WO2023226401A1 - 磁悬浮轴承、压缩机 - Google Patents

磁悬浮轴承、压缩机 Download PDF

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Publication number
WO2023226401A1
WO2023226401A1 PCT/CN2022/140606 CN2022140606W WO2023226401A1 WO 2023226401 A1 WO2023226401 A1 WO 2023226401A1 CN 2022140606 W CN2022140606 W CN 2022140606W WO 2023226401 A1 WO2023226401 A1 WO 2023226401A1
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WO
WIPO (PCT)
Prior art keywords
axial
iron core
magnetic
core
radial
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2022/140606
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English (en)
French (fr)
Inventor
胡余生
郭伟林
龚高
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Priority to US18/841,521 priority Critical patent/US20250163962A1/en
Priority to EP22943588.8A priority patent/EP4467831A4/en
Publication of WO2023226401A1 publication Critical patent/WO2023226401A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • 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
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0459—Details of the magnetic circuit
    • F16C32/0468—Details of the magnetic circuit of moving parts of the magnetic circuit, e.g. of the rotor
    • 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
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic 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
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0442—Active magnetic bearings with devices affected by abnormal, undesired or non-standard conditions such as shock-load, power outage, start-up or touchdown
    • 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
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0444—Details of devices to control the actuation of the electromagnets
    • 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
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0459—Details of the magnetic circuit
    • F16C32/0461—Details of the magnetic circuit of stationary parts of the magnetic circuit
    • 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
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0474—Active magnetic bearings for rotary movement
    • 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
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0474—Active magnetic bearings for rotary movement
    • F16C32/0476—Active magnetic bearings for rotary movement with active support of one degree of freedom, e.g. axial magnetic 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
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0474—Active magnetic bearings for rotary movement
    • F16C32/048—Active magnetic bearings for rotary movement with active support of two degrees of freedom, e.g. radial magnetic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/058—Bearings magnetic; electromagnetic
    • 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
    • F16C2360/00—Engines or pumps

Definitions

  • the present disclosure belongs to the technical field of bearing manufacturing, and specifically relates to a magnetic suspension bearing and a compressor.
  • Magnetic bearings have a series of excellent qualities such as non-contact, no wear, high speed, high precision, and no need for lubrication and sealing. They are high-tech products integrating electromagnetics, electronic technology, control engineering, signal processing, and mechanics.
  • Magnetic bearings are divided into three types: active, passive, and hybrid.
  • Active magnetic bearings have high stiffness and can be precisely controlled, but require a large volume and power consumption to generate unit bearing capacity; passive magnetic bearings utilize the attraction between magnetic materials. Or repulsive force achieves the suspension of the rotor, with relatively low stiffness and damping; hybrid magnetic bearings use permanent magnets to provide a bias magnetic field to replace the static bias magnetic field generated by electromagnets in active magnetic suspension bearings, reducing the number of ampere turns of the control winding and shrinking the bearing Volume, improve bearing carrying capacity, etc.; hybrid magnetic bearings have irreplaceable advantages in areas with strict volume and power consumption requirements. Magnetic bearings are mainly used in high-speed and ultra-high-speed applications. Therefore, the integration and miniaturization of the magnetic levitation system and improving the stability and reliability of the control system will be key research directions.
  • FIG. 1 The structure of a magnetic levitation bearing in the related art (taking a three-degree-of-freedom magnetic levitation bearing as an example) is shown in Figure 1.
  • the permanent magnet 10 is directly sleeved on the outside of the radial stator core 5.
  • the radial stator core 5 The matching gap between the outer side and the permanent magnet 10 should be as small as possible.
  • the radial stator core 5 is formed by stacking laminations. It is difficult to ensure the matching gap between the permanent magnet 10 and the radial stator core 5 in actual part processing. The same is true for the radial stator.
  • the assembly composed of the iron core 5, the permanent magnet 10 and the magnetic conductive ring 9 is an integral part.
  • the permanent magnet 10 is located between the radial stator core 5 and the magnetic conductive ring 9.
  • the shaft end surface of the magnetic conductive ring 9 is also connected to The lower core (axial stator core 1), and the permanent magnet 10 cannot be machined, so it is difficult to ensure the precise positioning of the relevant components in the magnetic suspension bearing.
  • the present disclosure provides a magnetic levitation bearing and a compressor that can overcome the limitation of the positioning accuracy of the radial stator core in the magnetic levitation bearing in the related art, where the permanent magnet is clamped between the magnetic conductive ring and the radial stator core. Due to the accuracy of the permanent magnets, the permanent magnets cannot be machined, so the positioning accuracy of the radial stator core is not high.
  • a magnetic suspension bearing which includes a first axial iron core and a radial iron core.
  • the first axial iron core has a first accommodation space, and an annular positioning device is provided in the first accommodation space.
  • the annular positioning boss has an axial positioning surface and a radial positioning surface.
  • a magnetic permeable ring is provided in the first accommodation space.
  • the magnetic permeable ring can be connected to the axial positioning surface and the radial positioning surface at the same time.
  • the positioning surfaces are cooperatively connected to position the magnetically conductive ring in the axial and radial directions of the first axial iron core, and the magnetically conductive ring is sleeved on the outer circumferential wall of the radial iron core.
  • one end of the central through hole of the magnetic ring has a limiting ring platform extending radially inward, and the limiting ring platform can adjust the axial direction of the radial iron core. form a limit.
  • the magnetic suspension bearing further includes a plurality of magnetic steels.
  • An annular gap is formed between the outer circumferential wall of the magnetic conductive ring and the wall of the first accommodation space.
  • the plurality of magnetic steels are arranged along the The circumferential spacing of the annular gap is set within the annular gap, and there is a clearance fit between the magnet and the annular gap.
  • the magnetic suspension bearing further includes two axial winding assemblies, and the two axial winding assemblies are connected to the two axial end surfaces of the radial iron core in one-to-one correspondence.
  • the axial winding assembly includes a winding bobbin and an axial control winding.
  • the axial control winding is wound in an annular groove of the winding bobbin, and the winding bobbin faces the
  • a plug-in structure is provided on one side of the radial core, and the winding bobbins respectively connected on two axial end surfaces of the radial core are connected into one body through the plug-in structure.
  • the plug-in structure includes a male seat and a female seat, and the same winding frame has both the male seat and the female seat.
  • a radial control winding is wound around the radial iron core, a cable through hole is configured on the first axial iron core, two of the axial control windings and the radial iron core are provided with a cable through hole.
  • the lead wire of the control winding is led out from the first accommodation space to the outside of the first accommodation space through the cable through hole.
  • the magnetic suspension bearing further includes a second axial iron core, the second axial iron core is detachably connected to the first axial iron core to be able to close the first accommodation space; and /Or, the annular positioning boss is a non-magnetic positioning ring detachably connected to the first accommodation space.
  • the magnetic suspension bearing further includes a rotating shaft assembly, the rotating shaft assembly includes a thrust plate, and the first axial iron core and/or the second axial iron core have thrust plate through holes embedded therein.
  • a protective bearing is installed, and the protective bearing gap is sleeved on the outer circumferential side of the thrust plate.
  • an axial clearance adjustment collar is set on the outer circumferential side of the thrust plate, and the protective bearing clearance is set on the outer circumferential side of the axial clearance adjustment collar.
  • the outer circumference of the thrust plate is The side is also equipped with a rotor core assembly and a locking piece spaced therefrom. The axial gap adjustment collar is clamped by the locking piece and the rotor core assembly.
  • the outer periphery of the axial gap adjustment collar An axial limit clearance groove is formed on the wall, and the inner ring of the protective bearing is set in the axial limit gap groove.
  • the axial length of the protective bearing is smaller than the axial length of the axial limit gap groove. length to create an axial protective gap between the two.
  • the magnetic suspension bearing further includes a rotating shaft assembly.
  • the rotating shaft assembly includes a non-magnetic conductive collar and a rotor core set on its outer circumferential side. Iron cores are provided at both axial ends of the rotor core.
  • the core shaft end baffle is used to position the rotor core in the axial direction.
  • the core shaft end baffle is magnetically conductive, and the core shaft section baffle is in contact with the adjacent first axial core.
  • an axial adjustment gap is formed between the second axial iron cores; or the rotating shaft assembly includes a magnetically conductive collar and a rotor iron core set on its outer circumferential side, and the axial ends of the rotor iron core are provided with
  • the iron core shaft end baffle is used to position the rotor iron core in the axial direction.
  • the iron core shaft end baffle is magnetically conductive, and the iron core shaft end baffle is in contact with the adjacent first axial iron core.
  • An axial adjustment gap is formed between the core or the second axial iron core.
  • the rotating shaft assembly includes a magnetically permeable collar, and a magnetic isolation plate is provided between the core shaft end baffle and the corresponding end of the rotor core.
  • the magnetic suspension bearing further includes a rotating shaft assembly.
  • the rotating shaft assembly includes a rotor core.
  • the rotor core is sleeved on the outer circumferential side of the thrust plate. Both axial ends of the rotor core are disposed There is an iron core shaft end baffle to axially position the rotor core, and the iron core shaft end baffle is magnetically conductive.
  • At least one of the two core shaft end baffles has an extension collar extending along its axial direction toward one side of the rotor core, and the extension collar is sleeved on the rotor core. between the central through hole of the core and the outer circumferential wall of the thrust plate.
  • the rotating shaft assembly further includes a non-magnetic conductive collar or a magnetically conductive collar, and the rotor core and the non-magnetic conductive collar or magnetically conductive collar are connected to the thrust plate by Positioning screws achieve positioning.
  • the present disclosure also provides a compressor, including the above-mentioned magnetic suspension bearing.
  • the present disclosure provides a magnetic levitation bearing and compressor.
  • the installation reference of the radial iron core is composed of the first axial iron core located at the outermost side in the radial direction - the annular positioning ring platform - the magnetic conductive ring - the central through hole of the magnetic conductive ring. It was jointly decided by both sides that this positioning dimension chain does not involve magnets (such as permanent magnets) in related technologies.
  • the positioning mating surfaces of each component in this dimension chain can be machined to ensure their shape and position accuracy, thereby ensuring their shape and position accuracy.
  • the positioning of the radial iron core is made more accurate, thereby effectively avoiding the problem in related technologies that the positioning accuracy of the radial iron core is relatively large due to its association with magnetic steel.
  • Figure 1 is a schematic diagram (section view) of the internal structure of a three-degree-of-freedom magnetic bearing in the related art.
  • the arrow in the figure shows the axial control magnetic circuit
  • Figure 2 is a schematic diagram (partial cross-sectional view) of the internal structure of a magnetic suspension bearing according to an embodiment of the present disclosure.
  • the arrows in the figure show the axial control magnetic circuit;
  • Figure 3 is a partial enlarged view of position I in Figure 2;
  • Figure 4 is a schematic diagram of the magnetic suspension bearing in Figure 2 along its axial perspective (from the second axial iron core side to the first axial iron core side).
  • the arrow in the figure shows the radial control magnetic circuit
  • Figure 5 is an exploded schematic diagram of the structure of the magnetic suspension bearing in Figure 2;
  • Figure 6 is a partial cross-sectional view of the magnetic suspension bearing in Figure 5;
  • Figure 7 is a schematic diagram (partial cross-sectional view) of the internal structure of a magnetic suspension bearing according to another embodiment of the present disclosure.
  • the arrows in the figure show the axial control magnetic circuit.
  • FIGS. 8 to 14 are respectively schematic structural diagrams of the rotor assembly in the magnetic suspension bearing in different embodiments (including the axial core structure).
  • a magnetic suspension bearing including a first axial iron core 101 and a radial iron core 201 .
  • the first axial iron core 101 has a first Accommodating space
  • the first accommodating space is provided with an annular positioning boss 102
  • the annular positioning boss 102 has an axial positioning surface and a radial positioning surface
  • the first accommodating space is provided with a magnetic ring 103, so
  • the magnetic conductive ring 103 can be cooperatively connected with the axial positioning surface and the radial positioning surface at the same time to realize the axial and radial positioning of the magnetic conductive ring 103 in the first axial iron core 101, so
  • the magnetic conductive ring 103 is mounted on the outer circumferential wall of the radial iron core 201 .
  • the installation reference of the radial iron core 201 in this technical solution is composed of the first axial iron core 101 located at the outermost side in the radial direction - the annular positioning boss 102 - the magnetic conductive ring 103 - the central through hole wall of the magnetic conductive ring 103 It was decided that this positioning dimension chain does not involve magnets (such as permanent magnets) in related technologies.
  • the positioning mating surfaces of each component in this dimension chain can be machined to ensure their shape and position accuracy, thereby making the diameter
  • the positioning of the radial iron core 201 is more accurate, thereby effectively avoiding the problem in the related art that the positioning accuracy of the radial iron core 201 is related to the magnetic steel and the problem of large positioning accuracy errors of the radial iron core 201 occurs.
  • one end of the central through hole of the magnetic ring 103 has a limiting ring platform extending radially inward, and the limiting ring platform can limit the radial core 201 A limit is formed in the axial direction, so that the radial direction of the radial core 201 is positioned by the central through hole of the magnetic ring 103, and the axial direction of the radial core 201 is positioned by the central through hole of the magnetic ring 103, and It can be understood that the final locking of the relative positions of the magnetically permeable ring 103 and the radial iron core 201 can be achieved through interference fit, pasting, etc.
  • the magnetically permeable ring 103 and the axial positioning surface and the radial positioning surface of the annular positioning boss 102 can also be connected by interference fit or pasting to achieve reliable positioning connection.
  • the magnetic suspension bearing further includes a plurality of magnets 301 (specifically, permanent magnets), and an annular gap is formed between the outer circumferential wall of the magnetic ring 103 and the wall of the first accommodation space.
  • a plurality of the magnets 301 are arranged in the annular gap at circumferential intervals along the annular gap, and there is a clearance fit between the magnets 301 and the annular gap.
  • the magnets 301 are arranged in the annular gap. The structure of the magnetic levitation bearing is made more compact.
  • the clearance fit between the magnetic steel 301 and the annular gap facilitates the installation of the magnetic steel 301 and prevents the magnetic steel 301 from exerting force on the magnetic conductive ring 103 and thereby affecting the shape of the magnetic conductive ring 103.
  • the unfavorable position configuration further reduces the positional accuracy of the radial core 201.
  • the processing difficulty of the magnet 301 at this time will be reduced because there is no need to pay too much attention to its excessive dimensional accuracy.
  • the magnet 301 can be a square cylinder-shaped magnet.
  • the outer circumferential wall of the corresponding magnetic permeable ring 103 and the inner wall of the first accommodation space are corresponding polygons, so as to match the square cylinder shape.
  • the mating surfaces between the magnets form a flat surface, so that this polygonal structure can be used to achieve circumferential positioning of multiple magnets without the need to separately set up corresponding magnet fixing frames, further simplifying the structure of the magnetic levitation bearing.
  • the magnetic suspension bearing further includes two axial winding assemblies, and the two axial winding assemblies are connected to the two axial end surfaces of the radial iron core 201 in one-to-one correspondence, and Compared with the technical solution of connecting the axial winding assembly to the two axial end faces of the magnetic ring in the related art, in this disclosure, it is connected to the radial iron core 201 so that it is radially away from the radial iron core 201. The distance to the control winding 202 is closer, and the lead wires of the two windings can be gathered at one place and then led out to the outside of the magnetic suspension bearing.
  • a cable through hole 1011 is constructed on the first axial iron core 101 , and the lead wires of the two axial control windings 402 and the radial control winding 202 are connected through the cable through hole 1011 .
  • the first accommodating space is led out to the outside of the first accommodating space, so that the structure of the magnetic suspension bearing is further simplified.
  • the axial winding assembly includes a winding bobbin 401 and an axial control winding 402.
  • the axial control winding is wound in an annular groove of the winding bobbin 401.
  • the winding bobbin 401 401 is provided with a plug-in structure on the side facing the radial core 201.
  • the winding bobbins 401 respectively connected on the two axial end surfaces of the radial core 201 are connected into one body through the plug-in structure.
  • the plug-in structure includes a male seat 4011 and a female seat 4012.
  • the same winding frame 401 has both the male seat 4011 and the female seat 4012.
  • one of the two opposite axial winding assemblies can
  • the male seat 4011 provided therein is reliably connected to the female seat 4012 provided thereon (for example, the two can be fixedly connected through pasting, interference fit, etc.).
  • the radial core 201 is also configured with a through hole for the plug structure to pass through.
  • the magnetic suspension bearing also includes a second axial iron core 104.
  • the second axial iron core 104 is detachably connected to the first axial iron core 101 to be able to close the first accommodation space, that is, the first accommodation space is closed.
  • the first axial iron core 101 and the second axial iron core 104 objectively form the outer shell of the magnetic suspension bearing. It should be particularly emphasized that in this disclosure, the axial winding assembly, radial iron core 201, radial control winding 202, magnetic conductive ring 103, annular positioning boss 102 and first axial iron core 101 are assembled in the magnetic suspension bearing.
  • the first part of the magnetic suspension bearing is constituted as a whole, the second axial iron core 104 constitutes the second part of the magnetic suspension bearing, and the rotating shaft assembly serves as the third part.
  • the integration degree and structural compactness of the magnetic suspension bearing of the present disclosure are improved. It greatly facilitates the assembly and disassembly process of magnetic bearings.
  • the annular positioning boss 102 is a non-magnetic positioning ring detachably connected to the first accommodation space, and it can be understood that the material of the first axial iron core 101 is Magnetic conductive material, the annular positioning boss 102 can be connected to the first accommodation space in an interference fit manner, that is, an interference fit is used between the annular positioning boss 102 and the first axial iron core 101 .
  • the magnetic suspension bearing further includes a rotating shaft assembly, the rotating shaft assembly includes a thrust plate 600 , and the first axial iron core 101 and/or the second axial iron core 104 have thrust plates passing through.
  • a protective bearing 601 is embedded in the hole, and the protective bearing 601 is sleeved on the outer circumferential side of the thrust plate 600 with a clearance.
  • the air gap g2 there is an axial air gap g3 (not shown in the figure) between the first axial iron core 101 and the adjacent iron core shaft end baffle 503.
  • the protective bearing 601 on the left side of the rotating shaft and There is an axial air gap g4 between the left end of the thrust plate 600, and an axial air gap g5 (not shown in the figure) between the protective bearing 601 on the right side of the rotating shaft and the right end of the thrust plate. It should be ensured that g2>g4, g3 > g5 so that the protective bearing 601 has a protective effect.
  • the control logic of the magnetic bearing includes axial bearing control logic and radial control logic.
  • the two control logics are roughly the same.
  • the axial bearing control logic as an example: when the sensor detects the axial air gap g2>g3, the controller controls The direction of the current in the bearing causes the electromagnetic magnetic circuit in the second axial iron core 104 to overlap with the permanent magnet magnetic circuit, and the front bearing output Ff (front bearing output) > Fr (rear bearing output) (in the orientation shown in Figure 3 The left side is front and the right side is rear), and the rotating shaft assembly moves to the left.
  • the controller controls the direction of the current in the bearing to change, so that the rotating shaft assembly can move to the right.
  • an axial clearance adjustment collar 602 is mounted on the outer circumferential side of the thrust plate 600 , and the protection bearing 601 is clearance mounted on the axial clearance adjustment collar 602 .
  • the thrust plate 600 is also equipped with a rotor core assembly and a locking piece 603 spaced apart from it.
  • the axial gap adjustment collar 602 is a combination of the locking piece 603 and the rotor core. The assembly is clamped, and an axial limit gap groove is formed on the outer peripheral wall of the axial gap adjustment collar 602.
  • the inner ring of the protective bearing 601 is set in the axial limit gap groove.
  • the axial length of the bearing 601 is less than the axial length of the axial limit gap groove to form an axial protection gap between the two.
  • the grooved axial clearance adjustment collar 602 adjusts the axial protection clearance of the protective bearing.
  • the locking member 603 may be, for example, a locking nut and a gasket between the locking nut and the inner ring of the protection bearing 601 . It can be understood that the axial direction of the protective bearing 601 should also be limited. For example, when the protective bearing 601 is assembled on the first axial iron core 101, the first axial iron core 101 is also provided with a bearing gland. 604, which is detachably connected to the outside of the first axial iron core 101.
  • the magnetic suspension bearing also includes a rotating shaft assembly.
  • the rotating shaft assembly includes a non-magnetic conductive collar 501 and a rotor core 502 sleeved on its outer circumferential side. Both axial ends of the rotor core 502 are provided with The core shaft end baffle 503 is positioned in the axial direction of the rotor core 502.
  • the core shaft end baffle 503 is magnetically conductive, and the core shaft section baffle 503 is in contact with the adjacent third
  • An axial adjustment gap is formed between one axial iron core 101 or the second axial iron core 102; or, the rotating shaft assembly includes a magnetically permeable collar 505 and a rotor iron core 502 set on its outer circumferential side.
  • Core shaft end baffles 503 are provided at both axial ends of the core 502 to position the rotor core 502 in the axial direction.
  • the core shaft end baffles 503 are magnetically conductive, and the core shaft end baffles are An axial adjustment gap is formed between the plate 503 and the adjacent first axial iron core 101 or the second axial iron core 102. This arrangement has small magnetic resistance and higher magnetic flux utilization.
  • a magnetic isolation plate 504 is also provided between the core shaft end baffle 503 and the corresponding end of the rotor core 502 to ensure that the magnetic flux can be guided from Pass through the magnetic collar 505.
  • the rotating shaft assembly includes a rotor core 502, which is sleeved on the outer circumferential side of the thrust plate 600, and iron cores are provided at both axial ends of the rotor core 502.
  • the shaft end baffle 503 is positioned in the axial direction of the rotor core 502, and the core shaft end baffle 503 is magnetically conductive.
  • at least one of the two core shaft end baffles 503 has an extension collar extending along its axial direction toward one side of the rotor core 502, and the extension collar is sleeved on the rotor core 502. between the central through hole of the rotor core 502 and the outer circumferential wall of the thrust plate 600 .
  • the iron core shaft end baffle 503 is provided, without the need to provide the aforementioned non-magnetic conductive collar 501 or magnetic conductive collar 505, which simplifies the structure of the rotating shaft assembly.
  • the rotating shaft assembly further includes a non-magnetic permeable collar 501 or a magnetic permeable collar 505.
  • the rotor core 502 and the non-magnetic permeable collar 501 or the magnetic permeable collar 505 are in contact with the stopper.
  • the push plates 600 are positioned by positioning screws. In this way, there is no need to use an interference fit between the components of the set, which improves assembly efficiency and facilitates replacement.
  • Protective bearing model 601 is a deep groove ball bearing or an angular contact ball bearing (used in pairs), which has the functions of radial protection and axial protection.
  • Angular contact bearings are generally used in pairs, and generally use steel bearings or ceramic balls.
  • the bearings may also be hybrid ceramic ball bearings.
  • the outer ring of the protective bearing 601 is radially interference assembled with the first axial iron core 101 and the second axial iron core 104 to limit the movement of the outer ring of the protective bearing in the axial direction, or use other limiting methods, such as glue. Sticky, bearing clamp hoop.
  • a compressor including the above-mentioned magnetic suspension bearing.

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Abstract

一种磁悬浮轴承、压缩机，其中的磁悬浮轴承，包括第一轴向铁芯(101)、径向铁芯(201)，第一轴向铁芯(101)具有第一容纳空间，第一容纳空间内具有环形定位凸台(102)，环形定位凸台(102)具有轴向定位面以及径向定位面，第一容纳空间内设有导磁环(103)，导磁环(103)能够同时与轴向定位面及径向定位面配合连接以实现对导磁环(103)在第一轴向铁芯(101)的轴向及径向的定位，导磁环(103)套装于径向铁芯(201)的外圆周壁上。该磁悬浮轴承、压缩机的径向铁芯的定位更加准确，从而有效避免现有技术中的径向铁芯的定位由于与磁钢有关联，径向铁芯的定位精度误差较大的问题出现。

Description

磁悬浮轴承、压缩机
相关申请的交叉引用
本公开是以申请号为202210582085.3，申请日为2022年5月26日，发明名称为“磁悬浮轴承、压缩机”的中国专利申请为基础，并主张其优先权，该中国专利申请的公开内容在此作为整体引入本公开中。
技术领域
本公开属于轴承制造技术领域，具体涉及一种磁悬浮轴承、压缩机。
背景技术
磁悬浮轴承具有无接触、无磨损、高转速、高精度、不需要润滑和密封等一系列优良品质，是集电磁学、电子技术、控制工程、信号处理、机械学一体的高新技术产物。
磁力轴承分为主动式、被动式、混合式三种类型，主动式磁力轴承刚度大，可以精密控制，但产生单位承载力所需体积和功耗较大；被动式磁力轴承利用磁性材料之间的吸力或斥力实现转子的悬浮，刚度和阻尼都比较低；混合式磁力轴承运用永磁体提供偏置磁场取代主动式磁悬浮轴承中电磁铁产生的静态偏置磁场，减少控制绕组的安匝数，缩小轴承体积，提高轴承承载能力等；混合式磁力轴承对体积和功耗有严格要求的领域有着不可替代的优势，磁力轴承又主要应用于高速、超高速场合。因此，磁悬浮系统的集成化、微型化和提高控制系统的稳定性与可靠性将是重点研究方向。
相关技术中的磁悬浮轴承(以三自由度磁悬浮轴承为例)结构如图1所示，永磁体10直接套设在径向定子铁芯5外侧，为减小漏磁，径向定子铁芯5外侧与永磁体10配合间隙应尽可能小，径向定子铁芯5由叠片叠装形成，实际零件加工很难保证永磁体10与径向定子铁芯5之间配合间隙，同样径向定子铁芯5、永磁体10、导磁环9组成的组件为一个整体零件，其中永磁体10位于径向定子铁芯5和导磁环9之间，导磁环9的轴端面还连接上、下铁芯(轴向定子铁芯1)，而永磁体10无法机加工，故难以保证对磁悬浮轴承内各相关部件的精准定位。
发明内容
因此，本公开提供一种磁悬浮轴承、压缩机，能够克服相关技术中的磁悬浮轴承中永磁体被夹持于导磁环与径向定子铁芯之间，径向定子铁芯的定位精度受限于永磁体的精度，而永磁体无法机加工从而使径向定子铁芯的定位精度不高的不足。
为了解决上述问题，本公开提供一种磁悬浮轴承，包括第一轴向铁芯和径向铁芯，所述第一轴向铁芯具有第一容纳空间，所述第一容纳空间内具有环形定位凸台，所述环形定位凸台具有轴向定位面以及径向定位面，所述第一容纳空间内设有导磁环，所述导磁环能够同时与所述轴向定位面及径向定位面配合连接以实现对所述导磁环在所述第一轴向铁芯的轴向及径向的定位，所述导磁环套装于所述径向铁芯的外圆周壁上。
在一些实施方式中，所述导磁环的中心通孔的一端孔口具有沿其径向向内延伸的限位环台，所述限位环台能够对所述径向铁芯的轴向形成限位。
在一些实施方式中，所述磁悬浮轴承还包括多个磁钢，所述导磁环的外圆周壁与所述第一容纳空间的壁体之间形成环形间隙，多个所述磁钢沿所述环形间隙的周向间隔设置于所述环形间隙内，且所述磁钢与所述环形间隙之间为间隙配合。
在一些实施方式中，所述磁悬浮轴承还包括两个轴向绕组组件，两个所述轴向绕组组件分别一一对应地连接于所述径向铁芯的轴向两个端面上。
在一些实施方式中，所述轴向绕组组件包括绕线骨架及轴向控制绕组，所述轴向控制绕组绕设于所述绕线骨架具有的环槽内，所述绕线骨架朝向所述径向铁芯一侧设有插接结构，所述径向铁芯的轴向两个端面上分别连接的所述绕线骨架通过所述插接结构连接为一体。
在一些实施方式中，所述插接结构包括公座及母座，同一所述绕线骨架上同时具有所述公座及母座。
在一些实施方式中，所述径向铁芯上绕设有径向控制绕组，所述第一轴向铁芯上构造有线缆通孔，两个所述轴向控制绕组及所述径向控制绕组的引出线经由所述线缆通孔被从所述第一容纳空间引出至所述第一容纳空间的外侧。
在一些实施方式中，所述磁悬浮轴承还包括第二轴向铁芯，所述第二轴向铁芯与所述第一轴向铁芯可拆卸连接以能够封闭所述第一容纳空间；和/或，所述环形定位凸台为可拆卸连接于所述第一容纳空间内的不导磁定位环。
在一些实施方式中，所述磁悬浮轴承还包括转轴组件，所述转轴组件包括推力盘，所述第一轴向铁芯和/或所述第二轴向铁芯具有的推力盘穿行孔内嵌装有保护轴承，所 述保护轴承间隙套装于所述推力盘的外圆周侧。
在一些实施方式中，所述推力盘的外圆周侧套装有轴向间隙调整套环，所述保护轴承间隙套装于所述轴向间隙调整套环的外圆周侧，所述推力盘的外圆周侧还套装有转子铁芯组件以及与其间隔设置的锁定件，所述轴向间隙调整套环为所述锁定件与所述转子铁芯组件所夹持，所述轴向间隙调整套环的外周壁上形成有轴向限位间隙槽，所述保护轴承的内圈套装于所述轴向限位间隙槽内，所述保护轴承的轴向长度小于所述轴向限位间隙槽的轴向长度以在两者之间形成轴向保护间隙。
在一些实施方式中，所述磁悬浮轴承还包括转轴组件，所述转轴组件包括非导磁套环以及套装于其外圆周侧的转子铁芯，所述转子铁芯的轴向两端设置有铁芯轴端挡板以对所述转子铁芯的轴向定位，所述铁芯轴端挡板导磁，且所述铁芯轴段挡板与与之邻近的所述第一轴向铁芯或者第二轴向铁芯之间形成轴向调整间隙；或者，所述转轴组件包括导磁套环以及套装于其外圆周侧的转子铁芯，所述转子铁芯的轴向两端设置有铁芯轴端挡板以对所述转子铁芯的轴向定位，所述铁芯轴端挡板导磁，且所述铁芯轴端挡板与与之邻近的所述第一轴向铁芯或者第二轴向铁芯之间形成轴向调整间隙。
在一些实施方式中，所述转轴组件包括导磁套环，所述铁芯轴端挡板与所述转子铁芯的对应端部之间还设有隔磁板。
在一些实施方式中，所述磁悬浮轴承还包括转轴组件，所述转轴组件包括转子铁芯，所述转子铁芯套装于止推盘的外圆周侧，所述转子铁芯的轴向两端设置有铁芯轴端挡板以对所述转子铁芯的轴向定位，所述铁芯轴端挡板导磁。
在一些实施方式中，两个所述铁芯轴端挡板中的至少一个具有朝向所述转子铁芯一侧沿其轴向延伸的延伸套环，所述延伸套环套装于所述转子铁芯的中心通孔与所述止推盘的外圆周壁之间。
在一些实施方式中，所述转轴组件还包括非导磁套环或者导磁套环，所述转子铁芯以及所述非导磁套环或者导磁套环与所述止推盘之间通过定位螺钉实现定位。
本公开还提供一种压缩机，包括上述的磁悬浮轴承。
本公开提供的一种磁悬浮轴承、压缩机，径向铁芯的安装基准由处于径向最外侧的第一轴向铁芯-环形定位环台-导磁环-导磁环的中心通孔孔壁共同决定，这一定位尺寸链中不涉及相关技术中的磁钢(例如永磁体)，这一尺寸链中的各个部件的定位配合面皆可以采用机加工等方式保证其形位精度，从而使径向铁芯的定位更加准确，从 而有效避免相关技术中的径向铁芯的定位由于与磁钢有关联，径向铁芯的定位精度误差较大的问题出现。
附图说明
图1为相关技术中的三自由度磁悬浮轴承的内部结构示意图(剖面图)，图中箭头示出轴向控制磁路；
图2为本公开一种实施例的磁悬浮轴承的内部结构示意图(部分剖面图)，图中箭头示出轴向控制磁路；
图3为图2中的I处的局部放大图；
图4为图2中的磁悬浮轴承沿其轴向视角下的示意图(从第二轴向铁芯一侧朝向第一轴向铁芯一侧)，图中箭头示出径向控制磁路；
图5为图2中的磁悬浮轴承的结构分解示意图；
图6为图5中的磁悬浮轴承的局部剖视图；
图7为本公开另一实施例的磁悬浮轴承的内部结构示意图(部分剖面图)，图中箭头示出轴向控制磁路
图8至图14分别为不同实施例中的磁悬浮轴承中的转子组件的结构示意图(含轴向铁芯部分结构)。
附图标记表示为：
1、轴向铁芯；2、轴向绕组骨架；3、轴向绕组；4、径向绕组；5、径向铁芯；6、转子铁芯；7、转子套环；8、铁芯限位挡板；9、导磁环；10、永磁体；11、轴向控制磁路；12、永磁偏置磁路；101、第一轴向铁芯；1011、线缆通孔；102、环形定位凸台；103、导磁环；104、第二轴向铁芯；201、径向铁芯；202、径向控制绕组；301、磁钢；401、绕线骨架；4011、公座；4012、母座；402、轴向控制绕组；501、非导磁套环；502、转子铁芯；503、铁芯轴端挡板；504、隔磁板；505、导磁套环；600、推力盘；601、保护轴承；602、轴向间隙调整套环；603、锁定件；604、轴承压盖。
具体实施方式
结合参见图2至图14所示，根据本公开的实施例，提供一种磁悬浮轴承，包括第一轴向铁芯101、径向铁芯201，所述第一轴向铁芯101具有第一容纳空间，所述第一容纳空间内具有环形定位凸台102，所述环形定位凸台102具有轴向定位面以及 径向定位面，所述第一容纳空间内设有导磁环103，所述导磁环103能够同时与所述轴向定位面及径向定位面配合连接以实现对所述导磁环103在所述第一轴向铁芯101的轴向及径向的定位，所述导磁环103套装于所述径向铁芯201的外圆周壁上。该技术方案中的径向铁芯201的安装基准由处于径向最外侧的第一轴向铁芯101-环形定位凸台102-导磁环103-导磁环103的中心通孔孔壁共同决定，这一定位尺寸链中不涉及相关技术中的磁钢(例如永磁体)，这一尺寸链中的各个部件的定位配合面皆可以采用机加工等方式保证其形位精度，从而使径向铁芯201的定位更加准确，从而有效避免相关技术中的径向铁芯201的定位由于与磁钢有关联，径向铁芯201的定位精度误差较大的问题出现。
在一些实施方式中，所述导磁环103的中心通孔的一端孔口具有沿其径向向内延伸的限位环台，所述限位环台能够对所述径向铁芯201的轴向形成限位，如此，径向铁芯201的径向由导磁环103的中心通孔实现定位，径向铁芯201的轴向则由导磁环103的中心通孔实现定位，而可以理解的是，所述导磁环103与所述径向铁芯201之间可以通过过盈配合、粘贴等方式实现对两者相对位置的最终锁定。所述导磁环103与环形定位凸台102具有的轴向定位面以及径向定位面之间也可以采用过盈配合或者粘贴的方式实现可靠的定位连接。
在一些实施方式中，所述磁悬浮轴承还包括多个磁钢301(具体例如永磁体)，所述导磁环103的外圆周壁与所述第一容纳空间的壁体之间形成环形间隙，多个所述磁钢301沿所述环形间隙的周向间隔设置于所述环形间隙内，且所述磁钢301与所述环形间隙之间为间隙配合，将磁钢301设置于环形间隙内使磁悬浮轴承的结构更加紧凑，同时磁钢301与环形间隙之间间隙配合，方便磁钢301安装的同时，还能够防止磁钢301施力于导磁环103之上进而对导磁环103形位构成不利进而降低径向铁芯201的位置精度，而可以理解的是，此时的磁钢301由于无需过多考虑其过高的尺寸精度，加工难度将降低。在一些实施例中，磁钢301可以采用方柱体形状的磁钢，此时对应的导磁环103的外圆周壁、第一容纳空间的内壁为相应的多边形，以与方柱体形状的磁钢之间的配合面形成平面，如此能够利用这一多边形的结构实现对多个磁钢的周向定位，而可以无需单独设置相应的磁钢固定架，进一步简化磁悬浮轴承的结构。
在一些实施方式中，所述磁悬浮轴承还包括两个轴向绕组组件，两个所述轴向绕组组件分别一一对应地连接于所述径向铁芯201的轴向两个端面上，与相关技术中将轴向绕组组件与导磁环的两个轴向端面连接的技术方案相比较，本公开中将其连接到 了径向铁芯201之上，使其距离径向铁芯201的径向控制绕组202的距离更近，两者的绕组引出线可以被汇总于一处，进而引出到磁悬浮轴承的外侧。例如所述第一轴向铁芯101上构造有线缆通孔1011，两个所述轴向控制绕组402及所述径向控制绕组202的引出线经由所述线缆通孔1011被从所述第一容纳空间引出至所述第一容纳空间的外侧，从而磁悬浮轴承的结构进一步得到精简。
在一些实施方式中，所述轴向绕组组件包括绕线骨架401及轴向控制绕组402，所述轴向控制绕组绕设于所述绕线骨架401具有的环槽内，所述绕线骨架401朝向所述径向铁芯201一侧设有插接结构，所述径向铁芯201的轴向两个端面上分别连接的所述绕线骨架401通过所述插接结构连接为一体，所述插接结构包括公座4011及母座4012，同一所述绕线骨架401上同时具有所述公座4011及母座4012，此时相对的两个所述轴向绕组组件中的一个能够通过其具有的公座4011与另一个具有的母座4012形成可靠连接(例如两者之间可以通过粘贴、过盈配合等方式实现固定连接)。能够理解的是，径向铁芯201上还构造有供所述插接结构穿行的通孔。
所述磁悬浮轴承还包括第二轴向铁芯104，所述第二轴向铁芯104与所述第一轴向铁芯101可拆卸连接以能够封闭所述第一容纳空间，也即所述第一轴向铁芯101与第二轴向铁芯104两者客观上形成磁悬浮轴承的外壳。需要特别强调的是，本公开中，磁悬浮轴承内的轴向绕组组件、径向铁芯201、径向控制绕组202、导磁环103、环形定位凸台102以及第一轴向铁芯101组装为一个整体构成磁悬浮轴承的第一部分、第二轴向铁芯104构成磁悬浮轴承的第二部分，而转轴组件则作为第三部分，如此本公开的磁悬浮轴承的集成度、结构紧凑度得到提高，极大的便利了磁悬浮轴承的组装拆卸过程。
在一些实施例中的，所述环形定位凸台102为可拆卸连接于所述第一容纳空间内的不导磁定位环，而能够理解的是，第一轴向铁芯101的材料则是导磁材料，所述环形定位凸台102具体可以采用过盈配合的方式连接于第一容纳空间内，也即环形定位凸台102与第一轴向铁芯101之间采用过盈配合。
在一些实施方式中，所述磁悬浮轴承还包括转轴组件，所述转轴组件包括推力盘600，所述第一轴向铁芯101和/或所述第二轴向铁芯104具有的推力盘穿行孔内嵌装有保护轴承601，所述保护轴承601间隙套装于所述推力盘600的外圆周侧。具体参见图3所示，径向铁芯201与转子铁芯502之间有径向气隙g1，第二轴向铁芯104与与之相邻的铁芯轴端挡板503之间有轴向气隙g2，第一轴向铁芯101与与之相邻的铁 芯轴端挡板503之间有轴向气隙g3(图中未示出)，处于转轴左侧的保护轴承601与推力盘600的左端之间有轴向气隙g4，处于转轴右侧的保护轴承601与推力盘的右端之间有轴向气隙g5(图中未示出)，应保证g2＞g4，g3＞g5以使保护轴承601具有保护作用，保护轴承601与推力盘600径向之间有气隙g6，g1＞g6。
该磁悬浮轴承的控制逻辑包括轴向轴承控制逻辑及径向控制逻辑，两个控制逻辑大致相同，以轴向轴承控制逻辑为例：当传感器检测到轴向气隙g2＞g3时，控制器控制轴承中电流方向，使第二轴向铁芯104中的电磁磁路与永磁磁路叠加，轴承前侧轴承出力Ff(前轴承出力)＞Fr(后轴承出力)(以图3所示方位左侧为前、右侧为后)，转轴组件向左移动，同理，当传感器检测到轴向气隙g2＜g3时，控制器控制轴承中电流方向改变，可以实现转轴组件向右移动。
在另一些实施方式中，如图7所示，所述推力盘600的外圆周侧套装有轴向间隙调整套环602，所述保护轴承601间隙套装于所述轴向间隙调整套环602的外圆周侧，所述推力盘600的外圆周侧还套装有转子铁芯组件以及与其间隔设置的锁定件603，所述轴向间隙调整套环602为所述锁定件603与所述转子铁芯组件所夹持，所述轴向间隙调整套环602的外周壁上形成有轴向限位间隙槽，所述保护轴承601的内圈套装于所述轴向限位间隙槽内，所述保护轴承601的轴向长度小于所述轴向限位间隙槽的轴向长度以在两者之间形成轴向保护间隙，通过更换具有不同槽宽(也即轴向长度)的轴向限位间隙槽的轴向间隙调整套环602对保护轴承的轴向保护间隙进行调整。所述锁定件603例如可以为锁定螺母以及处于锁定螺母与保护轴承601的内圈之间的垫片。能够理解的是，保护轴承601的轴向也应该被限位，例如当保护轴承601组装于第一轴向铁芯101上时，此时第一轴向铁芯101上还设有轴承压盖604，其可拆卸地连接于第一轴向铁芯101的外侧。
在一些实施方式中，磁悬浮轴承还包括转轴组件，所述转轴组件包括非导磁套环501以及套装于其外圆周侧的转子铁芯502，所述转子铁芯502的轴向两端设置有铁芯轴端挡板503以对所述转子铁芯502的轴向定位，所述铁芯轴端挡板503导磁，且所述铁芯轴段挡板503与与之邻近的所述第一轴向铁芯101或者第二轴向铁芯102之间形成轴向调整间隙；或者，所述转轴组件包括导磁套环505以及套装于其外圆周侧的转子铁芯502，所述转子铁芯502的轴向两端设置有铁芯轴端挡板503以对所述转子铁芯502的轴向定位，所述铁芯轴端挡板503导磁，且所述铁芯轴端挡板503与与之邻近的所述第一轴向铁芯101或者第二轴向铁芯102之间形成轴向调整间隙，该种 布置方式磁阻小，磁通利用率更高。当所述转轴组件包括导磁套环505时，所述铁芯轴端挡板503与所述转子铁芯502的对应端部之间还设有隔磁板504，以保证磁通能够从导磁套环505中经过。
在一个另外的实施例中，所述转轴组件包括转子铁芯502，所述转子铁芯502套装于止推盘600的外圆周侧，所述转子铁芯502的轴向两端设置有铁芯轴端挡板503以对所述转子铁芯502的轴向定位，所述铁芯轴端挡板503导磁。在一些实施方式中，两个所述铁芯轴端挡板503中的至少一个具有朝向所述转子铁芯502一侧沿其轴向延伸的延伸套环，所述延伸套环套装于所述转子铁芯502的中心通孔与所述止推盘600的外圆周壁之间。该技术方案中仅设置铁芯轴端挡板503，而无需设置前述的非导磁套环501或者导磁套环505，使转轴组件结构得到简化。
在一些实施方式中，所述转轴组件还包括非导磁套环501或者导磁套环505，所述转子铁芯502以及所述非导磁套环501或者导磁套环505与所述止推盘600之间通过定位螺钉实现定位，如此，套装的部件之间可以不必采用过盈配合的方式，提高装配效率，同时便于更换。
保护轴承601型号为深沟球轴承或是角接触球轴承(成对使用)，具有径向保护和轴向保护的作用，其中角接触轴承一般成对使用，一般采用钢制轴承或是陶瓷球轴承亦或是混合陶瓷球轴承。保护轴承601的外圈与第一轴向铁芯101、第二轴向铁芯104径向采用过盈装配，限制保护轴承外圈在轴向方向移动，或是采用其它限位方式，如胶粘、轴承卡箍箍住。
根据本公开的实施例，还提供一种压缩机，包括上述的磁悬浮轴承。
本领域的技术人员容易理解的是，在不冲突的前提下，上述各有利方式可以自由地组合、叠加。
以上仅为本公开的较佳实施例而已，并不用以限制本公开，凡在本公开的原则之内所作的任何修改、等同替换和改进等，均应包含在本公开的保护范围之内。以上仅是本公开的优选实施方式，应当指出，对于本技术领域的普通技术人员来说，在不脱离本公开技术原理的前提下，还可以做出若干改进和变型，这些改进和变型也应视为本公开的保护范围。

Claims (16)

  1. 一种磁悬浮轴承，包括第一轴向铁芯(101)和径向铁芯(201)，所述第一轴向铁芯(101)具有第一容纳空间，所述第一容纳空间内具有环形定位凸台(102)，所述环形定位凸台(102)具有轴向定位面以及径向定位面，所述第一容纳空间内设有导磁环(103)，所述导磁环(103)能够同时与所述轴向定位面及径向定位面配合连接以实现对所述导磁环(103)在所述第一轴向铁芯(101)的轴向及径向的定位，所述导磁环(103)套装于所述径向铁芯(201)的外圆周壁上。
  2. 根据权利要求1所述的磁悬浮轴承，其中，所述导磁环(103)的中心通孔的一端孔口具有沿其径向向内延伸的限位环台，所述限位环台能够对所述径向铁芯(201)的轴向形成限位。
  3. 根据权利要求1或2所述的磁悬浮轴承，还包括多个磁钢(301)，所述导磁环(103)的外圆周壁与所述第一容纳空间的壁体之间形成环形间隙，多个所述磁钢(301)沿所述环形间隙的周向间隔设置于所述环形间隙内，且所述磁钢(301)与所述环形间隙之间为间隙配合。
  4. 根据权利要求1至3中任一项所述的磁悬浮轴承，还包括两个轴向绕组组件，两个所述轴向绕组组件分别一一对应地连接于所述径向铁芯(201)的轴向两个端面上。
  5. 根据权利要求4所述的磁悬浮轴承，其中，所述轴向绕组组件包括绕线骨架(401)及轴向控制绕组(402)，所述轴向控制绕组绕设于所述绕线骨架(401)具有的环槽内，所述绕线骨架(401)朝向所述径向铁芯(201)一侧设有插接结构，所述径向铁芯(201)的轴向两个端面上分别连接的所述绕线骨架(401)通过所述插接结构连接为一体。
  6. 根据权利要求5所述的磁悬浮轴承，其中，所述插接结构包括公座(4011)及母座(4012)，同一所述绕线骨架(401)上同时具有所述公座(4011)及母座(4012)。
  7. 根据权利要求5或6所述的磁悬浮轴承，其中，所述径向铁芯(201)上绕设有径向控制绕组(202)，所述第一轴向铁芯(101)上构造有线缆通孔(1011)，两个所述轴向控制绕组(402)及所述径向控制绕组(202)的引出线经由所述线缆通孔(1011)被从所述第一容纳空间引出至所述第一容纳空间的外侧。
  8. 根据权利要求1至7中任一项所述的磁悬浮轴承，其中，还包括第二轴向铁芯(104)，所述第二轴向铁芯(104)与所述第一轴向铁芯(101)可拆卸连接以能够封闭所述第一容纳空间；和/或，所述环形定位凸台(102)为可拆卸连接于所述第一容纳空间内的不导磁定位环。
  9. 根据权利要求8所述的磁悬浮轴承，还包括转轴组件，所述转轴组件包括推力盘(600)，所述第一轴向铁芯(101)和/或所述第二轴向铁芯(104)具有的推力盘穿行孔内嵌装有保护轴承(601)，所述保护轴承(601)间隙套装于所述推力盘(600)的外圆周侧。
  10. 根据权利要求9所述的磁悬浮轴承，其中，所述推力盘(600)的外圆周侧套装有轴向间隙调整套环(602)，所述保护轴承(601)间隙套装于所述轴向间隙调整套环(602)的外圆周侧，所述推力盘(600)的外圆周侧还套装有转子铁芯组件以及与其间隔设置的锁定件(603)，所述轴向间隙调整套环(602)为所述锁定件(603)与所述转子铁芯组件所夹持，所述轴向间隙调整套环(602)的外周壁上形成有轴向限位间隙槽，所述保护轴承(601)的内圈套装于所述轴向限位间隙槽内，所述保护轴承(601)的轴向长度小于所述轴向限位间隙槽的轴向长度以在两者之间形成轴向保护间隙。
  11. 根据权利要求1至10中任一项所述的磁悬浮轴承，还包括转轴组件，所述转轴组件包括非导磁套环(501)以及套装于其外圆周侧的转子铁芯(502)，所述转子铁芯(502)的轴向两端设置有铁芯轴端挡板(503)以对所述转子铁芯(502)的轴向定位，所述铁芯轴端挡板(503)导磁，且所述铁芯轴段挡板(503)与与之邻近的所述第一轴向铁芯(101)或者第二轴向铁芯(102)之间形成轴向调整间隙；或者， 所述转轴组件包括导磁套环(505)以及套装于其外圆周侧的转子铁芯(502)，所述转子铁芯(502)的轴向两端设置有铁芯轴端挡板(503)以对所述转子铁芯(502)的轴向定位，所述铁芯轴端挡板(503)导磁，且所述铁芯轴端挡板(503)与与之邻近的所述第一轴向铁芯(101)或者第二轴向铁芯(102)之间形成轴向调整间隙。
  12. 根据权利要求11所述的磁悬浮轴承，其中，所述转轴组件包括导磁套环(505)，所述铁芯轴端挡板(503)与所述转子铁芯(502)的对应端部之间还设有隔磁板(504)。
  13. 根据权利要求1至10中任一项所述的磁悬浮轴承，其中，还包括转轴组件，所述转轴组件包括转子铁芯(502)，所述转子铁芯(502)套装于止推盘(600)的外圆周侧，所述转子铁芯(502)的轴向两端设置有铁芯轴端挡板(503)以对所述转子铁芯(502)的轴向定位，所述铁芯轴端挡板(503)导磁。
  14. 根据权利要求13所述的磁悬浮轴承，其中，两个所述铁芯轴端挡板(503)中的至少一个具有朝向所述转子铁芯(502)一侧沿其轴向延伸的延伸套环，所述延伸套环套装于所述转子铁芯(502)的中心通孔与所述止推盘(600)的外圆周壁之间。
  15. 根据权利要求13或14所述的磁悬浮轴承，其中，所述转轴组件还包括非导磁套环(501)或者导磁套环(504)，所述转子铁芯(502)以及所述非导磁套环(501)或者导磁套环(504)与所述止推盘(600)之间通过定位螺钉实现定位。
  16. 一种压缩机，其中，包括权利要求1至15中任一项所述的磁悬浮轴承。
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