CN113958608A - Magnetic fluid bearing - Google Patents

Magnetic fluid bearing Download PDF

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Publication number
CN113958608A
CN113958608A CN202111453492.6A CN202111453492A CN113958608A CN 113958608 A CN113958608 A CN 113958608A CN 202111453492 A CN202111453492 A CN 202111453492A CN 113958608 A CN113958608 A CN 113958608A
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China
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magnetic
magnetic fluid
yoke
magnetic yoke
pole
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CN202111453492.6A
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Chinese (zh)
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王政玉
王超颖
岑陈
张玉芹
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Individual
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Priority to CN202111453492.6A priority Critical patent/CN113958608A/en
Publication of CN113958608A publication Critical patent/CN113958608A/en
Priority to CN202210586980.2A priority patent/CN114934953A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
    • F16C32/0633—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being retained in a gap
    • F16C32/0637—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being retained in a gap by a magnetic field, e.g. ferrofluid bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0662—Details of hydrostatic bearings independent of fluid supply or direction of load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0662—Details of hydrostatic bearings independent of fluid supply or direction of load
    • F16C32/067—Details of hydrostatic bearings independent of fluid supply or direction of load of bearings adjustable for aligning, positioning, wear or play
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
    • F16C32/0696—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for both radial and axial load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C37/00—Cooling of bearings
    • F16C37/002—Cooling of bearings of fluid bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/002—Conductive elements, e.g. to prevent static electricity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/40—Sealings between relatively-moving surfaces by means of fluid
    • F16J15/43—Sealings between relatively-moving surfaces by means of fluid kept in sealing position by magnetic force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2210/00—Fluids
    • F16C2210/02—Fluids defined by their properties
    • F16C2210/06—Fluids defined by their properties magnetic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/20—Application independent of particular apparatuses related to type of movement
    • F16C2300/22—High-speed rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2380/00—Electrical apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2380/00—Electrical apparatus
    • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators

Abstract

The invention relates to a magnetic fluid bearing, which comprises an outer shell, a magnetic potential source, a left magnetic yoke, a right magnetic yoke, a rotating shaft, a pole tooth and magnetic fluid, wherein the pole tooth is positioned between the left magnetic yoke and the right magnetic yoke and fixed on the rotating shaft, a gap is reserved between the pole tooth and the magnetic yoke, an inner measuring flow channel and an outer measuring flow inlet channel are respectively arranged on the left magnetic yoke and the right magnetic yoke in a radiation manner, a radiator, a throttle valve, a filling valve and the like are connected between the two channels through pipelines, and the magnetic fluid is filled in the gap and the pipelines. When the magnetic fluid bearing is static, the magnetic fluid generates static sealing force by magnetic force and adhesion force; when the magnetic fluid bearing rotates, the surfaces of the pole teeth generate centrifugal force, pumping circulation and pressurization on the magnetic fluid, so that the heat dissipation, bearing and sealing capabilities are improved, and the magnetic fluid bearing is particularly suitable for running under high-speed and heavy-load working conditions. The magnetic fluid bearing can also be independently used as a rotary seal rotating or rotating electrode.

Description

Magnetic fluid bearing
Technical Field
The invention belongs to the field of supporting, sealing and high-speed collecting rings of rotating machinery, and particularly relates to a bearing and a bearing structure integrating bearing, lubricating, sealing and cooling under the conditions of heavy load bearing, high speed and large pressure difference.
Background
Under the working conditions of heavy load and high speed, the conventional mechanical rotary supporting system generally adopts a static pressure sliding bearing or a static and dynamic pressure sliding bearing besides a magnetic suspension bearing, wherein firstly, the required lubricating medium is provided by an external high-pressure gas or high-pressure liquid subsystem, so that the volume and the complexity of the system are increased; secondly, the problems of back flow and leakage of the lubricating medium exist, so that the application place is limited; thirdly, in special application occasions, a separate sealing device and a cooling device are required to be additionally arranged, so that the volume of the whole rotating system is increased. 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 200km/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.
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 has bearing and self-sealing capacity and generally comprises 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 due to the action between the magnetic field of the excitation magnet and the magnetic fluid, does not leak, can keep certain sealing performance and oil film lubrication under a low-speed or static state because external pollutants cannot enter a gap inside the bearing, and does not need an external lubricating oil subsystem and other mechanical sealing subsystems, so the magnetic fluid bearing has the characteristics of good sealing performance, small volume, strong shockproof capability, high rotation precision, low noise and suitability for high-speed operation.
In recent years, the application of the magnetic fluid technology in the aspects of rotary support, sealing, lubrication and cooling is continuously developed, but 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 throw leakage, bearing capacity reduction, sealing capacity reduction, magnetic potential source demagnetization and the like. There are still a number of problems that need 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 in the 'magnetic fluid bearing' of reference 1 (CN 202010343564.0) has certain functions of improving the bearing capacity at high speed and preventing 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 adsorption effect of the magnetic field of the permanent magnet to the magnetic fluid and the improvement of the bearing capacity are greatly reduced. 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 magnetic field generated by the excitation coil mainly passes through the inner sleeve and the outer sleeve of the bearing, and the magnetic particles or magnetic domains of the magnetic fluid are parallel to the axial direction, the magnetic excitation effect on the magnetic fluid is very small, and the effect of the magnetic particles or magnetic domains perpendicular to the surface of the shaft is also very small, and the bearing capacity is very small. To improve the excitation effect on the magnetic fluid, i.e. to improve the carrying capacity, a very large excitation current must be used, which in turn causes an increase in energy consumption and an increase in bearing temperature.
(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 the conditions of heavy load, high speed and high temperature, the mechanical seal of the magnetic fluid can often fail in long-term operation, and the sealing capability of the magnetic fluid can be greatly weakened or damaged. 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 the sealing effect, but the heat dissipation problem is difficult to solve when operating at high speed.
(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 "magnetic fluid sliding bearing" of the above-mentioned reference 2 (patent No. CN 201711483127.3) and the "magnetic fluid sliding bearing" of the reference 5 (patent No. CN 201810312388.7) have no structure and measure for cooling and heat dissipation, and only rely on the natural convection heat dissipation of the housing, so 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.
It is an urgent task to address the load carrying capacity, sealing capacity, lubrication performance, and operational reliability of high speed bearings.
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 magnetic fluid and the cooling capacity.
(4) In the aspect of collector rings required by motors and electric appliances, under the conditions of high power and high speed, the collector rings bear large current and high linear speed, the allowable linear speed of the solid electric brush is adopted, the material 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 speed, leakage prevention and cooling of the liquid metal collector become critical problems, and the solution proposed in reference 7 (netpage thesis) research on the liquid metal collector of the unipolar motor has a very complicated structure and does not have bearing and self-circulation cooling capabilities. To solve the problems of lubrication, cooling, sealing and the like of the collector, a comprehensive solution must be adopted.
Disclosure of Invention
The invention aims to provide a novel magnetic fluid bearing, which can solve the problems of magnetic fluid throwing leakage, low bearing capacity, low sealing capacity and the like in high-speed operation, improve the operation reliability, reduce the overall size and reduce the operation cost. And simultaneously extends to the fields of rotating seal and high-speed collecting ring.
The technical scheme provided by the invention is as follows:
a magnetic fluid bearing comprises an outer shell sleeve, a magnetic potential source, a left magnetic yoke, a right magnetic yoke, a rotating shaft or a shaft sleeve, a pole tooth and magnetic fluid, wherein the magnetic potential source is positioned between the left magnetic yoke and the right magnetic yoke or between the left magnetic yoke, the right magnetic yoke and the outer shell sleeve;
the cross section of the pole tooth is in a shape of a left-right symmetrical triangle, rectangle, trapezoid, ladder, M-shaped, inverted W-shaped or the like, or a left-right asymmetrical triangle, rectangle, trapezoid, ladder, M-shaped, inverted W-shaped or the like, and a tooth socket or a groove is formed on the surface of the pole tooth corresponding to the inner surface of the magnetic yoke;
the pole teeth have at least one pole tooth, the outer contour surface of the pole tooth is concentric with the rotating shaft or the shaft sleeve, and the inner contour surface formed by the left magnetic yoke, the magnetic potential source and the right magnetic yoke can be concentric with the pole teeth or have a certain eccentric distance;
at least one outer inflow channel and at least one inner outflow channel which are radiated are arranged on the left magnetic yoke and the right magnetic yoke or on one of the magnetic yokes, the inner port of the outer inflow channel is communicated with the gap at the root part of the corresponding pole tooth, the inner port of the inner outflow channel is communicated with the gap at the excircle part of the corresponding pole tooth, and the root part of the pole tooth can be provided with an annular confluence groove;
the outer side inflow channels on the left magnetic yoke and the right magnetic yoke can be linear channels or curved channels, and the direction of the outflow port of the outer side inflow channel is preferably aligned with or basically aligned with the flowing direction of the magnetic fluid on the surface of the pole tooth so as to prevent the backflow magnetic fluid from flowing to the gap between the magnetic yoke and the rotating shaft or the shaft sleeve when the centrifugal pressure is high;
a flow inlet and a flow outlet which are respectively communicated with the outer side flow inlet channel and the inner side flow outlet channel are arranged on the shell sleeve or the left magnetic yoke or the right magnetic yoke or the left and right magnetic yokes;
the flow inlet and the flow outlet on the shell sleeve or each magnetic yoke can be a pair or a plurality of pairs;
a magnetic fluid filling valve is connected between the inflow port and the outflow port on the outer shell or on the left magnetic yoke or on the right magnetic yoke or on the left magnetic yoke and the right magnetic yoke through a pipeline, and a radiator or a heat exchanger is connected in series or in parallel, namely the radiator or the heat exchanger can be connected in series independently between the inflow port and the outflow port on the corresponding outer shell of each magnetic yoke or on the left magnetic yoke or on the right magnetic yoke or on the left magnetic yoke and the right magnetic yoke, or the radiator or the heat exchanger can be connected in series after the inflow ports are connected, and the outflow ports are connected and then connected into one radiator or heat exchanger;
the magnetic potential source can be a permanent magnetic potential source, an electromagnetic magnetic potential source or a mixed magnetic potential source formed by combining permanent magnets and electromagnetic magnetic potential sources; the magnetic potential source can be positioned between the left magnetic yoke and the right magnetic yoke, between the left magnetic yoke and the right magnetic yoke and the outer casing, or between one magnetic yoke and the outer casing.
The magnetic fluid filling valve, the radiator or the heat exchanger are higher than the outer shell, namely for a transverse horizontally-mounted shaft or a longitudinal vertically-mounted shaft, the magnetic fluid filling valve, the radiator or the heat exchanger are arranged at the positions higher than the outer shell or an outer polar plate so as to ensure that the magnetic fluid is in good contact with the surfaces of polar teeth, a magnetic yoke and the like under the action of gravity during operation; the inside of the pipeline, the inside of the radiator or the heat exchanger and the like are filled with magnetic fluid, and the radiator or the heat exchanger is coupled with a cooling medium or a heating heat source. The radiator or the heat exchanger is coupled with a cooling medium or a heating heat source, and means that: when the magnetic fluid cooling device operates, the temperature of the magnetic fluid rises, and the magnetic fluid is coupled with an external low-temperature cooling medium through a radiator or a heat exchanger for cooling and radiating; when the external environment temperature is low, the magnetic fluid can be heated by an external heat source and coupled with heat through the heat exchanger to prevent the magnetic fluid from solidifying. The magnetic fluid comprises magnetic fluid with the particle size of magnetic solid particles being less than 10 nanometers or magnetic rheological fluid with the particle size of magnetic solid particles being nanometer or larger than nanometer. The carrier liquid of the magnetic fluid comprises: water-based or organic carrier liquid-based or liquid metal-based, etc., and preferably gallium-based alloy liquid metal is used as the magnetic fluid base liquid for the magnetic fluid bearing. The gap between the magnetic yoke and the pole teeth of the magnetic fluid bearing is 0.03mm-6 mm.
The size of the pole teeth in the technical scheme is obviously different from the size of the pole teeth expressed in the technical scheme of the existing magnetic fluid sealing device in that: the size of the pole teeth in the technical scheme is far larger than that of the pole teeth expressed in the technical scheme of the existing magnetic fluid sealing device, and the size range of tooth grooves or grooves formed in the surfaces of the pole teeth in the technical scheme is equivalent to that of the pole teeth in the technical scheme of the existing magnetic fluid sealing device, namely the tooth grooves or the grooves in the prior technical scheme are formed in the pole teeth in the technical scheme.
The excitation magnetic force line of the magnetic potential source in the technical scheme inevitably passes through the magnetic fluid between the pole teeth and the magnet yoke, so that the magnetic polarity particles or magnetic domains in the magnetic fluid turn to the direction of the magnetic force line, namely the direction of the magnetic polarity particles or magnetic domains is vertical to the surfaces of the magnet yoke and the pole teeth when the magnetic potential source is excited, thereby improving the bearing capacity and the sealing capacity and reducing the excitation magnetic potential.
In the application document of the invention, the left and right are habitual expressions of relative positions of elements corresponding to horizontal placement or installation of a shaft, and belong to the relation of up and down for vertical placement or installation; the terms "inner", "outer" or "inboard", "outboard" are used with respect to an element or a part.
The steps when assembling the magnetic fluid bearing are as follows:
(1) for a single-pole toothed magnetic fluid bearing: firstly, mounting and fixing a left magnetic yoke or a right magnetic yoke; secondly, installing an excitation magnetic potential source; thirdly, a rotating shaft with single-pole teeth or a shaft sleeve with single-pole teeth is installed; and fourthly, mounting and fixing the right magnetic yoke or the left magnetic yoke.
(2) For a bipolar toothed magnetic fluid bearing: firstly, mounting and fixing a left magnetic yoke or a right magnetic yoke; secondly, mounting a first pole tooth and a rotating shaft or a shaft sleeve; thirdly, an excitation magnetic potential source is installed; fourthly, mounting a second pole tooth; and fifthly, mounting and fixing the right magnetic yoke or the left magnetic yoke.
(3) The assembly of the multi-pole tooth magnetic fluid bearing is similar to the steps described above. When assembling, the outer surfaces of the magnetic yoke and the magnetic potential source can be coated with a layer of high-temperature resistant adhesive sealant or sealed by a sealing ring; the assembly between the pole teeth and the rotating shaft or the shaft sleeve can adopt a cold and hot assembly process.
When the pole teeth and the rotating shaft or the shaft sleeve rotate together, the magnetic fluid and the surfaces of the pole teeth are adhered, centrifugal force is generated under the centrifugal action of the grooves on the magnetic fluid, the centrifugal force borne by the magnetic fluid at the root parts of the pole teeth is extremely small or a negative pressure area is generated, the centrifugal force at the outer edges of the pole teeth is larger, the difference value of the centrifugal force at the two parts depends on the rotating speed, the shape and the size of the pole teeth and the like, and the magnetic fluid circulates in an outflow channel, a pipeline, a radiator or a heat exchanger, an inflow channel and a gap between a magnetic yoke and the pole teeth under the pumping action generated by the difference value of the centrifugal force, so that the cooling and heat dissipation capacity is improved. The circulating power of the magnetic fluid is the pumping action generated from the rotation of the pole teeth from the inside of the magnetic fluid bearing, and is different from the pumping effect of a circulating pump arranged from the outside, and the difference is that: the magnetic fluid leakage can occur in the gap between the two end faces of the magnetic fluid bearing when the circulating pump is installed outside, and the magnetic fluid bearing of the invention has the advantages that because the pole teeth are surrounded in the magnetic yoke, when the pole teeth rotate together with the rotating shaft or the shaft sleeve, the pumping force is generated in the magnetic fluid bearing, and because of the action of centrifugal force, the magnetic fluid in the gap flows along the surfaces of the pole teeth, and cannot flow to the two sides along the axial direction to be thrown to the outside. The higher the rotation speed, the stronger the pressurizing capacity, and the greater the bearing and sealing capacity.
When the magnetic fluid bearing is static, static sealing force is generated by the magnetic potential source through the magnetizing and adsorbing action of the magnetic yoke and the pole teeth on the magnetic fluid. When the magnetic fluid is in operation, the magnetic fluid generates a lubricating effect, and meanwhile, the axial separation of the pumping force generated by the surface on one side of the pole tooth and the groove thereof also plays a role in pressure balance and sealing for a high-pressure medium in a sealed space, and the axial thrust capability is improved. The radial force component generated by the pumping process can improve the radial bearing capacity.
The magnetic fluid bearing has the corrosion resistance after the outer surfaces of all parts are subjected to corrosion prevention treatment.
The above magnetic fluid bearing can be selected as follows: the pipeline is connected with a throttle valve, a safety valve, a filtering device and a release valve in series, the pipeline between a flow inlet and a flow outlet on the outer shell sleeve or on the left magnetic yoke or the right magnetic yoke or on the left and right magnetic yokes is connected with a one-way valve, a bypass switch valve and an energy storage device through a tee joint, the flow inlet of the one-way valve is communicated with the flow outlet of the tee joint on the pipeline, the flow outlet of the one-way valve is communicated with an oil inlet of the energy storage device, the bypass switch valve is connected in parallel to the flow inlet and the flow outlet of the one-way valve, and the magnetic potential source is a permanent magnet.
When the magnetic potential source is located on the axially magnetized permanent magnet between the left magnetic yoke and the right magnetic yoke, the outer shell is made of a non-magnetic conductive material. When the magnetic potential source is located between the magnetic yokes and the outer casing, the outer casing is made of magnetic conductive material. The throttle valve is used for adjusting the pressure and the flow of the magnetic fluid loop to achieve the purpose of adjusting the bearing capacity, the sealing capacity and the cooling capacity of the magnetic fluid bearing. The filter device is used for filtering scrap iron and large-particle impurities in the magnetic fluid loop and preventing the surfaces of the pole teeth and the magnetic yoke from being damaged. The air release valve is used for discharging gas in the magnetic fluid loop to prevent cavitation and air resistance. The energy accumulator and the matched one-way valve and bypass switch valve have the effects that when the energy accumulator runs at a high speed, high-pressure magnetic fluid can be injected into the energy accumulator through the one-way valve to store energy, and when the energy accumulator stops running or runs at a low speed, the one-way valve can be automatically closed; when the magnetic bearing is restarted or at a low speed, the bypass switch valve is opened, and the stored high-pressure magnetic fluid flows back to the bearing gap to prevent hard collision or friction between the pole teeth and the magnetic yoke. The accumulator also has the functions of storing magnetic fluid and pressurizing magnetic fluid and ensuring that the gap is always filled with the magnetic fluid. The throttle valve, the air release valve, the one-way valve and the bypass switch valve can be manual or automatic control electromagnetic valves or pneumatic and hydraulic valves.
The above magnetic fluid bearing can be selected as follows: a throttle valve, a safety valve, a filtering device and a release valve are connected in series on the pipeline, a one-way valve, a bypass switch valve and an energy storage device are connected on the pipeline between a flow inlet and a flow outlet on the outer shell sleeve or on the left magnetic yoke or the right magnetic yoke or on the left and right magnetic yokes through a tee joint, the flow inlet of the one-way valve is communicated with the flow outlet of the tee joint on the pipeline, the flow outlet of the one-way valve is communicated with an oil inlet of the energy storage device, and the bypass switch valve is connected in parallel on the flow inlet and the flow outlet of the one-way valve; the magnetic potential source is an electromagnet, and the outer casing is made of magnetic conductive material.
When the electromagnetic coil is used as a magnetic potential source, the electromagnetic coil can be positioned between the left magnetic yoke and the right magnetic yoke, or can be an axially excited electromagnetic coil wound on the left magnetic yoke provided with the coil slot frame or the right magnetic yoke provided with the coil slot frame or the left and right magnetic yokes provided with the coil slot frame; or the magnetic coils can be radially excited with the same polarity or different polarities on the outer circumferential surfaces of the left magnetic yoke and the right magnetic yoke or on the outer circumferential surface of one of the magnetic yokes; for a rotating shaft which is horizontally installed, the number of turns of the radial excitation coil distributed in the bearing area and the number of turns of the non-bearing area can be the same or different.
The above magnetic fluid bearing can be selected as follows: tooth sockets or grooves are formed in the inner surface of the magnetic yoke corresponding to the outer surfaces of the pole teeth, and the cross section outline shapes of the tooth sockets or the grooves are symmetrical triangles, rectangles or trapezoids or asymmetrical triangles, rectangles or trapezoids; the track trend shape of the tooth socket or the groove on the inner surface of the magnetic yoke can be circular, herringbone, oblique line or linear, the tooth socket or the groove on the inner surface of the magnetic yoke plays roles of oil wedge and magnetic gathering, and multiple tooth sockets or multiple grooves can more effectively improve the bearing capacity and improve the sealing capacity of the magnetic fluid. The shape of the tooth grooves or the grooves can be various structural shapes adopted by the existing sliding bearing, and the grooves of the tooth grooves can be filled with non-magnetic materials.
The above magnetic fluid bearing can be selected as follows: tooth sockets or grooves are formed in one side or two sides of the surface of the pole tooth corresponding to the magnet yoke or the whole surface of the pole tooth, and the cross section of each tooth socket or each groove is in a symmetrical triangular shape, a rectangular shape, a trapezoidal shape, a stepped shape or the like, or is in an asymmetrical triangular shape, a rectangular shape, a trapezoidal shape or the like; the track shape of the tooth socket or the groove on the surface of the pole tooth can be circular ring, herringbone, oblique line or straight line or parabolic line, and the groove of the tooth socket can be filled with non-magnetic material. When a plurality of tooth grooves exist on the outer side surface of the pole tooth, the axial sealing capacity of the bearing in the static state can be improved, when the pole tooth rotates, the tooth grooves or the grooves can also generate a pumping effect which is stronger than that of a smooth surface and is similar to a blade, and the axial sealing capacity and the bearing capacity can be further improved while the magnetofluid is cooled in a circulating mode. The surface of the pole tooth is provided with a circular track tooth socket or groove, so that the axial sealing capability can be improved; the linear track tooth grooves or grooves can improve the bearing capacity and the pumping capacity of the magnetic fluid; the herringbone, the oblique line-shaped and the parabola-shaped track tooth grooves or grooves can improve the axial sealing capacity, the bearing capacity and the pumping capacity of magnetic fluid. The pole teeth and the corresponding yokes of the structural shape can simultaneously have the functions of radial support bearing and axial thrust.
The above magnetic fluid bearing can be selected as follows: and when the magnetic potential source is a permanent magnet, the lining is made of a non-magnetic material. When the source of magnetic potential is an electromagnet, the liner may be of a non-magnetic material or a magnetic material.
The magnetic fluid bearing preferably adopts the technical scheme that: the cross-sectional profile shape of the pole tooth is M-shaped or inverted W-shaped, tooth grooves or grooves distributed in a radiation mode are machined on one or two outer side faces of the M-shaped or inverted W-shaped pole tooth, and annular tooth grooves or grooves are machined on the inner side faces of the M-shaped or inverted W-shaped pole tooth. The groove of the annular tooth groove can be filled with non-magnetic materials. The radial radiating gullets or grooves on the outer side produce a blade-like pumping action that is stronger than the smooth side as the tooth rotates. The inner side surface of the M-shaped or inverted W-shaped pole tooth is provided with an annular tooth socket or groove to improve the axial sealing capability. The magnetic fluid bearing is simultaneously suitable for the forward and reverse rotation operation of the rotating shaft.
The above magnetic fluid bearing can be selected as follows: the pole teeth are formed by axially overlapping left pole teeth, axially magnetized pole teeth permanent magnets and right pole teeth, the installation direction of the magnetic poles of the pole teeth permanent magnets is opposite to the direction of the magnetic poles of a magnetic potential source between the left magnetic yoke and the right magnetic yoke, and the rotating shaft or the shaft sleeve is made of non-magnetic conductive materials. The permanent magnet of the pole teeth can enhance the excitation capability, thereby improving the sealing capability of the magnetic fluid.
The above magnetic fluid bearing can be selected as follows: rolling or sliding protective bearings made of non-magnetic materials are arranged between the excircle of the pole tooth and a magnetic potential source or between the outer side of the left magnetic yoke and the outer side of the right magnetic yoke and the rotating shaft or the shaft sleeve, and the protective bearings play roles in preventing impact and positioning.
The above magnetic fluid bearing can be selected as follows: and disc-shaped isolating bodies with the diameter smaller than the outer diameter of the magnetic yoke are respectively sleeved on the rotating shaft or the shaft sleeve corresponding to the outer side of the left magnetic yoke or the outer side of the right magnetic yoke or the outer side surfaces of the left and right magnetic yokes, and the disc-shaped isolating bodies are in sliding fit or clearance fit with the outer side end surfaces of the magnetic yoke. The disc-shaped isolating body can be a rigid or elastic isolating plate body or a cylinder combined by rigidity and an elastic body with unequal diameters, and the circular isolating body can prevent the magnetic fluid and the sealed medium from being mutually fused. The disc-shaped isolating body can also be fixed on the outer side surface of the outer shell or each magnetic yoke, and the disc-shaped isolating body is in sliding fit or clearance fit with the rotating shaft or the shaft sleeve.
The above magnetic fluid bearing can be selected as follows: the magnetic yoke is characterized in that the rotating shaft or the shaft sleeve corresponding to the outer side of the left magnetic yoke or the outer side of the right magnetic yoke or the outer side of the left and right magnetic yokes is respectively sleeved with an isolator with the diameter smaller than the outer diameter of the magnetic yoke, the isolator is formed by combining an elastomer sleeved on the rotating shaft or the shaft sleeve and a circular isolating plate or an isolating membrane, the outer side of the circular isolating plate or the isolating membrane is in sealing connection with one end of the elastomer, the other end of the elastomer is in fixed sealing connection with the shaft sleeve or the rotating shaft, the circular isolating plate or the isolating membrane is in clearance fit with the shaft sleeve or the rotating shaft, a sealing ring can be arranged on the inner side of the circular isolating plate, the circular isolating plate or the isolating membrane can stretch out and draw back along the axial direction under the action of the elastomer, and the elastomer can be a rubber-plastic elastomer or an elastomer formed by a spring coated by a rubber-plastic material, and the like. According to the scheme, when the rotary machine is static and needs to seal gas in the cavity of the rotary machine, the isolating body enables the inner side face of the isolating plate or the isolating film to be in contact with and seal the outer surface of the magnetic yoke under the action of the elastic body, so that the gas sealing capability in the cavity of the rotary machine can be improved; when the rotary machine rotates, the circular rotary isolating plate or isolating membrane is just separated from the end face of the magnetic yoke by the centrifugal pumping pressurization action on one side of the pole teeth and the output pressure of the throttle valve is adjusted, and the pressure in the cavity is balanced with the pressure of the pumped magnetic fluid, so that the friction resistance is reduced.
The above magnetic fluid bearing can be selected as follows: one side or two sides of the pole tooth are provided with a pole tooth round platform along the axial direction, the outer circular surface of the pole tooth round platform is processed with an annular tooth groove or a spiral tooth groove or a helical tooth groove, and equivalently, the rotating shaft or the shaft sleeve at two sides of the installed pole tooth can be processed with the annular tooth groove or the spiral tooth groove or the helical tooth groove, so as to further improve the axial sealing capability. A counter flow groove can be further formed in the circular truncated cone at the root of the pole tooth corresponding to each inner port of the outer side inflow channel, and the counter flow groove has the function of counter-flushing the magnetic fluid from the outer side inflow port into the gap between the pole tooth and the magnetic yoke.
The above magnetic fluid bearing can be selected as follows: the left magnetic yoke and the right magnetic yoke are respectively formed by axially and parallelly superposing an outer polar plate and an inner polar plate, at least one radial outer side inflow channel is respectively arranged on the outer side surfaces of the inner polar plate of the left magnetic yoke and the inner polar plate of the right magnetic yoke, at least one radial inner side outflow channel is respectively arranged on the inner side surfaces of the inner polar plate of the left magnetic yoke and the inner polar plate of the right magnetic yoke, the length of the outer side inflow channel is greater than that of the inner side outflow channel, and the length difference between the outer side inflow channel and the inner polar plate of the right magnetic yoke is equal to 0.8-2 times of the height of a pole tooth; the inner port of the outer inflow channel is communicated with the gap at the root part of the corresponding pole tooth, and the inner port of the inner outflow channel is communicated with the gap at the excircle part of the corresponding pole tooth; the equivalent inner outflow channel can be arranged on two side surfaces of the magnetic potential source, or the equivalent inner outflow channel is arranged in the middle of the magnetic potential source and is used as a shared outflow channel, or the magnetic potential source is formed by connecting two magnetic potential sources in series, a polar plate is arranged between the two magnetic potential sources, and the polar plate is provided with the shared outflow channel; the equivalent outer inflow channel can also be arranged on each outer polar plate, and at least one radiating inner outflow channel on the left magnetic yoke and the right magnetic yoke preferentially adopts a channel which radiates tangentially with the inner circular surface of the magnetic yoke and the sectional area of the channel is gradually enlarged outwards.
The above magnetic fluid bearing can be selected as follows: outer ports of the outer side inflow channel and the inner side outflow channel are respectively communicated with the outer side confluence groove and the inner side confluence groove, and the outer side confluence groove and the inner side confluence groove are sealed; the outer confluence groove and the inner confluence groove can be of an integral annular shape, and can also be of segmented circular arcs corresponding to the outer ports of the outer inflow channels and the inner outflow channels respectively; and a flow inlet and a flow outlet which are respectively communicated with the outer side confluence groove and the inner side confluence groove are arranged on the shell sleeve or the left magnetic yoke or the right magnetic yoke or the left magnetic yoke and the right magnetic yoke.
The above magnetic fluid bearing can be selected as follows: the heating heat retainer is arranged on the outer shell. The heating heat retainer can be electric heating or liquid heating, and is used for heating and preserving the magnetic fluid before starting in a low-temperature environment so as to prevent the magnetic fluid from condensing.
The above magnetic fluid bearing can be selected as follows: an end cover can be arranged on the outer shell sleeve on the outer side of the left magnetic yoke and the right magnetic yoke, and a sealing ring is arranged between the end cover and the rotating shaft or the shaft sleeve or between the end cover and the outer side of the root part of the pole tooth.
The above magnetic fluid bearing can be selected as follows: the magnetic fluid bearing can be used as a magnetic fluid bearing unit, a magnetic fluid bearing group can be formed by a plurality of magnetic fluid bearing units, and the magnetic potential source can be equivalently arranged between adjacent magnetic yokes of every two magnetic fluid bearings to be used as a common magnetic potential source; or the source of magnetic potential is equivalently placed between the yoke and the outer shell of one or both magnetic fluid bearings.
The above magnetic fluid bearing can be selected as follows: and adjusting polar plates are arranged on two side faces of the excitation magnetic potential source.
The above magnetic fluid bearing can be selected as follows: and grooves for mounting sealing rings are arranged on the outer circular surfaces of the left magnetic yoke and the right magnetic yoke.
The above magnetic fluid bearing can be selected as follows: a baffle ring groove is processed on the inner circular surface of the shell of the magnetic fluid bearing near the outer side of each magnetic yoke, and a positioning baffle ring can be arranged in the baffle ring groove; or a positioning baffle table is processed on the inner circle surface of the shell sleeve near the outer side of one magnetic yoke, and a positioning baffle ring groove is processed on the outer side of the other magnetic yoke.
The above magnetic fluid bearing can be selected as follows: the outer surface of the outer shell is cylindrical or arc-shaped.
The above magnetic fluid bearing can be selected as follows: the outer shell is an outer shell with a flange or a thin-wall flanging on one side or an outer shell with a mounting base.
The above magnetic fluid bearing can be selected as follows: the outer shell, the left magnetic yoke, the right magnetic yoke and the like of the magnetic fluid bearing are of split structures, and the two halves are fixedly connected through bolts and nuts so as to be convenient to assemble and replace.
The above magnetic fluid bearing can be selected as follows: the outer shell is provided with a bearing seat outside, and the bearing seat is an integral bearing seat or a split bearing seat or a joint-shaped bearing seat and the like.
The above magnetic fluid bearing can be selected as follows: the surfaces of the magnetic yokes corresponding to the pole teeth are provided with or one of the surfaces is provided with a layer of shaft sleeve made of bronze or brass or bearing alloy material, so that the wear resistance of the bearing is improved.
The above magnetic fluid bearing can be selected as follows: the magnetic fluid bearing can be used as a magnetic fluid bearing unit, a plurality of magnetic fluid bearing units are connected in parallel to form a magnetic fluid bearing group, and every two magnetic fluid bearing units can be mutually attached and superposed; or may be installed with a space therebetween. When two magnetic fluids are installed at a space, the outer casings of the two magnetic fluid bearings are in sealed connection, the space can be used for installing a protective bearing, or the outer casings are provided with pipelines and medium injection valves communicated with the space, and injected media can be inert gases, liquid metals and cooling liquids or pumped into vacuum and the like according to needs so as to play a role in isolation protection or increasing bearing capacity or sealing capacity. The outer casing can also be provided with a pipeline, a radiator and a circulating pump which are communicated with the space of the outer casing, and liquid metal or heat-conducting medium is injected into the outer casing to improve the heat-radiating capacity. Or two ends of a rotating shaft of a rotating rotor are respectively provided with a group of bearing groups with a space, the outer shell sleeves of the two groups of bearing groups are communicated with a radiator and a circulating pump through pipelines, and the pipelines are communicated with the spaces of the two groups of bearing groups; the rotor or the rotating shaft is provided with a cooling medium flow passage which is communicated with the two spaces, so that the rotor body can be cooled.
When the magnetic fluid bearing adopts magnetic fluid with better electrical conductivity, the polar teeth or the shaft sleeve and the pipeline are conductors, and the pipeline and the polar teeth or the shaft sleeve are respectively connected with electrodes, so that the magnetic fluid bearing can be independently used as a rotary electrode or an electrical appliance rotary joint or a motor collecting ring with the functions of bearing, sealing and cooling heat dissipation.
The magnetic fluid bearing can be independently used as a sealing device with bearing, sealing and cooling heat dissipation capabilities.
Has the advantages that: (1) the bearing cooling effect is good. Because the pole teeth rotate along with the rotating shaft or the shaft sleeve, the pole teeth and the grooves formed on the surfaces of the pole teeth have pumping action similar to impeller blades of a water pump, and the magnetic yoke surrounds the pole teeth and has volute action similar to the water pump, magnetic fluid between the magnetic yoke and the pole teeth and magnetic fluid in a radiator or a heat exchanger can be pumped and circulated and transmit heat, the cooling and heat dissipation functions are realized, the temperature of the magnetic fluid is reduced, and the sealing capacity, the bearing capacity and the high-speed lubricating performance are enhanced. (2) And no leakage exists. Because the pole tooth is encircleed in yoke inner space, during the rotation, because the effect of the centrifugal force that pole tooth and slot produced magnetic fluid makes magnetic fluid flow along the pole tooth surface, can not throw along axial both ends and get rid of the outside and produce the leakage. (3) The bearing capacity is high. The pressure of the magnetic fluid is improved due to the centrifugal force generated by the pole teeth and the grooves on the magnetic fluid, so that the bearing capacity of the bearing is further improved. (4) And the bearing device has axial and radial bearing capacity. Because the pole teeth are surrounded in the inner space of the magnet yoke, and the outer circle surface and two side surfaces of the pole teeth are both coated by the magnetic fluid, the magnetic fluid bearing has radial and axial bearing capacity. (5) The bearing capacity is adjustable and controllable. By adopting the pole teeth with different shapes, the tooth grooves or the grooves on the pole teeth with different shapes and tracks and adjusting the opening degree of the throttle valve, the axial and radial bearing capacities with different sizes and the axial sealing capacities with different directions and sizes can be realized so as to adapt to the requirements of different working conditions. (6) Has multiple functional purposes. The magnetic fluid bearing can be used as a sealing device alone. When the magnetic fluid with better electrical conductivity is adopted, such as liquid metal magnetofluid, and the polar teeth or the shaft sleeve and the pipeline are conductors, the pipeline and the polar teeth or the shaft sleeve are respectively connected with electrodes, and when the polar teeth and the shaft sleeve or the shaft sleeve and the rotating shaft are insulated, the magnetofluid bearing can be used as a rotating electrode or an electrical appliance rotating joint or a motor collecting ring 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 single-pole tooth magnetic fluid bearing according to the present invention.
Fig. 2 is a schematic diagram of a basic structure of a bipolar tooth magnetic fluid bearing according to the present invention.
Fig. 3 is a schematic view of a partial basic structure of several pole teeth and tooth spaces or grooves thereof and corresponding yokes and tooth spaces or grooves thereof of a magnetic fluid bearing according to the present invention.
The serial number designations and corresponding designations in the drawings are as follows:
in fig. 1: 10-housing cover, 20-magnetic potential source, 30-left magnetic yoke, 40-right magnetic yoke, 50 shaft sleeve, 51-rotating shaft, 60-pole tooth, 70-magnetic fluid, 80-gap, 33-left magnetic yoke outer side inflow channel, 34-left magnetic yoke inner side outflow channel, 43-right magnetic yoke outer side inflow channel, 44-right magnetic yoke inner side outflow channel, 11-outer side confluence groove corresponding to left magnetic yoke outer side inflow channel, 12-inner side confluence groove corresponding to left magnetic yoke inner side outflow channel, 13-outer side confluence groove corresponding to right magnetic yoke outer side inflow channel, 14-inner side confluence groove corresponding to right magnetic yoke inner side outflow channel, a 1-inlet corresponding to left magnetic yoke, b 1-outlet corresponding to left magnetic yoke, a 2-inlet corresponding to right magnetic yoke, b 2-an outlet corresponding to the right magnetic yoke, 81-a magnetic fluid filling valve corresponding to the left magnetic yoke, 82-a magnetic fluid filling valve corresponding to the right magnetic yoke, 83-a circulation pipeline corresponding to the left magnetic yoke, 84-a circulation pipeline corresponding to the right magnetic yoke, 85-a radiator or heat exchanger corresponding to the left magnetic yoke, 86-a radiator or heat exchanger corresponding to the right magnetic yoke, 68-a left groove of the pole teeth, and 69-a right groove of the pole teeth.
In fig. 2: 10-outer shell, 20-magnetic potential source, 30-left magnetic yoke, 40-right magnetic yoke, 50-shaft sleeve, 51-rotating shaft, 60-pole tooth, 61-left pole tooth, 62-right pole tooth, a 1-inlet corresponding to left magnetic yoke, b 1-outlet corresponding to left magnetic yoke, a 2-inlet corresponding to right magnetic yoke, b 2-outlet corresponding to right magnetic yoke, 68-left groove of left pole tooth, 69-right groove of right pole tooth, 108-right tooth groove of left pole tooth, 109-left tooth groove of right pole tooth, 92-throttle corresponding to left magnetic yoke, 93-throttle corresponding to right magnetic yoke, 87, 88, 89-pipeline, 91-shared radiator or heat exchanger, 90-magnetic fluid filling/deflation valve, 94-one-way valve, 95-bypass switch valve, 96-energy accumulator, 97. 98-protective bearing, 70-magnetic fluid, 80-gap.
In fig. 3: 20-a source of magnetic potential, 30-a left yoke, 40-a right yoke, 51 a shaft or sleeve, 60-a pole tooth, 31-a left yoke outer plate, 32-a left yoke inner plate, 41-a right yoke outer plate, 42-a right yoke inner plate, 39-a left yoke outer plate spline, 49-a right yoke outer plate spline, 61 a-a pole tooth left bevel spline, 62 a-a pole tooth right bevel spline, 64-a pole tooth left circular truncated cone, 65-a left circular truncated cone spline, 66-a pole tooth right circular truncated cone, 67-a right circular truncated cone spline, 63-a pole tooth left bevel spline, 101-a left yoke inner plate oil wedge, 102-a right yoke inner plate oil wedge, 103-an outer bushing, 104-an inner bushing, 105-a pole tooth outer circular spline, 68-a pole tooth left spline, 69-a pole tooth right spline, 21-magnetic potential source left pole plate, 22-magnetic potential source right pole plate, 108-left pole tooth inner inclined plane tooth socket, 109-right pole tooth inner inclined plane tooth socket, 106-magnetic potential source inner yoke, 107-pole tooth permanent magnet, 111-pole tooth left isolation plate, 112-pole tooth right isolation plate, 110-protective bearing, 113-elastic isolator and 115-elastic body.
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.
The basic structure of a single-pole tooth magnetic fluid bearing as shown in fig. 1 includes an outer casing 10, a magnetic potential source 20, a left magnetic yoke 30, a right magnetic yoke 40, a rotating shaft 51, a shaft sleeve 50, a pole tooth 60, a magnetic fluid 70, a gap 80, a left magnetic yoke 30, a magnetic potential source 20, and a right magnetic yoke 40 enclosed in the outer casing 10, the pole tooth 60 fixed on the shaft sleeve 50 and located between the left magnetic yoke 30 and the right magnetic yoke 40, a gap 80 remaining between the left magnetic yoke 30, the magnetic potential source 20, the right magnetic yoke 40, the pole tooth 60, and the shaft sleeve 50, 6 oblique radiation left grooves 68 and 6 oblique radiation right grooves 69 evenly distributed along the circumference on the outer surface of the pole tooth 60, the magnetic fluid 70 filled in the gap 80, the magnetic fluid 70 using gallium-indium-tin alloy as a base fluid; the left magnetic yoke 30, the right magnetic yoke 40 and the pole teeth 60 are made of magnetic conductive materials.
The outer sides of the left magnetic yoke 30 and the right magnetic yoke 40 are respectively provided with 6 radially radiating outer inflow channels 33 and 43, the inner sides of the left magnetic yoke 30 and the right magnetic yoke 40 are respectively and uniformly provided with 6 radially radiating inner outflow channels 34 and 44, the length of the outer inflow channels 33 and 43 is greater than that of the inner outflow channels 34 and 44, and the length difference between the two is equal to 1.1 times of the height of the gear pole 60; the inner ports of the outer inlet passages 33, 43 communicate with the gaps 80 at the root of the corresponding tooth 60, and the inner ports of the inner outlet passages 34, 44 communicate with the gaps 80 at the outer circumferential surface of the corresponding tooth 60.
Outer end openings of the outer inlet channels 33 and 43 and the inner outlet channels 34 and 44 of the magnetic yokes 30 and 40 are provided with outer confluence grooves 11 and 13 and inner confluence grooves 12 and 14, outer end openings of the outer inlet channels 33 and 43 and the inner outlet channels 34 and 44 are respectively communicated with the outer confluence grooves 11 and 13 and the inner confluence grooves 12 and 14, and the outer confluence grooves 11 and 13 are respectively sealed with the inner confluence grooves 12 and 14.
The outer wall surface of the jacket 10 is provided with inlets a1, a2 and outlets b1, b2 which communicate with the outer bus ducts 11, 13 and the inner bus ducts 12, 14, respectively. The inlet and outlet of each yoke may be a pair or multiple pairs, and only one pair is shown in fig. 1 for simplicity.
Magnetic fluid filling valves 81 and 82, and heat sinks 85 and 86 (only two circuits of pipes, filling valves and heat sinks are shown in fig. 1 for simplicity) are respectively connected in series between the inlets a1 and a2 and the outlets b1 and b2 on the housing sleeve 10 through pipes 83 and 84, and are connected in series or in parallel, the magnetic fluid filling valves 81 and 82 and the heat sinks 85 and 86 are located at positions higher than the housing sleeve 10, so as to ensure that the magnetic fluid 70 is in good contact with the pole teeth 60 and the inner surfaces of the yokes 30 and 40 by gravity during operation.
The magnetic fluid fills the conduits 83, 84, radiators or heat exchangers 85, 86. The teeth 60 are symmetrically triangular.
When the magnetic fluid bearing is at rest, the magnetic fluid 70 in the gap 80 is adsorbed among the left magnetic yoke 30, the right magnetic yoke 40 and the pole teeth 60 under the action of the magnetic field of the permanent magnet 20, and the magnetic fluid generates static sealing force by means of magnetic force and self adhesion. When the magnetic fluid bearing rotates, the centrifugal action of the grooves 68 and 69 on the two inclined surfaces of the pole teeth 60 on the magnetic fluid causes the magnetic fluid to pump and pressurize towards the symmetric center of the pole teeth 60, thereby improving the sealing capability and the radial and axial bearing capability of the bearing, and avoiding the problem of magnetic fluid leakage along the axial direction. The higher the rotating speed, the stronger the pressurizing capacity and the larger the bearing capacity. The centrifugal pumping action of the magnetic fluid by the grooves 68, 69 on the two sloped surfaces of the teeth 60 also causes the magnetic fluid to circulate and dissipate heat in the outflow channels 34, 44, the conduits 83, 84, the heat sinks 85, 86, and the inflow channels 33, 43.
As shown in fig. 2, a basic structure of a bipolar tooth magnetic fluid bearing, a shaft sleeve 50 is sleeved on a rotating shaft 51, a pole tooth 60 is composed of a left pole tooth 61 and a right pole tooth 62, the pole tooth 60 is sleeved on the shaft sleeve 50, a permanent magnetic potential source 20 is located between the left pole tooth 61 and the right pole tooth 62, a magnetic fluid filling valve/air release valve 90 is respectively connected between an inlet a1 and an outlet a2 and an outlet b1 and an outlet b2 on a housing sleeve 10 through pipelines 87, 88 and 89, a radiator 91 and throttle valves 92 and 93 are connected in series or in parallel; the pipeline 88 is connected with a one-way valve 94, a bypass switch valve 95 and an energy storage device 96 through a tee joint, a flow inlet of the one-way valve 94 is communicated with a flow outlet of the tee joint on the pipeline 88, a flow outlet of the one-way valve 94 is communicated with a flow inlet of the energy storage device 96, and the bypass switch valve 95 is connected in parallel with the flow inlet and the flow outlet of the one-way valve 94; a protection bearing 97 is attached to the outer side of the left yoke 30, and a protection bearing 98 is attached to the outer side of the right yoke 40. The magnetic fluid fill/vent valve 90 and the radiator 91 are located at a position higher than the position of the outer shell 10.
The left inclined plane of the left pole tooth 61 is evenly provided with 6 grooves 68 along the circumference, and the right inclined plane can be provided with 2 annular tooth grooves 108. 6 grooves 69 are uniformly distributed on the right inclined plane of the right pole tooth 62 along the circumference, and 2 annular tooth grooves 109 are formed on the right inclined plane. The teeth 61, 62 may be symmetrical or asymmetrical. The structure and function of the other parts are similar to those of fig. 1, and are not described in detail herein.
When the magnetic fluid bearing is at rest, the magnetic fluid 70 in the gap 80 is absorbed between the left and right magnetic yokes 30 and 40 and the left and right pole teeth 61 and 62 of the pole teeth 60 under the action of the magnetic field of the permanent magnetic potential source 20, and the magnetic absorption force and the magnetic fluid self-adhesion effect generate static sealing force. When the magnetic fluid bearing rotates, besides the existing static sealing function, the groove 68 on the left inclined plane of the left pole tooth 61 of the pole tooth 60 and the groove 69 on the right inclined plane of the right pole tooth 62 perform centrifugal action on the magnetic fluid, so that the magnetic fluid is pumped and pressurized to the symmetric centers of the left pole tooth 61 and the right pole tooth 62, and the higher the rotating speed is, the stronger the pressurizing capacity is, and the larger the bearing capacity is; the right bevel and the tooth groove 108 of the left pole tooth 61 and the left bevel and the tooth groove 109 of the right pole tooth 62 also generate centrifugal force for the magnetic fluid, but simultaneously, the trend of vacuum negative pressure generated on the interface between the left bevel and the tooth groove exists, and the centrifugal force and the negative pressure can reach balance, so the magnetic fluid between the left pole tooth 61 and the right pole tooth 62 can not be pumped out. Therefore, the sealing capacity is improved, the radial and axial bearing capacity of the bearing is improved, and the problem of magnetic fluid leakage along the axial direction is solved. The centrifugal pumping action of the magnetic fluid by the grooves 68 on the left inclined surface of tooth 61 and the grooves 69 on the right inclined surface of tooth 62 also circulates the magnetic fluid in the conduits 87, 88, 89, the heat sink 91, and the throttle valves 93, 93 to dissipate heat. The energy accumulator 96, the one-way valve 94 and the bypass switch valve 95 are matched with each other, so that when the engine runs at a high speed, high-pressure magnetic fluid is injected into the energy accumulator 96 through the one-way valve 94 to store energy, and when the engine stops or runs at a low speed, the one-way valve 94 is automatically closed; when the motor is restarted or at a low speed, the bypass switch valve 95 is opened, and the high-pressure magnetic fluid in the energy accumulator 96 flows back to the bearing gap, so that hard collision and direct friction between the pole teeth and the magnetic yoke are prevented during starting. The throttle valves 92 and 93 are used for regulating the flow and pressure of the magnetic fluid along each loop of the circumference, thereby regulating the sealing pressure difference and the bearing capacity of the magnetic fluid bearing. The opening degrees of the throttle valves 92 and 93 and the switch valve 95 can be automatically controlled through sensors and an intelligent control system according to the requirements of working conditions.
Fig. 3 shows a partial basic structure of several pole teeth and tooth spaces or grooves thereof and corresponding yokes and tooth spaces or grooves thereof of a magnetic fluid bearing according to the present invention.
Fig. 3 (a) shows a local structure of a magnetic fluid bearing with bilateral symmetry of the sections of the pole teeth and the magnetic yokes, the section of the pole teeth 60 is a triangle with bilateral symmetry, an annular tooth groove 39 is arranged on the inner circular surface of the outer pole plate 31 of the left magnetic yoke 30, an annular tooth groove 49 is arranged on the inner circular surface of the outer pole plate 41 of the right magnetic yoke 40, annular grooves 61a and 62a are respectively arranged on the left and right sides of the outer surface of the pole teeth 60, the magnetic potential source 20 is a permanent magnet, the pole teeth 60 is directly connected with a rotating shaft 51, or the pole teeth 60 is directly connected with a shaft sleeve, and the shaft sleeve is further connected with the rotating shaft 51. The teeth 60 may also be asymmetrically triangular.
When the magnetic fluid bearing is static, the magnetic fluid (not shown in the figure) in the gap plays a static sealing role by the left yoke tooth groove 39, the right yoke tooth groove 49 and the tooth grooves 61a and 62a of the pole teeth 60 under the action of a magnetic field; when the magnetic fluid bearing rotates, in addition to the static sealing function, the centrifugal effect of the two inclined surfaces of the pole teeth 60 on the magnetic fluid enables the magnetic fluid to be pumped and pressurized to the symmetrical center of the pole teeth 60, the radial and axial bearing capacity of the bearing is improved while the sealing capacity is improved, and the problem of leakage of the magnetic fluid along the axial direction is solved.
Fig. 3 (b) is a partial structure of a magnetic fluid bearing with bilateral symmetry of sections of a pole tooth and a magnetic yoke, the section of the pole tooth 60 is a trapezoid with bilateral symmetry, a groove 101 is arranged on the inner circular surface of an inner pole plate 32 of a left magnetic yoke 30, a groove 102 is arranged on the inner circular surface of an inner pole plate 42 of a right magnetic yoke 40, the grooves 101 and 102 play a role of an oil wedge, a left round platform 64 and a right round platform 66 are arranged on the pole tooth 60, a tooth socket 65 is arranged on the left round platform, a tooth socket 67 is arranged on the right round platform, a groove 63 is arranged on a left inclined surface of the pole tooth 60, a tooth socket 62 is arranged on a right inclined surface, 103 is an outer bushing, 104 is an inner bushing, a magnetic potential source 20 is an electrically excited magnetic potential source, and the pole tooth 60 is directly connected with a rotating shaft 51.
When the magnetic fluid bearing is static, under the action of a magnetic field, the magnetic fluid (not shown in the figure) in the gap plays a static sealing role by the tooth grooves 65 of the left circular truncated cone 64, the tooth grooves 67 of the right circular truncated cone 66 and the right inclined plane upper tooth grooves 62 of the pole teeth 60; when the magnetic fluid bearing rotates, in addition to the static sealing function, the centrifugal action of the groove 63 on the left inclined surface of the pole tooth 60 on the magnetic fluid causes the magnetic fluid to be pumped and pressurized to the right side along the gap, and when high-pressure medium is in the mechanical cavity on the right side of the right magnetic yoke 40, the opening degree of the throttle valve is adjusted to enable the pressure of the magnetic fluid and the pressure of the medium to be balanced or basically balanced, so that the dynamic sealing effect is achieved. The sealing capacity is improved, the radial and axial bearing capacity of the bearing is improved, and the problem of leakage of magnetic fluid along the axial direction is solved. This structure can be used for sealing and bearing of high differential pressure medium on one side.
Fig. 3 (c) shows a local structure of a magnetic fluid bearing with bilateral symmetry of the sections of the pole teeth and the magnetic yokes, wherein the sections of the pole teeth are bilaterally symmetric rectangles, an annular tooth groove 39 is arranged on the inner circular surface of the outer pole plate 31 of the left magnetic yoke 30, an annular tooth groove 49 is arranged on the inner circular surface of the outer pole plate 41 of the right magnetic yoke 40, radial grooves 68 and 69 are respectively arranged on the left and right side surfaces of the pole teeth 60, a tooth groove 105 is arranged on the outer circular surface of the pole teeth 60, the magnetic potential source 20 is a permanent magnet, and a non-magnetic lining 103 is arranged on the inner circular surface of the magnetic potential source. The teeth 60 are directly connected to the shaft 51, or the teeth 60 are directly connected to a sleeve, which is then connected to the shaft 51.
When the magnetic fluid bearing is at rest, the magnetic fluid (not shown in the figure) in the gap plays a static sealing role by the left yoke tooth groove 39, the right yoke tooth groove 49 and the tooth groove 105 on the outer circular surface under the action of the magnetic field. When the magnetic fluid bearing rotates, in addition to the existing static sealing function, the centrifugal action of the radial grooves 68 and 69 on the two side surfaces of the pole tooth 60 on the magnetic fluid enables the magnetic fluid to be pumped and pressurized along the radial direction of the pole tooth 60, the sealing capability is improved, the radial and axial bearing capability of the bearing is also improved, and the problem of magnetic fluid leakage along the axial direction cannot occur.
Fig. 3 (d) shows a local structure of a magnetic fluid bearing with bilateral symmetry of pole teeth and yoke sections, the pole teeth 60 have a bilateral symmetry M-shape in section, the left and right sides of the pole teeth 60 are respectively provided with a left truncated cone 64 and a right truncated cone 66, the left truncated cone 64 is provided with a tooth space 65, the right truncated cone 66 is provided with a tooth space 67, the left and right outer side surfaces of the pole teeth 60 are respectively provided with radial grooves 68 and 69, the inner circular surface of the magnetic potential source 20 is provided with an inner bushing 103, the magnetic potential source 20 is a permanent magnetic potential source, the two sides of the magnetic potential source 20 are respectively provided with a magnetic potential source plate 21 and a magnetic potential source plate 22, and the pole teeth 60 are directly connected with the rotating shaft 51.
When the magnetic fluid bearing is static, under the action of a magnetic field, the magnetic fluid (not shown in the figure) in the gap plays a static sealing role by the tooth socket 65 on the left circular truncated cone 64 and the tooth socket 67 on the right circular truncated cone 66 of the pole tooth 60; when the magnetic fluid bearing rotates, in addition to the existing static sealing function, the centrifugal action of the radial grooves 68 and 69 on the two outer side surfaces of the pole teeth 60 on the magnetic fluid enables the magnetic fluid to be pumped and pressurized along the radial direction of the pole teeth 60, the sealing capability is improved, the radial and axial bearing capability of the bearing is also improved, and the problem of leakage of the magnetic fluid along the axial direction cannot occur.
Fig. 3 (e) is a partial structure of a magnetic fluid bearing with bilateral symmetry of the sections of the pole teeth and the magnetic yokes, the section of the pole teeth 60 is a symmetrical inverted W-shaped bipolar tooth structure formed by splicing a left pole tooth 61 and a right pole tooth 62, a groove 101 is arranged on the inner circular surface of the inner pole plate 32 of the left magnetic yoke 30, a groove 102 is arranged on the inner circular surface of the inner pole plate 42 of the right magnetic yoke 40, the grooves 101 and 102 play a role of an oil wedge, a left circular truncated cone 64 is arranged on the left pole tooth 61, and a tooth socket 65 is arranged on the left circular truncated cone 64; the right pole tooth 62 is provided with a right circular truncated cone 66, the right circular truncated cone 66 is provided with a tooth groove 67, the left inclined plane of the left pole tooth 61 is provided with a groove 68, the right inclined plane of the left pole tooth 61 is provided with a tooth groove 108, the right inclined plane of the right pole tooth 62 is provided with a groove 69, the left inclined plane of the right pole tooth 62 is provided with a tooth groove 109, a pole tooth permanent magnetic potential source 107 is arranged between the left pole tooth 61 and the right pole tooth 62, 106 is an inner yoke of the magnetic potential source 20, the inner surface of the inner yoke is provided with an inner bushing 103, the magnetic potential source 20 is an electric excitation magnetic potential source, and the pole tooth 60 is directly connected with the rotating shaft 50.
When the magnetic fluid bearing is at rest, under the action of a magnetic field, the magnetic fluid (not shown in the figure) in the gap plays a static sealing role by the tooth socket 65 and the tooth socket 108 on the left pole tooth 61 and the tooth socket 67 and the tooth socket 109 on the right pole tooth 62; when the magnetic fluid bearing rotates, in addition to the existing static sealing function, the centrifugal effect of the grooves 68 and 69 on the outer surfaces of the two sides of the pole teeth 60 on the magnetic fluid enables the magnetic fluid to be pumped and pressurized to the symmetrical center of the pole teeth 60, the higher the rotating speed is, the stronger the pressurizing capacity is, the larger the bearing and sealing capacities are, so that the radial and axial bearing capacities of the bearing are improved while the sealing capacity is improved, and the problem of leakage of the magnetic fluid along the axial direction cannot occur.
FIG. 3 (f) is a partial structure of a left-right asymmetric magnetic fluid bearing with a pole tooth and a yoke section, the pole tooth 60 section is a left-right asymmetric trapezoid, the inner circular surface of the inner pole plate 32 of the left yoke 30 is provided with a groove 101, the right yoke is provided with only the inner pole plate 42, the inner side surface of the inner pole plate 42 is provided with a tooth socket 49, the pole tooth 60 is provided with a left round table 64, the left round table is provided with a tooth socket 65, the left inclined surface of the pole tooth 60 is provided with a groove 63, the right side surface is provided with a tooth socket 62, 110 is a protective bearing, 111 is a rotary isolation plate fixed on the rotating shaft 51, the inner side surface of the rotary isolation plate 111 is in clearance fit or sliding fit with the outer side surface of the left yoke 30, 113 is an elastic isolation body fixed on the right side of the rotating shaft 51, the elastic isolation body 113 is composed of a circular isolation plate 112 and an elastic body 115, the circular isolation plate 112 is in clearance fit or sliding fit with the outer side surface of the inner pole plate 42 of the right yoke, the round isolation plate 112 is in clearance fit or sliding fit with the rotating shaft 51, the elastic body 115 is sleeved on the rotating shaft 51, the outer end of the elastic body is hermetically fixed on the rotating shaft 51, the magnetic potential source 20 is a permanent magnetic excitation magnetic potential source, the pole teeth 60 are directly connected with the rotating shaft 51, or the pole teeth 60 are directly connected with a shaft sleeve, and the shaft sleeve is further connected with the rotating shaft 51.
When the magnetic fluid bearing is at rest, under the action of a magnetic field, the magnetic fluid (not shown in the figure) in the gap plays a static sealing role by the tooth socket 65 on the left truncated cone 64 of the pole tooth 60 and the tooth socket 62 on the right side of the pole tooth 60, and the tooth socket 49 on the left side of the right yoke inner pole plate 42; meanwhile, the separator 112 contacts the outer side of the inner pole plate 42 of the right magnetic yoke under the thrust action of the elastomer 115, and also plays a role in sealing. When the magnetic fluid bearing rotates, besides the static sealing function, the groove 63 on the left side inclined surface of the pole tooth 60 pumps magnetic fluid to the right side and pressurizes the magnetic fluid, the higher the rotating speed is, the stronger the pressurizing capacity is, and the higher the bearing and sealing capacity is, when the right medium of the inner pole plate 42 is a high-pressure medium, the opening degree of the throttle valve is adjusted, the pressure of the magnetic fluid can be balanced with the pressure of the medium, and meanwhile, the isolation plate 112 is separated from the outer end surface of the inner pole plate 42 of the right magnetic yoke under the pressure action of the magnetic fluid, so that the friction resistance in operation is reduced. Therefore, the sealing capacity is improved, the radial and axial bearing capacity of the bearing is improved, and the problem of leakage of the magnetic fluid along the axial direction is solved. The rotary isolation plates 111 and 112 rotate along with the rotating shaft, so that mutual dissolution and reaction between the medium and the magnetic fluid can be prevented.
The above embodiments may be used alone as the sealing means. When the magnetic fluid with better electrical conductivity is adopted, such as liquid metal magnetofluid, and the polar teeth or the shaft sleeve and the pipeline are conductors, the pipeline and the polar teeth or the shaft sleeve are respectively connected with electrodes, and when the polar teeth and the shaft sleeve or the shaft sleeve and the rotating shaft are insulated, the magnetofluid bearing can be used as a rotating electrode or an electrical appliance rotating joint or a motor collecting ring with bearing, lubricating and sealing capabilities.
While the device and its extended use have been described in connection with preferred embodiments, the invention is not limited to the specific constructions and combinations illustrated herein and in the drawings, but, on the contrary, it is intended to cover such equivalents and devices as may be derived from various alternatives, subcombinations, and equivalents of the various features which are included within the scope of the invention as defined by the claims.

Claims (10)

1. A magnetic fluid bearing comprises an outer shell, a magnetic potential source, a magnetic yoke, a rotating shaft or a shaft sleeve and magnetic fluid, and is characterized in that:
the magnetic yoke is divided into a left magnetic yoke and a right magnetic yoke, the magnetic potential source is positioned between the left magnetic yoke and the right magnetic yoke or between the left magnetic yoke, the right magnetic yoke and the outer shell sleeve, and the left magnetic yoke, the magnetic potential source and the right magnetic yoke are encapsulated in the outer shell sleeve;
the magnetic pole comprises a rotating shaft or a shaft sleeve, a left magnetic yoke and a right magnetic yoke, wherein the rotating shaft or the shaft sleeve is provided with a pole tooth, the pole tooth is fixed on the rotating shaft or the shaft sleeve and is positioned between the left magnetic yoke and the right magnetic yoke, the cross section of the pole tooth is in a shape of a triangle, a rectangle, a trapezoid, an M shape or an inverted W shape which are bilaterally symmetrical, or in a shape of a triangle, a rectangle, a trapezoid, a step, an M shape or an inverted W shape which are bilaterally asymmetrical, a groove or a tooth socket is formed in the surface of the pole tooth corresponding to the inner surface of the magnetic yoke, the pole tooth is provided with at least one pole tooth, and the left magnetic yoke, the right magnetic yoke and the pole tooth are made of magnetic conducting materials;
gaps are reserved among the left magnetic yoke, the magnetic potential source, the right magnetic yoke, the pole teeth and the rotating shaft or the shaft sleeve, and the magnetic fluid is injected into the gaps;
at least one outer side inflow channel and at least one inner side outflow channel which are radiated are arranged on the left magnetic yoke, the right magnetic yoke or one of the magnetic yokes, the inner port of the outer side inflow channel is communicated with the gap at the root part of the corresponding pole tooth, and the inner port of the inner side outflow channel is communicated with the gap at the outer circular surface of the corresponding pole tooth;
the shell is sleeved with a left magnetic yoke or a right magnetic yoke or a left magnetic yoke and a right magnetic yoke, wherein a flow inlet and a flow outlet which are respectively communicated with an outer side flow inlet channel and an inner side flow outlet channel are directly arranged on the left magnetic yoke or the right magnetic yoke or the left magnetic yoke or the right magnetic yoke through pipelines, a communicating pipeline is arranged between the flow inlet and the flow outlet, a magnetic fluid filling valve is connected to the communicating pipeline, the communicating pipeline is connected in series or in parallel with a radiator or a heat exchanger, and the communicating pipeline, the radiator or the heat exchanger are filled with magnetic fluid.
2. A magnetic fluid bearing according to claim 1, wherein a throttle valve, a safety valve, a filter and a release valve are connected in series to the connection pipe, a check valve, a bypass switch valve and an accumulator are connected to the connection pipe via a tee joint, an inlet of the check valve is connected to an outlet of the tee joint on the connection pipe, an outlet of the check valve is connected to an inlet of the accumulator, and the bypass switch valve is connected to the inlet and the outlet of the check valve in parallel.
3. A magnetic fluid bearing according to claim 1, wherein splines or grooves are formed on an inner surface of the yoke corresponding to an outer surface of the teeth.
4. A magnetic fluid bearing according to claim 1, wherein the cross-sectional profile of the teeth is M-shaped or inverted W-shaped, with splines or grooves on one or both outer flanks of the M-shaped or inverted W-shaped teeth and annular splines on the inner flanks of the M-shaped or inverted W-shaped teeth.
5. A magnetic fluid bearing according to claim 1, wherein the pole teeth are formed by axially stacking a left pole tooth, an axially magnetized pole tooth permanent magnet, and a right pole tooth, the pole polarity installation direction of the pole tooth permanent magnet is opposite to the pole polarity direction of the magnetic potential source between the left and right magnetic yokes, and the rotating shaft or the shaft sleeve is made of a non-magnetic conductive material.
6. A magnetic fluid bearing according to claim 1 or 2 or 3 or 4 or 5, wherein a protective bearing is provided between the outer circumference of the teeth and the source of magnetic potential.
7. A magnetic fluid bearing according to claim 1 or 2 or 3 or 4 or 5, wherein a circular spacer having a diameter smaller than the outer diameter of the yoke is fitted around the shaft or the sleeve corresponding to the outer side of the left or right yoke or the outer sides of the left and right yokes, respectively, and the spacer is in sliding fit or clearance fit with the outer end surface of the yoke.
8. A magnetic fluid bearing according to claim 1, 2, 3, 4 or 5, wherein one or both outer sides of the pole teeth are provided with a truncated cone of pole teeth in the axial direction, and the outer circumferential surface of the truncated cone of pole teeth is provided with an annular spline or a helical spline.
9. A magnetic fluid bearing according to claim 1, 2, 3, 4 or 5, wherein the outlet of the outer inlet passage is oriented in the direction of the magnetic fluid flow over the tooth surface.
10. A magnetic fluid bearing according to claim 1, 2, 3, 4 or 5, wherein a heating insulator is provided on the outer shell.
CN202111453492.6A 2021-12-01 2021-12-01 Magnetic fluid bearing Pending CN113958608A (en)

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CN202111453492.6A CN113958608A (en) 2021-12-01 2021-12-01 Magnetic fluid bearing
CN202210586980.2A CN114934953A (en) 2021-12-01 2022-05-27 Magnetic fluid bearing

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024003073A1 (en) * 2022-06-27 2024-01-04 Inventus Engineering Gmbh Apparatus having a magnetorheological braking device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024003073A1 (en) * 2022-06-27 2024-01-04 Inventus Engineering Gmbh Apparatus having a magnetorheological braking device

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Application publication date: 20220121