer sleeve magnetic potential source, 150 c-a cylinder, 150 d-a first outer sleeve magnetic potential barrier liner, 150 e-a second outer sleeve magnetic potential barrier liner, 110 c-a first inner sleeve magnetic potential barrier liner, 110 b-a second inner sleeve magnetic potential barrier liner, 130 a-a first outer sleeve magnetic potential source first magnetic yoke, 130 b-a first outer sleeve magnetic potential source second magnetic yoke, 140 a-a second outer sleeve magnetic potential source first magnetic yoke, 140 b-a second outer sleeve magnetic potential source second magnetic yoke, 160 a-a first throttle valve, 160 b-a second throttle valve, 160 c-a third throttle valve, 160 d-a fourth throttle valve, 301 a-a left dust ring, 301 b-a right dust ring, 302 a-a left seal ring, 302 b-a right seal ring, 22 a-a first magnetic fluid deflation valve, 22 b-a second magnetic fluid filling air release valve, 23 a-a first outer sleeve flow channel, 23 b-a second outer sleeve flow channel, 24 a-a third outer sleeve flow channel and 24 b-a fourth outer sleeve flow channel. 200-an inner sleeve comprising: 201-disc or ring, 213 a-left annular tooth space, 213 b-right annular tooth space, 212 e-first disc or ring radial flow channel, 212 a-first left disc or ring axial flow channel, 212 b-first right disc or ring axial flow channel, 212 f-second disc or ring radial flow channel, 212 c-second left disc or ring axial flow channel, 212 d-second right disc or ring axial flow channel; 210 d-shaft sleeve.

In fig. 6: 201-disc or ring, 212 e-first disc or ring radial flow channel, 213 b-right annular tooth space, 213 c-disc or ring external circular surface tooth space.

In the attached figure 7: 201-disc or ring, 212 a-first left disc or ring axial flow channel, 212 b-first right disc or ring axial flow channel, 212 e-first left disc or ring radial flow channel, 212 g-first right disc or ring radial flow channel, 213 a-left annular tooth groove, 213 b-right annular tooth groove, 213 c-disc or ring outer circular surface tooth groove.

In the attached figure 8: 201 a-left disc or ring, 201 b-right disc or ring, 212 e-first disc or ring radial flow channel, 213 a-left annular tooth space, 213 b-right annular tooth space, 110 c-second inner sleeve magnetism isolating bush, 120 b-inner sleeve magnetism potential source.

Detailed Description

The invention is further illustrated by the following specific examples, which are intended to be illustrative of the invention and are not intended to be a further limitation of the invention.

A magnetic fluid bearing having a source of magnetic potential on a housing shell 100 as shown in fig. 1: the method comprises the following steps: the inner sleeve 200 is positioned in the inner space of the outer sleeve 100, and the inner cavity of the outer sleeve 100 is matched with the profile surface of the outer surface of the inner sleeve 200 in a clearance fit mode.

In the scheme, the inner sleeve 200 is a magnetic-conductivity rectangular disc or ring 201 with a shaft hole 210 in the center, and the outer sleeve 100 surrounds the rectangular disc or ring 201; the outer shell 100 is composed of a second outer-shell magnetism-isolating bush 110a which is in clearance fit with the outer circumference of a rectangular disc or a circular ring 201, an axially excited permanent-magnet outer-shell magnetic potential source 120a which is arranged on the outer circumference of the second outer-shell magnetism-isolating bush 110a, a first magnetic yoke 130 and a second magnetic yoke 140 which are arranged on two side faces of the rectangular disc or the circular ring 201, the second outer-shell magnetism-isolating bush 110a and the outer-shell magnetic potential source 120a, and a non-magnetic-conducting first outer-shell magnetism-isolating bush 150 which is arranged on the outer circumferences of the first magnetic yoke 130, the second magnetic yoke 140 and the outer-shell magnetic potential source 120 a.

The first magnetic yoke 130 is a circular plate body with a first magnetic yoke through hole 133 in the center, a first magnetic yoke through hole tooth slot 134 is arranged on the inner circular surface of the first magnetic yoke through hole 133, a first annular tooth slot 131 is arranged on the inner side surface of the first magnetic yoke 130, a first through hole 132 and a first lubricant filling and releasing valve 160 are arranged on the body of the first magnetic yoke 130, and the first lubricant filling and releasing valve 160 is in clearance communication with the outer shell 100 and the inner sleeve 200 through the first through hole 132.

The second yoke 140 is a circular plate body having a second yoke through hole 143 at the center, a second yoke through hole spline 144 is provided on the inner circumferential surface of the second yoke through hole 143, a second annular spline 141 is provided on the inner circumferential surface of the second yoke 140, a second communication hole 142 and a second lubricant filling valve 161 are provided on the body of the second yoke 140, and the second lubricant filling valve 161 is in gap communication with the outer sleeve 100 and the inner sleeve 200 through the second communication hole 142.

The sizes of the relevant elements of the tooth grooves of the first annular tooth groove 131 on the inner side surface of the first yoke 130 and the second annular tooth groove 141 on the inner side surface of the second yoke 140 are: let Lg be the average gap between the inside profile of the first yoke 130 or the second yoke 140 and the outside profile of the rectangular disc or the circular ring 201, with Lg =0.05mm, tooth width Lt =0.4mm, slot width Ls =0.8mm, and tooth height Lh =0.7 mm. The average gap between the inner circular tooth surfaces of the first and second yoke through-

holes

133 and 143 and the rotation shaft is 0.1mm, and the sizes of relevant elements of the first and second yoke through-

hole tooth grooves

134 and 144 are the same as described above. The average radius gap e =0.01mm between the outer circular surface of the disc or ring 201 and the second outer sleeve magnetism isolating bush 110 a. The liquid metal magnetic fluid lubricant is filled in the gaps between the first and second yoke through-

hole tooth grooves

134 and 144 and the rotation shaft and the gap between the outer case 100 and the inner case 200. The lubricant is injected 3/4 of the volume of the gap between the outer shell 100 and the inner shell 200, and the second outer magnetic-isolation bushing 110a is a collar made of a material which is both magnetic-isolation or diamagnetic and wear-resistant.

Before operation, the liquid metal magnetic fluid lubricant is filled into the gap between the outer shell 100 and the inner shell 200 through the lubricant filling

purge valves

160, 161 and the communication holes 132, 142.

When the magnetic fluid lubricant is injected into the first and second

annular teeth grooves

131 and 141 from the gap between the first yoke through hole 133 of the first yoke 130 and the disc or ring 201 and the gap between the second yoke through hole 143 of the second yoke 140 and the disc or ring 201, respectively, with the injection needle, the lubricant-filling

purge valves

160 and 161 may not be provided.

When the bearing is stationary, the liquid metal magnetic fluid lubricant remains in the gap between the outer jacket 100 and the inner jacket 200 under the adsorption of the magnetic field of the outer jacket magnetic potential source 120 a.

When the disc or the ring 201 rotates, on one hand, under the action of centrifugal force generated by the disc or the ring 201 on the liquid metal magnetic fluid lubricant, the magnetic fluid lubricant tends to the outer circular surface of the disc or the ring 201, and the lubricant cannot leak along the axial direction; on the other hand, an oil wedge is formed between the outer circular surface of the disc or ring 201 and the inner circular surface of the second outer sleeve magnetism isolating bush 110a, the liquid metal magnetofluid lubricant with the rigidity enhanced by the magnetic field excitation enters the oil wedge to form an oil film, and a lubricating effect and a supporting force are generated. Meanwhile, the liquid metal magnetic fluid lubricant has a high thermal conductivity, and can rapidly transfer heat to the outer shell 100 by thermal conduction and dissipate heat.

A magnetic fluid bearing having a magnetic potential source provided on an inner sleeve 200 as shown in fig. 2: the method comprises the following steps: the inner sleeve 200 is positioned in the inner space of the outer sleeve 100, and the contour surface of the inner cavity of the outer sleeve 100 is matched with the contour surface of the outer surface of the inner sleeve 200 in a clearance fit mode.

In this scheme, the inner sleeve 200 is composed of an axially excited annular permanent magnetic inner sleeve magnetic potential source 120b with a circular hole in the center, annular magnetic

pole guide plates

200a and 200b located on two magnetic pole surfaces of the inner sleeve magnetic potential source 120b, a first inner sleeve magnetic isolation bushing 110b located on the outer circular surfaces of the annular inner sleeve magnetic potential source 120b and the annular magnetic

pole guide plates

200a and 200b, and a second inner sleeve magnetic isolation bushing 110c located on the inner circular surfaces of the annular inner sleeve magnetic potential source 120b and the annular magnetic

pole guide plates

200a and 200 b.

The outer shell 100 is composed of a first magnetic yoke 130 and a second magnetic yoke 140 which are positioned at two sides of a disc or a ring 201, and a magnetic conductive cylinder 150b which is positioned on the outer circular surfaces of the first magnetic yoke 130 and the second magnetic yoke 140.

The first magnetic yoke 130 is a circular plate body with a first magnetic yoke through hole 133 at the center, a first magnetic yoke through hole tooth slot 134 is arranged on the inner circular surface of the first magnetic yoke through hole 133, a first annular tooth slot 131 is arranged on the inner side surface of the first magnetic yoke 130, a first through hole 132 and a first lubricant filling and releasing valve 160 are arranged on the body of the first magnetic yoke 130, and the first lubricant filling and releasing valve 160 is in clearance communication with the outer shell 100 and the inner sleeve 200 through the first through hole 132.

The second yoke 140 is a circular plate having a second yoke through hole 143 at the center, a second yoke through hole spline 144 is provided on the inner circumferential surface of the second yoke through hole 143, a second annular spline 141 is provided on the inner circumferential surface of the second yoke 140, a second communication hole 142 and a second lubricant filling valve 161 are provided on the second yoke 140, and the second lubricant filling valve 161 is in clearance communication with the space between the outer shell 100 and the inner shell 200 through the second communication hole 142.

The sizes of the relevant elements of the tooth grooves of the first annular tooth groove 131 on the inner side surface of the first yoke 130 and the second annular tooth groove 141 on the inner side surface of the second yoke 140 are: let Lg be the average gap between the inside profile of the first yoke 130 or the second yoke 140 and the outside profile of the disc or the ring 201, Lg =0.05mm, tooth width Lt =0.4mm, slot width Ls =0.8mm, and tooth height Lh =0.7 mm. The average gap between the inner circular tooth surfaces of the first and second yoke through-

holes

hole tooth grooves

134 and 144 are the same as described above. The radius clearance e =0.01mm between the outer circular surface of the disc or ring 201 and the magnetic cylinder 150 b. Magnetic fluid lubricating grease is filled in gaps among the first through hole tooth groove 134, the second through hole tooth groove 144 and the rotating shaft, liquid metal magnetic fluid lubricant is filled in a gap between the outer shell 100 and the inner shell 200, the occupied gap is filled with the liquid metal magnetic fluid lubricant, and the first inner shell magnetism isolating bush 110b is a lantern ring made of materials which are magnetism isolating or diamagnetic and wear resistant.

Before operation, liquid metal magnetic fluid lubricant is filled into a gap between the outer shell 100 and the inner shell 200 through the lubricant filling and releasing

valves

160 and 161 and the communication holes 132 and 142; magnetic fluid grease is injected into the gaps between the first and second yoke through-

hole tooth grooves

134 and 144 and the rotation shaft by an injector.

When the magnetic fluid lubricant is injected into the first and second

annular teeth grooves

purge valves

160 and 161 may not be provided.

When the bearing is static, the liquid metal magnetic fluid lubricant is retained in the gap between the outer shell 100 and the inner sleeve 200 under the adsorption action of the magnetic field of the inner sleeve magnetic potential source 120 b; magnetic fluid grease remains in the gaps between the first yoke through-hole spline 134, the second yoke through-hole spline 144, and the rotating shaft.

When the disc or the ring 201 rotates, on one hand, under the action of centrifugal force generated by the disc or the ring 201 on the liquid metal magnetic fluid lubricant, the lubricant tends to the outer circular surface of the disc or the ring of the bearing, and the lubricant cannot leak along the axial direction; on the other hand, an oil wedge is formed between the outer circumferential surface of the first inner sleeve magnetism isolating bush 110b of the inner sleeve 200 and the inner circumferential surface of the cylinder 150b of the outer sleeve 100, and the liquid metal magnetofluid lubricant with enhanced rigidity by excitation enters the oil wedge to form an oil film, so that a lubricating effect and a supporting force are generated. Meanwhile, the liquid metal magnetic fluid lubricant has a high thermal conductivity, and can rapidly transfer heat to the outer shell 100 in a thermal conduction manner and dissipate heat.

The magnetic potential source shown in fig. 3 is a magnetic fluid bearing provided on both the inner sleeve 200 and the outer sleeve 100: the method comprises the following steps: the inner sleeve 200 is positioned in the inner space of the outer sleeve 100, and the outer sleeve 100 is matched with the corresponding profile surface of the inner sleeve 200 in a clearance fit manner.

In this scheme, the inner sleeve 200 is composed of an axially excited annular permanent magnetic inner sleeve magnetic potential source 120b with a shaft hole in the center, annular magnetic

pole guide plates

200a and 200b located on the two magnetic pole surfaces of the inner sleeve magnetic potential source 120b, a first inner sleeve magnetism isolating bush 110b located on the outer circular surfaces of the annular inner sleeve magnetic potential source 120b and the annular magnetic

pole guide plates

200a and 200b, and a second inner sleeve magnetism isolating bush 110c located on the inner circular surfaces of the annular inner sleeve magnetic potential source 120b and the annular magnetic

pole guide plates

200a and 200 b.

The outer shell 100 is enclosed outside a disc or ring 201; the outer shell 100 is composed of a second outer sleeve magnetic isolation bushing 110a which is positioned outside the outer circular surface of the disc or ring 201 and is in clearance fit with the outer circular surface of the outer sleeve magnetic isolation bushing 110a, an axially excited permanent magnetic outer sleeve magnetic potential source 120a which is positioned on the outer circular surface of the outer sleeve magnetic isolation bushing 110a, a first magnetic yoke 130 and a second magnetic yoke 140 which are positioned on two side surfaces of the disc or ring 201, the outer sleeve magnetic isolation bushing 110a and the outer sleeve magnetic potential source 120a, and a first outer sleeve magnetic isolation bushing 150 which is positioned on the outer circular surfaces of the first magnetic yoke 130, the second magnetic yoke 140 and the outer sleeve magnetic potential source 120 a.

The sizes of the relevant elements of the tooth grooves of the first annular tooth groove 131 on the inner side surface of the first yoke 130 and the second annular tooth groove 141 on the inner side surface of the second yoke 140 are: let Lg be the average gap between the inner contour surface of the first yoke 130 and the second yoke 140 and the outer contour surface of the disc or the ring 201, and the gap Lg =0.06mm, the tooth width Lt =0.4mm, the groove width Ls =0.8mm, and the tooth height Lh =0.7 mm. The average gap between the inner circular tooth surface of the first or second yoke through-

hole

133 or 143 and the rotation shaft is 0.16mm, and the sizes of relevant elements of the first or second yoke through-

hole teeth slots

134 and 144 are the same as described above. The radial clearance e =0.015mm between the outer circular surface of the disc or ring 201 and the inner circular surface of the outer magnetic isolation bushing 110 a. The liquid metal magnetic fluid lubricant is filled in the gaps between the first and second yoke through-

hole tooth grooves

134 and 144 and the rotation shaft and the gap between the outer case 100 and the inner case 200. The lubricant is injected into 3/4 with the volume of all gaps, and the second outer magnetic-isolation bushing 110a and the first inner magnetic-isolation bushing 110b are annular bodies made of magnetic-isolation or diamagnetic and wear-resistant materials.

The magnetic potential source and the function of the magnetic potential source in the embodiment are jointly composed of an outer sleeve magnetic potential source 120a and an inner sleeve magnetic potential source 120b, and the axial excitation directions of the outer sleeve magnetic potential source 120a and the inner sleeve magnetic potential source 120b are opposite. The principle of this embodiment in various operating states and the functions of the elements are basically the same as those of the above embodiment 1 and embodiment 2, and are not described again here.

A magnetic fluid bearing having a source of magnetic potential on the outer housing 100 as shown in fig. 4: the method comprises the following steps: the outer sleeve 100 and the inner sleeve 200, the inner sleeve 200 is located in the inner space of the outer sleeve 100, and the outer sleeve 100 is matched with the corresponding profile surface of the inner sleeve 200 in a clearance fit manner.

In this embodiment, the inner sleeve 200 includes: the magnetic conduction trapezoidal disc or ring 201 with a shaft hole in the center, a left annular tooth groove 213a and a right annular tooth groove 213b on two side faces of the trapezoidal disc or ring 201, a first disc or ring radial flow channel 212e in the trapezoidal disc or ring 201, a first left disc or ring axial flow channel 212a, a first right disc or ring axial flow channel 212b, a first left check valve 211a, a first right check valve 211b and a first spring 211 e; a second disc or ring radial flow passage 212f, a second left disc or ring axial flow passage 212c, a second right disc or ring axial flow passage 212d, a second left check valve 211c, a second right check valve 211d, a second spring 211 f; a sleeve 210d on the shaft hole of the disc or ring 201, a first collar-shaped spline 210a on the sleeve 210d, and a second collar-shaped spline 210 b.

In the technical scheme, the outer shell 100 comprises: a second outer sleeve magnetism isolating bush 110a positioned on the inner circular surface of the outer sleeve magnetic potential source 120a, a first outer sleeve magnetism isolating bush 150 positioned on the outer circular surface of the outer sleeve magnetic potential source 120a, a first magnetic yoke 130 positioned on both sides of the outer sleeve magnetic potential source 120a and both sides of the disc or the ring 201, a second magnetic yoke 140, a first magnetic yoke through hole tooth slot 134 positioned on the inner circular surface of the first magnetic yoke through hole, a second magnetic yoke through hole tooth slot 144 positioned on the inner circular surface of the second magnetic yoke through hole, a first outer sleeve flow channel 23a positioned on the first magnetic yoke 130 and positioned outside a non-bearing area, a second outer sleeve flow channel 23b positioned on the second magnetic yoke 140 and positioned outside the non-bearing area, a third outer sleeve flow channel 24a arranged in the first magnetic yoke 130, and a fourth outer sleeve flow channel 24b arranged in the second magnetic yoke 140; a first throttle valve 160c provided in the third outer flow passage 24a in the body of the first yoke 130, and a fourth throttle valve 160d provided in the body of the second yoke 140 and in the fourth outer flow passage 24 b. The first throttle valve 160a, the first radiator 21a and the first magnetic fluid filling and deflation valve 22a are connected in series on the pipeline of the first jacket flow channel 23 a; the second throttle valve 160b, the second radiator 21b and the second magnetic fluid filling and deflation valve 22b are connected in series on the pipeline of the second outer sleeve flow passage 23 b.

In the bearing area, an energy storage pipeline 30 is arranged through the outer sleeve magnetic potential source 120a and the second outer sleeve magnetic isolation bushing 110a, one port of the energy storage pipeline 30 is communicated with a gap between the outer sleeve 100 and the inner sleeve 200 in the bearing area, the other port of the energy storage pipeline 30 is communicated with an energy storage one-way valve 31, an energy storage switch valve 32 and an energy storage 33, a flow inlet of the energy storage one-way valve 31 is communicated with the other port of the energy storage pipeline 30, a flow outlet of the energy storage one-way valve 31 is communicated with a flow inlet of the energy storage 33, a flow outlet and a flow inlet of the energy storage switch valve 32 are connected in parallel to the flow inlet and the flow outlet of the energy storage one-way valve 31, and liquid metal magnetic fluid lubricants are filled in the energy storage pipeline 30 and the energy storage 33.

The sizes of the relevant elements of the left annular tooth groove 213a and the right annular tooth groove 213b on the two side surfaces of the trapezoidal disc or the circular ring 201 are as follows: let Lg be the average gap between the inner profile of the first yoke 130 or the second yoke 140 and the outer profile of the trapezoidal disk or the circular ring 201, and the gap Lg =0.015mm, the tooth width Lt =0.4mm, the groove width Ls =0.7mm, and the tooth height Lh =0.6 mm. The corresponding gap between the tooth surface of the first yoke through-hole tooth groove 134 and the tooth surface of the second yoke through-hole tooth groove 144 and the tooth surface of the first collar-shaped tooth groove 210a and the tooth surface of the second collar-shaped tooth groove 210b on the sleeve 210d is 0.1mm, and the relevant element size of each tooth groove is substantially the same as the above-mentioned tooth groove. The average radius clearance e =0.015mm between the outer circular surface of the trapezoidal disc or ring 201 and the second outer sleeve magnetism-isolating bush 110 a. The liquid metal magnetic fluid lubricant is injected into the gaps between the first and second yoke through-

hole tooth grooves

134 and 144 and the first and second collar-shaped tooth grooves 210a and 210b of the sleeve 210d and the gaps between the outer shell 100 and the inner shell 200. The lubricant is injected in an amount equal to the volume of all gaps, and the second outer sleeve magnetic-isolating bush 110a is a collar made of a material that is both magnetic-isolating or diamagnetic and wear-resistant.

relief valves

22a and 22b and the first and second outer

shell flow passages

23a and 23 b.

When the bearing is static, the liquid metal magnetic fluid lubricant is retained in the gap between the outer casing 100 and the inner casing 200 under the adsorption action of the magnetic field of the outer casing magnetic potential source 120a to generate a sealing action, and meanwhile, the first left check valve 211a, the first right check valve 211b, the second left check valve 211c and the second right check valve 211d respectively seal the first left disc or circular ring axial flow passage 212a, the first right disc or circular ring axial flow passage 212b, the second left disc or circular ring axial flow passage 212c and the second right disc or circular ring axial flow passage 212d under the action of the first spring 211 e.

When the disc or ring 201 rotates, on the one hand, under the centrifugal force generated by the first disc or ring radial flow passage 212e, the second disc or ring radial flow passage 212f and the two sides of the disc or ring 201 facing the liquid metal magnetic fluid lubricant, the liquid metal magnetic fluid lubricant circulates in the first outer jacket flow passage 23a and the second outer jacket flow passage 23b and dissipates heat through the first radiator 21a and the second radiator 21b, and circulates in the third outer jacket flow passage 24a and the fourth outer jacket flow passage 24b and dissipates heat through the outer jacket 200. Meanwhile, the disc or the ring 201 rotates to enable the liquid metal magnetic fluid lubricant to flow to the outer circular surface of the disc or the ring 201, low pressure or negative pressure is generated at the inlet of the first left disc or ring axial flow passage 212a, the first right disc or ring axial flow passage 212b, the second left disc or ring axial flow passage 212c and the second right disc or ring axial flow passage 212d, and the lubricant cannot leak outwards along the axial direction; on the other hand, in the bearing area, an oil wedge is formed between the disc or the ring 201 and the second outer sleeve magnetism isolating bush 110a, the liquid metal magnetofluid lubricant with the rigidity enhanced by excitation enters the oil wedge to form an oil film, and a lubricating effect and a supporting force are generated.

When all the throttle valves on one side of the bearing are closed or the outer sleeve flow channel is not arranged on the side, all the throttle valves on the other side are opened, and the disc or the ring rotates, the magnetofluid lubricant generates a flowing trend towards the other side under the centrifugal force action of the radial flow channel of the disc or the ring, and the magnetic fluid lubricant is suitable for places with higher pressure in equipment on the other side of the bearing.

The energy accumulator 33 and the matched energy storage one-way valve 31 and energy storage switch valve 32 have the following functions: high-pressure lubricant formed in high-speed operation can be injected into the energy accumulator 33 through the energy storage one-way valve 31 to be stored and store energy, and the energy storage one-way valve 31 can be automatically closed when the engine is stopped or at low speed; when the bearing is restarted or at a low speed, the energy storage switch valve 32 is opened, the stored high-pressure lubricant flows back to the gap of the bearing area, and the hard collision friction between the outer circular surface of the disc or the circular ring 201 of the inner sleeve and the inner circular surface of the second outer sleeve magnetism-isolating sleeve 110a is prevented. The energy storage switch valve 32 may be a solenoid valve or a pneumatic or hydraulic valve controlled automatically by various sensors and a programmable controller. The bearing of the technical scheme is particularly suitable for a rotary supporting system with heavy load, high speed and frequent starting.

A magnetic fluid bearing in which magnetic potential sources are respectively provided at inner circumferential surfaces of through holes of first and second yokes as shown in fig. 5: the method comprises the following steps: the inner sleeve 200 is positioned in the inner space of the outer sleeve 100, and the outer sleeve 100 is matched with the corresponding profile surface of the inner sleeve 200 in a clearance fit manner.

In this embodiment, the inner sleeve 200 includes: the magnetic conduction rectangular disc or ring 201 with a shaft hole in the center, a left annular tooth groove 213a and a right annular tooth groove 213b on two side faces of the rectangular disc or ring 201, a first disc or ring radial runner 212e in the rectangular disc or ring 201, a first left disc or ring axial runner 212a, and a first right disc or ring axial runner 212 b; a second disk or ring radial flow path 212f, a second left disk or ring axial flow path 212c, a second right disk or ring axial flow path 212 d; and a sleeve 210d positioned on the axial hole of the disc or ring 201.

In this technical solution, the outer shell 100 includes: a third inner bushing 110a located outside the outer circular surface of the rectangular disk or ring 201, a cylinder 150c located on the outer circular surface of the third inner bushing 110a, a first throttle 160a, a second throttle 160b, a third throttle 160c, a fourth throttle 160d located on the cylinder 150c, a first outer magnetic potential source 120a located outside the two sides of the disk or ring 201, a second outer magnetic potential source 120b, a first outer magnetic barrier 150d and a first inner magnetic barrier 110c located on the non-magnetic pole surface of the first outer magnetic potential source 120a, a second outer magnetic barrier 150e and a second inner magnetic barrier 110b located on the non-magnetic pole surface of the second outer magnetic potential source 120b, a first outer magnetic potential source located on the magnetic pole surface of the first outer magnetic potential source 120a, a first magnetic yoke tooth space 213c on the inner side surface thereof, a second outer magnetic potential source 130b, a second magnetic yoke 213a and a on the inner side surface thereof located on the magnetic pole surface of the second outer magnetic potential source 120b, and a second magnetic yoke 140a and a on the inner side surface thereof d. A second outer cover magnetic potential source second magnetic yoke 140b, a left dust-proof ring 301a positioned on the outer side surface of the first outer cover magnetic potential source second magnetic yoke 130b, a right dust-proof ring 301b positioned on the outer side surface of the second outer cover magnetic potential source second magnetic yoke 140b of the second outer cover magnetic potential source 120b, a left sealing ring 302a positioned on the inner circumferential surface of the first outer cover magnetic potential source first magnetic yoke 130a, and a right sealing ring 302b positioned on the inner circumferential surface of the second outer cover magnetic potential source first magnetic yoke 140 a. The first magnetic fluid filling and deflation valve 22a is positioned on the first outer sleeve magnetic potential source first outer sleeve magnetic isolation lining 150d, the second magnetic fluid filling and deflation valve 22b is positioned on the second outer sleeve magnetic potential source second outer sleeve magnetic isolation lining 150e, the first outer sleeve flow channel 23a and the third outer sleeve flow channel 24a are positioned on the first outer sleeve magnetic potential source first magnetic yoke 130a, and the second outer sleeve flow channel 23b and the fourth outer sleeve flow channel 24b are positioned on the second outer sleeve magnetic potential source first magnetic yoke 140 a. The first inner sleeve magnetic isolation bushing 110c and the second inner sleeve magnetic isolation bushing 110b may be air gaps.

Liquid metal magnetofluid lubricant is filled in the gaps between the outer sleeve 100 and the rectangular disc or the circular ring 201 and in each flow channel, and oil-based magnetofluid lubricant is filled in the gaps between the tooth grooves of the inner circular surface of each magnetic yoke and the shaft sleeve 210 d. When all the throttle valves on one side of the bearing are closed or the outer sleeve flow channel is not arranged on the side, all the throttle valves on the other side are opened, and the disc or the ring rotates, the magnetofluid lubricant generates a flowing trend towards the other side under the centrifugal force action of the radial flow channel of the disc or the ring, and the magnetic fluid lubricant is suitable for places with higher pressure in equipment on the other side of the bearing.

The operation principle of the technical scheme is basically the same as that of the technical scheme, and the detailed description is omitted here.

An asymmetric trapezoidal disk or ring radius cross-section as shown in figure 6: the disc or ring 201 is provided with a first disc or ring radial flow passage 212e, a right annular tooth groove 213b and a disc or ring outer circular surface tooth groove 213 c. When the disc or ring 201 rotates, the first disc or ring radial flow channel 212e performs a pumping action similar to a pump impeller blade on the magnetic fluid lubricant, so that the magnetic fluid lubricant circularly dissipates heat in gaps between the disc or ring flow channels and the outer sleeve flow channel or between the outer sleeve and the inner sleeve. The right annular tooth grooves 213b, the disc or ring outer circular surface tooth grooves 213c and the magnetic fluid lubricant on the tooth grooves jointly play a sealing role under the action of an outer sleeve magnetic potential source when the disc or ring 201 is static and rotates. The centrifugal action of the left disc or ring radial flow channel 212e of the asymmetric trapezoidal disc or ring 201 on the magnetic fluid lubricant can pressurize to the right side through the gap between the outer casing and the inner casing, so that a rightward flowing trend is generated, and the magnetic fluid lubricant sealing device is suitable for bearings and sealing when the pressure in the right space of the bearing is high. Conversely, when the left side pressure of the bearing is higher, a radial flow passage can be separately arranged on the right side of the disc or the ring.

A symmetrical rectangular disc or ring radius cross-section as shown in figure 7: the disc or ring 201 is provided with a first left disc or ring axial flow passage 212a, a first right disc or ring axial flow passage 212b, a first left disc or ring radial flow passage 212e, a first right disc or ring radial flow passage 212g, a left annular tooth groove 213a, a right annular tooth groove 213b, and a disc or ring outer circular surface tooth groove 213 c. When the disc or the ring 201 rotates, the first disc or ring radial flow passage 212e and the first right disc or ring radial flow passage 212g have a pumping effect similar to a pump impeller blade on the magnetic fluid lubricant, so that the magnetic fluid lubricant circularly dissipates heat in gaps between the disc or ring flow passages and the outer sleeve flow passage or between the outer sleeve and the inner sleeve; the left annular tooth groove 213a, the right annular tooth groove 213b, the disc or ring outer circular surface tooth groove 213c and the magnetic fluid lubricant on the tooth grooves jointly play a sealing role under the action of the outer sleeve magnetic potential source when the disc or ring 201 is static and rotates.

An outer profile plane symmetric inverted W-shaped disc or ring radius cross-section as shown in figure 8: the disc or the ring comprises a left disc or ring 201a and a right disc or ring 201b, the outer contour surface of the disc or the ring is an inverted W-shaped disc or ring, a first left disc or ring radial flow channel 212e and a left annular tooth groove 213a are arranged on the left disc or ring 201 a; a right circular tooth groove 213b is arranged on the right disc or the circular ring 201 b; a second inner sleeve magnetism isolating bush 110c and an inner sleeve magnetic potential source 120b are arranged between the left disc or ring 201a and the right disc or ring 201 b. When the disc or the ring 201 rotates, the first disc or ring radial flow channel 212e plays a pumping role similar to a pump impeller blade for the magnetic fluid lubricant, so that the magnetic fluid lubricant circularly dissipates heat in the disc or ring flow channel and the outer sleeve flow channel or the gap between the outer sleeve and the inner sleeve; when the disc or the ring 201 is static and rotating, the left annular tooth groove 213a, the right annular tooth groove 213b and the magnetic fluid lubricant on the tooth grooves jointly play a sealing role under the action of the inner sleeve magnetic potential source 120 b; the second inner sleeve magnetic shield sleeve 110c can prevent the short circuit and the leakage of the two magnetic poles of the inner sleeve magnetic potential source 120 b. The centrifugal action of the left disc or ring radial flow channel 212e of the symmetrical inverted W-shaped disc or ring 201 on the magnetic fluid lubricant can pressurize to the right through the gap between the outer sleeve and the inner sleeve to generate a trend of flowing to the right, and the magnetic fluid lubricant is suitable for bearings and sealing when the pressure of the space on the right side of the bearing is high. Conversely, when the left side pressure of the bearing is higher, a radial flow passage can be separately arranged on the right side of the disc or the ring.

The above embodiments can be used as bearings, or can be used alone as a sealing device with bearing capacity. When electrodes are respectively connected to the outer housing 100 and the rotating shaft connected to the inner housing 200, the bearing can be used as a rotating electrode or an electrical rotating joint or a motor collecting ring with bearing, lubricating and sealing capabilities.

While the device and its extended use have been described in connection with preferred embodiments, the invention is not limited to the specific constructions and combinations illustrated herein and in the drawings, but, on the contrary, it is intended to cover such equivalents and devices as may be derived from various alternatives, subcombinations, and equivalents of the various features which are included within the scope of the invention as defined by the claims.

Claims

1. A magnetic fluid bearing comprising: outer jacket, endotheca, the endotheca is located the inner space of outer jacket, leave the clearance between outer jacket and the endotheca, be equipped with the magnetic potential source on the outer jacket, still be equipped with the emollient on the outer jacket and annotate the bleed valve, the emollient annotate the bleed valve with the clearance intercommunication, annotate magnetic fluid emollient, its characterized in that in the clearance:

the inner sleeve is at least one rotatable magnetic conductive disc or ring, and the center of the disc or ring is provided with a shaft hole;

the outer shell is a cavity sleeved outside the disc or the ring, the outer shell is composed of at least one group of outer magnetic potential source, a first outer magnetic isolation bushing, a second outer magnetic isolation bushing, a first magnetic yoke and a second magnetic yoke, the outer magnetic potential source is an annular body, the first outer magnetic isolation bushing and the second outer magnetic isolation bushing are annular bodies and are respectively arranged on two non-magnetic pole surfaces of the outer magnetic potential source, the first magnetic yoke and the second magnetic yoke are circular bodies made of magnetic conductive materials and are respectively arranged on two magnetic pole surfaces of the magnetic potential source and outside the outer surface of the disc or the ring, the first outer magnetic isolation bushing and the second outer magnetic isolation bushing are made of diamagnetic or paramagnetic substances, and the first outer magnetic isolation bushing or the second outer magnetic isolation bushing directly corresponding to the outer surface of the disc or the ring is made of materials which are magnetic isolation and wear resistant;

the contour surface of the inner surface or the inner surface of the cavity of the outer shell is matched with the contour surface of the outer surface or the outer surface of the disc or the ring in shape, and a gap is reserved between the contour surfaces;

the first magnetic yoke is a round body without a hole in the center or a round body with a through hole or a blind hole in the center, and the second magnetic yoke is a round body with a through hole in the center;

the diameter of the outer circular surface of the disc or the ring is larger than the diameter of the central through holes of the first magnetic yoke and the second magnetic yoke, and the diameter of the shaft hole of the disc or the ring is smaller than the diameter of the central through holes of the first magnetic yoke and the second magnetic yoke;

at least one group of annular tooth grooves taking the axle center of the axle hole of the disc or the ring as the circle center are respectively or simultaneously arranged on the outer surface of the inner sleeve or the inner surface of the outer shell;

the outer sleeve magnetic potential source is a permanent magnet magnetic potential source or a direct current electromagnetic magnetic potential source or a mixed magnetic potential source combining permanent magnet and direct current electromagnetism.

2. A magnetic fluid bearing comprising: outer housing, endotheca, the endotheca is located the inner space of outer housing, leave the clearance between outer housing and the endotheca, the outer housing is equipped with emollient filling bleed valve, emollient filling bleed valve with the clearance intercommunication, annotate magnetic fluid emollient, its characterized in that in the clearance:

the inner sleeve is a disc or a ring consisting of at least one group of inner sleeve magnetic potential source, a first magnetic conductive plate, a second magnetic conductive plate, a first inner sleeve magnetic isolation bushing and a second inner sleeve magnetic isolation bushing, the center of the disc or the ring is provided with a shaft hole, the inner sleeve magnetic potential source is an annular permanent magnet with a circular hole in the center, the first magnetic conductive plate and the second magnetic conductive plate are annular magnetic conductive plate bodies with inner circular holes, the first magnetic conductive plate and the second magnetic conductive plate are respectively positioned on two magnetic pole surfaces of the inner sleeve magnetic potential source, the first inner sleeve magnetic isolation bushing and the second inner sleeve magnetic isolation bushing are annular bodies, the first inner sleeve magnetic isolation bushing and the second inner sleeve magnetic isolation bushing are respectively positioned on two non-magnetic pole surfaces of the inner sleeve magnetic potential source and on outer circular surfaces of the first magnetic conductive plate and the second magnetic conductive plate, the first inner sleeve magnetic isolation bushing and the second inner sleeve magnetic isolation bushing are made of diamagnetic or paramagnetic substances, the first inner sleeve magnetism-isolating bush or the second inner sleeve magnetism-isolating bush which directly corresponds to the inner circle surface of the outer shell is made of magnetism-isolating and wear-resisting materials;

the outer shell is a cavity arranged outside the disc or the ring, and consists of a first magnetic yoke, a second magnetic yoke and a magnetic conductive cylinder, wherein the first magnetic yoke and the second magnetic yoke are round bodies made of magnetic conductive materials and are respectively positioned outside two side surfaces of the disc or the ring, the magnetic conductive cylinder is a cylindrical shell made of ferromagnetic substances, an abrasion-resistant layer or a bearing bush is laid on the inner circular surface of the magnetic conductive cylinder, and the magnetic conductive cylinder is arranged on the outer circular surfaces of the first magnetic yoke and the second magnetic yoke;

the diameter of the outer circular surface of the disc or the ring is larger than the diameter of the central through hole of the first magnetic yoke and the second magnetic yoke, and the diameter of the inner circular surface of the shaft hole of the disc or the ring is smaller than the diameter of the central through hole of the first magnetic yoke and the central through hole of the second magnetic yoke;

at least one group of annular tooth grooves taking the axle center of the axle hole of the disc or the ring as the circle center are respectively or simultaneously arranged on the outer surface of the inner sleeve or the inner surface of the outer shell.

3. A magnetic fluid bearing comprising: the lubricant filling and releasing device comprises an outer shell sleeve and an inner sleeve, wherein the inner sleeve is positioned in the inner space of the outer shell sleeve, a gap is reserved between the outer shell sleeve and the inner sleeve, a magnetic potential source is arranged on the outer shell sleeve, a lubricant filling and releasing valve is also arranged on the outer shell sleeve, the lubricant filling and releasing valve is communicated with the gap between the outer shell sleeve and the inner sleeve, and a magnetic fluid lubricant is injected into the gap, and the lubricant filling and releasing device is characterized in that:

the inner sleeve is a disc or a ring which consists of at least one group of inner sleeve magnetic potential source, a first magnetic conductive pole plate, a second magnetic conductive pole plate, a first inner sleeve magnetism isolating bush and a second inner magnetism isolating bush, the center of the disc or the ring is provided with a shaft hole, the inner sleeve magnetic potential source is an annular permanent magnet with a circular hole in the center, the first magnetic conductive pole plate and the second magnetic conductive pole plate are annular magnetic conductive plate bodies with inner circular holes, the first magnetic conductive pole plate and the second magnetic conductive pole plate are respectively positioned on two magnetic pole surfaces of the inner sleeve magnetic potential source, the first inner sleeve magnetism isolating bush and the second inner sleeve magnetism isolating bush are circular ring bodies, the first inner sleeve magnetism isolating bush and the second inner sleeve magnetism isolating bush are respectively positioned on two non-magnetic pole surfaces of the inner sleeve magnetic potential source and on the outer circular surfaces of the first magnetic conductive pole plate and the second magnetic conductive pole plate, the first inner sleeve magnetism isolating bush and the second inner sleeve magnetism isolating bush are made of diamagnetic or paramagnetic substances, the first inner magnetism isolating bush or the second inner magnetism isolating bush which directly corresponds to the inner circle surface of the outer shell is made of materials which are magnetism isolating and wear resistant;

the outer shell is a cavity sleeved outside the disc or the ring, the outer shell is composed of at least one group of outer magnetic potential source, a first outer magnetic isolation bushing, a second outer magnetic isolation bushing, a first magnetic yoke and a second magnetic yoke, the outer magnetic potential source is an annular body, the first outer magnetic isolation bushing and the second outer magnetic isolation bushing are annular bodies and are respectively arranged on two non-magnetic pole faces of the outer magnetic potential source, the first magnetic yoke and the second magnetic yoke are circular bodies made of magnetic conductive materials and are respectively arranged on two magnetic pole faces of the outer magnetic potential source and outside the outer surface of the disc or the ring, the first outer magnetic isolation bushing and the second outer magnetic isolation bushing are made of diamagnetic or paramagnetic substances, and the first outer magnetic isolation bushing or the second outer magnetic isolation bushing directly corresponding to the outer surface of the disc or the ring is made of materials which are magnetic isolation and wear-resistant;

the inner sleeve magnetic potential source and the outer sleeve magnetic potential source are excited in series on a magnetic loop;

the first magnetic yoke is a round body with no hole in the center or a round body with a through hole or a blind hole in the center, and the second magnetic yoke is a round body with a through hole in the center;

4. A magnetic fluid bearing according to claim 1, 2 or 3, wherein rolling grooves are provided on the outer surface of the disc or ring and on the inner surface of the outer housing corresponding to the outer surface of the disc or ring, and at least two rolling elements are symmetrically arranged in the rolling grooves.

5. A magnetic fluid bearing according to claim 1, 2 or 3, wherein at least two linear or arc-shaped disc or ring flow paths are symmetrically and uniformly arranged on the body of the disc or ring along the circumference, the disc or ring flow paths are provided with a fluid inlet and a fluid outlet, the fluid inlet of the disc or ring flow path is arranged at a position close to the axial hole of the disc or ring, the fluid inlet of the disc or ring flow path is communicated with the gap at one side or two sides between the inner sleeve and the outer sleeve, the fluid outlet of the disc or ring flow path is arranged on the outer circumferential surface of the disc or ring or on one side or two sides close to the outer circumferential surface of the disc or ring, and the magnetic fluid in the disc or ring flow path is filled with lubricant.

6. A magnetic fluid bearing according to claim 1 or claim 3, wherein the source of casing magnetic potential is a source of permanent magnet casing magnetic potential, the thickness of the source of permanent magnet casing magnetic potential in the region corresponding to the load bearing region being greater than the thickness of the non-load bearing region.

7. A magnetic fluid bearing according to claim 5, wherein at least one outer sleeve flow passage is provided in the housing or in a pipe provided outside the housing through the outer sleeve, the outer sleeve flow passage is provided with a flow inlet and a flow outlet, the flow inlet of the outer sleeve flow passage is provided on an inner side surface of the first yoke or the second yoke or on an inner circumferential surface of the outer sleeve, the flow inlet of the outer sleeve flow passage is communicated with the flow outlet of the disk or the ring flow passage through a gap between the inner sleeve and the outer sleeve, the flow outlet of the outer sleeve flow passage is provided on an inner side surface near the through hole of the first yoke or the second yoke, and the flow outlet of the outer sleeve flow passage is communicated with the flow inlet of the disk or the ring flow passage through a gap between the outer sleeve and the inner sleeve, the outer sleeve flow passage is provided with a throttle valve, and the outer sleeve flow passage is filled with a magnetic fluid lubricant.

8. A magnetic fluid bearing according to claim 7, wherein at least one of the jacket flow passages is provided in a conduit disposed outside the jacket, and a filter and a radiator are connected in series to the conduit.

9. A magnetic fluid bearing according to claim 1, 2 or 3, wherein at least one energy storage pipeline is connected to a gap between the outer sleeve and the inner sleeve through the outer sleeve in a bearing area of the bearing, one port of the energy storage pipeline is connected to the gap in the bearing area, the other port of the energy storage pipeline is connected to an energy storage check valve, an energy storage switch valve and an energy storage device, a flow inlet of the energy storage check valve is connected to the other port of the energy storage pipeline, a flow outlet of the energy storage check valve is connected to a flow inlet of the energy storage device, the flow outlet and the flow inlet of the energy storage switch valve are connected in parallel to the flow inlet and the flow outlet of the energy storage check valve, and the energy storage device are filled with magnetic fluid lubricant.

10. A magnetic fluid bearing according to claim 1, 2 or 3, wherein a sleeve or a shaft is provided in the shaft hole of the disc or the ring, the axial length of the sleeve or the shaft is equal to or greater than the distance between the outer side surface of the first yoke and the outer side surface of the second yoke, and an annular tooth groove or a helical tooth groove or a skewed tooth groove or a combination of the annular tooth groove and the skewed tooth groove or the helical tooth groove is provided on the outer circumferential surface of the sleeve or the shaft within the range corresponding to the first yoke and the second yoke.

11. A magnetic fluid bearing according to claim 5, wherein a check valve is provided in the flow passage of the disc or the ring, and the flow inlet of the check valve is directed toward the flow inlet of the flow passage of the disc or the ring.

12. A magnetic fluid bearing according to claim 1, 2 or 3, wherein a magnetically permeable annular spacer is provided in a gap between the inner side of the first yoke or the second yoke and the outer side of the disc or the ring, and the inner diameter of the annular spacer is smaller than the diameter of the axial hole of the disc or the ring.