WO2019119973A1 - 一种磁悬浮轴承、磁悬浮转子支承组件和压缩机 - Google Patents

一种磁悬浮轴承、磁悬浮转子支承组件和压缩机 Download PDF

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Publication number
WO2019119973A1
WO2019119973A1 PCT/CN2018/112312 CN2018112312W WO2019119973A1 WO 2019119973 A1 WO2019119973 A1 WO 2019119973A1 CN 2018112312 W CN2018112312 W CN 2018112312W WO 2019119973 A1 WO2019119973 A1 WO 2019119973A1
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WO
WIPO (PCT)
Prior art keywords
radial
rotor
stator core
axial
extension
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/CN2018/112312
Other languages
English (en)
French (fr)
Inventor
张小波
龚高
胡余生
刘健宁
张芳
田思园
张超
苏久展
李欣
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 Green Refrigeration Technology Center Co Ltd of Zhuhai
Original Assignee
Gree Green Refrigeration Technology Center Co Ltd 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 Green Refrigeration Technology Center Co Ltd of Zhuhai filed Critical Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Priority to EP18893018.4A priority Critical patent/EP3670946B1/en
Priority to US16/652,459 priority patent/US11323007B2/en
Publication of WO2019119973A1 publication Critical patent/WO2019119973A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/09—Structural association with bearings with 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
    • F16C32/0485—Active magnetic bearings for rotary movement with active support of three degrees of freedom
    • 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
    • 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
    • F04D29/051—Axial thrust balancing
    • 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
    • F16C2360/44—Centrifugal pumps
    • 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
    • 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
    • F16C32/0465—Details of the magnetic circuit of stationary parts of the magnetic circuit with permanent magnets provided in the magnetic circuit of the electromagnets

Definitions

  • the invention belongs to the technical field of magnetic levitation, and in particular relates to a magnetic suspension bearing, a magnetic suspension rotor supporting assembly and a compressor.
  • an axial and radial bias magnetic circuit is provided through a permanent magnetic circuit to provide a certain radial and axial force to the thrust disk; the control magnetic circuit is positively connected to the control coil.
  • the change of the superposition effect of the control magnetic circuit and the permanent magnet bias magnetic circuit in the axial direction can be adjusted, thereby adjusting the force variation in the axial direction of the thrust disk, and controlling the axial force of the thrust plate. effect.
  • the present invention has devised a magnetic suspension bearing, a magnetic suspension rotor support assembly and a compressor.
  • the technical problem to be solved by the present invention is to overcome the defects that the radial direction of the rotor of the magnetic suspension bearing in the prior art cannot be adjusted or can not be precisely adjusted, resulting in a bearing with low design flexibility and a small application range, thereby A magnetic suspension bearing, a magnetic suspension rotor support assembly and a compressor are provided.
  • the present invention provides a magnetic suspension bearing for supporting the rotor by interacting with a thrust disk on the rotor, comprising:
  • a radial stator core which is an annular structure, is disposed radially outward of the thrust plate, and corresponds to the thrust plate in a rotor axial direction, between the radial stator core and the thrust plate Along the first radial gap X1,
  • a radial control coil is disposed on the radial stator core and is capable of generating a radial electromagnetic force against the thrust disk in a radial direction of the rotor.
  • two adjacent through grooves are arranged along a circumferential direction of the radial stator core such that a length direction of the magnetic pole faces the radial stator core Extending in a radial direction; the radial control coil is wound around the pole such that the axis of the radial control coil is along a radial direction of the radial stator core.
  • the plurality of magnetic poles are evenly distributed along the circumferential direction of the radial stator core, and one of the radial control coils is wound around each of the magnetic poles.
  • the magnetic poles are four, and the adjacent two magnetic poles are separated by a circumferential angle of 90° in the circumferential direction of the radial stator core.
  • a permanent magnet disposed radially outward of the radial stator core and corresponding to an axial position of the radial stator core
  • a second stator core that is extendable from a radially outer side of the permanent magnet to a position adjacent the thrust disk to generate a permanent magnet force in the rotor axial direction and/or in the rotor radial direction to the thrust disk.
  • the second stator core includes a front stator core:
  • the front stator core includes a first axial extension, a first radial extension, and a second axial extension;
  • One end of the first axial extension portion is located radially outward of the permanent magnet and the other end extends in the axial direction of the rotor.
  • One end of the first radial extension is in contact with the other end of the first axial extension, and the other end of the first radial extension extends in a radial direction of the rotor.
  • One end of the second axial extension is in contact with the other end of the first radially extending portion, and the other end of the second axial extension extends in the axial direction of the rotor to a position close to the thrust plate And the other end of the second axial extension is spaced apart from the thrust disk by a first axial gap X2 in the axial direction of the rotor.
  • the second stator core includes a rear stator core:
  • the rear stator core includes a third axial extension, a second radial extension, and a fourth axial extension.
  • One end of the third axial extension portion is located radially outward of the permanent magnet and the other end extends in the axial direction of the rotor.
  • One end of the second radial extension is in contact with the other end of the third axial extension, and the other end of the second radial extension extends in a radial direction of the rotor.
  • One end of the fourth axial extension is in contact with the other end of the second radially extending portion, and the other end of the fourth axial extension extends in the axial direction of the rotor to a position close to the thrust plate And the other end of the fourth axial extension is spaced apart from the thrust disk by a second axial gap X3 in the axial direction.
  • the second stator core includes a rear stator core:
  • the rear stator core includes a third axial extension and a second radial extension
  • One end of the third axial extension portion is located radially outward of the permanent magnet and the other end extends in the axial direction of the rotor.
  • One end of the second radial extension is in contact with the other end of the third axial extension, and the other end of the second radial extension extends in a radial direction of the rotor.
  • a rotor retaining ring disposed on one side of the thrust disk axially adjacent to the second radially extending portion, the rotor retaining ring being fixedly coupled to the rotor;
  • the other end of the second radially extending portion extends in a radial direction of the rotor to a position close to the rotor retaining ring, and the other end of the second radially extending portion is radially opposite to the rotor retaining ring
  • the directions are separated by a second radial gap X3'.
  • the front stator core and the rear stator core are simultaneously included, the front stator core and the rear stator core are in contact with each other at a radially outer side of the permanent magnet so that the magnetic field can be continuous at the joint position Turn on.
  • the abutting position is located radially outward of the permanent magnet and opposite to an axial end surface of the permanent magnet in the axial direction of the rotor.
  • the present invention also provides a magnetic levitation rotor support assembly comprising a rotor and the magnetic levitation bearing of any of the foregoing, the magnetic levitation bearing being capable of supporting the rotor.
  • the rotor includes an optical axis and a thrust disk fixedly coupled to a radially outer side of the optical axis, and an axial and/or radial magnetic force is generated between the magnetic suspension bearing and the thrust disk to support the rotor.
  • the present invention also provides a compressor comprising the magnetic levitation rotor support assembly of any of the preceding claims.
  • the magnetic suspension bearing, the magnetic suspension rotor support assembly and the compressor provided by the invention have the following beneficial effects:
  • the magnetic suspension bearing, the magnetic suspension rotor support assembly and the compressor of the present invention through a radial stator core, having an annular structure, disposed radially outward of the thrust disk, and in the rotor axial direction with the thrust disk
  • a radial stator core and the thrust disk are separated from each other by a first radial gap X1
  • a radial control coil is disposed on the radial stator core and can be generated in a radial direction of the rotor.
  • the radial electromagnetic force of the thrust disk can generate a controllable and adjustable radial electromagnetic force on the thrust disk in the radial direction of the rotor, can make the flexibility of the bearing can be designed larger, and the application range of the bearing is effectively improved. Different from the axial force adjustment of the original technology, the radial force of the bearing can be adjusted, so the magnetic suspension bearing can be applied to more horizontal turbine machinery to expand the application range of the bearing;
  • the magnetic suspension bearing, the magnetic suspension rotor support assembly and the compressor of the present invention due to the general centrifugal compressor, have a large backward axial force during compressor operation and shutdown, which weakens or even cancels the force.
  • the present invention can eliminate the original axial force generated by the thrust plate and the radial force on the rotor retaining ring by providing the rotor retaining ring and the matching rear stator core.
  • the axial force of the air gap X3 is cancelled, so that the axial force generated by the front stator core can be used to offset the axial force of the compressor, instead
  • the radial force provided by the X3' air gap is applied to the centrifugal compressor to further reduce the operating current of the magnetic suspension bearing, reduce the loss, reduce the operating cost of the compressor, and improve the competitiveness of the product.
  • Embodiment 1 is an internal structural view in a longitudinal section of Embodiment 1 of a magnetic suspension bearing of the present invention
  • Figure 2 is a view showing the structure of the magnetic suspension bearing of the present invention in the direction of the rotor axis;
  • Figure 3 is an internal structural view in a longitudinal section of Embodiment 2 of the magnetic suspension bearing of the present invention.
  • Fig. 4 is a view showing the structure of the embodiment 2 of the magnetic suspension bearing of the present invention in the direction of the rotor axis.
  • the present invention provides a magnetic suspension bearing for supporting the rotor by interacting with a thrust plate 2 on the rotor, comprising:
  • the magnetic levitation bearing of the present invention is disposed radially outward of the thrust disk 2 of the rotor, and the rotor includes an optical axis 1 and a thrust plate 2 fixedly coupled to the radially outer peripheral surface of the optical axis 1,
  • a radial stator core 5 having an annular structure disposed radially outward of the thrust plate 2 and corresponding to the thrust plate 2 in a rotor axial direction, the radial stator core 5 and the The thrust discs 2 are separated by a first radial gap X1,
  • the radial stator core and the thrust disk are disposed by a radial stator core, an annular structure, disposed radially outward of the thrust disk, and corresponding to the thrust disk in a rotor axial direction
  • the radial stator is disposed on the radial stator core and can generate radial electromagnetic force to the thrust disk in the radial direction of the rotor, which is generated by the radial control coil
  • Electromagnetic magnetic circuit is shown in Figure 2, It is shown that the electromagnetic magnetic circuit surrounds the coil from the radially outer side of the coil, passes through the radial stator core in the radial direction, passes through the first radial gap X1, and then penetrates into the thrust disk 2 in the radial direction.
  • the disk 2 is circumferentially surrounded by a portion of the arc length, and then passes through the first radial gap X1 in the radial direction into the radial stator core 5, thereby forming an annular electromagnetic magnetic circuit as shown in FIG.
  • the electromagnetic force (ie, the control force) of the thrust disk in the radial direction ie, the control force
  • the ability to generate a controllable and adjustable radial electromagnetic force on the thrust disk in the radial direction of the rotor enables the bearing to be designed to be more flexible, and the application range of the bearing is effectively improved, which is different from the axial force of the prior art. Adjustment, the radial force of the bearing can be adjusted, so the magnetic suspension bearing can be applied to more horizontal turbine machinery to expand the range of applications of this type of bearing.
  • two or more through grooves 9 disposed on the radial stator core 5 at a position between a radially inner side and a radially outer side of the radial stator core, and the through groove 9 is axially oriented
  • two adjacent through grooves 9 form a pair of through grooves, and between the two through grooves 9 in one of the pair of through grooves, a diameter can be formed
  • the magnetic pole 10 is wound around the control coil 4.
  • two adjacent through grooves 9 are arranged along the circumferential direction of the radial stator core 5 such that the length direction of the magnetic pole 10 faces the radial stator
  • the radial direction of the iron core 5 extends; the radial control coil 4 is wound around the magnetic pole 10 such that the axis of the radial control coil 4 is along the radial direction of the radial stator core 5.
  • the longitudinal direction of the magnetic pole is arranged along the radial direction of the radial stator core so that the surrounding axis of the coil is also along the radial direction of the stator core, thereby being able to effectively follow
  • the radial direction acts on the electromagnetic force on the thrust disk, relative to the coil winding method in the background art (which is wound around the direction of the rotating shaft, and thus the electromagnetic force is formed along the axis of the rotor),
  • the adjustable electromagnetic force ie, the control magnetic force
  • the magnetic poles 10 are a plurality of, and the plurality of magnetic poles 10 are evenly distributed along the circumferential direction of the radial stator core 5, and one of the radial control coils 4 is wound around each of the magnetic poles 10. This is a preferred number of magnetic poles of the present invention and an arrangement thereof.
  • the stator cores are evenly distributed in the circumferential direction, and electromagnetic force in the radial direction can be generated at positions different in the circumferential direction, thereby increasing the diameter.
  • the magnitude of the electromagnetic force is such that its force is enhanced and uniform.
  • the magnetic poles 10 are four, and the circumferential angles between the adjacent two magnetic poles 10 are 90° apart in the circumferential direction of the radial stator core 5.
  • a permanent magnet 6 disposed radially outward of the radial stator core 5 and corresponding to an axial position of the radial stator core 5,
  • a second stator core is further extendable from a radially outer side of the permanent magnet 6 to a position close to the thrust disk 2 to generate a permanent magnet force in the rotor axial direction and/or in the rotor radial direction of the thrust disk 2. .
  • the biasing force in the radial direction ie, the permanent magnet force
  • the hybrid bias can reduce or even replace the radial and axial bias currents and reduce the magnetic force.
  • Bearing working loss; the invention proposes a hybrid bias magnetic suspension bearing, which double reduces bearing loss, and the radial force can be adjusted, which increases the flexibility of the bearing design and expands its use range.
  • the permanent magnet magnetic circuit generated by the permanent magnet 6 is as shown in FIG. It is shown that the permanent magnetic circuit penetrates from the permanent magnet 6 into the inside of the second core in a radial direction (partly on the left side and the other part on the right side), and the magnetic circuit on the left side sequentially in the second core Passing along the axial direction, piercing in the radial direction, and then passing through the axial direction, then passing through the first axial gap X2, the thrust disk 2, and then returning radially to the permanent magnet 6 to form a complete ring a permanent magnetic circuit (biasing magnetic circuit) to form a permanent magnet force (ie, a biasing force) in the axial direction of the thrust disk; the magnetic circuit on the right side is sequentially disposed in the axial direction inside the second core, Passing through in the radial direction, then passing through the axial direction, then passing through the second axial gap X3, the thrust disk 2, and then returning radially to the permanent magnet 6, forming a complete annular permanent magnet magnetic circuit (
  • the cost of magnetic suspension bearings mainly includes its structural manufacturing cost and later operating costs, while the later operating costs mainly depend on the operating current. The higher the current, the higher the operating cost. Therefore, designing a magnetic suspension bearing with a small operating current has been the industry's goal.
  • active magnetic suspension bearings active magnetic suspension bearings, permanent magnetic suspension bearings and hybrid magnetic bearings are included.
  • the control force of the active magnetic suspension bearing is determined by the coil current; the permanent magnet magnetic suspension bearing has no coil current, and the electromagnetic force is provided by the permanent magnet; the hybrid magnetic suspension bearing combines the functions of the former two, and the electromagnetic force is provided by the permanent magnet and the coil current.
  • Hybrid bearings generally provide only one-way (axial or radial) permanent magnetic bias magnetic force, one-way control magnetic force (axial or radial).
  • the second stator core includes a front stator core 3:
  • the front stator core 3 includes a first axial extension 31, a first radial extension 32 and a second axial extension 33;
  • One end of the first axial extending portion 31 is located radially outward of the permanent magnet 6 and the other end extends in the axial direction of the rotor.
  • One end of the first radial extension 32 is in contact with the other end of the first axial extension 31, and the other end of the first radial extension 32 extends in the radial direction of the rotor.
  • One end of the second axial extension 33 is in contact with the other end of the first radial extension 32, and the other end of the second axial extension 33 extends in the axial direction of the rotor to be close to the thrust The position of the disk 2, and the other end of the second axial extension 33 is spaced apart from the thrust disk 2 by a first axial gap X2 in the axial direction of the rotor.
  • the extension portion 32 and the second axial extension portion 33 can form a magnetic circuit conduction, and electrically connect the magnetic circuit on the permanent magnet 6 to the right end end surface of the second axial extension portion (as shown in FIG. 1), and then pass through the thrust plate 2
  • the first axial gap X2 formed between them creates an axial force acting on the left end face of the thrust plate, forming an axial biasing force (or axial permanent magnet force) in one direction.
  • the second stator core includes a rear stator core 7:
  • the rear stator core 7 includes a third axial extension 71, a second radial extension 72, and a fourth axial extension 73,
  • One end of the third axial extending portion 71 is located radially outward of the permanent magnet 6 and the other end extends in the axial direction of the rotor.
  • One end of the second radial extension 72 is in contact with the other end of the third axial extension 71, and the other end of the second radial extension 72 extends in the radial direction of the rotor.
  • One end of the fourth axial extending portion 73 is in contact with the other end of the second radially extending portion 72, and the other end of the fourth axial extending portion 73 extends in the axial direction of the rotor to be close to the thrust.
  • the position of the disk 2, and the other end of the fourth axial extension is spaced apart from the thrust disk 2 by a second axial gap X3 in the axial direction.
  • the extension portion 72 and the fourth axial extension portion 73 can form a magnetic circuit conduction, and electrically connect the magnetic circuit on the permanent magnet 6 to the left end end surface of the fourth axial extension portion (as shown in FIG. 1), and then pass through the thrust plate 2
  • the second axial gap X3 formed therebetween creates an axial force acting on the right end face of the thrust plate, forming an axial biasing force (or axial permanent magnet force) in the other direction.
  • this embodiment only replaces the specific structure of the rear stator core in Embodiment 1, and the others are the same as Embodiment 1, preferably,
  • the second stator core includes a rear stator core 7:
  • the rear stator core 7 includes a third axial extension 71 and a second radial extension 72,
  • One end of the third axial extending portion 71 is located radially outward of the permanent magnet 6, and the other end extends in the axial direction of the rotor.
  • One end of the second radial extension 72 is in contact with the other end of the third axial extension 71, and the other end of the second radial extension 72 extends in the radial direction of the rotor.
  • a rotor retaining ring 8 disposed on an axial side of the thrust plate 2 and adjacent to the second radial extending portion 72, the rotor retaining ring 8 being fixedly coupled to the rotor;
  • the other end of the second radially extending portion 72 extends in a radial direction of the rotor to a position close to the rotor retaining ring 8 , and the other end of the second radially extending portion 72 and the rotor retaining ring 8
  • the second radial gap X3' is spaced apart in the radial direction.
  • the extension portion 72 is capable of forming a magnetic circuit to conduct the magnetic path on the permanent magnet 6 to the lower end end surface of the second radially extending portion (as shown in FIG. 3), and further to form a second path formed between the rotor and the rotor retaining ring 8.
  • An axial force acting on the upper end surface of the rotor baffle is generated to the gap X3' to form a radial electromagnetic force (or a radial control magnetic force) in one direction.
  • the present invention provides a rotor retaining ring and The matching rear stator core can cancel the original axial force generated on the thrust disc, change the radial force to the rotor retaining ring, and convert to the radial force acting on the rotor, and the air gap
  • the axial force of the X3 is removed, so that the axial force generated by the front stator core can be used to offset the axial force of the compressor, and the radial force provided by the X3' air gap is applied to the centrifugal compressor. Further reduce the operating current of the magnetic suspension bearing, reduce the loss, reduce the operating cost of the compressor, and improve the competitiveness of the product.
  • the magnetic circuit direction of Embodiment 2 is substantially the same as the magnetic circuit direction of Embodiment 1, and the permanent magnetic circuit arrow of FIG. 3-4 is specifically referred to.
  • the disk 2 is circumferentially surrounded by a portion of the arc length, and then passes through the first radial gap X1 in the radial direction into the radial stator core 5, thereby forming an annular electromagnetic magnetic circuit as shown in FIG. ), thereby forming an electromagnetic force (ie, a control force) in the radial direction of the thrust disk.
  • the permanent magnet magnetic circuit generated by the permanent magnet 6 is as shown in FIG. It is shown that the permanent magnetic circuit penetrates from the permanent magnet 6 into the inside of the second core in a radial direction (partly on the left side and the other part on the right side), and the magnetic circuit on the left side sequentially in the second core Passing along the axial direction, piercing in the radial direction, and then passing through the axial direction, then passing through the first axial gap X2, the thrust disk 2, and then returning radially to the permanent magnet 6 to form a complete ring a permanent magnetic circuit (biasing magnetic circuit) to form a permanent magnet force (ie, a biasing force) in the axial direction of the thrust disk; the magnetic circuit on the right side is sequentially disposed in the axial direction inside the second core, Passing through in the radial direction, entering the rotor retaining ring 8 through the second radial gap X3' in the radial direction, and then passing through the rotor retaining ring in the axial direction,
  • the front stator core 3 and the rear stator core 7 are simultaneously included, the front stator core 3 and the rear stator core 7 are in contact with each other at a radially outer side of the permanent magnet 6, so that the magnetic field is The connected position can be continuously turned on.
  • the radially outer side of the front stator core 3 is connected to one end opposite to the rear stator core 7 and the radially outer side of the rear stator core 7 at an end opposite to the front stator core 3 .
  • the magnetic field can be turned on at the contact position 11, thereby ensuring the generation of the permanent magnet force without being weakened.
  • the contact position 11 is located radially outward of the permanent magnet 6 and is opposite to an axial end surface of the permanent magnet 6 in the axial direction of the rotor. As shown in FIGS. 1 and 3, this is a preferred arrangement position of the front stator core and the rear stator core in the magnetic suspension bearing of the present invention, which can effectively ensure that the two are well connected and further ensure the normal magnetic flux. Turn on.
  • the invention provides a novel hybrid bias magnetic suspension bearing, which can provide the bias magnetic force in the axial direction and the radial direction, and the control magnetic force in the radial direction, which can reduce the operating current of the control coil, reduce bearing loss and reduce operating cost.
  • the optimized bearing structure (Fig. 3) can provide a large axial biasing force to weaken or even reduce the influence of aerodynamic forces on the rotor, reduce the operating current of the magnetic suspension bearing of the magnetic suspension system, and reduce the magnetic levitation. The operating cost of the centrifuge.
  • a hybrid bias magnetic suspension bearing structure which provides axial and radial bias magnetic force and control magnetic force in radial direction; reduces bearing loss and reduces operating cost of magnetic suspension bearing.
  • a hybrid bias magnetic suspension bearing structure suitable for centrifugal compressors is proposed, which can provide large axial biasing force to offset axial aerodynamic force and reduce the working current of axial magnetic suspension bearing of magnetic suspension system, thereby reducing bearing loss and bearing. Operating costs.
  • X1 is a radial gap formed by the inner circle of the 5-radial stator core and the outer circle of the 2-thrust disk, which can provide radial biasing force and control magnetic force.
  • X2 is a 3-front stator core with a small diameter right end face formed on the left end face of the 2-thrust disk, providing an axial biasing force to the left.
  • X3 is a 7- rear stator core with a small diameter left end surface formed with the right end surface of the 2-thrust disk, and the axial biasing force shown to the right in FIG. 1 is provided.
  • X3' is a 7- rear stator core inner circular surface formed with an outer circumference of the 8-rotor retaining ring to provide a radial biasing force.
  • X1 is the radial clearance formed by the inner circle of the 5-radial stator core and the outer circumference of the 2-thrust disk, which provides radial biasing force and control magnetic force.
  • X2 is a small front end face of the 3-front stator core and a left end face of the 2-thrust disk, providing an axial biasing force to the left.
  • X3 is a rear end portion of the rear stator core 1 having a small diameter and a right end surface of the 2-thrust disk, and provides an axial biasing force to the right.
  • X3' is a 7'- rear stator core inner circular surface formed with an outer circumference of the 8-rotor retaining ring to provide a radial biasing force.
  • Embodiment 1 (Embodiment 1):
  • the 6-permanent magnet provides a radial permanent magnet bias magnetic force through the air gap X1 after the assembly relationship is completed as shown.
  • 6- permanent magnets provide axial bias magnetic force through air gaps X2 and X3 respectively
  • the 4-radial control coil energizes and provides radial control of the magnetic force through the air gap X1.
  • the hybrid bias magnetic suspension bearing can provide the axial force of the permanent magnet bias, a part of the permanent magnet biased radial force and the controllable electromagnetic radial force, so that the bearing can reduce the axial and radial directions.
  • the current also provides a controlled radial force for active suspension.
  • Embodiment 2 (Embodiment 2):
  • the 6-permanent magnet provides a radial permanent magnet bias magnetic force through the air gap X1.
  • 6- permanent magnet provides axial offset magnetic force through air gap X2
  • 6- permanent magnet provides radial bias magnetic force through air gap X3'
  • the 4-radial control coil is energized, it will provide radial control of the magnetic force through the air gap X1.
  • the hybrid bias magnetic suspension bearing can provide a large permanent magnet biasing axial force, and cancel the axial force of the pneumatic component (such as impeller, diffuser, etc.) in the magnetic suspension centrifugal compressor to reduce the rotor.
  • the rotor runs in axial load.
  • a further part of the permanent magnet biased radial force and the controllable electromagnetic radial force can be provided.
  • two air gaps (X1 and X3') provide radial biasing force, which can be further reduced.
  • the coil current is controlled radially during operation. Thereby, the axial and radial currents can be further reduced, and a controllable radial force can be provided to achieve the effect of active suspension.
  • the present invention also provides a magnetic levitation rotor support assembly comprising a rotor and the magnetic levitation bearing of any of the foregoing, the magnetic levitation bearing being capable of supporting the rotor.
  • the magnetic suspension bearing By including the aforementioned magnetic suspension bearing, it is possible to generate a controllable and adjustable radial electromagnetic force in the radial direction of the thrust disk, which can make the flexibility of the bearing can be designed larger, and the application range of the bearing is effectively improved, which is different from the original
  • the technical axial force adjustment, the radial force of the bearing can be adjusted, so the magnetic suspension bearing can be applied to more horizontal turbine machinery to expand the application range of the bearing;
  • the present invention provides a rotor retaining ring and The matching rear stator core can cancel the original axial force generated on the thrust disc, change the radial force to the rotor retaining ring, and convert to the radial force acting on the rotor, and the air gap
  • the axial force of the X3 is removed, so that the axial force generated by the front stator core can be used to offset the axial force of the compressor, and the radial force provided by the X3' air gap is applied to the centrifugal compressor. Further reduce the operating current of the magnetic suspension bearing, reduce the loss, reduce the operating cost of the compressor, and improve the competitiveness of the product.
  • the rotor includes an optical axis 1 and a thrust disk 2 fixedly coupled to a radially outer side of the optical axis 1, and an axial and/or radial magnetic force can be generated between the magnetic suspension bearing and the thrust disk 2 to support the rotor Said rotor.
  • the radial direction of the disc produces an adjustable electromagnetic force that allows the radial direction of the rotor to be adjusted, expanding the range of applications of the bearing and applying it to more centrifugal compressors (horizontal turbine machinery).
  • the present invention also provides a compressor comprising the magnetic levitation rotor support assembly of any of the preceding claims. It is preferably a centrifugal compressor.
  • a compressor comprising the magnetic levitation rotor support assembly of any of the preceding claims. It is preferably a centrifugal compressor.
  • the aforementioned magnetic levitation rotor bearing assembly it is possible to generate a controllable and adjustable radial electromagnetic force in the radial direction of the thrust disk, which can make the bearing flexible design larger, and the application range of the bearing can be effectively improved.
  • the radial force of the bearing can be adjusted, so the magnetic suspension bearing can be applied to more horizontal turbine machinery to expand the application range of the bearing;
  • the invention can cancel the original axial force generated on the thrust disc, change the radial force to the rotor retaining ring, and convert to the rotor.
  • the upper radial force cancels the axial force of the air gap X3, so that the axial force generated by the front stator core can be used to offset the axial force of the compressor, instead of the diameter provided by the X3' air gap Xiangli, applied to centrifugal compressors, further reduces the operating current of magnetic suspension bearings, reduces losses, reduces compressor operating costs, and improves product competitiveness.

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Abstract

磁悬浮轴承、磁悬浮转子支承组件和压缩机，磁悬浮轴承用于通过与转子上的推力盘（2）相作用而支承转子，其包括：为环状结构的径向定子铁芯（5），设置在推力盘（2）的径向外侧，且在转子轴向上与推力盘（2）相对应，径向定子铁芯（5）与推力盘（2）之间相隔第一径向间隙X1，径向控制线圈（4）设置在径向定子铁芯（5）上，且能沿转子径向方向产生对推力盘（2）的径向电磁力。该磁悬浮轴承能沿转子径向方向产生对推力盘可调控的径向电磁力，使得轴承的柔性能够设计得更大，轴承的应用范围得到有效提高。

Description

一种磁悬浮轴承、磁悬浮转子支承组件和压缩机
本申请要求于2017年12月21日提交中国专利局、申请号为201711390234.1、发明名称为“一种磁悬浮轴承、磁悬浮转子支承组件和压缩机”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明属于磁悬浮技术领域，具体涉及一种磁悬浮轴承、磁悬浮转子支承组件和压缩机。
背景技术
原有技术的磁悬浮轴承中工作时，通过永磁磁路提供轴向和径向的偏置磁路，给推力盘提供一定的径向、轴向力；控制磁路在控制线圈通入正、负方向的电流时，可以调节控制磁路和永磁偏置磁路在轴向方向上的叠加效果变化，从而调节推力盘轴向方向的受力变化，起到控制推力盘轴向受力的效果。
但是对于卧式磁悬浮透平机械，一般要克服重力作用，以及竖直平面内的离心力作用。因此，其转子在径向方向的受力需可以调节，而目前技术中的磁悬浮轴承在转子的径向方向的受力无法进行调节，导致轴承的设计柔性较低、应用范围较小。并且一般的离心式压缩机，在压缩机运行和停机时都会有一个向后的较大轴向力，该轴向力会对转子的稳定性造成不良的影响，影响其结构强度和使用寿命。
由于现有技术中的磁悬浮轴承存在在转子的径向方向的受力无法进行调节的问题，导致轴承的设计柔性较低、应用范围较小，且压缩机运行和停机时都会有一个向后的较大轴向力，该轴向力会对转子的稳定性造成不良的影响，影响其结构强度和使用寿命，因此本发明研究设计出一种磁悬浮轴承、磁悬浮转子支承组件和压缩机。
发明内容
因此，本发明要解决的技术问题在于克服现有技术中的磁悬浮轴承的转子的径向方向的受力无法调控或无法精确调控，导致轴承的设计柔性较低、应用范围较小的缺陷，从而提供一种磁悬浮轴承、磁悬浮转子支承组件和压缩机。
本发明提供一种磁悬浮轴承，用于通过与转子上的推力盘相作用而支承所述转子，其包括：
径向定子铁芯，为环状结构、设置在所述推力盘的径向外侧、且在转子轴向上与所述推力盘相对应，所述径向定子铁芯与所述推力盘之间相隔第一径向间隙X1，
径向控制线圈，设置在所述径向定子铁芯上、且能沿转子径向方向产生对所述推力盘的径向电磁力。
优选地，
还包括两个以上的通槽，设置在所述径向定子铁芯上、位于径向定子铁芯径向内侧和径向外侧之间的位置，且所述通槽沿轴向方向贯通所述径向定子铁芯，两个相邻所述通槽形成一个通槽对、且在一个所述通槽对中的两个所述通槽之间形成能够供所述径向控制线圈缠绕的磁极。
优选地，
在一个所述通槽对中、两个相邻的所述通槽沿所述径向定子铁芯的周向进行排布，使得所述磁极的长度方向朝着所述径向定子铁芯的径向方向延伸；所述径向控制线圈围绕所述磁极缠绕、使得所述径向控制线圈的围绕轴线沿着所述径向定子铁芯的径向方向。
优选地，
所述磁极为多个、多个所述磁极沿所述径向定子铁芯的周向方向均匀分布，且在每个磁极上均缠绕一个所述径向控制线圈。
优选地，
所述磁极为4个、且相邻两磁极之间在径向定子铁芯的周向上相隔90°的圆周角。
优选地，
还包括永磁体，所述永磁体设置在所述径向定子铁芯的径向外侧、且与所述径向定子铁芯的轴向位置相对应，
还包括第二定子铁芯，能够从永磁体的径向外侧延伸至靠近所述推力盘的 位置，以对所述推力盘产生沿转子轴向和/或沿转子径向的永磁力。
优选地，
所述第二定子铁芯包括前定子铁芯：
所述前定子铁芯包括第一轴向延伸部、第一径向延伸部和第二轴向延伸部；
所述第一轴向延伸部的一端位于所述永磁体的径向外侧、另一端沿转子轴向方向进行延伸，
所述第一径向延伸部的一端与所述第一轴向延伸部的另一端相接、所述第一径向延伸部的另一端沿着转子径向方向延伸，
所述第二轴向延伸部的一端与所述第一径向延伸部的另一端相接、所述第二轴向延伸部的另一端沿转子轴向方向延伸至靠近所述推力盘的位置，且所述第二轴向延伸部的另一端与所述推力盘之间在转子轴向方向相隔第一轴向间隙X2。
优选地，
所述第二定子铁芯包括后定子铁芯：
所述后定子铁芯包括第三轴向延伸部、第二径向延伸部和第四轴向延伸部，
所述第三轴向延伸部的一端位于所述永磁体的径向外侧、另一端沿转子轴向方向进行延伸，
所述第二径向延伸部的一端与所述第三轴向延伸部的另一端相接、所述第二径向延伸部的另一端沿着转子径向方向延伸，
所述第四轴向延伸部的一端与所述第二径向延伸部的另一端相接、所述第四轴向延伸部的另一端沿转子轴向方向延伸至靠近所述推力盘的位置，且所述第四轴向延伸部的另一端与所述推力盘之间在轴向方向相隔第二轴向间隙X3。
优选地，
所述第二定子铁芯包括后定子铁芯：
所述后定子铁芯包括第三轴向延伸部和第二径向延伸部，
所述第三轴向延伸部的一端位于所述永磁体的径向外侧、另一端沿转子轴向方向进行延伸，
所述第二径向延伸部的一端与所述第三轴向延伸部的另一端相接、所述第二径向延伸部的另一端沿着转子径向方向延伸，
还包括设置于所述推力盘轴向一侧、靠近所述第二径向延伸部位置的转子 挡环，所述转子挡环与所述转子固定连接；
所述第二径向延伸部的另一端沿转子径向方向延伸至靠近所述转子挡环的位置，且所述第二径向延伸部的另一端与所述转子挡环之间在径向方向相隔第二径向间隙X3’。
优选地，
当同时包括前定子铁芯和后定子铁芯时，所述前定子铁芯与所述后定子铁芯在所述永磁体的径向外侧的位置相接、以使得磁场在相接位置能够连续导通。
优选地，
所述相接位置位于所述永磁体的径向外侧、且在转子轴向方向上与所述永磁体的一轴向端面相对。
本发明还提供一种磁悬浮转子支承组件，其包括转子和前任一项所述的磁悬浮轴承，所述磁悬浮轴承能够对所述转子进行支承。
优选地，
所述转子包括光轴和固定连接于所述光轴径向外侧的推力盘，所述磁悬浮轴承与所述推力盘之间能够产生轴向和/或径向的磁力而支承所述转子。
本发明还提供一种压缩机，其包括前任一项所述的磁悬浮转子支承组件。
本发明提供的一种磁悬浮轴承、磁悬浮转子支承组件和压缩机具有如下有益效果：
1.本发明的磁悬浮轴承、磁悬浮转子支承组件和压缩机，通过径向定子铁芯，为环状结构、设置在所述推力盘的径向外侧、且在转子轴向上与所述推力盘相对应，所述径向定子铁芯与所述推力盘之间相隔第一径向间隙X1，径向控制线圈，设置在所述径向定子铁芯上、且能沿转子径向方向产生对所述推力盘的径向电磁力，能够产生对推力盘沿转子径向方向的可控可调节的径向电磁力、能够使得轴承的柔性能够设计得更大，轴承的应用范围得到有效提高，区别于原有技术的轴向受力调节，该轴承径向受力可以调节，因此该磁悬浮轴承可应用到更多的卧式透平机械上，扩大该类轴承应用范围；
2.本发明的磁悬浮轴承、磁悬浮转子支承组件和压缩机，由于一般的离心式压缩机，在压缩机运行和停机时都会有一个向后的较大轴向力，为削弱甚至抵消该作用力对转子稳定性不良影响，本发明通过设置转子挡环和与之相匹配 的后定子铁芯，能够取消掉原有的对推力盘产生的轴向力、改为对转子挡环产生径向力、再转换为作用于转子上的径向力，将气隙X3的轴向力作用取消，使得前定子铁芯产生的轴向力能够被用于抵消该压缩机的轴向力，改为由X3’气隙提供的径向力，应用到离心压缩机中，进一步的缩减磁悬浮轴承工作电流，降低损耗，减小压缩机运营成本，提高产品竞争力。
附图说明
图1是本发明的磁悬浮轴承的实施例1纵向截面内的内部结构图；
图2是本发明的磁悬浮轴承的实施例1沿转子轴线方向的观察结构图；
图3是本发明的磁悬浮轴承的实施例2纵向截面内的内部结构图；
图4是本发明的磁悬浮轴承的实施例2沿转子轴线方向的观察结构图。
图中附图标记表示为：
1、光轴；2、推力盘；3、前定子铁芯；31、第一轴向延伸部；32、第一径向延伸部；33、第二轴向延伸部；4、径向控制线圈；5、径向定子铁芯；6、永磁体；7、后定子铁芯；71、第三轴向延伸部；72、第二径向延伸部；73、第四轴向延伸部；8、转子挡环；9、通槽；10、磁极；11、相接位置。
具体实施方式
附图1-4中的
Figure PCTCN2018112312-appb-000001
表示偏置磁路(即永磁所产生的磁路)，
Figure PCTCN2018112312-appb-000002
表示控制磁路(即电流线圈所产生的磁路)。
实施例1
如图1-2所示，本发明提供一种磁悬浮轴承，用于通过与转子上的推力盘2相作用而支承所述转子，其包括：
本发明的磁悬浮轴承设置在转子的推力盘2的径向外侧，转子包括光轴1和固定连接在光轴1径向外周面上的推力盘2，
径向定子铁芯5，为环状结构、设置在所述推力盘2的径向外侧、且在转子轴向上与所述推力盘2相对应，所述径向定子铁芯5与所述推力盘2之间相隔第一径向间隙X1，
径向控制线圈4，设置在所述径向定子铁芯5上、且能沿转子径向方向产 生对所述推力盘2的径向电磁力。
通过径向定子铁芯，为环状结构、设置在所述推力盘的径向外侧、且在转子轴向上与所述推力盘相对应，所述径向定子铁芯与所述推力盘之间相隔第一径向间隙X1，径向控制线圈，设置在所述径向定子铁芯上、且能沿转子径向方向产生对所述推力盘的径向电磁力，径向控制线圈产生的电磁磁路如图2所示、以
Figure PCTCN2018112312-appb-000003
表示，该电磁磁路从线圈径向外侧环绕线圈、再沿径向方向穿过径向定子铁芯、再穿过第一径向间隙X1、再沿径向穿入推力盘2中，在推力盘2中沿周向环绕一部分弧长后、再沿径向穿过第一径向间隙X1、进入径向定子铁芯5中，从而形成如图2所示的环形电磁磁路，从而形成对推力盘沿径向方向的电磁力(即控制力)。能够产生对推力盘沿转子径向方向的可控可调节的径向电磁力、能够使得轴承的柔性能够设计得更大，轴承的应用范围得到有效提高，区别于原有技术的轴向受力调节，该轴承径向受力可以调节，因此该磁悬浮轴承可应用到更多的卧式透平机械上，扩大该类轴承应用范围。
优选地，
还包括两个以上的通槽9，设置在所述径向定子铁芯5上、位于径向定子铁芯径向内侧和径向外侧之间的位置，且所述通槽9沿轴向方向贯通所述径向定子铁芯5，两个相邻所述通槽9形成一个通槽对、且在一个所述通槽对中的两个所述通槽9之间形成能够供所述径向控制线圈4缠绕的磁极10。
这是本发明的磁悬浮轴承中形成能够供线圈缠绕以提供径向方向电磁力的磁极的设置方式，通过开通槽的形式、在径向定子铁芯面板上形成如图2所示的中间连接部(即磁极)和两边的中空部(即通槽)，能够使得线圈能够从一侧通槽穿入、从另一侧通槽穿出，从而围绕中间连接部(即磁极)环绕成线圈组，进而产生沿径向方向的电磁力作用。
优选地，
在一个所述通槽对中、两个相邻的所述通槽9沿所述径向定子铁芯5的周向进行排布，使得所述磁极10的长度方向朝着所述径向定子铁芯5的径向方向延伸；所述径向控制线圈4围绕所述磁极10缠绕、使得所述径向控制线圈4的围绕轴线沿着所述径向定子铁芯5的径向方向。
由于线圈的缠绕是围绕磁极进行缠绕的，因此磁极的长度方向沿着径向定子铁芯的径向方向布置能够使得线圈的围绕轴线也沿着定子铁芯的径向方向， 从而能够有效地沿着径向方向产生作用与推力盘上的电磁力，相对于背景技术中的线圈缠绕方式而言(其是环绕转轴的方向进行缠绕的、因此形成的电磁力是沿着转子的轴线方向)、能够形成沿转子径向方向的可供调节的电磁力(即控制磁力)，使得轴承的安全可靠性能得以增加，应用范围更加广泛。
优选地，
所述磁极10为多个、多个所述磁极10沿所述径向定子铁芯5的周向方向均匀分布，且在每个磁极10上均缠绕一个所述径向控制线圈4。这是本发明的磁极的优选个数及其排布方式，在定子铁芯的周向方向均布、能够在周向方向不同的位置均能够产生沿径向方向的电磁力作用，从而增加径向电磁力的大小，使其作用力得以增强和均匀。
优选地，
所述磁极10为4个、且相邻两磁极10之间在径向定子铁芯5的周向上相隔90°的圆周角。这是本发明的磁极的进一步的优选个数和布置形式，如图2和4所示，其在圆周方向均布、且4个分别产生4处沿径向方向的可控电磁力，相比于1个磁极和1组线圈而言其电磁力增大了4倍，有效地提高了可控电磁力的作用。
优选地，
还包括永磁体6，所述永磁体6设置在所述径向定子铁芯5的径向外侧、且与所述径向定子铁芯5的轴向位置相对应，
还包括第二定子铁芯，能够从永磁体6的径向外侧延伸至靠近所述推力盘2的位置，以对所述推力盘2产生沿转子轴向和/或沿转子径向的永磁力。
这是本发明的磁悬浮轴承的进一步优选的结构形式，通过设置永磁体和第二定子铁芯，能够使得在电磁线圈产生径向电磁力的基础上进一步地还能够产生沿转子轴向和/或径向方向的偏置力(即永磁力)，形成混合偏置的径向磁力可以调节的磁悬浮轴承，混合偏置可以起到减小甚至替代径向、轴向偏置电流的作用，降低磁轴承工作损耗；本发明提出一种混合偏置磁悬浮轴承，双重降低轴承损耗，同时径向力为可以调节的，增大该轴承设计柔性，扩大其使用范围。
永磁体6产生的永磁磁路如图1所示、以
Figure PCTCN2018112312-appb-000004
表示，该永磁磁路从永磁体6沿径向方向穿入第二铁芯的内部(一部分位于左侧、另一部分位于右 侧)，位于左侧的磁路在第二铁芯内部依次地沿轴线方向穿设、沿径向方向穿设、再沿轴线方向穿设，接着穿过第一轴向间隙X2，推力盘2，再沿径向回到永磁体6中，形成一个完整的环形永磁磁路(偏置磁路)，从而形成对推力盘沿轴向方向的永磁力(即偏置力)；位于右侧的磁路在第二铁芯内部依次地沿轴线方向穿设、沿径向方向穿设、再沿轴线方向穿设，接着穿过第二轴向间隙X3，推力盘2，再沿径向回到永磁体6中，形成一个完整的环形永磁磁路(偏置磁路)，从而形成对推力盘沿轴向方向的永磁力(即偏置力)。
一般的，磁悬浮轴承成本主要包含其结构制造成本以及后期运营成本，而后期运营成本主要取决于其运行电流大小，电流越大，运营成本越高。因而，设计一款工作电流小的磁悬浮轴承一直是行业追求的目标。对于磁悬浮轴承，包含主动式磁悬浮轴承、永磁悬浮轴承以及混合式磁悬浮轴承。主动式磁悬浮轴承控制力全靠线圈电流大小决定；永磁磁悬浮轴承无线圈电流，靠永磁体提供电磁力；混合式磁悬浮轴承融合前两者的作用，电磁力靠永磁体和线圈电流提供。混合式轴承一般的仅能提供单向(轴向或者径向)的永磁偏置磁力，单向的控制磁力(轴向或者径向)。
本文提出一种全新的混合偏置的磁悬浮轴承，可以提供轴向、径向方向的偏置磁力，径向方向的控制磁力，可以减小控制线圈运行电流，降低轴承损耗，减少运营成本。
优选地，
所述第二定子铁芯包括前定子铁芯3：
所述前定子铁芯3包括第一轴向延伸部31、第一径向延伸部32和第二轴向延伸部33；
所述第一轴向延伸部31的一端位于所述永磁体6的径向外侧、另一端沿转子轴向方向进行延伸，
所述第一径向延伸部32的一端与所述第一轴向延伸部31的另一端相接、所述第一径向延伸部32的另一端沿着转子径向方向延伸，
所述第二轴向延伸部33的一端与所述第一径向延伸部32的另一端相接、所述第二轴向延伸部33的另一端沿转子轴向方向延伸至靠近所述推力盘2的位置，且所述第二轴向延伸部33的另一端与所述推力盘2之间在转子轴向方向相隔第一轴向间隙X2。
这是本发明的磁悬浮轴承的实施例1的第二定子铁芯包括前定子铁芯时、前定子铁芯的优选结构形式，通过依次相接的第一轴向延伸部31、第一径向延伸部32和第二轴向延伸部33能够形成磁路导通，将永磁体6上的磁路导通至第二轴向延伸部的右端端面(如图1)，进而通过与推力盘2之间形成的第一轴向间隙X2产生作用至推力盘左端面上的轴向力，形成一个方向的轴向偏置力(或称轴向永磁力)。
优选地，
所述第二定子铁芯包括后定子铁芯7：
所述后定子铁芯7包括第三轴向延伸部71、第二径向延伸部72和第四轴向延伸部73，
所述第三轴向延伸部71的一端位于所述永磁体6的径向外侧、另一端沿转子轴向方向进行延伸，
所述第二径向延伸部72的一端与所述第三轴向延伸部71的另一端相接、所述第二径向延伸部72的另一端沿着转子径向方向延伸，
所述第四轴向延伸部73的一端与所述第二径向延伸部72的另一端相接、所述第四轴向延伸部73的另一端沿转子轴向方向延伸至靠近所述推力盘2的位置，且所述第四轴向延伸部的另一端与所述推力盘2之间在轴向方向相隔第二轴向间隙X3。
这是本发明的磁悬浮轴承的实施例1的第二定子铁芯包括后定子铁芯时、后定子铁芯的优选结构形式，通过依次相接的第三轴向延伸部71、第二径向延伸部72和第四轴向延伸部73能够形成磁路导通，将永磁体6上的磁路导通至第四轴向延伸部的左端端面(如图1)，进而通过与推力盘2之间形成的第二轴向间隙X3产生作用至推力盘右端面上的轴向力，形成另一个方向的轴向偏置力(或称轴向永磁力)。
实施例2
参见图3-4，本实施例仅仅是对实施例1中后定子铁芯的具体结构做出了相应的替换，其他均与实施例1相同，优选地，
所述第二定子铁芯包括后定子铁芯7：
所述后定子铁芯7包括第三轴向延伸部71和第二径向延伸部72，
所述第三轴向延伸部71的一端位于所述永磁体6的径向外侧、另一端沿 转子轴向方向进行延伸，
所述第二径向延伸部72的一端与所述第三轴向延伸部71的另一端相接、所述第二径向延伸部72的另一端沿着转子径向方向延伸，
还包括设置于所述推力盘2轴向一侧、靠近所述第二径向延伸部72位置的转子挡环8，所述转子挡环8与所述转子固定连接；
所述第二径向延伸部72的另一端沿转子径向方向延伸至靠近所述转子挡环8的位置，且所述第二径向延伸部72的另一端与所述转子挡环8之间在径向方向相隔第二径向间隙X3’。
这是本发明的磁悬浮轴承的实施例2的第二定子铁芯包括后定子铁芯时、后定子铁芯的优选结构形式，通过依次相接的第三轴向延伸部71和第二径向延伸部72能够形成磁路导通，将永磁体6上的磁路导通至第二径向延伸部的下端端面(如图3)，进而通过与转子挡环8之间形成的第二径向间隙X3’产生作用至转子挡环上端面上的轴向力，形成一个方向的径向电磁力(或称径向控制磁力)。
由于一般的离心式压缩机，在压缩机运行和停机时都会有一个向后的较大轴向力，为削弱甚至抵消该作用力对转子稳定性不良影响，本发明通过设置转子挡环和与之相匹配的后定子铁芯，能够取消掉原有的对推力盘产生的轴向力、改为对转子挡环产生径向力、再转换为作用于转子上的径向力，将气隙X3的轴向力作用取消，使得前定子铁芯产生的轴向力能够被用于抵消该压缩机的轴向力，改为由X3’气隙提供的径向力，应用到离心压缩机中，进一步的缩减磁悬浮轴承工作电流，降低损耗，减小压缩机运营成本，提高产品竞争力。
实施例2的磁路方向与实施例1的磁路方向基本相同，具体参见图3-4的永磁磁路箭头
Figure PCTCN2018112312-appb-000005
和电磁磁路箭头
Figure PCTCN2018112312-appb-000006
的方向。即径向控制线圈产生的电磁磁路如图4所示、以
Figure PCTCN2018112312-appb-000007
表示，该电磁磁路从线圈径向外侧环绕线圈、再沿径向方向穿过径向定子铁芯、再穿过第一径向间隙X1、再沿径向穿入推力盘2中，在推力盘2中沿周向环绕一部分弧长后、再沿径向穿过第一径向间隙X1、进入径向定子铁芯5中，从而形成如图2所示的环形电磁磁路(两个环形)，从而形成对推力盘沿径向方向的电磁力(即控制力)。
永磁体6产生的永磁磁路如图3所示、以
Figure PCTCN2018112312-appb-000008
表示，该永磁磁路从永磁体6沿径向方向穿入第二铁芯的内部(一部分位于左侧、另一部分位于右 侧)，位于左侧的磁路在第二铁芯内部依次地沿轴线方向穿设、沿径向方向穿设、再沿轴线方向穿设，接着穿过第一轴向间隙X2，推力盘2，再沿径向回到永磁体6中，形成一个完整的环形永磁磁路(偏置磁路)，从而形成对推力盘沿轴向方向的永磁力(即偏置力)；位于右侧的磁路在第二铁芯内部依次地沿轴线方向穿设、沿径向方向穿设，沿径向方向穿过第二径向间隙X3’进入转子挡环8中、再沿轴线方向穿设转子挡环，进入推力盘2中，再沿径向回到永磁体6中，形成一个完整的环形永磁磁路(偏置磁路)，从而形成对推力盘沿轴向方向的永磁力(即偏置力)。
优选地，
当同时包括前定子铁芯3和后定子铁芯7时，所述前定子铁芯3与所述后定子铁芯7在所述永磁体6的径向外侧的位置相接、以使得磁场在相接位置能够连续导通。所述前定子铁芯3的径向外侧在与所述后定子铁芯7相对的一端、与所述后定子铁芯7的径向外侧在与所述前定子铁芯3相对的一端相接。
通过将前定子铁芯与后定子铁芯之间相接、能够使得磁场能够在相接位置11处被导通，进而保证永磁力的产生而不会减弱。
优选地，
所述相接位置11位于所述永磁体6的径向外侧、且在转子轴向方向上与所述永磁体6的一轴向端面相对。如图1和3所示，这是本发明的磁悬浮轴承中前定子铁芯和后定子铁芯相接位置的优选设置位置，能够有效地保证二者良好地相接、进一步保证磁通的正常导通。
本发明提出一种全新的混合偏置的磁悬浮轴承，可以提供轴向、径向方向的偏置磁力，径向方向的控制磁力，可以减小控制线圈运行电流，降低轴承损耗，减少运营成本，同时，优化后的轴承结构(如图3)，可以提供较大的轴向偏置磁力去削弱、甚至减小气动力对转子的影响，减小磁悬浮系统轴向磁悬浮轴承的工作电流，降低磁悬浮离心机的运营成本。
1、提出一种混合偏置磁悬浮轴承结构，提供轴向、径向偏置磁力以及径向方向的控制磁力；降低轴承损耗，减少磁悬浮轴承运营成本。
2、提出一种适用于离心压缩机的混合偏置磁悬浮轴承结构，可以提供较大的轴向偏置力抵消轴向气动力，降低磁悬浮系统轴向磁悬浮轴承工作电流，从而降低轴承损耗及轴承运营成本。
其中，X1为5-径向定子铁芯内圆与2-推力盘外圆形成的径向间隙，可提供径向偏置力和控制磁力。X2为3-前定子铁芯的直径小的右端面与2-推力盘的左端面形成，提供图示向左的轴向偏置力。X3为7-后定子铁芯的直径小的左端面与2-推力盘的右端面形成，提供图1示向右的轴向偏置力。X3’为7-后定子铁芯内圆面与8-转子挡环外圆面形成，提供径向偏置力。
各间隙：
X1为5-径向定子铁芯内圆与2-推力盘外圆形成的径向间隙，可提供径向偏置力和控制磁力。
X2为3-前定子铁芯小的右端面与2-推力盘的左端面形成，提供图示向左的轴向偏置力。
X3为7-后定子铁芯1的直径小的左端面与2-推力盘的右端面形成，提供图示向右的轴向偏置力。
X3’为7’-后定子铁芯内圆面与8-转子挡环外圆面形成，提供径向偏置力。
实施方式1(实施例1)：
如图1-2所示，按图示位置完成装配关系后，6-永磁体通过气隙X1提供径向永磁偏置磁力
Figure PCTCN2018112312-appb-000009
6-永磁体通过气隙X2、X3提供轴向偏置磁力分别为
Figure PCTCN2018112312-appb-000010
Figure PCTCN2018112312-appb-000011
工作时，4-径向控制线圈通电后，将通过气隙X1提供径向控制磁力
Figure PCTCN2018112312-appb-000012
从而此实施方式可以提供的径向力为：
Figure PCTCN2018112312-appb-000013
从而此实施方式可以提供的轴向力为：
Figure PCTCN2018112312-appb-000014
由此可见，该混合偏置磁悬浮轴承可以提供永磁偏置的轴向力，一部分永磁偏置的径向力和可控制的电磁径向力，从而该轴承可以减小轴向、径向电流的同时还能提供可控制的径向力，起到主动悬浮的效果。
实施方式2(实施例2)：
如图3-4所示，按图示位置完成装配关系后，6-永磁体通过气隙X1提供径向永磁偏置磁力
Figure PCTCN2018112312-appb-000015
6-永磁体通过气隙X2提供轴向偏置磁力为
Figure PCTCN2018112312-appb-000016
6-永磁体通过气隙X3’提供径向偏置磁力为
Figure PCTCN2018112312-appb-000017
工作时，4-径向控制线圈通电后， 将通过气隙X1提供径向控制磁力
Figure PCTCN2018112312-appb-000018
从而此实施方式可以提供的径向力为：
Figure PCTCN2018112312-appb-000019
从而此实施方式可以提供的轴向力为：
Figure PCTCN2018112312-appb-000020
由此可见，该混合偏置磁悬浮轴承可以提供较大的永磁偏置的轴向力，抵消磁悬浮离心压缩机中气动组件(如叶轮、扩压器等)对转子的轴向力，减小转子运行轴向载荷。另可以提供一部分永磁偏置的径向力和可控制的电磁径向力，该种实施方式径向方向有2个气隙(X1和X3’)提供径向偏置力，从而可以进一步降低运行时径向控制线圈电流。从而在进一步减小轴向、径向电流的同时还能提供可控制的径向力，起到主动悬浮的效果。
本发明还提供一种磁悬浮转子支承组件，其包括转子和前任一项所述的磁悬浮轴承，所述磁悬浮轴承能够对所述转子进行支承。
通过包括前述的磁悬浮轴承，能够产生对推力盘沿转子径向方向的可控可调节的径向电磁力、能够使得轴承的柔性能够设计得更大，轴承的应用范围得到有效提高，区别于原有技术的轴向受力调节，该轴承径向受力可以调节，因此该磁悬浮轴承可应用到更多的卧式透平机械上，扩大该类轴承应用范围；
由于一般的离心式压缩机，在压缩机运行和停机时都会有一个向后的较大轴向力，为削弱甚至抵消该作用力对转子稳定性不良影响，本发明通过设置转子挡环和与之相匹配的后定子铁芯，能够取消掉原有的对推力盘产生的轴向力、改为对转子挡环产生径向力、再转换为作用于转子上的径向力，将气隙X3的轴向力作用取消，使得前定子铁芯产生的轴向力能够被用于抵消该压缩机的轴向力，改为由X3’气隙提供的径向力，应用到离心压缩机中，进一步的缩减磁悬浮轴承工作电流，降低损耗，减小压缩机运营成本，提高产品竞争力。
优选地，
所述转子包括光轴1和固定连接于所述光轴1径向外侧的推力盘2，所述磁悬浮轴承与所述推力盘2之间能够产生轴向和/或径向的磁力而支承所述转子。这是本发明的转子的优选结构形式，通过本发明的磁悬浮轴承与推力盘之间的相互作用，从而产生对推力盘轴向和/或径向方向的磁力作用，形成磁悬浮，尤其是对推力盘的径向方向产生可调节的电磁力，使得转子径向方向可以得以 调控，扩大了轴承的应用范围，应用于更多的离心压缩机(卧式透平机械上)上。
本发明还提供一种压缩机，其包括前任一项所述的磁悬浮转子支承组件。优选为离心压缩机。通过包括前述的磁悬浮转子支承组件，能够产生对推力盘沿转子径向方向的可控可调节的径向电磁力、能够使得轴承的柔性能够设计得更大，轴承的应用范围得到有效提高，区别于原有技术的轴向受力调节，该轴承径向受力可以调节，因此该磁悬浮轴承可应用到更多的卧式透平机械上，扩大该类轴承应用范围；
本发明通过设置转子挡环和与之相匹配的后定子铁芯，能够取消掉原有的对推力盘产生的轴向力、改为对转子挡环产生径向力、再转换为作用于转子上的径向力，将气隙X3的轴向力作用取消，使得前定子铁芯产生的轴向力能够被用于抵消该压缩机的轴向力，改为由X3’气隙提供的径向力，应用到离心压缩机中，进一步的缩减磁悬浮轴承工作电流，降低损耗，减小压缩机运营成本，提高产品竞争力。
以上所述仅为本发明的较佳实施例而已，并不用以限制本发明，凡在本发明的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本发明的保护范围之内。以上所述仅是本发明的优选实施方式，应当指出，对于本技术领域的普通技术人员来说，在不脱离本发明技术原理的前提下，还可以做出若干改进和变型，这些改进和变型也应视为本发明的保护范围。

Claims (14)

  1. 一种磁悬浮轴承，用于通过与转子上的推力盘相作用而支承所述转子，其特征在于：包括：
    径向定子铁芯(5)，为环状结构、设置在所述推力盘(2)的径向外侧、且在转子轴向上与所述推力盘(2)相对应，所述径向定子铁芯(5)与所述推力盘(2)之间相隔第一径向间隙X1，
    径向控制线圈(4)，设置在所述径向定子铁芯(5)上、且能沿转子径向方向产生对所述推力盘(2)的径向电磁力。
  2. 根据权利要求1所述的磁悬浮轴承，其特征在于：
    还包括两个以上的通槽(9)，设置在所述径向定子铁芯(5)上、位于径向定子铁芯径向内侧和径向外侧之间的位置，且所述通槽(9)沿轴向方向贯通所述径向定子铁芯(5)，两个相邻所述通槽(9)形成一个通槽对、且在一个所述通槽对中的两个所述通槽(9)之间形成能够供所述径向控制线圈(4)缠绕的磁极(10)。
  3. 根据权利要求2所述的磁悬浮轴承，其特征在于：
    在一个所述通槽对中、两个相邻的所述通槽(9)沿所述径向定子铁芯(5)的周向进行排布，使得所述磁极(10)的长度方向朝着所述径向定子铁芯(5)的径向方向延伸；所述径向控制线圈(4)围绕所述磁极(10)缠绕、使得所述径向控制线圈(4)的围绕轴线沿着所述径向定子铁芯(5)的径向方向。
  4. 根据权利要求2所述的磁悬浮轴承，其特征在于：
    所述磁极(10)为多个、多个所述磁极(10)沿所述径向定子铁芯(5)的周向方向均匀分布，且在每个磁极(10)上均缠绕一个所述径向控制线圈(4)。
  5. 根据权利要求4所述的磁悬浮轴承，其特征在于：
    所述磁极(10)为4个、且相邻两磁极(10)之间在径向定子铁芯(5)的周向上相隔90°的圆周角。
  6. 根据权利要求1-5中任一项所述的磁悬浮轴承，其特征在于：
    还包括永磁体(6)，所述永磁体(6)设置在所述径向定子铁芯(5)的径向外侧、且与所述径向定子铁芯(5)在轴向方向上的位置相对应，
    还包括第二定子铁芯，能够从永磁体(6)的径向外侧延伸至靠近所述推 力盘(2)的位置，以对所述推力盘(2)产生沿转子轴向和/或沿转子径向的永磁力。
  7. 根据权利要求6所述的磁悬浮轴承，其特征在于：
    所述第二定子铁芯包括前定子铁芯(3)：
    所述前定子铁芯(3)包括第一轴向延伸部(31)、第一径向延伸部(32)和第二轴向延伸部(33)；
    所述第一轴向延伸部(31)的一端位于所述永磁体(6)的径向外侧、另一端沿转子轴向方向进行延伸，
    所述第一径向延伸部(32)的一端与所述第一轴向延伸部(31)的另一端相接、所述第一径向延伸部(32)的另一端沿着转子径向方向延伸，
    所述第二轴向延伸部(33)的一端与所述第一径向延伸部(32)的另一端相接、所述第二轴向延伸部(33)的另一端沿转子轴向方向向着靠近所述推力盘(2)的位置延伸，且所述第二轴向延伸部(33)的另一端与所述推力盘(2)之间在转子轴向方向相隔第一轴向间隙X2。
  8. 根据权利要求6-7中任一项所述的磁悬浮轴承，其特征在于：
    所述第二定子铁芯包括后定子铁芯(7)：
    所述后定子铁芯(7)包括第三轴向延伸部(71)、第二径向延伸部(72)和第四轴向延伸部(73)，
    所述第三轴向延伸部(71)的一端位于所述永磁体(6)的径向外侧、另一端沿转子轴向方向进行延伸，
    所述第二径向延伸部(72)的一端与所述第三轴向延伸部(71)的另一端相接、所述第二径向延伸部(72)的另一端沿着转子径向方向延伸，
    所述第四轴向延伸部(73)的一端与所述第二径向延伸部(72)的另一端相接、所述第四轴向延伸部(73)的另一端沿转子轴向方向延伸至靠近所述推力盘(2)的位置，且所述第四轴向延伸部的另一端与所述推力盘(2)之间在轴向方向相隔第二轴向间隙X3。
  9. 根据权利要求6-7中任一项所述的磁悬浮轴承，其特征在于：
    所述第二定子铁芯包括后定子铁芯(7)：
    所述后定子铁芯(7)包括第三轴向延伸部(71)和第二径向延伸部(72)，
    所述第三轴向延伸部(71)的一端位于所述永磁体(6)的径向外侧、另 一端沿转子轴向方向进行延伸，
    所述第二径向延伸部(72)的一端与所述第三轴向延伸部(71)的另一端相接、所述第二径向延伸部(72)的另一端沿着转子径向方向延伸，
    还包括设置于所述推力盘(2)轴向一侧、靠近所述第二径向延伸部(72)位置的转子挡环(8)，所述转子挡环(8)与所述转子固定连接；
    所述第二径向延伸部(72)的另一端沿转子径向方向延伸向着靠近所述转子挡环(8)的位置延伸，且所述第二径向延伸部(72)的另一端与所述转子挡环(8)之间在径向方向相隔第二径向间隙X3’。
  10. 根据权利要求8-9中任一项所述的磁悬浮轴承，其特征在于：
    当同时包括前定子铁芯(3)和后定子铁芯(7)时，所述前定子铁芯(3)与所述后定子铁芯(7)在所述永磁体(6)的径向外侧的位置相接、以使得磁场在相接位置能够连续导通。
  11. 根据权利要求10所述的磁悬浮轴承，其特征在于：
    所述相接位置位于所述永磁体(6)的径向外侧、且在转子轴向方向上与所述永磁体(6)的一轴向端面相对。
  12. 一种磁悬浮转子支承组件，其特征在于：
    包括转子和权利要求1-11中任一项所述的磁悬浮轴承，所述磁悬浮轴承能够对所述转子进行支承。
  13. 根据权利要求12所述的磁悬浮转子支承组件，其特征在于：
    所述转子包括光轴(1)和固定连接于所述光轴(1)径向外侧的推力盘(2)，所述磁悬浮轴承与所述推力盘(2)之间能够产生轴向和/或径向的磁力而支承所述转子。
  14. 一种压缩机，其特征在于：包括权利要求12-13中任一项所述的磁悬浮转子支承组件。
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US20200235635A1 (en) 2020-07-23
CN108087321B (zh) 2023-11-21
US11323007B2 (en) 2022-05-03

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