CN114623162A

CN114623162A - Bearing

Info

Publication number: CN114623162A
Application number: CN202210187674.1A
Authority: CN
Inventors: 王政玉; 王超颖; 岑陈; 张玉芹
Original assignee: Individual
Current assignee: Individual
Priority date: 2022-02-28
Filing date: 2022-02-28
Publication date: 2022-06-14

Abstract

The invention relates to a bearing comprising: the pump wheel is positioned in the outer sleeve, the pump wheel is composed of a hub, a cover plate and blades, the cover plate and the blades are sleeved on the hub, the cover plate is a circular plate body with certain bearing thickness, the outer sleeve is composed of end covers on two sides and a cylinder body in the middle, a sealing structure is arranged at a gap between an inner circular surface of the end cover with an inner circular through hole and an outer circular surface of the hub, and a lubricant filling air release valve is arranged on the outer sleeve. The blade flow passage formed between the cover plate and each blade, the suction flow passage arranged at the outer edge of the hub, and the outer flow passage arranged between the outer surface of the cover plate of the pump wheel and the inner wall surface of the outer sleeve form a circulation flow passage of lubricant, and the circulation flow passage is filled with the lubricant. The bearing has good cooling effect, less or no lubricant leakage, axial and radial bearing capacity and high bearing capacity, can be used as a bearing, and can also be independently used as a rotary sealing device or a collector or a gas-liquid rotary joint with the bearing capacity of the bearing.

Description

Bearing

Technical Field

The invention belongs to the field of supporting and sealing of rotary machinery, and particularly relates to a bearing, lubricating and sealing structure of a bearing and application of the bearing in collector and gas-liquid rotary joint.

Background

The existing mechanical rotary supporting system generally adopts a rolling or common sliding bearing under the working conditions of low load, medium speed, low load and medium load; under the working conditions of high speed and light load, a magnetic suspension or air suspension bearing is required; under heavy load and high speed conditions, static pressure sliding bearings or static and dynamic pressure sliding bearings are generally adopted. In any case, the bearings may be damaged due to improper assembly, improper lubrication, contamination, or overload fatigue. Bearing oil leakage and excessive temperature rise are manifestations of impending bearing failure. The problem of sealing and heat dissipation of the bearing is an important problem for prolonging the service life of the bearing.

The static pressure sliding bearing and the static and dynamic pressure sliding bearing can effectively solve the problem of heat dissipation due to the arrangement of an external lubricating oil circulation subsystem, but the externally arranged subsystem of high-pressure gas or high-pressure liquid needs to be provided with a pressurizing oil pump, an oil return device, an oil receiving device and the like, so that the size, the complexity and the energy consumption of the system are increased, and the application places are limited. Such as gas or liquid hydrostatic bearings or hydrostatic bearing systems employed on steam turbines, whose lubricating medium is supplied by a high pressure gas or liquid lubricant supply subsystem external to the bearing, while requiring the addition of a separate sealing subsystem. In order to prolong the service life of the bearing, the bearing is also provided with a cooling circulation subsystem. The mechanical rotary supporting system formed by the subsystems occupies a large space, has poor operation stability, large operation loss and high operation cost. The following steps are repeated: the novel high-speed railway traction motor has high rotating speed, the running speed of a locomotive is more than 300km/h, the rotating speed of the traction motor is tens of thousands of revolutions per minute, the traditional rolling bearing, static pressure air bearing and static pressure oil film bearing are adopted, and the reliability of an oil supply or air supply subsystem, a sealing subsystem and a cooling subsystem, the vibration and noise of the bearing, the dust prevention and water prevention performance, the space size performance and the like are difficult to meet the requirements.

Since the 1960 s a magnetic fluid bearing was developed which is a bearing employing a magnetic fluid lubricant and which has lubricating, load-bearing and self-sealing capabilities. A magnetic fluid is a stable suspension that has both the liquid fluid properties and the electromagnetic properties of certain solid magnetic materials. 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 and a liquid metal base 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 magnetic fluid bearing is generally composed of a bearing inner sleeve, an outer sleeve, an excitation magnet, magnetic fluid filled between a shaft sleeve and a rotating shaft and the like. 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: since the radial size of the magnetic particles is 3-4 orders of magnitude smaller than the bearing gap, they are not subject to wear; the magnetic fluid bearing has certain self-sealing performance at rest and low speed due to the action between the magnetic field of the excitation magnet and the magnetic fluid, leakage cannot occur, external pollutants cannot enter a gap inside the bearing, certain oil film lubrication can be kept, and an external lubricating oil subsystem and other mechanical sealing subsystems are not needed, so that the magnetic fluid bearing has the characteristics of good sealing performance, small size, strong shockproof capability, high rotation precision, low noise and suitability for high-speed operation. The experimental results in another paper "research on the properties of magnetic fluid lubricated 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 a magnetic field, which shows that the lubrication states of the traditional sliding bearing at starting, low speed and high speed are boundary lubrication or partial oil film lubrication, while the magnetic fluid lubrication bearing is in the boundary lubrication or partial oil film lubrication states at starting and low speed, and good full oil film lubrication can be formed in the higher speed running process, so that the bearing capacity of the magnetic fluid lubrication bearing can be also shown to be 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. Another article on the chinese knowledge network, the study on the static supporting force and lubrication characteristics of magnetic fluid bearings, indicates that: the magnetic fluid lubricating film can still generate supporting and bearing capacity between two low-speed or static planes; for the sliding bearing, the supporting force generated by the magnetic fluid film under the action of the non-uniform magnetic field is larger than the static supporting force of the magnetic fluid film under the uniform magnetic field; two groups of magnetic fluid bearings are installed in parallel, and when a magnetic fluid sealed cavity exists between the two bearings, the axial supporting capacity of the magnetic fluid bearings is more than twice of the static magnetic force of the magnetic fluid without the cavity under the same condition.

In recent years, the application of the magnetic fluid technology in the aspects of rotary support, sealing, lubrication and cooling is continuously developed, but because the existing magnetic fluid bearing has structural problems, a rotating shaft or a shaft sleeve can generate great centrifugal force and frictional heat to the magnetic fluid under the conditions of high speed and heavy load, so that the magnetic fluid has the problems of throwing leakage, temperature rise, bearing capacity reduction, sealing capacity reduction, permanent magnet demagnetization and the like. 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 order to solve the problem of centrifugal force generated throwing leakage to the magnetic fluid, the turbofan arranged at two ends of the bearing of the magnetic fluid bearing in the reference 1 (CN 202010343564.0) has a certain effect of preventing the throwing leakage of the magnetic fluid, but because the inner ring of the bearing generates a magnetic circuit short circuit to the excitation permanent magnet, the magnetizing and adsorbing effect of the magnetic field of the permanent magnet to the magnetic fluid and the improvement of the bearing capacity are greatly reduced, the patent mainly depends on the turbofan to cool and radiate the magnetic fluid, but the position where the turbofan is arranged can not form air current conversion, and the improvement of the heat radiation 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, the sealing capacity and the lubricating performance of the permanent magnet are still reduced or lost. In the "magnetic fluid sliding bearing" of 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, the excitation effect of the magnetic field on the magnetic fluid is very small, and the bearing capacity is very 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 the temperature of the self-sealing bearing.

(2) In the aspect of using magnetic fluid for sealing, in order to solve the problem of near zero leakage of a rotating shaft system lubricant, the magnetic fluid is used for single-stage or multi-stage sealing in a low-pressure-difference environment such as the shaft sealing of a vacuum pump; for high pressure difference environment, such as shaft seal of a high pressure compressor and seal of a stirring shaft of a high pressure reaction kettle, people need to add other mechanical seals besides adopting magnetic fluid seal. Especially under heavy load, high speed and high temperature conditions, the mechanical seal of the engine often fails in long-term operation. The "stepped magnetic fluid sealing device" of reference 3 (patent No. CN 2017113263225.9) can effectively prevent magnetic fluid from being thrown and leaked, and ensure sealing effect, but when operating at high speed, its heat dissipation problem needs to be solved by adding a water jacket, a heat sink and a circulating pump.

(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 4 (patent No. CN 03228086.6), cooling and heat dissipation are performed by a fan attached to the hub. For another example: the "magnetohydrodynamic sliding bearing" of the above-mentioned reference 2 (patent No. CN 201711483127.3) and the "magnetohydrodynamic sliding bearing" of the reference 5 (patent No. CN 201810312388.7) have no structure and measure for separately cooling and dissipating heat, and thus the cooling effect is poor. The following steps are repeated: the "magnetic fluid cooling structure and the corresponding magnetic fluid sealing device" of reference 6 (patent application No. 200820155225.4) cools the magnetic fluid and the permanent magnet by pumping a cooling liquid from the outside. In reference 7, the inventor of the present invention applies (patent No. 202122988716.5, utility model No. 202111453492.6) "a magnetic fluid bearing", which can effectively solve the problems of bearing, sealing, heat dissipation, lubrication, etc. of medium and large bearings, but is only suitable for magnetic fluid lubricants, and has the problems of complex structure, large volume, and high cost for small bearing systems. In contrast, the inventor of the present invention applied to "a magnetic fluid self-sealing bearing" (patent No. 202210035727.8, utility model No. 202220080759.5) which is suitable for high-speed small and large bearings, but is only suitable for magnetic fluid lubricants, and requires a plurality of bearings to be used in parallel when bearing heavy load.

The bearing capacity, high-speed performance, lubricating performance, sealing capacity and the like of the magnetic fluid bearing are closely related to the bearing structure and size, the type of the magnetic fluid, cooling capacity, radial pressure distribution state and the like. It is an urgent task to solve the bearing capacity, sealing capacity, lubricating performance and operational reliability of high-speed and heavy-duty bearings.

(4) In the aspect of the collector electrode required by a motor and an electric appliance, under the conditions of high power and high speed, the collector electrode bears large current and has high linear speed. The allowable linear velocity of the solid brush 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 linear velocity, leakage prevention and cooling of the collector liquid metal become key problems, and the solution proposed in reference 9 (the chinese thesis) (research on collector device for liquid metal of unipolar motor) is very complex in structure and does not have bearing and self-circulation cooling capabilities. To solve the problems of lubrication, cooling, sealing, support and the like of the collector, a comprehensive solution must be adopted.

(5) In the aspect of fluid rotary joints, the currently adopted rotary joints mainly comprise parts such as supporting bearings, sealing rings, compression springs and the like, are large in abrasion and easy to leak, and are not suitable for high-speed rotating occasions.

Disclosure of Invention

The invention aims to provide a novel bearing, which is suitable for running by adopting a general non-magnetic fluid lubricant and a magnetic lubricant, solves the problems of lubricant leakage, heat dissipation, low bearing capacity, low sealing capacity and the like during high-speed running, and further improves the running reliability. While extending to applications in rotary sealing joints and high-speed collectors.

The technical scheme provided by the invention is as follows:

a bearing, comprising: the centrifugal pump is characterized in that the outer sleeve consists of a cylinder body and end covers on two sides of the cylinder body, the end cover on one side is a plate body with a through hole in the center, the end cover on the other side is a solid plate body or a plate body with a through hole or a blind hole in the center, a lubricant filling air release valve is arranged on the outer sleeve, the pump wheel consists of a hub, a cover plate and blades, the cover plate and the blades are arranged on the hub, at least one suction flow channel of the pump wheel is arranged at the joint of the cover plate and the hub, and a sealing structure is arranged at a gap between the inner circular surface of an inner circular hole of the end cover with the through hole in the center and the outer circular surface of the hub;

the space between the cover plate and each blade forms a blade flow passage of the pump wheel, a discharge flow passage of the pump wheel is formed in a gap between the outer edge rotating surface of each blade and the inner circular surface of the outer sleeve, a discharge flow passage of the pump wheel is formed in a gap between the outer edge rotating surface of each blade and the inner circular surface of the cylinder body, a gap between the outer edge rotating surface of the pump wheel and the inner circular surface of the cylinder body, a discharge flow passage and a gap between the outer edge end surface of the cover plate and the inner circular surface of the end cover form an outer flow passage of the pump wheel together, a blade flow passage and a suction flow passage of the pump wheel form an inner flow passage of the pump wheel together, the outer flow passage of the pump wheel is communicated with the inner flow passage of the pump wheel, and the air release valve is communicated with the outer flow passage and the inner flow passage of the pump wheel. And the outer flow passage and the inner flow passage are filled with lubricant.

The jacket comprises various shells which are similar and equivalent to the jacket, can be assembled and are provided with inner cavities. Such as: the end cover on one side is integrated with the cylinder body, and the other end cover can be independently installed.

The jacket can be an integrated structure with a mounting seat, or a cylindrical jacket and the like which are arranged in a bearing seat or an end cover of mechanical equipment, and can be an integral jacket or a split jacket.

The cover plate is a plate body with certain thickness and bearing capacity, the cover plate can be an independent annular body sleeved on the hub, and the cover plate, the blades and the hub can also be manufactured into a whole.

The outer circle rotating contour surface of the pump wheel can also be in an arc shape or an arc shape along the axial contour line, and the shape of the inner circle surface of the outer sleeve is matched with the shape of the outer sleeve so as to adapt to radial fluctuating load.

The radial two sides of the end cover are respectively provided with an end face, and the inner side end face of the end cover is an inner end face of the end cover close to the center of the bearing; the radial two sides of the cover plate are respectively provided with an end face, and the outer end face of the cover plate is the outer end face of the cover plate far away from the center of the bearing.

The suction flow passage can be a flow passage with a uniform cross section or a throttling flow passage with a non-uniform cross section. Reducing the cross-sectional area of the suction flow passage may increase the pressure of lubricant between the end face of the end cap inboard and the end face of the cover plate outboard during operation.

The shape of the inner surface of the cylinder body comprises a cylindrical inner surface or a cylindrical surface in a bearing area, a non-circular surface in a non-bearing area, or the shape of the inner surface of a bearing bush or a shaft sleeve of various conventional sliding bearings.

In this document, the bearing region refers to a region where the gap between the outer peripheral surface of the pump wheel and the inner circumferential surface of the outer sleeve is small after a load is applied, and the non-bearing region refers to a region where the gap between the outer peripheral surface of the pump wheel and the inner circumferential surface of the outer sleeve is large after a load is applied.

The hub can be in the shape of a cylinder with equal diameter, an olive-shaped or stepped cylinder with unequal diameter, or a cylinder combined by the cylinder and the step. The inner circle surface of the hub is provided with a key slot.

The outer surface of the hub is provided with at least one suction flow channel of the pump wheel, namely the suction flow channel is arranged on the hub or on a cover plate close to the hub or between the hub and the cover plate.

In the present specification, the term "a" or "an" means that the element is included in a certain range on or near the element.

The outer edge rotating surface of the pump wheel is an integral rotating profile surface of the pump wheel and comprises an outer circle rotating surface of a cover plate and an outer edge rotating surface of a blade.

The lubricant comprises: lubricating oil, grease, water, magnetic fluid lubricant, non-magnetic fluid lubricant, gas lubricant, solid lubricant, and the like. The solid lubricant is solid lubricating material which is cladded on the inner circular surface of the cylinder body of the outer sleeve and the inner side end surface of the end cover of the outer sleeve or the outer side end surface and the outer circular surface of the cover plate of the pump impeller. The added lubricant comprises full or partial lubricant.

The lubricant can be added with one kind of lubricant or added with lubricants with different properties at different positions. For example: lubricating grease can be filled in a gap between the inner circular surface of the inner circular hole of the end cover of the outer sleeve and the corresponding outer circular surface of the hub to play a role in sealing and lubricating, and at the moment, a lubricating agent filling air release valve is required to be independently arranged on the end cover; lubricating oil or water is filled in the inner flow passage and the outer flow passage to play a role in lubrication; a layer of polytetrafluoroethylene solid lubricant can be cladded on the inner surface of the cylinder body of the outer sleeve and the inner side end surface of the end cover of the outer sleeve or the outer side end surface and the outer circular surface of the cover plate of the pump wheel, so that the wear-resisting and lubricating effects are achieved.

The materials of the outer sleeve and the cover plate of the pump wheel can be porous materials such as powder metallurgy, and the like, and the pores of the porous materials are fully soaked with lubricating oil, so that the oil-free lubrication bearing is realized.

The bearing has the following optional technical scheme: and oil wedges or oil cavities with different structures adopted by the existing hydrodynamic pressure lubricating bearing can be selectively arranged on the inner circular surface of the cylinder body of the outer sleeve or the end surface of the inner side of the end cover of the outer sleeve according to different working condition requirements.

The bearing has the following optional technical scheme: at least one cover plate flow channel which radiates in the radial direction is arranged on the cover plate, a flow inlet of the cover plate flow channel is communicated with the suction flow channel, and a flow outlet of the cover plate flow channel is communicated with a gap at the outer circular surface of the cover plate. The cover plate flow passage and the suction flow passage form an inner flow passage together.

The bearing has the following optional technical scheme: the outer sleeve flow passage can also be a discharge flow passage communicated with the pump wheel and a suction flow passage communicated with the pump wheel by at least one pipeline penetrating through the outer sleeve and outside the outer sleeve. The pipeline can be connected with a throttle valve, a radiator and the like in series.

The bearing has the following optional technical scheme: on the outer sleeve, at least four pipelines are communicated with the gap between the bearing outer sleeve and the pump wheel, wherein at least two pipelines are oil inlet pipes, the other two pipelines are oil outlet pipes, the oil inlet pipes and the oil outlet pipes are arranged in a staggered mode at intervals of a spatial distance along the circumference, a throttler, an oil supply pump, an energy accumulator, a filter, an oil tank and the like are connected between outer ports of the pipelines, the connection mode of the throttler, the oil supply pump, the energy accumulator, the filter, the oil tank and the like is the same as that of the existing hydrostatic bearing, and the repeated description is omitted.

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. Alternatively, a lubricant filling hole can be directly formed in the outer 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 outer side end face of the cover plate is in clearance fit with the inner side end face of the end cover, and the axial clearance sizes of the cover plate and the end cover can be the same; the gap with different sizes can be set according to the requirements of working conditions, namely the thickness of the end cover corresponding to the bearing area and the thickness of the end cover corresponding to the non-bearing area are designed into different thicknesses so as to obtain gaps with different sizes, the sectional area of the gap corresponding to the bearing area is different from that of the gap corresponding to the non-bearing area, different throttling effects on the lubricant in the bearing area and the non-bearing area are achieved, and therefore the radial forces borne by the hub in different areas on the circumference are different.

The structural type of the pump impeller in the technical scheme comprises: the pump impeller is a semi-open type pump impeller with the cover plate on one side and the cover plate on the other side, or an open type pump impeller with the cover plate in the middle and the blades on two sides; the cross section of the blade comprises a straight blade with a uniform cross section or unequal cross sections, an arc blade with a uniform cross section or unequal cross sections and the like; or a centrifugal pump wheel with various structures such as diffusion blades and the like is arranged between the two blades; the outer contour shape of the radial axial section of the pump wheel can be a symmetrical trapezoid or an asymmetrical trapezoid, and can also be a symmetrical rectangle or an asymmetrical rectangle, and the like; the section of the blade flow passage of the pump wheel can be a uniform section flow passage, and can also be a divergent section or a convergent section flow passage. The pump wheel structure can also be a Tesla pump type impeller formed by stacking more than three disks at certain axial intervals. The radial center line of the pump wheel can be perpendicular to the axial center line of the hub, and can also be an inclined pump wheel forming an acute angle with the axial center line of the hub.

The bearing has the following optional technical scheme: the blades of the pump wheel are at least two grooves or holes which are uniformly arranged on a cover plate of the pump wheel and radiate along the circumferential radial direction, a partition wall formed between the two grooves or the two holes plays a role of the blade, the inner port of each groove or hole is communicated with the suction flow channel, and the outer port of each groove or hole is communicated with the discharge flow channel. The groove is arranged on the side end face of the cover plate, and the hole is arranged in the cover plate body. The grooves or holes radiating radially along the circumference can be straight-line grooves or holes, and can also be oblique-line or curved-line grooves or holes.

The bearing has the following optional technical scheme: a sealing structure is arranged at a gap between the inner circular surface of the end cover with the through hole at the center and the outer circular surface of the hub, the sealing structure is that tooth grooves or grooves are arranged on the inner circular surface of the inner circular hole of the end cover of the outer sleeve or the outer circular surface of the hub of the pump wheel corresponding to the inner circular surface, and the axial section profile shapes of the teeth of the tooth grooves are symmetrical triangles, rectangles, trapezoids, arcs and the like, or asymmetrical triangles, rectangles, trapezoids and the like; the tracks of the grooves formed on the whole circular surface by the tooth grooves can be circular, spiral or parabolic and the like, and form a non-contact sealing structure of labyrinth seal or centrifugal seal or spiral seal, and the sealing gaps are filled with lubricant.

The bearing has the following optional technical scheme: and a sealing structure is arranged at a gap between the inner circular surface of the through hole of the end cover with the through hole in the center and the outer circular surface of the hub, and a sealing ring is arranged between the inner circular surface of the inner circular hole of the end cover of the outer sleeve and the outer circular surface of the hub. The preferred scheme is as follows: a concave annular cavity is arranged at an inner circular hole of the end face of the inner side of the end cover, a graphite thin ring or a layer of solid lubricant is cladded on the inner surface of the annular cavity, an annular groove is arranged on the outer circular surface of the hub, and a V-shaped, V-shaped or U-shaped elastic sealing ring with a spring is arranged in the annular cavity of the end cover and the annular groove of the hub to form contact sealing. When the sealing device is static, the sealing device is opened by a hook-shaped, V-shaped or U-shaped elastic sealing ring through a spring; when the pressure of the lubricant in the inner cavity of the bearing is higher than the external pressure, the pressure of the lubricant can enable the annular sealing ring to effectively seal a gap between the end cover and the hub; when the pressure at the suction flow passage of the bearing inner cavity is lower than the external pressure, the lubricant can continuously flow into the blade flow passage, and the lubricant cannot axially leak from the gap at the inner circular surface of the end cover. When the pump wheel generates small axial movement, the opening of the V-shaped or U-shaped elastic sealing ring with the spring is compressed or automatically opened to keep a sealing state. The second preferred scheme is as follows: a concave annular cavity is arranged at an inner circular hole of the end face of the inner side of the end cover, an annular groove is arranged at the outer circular face of the hub, an annular permanent magnet with a plurality of annular tooth grooves on one end face is placed into the annular cavity and the annular groove, the annular permanent magnet is sealed and fixed in the annular groove on the hub, and a magnetic lubricating sealant is filled in the annular tooth grooves.

The bearing has the following optional technical scheme: the sealing structure is characterized in that a permanent magnetic inner sleeve is arranged on the inner circular surface of the inner circular hole of the outer sleeve end cover, the permanent magnetic inner sleeve is composed of an annular magnetic ring, annular polar plates positioned on two sides of the annular magnetic ring and an air gap or a magnetism isolating body arranged on the non-N, S magnetic polar surface of the annular magnetic ring, the permanent magnetic ring is axially excited, and a tooth groove is formed in the inner circular surface of the annular polar plate; or a permanent magnetic outer sleeve is arranged on the outer circular surface of the hub, a tooth groove is arranged on the outer circular surface of the annular polar plate, and a magnetic lubricating sealant is filled in the gap of the tooth groove. At this time, a lubricant filling and discharging valve needs to be arranged on the end cover. The permanent magnetic inner sleeve or the permanent magnetic outer sleeve can also be a hollow cylindrical magnet, the hollow cylindrical magnet is excited in the radial direction, and a tooth groove is formed in the outer circular surface or the inner circular surface of the hollow cylindrical magnet.

The bearing has the following optional technical scheme: the outer side end face of the cover plate of the pump wheel is provided with annular teeth or grooves, the inner side end face of the end cover of the outer sleeve is provided with annular grooves or teeth, the teeth or grooves on the outer side end face of the cover plate are matched with the grooves or teeth on the inner side end face of the end cover to form a non-contact gap sealing structure, and meanwhile, the inner circle face of the inner circle hole of the end cover of the outer sleeve is provided with a permanent magnetic inner sleeve.

The bearing has the following optional technical scheme: a concave annular cavity is arranged at an inner circular hole of the end face of the inner side of the end cover, a layer of solid lubricant is cladded on the inner surface of the annular cavity, an annular groove is arranged at the outer circular surface of the hub, a V-shaped or U-shaped elastic sealing ring with a spring is arranged in the annular cavity of the end cover and the annular groove of the hub to form contact sealing, and meanwhile, a permanent magnetic inner sleeve is arranged on the inner circular surface of the inner circular hole of the end cover of the outer sleeve.

The bearing has the following optional technical scheme: an oil groove is arranged on the inner circular surface of the cylinder body of the outer sleeve corresponding to the non-bearing area, and the oil groove comprises an axial or circumferential or oblique or threaded line.

The bearing has the following optional technical scheme: an annular rolling groove is formed in the inner circular surface of the cylinder body of the outer sleeve and the outer circular surface of the cover plate of the pump wheel, a rolling body is arranged in the annular rolling groove, and a retainer is arranged on the rolling body.

The equivalent scheme of the technical scheme can also be as follows: and a traditional sliding bearing or rolling bearing is arranged between the inner circular surface of the cylinder body of the outer sleeve and the outer circular surface of the cover plate of the pump wheel. At the moment, the traditional sliding bearing or rolling bearing replaces the bearing function between the cylinder body and the cover plate, for the purpose, an outer shell of the traditional bearing is used as one part of the cylinder body, an inner sleeve of the traditional bearing is used as one part of the cover plate or the cover plate, and an outer sleeve of the original bearing still plays roles in sealing, heat dissipation and supporting.

The bearing has the following optional technical scheme: an annular rolling groove is formed in the end face of the inner side of the end cover of the outer sleeve and the end face of the outer side of the cover plate of the pump wheel, a rolling body is arranged in the annular rolling groove, and a retainer is arranged on the rolling body, so that the thrust bearing is formed.

The equivalent scheme of the technical scheme can also be as follows: a conventional thrust bearing is mounted between the inboard end face of the end cap of the outer sleeve and the outboard end face of the cover plate of the pump wheel.

The bearing has the following optional technical scheme: an annular rolling groove is formed in the inner circular surface of the cylinder body of the outer sleeve and the outer circular surface of the cover plate of the pump wheel, a rolling body is arranged in the annular rolling groove, and a retainer is arranged on the rolling body; and an annular rolling groove is formed in the end face of the inner side of the end cover of the outer sleeve and the end face of the outer side of the cover plate of the pump wheel, a rolling body is arranged in the annular rolling groove, and a retainer is arranged on the rolling body.

The bearing has the following optional technical scheme: an exciting body is arranged on the cylinder body in the non-bearing area, and a separating magnet is arranged on the non-N, S magnetic pole surface of the exciting body, wherein the separating magnet is an air gap or a diamagnetic or paramagnetic low-permeability material. The exciter acts to suspend the pump impeller.

The bearing has the following optional technical scheme: a pipeline is connected to the gap between the outer sleeve and the pump wheel, one end of the pipeline is communicated with the gap, and the other end of the pipeline is communicated with an oil reservoir or an oil cup. The oil reservoir or cup stores lubricant.

The bearing has the following optional technical scheme: at least one pipeline is arranged, one end port of the pipeline is communicated with a gap in a bearing area between the inner circular surface of the cylinder body of the outer sleeve and the outer circular surface of the pump wheel cover plate, the other end port of the pipeline is communicated with a gap in a non-bearing area between the inner circular surface of the cylinder body of the outer sleeve and the outer circular surface of the pump wheel cover plate, and a starting pressurized oil pump and an oil storage tank are connected in series on the pipeline. Before the bearing runs, the pressurizing oil pump is started to enable the pump wheel to float, so that the pump wheel is prevented from colliding with the outer sleeve; after the bearing is operated, the start-up pressurizing oil pump can be closed, and the lubricating oil pressurized by the pump wheel can generate a lubricating oil film.

The bearing has the following optional technical scheme: at least one energy storage pipeline is connected to a gap in a bearing area between the outer edge rotating surface of the pump wheel and the inner circular surface of the cylinder body of the outer sleeve, 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 a one-way valve, a switch valve or a pressure flow control valve and an energy accumulator, a flow inlet of the one-way valve is communicated with a flow outlet of the energy storage pipeline, a flow outlet of the one-way valve is communicated with a flow inlet of the energy accumulator, and the switch valve or the pressure flow control valve is connected to the flow inlet and the flow outlet of the one-way valve in parallel.

The bearing has the following optional technical scheme: an annular confluence groove is arranged on the end cover at the outflow port of the outer sleeve runner or the inflow port of the suction runner on the corresponding cover plate along the circumference.

The bearing has the following optional technical scheme: the end cover is provided with at least two screw holes, and screws are arranged during disassembly, so that disassembly is convenient.

The bearing has the following optional technical scheme: when the outer surface of the outer sleeve is a round surface, a positioning hole or a positioning groove or a key slot is arranged on the outer round surface of the outer sleeve.

The bearing has the following optional technical scheme: and radial grooves are formed in the end face of the inner side of the end cover to increase the circulation flow of the lubricant.

The bearing has the following optional technical scheme: an annular gasket is additionally arranged in a gap between the end face of the inner side of the end cover and the end face of the outer side of the cover plate, radial grooves or through holes can be formed in the annular gasket, the gasket is used for adjusting the axial gap, and the grooves or the through holes in the gasket form lubricant flow passages.

The bearing has the following optional technical scheme: and a bearing bush or an inner bushing is arranged on the inner circular surface of the cylinder body of the outer sleeve or the end surface of the inner side of the end cover of the outer sleeve. According to different requirements of working conditions, oil wedges or oil cavities with different structures adopted by the existing liquid hydrostatic lubrication bearing are arranged on the inner contour surface of the bearing bush or the inner bushing.

The bearing has the following optional technical scheme: an oil level gauge is arranged on the outer sleeve through a pipeline. One end port of the pipeline is communicated with the discharge flow channel at the bottom of the pump wheel, and the other end port of the pipeline is communicated with the inlet of the oil level gauge.

The purpose and the function of the pump impeller in the invention are different from the main purpose and the function of the pump impeller of the existing centrifugal pump, the main purpose and the function of the pump impeller of the existing centrifugal pump are to lift or circulate liquid outwards, and the pump impeller in the invention realizes the circulation of lubricant in an outer flow passage and an inner flow passage of a bearing, so that the heat dissipation capacity, the lubrication performance and the bearing capacity are improved. The outer sleeve of the centrifugal pump is different from the pump shell structure of the existing centrifugal pump, the inner cavity of the pump shell of the existing centrifugal pump is in a vortex shape and needs to be provided with the isolating tongue, the inner cavity surface of the cylinder body of the outer sleeve of the centrifugal pump is in a cylindrical shape or a non-cylindrical shape, the isolating tongue does not need to be arranged, and the cylinder body needs to bear the load on the cover plate.

When the bearing operates, the pump impeller rotates, and an oil wedge is formed between the outer circular surface of the cover plate of the pump impeller and the inner circular surface of the outer sleeve in a bearing area and bears load; the vanes of the pump wheel pump the lubricant to circulate in the inner flow passage and the outer flow passage of the pump wheel, so that the working condition of the dynamic pressure bearing or the dynamic and static pressure bearing is realized, and meanwhile, the convective heat transfer of the lubricant is realized, thereby improving the heat transfer efficiency.

In the bearing of the invention, the power for circulating the lubricant comes from the pumping action generated by the pump wheel in the bearing, and is different from the pumping effect of the existing hydrostatic bearing with a circulating pump arranged from the outside, and the differences are that: when the pressure of the externally installed circulating pump is too high, the lubricant can be caused to leak along the axial direction at the gap between two end faces of the traditional bearing, but the bearing of the invention has the advantages that the pump wheel is enclosed in the outer sleeve, the pumping force is generated in the inner part, the lubricant in the gap can continuously and circularly flow in the inner part according to the continuity principle of hydromechanics, a low-pressure or negative-pressure area is generated at the suction flow channel of the pump wheel, and the lubricant cannot be thrown to the outside at two ends of the hub. The seal structure between the inner circumferential surface of the end cover and the outer circumferential surface of the hub prevents leakage of the lubricant even if the pressure at the suction flow passage of the pump impeller is greater than the external pressure. The higher the speed of rotation, the greater the load bearing and sealing capability.

The bearing has the following optional technical scheme: the outer sleeve is provided with at least one outer sleeve flow channel, the outer sleeve is provided with a flow inlet and a flow outlet, the flow inlet of the outer sleeve flow channel is communicated with a gap between the outer edge rotating surface of the pump impeller and the inner circular surface of the outer sleeve, the flow outlet of the outer sleeve flow channel is communicated with the suction flow channel through a gap between the inner side end surface of the end cover and the cover plate, and the outer sleeve flow channel is filled with lubricant. The outer sleeve flow passage can also be connected with a throttler, a radiator, a filter and the like in series.

The inlet of the outer sleeve runner is communicated with the gap at the outer edge rotating surface of the pump impeller, the inlet of the outer sleeve runner is communicated with the gap at the outer circular surface of the cover plate of the pump impeller or the inlet of the outer sleeve runner is communicated with the gap at the outer edge of the blade in the bearing area, and the inlets of the inner and outer sleeve runners are communicated with the discharge runner of the pump impeller in the non-bearing area. In the technical scheme, a confluence groove can be arranged at the flow inlet of the outer sleeve flow passage along the circumference, and the confluence groove can be continuous or discontinuous along the circumference.

The jacket flow channel arranged on the jacket consists of an axial flow channel and a radial flow channel which are arranged on the end cover of the jacket, and a radial flow channel and an axial flow channel which are arranged on the cylinder body of the jacket, and all the axial flow channels are communicated with each other.

The bearing has the following optional technical scheme: the outer sleeve flow passage can also be an independent pipeline arranged outside the outer sleeve. The inlet of the pipeline is communicated with the gap at the rotating surface of the outer edge of the pump wheel, and the outlet of the pipeline is communicated with the gap at the corresponding suction flow channel through the cover plate. The independent pipeline can also be connected with a throttler, a radiator, a filter and the like in series.

In the technical scheme, the flow passage is arranged on the outer sleeve or outside the outer sleeve, so that the circulation flow and the heat dissipation capacity of the lubricant can be enhanced.

And a throttler is arranged on the outer sleeve flow channel. The method comprises the steps that throttle valves are arranged on all jacket runners, or throttle valves are arranged on the jacket runners corresponding to the bearing areas according to working condition requirements, and no throttle valve is arranged on the jacket runners corresponding to the non-bearing areas. The throttle valve can be arranged in a radial or axial jacket flow passage on an end cover of the jacket, and also can be arranged on a radial or axial jacket flow passage on a cylinder body of the jacket.

The bearing has the following optional technical scheme: in the non-bearing area, the sectional area of a radial runner on the cylinder body is smaller than that of an axial runner on the cylinder body, and the diameter of a flow outlet of the axial runner at the joint of the axial runner and the radial runner is smaller than that of other parts of the axial runner, so that a nozzle is formed; according to the Bernoulli principle, when the pump wheel runs at high speed, the pressurized lubricant flows through the nozzles of the axial flow passages to suck the lubricant in the radial flow passages, and negative pressure is formed at the gaps of the outer circular surfaces of the cover plates so as to relieve the radial pressure of the lubricant on the pump wheel in the non-bearing area.

The bearing has the following optional technical scheme: and a throttler or a throttler is arranged on the outer sleeve flow passage.

The bearing has the following optional technical scheme: and a bearing bush or an inner bushing is arranged on the inner circular surface of the cylinder body of the outer sleeve or the inner side surface of the end cover of the outer sleeve, and an oil groove and a radial oil hole are formed in the bearing bush or the inner bushing.

The bearing has the following optional technical scheme: the flow passage of the outer sleeve is provided with a throttleer or a throttleer, the inner circular surface of the cylinder body of the outer sleeve or the inner side surface of the end cover of the outer sleeve is provided with a bearing bush or an inner bushing, and the bearing bush or the inner bushing is provided with an oil groove and a radial oil hole. According to the requirements of different working conditions, oil wedges or oil cavities with different structures adopted by the traditional hydrodynamic lubrication bearing are arranged on the inner contour surface of the bearing bush or the inner bushing.

The bearing has the following optional technical scheme: the outer surface of the outer sleeve is provided with radiating fins.

The bearing has the following optional technical scheme: and the outer edge of the cover plate is provided with an axial groove or an axial through hole.

The bearing has the following optional technical scheme: the bearing bush or the inner bushing is in spherical contact with the inner circular surface of the outer sleeve to form the self-aligning sliding bearing so as to automatically adapt to the deformation of the shaft.

The bearing bush or the inner bushing comprise bearing bush or inner bushing structures and materials which are adopted by various existing sliding bearings adapting to different working conditions. The inner contour surface of the bearing bush or the inner bushing can be a circular surface, or can be designed into a partial circular surface and a partial non-circular surface according to the requirements of working conditions. For example: circular surfaces in the bearing area, elliptical surfaces in the non-bearing area, etc.

The bearing bush or the inner bushing on the inner circular surface of the cylinder body of the outer sleeve can be in interference fit or fused with the inner circular surface of the cylinder body into a whole, and can also be in clearance fit with the inner circular surface of the cylinder body of the outer sleeve to form a floating slip ring.

The bearing has the following optional technical scheme: tooth sockets or grooves are arranged on the end face of the outer side of the cover plate or the end face of the inner side of the end cover, and tooth sockets or grooves are arranged on the inner circular face of the inner circular hole of the end cover or the outer circular face of the corresponding hub.

The inner circle surface of the end cover of the outer sleeve or the outer circle surface of the hub of the pump wheel corresponding to the inner circle surface is provided with a tooth socket or a groove, the cross section of the outer sleeve is the tooth socket when the outer sleeve is cut along the axial radius, the cross section outline shape of the tooth socket is symmetrical triangle, rectangle, trapezoid, arc or the like, or asymmetrical triangle, rectangle, trapezoid or the like; when the tooth grooves on the outer circular surface of the hub of the pump wheel are triangular teeth, the tooth inclined surface on the outermost side of the hub is provided with grooves which are uniformly distributed in a radiation manner, and the grooves can pump lubricant to the center of the bearing when the pump wheel rotates forwards or reversely. The section of the groove is a groove when the groove is cut along the radial radius, the groove can be at least one continuous or discontinuous groove, the track of the groove on the outer circular surface of the hub can be a circular ring shape, a spiral shape or a parabola shape or a circular ring shape or a spiral groove consisting of a plurality of herringbone or oblique grooves, or other various groove structure shapes adopted by the existing shaft seal. The gullets or grooves may also be composite gullets or grooves of various combinations of gullets or grooves described above, for example, a composite sealing structure in which helical grooves are provided on the outer side of two end regions or one end region on the hub, and annular grooves of triangular teeth are provided on the inner side of two end regions or one end region. Multiple tooth grooves or multiple grooves can effectively improve the bearing capacity and the sealing capacity.

The bearing has the following optional technical scheme: the excitation body is arranged on the outer sleeve or the cover plate, the non-N, S magnetic pole surface of the excitation body is provided with a magnetism isolating body, the magnetism isolating body is made of low-permeability materials of air gaps or diamagnetic substances or paramagnetic substances, the inner circular surface of the cylinder body is provided with an axial groove, the end surface of the inner side of the end cover is provided with a radial groove, the inner circular surface of the inner circular hole of the end cover with the central hole or the outer circular surface of the corresponding hub is provided with a tooth socket or a groove, the outer sleeve, the cover plate and the hub are made of magnetic conductive materials, and the tooth socket or the groove and each flow passage and each gap are filled with magnetic fluid lubricants. The bearing with exciter and magnetic fluid lubricant belongs to magnetic fluid bearing.

When the outer sleeves on the two sides of the bearing or the two cover plates of the pump wheel are simultaneously provided with the excitation bodies, the polarities of the two excitation bodies are oppositely arranged along the same axial polarity. Excitation bodies can be arranged on the two end covers of the outer sleeve and the cylinder body of the outer sleeve at the same time, and can be uniformly distributed along the circumference or non-uniformly distributed according to different positions of a bearing area; the permanent magnets can also be arranged on the outer sleeve and the cover plate of the pump wheel. The magnetic field of the permanent magnet plays a role in improving the axial and radial sealing capacity and the axial and radial bearing capacity of the bearing through the magnetic fluid.

In the technical scheme, the exciter body can be a permanent magnet, an electromagnet or an exciter body formed by mixing the permanent magnet and the electromagnet; the excitation can be homopolar excitation or heteropolar excitation; the magnetic field intensity of the excitation body along the circumference can be uniform or uneven in bias, and the magnetic suspension effect of a certain degree can be realized by the uneven bias magnetic field. When the excitation body is arranged on the end cover of the outer sleeve, axial excitation is adopted; when the excitation body is placed on the cylinder body of the outer sleeve, the excitation body is preferably placed on the outer sleeve corresponding to the cover plate of the pump impeller, and radial excitation is adopted; when the radial excitation of the electromagnetic coil is adopted, the electromagnetic coil is arranged on the cylinder body of the outer sleeve corresponding to the excircle surface of the cover plate of the pump wheel, the electromagnetic coil is uniformly or non-uniformly distributed along the circumference, and the number of turns of each coil in the bearing area and the number of turns of each coil in the non-bearing area can be different, so that the purpose of magnetic bias suspension is achieved. The number of turns or the current of the magnet exciting coils at different positions can be controlled, so that the magnetization intensity of the magnetic fluid lubricant and the magnetic bias degree of the pump wheel can be controlled, the pressure distribution of the bearing along the circumference can be adjusted, and the purposes of adjusting the pressure difference between a bearing area and a non-bearing area, the bearing capacity and the resonance frequency point of a shaft are achieved. The exciter can be a permanent magnet only arranged on the cover plate of the pump wheel, and can adopt radial excitation or axial excitation. The magnetizing action of the exciting body on the magnetic fluid lubricant can improve the rigidity of the magnetic fluid lubricant along the direction of magnetic lines of force, thereby improving the bearing capacity and the sealing capacity of the bearing.

The bearing has the following optional technical scheme: the N pole face or the S pole face of the exciting body can be separately provided with a pole plate.

The bearing has the following optional technical scheme: a pipeline is connected to the gap between the outer sleeve and the pump wheel, one end of the pipeline is communicated with the gap, and the other end of the pipeline is communicated with an oil reservoir. The oil reservoir stores magnetic lubricant therein.

The bearing has the following optional technical scheme: the outer sleeve flow passage can also be an independent pipeline arranged outside the outer sleeve. The inlet of the pipeline is communicated with the gap at the rotating surface of the outer edge of the pump wheel, the outlet of the pipeline passes through the cover plate and is communicated with the gap at the corresponding suction flow channel of the cover plate, and the flow channel is filled with magnetic fluid lubricant. The independent pipeline can also be connected with a throttler, a radiator, a filter and the like in series.

The bearing has the following optional technical scheme: and oil wedges or oil cavities with different structures adopted by the traditional hydrodynamic pressure lubrication bearing are arranged on the inner circular surface of the cylinder body of the outer sleeve or the end surface of the inner side of the end cover of the outer sleeve according to the requirements of different working conditions.

The bearing has the following optional technical scheme: and a bearing bush or an inner bushing is arranged on the inner circular surface of the cylinder body of the outer sleeve or the end surface of the inner side of the end cover of the outer sleeve. According to the requirements of different working conditions, oil wedges or oil cavities with different structures adopted by the traditional hydrodynamic lubrication bearing are arranged on the inner contour surface of the bearing bush or the inner bushing.

The bearing has the following optional technical scheme: and the lubricant with different properties is filled in different positions. For example: a gap between the inner circular surface of the inner circular hole of the end cover of the outer sleeve and the outer circular surface of the hub can be filled with magnetic fluid lubricant, and at the moment, a lubricant filling and air release valve needs to be arranged on the end cover; lubricating oil or water is filled in the inner flow passage and the outer flow passage; and cladding a layer of polytetrafluoroethylene solid lubricant on the inner circular surface of the cylinder body of the outer sleeve and the end surface of the inner side of the end cover of the outer sleeve or on the end surface and the outer circular surface of the cover plate of the pump impeller.

The bearing has the following optional technical scheme: and a sealing ring is arranged between the inner circular surface of the inner circular hole of the end cover with the central hole of the outer sleeve and the outer circular surface of the hub. The preferred scheme is as follows: a concave annular cavity is arranged at an inner circular hole of the inner side surface of the end cover, an annular groove is arranged at the outer circular surface of the hub, an annular elastic sealing ring is arranged in the annular cavity of the end cover and the annular groove of the hub, and the contact of the end surface of the annular elastic sealing ring with the end surface of the annular cavity and the end surface of the annular groove is preferably selected to be linear contact. The pressure of the magnetic lubricant in the gap between the end face of the inner side of the end cover and the end face of the outer side of the cover plate can enable the annular elastic sealing ring to effectively seal the gap between the end cover and the hub.

The bearing has the following optional technical scheme: a pipeline is arranged, one port of the pipeline is communicated with a gap in a bearing area between the inner circular surface of the cylinder body of the outer sleeve and the outer circular surface of the pump wheel cover plate, the other port of the pipeline is communicated with a gap in a non-bearing area between the inner circular surface of the cylinder body of the outer sleeve and the outer circular surface of the pump wheel cover plate, and a starting pressure oil pump and a magnetic fluid storage tank are connected to the pipeline in series. The inlet of the starting pressure oil pump can be connected with a one-way valve in series.

The bearing has the following optional technical scheme: a plurality of bearings are combined in parallel to form a bearing group, and the two bearings can be abutted together in the axial direction or separated by a space. When two bearings form a bearing group by a space, the two bearings need to be connected together in a sealing way through a connecting sleeve, the connecting sleeve is provided with a pipeline and a medium filling valve which are communicated with the space, and the filled medium can be inert gas, liquid metal and cooling liquid or the space is pumped into vacuum and the like according to the needs so as to play the roles of isolation protection or increasing the bearing capacity or the sealing capacity. The connecting sleeve can be further provided with two pipelines communicated with the space of the connecting sleeve, the radiator and the circulating pump are connected in series through the two pipelines, and heat-conducting media are injected into the pipelines and the space to improve the heat-radiating capacity.

The lubricant filling and air releasing valve is higher than the outer sleeve to ensure that the lubricant fills the gaps and the flow passages under the action of gravity.

In the technical scheme, when the bearing is static, the static sealing force is generated by the magnetic field of the excitation body through the magnetization adsorption action of the end cover of the outer sleeve and the cylinder body on the magnetic fluid lubricant. During operation, the pumping force generated by the blades of the pump wheel can improve the axial thrust capacity; the unbalanced radial force component created by the pumping process can increase the radial load capacity. When the pump wheel rotates, a low-pressure or negative-pressure area is generated at the suction flow passage of the pump wheel, so that the leakage of the magnetic lubricant along the axial direction is reduced or eliminated. When the jacket is provided with the jacket runner, the pump wheel drives the magnetic fluid lubricant to circulate in the jacket runner, so that the circulation volume and the heat dissipation capacity of the lubricant can be enhanced.

The bearing has the following optional technical scheme: at least one pipeline is connected between the gap corresponding to the outer edge rotating surface of the pump wheel and the gap corresponding to the end cover of the suction flow channel, a throttle valve and a radiator are connected on the pipeline in series, and a filter, an energy accumulator and the like can be connected on the pipeline in series. The pipeline can directly penetrate through the outer sleeve or penetrate through the bearing bush or the inner bushing and the end cover, and the port of the pipeline is communicated with the gap; the end opening of the pipeline can also be directly connected to the cylinder body of the outer sleeve and the end cover, and the cylinder body and the end cover are provided with flow channels which communicate the end opening of the pipeline with the gap.

The throttle valve comprises a small-hole throttle valve or a capillary throttle valve or a slide valve feedback throttle valve or a film feedback throttle valve. The connection mode of the throttle valve, the radiator, the filter, the energy accumulator and the like is basically the same as that of the external lubricating oil supply system of the existing hydrostatic bearing, and the connection mode is not described again.

In the technical scheme, the inflow port of the pipeline can be arranged on the outer circular surface of the outer sleeve or the outer end surface of the end cover, and at the moment, a flow channel is arranged on the outer sleeve or the bearing bush or the inner sleeve and is communicated with the inflow port of the pipeline and a gap at the outer edge of the pump impeller; when the outflow port of the pipeline is arranged on the outer side surface of the end cover, a flow channel is arranged on the end cover, and the flow channel is communicated with the outflow port of the pipeline and a gap at the suction flow channel.

The throttler can adjust the radial pressure at different positions of the circumference of the bearing, the radiator can improve the heat dissipation capacity of the bearing, the filter is used for filtering impurities in the lubricant, and the energy accumulator can store the high-pressure lubricant; the technical scheme is applicable to both the technical scheme of adopting the common lubricant and the technical scheme of adopting the magnetic fluid lubricant.

The bearing has the following optional technical scheme: an energy storage pipeline is connected to a gap in a bearing area between the outer edge surface of the pump wheel and the inner circular surface of the cylinder body of the outer sleeve or through the bearing bush or the inner sleeve and the end cover, 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 a one-way valve, a switch valve or a pressure flow control valve and an energy accumulator, a flow inlet of the one-way valve is communicated with a flow outlet of the energy storage pipeline, a flow outlet of the one-way valve is communicated with a flow inlet of the energy accumulator, and the switch valve or the pressure flow control valve is connected to the flow inlet and the flow outlet of the one-way valve in parallel. In this embodiment, a groove or oil chamber may be provided on the inner circumferential surface of the jacket in the area corresponding to the bearing area.

The energy accumulator and the matched one-way valve, switch valve or pressure flow control valve have the following functions: when the engine runs at a high speed, high-pressure lubricant is injected into the energy accumulator through the one-way valve to be stored and store energy, and when the engine stops or runs at a low speed, the one-way valve is automatically closed; when the pump is restarted or at a low speed, the switch valve or the pressure flow control valve is opened, the stored high-pressure lubricant flows back into a gap of a bearing area, and hard collision or friction is prevented from being generated between the outer circular surface of the cover plate of the pump impeller and the inner circular surface of the cylinder body of the outer sleeve. The throttle valve, the one-way valve, the switch valve or the pressure flow control valve can be manual or can be electromagnetic valves or pneumatic and hydraulic valves which are automatically controlled by various sensors and a programmable controller.

In the technical scheme, the one-way valve, the switch valve or the pressure flow control valve and the energy accumulator can also be directly designed on the sleeve body of the outer sleeve, namely, an energy storage flow channel is directly processed on the sleeve body of the outer sleeve, one end of the energy storage flow channel is communicated with a gap in a bearing area between the outer circular surface of the cover plate of the pump wheel and the inner circular surface of the outer sleeve, and the other end of the energy storage flow channel is communicated with the one-way valve, the switch valve and the energy accumulator which are directly processed and arranged on the sleeve body of the outer sleeve. The technical scheme is applicable to both the technical scheme of adopting the common lubricant and the technical scheme of adopting the magnetic fluid lubricant.

The bearing has the following optional technical scheme: through the outer sleeve, a pipeline is communicated between a gap on the outer circular surface of the cover plate in the bearing area and a gap on the suction flow channel corresponding to the end cover, and an electric oil pump, an oil storage tank, a filter and a switch valve are connected on the pipeline in series. Before the bearing runs, the electric oil pump is started to pump high-pressure oil for the bearing area, and collision between the cover plate of the pump wheel and the cylinder of the outer sleeve is prevented when the electric oil pump is started or at low speed. The electric oil pump may be turned off when the rotational speed of the impeller causes the centrifugal force of the lubricant to reach a level at which the impeller can float. An oil cavity or an oil groove can be arranged on the inner circular surface of the outer sleeve or the inner circular surface of the bearing bush or the bush in the bearing area.

The bearing has the following optional technical scheme: an annular rolling groove is formed in the inner circular surface of the cylinder body of the outer sleeve and the outer circular surface of the cover plate of the pump wheel or in the inner side end surface of the end cover of the outer sleeve and the outer end surface of the cover plate of the pump wheel, a rolling body is arranged in the annular rolling groove, and a retainer is arranged on the rolling body.

The bearing has the following optional technical scheme: at least one axial groove is formed in the inner circular surface of the cylinder, and at least one radial groove is formed in the end face of the inner side of the end cover. When lubricant with higher viscosity is adopted, the axial grooves and the radial radiating grooves can ensure smooth lubricant and small assembly clearance between the cover plate and the end cover.

The bearing has the following optional technical scheme: the hub is provided with at least one hub flow passage, one port of the hub flow passage is communicated with a blade flow passage of the pump wheel, the other port of the hub flow passage is communicated with a flow passage on a shaft of external equipment, a pipeline is connected to a gap corresponding to the outer edge of the blade on a cylinder body of an outer sleeve or a bearing bush or an inner sleeve, one port of the pipeline is communicated with the gap at the outer edge of the blade, and the other port of the pipeline is communicated with the pipeline of the external equipment. The technical scheme can be used as a rotary joint bearing and a rotary joint.

The bearing has the following optional technical scheme: the outer sleeve or the outer sleeve runner is connected with an electrode, the hub is connected with another electrode, the outer sleeve, the hub and the cover plate are made of conductive and magnetic materials, and a space gap between the pump wheel and the outer sleeve is filled with liquid metal magnetic fluid. The technical scheme can be used as a rotary collector bearing and a collector.

The bearing has the following optional technical scheme: the two sides of the end cover of the outer sleeve are provided with the isolation plates, the isolation plates can be in transition fit with the rotating shaft and are fixed on the end cover of the outer sleeve, the isolation plates can also be fixed on the rotating shaft and in transition fit with the end cover of the outer sleeve, the isolation plates can be made of rigid materials or semi-flexible materials, the isolation plates can prevent lubricants from being mutually fused with sealed media, and the dustproof effect can also be achieved.

Has the advantages that: (1) the bearing cooling effect is good. Because of the rotation of the pump wheel and the pumping action of the pump wheel, lubricating oil can circularly flow in the bearing, the convection heat dissipation is realized through the outer surface of the outer sleeve or an external cooler, and the heat dissipation effect is far higher than that of the conduction heat dissipation. (2) The sealing performance is good. Because the lubricant circulates in the bearing, when the pump wheel rotates at high speed, a low-pressure or negative-pressure area can be formed at the suction flow passage of the pump wheel, the lubricant is not easy to leak at two ends of the hub, particularly, when the magnetic fluid lubricant is adopted, the magnetic lubricant is adsorbed in the gap of the tooth socket by a magnetic field, and the leakage cannot be generated at rest or at low speed. When the elastic sealing ring is arranged between the end surface of the inner side of the end cover and the annular groove on the outer circular surface of the hub, and the pressure of the inner cavity of the bearing is higher than the external pressure of the external bearing, the sealing effect is better. (3) The bearing capacity is high. The generation of the bearing capacity comprises the following steps: the bearing capacity generated by an oil wedge between a shaft neck and a shaft sleeve of a traditional dynamic pressure sliding bearing is similar to that between the inner circular surface of a cylinder body of an outer sleeve and a cover plate of a pump wheel; when the non-uniformly arranged exciter body is arranged and the magnetic fluid lubricant is adopted, the thickness and the rigidity of a magnetic oil film in a bearing area are increased by the magnetic fluid under the excitation action of the biased exciter body, so that the bearing capacity is increased; when the pump wheel rotates, the pump wheel generates radial centrifugal force on the lubricant, the throttle valve in the non-bearing area is opened or adjusted, a pressure relief effect is generated, the radial pressure of the non-bearing area is reduced, and the throttle valve in the bearing area is closed or adjusted, a pressure boosting effect is generated, so that the bearing capacity in the bearing area is increased. (4) And the bearing device has axial and radial bearing capacity. Because the pump wheel is enclosed in the inner space of the outer sleeve, the outer circle surface and the end surfaces at two sides of the cover plate of the pump wheel can bear load. (5) The bearing and sealing capacity is adjustable and controllable. By adopting pump wheels with different shapes, tooth sockets or grooves with different shapes and tracks and adjusting the opening degrees of throttle valves at different positions, the axial and radial sealing and bearing capacities with different sizes can be realized so as to adapt to the requirements of different working conditions. (6) The energy consumption is low. Because of adopting good sealing structure, the bearing adopting non-Newtonian fluid lubricating grease with high operation energy consumption is changed into the Newtonian fluid lubricating grease bearing with low operation energy consumption, and the friction loss can be reduced. (7) Has multiple functional purposes. The bearing not only can be used as a bearing, but also can be independently used as a rotary sealing device with bearing capacity; when the liquid metal magnetofluid with better electrical conductivity is adopted, the hub and the outer sleeve are conductors, the outer sleeve and the hub are respectively connected with electrodes, and the bearing can be used as a rotating electrode with bearing, lubricating and sealing capabilities, or an electrical appliance rotating joint or a motor collecting ring. When the through flow channel is arranged on the hub, the rotating shaft and the outer sleeve of the bearing, the bearing can be used as a gas or liquid rotary joint with bearing, lubricating and sealing capabilities.

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

Drawings

Fig. 1 is a schematic diagram of a basic structure of a bearing according to the present invention.

Fig. 2 is a schematic view of a bearing structure with an outer sleeve runner and a throttle valve according to the present invention.

Fig. 3 is a schematic diagram of a basic structure of a bearing with self-sealing capability according to the present invention.

FIG. 4 is a schematic axial cross-sectional view of several pump radii of a bearing of the present invention.

The serial number designations and corresponding designations in the drawings are as follows:

in fig. 1: 10-outer sleeve, 11a, 11 b-outer sleeve end cover, 12-outer sleeve barrel, 15a, 15 b-sealing ring, 20-pump wheel, 21a, 21b, 21 c-pump wheel cover plate, 22a, 22 b-pump wheel blade, 23 a-pump wheel hub, 23 b-pump wheel hub or shaft sleeve, 23 c-pump wheel hub or shaft sleeve, 24a, 24 b-pump wheel blade flow channel, 25a, 25 b-pump wheel suction flow channel, 26a, 26 b-discharge flow channel, 40-lubricating oil filling air release valve.

In fig. 2: 10-outer sleeve, 11-end cover of outer sleeve, 12-cylinder of outer sleeve, 13-bearing bush or inner bushing, 14-radiating fin, 15-sealing ring, 16-outer sleeve flow channel, 17-outer sleeve flow channel inlet, 18-outer sleeve flow channel outlet, 8-annular groove on end cover, 20-pump wheel, 21-cover plate of pump wheel, 9-annular tooth on cover plate, 22-blade of pump wheel, 23-hub of pump wheel, 24-blade flow channel of pump wheel, 25-suction flow channel of pump wheel, 26-discharge flow channel, 27-forward spiral groove, 28-reverse spiral groove, 30-rotating shaft, 40-lubricating oil filling air release valve, 50-throttling valve on outer sleeve, 60-energy storage pipeline, 61-one-way valve, 62-switch valve or pressure flow control valve, 63-energy storage, 64-air release valve.

In FIG. 3: 10-jacket, 11-jacket end cover, 12-jacket cylinder, 13-bearing bush or inner bushing, 15-sealing ring, 16-jacket flow channel, 17-jacket flow channel inlet, 18-jacket flow channel outlet, 19-inner circular surface tooth socket of end cover, 20-pump wheel, 21-pump wheel cover plate, 22-pump wheel blade, 23-pump wheel hub, 24-pump wheel blade flow channel, 27-forward spiral groove, 28-reverse spiral groove, 29-groove on cover plate, 30-rotating shaft, 40-lubricating grease filling air release valve, 50-casing throttle valve, 70-exciting body, 71-magnetic force line, 80, 81-magnet separator, 90-cooler throttle valve, 91-cooler, 92-filter, 60-energy storage pipeline, 61-one-way valve, 62-switching valve or pressure flow control valve, 63-energy storage device and 64-charging air release valve.

In fig. 4: 21-the cover plate of the pump wheel, 22-the blades of the pump wheel, 25-the suction flow channel of the pump wheel, 29-the groove on the cover plate 21 of the pump wheel, and 23-the hub or shaft sleeve of the pump wheel.

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 bearing as shown in figure 1, comprising: the pump wheel 20 is arranged in the outer sleeve 10, the pump wheel 20 is composed of hubs 23a, 23b, 23c, cover plates 21a, 21b, 21c and blades 22a, 22b, the outer sleeve 10 is composed of end covers 11a, 11b and a cylinder 12 on two sides, V-shaped sealing rings 15a, 15b are arranged at the gaps between the inner circular surfaces of the end covers 11a, 11b and the outer circular surfaces of the hubs 23b, 23c, suction flow passages 25a, 25b are arranged at the inner circles of the cover plates 21a, 21b, blade flow passages 24a, 24b are formed between the cover plates 21a, 21b, 21c and the blades 22a, 22b, the blade flow passages 24a, 24b and the suction flow passages 25a, 25b jointly form the inner flow passage of the pump wheel, the flow passages at the outer edge surfaces of the blades 22a, 22b are the discharge flow passages 26a, 26b of the pump wheel, the gaps between the outer circular surfaces of the cover plates 21a, 21b, 21c and the inner circular surfaces of the outer sleeve 12 of the outer sleeve 10 of the pump wheel 20 are in clearance fit with the inner circular surfaces of the cylinder 12 of the outer sleeve 10, the outer edge surfaces of the blades 22a and 22b of the pump impeller 20 are in clearance fit with the inner circular surface of the cylinder 12 of the outer sleeve 10, the outer end surfaces of the cover plates 21a and 21b of the pump impeller 20 are in clearance fit with the inner end surfaces of the end covers 11a and 11b at two sides of the outer sleeve 10, the blade flow passages 24a and 24b of the pump impeller 20 are communicated with the clearance at the outer circular surface of the pump impeller 20, the outer sleeve 10 is provided with a lubricant filling and releasing valve 40, the filling and releasing valve 40 is communicated with the discharge flow passages 26a and 26b of the pump impeller, the outer end surfaces and the outer circular surfaces of the cover plates 21a and 21b, the outer circular surface of the cover plate 21c, the inner end surfaces of the end covers 11a and 11b at two sides and the inner circular surface of the cylinder 12 are coated with a layer of polytetrafluoroethylene solid lubricant, and the lubricant filling and releasing valve 40 fills the bearing clearance and the lubricant with one third of the volume of the flow passages.

When the impeller 20 of the bearing is started, the teflon solid lubricant on the inner circumferential surface of the cylinder 12 can reduce friction and damage between the outer circumferential surfaces of the cover plates 21a, 21b, 21c and the inner circumferential surface of the cylinder 12, and when the impeller 20 rotates, the lubricant is thrown into the gaps through the

discharge flow passages

26a, 26b by the vanes 22a, 22b, and then returns to the

vane flow passages

24a, 24b through the

suction flow passages

25a, 25 b. Lubricating oil circulates in each clearance and runner, improves lubricated effect on the one hand, improves the heat-sinking capability on the other hand. The V-shaped sealing rings 15a, 15b perform a sealing function.

A bearing as shown in figure 2, comprising: the pump impeller 20 is positioned in the outer sleeve 10, the pump impeller 20 is composed of a hub 23, a cover plate 21 and blades 22, a suction flow passage 25 is arranged at the inner edge of the cover plate 21, a blade flow passage 24 between the cover plate 21 and the blades 22 and the suction flow passage 25 jointly form an inner flow passage of the pump impeller, the flow passage at the outer edge of the blades 22 is a discharge flow passage 26 of the pump impeller, the outer sleeve 10 is composed of end covers 11 at two sides and a cylinder 12, the pump impeller 20 is fixed on a rotating shaft 30, the outer circular surface of the cover plate 21 of the pump impeller 20 is in clearance fit with the inner circular surface of the cylinder 12 of the outer sleeve 10, the outer circular rotating surface of the blades 22 of the pump impeller 20 is in clearance fit with the inner circular surface of the cylinder 12 of the outer sleeve 10, the outer end surface of the cover plate 21 of the pump impeller 20 is in clearance fit with the inner end surfaces of the end covers 11 at two sides of the outer sleeve 10, 6 outer sleeve flow passages 16 are arranged on the outer sleeve 10, a flow inlet 17 and an outlet 18 are arranged on the outer sleeve flow passage 16, the inlet 17 of the outer sleeve flow channel 16 is communicated with the gap at the outer edge rotating surface of the pump wheel 20, the outlet 18 of the outer sleeve flow channel 16 is communicated with the gap at the suction flow channel 25 of the pump wheel, the blade flow channel 24 of the pump wheel is communicated with the gap at the outer circle rotating surface of the pump wheel 20, and the outer surface of the outer sleeve 10 is provided with the radiating fin 14. The throttling device 50 is arranged on the outer sleeve flow passage 16, the inner lining 13 is arranged on the inner circular surface of the outer sleeve 10, the inner lining 13 is provided with an axial oil groove and a radial oil through hole, the outer circular surface of the hub 23 is respectively provided with a forward spiral tooth groove 27, a reverse spiral tooth groove 28 and a sealing ring 15, and the inner side end surface of the end cover 11 of the outer sleeve 10 is provided with an annular groove 8 which is in clearance fit with the annular tooth 9 on the outer side end surface of the cover plate 11 of the pump impeller 20. The outer sleeve 10 is provided with a lubricant filling and air discharging valve 40, the filling and air discharging valve 40 is communicated with the outer sleeve flow passage 16, and lubricating oil is filled in each flow passage and each gap. The energy storage pipeline 60 is connected to a gap in a bearing area between the outer edge rotating surface of the pump impeller 20 and the inner circular surface of the cylinder 12 of the outer sleeve 10 through the outer sleeve 10 and the inner sleeve 13, one port of the energy storage pipeline 60 is communicated with the gap in the bearing area, the other port of the energy storage pipeline 60 is communicated with a one-way valve 61, a switch valve 62, an energy storage 63 and a lubricant filling and deflating valve 64, the inflow port of the one-way valve 61 is communicated with the outflow port of the energy storage pipeline 60, the outflow port of the one-way valve 61 is communicated with the inflow port of the energy storage 63, the switch valve 62 is connected to the inflow port and the outflow port of the one-way valve 61 in parallel, and the lubricant filling and deflating valve 64 is connected to the pipeline of the inflow port of the energy storage 63.

Before operation, firstly, lubricant is filled into the cavity of the bearing through the lubricant filling and air release valves 40 and 64 and gas is removed, and when the pump impeller 20 is in a standing state, the sealing ring 15 prevents the lubricant from leaking; when the pump impeller 20 rotates, firstly, the vanes 22 pump the lubricant in the cavities to circulate in the outer sleeve flow passage 16 and the gap between the bearing outer sleeve 10 and the pump impeller 20, so that the lubricating performance and the heat dissipation capacity are improved; secondly, an annular groove 8 on an end cover 11 of the outer sleeve 10 is in clearance fit with an annular tooth 9 on a cover plate 21 of the pump wheel 20 to form labyrinth seal; thirdly, when the pump impeller 20 rotates at a high speed, the lubricant pressurized by the pump impeller 20 is stored in the energy accumulator 63 through the one-way valve 61, and when the engine is restarted or at a low speed, the switch valve or the pressure flow control valve 62 is opened, the stored high-pressure lubricant flows back to a gap in a bearing area between the outer circular surface of the cover plate 21 of the pump impeller 20 and the inner circular surface of the cylinder 12 of the outer sleeve 10, and the outer circular surface of the cover plate 21 and the inner circular surface of the cylinder 12 are prevented from colliding and rubbing with each other. When the pump wheel 20 rotates, the forward spiral tooth grooves 27 and the reverse spiral tooth grooves 28 push the lubricant in the grooves to the center of the bearing, and the lubricant is prevented from leaking in the axial direction. Adjusting the opening of each throttle valve 50 can adjust the radial pressure of the lubricant at different circumferential positions. The pump impeller 20 is more axially sealed when it adopts the structure shown in fig. 3 (e) or (h).

A bearing as shown in figure 3, comprising: the pump impeller 20 and the outer sleeve 10, the pump impeller 20 is located in the outer sleeve 10, the pump impeller 20 is composed of a hub 23, a cover plate 21 and blades 22, a suction flow passage 25 is arranged at the inner edge of the cover plate 21, a blade flow passage 24 between the cover plate 21 and the blades 22 and the suction flow passage 25 jointly form a pump impeller inner flow passage, a flow passage close to the outer edge of the blades 22 is a pump impeller discharge flow passage 26, the outer sleeve 10 is composed of end covers 11 and a cylinder 12 at two sides, the pump impeller 20 is fixed on a rotating shaft 30, the outer circular surface of the cover plate 21 of the pump impeller 20 is in clearance fit with the inner circular surface of the cylinder 12 of the outer sleeve 10, the rotating contour surface of the outer edge of the blades 22 of the pump impeller 20 is in clearance fit with the inner circular surface of the cylinder 12 of the outer sleeve 10, the outer end surface of the cover plate 21 of the pump impeller 20 is in clearance fit with the inner end surfaces of the end covers 11 at two sides of the outer sleeve 10, 6 outer sleeve flow passages 16 are arranged on the outer sleeve 10, a flow inlet 17 and an outlet 18 are arranged on the outer sleeve flow passage 16, the inlet 17 of the outer sleeve flow passage 16 is communicated with the gap at the rotating surface of the edge of the pump wheel 20, the outlet 18 of the outer sleeve flow passage 16 is communicated with the gap at the suction flow passage 25 of the pump wheel, the discharge flow passage 26 of the pump wheel 20 is communicated with the gap at the rotating surface of the outer edge of the pump wheel 20, the end cover 11 of the outer sleeve 10 is provided with the exciting body 70, the non-N, S magnetic pole surface of the exciting body 70 is provided with the magnetic isolation bodies 80 and 81, the magnetic isolation bodies 80 and 81 can prevent the short circuit of the magnetic field nearby, the outer side end surface of the cover plate 21 of the pump wheel 20 is provided with the annular groove 29, the outer sleeve 10, the cover plate 21 and the hub 23 are made of magnetic conductive materials, the outer sleeve flow passage 16 is provided with the throttle 50, the bearing bush 13 is arranged on the inner circle surface of the cylinder 12 of the outer sleeve 10, the bearing bush 13 is provided with a plurality of oil grooves and radial oil holes, and the outer circle surface of the hub 23 is respectively provided with the forward spiral tooth groove 27, the reverse spiral tooth groove 28 and the sealing ring 15. Magnetic fluid lubricant is filled in each flow passage and each clearance. The solid line 71 with an arrow in the figure is the magnetic flux of the field body. The energy storage pipeline 60 is connected to a gap in a bearing area between the outer edge rotating surface of the pump impeller 20 and the inner circular surface of the cylinder 12 of the outer sleeve 10 through the outer sleeve 10 and the inner sleeve 13, one port of the energy storage pipeline 60 is communicated with the gap in the bearing area, the other port of the energy storage pipeline 60 is communicated with a one-way valve 61, a switch valve 62, an energy storage 63 and a lubricant filling and deflating valve 64, the inflow port of the one-way valve 61 is communicated with the outflow port of the energy storage pipeline 60, the outflow port of the one-way valve 61 is communicated with the inflow port of the energy storage 63, the switch valve 62 is connected to the inflow port and the outflow port of the one-way valve 61 in parallel, and the lubricant filling and deflating valve 64 is connected to the pipeline of the inflow port of the energy storage 63. A pipeline is connected between the gap of the inner circular surface of the cylinder 12 and the gap of the suction flow channel 25 corresponding to the cover plate 21 through the outer sleeve 10 and the bearing bush or the inner bushing 13, a throttle valve 90, a radiator 91 and a filter 92 are connected in series on the pipeline, and a lubricant filling air release valve 40 is also connected on the pipeline.

Before operation, the magnetic fluid lubricant is filled in each flow passage and each gap of the bearing through the lubricant filling and exhausting valves 40 and 64, and gas is exhausted, when the bearing is in a standing state, the sealing ring 15 seals the magnetic fluid lubricant, and the exciting magnet 70 adsorbs the magnetic lubricant in the gap through which the magnetic loop passes, so that the magnetic fluid lubricant is prevented from leaking; when the pump impeller 20 rotates, firstly, the vanes 22 pump the magnetic fluid lubricant to circulate in each flow passage, so that the lubricating performance and the heat dissipation capacity are improved; secondly, the magnetic fluid lubricant is further cooled, radiated and filtered through a throttle valve 90, a radiator 91 and a filter 92; thirdly, when the magnetic lubricant pressurized by the centrifugal force of the pump impeller 20 is stored in the accumulator 63 through the check valve 61 during high-speed operation, and when the switch valve 62 is opened during restart or low-speed operation, the stored high-pressure magnetic lubricant flows back to the gap between the bearing area between the outer circumferential surface of the cover plate 21 of the pump impeller 20 and the inner circumferential surface of the cylinder 12 of the outer casing 10, thereby preventing the outer circumferential surface of the cover plate 21 of the pump impeller 20 and the inner circumferential surface of the cylinder 12 of the outer casing 10 from colliding and rubbing with each other. When the pump wheel 20 rotates, the forward spiral tooth grooves 27 and the reverse spiral tooth grooves 28 push the magnetic fluid lubricant in the grooves to the center of the bearing, and the magnetic fluid lubricant is prevented from leaking in the axial direction. Adjusting the opening of each throttle valve 50, 90 allows for adjusting the radial pressure of the magnetic fluid lubricant at different circumferential locations. The pump impeller 20 is more axially sealed when it adopts the structure shown in fig. 3 (e) or (h).

Shown in fig. 4 are several impeller radius axial cross-sectional shapes of a bearing of the present invention.

Fig. 4 (a) is a symmetrical pump impeller structure with rectangular cross section, both sides are provided with cover plates 21, the vanes 22 are arranged between the two cover plates 21, the outer side surface and the outer circular surface of the cover plate 21 are also provided with

annular grooves

29, 25 are suction flow channels of the pump impeller, and 23 are a hub or a shaft sleeve of the pump impeller. The cover plate 21 and the blades 22 of the pump wheel can also be a hollow rotating body, the outer circular surface of the hollow rotating body is provided with an annular groove, the joint of the hollow rotating body and the hub 23 is provided with a suction flow channel 25 of the pump wheel, the hollow rotating body is provided with through holes which are uniformly distributed and radiate along the circumference, the through holes are communicated with the suction flow channel 25 and the annular groove, and the partition wall between the two through holes replaces the action of the blades.

Fig. 4 (b) shows an asymmetric trapezoidal section pump impeller structure, in which a cover plate 21 is provided on one side, vanes 22 are provided on the other side, and annular grooves 29 are provided on the outer end surface and the outer circumferential surface of the cover plate 21. The blades 22 may also be equivalently radial splines formed in the

shroud

21, 23 may be the hub or sleeve of the pump wheel, and the suction flow passages 25 may be provided between circumferentially arranged blades 22. The cover plate 21 and the blades 22 of the pump wheel can also be a hollow rotating body, the connection part of the hollow rotating body and the hub 23 is provided with a suction flow channel 25 of the pump wheel, one side end face of the hollow rotating body is provided with grooves which are uniformly distributed and radiated along the circumference, the grooves are communicated with the suction flow channel 25, and the partition wall between the two grooves replaces the function of the blades.

Fig. 4 (c) shows a symmetrical pump impeller structure with trapezoidal cross section, wherein the two sides are provided with cover plates 21, the vanes 22 are arranged between the two cover plates 21, the outer end surface and the outer circumferential surface of the cover plates are provided with

annular grooves

29, 25 are suction flow channels of the pump impeller, and 23 are a hub or a shaft sleeve of the pump impeller.

Fig. 4 (d) shows a symmetrical pump wheel structure with a trapezoidal cross section, with a cover plate 21 in the middle and vanes 22 on both sides of the cover plate 21. The blades 22 may also be equivalently radial gullets formed in the shroud 21, with the suction flow passages 25 being provided between each set of circumferentially arranged blades 22. 23 is the hub or shaft sleeve of the pump wheel, the outer sleeve flow channels are set into two independent sets of flow channels, and each set of outer sleeve flow channels are respectively provided with a flow inlet corresponding to the pump wheel blade and two lubricant filling and air release valves (not shown in the figure).

Fig. 4 (e) shows a symmetrical pump wheel structure with a rectangular cross section, which has three cover plates 21, two vanes 22 disposed between the three cover plates 21, and

annular grooves

29, 25 for the suction flow channel of the pump wheel and 23 for the hub or shaft sleeve of the pump wheel, which are further disposed on the outer circumferential surface of the cover plate 21. The jacket flow channels are arranged into two independent groups of flow channels, and each group of jacket flow channels are respectively provided with a flow inlet and a lubricant filling and air discharging valve (not shown in the figure) corresponding to the blades.

Fig. 4 (f) shows a symmetrical tesla pump impeller structure with a rectangular cross section, which is provided with four cover plates 21, no shaped blades are arranged between the cover plates 21, the gap between the cover plates 21 is small, lubricant generates centrifugal action similar to the shaped blades by the adhesion action of the surfaces of the cover plates 21 when the pump impeller rotates, 25 is a suction flow passage of the pump impeller, and 23 is a pump impeller hub or a shaft sleeve.

Fig. 4 (g) is a symmetrical trapezoidal pump impeller structure in which the outer diameter of the vane 22 is greater than that of the pump impeller cover plate 21, the vane 22 with a larger outer diameter can generate a larger centrifugal force, the cover plates 21 are disposed on both sides, the vane 22 is disposed between the two cover plates 21, the outer side surface and the outer circumferential surface of the cover plate 21 are further provided with

annular grooves

29, 25 are suction flow channels of the pump impeller, 23 is a hub or a shaft sleeve of the pump impeller, and the inner circumferential surface structure of the outer sleeve is matched with the pump impeller structure. The discharge flow channels of the outer peripheral rotating surface of the vane 22 and the inner circular surface of the outer sleeve corresponding thereto are communicated with the gaps of the outer circular surface of the cover plate of the pump impeller through the outer sleeve flow channels, or through an outer sleeve auxiliary flow channel separately provided on the outer sleeve (not shown in the figure).

Fig. 4 (h) shows a symmetrical rectangular pump impeller structure formed by two vanes 22 and 3 cover plates 21, wherein the two vanes 22 are respectively arranged in the middle of the 3 cover plates 21, the outer end surface and the outer circumferential surface of the cover plate 21 are further provided with annular grooves 29, the grooves 29 and the middle cover plate 21 are beneficial to improving the axial sealing capability, 25 is a suction flow passage of the pump impeller, and 23 is a hub or a shaft sleeve of the pump impeller. The outer sleeve flow passages are arranged into two independent groups of flow passages, and each group of outer sleeve flow passages are respectively provided with a flow inlet and a lubricant filling and air discharging valve (not shown in the figure) corresponding to the blades.

In the above-mentioned fig. 4 (a), (b), (c), (g) and (h), according to the working condition and the structural requirement, the groove 29 may be filled with a non-magnetic material, or may be provided with an annular tooth and rotationally engaged with the groove on the inner side surface of the outer cover.

In the above-mentioned fig. 4 (e) and (h), the cross-sectional profile shape of the outer edge portion of the cover plate 21 located in the middle may be a bilaterally symmetrical or asymmetrical triangle, rectangle, trapezoid, M-shape, inverted W-shape or arc, the surface of each middle shape of the outer edge portion of the cover plate 21 is provided with a groove or a tooth socket, the shape of the corresponding inner surface of the outer sleeve is matched with the cross-sectional profile shape of the outer edge portion of the cover plate, and the two are in rotational clearance fit.

The above embodiments can be used as bearings, or can be used alone as a sealing device with bearing capacity. When the liquid metal magnetic fluid with better electrical conductivity is used as the lubricant, the hub and the outer sleeve are conductors, the outer sleeve and the hub are respectively connected with electrodes, and the bearing can be used as a rotating electrode with bearing, lubricating and sealing capabilities, or an electrical appliance rotating joint or a motor collecting ring. When the through flow channel is arranged on the hub, the matched shaft and the outer sleeve of the bearing, the bearing can be used as a gas or liquid rotary joint 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 bearing, comprising: the centrifugal pump is characterized in that the outer sleeve consists of a cylinder body and end covers on two sides of the cylinder body, the end cover on one side is a plate body with a through hole in the center, the end cover on the other side is a solid plate body or a plate body with a through hole or a blind hole in the center, a lubricant filling air release valve is arranged on the outer sleeve, the pump wheel consists of a hub, a cover plate and blades, the cover plate and the blades are arranged on the hub, at least one suction flow channel of the pump wheel is arranged at the joint of the cover plate and the hub, and a sealing structure is arranged at a gap between the inner circular surface of an inner circular hole of the end cover with the through hole in the center and the outer circular surface of the hub;

the space between the cover plate and each blade forms a blade flow passage of the pump wheel, a discharge flow passage of the pump wheel is formed in a gap between the outer edge rotating surface of each blade and the inner circular surface of the outer sleeve, the outer edge rotating surface of the pump wheel is in clearance fit with the inner circular surface of the cylinder body, the outer end surface of the cover plate is in clearance fit with the inner side end surface of the end cover, the gap between the outer edge rotating surface of the pump wheel and the inner circular surface of the cylinder body, the discharge flow passage and the gap between the outer end surface of the cover plate and the inner side end surface of the end cover form an outer flow passage of the pump wheel together, the blade flow passage and the suction flow passage of the pump wheel form an inner flow passage of the pump wheel together, the outer flow passage of the pump wheel is communicated with the inner flow passage of the filling pump wheel, and the air release valve is communicated with the outer flow passage and the inner flow passage of the pump wheel.

2. The bearing of claim 1, wherein at least one outer casing flow passage is provided on or through the outer casing, the outer casing flow passage is provided with a flow inlet and a flow outlet, the flow inlet of the outer casing flow passage is communicated with a gap between the outer peripheral rotating surface of the pump impeller and the inner circumferential surface of the outer casing, the flow outlet of the outer casing flow passage is communicated with the suction flow passage through a gap between the inner end surface of the end cap and the cover plate, and the outer casing flow passage is filled with a lubricant.

3. A bearing according to claim 2 wherein a restrictor or throttle is provided in the outer sleeve flow path.

4. A bearing according to claim 1, 2 or 3, wherein the outer sleeve or cover plate is provided with an exciter body, the non N, S pole face of the exciter body is provided with a magnetism isolating body, the magnetism isolating body is an air gap or diamagnetic or paramagnetic material, the inner surface of the cylinder body is provided with an axial groove, the inner end face of the end cap is provided with a radial groove, the inner surface of the inner hole of the end cap with the through hole at the center or the outer surface of the corresponding hub is provided with a tooth groove or groove, the outer sleeve, cover plate and hub are made of magnetic conductive materials, and the lubricant is a magnetic fluid lubricant.

5. A bearing according to claim 1, 2 or 3, wherein at least one pipeline is connected between the discharge flow passage and the gap of the suction flow passage corresponding to the end cover through the outer sleeve, the inlet of the pipeline is communicated with the discharge flow passage, the outlet of the pipeline is communicated with the suction flow passage, and the pipeline is connected with a throttle valve, a radiator and a filter in series.

6. The bearing of claim 4, wherein at least one pipeline is connected between the discharge flow passage and the gap of the suction flow passage corresponding to the end cover through the outer sleeve, a flow inlet of the pipeline is communicated with the discharge flow passage, a flow outlet of the pipeline is communicated with the suction flow passage, and a throttle valve, a radiator and a filter are connected to the pipeline in series.

7. A bearing according to claim 1, 2 or 3, wherein at least one energy storage pipeline is connected to a gap between the outer edge rotating surface of the pump wheel and the inner circumferential surface of the cylinder body of the outer sleeve through the outer sleeve in the bearing area, 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 a one-way valve, a switch valve or a pressure flow control valve and an energy accumulator, the inflow port of the one-way valve is communicated with the other port of the energy storage pipeline, the outflow port of the one-way valve is communicated with the inflow port of the energy accumulator, and the switch valve or the pressure flow control valve is connected to the inflow port and the outflow port of the one-way valve in parallel.

8. A bearing according to claim 4, wherein at least one energy storage pipeline is connected to a gap between the outer edge rotating surface of the pump wheel and the inner circumferential surface of the cylinder body of the outer sleeve in the bearing area through the outer sleeve, 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 a one-way valve, a switch valve or a pressure flow control valve and an energy accumulator, the inlet of the one-way valve is communicated with the other port of the energy storage pipeline, the outlet of the one-way valve is communicated with the inlet of the energy accumulator, and the switch valve or the pressure flow control valve is connected to the inlet and the outlet of the one-way valve in parallel.

9. A bearing according to claim 1 or 2, wherein an annular rolling groove is formed on the inner circumferential surface of the cylinder of the outer sleeve and the outer circumferential surface of the cover plate of the pump impeller, or on the inner end surface of the end cover of the outer sleeve and the outer end surface of the cover plate of the pump impeller, a rolling body is arranged in the annular rolling groove, and a retainer is arranged on the rolling body.

10. A bearing according to claim 1, 2 or 3, wherein the cylindrical body has at least one axial groove formed in an inner circumferential surface thereof, and at least one radial groove formed in an inner end surface of the end cap.