US20130343927A1 - Electric centrifugal compressor for vehicles - Google Patents

Electric centrifugal compressor for vehicles Download PDF

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Publication number
US20130343927A1
US20130343927A1 US13/925,390 US201313925390A US2013343927A1 US 20130343927 A1 US20130343927 A1 US 20130343927A1 US 201313925390 A US201313925390 A US 201313925390A US 2013343927 A1 US2013343927 A1 US 2013343927A1
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US
United States
Prior art keywords
axial
electric compressor
motor
shaft
compressor according
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.)
Abandoned
Application number
US13/925,390
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English (en)
Inventor
Lateb Ramdane
Joaquim Da Silva
Eric Helene
Frederic Ponson
Ulrich Schroeder
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.)
Societe de Mecanique Magnetique SA
SKF AB
Original Assignee
SKF AB
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 SKF AB filed Critical SKF AB
Assigned to SOCIETE DE MECANIQUE MAGNETIQUE reassignment SOCIETE DE MECANIQUE MAGNETIQUE ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SCHROEDER, ULRICH, DA SILVA, JOAQUIM, HELENE, ERIC, PONSON, FREDERIC, RAMDANE, LATEB
Publication of US20130343927A1 publication Critical patent/US20130343927A1/en
Abandoned 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
    • 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
    • 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
    • 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
    • F16C32/0493—Active magnetic bearings for rotary movement integrated in an electrodynamic machine, e.g. self-bearing motor
    • F16C32/0495—Active magnetic bearings for rotary movement integrated in an electrodynamic machine, e.g. self-bearing motor generating torque and axial force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C32/0493—Active magnetic bearings for rotary movement integrated in an electrodynamic machine, e.g. self-bearing motor
    • F16C32/0497—Active magnetic bearings for rotary movement integrated in an electrodynamic machine, e.g. self-bearing motor generating torque and radial force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • 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
    • H02K7/083—Structural association with bearings radially supporting the rotary shaft at both ends of the rotor
    • 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
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans

Definitions

  • the present invention relates to a compact electric centrifugal compressor which is more specifically but not exclusively adapted to be used in a Heat Ventilation Air Conditioning (HVAC) installation for vehicles.
  • HVAC Heat Ventilation Air Conditioning
  • the vehicles may include in particular terrestrial vehicles such as hybrid electric vehicles (HEV) or electric vehicles (EV) as well as aircrafts or other kinds of vehicles.
  • terrestrial vehicles such as hybrid electric vehicles (HEV) or electric vehicles (EV) as well as aircrafts or other kinds of vehicles.
  • HEV hybrid electric vehicles
  • EV electric vehicles
  • HVAC electric compressors Two main categories of HVAC electric compressors are used in HEV/EV vehicles: rotary like vane compressors and oscillating like scroll type compressors.
  • Lubricants are needed for different mechanical parts
  • Lubricants should be carefully chosen to protect the electric motor windings from the risk of insulation failure, An oil separator and leak detection devices are required to avoid contamination of the electric systems in EV/HEV vehicles,
  • the conventional electric compressors have a speed which is limited and cannot exceed 10,000 rpm. Friction losses are detrimental to the operation of the electric compressor.
  • the invention is intended more especially, although not exclusively, to automotive air conditioning applications and therefore further aims at providing an electric compressor which takes into account the high level of vibrations generated in a vehicle and which is as compact as possible.
  • a compact electric compressor comprising a motor portion and a centrifugal compressor portion driven by the motor portion through a shaft
  • the motor portion comprises first and second radial bearingless motors spaced apart along the shaft and configured for rotating the shaft and maintaining it in a defined radial position in a contactless manner during functional operation of the electric compressor and axial electromagnetic means located between the first and second radial bearingless motors and configured for maintaining the shaft in a defined axial position during functional operation of the electric compressor and wherein auxiliary landing bearing are located at each end of the shaft in the vicinity of each of the first and second radial bearingless motors.
  • the axial electromagnetic means comprise an axial bearingless motor.
  • the axial electromagnetic means comprise an active axial magnetic bearing.
  • Separators may be provided between the radial bearingless motors and the axial electromagnetic means.
  • the radial bearingless motors each comprise a rotor portion having a plurality of pole pairs armatures and a stator portion comprising a core with slots for receiving windings configured to impress a motor torque and a radial bearing force.
  • Separate windings may be provided in the slots of the stator portion for impressing a motor torque and an axial bearing force.
  • common windings may be provided in the slots of the stator portion for impressing a motor torque and an axial bearing force.
  • the radial bearingless motors comprise a rotor portion chosen among an induction rotor, a permanent magnet rotor, a hysteresis rotor and a reluctance rotor.
  • the centrifugal compressor portion comprises a wheel at a first end of the shaft and control circuits associated with the radial bearingless motors and the axial electromagnetic means are located at a second end of the shaft and are connected to the radial bearingless motors and the axial electromagnetic means via a feedthrough.
  • the centrifugal compressor portion may comprise a variety of configurations and in particular may comprise a single wheel, double wheels, tandem wheels or double tandem wheels.
  • the axial bearingless motor may comprise a rotor portion having a plurality of pole pairs armatures and first and second stator portions each comprising a core with slots respectively for receiving windings configured to impress a motor torque and an axial bearing force, the first and second stator portions being located on each side of the rotor portion.
  • the active axial magnetic bearing may comprise a disc armature integral with the shaft and first and second stator electromagnets facing the disc armature in a contactless manner on each side of the latter.
  • FIG. 1 is a schematic longitudinal sectional view of an electric compressor comprising a compressor portion and a motor portion comprising an electric motor, two radial magnetic bearings and a magnetic thrust bearing and further schematically showing a control device;
  • FIG. 2 is another schematic longitudinal sectional view of an electric compressor comprising a compressor portion and a motor portion comprising an electric motor, two radial magnetic bearings and a magnetic thrust bearing;
  • FIG. 3 is another schematic longitudinal sectional view of an electric compressor comprising a compressor portion and a motor portion comprising an electric motor, two radial magnetic bearings and a magnetic thrust bearing which is divided into two parts;
  • FIG. 4 is a schematic longitudinal sectional view of an electric compressor comprising a compressor portion (not shown) and a motor portion comprising two radial bearingless motors and an active axial magnetic bearing or an axial bearingless motor;
  • FIG. 5 is a perspective view of an axial bearingless motor (the winding being not represented);
  • FIG. 6 is a perspective view of a radial bearingless motor (the winding being not represented);
  • FIG. 7 is a schematic view of an example of compressor portion comprising double wheels
  • FIG. 8 is a schematic view of an example of compressor portion comprising tandem wheels.
  • FIG. 9 is a schematic view of an example of compressor portion comprising double tandem wheels.
  • FIG. 2 shows an example of a centrifugal electric compressor for heat ventilation air conditioning (HVAC) which may be dedicated for hybrid electric vehicles (HEV) or electric vehicles (EV) or else for aircrafts or other types of vehicles.
  • HVAC heat ventilation air conditioning
  • HEV hybrid electric vehicles
  • EV electric vehicles
  • FIG. 2 shows an example of a centrifugal electric compressor for heat ventilation air conditioning (HVAC) which may be dedicated for hybrid electric vehicles (HEV) or electric vehicles (EV) or else for aircrafts or other types of vehicles.
  • HVAC heat ventilation air conditioning
  • a rotor shaft 15 of a motor portion 20 is coupled to a centrifugal compressor wheel 11 of a compressor portion 10 to drive the centrifugal compressor wheel 11 .
  • An electrical motor 30 comprises a rotor 31 which may be of any type chosen among induction rotor, permanent magnet rotor, hysteresis rotor and reluctance rotor.
  • the electrical motor 30 further comprises a stator 32 with windings 32 a.
  • First and second active radial magnetic bearings 40 , 50 are located on each side of the electrical motor 30 to support the shaft 15 in levitation during functional operation of the electric compressor.
  • Each active radial magnetic bearing 40 , 50 comprises a rotor 41 , 51 fast with the shaft 15 and a stator 42 , 52 with windings 42 a , 52 a.
  • An active axial magnetic bearing 60 (thrust bearing) comprises on the one hand a disc 61 which is mounted perpendicular to the axis of the shaft 15 and constitutes a rotor armature and on the other hand first and second stators 62 , 63 each having at least one annular coil or winding 62 a , 63 a located in a stator 62 , 63 which may have a C-shaped core, as shown in FIG. 2 .
  • each stator 62 , 63 could have an E-shaped core with two coils.
  • the radial bearing rotors 41 , 51 are equipped with ferromagnetic laminations which are held in position by the magnetic fields created by the electromagnets of the stators 42 , 52 .
  • the shaft 15 is levitated in a contactless manner due to the radial magnetic bearings.
  • the shaft's position is monitored by sensors (not shown), e.g. of the variable inductive type, which detect any deviation from nominal position and emit signals which are used in a control system (not shown in FIG. 2 ) to command currents in the windings 42 a , 52 a of the radial bearings in order to bring the shaft 15 back to its nominal position.
  • the axial bearing 60 is based on the same principle and sensors (not shown) send signals to a controller to adjust command currents in the coils 62 a , 63 a of the axial bearing 60 to adjust the axial position of the shaft 15 .
  • Auxiliary landing bearings 8 are used for supporting the shaft 15 essentially during a starting or stopping operation of the motor portion 20 , but also during brief intermittent periods in case of shock-loads due to the usually high level of vibrations present in a vehicle.
  • auxiliary bearings also known as emergency bearings, are provided in order to support the shaft while the machine is being stopped or in the event of a total or partial failure of the magnetic suspension, thereby preventing direct contact between the magnetic circuits of the rotors and the stators of the magnetic bearings or bearingless motors when the windings of the stator electromagnets are not properly powered, thus avoiding damage to the laminations thereof.
  • auxiliary bearings leave clearance about the rotary shaft and do not themselves, rotate.
  • the clearance provided for the auxiliary bearings is generally about one half the width of the air gap of the magnetic bearings or bearingless motors.
  • the auxiliary landing/touch down bearings 8 may have a variety of designs and may be for example rolling bearings, needle bearings, plain bearings, bushings, etc. . . .
  • Separators 9 may be located between the stator windings of the magnetic bearings 40 , 50 , 60 and of the electrical motor 30 .
  • the axial bearing 60 comprises a disc armature 61 and two stators 62 , 63 located at an end of the shaft 15 , whereas the compressor wheel is located at the other end of the shaft.
  • the axial bearing 60 can also be located on the same side than the compressor wheel 11 .
  • control circuits 70 comprising a variable frequency drive 71 and amplifiers 72 associated with the electrical motor 30 and the radial electromagnetic bearings 40 , 50 , 60 are integrated in a flange and located at a second end of the iron shaft 15 .
  • the control circuits 70 are connected to the electrical motor 30 and to the radial and axial electromagnetic bearings via a feedthrough 74 .
  • a connector 73 serves to connect the control circuits 70 to a further controller located remote from the electric compressor.
  • FIG. 3 shows an embodiment which is similar to the embodiment of FIG. 2 , but the axial magnetic bearing is split into two parts 60 A, 60 B which are located at both ends of the shaft 15 .
  • a disc armature 61 A integral with the shaft 15 is located at a first end of the shaft 15 near the compressor wheel 11 and cooperates with a first stator 62 having a first coil 62 a which could be similar to the stator 62 of FIG. 1 .
  • a disc armature 61 B integral with the shaft 15 is located at a second end of the shaft 15 and cooperates with a second stator 63 having a second coil 63 a which could be similar to the stator 63 of FIG. 2 .
  • FIGS. 1 to 3 show a compressor portion 10 having a single wheel. However other designs of the compressor portion 10 may be used in combination with the different embodiments disclosed herein.
  • a compressor portion 10 may include double wheels 11 , 13 .
  • a compressor portion 10 A, 10 B may include tandem wheels 11 , 12 .
  • a compressor portion 10 A, 10 B may include double tandem wheels 11 , 13 , 12 , 14 .
  • the configurations of compressor wheels according to FIGS. 7 to 9 are intended either to increase the pressure ratio or to increase the flow.
  • FIG. 4 shows an embodiment with an iron shaft 15 and a motor portion 20 which are more compact than the embodiments of FIGS. 1 to 3 since the electrical motor 30 and the radial magnetic bearings 40 , 50 are replaced by first and second radial bearingless motors 140 , 150 .
  • the compressor portion 10 has been omitted but may be realized as previously described with reference to FIGS. 1 to 3 and 7 to 9 .
  • FIG. 4 allows reducing the shaft length and hence improves the overall layout.
  • the radial bearingless motors 140 , 150 each comprise a disc-like central armature 141 , 151 integral with the shaft 15 and a stator 142 , 152 with windings 142 a , 152 a.
  • FIG. 6 An example of radial bearingless motor 180 is represented in FIG. 6 .
  • Such radial bearingless motor 180 comprises a rotor 181 integral with the shaft 15 and a stator 182 with slots 184 for receiving coils 185 .
  • the rotor 181 carries different structural elements 183 depending on the chosen principle (permanent magnet, induction, switched reluctance, hysteresis).
  • stator windings 185 achieve both functions of torque windings and suspension force windings.
  • torque windings As an example if two magnetic fields, which may be created by two winding sets with a difference in the pole pair number of one, are superposed, a torque and a radial force will be produced. It is thus possible for example to combine a 4-pole motor winding of a reluctance motor with a 2-pole bearing winding, but many other embodiments are possible.
  • U.S. Pat. No. 6,727,618 B1 discloses an example of bearingless switched reluctance motor.
  • stator portions 142 , 152 , 182 of the radial bearingless motors 140 , 150 , 180 separated coils may be used to impress the bearing force and the motor torque.
  • the needed bearing force and motor torque may be generated in each coil by combined windings.
  • a single coil will carry jointly the required motor and bearing ampere-turns.
  • reference numeral 130 may designate an axial bearingless motor as well as an axial active magnetic bearing.
  • the disc armature 131 and the stator portions 132 , 133 with windings 132 a and 133 a respectively may be constituted like the thrust bearing 60 illustrated in FIG. 2 , i.e. the windings 132 a , 133 a would be constituted by annular coils centered on the axis of the shaft 15 .
  • the axial magnetic bearing 130 could also comprise stator portions 132 , 133 having a C-shape with a single annular coil 132 a , 133 a as shown in FIG. 4 or having an E-shape with two concentric annular coils.
  • FIG. 4 comprises first and second radial bearingless motors 140 , 150 and a central axial bearingless motor located between the first and second radial bearingless motors 140 , 150 .
  • the axial bearingless motor 130 also comprises a disc armature 131 integral with the shaft 15 and first and second stator portions 132 , 133 located on each side of the disc armature 131 , but the windings 132 a and 133 a are differently arranged.
  • FIG. 5 shows in perspective an example of a possible configuration of an axial bearingless motor 130 .
  • the axial bearingless motor 130 of FIG. 5 comprises a rotor portion 131 having a plurality of pole pairs armatures 138 and first and second stator portions 132 , 133 each comprising a core with slots 134 , 135 respectively for receiving windings (not shown in FIG. 5 ) configured to impress a motor torque and an axial bearing force, the first and second stator portions 132 , 133 being located on each side of the rotor portion 131 .
  • stator portions 132 , 133 of the axial bearingless motor separated coils may be used to impress the bearing force and the motor torque.
  • the needed bearing force and motor torque may be generated in each coil by combined windings.
  • a single coil will carry jointly the required motor and bearing ampere-turns.
  • a plurality of pole pairs armatures 138 are shown in FIG. 5 by way of example.
  • the rotor 131 may carry different structural elements depending on the chosen principle (permanent magnet, induction, switched reluctance, hysteresis).
  • the stator 132 and the rotor 131 with permanent magnets 138 may constitute a permanent magnet motor, where the permanent magnets 138 on the rotor surface produce an axial force in a first direction (upward direction in the configuration of FIG. 5 ), whereas the stator 133 and rotor 131 may constitute a synchronous reluctance motor, where the winding currents of the synchronous reluctance motor produce an adjustable axial force in the opposite direction with respect to the first direction (downward direction in the configuration of FIG. 5 ).
  • the axial position of the rotor can thus be controlled by the currents of the synchronous motor.
  • other combinations of motor types may be chosen as soon as the axial bearingless motor 130 achieves the two functions of impressing a motor torque and an axial bearing force.
  • Active radial magnetic bearings 140 and 150 similar to previously described active radial magnetic bearings 40 and 50 and comprising a rotor armature 141 , 151 and a stator 142 , 152 with windings 142 a , 152 a may be located on each side of an axial bearingless motor 130 .
  • first and second radial bearingless motors 140 , 150 are preferably used in combination with an axial bearingless motor 130 or a thrust magnetic bearing.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Power Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
US13/925,390 2012-06-22 2013-06-24 Electric centrifugal compressor for vehicles Abandoned US20130343927A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP12305730 2012-06-22
EP12305730.9A EP2677177B1 (en) 2012-06-22 2012-06-22 Electric centrifugal compressor for vehicles

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US13/925,390 Abandoned US20130343927A1 (en) 2012-06-22 2013-06-24 Electric centrifugal compressor for vehicles

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US (2) US20140023534A1 (zh)
EP (1) EP2677177B1 (zh)
JP (1) JP6193007B2 (zh)
CN (1) CN103821735A (zh)
CA (1) CA2820449A1 (zh)

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US11971045B2 (en) 2017-05-09 2024-04-30 Daikin Industries, Ltd. Turbo compressor
US12012965B2 (en) 2022-08-22 2024-06-18 White Knight Fluid Handling Inc. Pump having opposing magnets between a rotor and stator, and related assemblies, systems, and methods

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CA2820449A1 (en) 2013-12-22
JP6193007B2 (ja) 2017-09-06
CN103821735A (zh) 2014-05-28

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