[go: up one dir, main page]

WO2008032430A1 - Dispositif à coussinet magnétique intégré à un moteur - Google Patents

Dispositif à coussinet magnétique intégré à un moteur Download PDF

Info

Publication number
WO2008032430A1
WO2008032430A1 PCT/JP2007/000898 JP2007000898W WO2008032430A1 WO 2008032430 A1 WO2008032430 A1 WO 2008032430A1 JP 2007000898 W JP2007000898 W JP 2007000898W WO 2008032430 A1 WO2008032430 A1 WO 2008032430A1
Authority
WO
WIPO (PCT)
Prior art keywords
motor
cooling
magnetic bearing
coil
air
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/JP2007/000898
Other languages
English (en)
Japanese (ja)
Inventor
Takayoshi Ozaki
Hiroyuki Yamada
Kenichi Suzuki
Nobuyuki Suzuki
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.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
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
Priority claimed from JP2006247882A external-priority patent/JP2008072812A/ja
Priority claimed from JP2006247879A external-priority patent/JP2008072809A/ja
Priority claimed from JP2006247881A external-priority patent/JP2008072811A/ja
Priority claimed from JP2006247880A external-priority patent/JP2008072810A/ja
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of WO2008032430A1 publication Critical patent/WO2008032430A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
    • F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/36—Power transmission arrangements between the different shafts of the gas turbine plant, or between the gas-turbine plant and the power user
    • 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
    • F04D29/059—Roller 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
    • F16C37/00—Cooling of bearings
    • F16C37/005—Cooling of bearings of 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
    • F16C39/00—Relieving load on bearings
    • F16C39/06—Relieving load on bearings using magnetic means
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K21/00—Synchronous motors having permanent magnets; Synchronous generators having permanent magnets
    • H02K21/12—Synchronous motors having permanent magnets; Synchronous generators having permanent magnets with stationary armatures and rotating magnets
    • H02K21/24—Synchronous motors having permanent magnets; Synchronous generators having permanent magnets with stationary armatures and rotating magnets with magnets axially facing the armatures, e.g. hub-type cycle dynamos
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K29/00—Motors or generators having non-mechanical commutating devices, e.g. discharge tubes or semiconductor devices
    • H02K29/06—Motors or generators having non-mechanical commutating devices, e.g. discharge tubes or semiconductor devices with position sensing devices
    • H02K29/08—Motors or generators having non-mechanical commutating devices, e.g. discharge tubes or semiconductor devices with position sensing devices using magnetic effect devices, e.g. Hall-plates, magneto-resistors
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K3/00—Details of windings
    • H02K3/04—Windings characterised by the conductor shape, form or construction, e.g. with bar conductors
    • H02K3/24—Windings characterised by the conductor shape, form or construction, e.g. with bar conductors with channels or ducts for cooling medium between the conductors
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K3/00—Details of windings
    • H02K3/46—Fastening of windings on the stator or rotor structure
    • H02K3/47—Air-gap windings, i.e. iron-free windings
    • 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
    • F16C2362/00—Apparatus for lighting or heating
    • F16C2362/52—Compressors of refrigerators, e.g. air-conditioners
    • 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

Definitions

  • the present invention relates to a magnetic bearing device used for an air cycle refrigeration cooling turbine unit or the like, and in particular, a rolling bearing and a magnetic bearing are used in combination, and the magnetic bearing performs either one or both of an axial load and a bearing preload.
  • the present invention relates to a motor-type magnetic bearing device that is supported.
  • the air cycle refrigeration cooling system uses air as a refrigerant, and thus is less energy efficient than using chlorofluorocarbon, ammonia gas, or the like, but is preferable in terms of environmental protection. Also, in facilities that can directly inject refrigerant air, such as refrigerated warehouses, there is a possibility that the total cost may be reduced due to omission of internal fans and defrosters, etc.
  • An air cycle refrigeration cooling system as shown in Japanese Patent No. 2 6 2 3 2 0 2 has been proposed.
  • a turbine unit in which a compressor wheel and an expansion turbine wheel are attached to a common main shaft is used as a compressor and an expansion turbine. This turbine unit improves the efficiency of the air cycle refrigerator by driving the compressor wheel with the power generated by the expansion turbine.
  • JP-A-7_9 1 7 60 a turbine compressor for process gas processing, not for refrigeration and cooling, has a turbine impeller at one end of a main shaft and a compressor impeller at the other end.
  • magnetic bearing type turbine compressors that are mounted and supported by journals and thrust bearings in which the main shaft is controlled by electromagnet current.
  • Tokuhei Hei 8 _ 2 6 1 2 3 7 discloses that a thrust load acting on a rolling bearing for supporting a main shaft does not lead to shortening of the bearing life. It has been proposed to reduce the thrust load acting on the rolling bearing with a thrust magnetic bearing.
  • This motor-type magnetic bearing device is used in an air cycle refrigeration cooling turbine unit in which a compressor impeller 4 6a of a compressor 4 6 and a turbine impeller 4 7a of an expansion turbine 4 7 are attached to both ends of a main shaft 53.
  • the radial load of the main shaft 5 3 is supported by the rolling bearings 5 5 and 5 6, and the axial load is supported by the electromagnet 5 7, and the driving force by the motor 6 8 provided coaxially with the main shaft 5 3 and the turbine impeller 4 7 a
  • the compressor impeller 4 6a is driven to rotate with the driving force of.
  • the electromagnet 5 7 that supports the axial load is arranged so as to face the thrust plate 5 3 a that is perpendicular and coaxial with the main shaft 53 without contact, and outputs the sensor 5 8 that detects the axial force.
  • the motor 68 is of an axial gap type, and a motor rotor 6 8 a is formed on another thrust plate 53 b provided perpendicularly to the main shaft 53 and on the same axis, and the motor rotor 68 is formed in the axial direction.
  • the motor stators 6 8 b are arranged so as to face each other.
  • the thruster applied to the main shaft 53 is supported by the electromagnet 57.
  • the acting thrust force can be reduced.
  • the small gaps between the impellers 4 6 a and 4 7 a and the housings 4 6 b and 4 7 b are unified.
  • the long-term durability of the rolling bearings 5 5 and 5 6 against the thrust load can be improved.
  • the thrust plate 5 3 a for the electromagnet 5 7 and the thrust plate 5 3 b for the motor 6 8 are provided separately on the main shaft 53, the shaft length of the main shaft 53 is longer. There is a problem that the compactness of the entire device is insufficient, and the natural frequency is lowered, making high-speed rotation difficult.
  • the present invention can improve the long-term durability of a rolling bearing against a thrust load, can cope with compaction and high-speed rotation, and can provide a sufficient motor cooling effect.
  • the object is to provide a bearing device.
  • a motor-type magnetic bearing device of the present invention uses a rolling bearing and a magnetic bearing in combination, the rolling bearing supports a radial load, the magnetic bearing supports one or both of an axial load and a bearing preload,
  • the electromagnet constituting the magnetic bearing is attached to the spindle housing so as to face the flange-shaped thrust plate made of a ferromagnetic material provided on the main shaft in a non-contact manner, and the motor rotor of the axial gear motor is connected to the thrust gear.
  • a motor stator having a motor coil is installed in the spindle housing, and a cooling passage is provided in the motor to cool the motor by supplying a cooling medium.
  • the rolling bearing supports the radial load, and the magnetic bearing supports one or both of the axial load and the bearing preload. It can be supported with high accuracy and long-term durability of the rolling bearing can be secured, and damage when the power supply is stopped in the case of supporting only the magnetic bearing can be avoided.
  • the permanent magnet of the motor rotor is provided on the thrust plate facing the electromagnet of the magnetic bearing, the spindle length is shortened by the combined use of the thrust plate of the magnetic bearing and the motor port, resulting in compactness and natural vibration. The decrease in the number can be avoided, and low-vibration rotation during high-speed rotation is possible.
  • the motor is an axial gap type and generates a large amount of heat at the motor stage, so that it cannot be cooled sufficiently by indirect cooling from the outside of the motor case, as is done with ordinary motors.
  • the motor is directly cooled by the cooling medium supplied in the motor, an excellent cooling effect can be obtained. As a result, a decrease in motor efficiency and a deterioration in safety due to insufficient cooling can be avoided.
  • the cooling medium is a cooling liquid, and it is preferable to provide the cooling passage through which the cooling liquid flows into the motor stator so that the cooling liquid contacts the winding of the motor coil. According to this configuration, the necessary motor cooling effect can be obtained with a simple configuration in which only a cooling passage for flowing the cooling liquid into the motor stator is provided.
  • the motor stage includes a motor coil accommodated in a case made of a polymer material, the cooling passage is provided in the case, and the cooling passage is provided in the motor coil. It may have a coolant passage groove that faces and opens. According to this configuration, an excellent cooling effect can be obtained because the cooling passage for flowing the coolant into the motor stator is provided so that the coolant contacts the windings of the motor coil.
  • the circulation path is a cold opening facing the motor coil. Since it has a reject liquid passage groove and the path cross section is made smaller, the same amount of coolant flows and the coolant flows at a high speed, further improving the cooling efficiency.
  • the motor case is made of a polymer material, it is easy to form a cooling passage such as a coolant passage groove, and because it is non-magnetic, it does not affect the magnetic field.
  • the cooling passage is provided in the case and is supplied with an inlet through which coolant is supplied from the outside of the case, and an in-case cooling path provided in the case that communicates with the inlet.
  • One or a plurality of discharge ports provided in the cooling path in the case may be provided.
  • a sensor for detecting the passage of the permanent magnet of the motor rotor may be arranged outside the case in order to take a timing for switching the current to the motor coil.
  • the sensor is necessary for controlling the motor, but if this sensor comes into contact with the coolant, there is a risk of deterioration or short-circuiting.
  • by disposing the sensor outside the case it is possible to avoid the coolant from touching the sensor.
  • a plurality of the motor coils may be arranged in a common case on the same circumference, and a plurality of the cooling liquid passage grooves may be provided so as to face the end surfaces of the coils.
  • a plurality of cooling liquid passage grooves are provided facing the end face of each coil, the cooling liquid flows at a high speed into each cooling liquid passage groove, so that the cooling effect on the motor coil can be further enhanced.
  • the motor coil is a coreless coil having a hollow inside
  • the motor stator is provided with a cooling passage for flowing a coolant into the hollow portion of the motor coil. May be.
  • the cooling passage for flowing the coolant in the hollow portion of the motor coil is provided, a sufficient cooling effect can be obtained. This reduces motor efficiency and safety due to insufficient cooling. Can be avoided.
  • the cooling passage can be made compact, and the motor stator can be prevented from being enlarged due to the formation of the cooling passage. If the coolant flows directly in contact with the coil winding in the hollow portion of the motor coil, the cooling effect is further improved.
  • the motor coil is divided into a plurality of coil divided bodies arranged in the axial direction, and a hollow portion that allows coolant to flow into the hollow portion of the coil from the outer periphery of the coil between the coil divided bodies
  • An inflow path may be provided.
  • a compressor side impeller is attached to the main shaft on the main shaft, and either one or both of motor power and dynamic force generated by the turbine side impeller are used. It may be applied to a compression / expansion turbine system for driving the compressor. In this configuration, a stable high-speed rotation of the main shaft can be obtained while maintaining an appropriate clearance between the impellers, and long-term durability and life of the bearing can be improved.
  • the cooling medium is air
  • the cooling passage is supplied to the motor section cooling air introduction path for supplying cooling air into the motor from the outside, and is supplied. It may have a discharge path for exhausting the air outside the motor.
  • the necessary motor cooling can be performed with a simple configuration in which a cooling air introduction path and a discharge path are provided.
  • the motor part cooling air introduction path may introduce a part of the air flowing into the turbine blade or the air discharged from the turbine blade into the motor.
  • the air that flows into or out of the turbine blades is used, so cooling air can be forcibly circulated without the need for a dedicated air supply source such as fans. Good motor cooling.
  • the motor part cooling air introduction path is a path for supplying air to the inner diameter part of the motor rotor, and the discharge path is exhausted from the outer diameter part of the motor rotor.
  • a route is preferred.
  • the motor rotor becomes large in the radial direction, and the centrifugal force due to the rotation of the motor rotor affects the air in the motor. Therefore, the axial gearup motor is introduced from the inner diameter portion of the motor rotor and discharged from the outer diameter portion. By doing so, an efficient flow of cooling air can be obtained, and a more excellent cooling effect can be obtained.
  • the motor-integrated magnetic bearing device may be used in an air cycle refrigeration cooling system that uses air to perform air conditioning or refrigeration. Since the air cycle refrigeration cooling system uses air with a small specific heat as a refrigerant, it requires high-speed rotation. Therefore, motor cooling and other effects are effectively exhibited by the motor body type magnetic bearing device of the present invention.
  • the above air cycle refrigeration cooling system can, for example, compress the incoming air by a compressor of a turbine unit, cool by another heat exchanger, adiabatic expansion by an expansion turbine of the turbine unit, or compress by a precompression means. , Cooling by a heat exchanger, compression by a compressor of a turbine unit, cooling by another heat exchanger, and adiabatic expansion by an expansion turbine of the turbine unit.
  • FIG. 1 is a longitudinal sectional view of a turbine unit incorporating a motor-integrated magnetic bearing device according to a first embodiment of the present invention.
  • FIG. 2 is an exploded front view of a motor stator in the turbine unit.
  • FIG. 3 is a block diagram showing an example of a magnetic bearing controller used in a motor type magnetic bearing device.
  • FIG. 4 is a block diagram showing an example of a motor controller used in a motor type magnetic bearing device.
  • FIG. 5 is a longitudinal sectional view showing a motor in a motor type magnetic bearing device.
  • FIG. 6 is a cross-sectional view showing a partial module of the motor stator.
  • FIG. 7 is a front view of a partial module of the motor stator.
  • FIG. 8 is a cross-sectional view of the motor along the line V I 1 1—V I 1 1 in FIG.
  • FIG. 9 is a longitudinal sectional view showing a motor in a motor type magnetic bearing device according to a second embodiment of the present invention.
  • FIG. 10 is a cross-sectional view showing a part of the module of the motor stator.
  • FIG. 11 is a sectional view of the motor taken along line XI—XI in FIG.
  • FIG. 12 is a longitudinal sectional view of a turbine unit in which a motor type magnetic bearing device according to a third embodiment of the present invention is incorporated.
  • FIG. 13 is a longitudinal sectional view showing a motor in a motor type magnetic bearing device according to a fourth embodiment of the present invention.
  • FIG. 14 is a transverse sectional view showing a part of the motor stator module.
  • FIG. 15 is a longitudinal sectional view of a turbine unit in which a motor type magnetic bearing device according to a fifth embodiment of the present invention is incorporated.
  • FIG. 16 is a longitudinal sectional view of a turbine unit in which a motor type magnetic bearing device according to a sixth embodiment of the present invention is incorporated.
  • FIG. 17 is a system diagram of an air cycle refrigeration cooling system to which the turbine unit of FIG. 1 is applied.
  • FIG. 18 is a longitudinal sectional view of the proposed example.
  • FIG. 1 is a longitudinal sectional view of a turbine unit 5 incorporating the motor-integrated magnetic bearing device of the first embodiment.
  • This turbine unit 5 constitutes a compression / expansion turbine system, and includes a compressor 6 and an expansion turbine 7, and a compressor impeller 6a of the compressor 6 and a turbine impeller 7a of the expansion turbine 7 are main shafts. 1 Fits to both ends of 3. Low carbon steel with good magnetic properties is used as the material for the main shafts 13.
  • the compressor 6 is connected to the compressor impeller 6 a and a minute gap d.
  • the expansion turbine 7 has a turbine housing 7 b that is opposed to the turbine impeller 7 a via a minute gap d 2, and the air sucked from the outer periphery as indicated by an arrow 7 c is received by the turbine impeller 7 a. Adiabatic expansion and exhaust in the axial direction from the central outlet 7d.
  • the motor-integrated magnetic bearing device in the turbine unit 5 is configured such that the main shaft 13 is supported by a plurality of bearings 15 and 16 in the radial direction, and either the axial load applied to the main shaft 13 or the bearing preload is applied. One or both are supported by an electromagnet 17 that constitutes a part of the magnetic bearing, and an axial gap type motor 28 that rotationally drives the main shaft 13 is provided.
  • the turbine unit 5 includes a sensor 18 that detects a thrust force acting on the main shaft 13, and a magnetic bearing controller 1 9 that controls the supporting force of the electromagnet 17 according to the output of the sensor 18. And a motor controller 29 for controlling the motor 28 independently of the electromagnet 17.
  • the electromagnet 17 is composed of two flange-shaped slurries made of a ferromagnetic material which is provided perpendicularly and coaxially to the main shaft 13 so as to be aligned in the axial direction at the axial intermediate portion of the main shaft 13.
  • a pair of support plates 1 3 a and 1 3 b are installed on the spindle housing 14 so as to face each side in a non-contact manner.
  • one of the electromagnets 17 constituting the magnetic bearing unit is opposed to the one surface of the thrust plate 13 a located near the expansion turbine 7 toward the expansion turbine 7 as an electromagnet target without contact.
  • the other electromagnet 17 constituting the magnetic bearing unit has one surface facing the compressor 6 side of the thrust plate 13 b positioned near the compressor 6 as an electromagnet target, and is opposed to this one surface in a non-contact manner. Is installed in the spindle housing 14.
  • the magnetic bearing is constituted by the electromagnets 17 and 17 and the thrust plates 13a and 13b.
  • the motor 28 is composed of a motor unit 2 8a provided on the main shaft 13 alongside the electromagnet 17 and a motor unit 2 8b facing the motor rotor 28a in the axial direction. It is. Specifically, the motor rotor 28a constituting one part of the motor unit is provided on each side of the main shaft 13 opposite to the side on which the electromagnets 17 of the thrust plates 13a, 13b are opposed. By arranging the permanent magnets 28 aa arranged at equal pitches in the circumferential direction, a pair of left and right is configured. Thus, between the permanent magnets 28 a a arranged opposite to each other in the axial direction, the magnetic poles are set to be different from each other.
  • the thrust plates 1 3 a and 1 3 b provided so as to be integrated with the main shaft 1 3 are replaced with permanent magnets 2 8 Can also be used as aa back yoke and electromagnet target.
  • the motor stator 28 b which is another part of the motor unit, faces the surfaces of both motor rotors 28 a in a non-contact manner at the center position in the axial direction between the pair of left and right motor rotors 28 a.
  • a plurality of concentrated winding motor coils 2 8 ba arranged without a core are installed in the spindle housing 14.
  • the motor stator 28 b includes a plurality of motor coils 28 ba arranged in the circumferential direction and integrated with each other (two here).
  • Modules 2 8 b 1, 2 8 b It is divided into two parts. As a result, it can be incorporated as a part of a motor teeter 2 8 b force motor unit disposed between two thrust plates 1 3 a and 13 b integral with the main shaft 13.
  • the motor 28 rotates the main shaft 13 by a mouth-lens force acting between the motor rotor 28a and the motor stator 28b.
  • this axial gap type motor 28 is a coreless motor, the negative rigidity due to the magnetic force pulling between the motor rotor 28a and the motor stator 28b is zero. ing.
  • the bearings 15 and 16 that support the main shaft 13 are rolling bearings and have a function of regulating the axial direction position.
  • deep groove ball bearings are used as an anguilla ball bearing. Deep groove ball bearings have a thrust support function in both directions, and return the inner and outer rings in the axial position to the neutral position.
  • These two bearings 15 and 16 are arranged in the vicinity of the compressor wheel 6a and the turbine wheel 7a in the spindle housing 14 respectively, and electromagnets 17 and thrust plates 13a and 13b. Since the rolling bearings 15 and 16 that support the radial load of the main shaft 1 3 sandwiched between them are positioned apart from each other in the axial direction, the main shaft 13 can be stably supported.
  • the main shaft 13 is a stepped shaft having a large-diameter portion 13c at an intermediate portion and small-diameter portions 13d at both ends.
  • the bearings 15 and 16 on both sides have their inner rings 15 a and 16 a fitted into the small-diameter portion 13 d in a press-fit state, and one of the width surfaces is between the large-diameter portion 13 c and the small-diameter portion 13 d Engage with the step surface.
  • the bearings 6 a and 7 a side of the bearings 15 and 16 on both sides of the spindle housing 14 are formed so that the inner diameter surface is close to the main shaft 13 and the non-contact seal 2 is provided on the inner diameter surface. 1 and 2 2 are formed.
  • the non-contact seals 2 1 and 2 2 are labyrinth seals in which a plurality of circumferential grooves are arranged in the axial direction on the inner diameter surface of the spiddle housing 14, but other non-contact seal means But it ’s okay.
  • the sensor 18 is a stationary side near the bearing 16 on the turbine impeller 7a side. That is, it is provided on the spindle housing 14 side.
  • a bearing 16 provided with the sensor 18 in the vicinity thereof has an outer ring 16 b fitted in a fixed state in the bearing housing 23.
  • the bearing housing 2 3 is formed in a ring shape and has an inner flange 2 3 a that engages with the width surface of the outer ring 16 b of the bearing 16 at one end, and an inner diameter surface provided on the spindle housing 14 2 4 is movably fitted in the axial direction.
  • the inner flange 2 3 a is provided at the center end in the axial direction.
  • the sensors 1 8 are distributed and arranged at a plurality of circumferential locations around the main shaft 1 3 (for example, 2 locations), fixed to the inner flange 2 3 a side of the bearing housing 2 3 and the spindle housing 1 4 It is interposed between one of the electromagnets 17 which is the formed member.
  • the sensor 18 is preloaded by a sensor preload spring 25.
  • the sensor preload spring 25 is housed in a housing recess provided in the spindle housing 14 to urge the outer ring 16 b of the bearing 16 in the axial direction.
  • the outer ring 16 b and the bearing housing 2 3 Preload sensor 1 8 via.
  • the sensor preload spring 25 is composed of, for example, coil springs provided at a plurality of locations in the circumferential direction around the main shaft 13.
  • the preload by the sensor preload spring 25 is to detect any movement of the main shaft 13 in the axial direction by detecting the thrust force by pressing force. It is larger than the average thruster acting on the main shaft 13 in the normal operation state of 5.
  • the bearing 15 on the non-arrangement side of the sensor 18 is installed so as to be movable in the axial direction with respect to the spindle housing 14, and is elastically supported by a bearing preload spring 26.
  • the outer ring 1 5 b of the bearing 15 is fitted to the inner surface of the spindle housing 14 4 so as to be movable in the axial direction.
  • the bearing preload spring 2 6 is formed between the outer ring 15 b and the spindle housing 14. Is intervening.
  • the bearing preload spring 26 is configured to urge the outer ring 15 b facing the step surface of the main shaft 13 with which the width surface of the inner ring 15 a is engaged, and applies a preload to the bearing 15.
  • the bearing preloading spring 26 is composed of coil springs and the like provided at a plurality of locations around the main shaft 13 in the circumferential direction, and is accommodated in receiving recesses provided in the spindle housing 14 respectively. It is.
  • the bearing preload spring 26 is assumed to have a smaller spring constant than the sensor preload spring 25.
  • the dynamic model of the motor-integrated magnetic bearing device in the turbine unit 5 can be constituted by a simple panel system. That is, this panel system includes a synthetic panel formed by bearings 15 and 16 and a support system for these bearings (sensor preload spring 25, bearing preload spring 26, bearing housing 23, etc.), and a motor unit ( This is a configuration in which a synthetic panel formed by the electromagnet 17 and the motor 28) is arranged in parallel.
  • this spring system the composite panel formed by the bearings 15 and 16 and the support system of these bearings has rigidity that acts in proportion to the amount of displacement in the direction opposite to the displaced direction.
  • the composite panel formed by the electromagnet 17 and the motor 28 has a negative stiffness that acts in proportion to the amount of displacement in the direction of displacement.
  • Synthetic panel stiffness due to bearings, etc. ⁇ Electromagnet ⁇ Negative stiffness value of synthetic panel due to motor ...
  • (1) the phase of the mechanical system is delayed by 180 °, resulting in an unstable system.
  • the magnetic bearing controller 19 that controls 17 it is necessary to add a phase compensation circuit in advance, and the configuration of the controller 19 becomes complicated.
  • the phase of the mechanical system can be prevented from being delayed by 180 ° in the control band, so that the magnetic bearing controller 19 can be controlled even when the motor 28 is operating at a high load and an excessive axial load is applied.
  • the circuit configuration of controller 19 can be configured as simple as using proportional or proportional integration.
  • the detection outputs P 1 and P 2 of the sensors 18 are added and subtracted by the sensor output calculation circuit 30 and the calculation results are compared by the comparator 31. Deviation is calculated by comparing with the reference value of the reference value setting means 3 2, and the calculated deviation is proportionally integrated (or appropriately set by the PI compensation circuit (or P compensation circuit) 3 3 according to the turbine unit 5 (or Proportional) By processing, the control signal of the electromagnet 17 is calculated.
  • the output of PI compensation circuit (or P compensation circuit) 3 3 3 is input to power circuits 3 6 and 3 7 that drive electromagnets 1 7 1 and 1 7 2 in each direction via diodes 3 4 and 3 5.
  • the magnet stones 17 1 and 17 2 are a pair of magnet stones 17 facing the thrust plate 13 a shown in FIG. 1 and only the attractive force acts on them.
  • the two electromagnets 1 7 1 and 1 7 2 are selectively driven.
  • the phase adjustment circuit 38 can adjust the phase of the motor drive current using the rotation angle of the motor rotor 28 a as a feedback signal based on the rotation synchronization command signal. Constant rotation control is performed by supplying the motor drive current corresponding to the adjustment result from the motor drive circuit 39 to the motor coil 28 ba of the motor stator 28 b.
  • the timing of switching the supply of motor drive current to the motor coil 2 8 ba is the output of the position detection sensor 40 that detects the passage of the permanent magnet 2 8 aa of the motor rotor 2 8 a provided in the motor stator 28 b Is determined by the phase adjustment circuit 38.
  • the rotation synchronization command signal is calculated according to the output of a rotation angle detection sensor (not shown) provided in the motor rotor 28 a.
  • FIG. 5 is a longitudinal sectional view showing the motor 28, and FIG. 6 is a transverse sectional view of a partial module 2 8 b 1 of the motor stator 2 8 b.
  • the motor stator 28b includes the plurality of motor coils 28b and the polymer material case 28b that is an insulating material containing the motor coils 28ba therein.
  • Case 2 8 bb is provided for each of the modules 2 8 b 1 and 2 8 b 2 as described above.
  • This case 28 bb is provided with a cooling passage 41 that allows the coolant 20 to flow into the motor stator 28 b so that the coolant 20 contacts the winding of the motor coil 28 ba as a coolant. ing.
  • the cooling passage 4 1 includes an inlet 4 1 a to which the coolant 20 is supplied from the outside of the case 2 8 bb, and an in-case cooling provided in the case 2 8 bb in communication with the inlet 4 1 a. And a path 4 1 b and one or a plurality of discharge ports 4 1 c provided in the cooling path 4 1 b in the case.
  • the remaining space excluding the space occupied by the motor coil 2 8 ba in the case 2 8 bb is defined as the cooling path 4 1 b in the case, and the inlet 4 1 a and the outlet in the outer periphery 4 1 c is arranged.
  • Pump P is installed outside the bearing device, pump P and inlet 41a are connected by supply path 61, and pump P and outlet 41c are connected by recovery path 62.
  • the recovery path 62 is provided with a radiator R, and a reservoir / tank T for replenishing the coolant 20 to the radiator R is connected.
  • Coolant 20 from the pump P passes through the supply path 61 and enters the cooling path 4 1 b in the case from the inlet 4 1 a to cool the motor 2 8.
  • the coolant 20 after cooling the motor returns to the pump P from the discharge port 4 1 c through the recovery path 6 2, dissipates heat in the radiator R, and returns to a low temperature.
  • FIG. 7 shows a front view of a partial module 28 b 1 of the motor stator 28 b
  • FIG. 8 shows a cross-sectional view of the motor 28 along the line VIII-VIII in FIG.
  • the motor rotor 2 8 a on the outer surface of the case 2 8 bb in the motor stator 2 8 b A position detection sensor 40 for detecting the passage of the permanent magnet 28 aa is provided.
  • the position detection sensor 40 outside the case 28 bb of the motor stator 28 b, it is possible to avoid the position detection sensor 40 from touching the coolant 20.
  • FIG. 9 is a longitudinal sectional view showing a motor in the motor-integrated magnetic bearing device according to the second embodiment of the present invention.
  • FIG. 10 shows a portion module 2 8 of the motor stator 2 8 b.
  • FIG. 11 shows a cross-sectional view of the motor 28 along the line XI-XI in FIG.
  • the cooling path 4 1 b in the case has a plurality of cooling liquid passage grooves 4 1 ba that open facing each motor coil 2 8 ba and are arranged radially in the radial direction of the case 2 8 bb.
  • the cooling path in the case 4 1 b includes an outer periphery of the cooling path 4 1 bb positioned on the outer periphery of the motor coil 2 8 ba and extending in an arc shape, and the motor from the outer periphery of the cooling path 4 1 bb Coil 2 8 Ba
  • the coolant passage groove 4 1 ba along the both end faces of each motor coil 2 8 b is opened along the surface of the motor coil 2 8 ba, and the coolant flowing in the groove is transferred to the motor coil 2 8 ba. Touch the coil winding directly.
  • a plurality of cooling path outer peripheral parts 4 1 bb are provided side by side in the arc direction, and an inlet 4 1 a is provided in one of the cooling path outer peripheral parts 4 1 bb (one in the center in the illustrated example).
  • a discharge port 4 1 c is formed in the outer peripheral portion 4 1 bb of the remaining cooling path (two on both sides in the illustrated example).
  • Other configurations are the same as those of the first embodiment shown in FIGS.
  • the turbine unit 5 having this configuration is applied to, for example, an air cycle refrigeration cooling system so that air as a cooling medium can be efficiently heat-exchanged by a subsequent heat exchanger (not shown here).
  • the temperature is increased by compressing at 6 and the air cooled by the heat exchanger in the subsequent stage is further insulated by the expansion turbine 7 to a target temperature, for example, a very low temperature of about 30 ° C. to about 60 ° C. Used to cool and discharge by expansion.
  • the turbine unit 5 is fitted to the main shaft 1 3 common to the thrust plate 1 3 a and the motor rotor 2 8 a, and the motor 2 8
  • the compressor impeller 6a is driven by one or both of the power of the turbine and the power generated by the turbine impeller 7a.
  • stable high-speed rotation of the main shaft 13 can be obtained while maintaining appropriate gaps d 1 and d 2 between the impellers 6 a and 7 a, and the long-term durability of the bearings 15 and 16 can be improved. Improved lifespan is obtained.
  • a thrust force is applied to the main shaft 13 of the turbine unit 5 by the air pressure acting on the impellers 6 a and 7 a.
  • the turbine unit 5 used in the air cooling system rotates at a very high speed of, for example, about 80,000 to 100,000 revolutions per minute.
  • the thrust force acts on the rolling bearings 15 and 16 that rotatably support the main shaft 13, the long-term durability of the bearings 15 and 16 decreases.
  • the thrust force is supported by the electromagnet 17, it is applied to the rolling bearings 15 and 16 for supporting the spindle 13 while suppressing an increase in torque without contact.
  • the thrust force used can be reduced.
  • a sensor 18 for detecting the thrust force acting on the main shaft 13 and a magnetic bearing controller 19 for controlling the supporting force by the electromagnet 17 according to the output of the sensor 18 are provided. Therefore, the rolling bearings 15 and 16 can be used in an optimum state with respect to the thrust force according to the bearing specifications.
  • a magnetic bearing unit is constructed by arranging two electromagnets 17 on the outer side in the axial direction of two thrust plates 13a, 13b arranged on the main shaft 13 in the axial direction.
  • an axial gap type motor 28 By arranging an axial gap type motor 28 at a position between the plates 1 3 a and 1 3 b to form a motor unit, the magnetic bearing unit and the motor unit are made into a compact and integrated structure.
  • the shaft length of 3 can be shortened, and the natural frequency of the main shaft 13 can be increased accordingly, so that the main shaft 13 can be rotated at high speed.
  • the motor 28 is of an axial gap type and generates a large amount of heat at the motor stator 28 b, and is performed by a general motor.
  • Such indirect cooling from the outside of the motor case does not provide sufficient cooling.
  • the cooling passage 4 1 is provided so that the coolant 20 flows into the motor stator 28 b so that the coolant 20 contacts the winding of the motor coil 28 ba. Cooling takes place.
  • the cooling passage 4 1 flows through the cooling passage groove 4 1 ba that opens to face the motor coil 2 8 ba. Therefore, if the overall flow rate is the same, the cooling passage 41 will flow in a narrow channel cross section. The flow rate becomes high. As a result, a decrease in motor efficiency and a deterioration in safety due to insufficient cooling can be avoided.
  • FIG. 12 is a cross-sectional view of a turbine unit incorporating a motor-integrated magnetic bearing device according to a third embodiment of the present invention.
  • this turbine unit 5 has only one flange-like thrust plate made of a ferromagnetic material that is provided perpendicularly and coaxially to the main shaft 13 and is used as a thrust plate 13 a.
  • a pair of left and right electromagnets 17 and 17 are installed on the spindle housing 14 so as to face both surfaces in a non-contact manner.
  • the motor 28 includes a motor rotor 28a provided on the main shaft 13 and a motor stator 28b that faces the motor rotor 28a in the axial direction.
  • the motor rotor 28 a is arranged by arranging permanent magnets 28 aa arranged at equal pitches in the circumferential direction on the outer diameter side of the thrust plate 13 a on the both sides of the electromagnet 17 facing each other. A pair is constructed. Thus, between the permanent magnets 28 aa arranged opposite to each other in the axial direction, the magnetic poles are set to be different from each other.
  • the thrust plate 1 3 a doubles as the back yoke of the permanent magnet 2 8 aa.
  • the motor stabilizer 28 b is a ferromagnetic material (for example, low carbon steel and key) installed in the spindle housing 14 so as to face the motor rotor 28 a on both sides of the thrust plate 13 a without contact.
  • a pair of left and right coils are formed by winding a motor coil ba around a pair of stator yokes 2 8 bb made of a steel plate.
  • the two left and right motors 28 configured with the thrust plate 1 3 a sandwiched between them are driven by the magnetic force acting between the motor rotor 2 8 a and the motor stator 2 8 b. Rotate.
  • the position of the motor rotor 28 b on the thrust plate 13 a is on the outer diameter side with respect to the position facing the electromagnet 17, a larger torque can be obtained with a small motor driving current.
  • Other configurations are the same as those of the first embodiment in FIG. 1, and the description thereof is omitted here.
  • FIG. 13 the motor coil 28 ba in the fourth embodiment is divided into a plurality of (here, two) coil division bodies 2 8 ba 1 and 2 8 ba 2 arranged in the axial direction.
  • the in-case cooling path 4 1 b is formed between the coil divided bodies 2 8 ba 1 and 2 8 ba 2 arranged in the axial direction, and the hollow of the coil 2 8 ba from the outer periphery of the coil 2 8 ba.
  • the part 2 8 baa has a hollow part inflow passage 4 1 ba through which the coolant 20 flows. As shown in FIG.
  • the cooling path 4 1 b in the case includes an arc-shaped outer peripheral path portion 4 1 bb along the outer peripheral portion of the case 28 bb, and a plurality of branches branched from the outer peripheral path portion 4 1 bb.
  • Hollow part inflow path 4 1 ba, motor coil 2 8 ba hollow part 2 8 baa, case 2 8 bb inner circumference part of motor coil 2 8 ba axially on both sides in axial direction than motor coil 2 8 ba From the inner peripheral path part 4 1 bc between the inner peripheral path part 4 1 bc and the adjacent motor coil 2 8 ba. It consists of a plurality of discharge path portions 4 1 bd extending to the outer diameter side.
  • the inlet 4 1 a is provided in the outer peripheral passage portion 4 1 bb, and the outlet 4 1 c is provided at the tip of each discharge passage portion 4 1 bd.
  • the motor 28 is of an axial gear type and has a large amount of heat generated by the motor stator 28b, so that the motor case can be operated by a general motor. Indirect cooling from the outside of the door does not provide sufficient cooling.
  • the cooling passage 41 through which the cooling liquid 20 flows is provided in the hollow portion 28 baa of the motor coil 28ba, a sufficient cooling effect can be obtained. As a result, a decrease in motor efficiency and a deterioration in safety due to insufficient cooling can be avoided.
  • the coolant 20 flowing from the inlet 4 1 a of the cooling passage 4 1 into the cooling passage 4 1 b in the case passes through the hollow portion inflow passage 4 1 ba and the hollow portion of each motor coil 2 8 ba 2 8 baa Therefore, the coolant 20 can be efficiently brought into contact with the coil winding, and the cooling effect on the motor coil 28 ba can be enhanced.
  • the coolant 20 that flows into the hollow portion 2 8 baa of each motor coil 2 8 ba and contributes to the cooling of the motor coil 2 8 ba is discharged from the discharge port 4 1 c to the outside of the case 2 8 bb. .
  • the cooling passage 41 can be configured in a compact manner, so that the cooling passage 41 can be formed. It is possible to avoid an increase in the size of the motor stabilizer 2 8 b.
  • This fourth embodiment can also be applied to the configuration of FIG.
  • air is used as a cooling medium.
  • the motor part cooling air introduction path 4 2 A for supplying cooling air into the motor 28 from the outside, and the supplied air is exhausted to the outside of the motor 28.
  • Cooling passage consisting of a discharge path 4 2 B 4 1 A force is provided in the spindle housing 14.
  • the discharge path 4 2 B is opened from the outer diameter portion of the motor rotor 28 a in the space inside the motor 28 to the outer diameter surface of the spindle / housing 14.
  • the motor part cooling air introduction path 4 2 A is for introducing a part of the air flowing into the turbine impeller 7 a into the motor 28, and sucking in the space inside the turbine housing 7 b
  • a path inlet 45 is opened between the opening and the turbine impeller 7a.
  • the passage inlet 43 may be opened to the discharge port 7 d in the turbine housing 7 b, and in that case, a part of the air discharged from the turbine blade 7 a is introduced into the motor 28.
  • Motor section cooling air introduction path 4 2 A is branched into two branch paths 4 2 A a, 4 2 A b, and the motor side that becomes the path exit at the end of each branch path 4 2 A a, 4 2 A b Opening from the opening 4 4 to the space around the motor rotor in the motor 28.
  • the two branch paths 4 2 A a and 4 2 A b respectively pass through the yokes of the electromagnets 17 of the magnetic bearings on both sides, and the motor side opening 4 4 is located at the inner peripheral portion of the motor rotor 28 a is doing.
  • the motor part cooling air introduction path 4 2 A for supplying cooling air into the motor 28 from the outside, and the air is supplied. Since a discharge path 4 2 B for exhausting the air outside the motor is provided, the required motor can be obtained with a simple configuration simply by providing the cooling path 4 1 A consisting of the introduction path 4 2 A and the discharge path 4 2 B. Cooling is possible.
  • the motor air supply path 4 2 A uses the air that flows into or discharges from the turbine blade 7 a, so that a dedicated air supply source such as a fan is not required. Efficient motor cooling can be performed with a simple configuration.
  • the motor 28 is an axial gap motor
  • the main shaft 1 3 can be configured to be short, and the main shaft 28 can be rotated at high speed without causing a resonance problem.
  • the motor 28 can be efficiently cooled. Difficult to do. Force, and as above Since a part of the air flowing into the turbine blade 7a or the air discharged from the turbine blade 7a is introduced into the motor 28, an excellent cooling effect by forced circulation of the cooling air can be obtained with a simple configuration.
  • the motor rotor 28a is large in the radial direction, and the centrifugal force due to the rotation of the motor rotor 28a affects the air in the motor 28.
  • 2 A and the discharge path 4 2 B are introduced from the inner diameter part of the motor rotor 2 8 a and discharged from the outer diameter part, so that an efficient flow of cooling air can be obtained and a more excellent cooling effect can be obtained. can get.
  • the turbine unit 5 shown in FIG. 15 has only one flange-like thrust plate made of a ferromagnetic material that is perpendicular to the main shaft 1 3 and coaxial with the thrust plate.
  • a pair of left and right electromagnets 17 and 17 are installed on the spindle housing 14 so that 1 3 a is an electromagnet target and faces both surfaces in a non-contact manner.
  • the motor section cooling air introduction path 4 2 A is branched into two branch paths 4 2 A a and 4 2 Ab, but in this sixth embodiment, the motor Partial cooling air introduction path 4 2 D is not branched and is one.
  • the motor part cooling air introduction path 4 2 D and the discharge path 4 2 B form a cooling path 4 1 B.
  • the other configuration is the same as that of the fifth embodiment in FIG. 15, and the description thereof is omitted here.
  • the motor part cooling air introduction path 4 2 D has one structure without branching, thereby simplifying the structure as compared with the fifth embodiment.
  • This sixth embodiment is also applicable to the configuration of FIG.
  • FIG. 17 shows the overall configuration of an air cycle refrigeration cooling system using the turbine unit 5 according to each of the above embodiments.
  • This air cycle refrigeration cooling system is a system that directly cools the air in the space to be cooled 10 such as a refrigeration warehouse as a refrigerant, and discharges air from the air intake 1 a that opens in the space to be cooled 10.
  • Air circulation path 1 leading to b In this air circulation path 1, pre-compression means 2, first heat exchanger 3, compressor 6 of turbine unit 5 for air cycle refrigeration cooling, second heat exchanger 3, intermediate heat exchanger 9, and the turbine
  • the expansion turbine 7 of the unit 5 is provided in order.
  • the intermediate heat exchanger 9 exchanges heat between the inflow air in the vicinity of the intake 1a in the same air circulation path 1 and the air that has been heated by the subsequent compression and cooled. Air near inlet 1a passes through heat exchanger 9a.
  • the pre-compression means 2 comprises a blower or the like, and is driven by a motor 2a.
  • the first heat exchanger 3 and the second heat exchanger 8 have heat exchangers 3 a and 8 a for circulating a cooling medium, respectively, and a cooling medium such as water in the heat exchangers 3 a and 8 a Heat exchange with the air in the air circulation path 1.
  • Each of the heat exchangers 3 a and 8 a is connected to the cooling tower 11 by piping, and the cooling medium heated by the heat exchange is cooled by the cooling tower 11.
  • An air cycle refrigeration cooling system having a configuration not including the pre-compression means 2 may be used.
  • This air cycle refrigeration cooling system is a system that keeps the cooled space 10 at about 0 ° C to -60 ° C, and is 0 ° from the cooled space 10 to the inlet 1a of the air circulation path 1.
  • C ⁇ -Air of 1 atm flows at around 60 ° C.
  • the air flowing into the intake 1a is used to cool the air in the latter stage in the air circulation path 1 by the intermediate heat exchanger 9, and the temperature is raised to 30 ° C.
  • This heated air remains at 1 atm, but is compressed to 1.4 atm by pre-compression means 2, and the temperature is raised to 70 ° C by the compression.
  • the first heat exchanger 3 only needs to cool the heated air at 70 ° C, so it can be cooled efficiently even with cold water at room temperature, and it is cooled to 40 ° C.
  • Air at 40 ° C and 1.4 atm cooled by heat exchange is compressed to 1.8 atm by the compressor 6 of the turbine unit 5, and is heated to about 70 ° C by this compression. Cooled to 40 ° C by the second heat exchanger 8. This 40 ° C air is cooled to –20 ° C by –30 ° C air in the intermediate heat exchanger 9. The atmospheric pressure is maintained at 1.8 atm which is discharged from the compressor 6. The air cooled to 20 ° C in the intermediate heat exchanger 9 is adiabatically expanded by the expansion turbine 7 of the turbine unit 5, cooled to _55 ° C, and discharged from the outlet 1b. Are discharged to the cooled space 10. This air cycle refrigeration cooling system performs such a refrigeration cycle.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Abstract

L'invention concerne un dispositif à coussinet magnétique intégré à un moteur, dans lequel la durabilité à long terme de roulements à bille est améliorée malgré une charge de poussée et dans lequel un effet de refroidissement de moteur suffisant est obtenu. Le dispositif à coussinet magnétique intégré au moteur utilise conjointement des roulements à bille (15, 16) et un coussinet magnétique, les roulements à bille (15, 16) supportant une charge radiale et le coussinet magnétique supportant soit une charge axiale soit une pré-charge de coussinet. Un électro-aimant (17) du coussinet magnétique est installé sur un corps de broche (14), de telle sorte que l'électro-aimant est tourné vers des plaques de poussée (13a, 13b) de type bride, sans entrer en contact avec elles. Lesdites plaques de poussée (13a, 13b) sont faites d'un matériau ferromagnétique et disposées sur un arbre principal (13). Des rotors de moteur (28a) d'un moteur (28) d'espace axial sont constitués des plaques de poussée (13a, 13b) et d'aimants permanents (28aa) disposés à espacement egal et périphérique sur les plaques de poussée. Un stator de moteur (28b) est muni d'une bobine moteur (28ba) et placé dans le corps de broche (14) de façon à faire face au rotor de moteur (28a). Dans le stator de moteur (28b), un trajet de refroidissement (41) est formé pour amener le liquide de refroidissement à s'écouler vers l'intérieur du stator de moteur (28b), et le trajet de refroidissement (41) est formé de telle sorte que le liquide de refroidissement est en contact avec un fil d'enroulement de la bobine de moteur (28ba).
PCT/JP2007/000898 2006-09-13 2007-08-23 Dispositif à coussinet magnétique intégré à un moteur Ceased WO2008032430A1 (fr)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP2006247882A JP2008072812A (ja) 2006-09-13 2006-09-13 モータ一体型磁気軸受装置およびモータ装置
JP2006-247881 2006-09-13
JP2006247879A JP2008072809A (ja) 2006-09-13 2006-09-13 モータ一体型の磁気軸受装置
JP2006-247879 2006-09-13
JP2006247881A JP2008072811A (ja) 2006-09-13 2006-09-13 モータ一体型の磁気軸受装置
JP2006-247882 2006-09-13
JP2006-247880 2006-09-13
JP2006247880A JP2008072810A (ja) 2006-09-13 2006-09-13 モータ一体型の磁気軸受装置

Publications (1)

Publication Number Publication Date
WO2008032430A1 true WO2008032430A1 (fr) 2008-03-20

Family

ID=39183499

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2007/000898 Ceased WO2008032430A1 (fr) 2006-09-13 2007-08-23 Dispositif à coussinet magnétique intégré à un moteur

Country Status (1)

Country Link
WO (1) WO2008032430A1 (fr)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2468018A (en) * 2009-02-13 2010-08-25 Isis Innovation Cooling a permanent magnet electrical machine with wound stator bars
EP2186996A3 (fr) * 2008-11-12 2011-04-20 Atlas Copco Energas Gmbh Rotor de turbomachine
EP2412630A1 (fr) * 2010-07-27 2012-02-01 Siemens Aktiengesellschaft Entraînement d'une hélice de queue d'un hélicoptère
CN102434587A (zh) * 2011-09-19 2012-05-02 北京航空航天大学 具有被动阻尼作用的永磁被动式轴向磁悬浮轴承
US8581455B2 (en) 2009-04-14 2013-11-12 Isis Innovation Ltd. Electric machine—evaporative cooling
US9071117B2 (en) 2009-02-13 2015-06-30 Isis Innovation Ltd. Electric machine—flux
US9287755B2 (en) 2010-08-19 2016-03-15 Yasa Motors Limited Electric machine—over-moulding construction
US9318938B2 (en) 2009-02-13 2016-04-19 Isis Innovation Ltd. Electric machine-modular
GB2559854A (en) * 2015-10-16 2018-08-22 Yasa Ltd Axial flux machine
CN108775342A (zh) * 2018-06-12 2018-11-09 尹苑苑 一种提高空调压缩机使用寿命的方法
CN111288726A (zh) * 2020-02-28 2020-06-16 佛山格尼斯磁悬浮技术有限公司 磁悬浮内螺纹铜管加工设备的温度监控系统及方法、装置
WO2021032236A1 (fr) * 2019-08-20 2021-02-25 Schaeffler Technologies AG & Co. KG Machine à rotor à disque pour entraînement de véhicule automobile
CN114623162A (zh) * 2022-02-28 2022-06-14 王超颖 一种轴承
CN116914976A (zh) * 2023-08-29 2023-10-20 采埃孚股份公司 同轴电驱动装置
US11835088B2 (en) 2021-05-28 2023-12-05 Rolls-Royce North American Technologies, Inc. Thrust bearing for a rotating machine

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08242557A (ja) * 1995-03-01 1996-09-17 Sawafuji Electric Co Ltd 高速回転機の冷却構造
JPH08261237A (ja) * 1995-03-17 1996-10-08 Aisin Seiki Co Ltd ガスタービンエンジン
JPH11503223A (ja) * 1995-04-05 1999-03-23 ロートフロー・コーポレイション 冷却システム
JP2002095209A (ja) * 2000-09-14 2002-03-29 Mitsubishi Heavy Ind Ltd 電力貯蔵用フライホイール装置
JP2003065621A (ja) * 2001-08-24 2003-03-05 Shimadzu Corp 冷却システム
JP2005261083A (ja) * 2004-03-11 2005-09-22 Nissan Motor Co Ltd 回転電機の冷却構造
JP2006014564A (ja) * 2004-06-29 2006-01-12 Nissan Motor Co Ltd ディスク型回転電機のステータ冷却構造

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08242557A (ja) * 1995-03-01 1996-09-17 Sawafuji Electric Co Ltd 高速回転機の冷却構造
JPH08261237A (ja) * 1995-03-17 1996-10-08 Aisin Seiki Co Ltd ガスタービンエンジン
JPH11503223A (ja) * 1995-04-05 1999-03-23 ロートフロー・コーポレイション 冷却システム
JP2002095209A (ja) * 2000-09-14 2002-03-29 Mitsubishi Heavy Ind Ltd 電力貯蔵用フライホイール装置
JP2003065621A (ja) * 2001-08-24 2003-03-05 Shimadzu Corp 冷却システム
JP2005261083A (ja) * 2004-03-11 2005-09-22 Nissan Motor Co Ltd 回転電機の冷却構造
JP2006014564A (ja) * 2004-06-29 2006-01-12 Nissan Motor Co Ltd ディスク型回転電機のステータ冷却構造

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2186996A3 (fr) * 2008-11-12 2011-04-20 Atlas Copco Energas Gmbh Rotor de turbomachine
GB2468018B (en) * 2009-02-13 2014-06-04 Isis Innovation Electric machine - cooling
WO2010092400A3 (fr) * 2009-02-13 2011-06-23 Isis Innovation Ltd Machine électrique - refroidissement
US9496776B2 (en) 2009-02-13 2016-11-15 Oxford University Innovation Limited Cooled electric machine
CN102396134A (zh) * 2009-02-13 2012-03-28 Isis创新有限公司 电机-冷却
KR101747975B1 (ko) 2009-02-13 2017-06-27 옥스포드 유니버시티 이노베이션 리미티드 전기 기계 - 냉각
JP2012518376A (ja) * 2009-02-13 2012-08-09 アイシス イノベイシヨン リミテツド 電気機械−冷却
US9318938B2 (en) 2009-02-13 2016-04-19 Isis Innovation Ltd. Electric machine-modular
GB2468018A (en) * 2009-02-13 2010-08-25 Isis Innovation Cooling a permanent magnet electrical machine with wound stator bars
US9071117B2 (en) 2009-02-13 2015-06-30 Isis Innovation Ltd. Electric machine—flux
US9054566B2 (en) 2009-04-14 2015-06-09 Isis Innovation Ltd Electric machine—evaporative cooling
US8581455B2 (en) 2009-04-14 2013-11-12 Isis Innovation Ltd. Electric machine—evaporative cooling
RU2526331C1 (ru) * 2010-07-27 2014-08-20 Сименс Акциенгезелльшафт Привод хвостового винта вертолета
US9631516B2 (en) 2010-07-27 2017-04-25 Siemens Aktiengesellschaft Drive of a tail rotor of a helicopter
CN103108803A (zh) * 2010-07-27 2013-05-15 西门子公司 直升飞机的尾桨的驱动装置
WO2012019864A3 (fr) * 2010-07-27 2012-10-11 Siemens Aktiengesellschaft Entraînement d'un rotor de queue d'un hélicoptère
EP2412630A1 (fr) * 2010-07-27 2012-02-01 Siemens Aktiengesellschaft Entraînement d'une hélice de queue d'un hélicoptère
US9287755B2 (en) 2010-08-19 2016-03-15 Yasa Motors Limited Electric machine—over-moulding construction
CN102434587A (zh) * 2011-09-19 2012-05-02 北京航空航天大学 具有被动阻尼作用的永磁被动式轴向磁悬浮轴承
GB2559854A (en) * 2015-10-16 2018-08-22 Yasa Ltd Axial flux machine
GB2559854B (en) * 2015-10-16 2020-04-29 Yasa Ltd Axial flux machine
CN108775342A (zh) * 2018-06-12 2018-11-09 尹苑苑 一种提高空调压缩机使用寿命的方法
CN108775342B (zh) * 2018-06-12 2020-09-08 浏阳市明诚竹业有限公司 一种提高空调压缩机使用寿命的方法
WO2021032236A1 (fr) * 2019-08-20 2021-02-25 Schaeffler Technologies AG & Co. KG Machine à rotor à disque pour entraînement de véhicule automobile
CN114207994A (zh) * 2019-08-20 2022-03-18 舍弗勒技术股份两合公司 用于机动车辆驱动的盘式转子机器
US12334786B2 (en) 2019-08-20 2025-06-17 Schaeffler Technologies AG & Co. KG Disc rotor machine with stator having core segents, with rotor disc with cooling device
CN111288726A (zh) * 2020-02-28 2020-06-16 佛山格尼斯磁悬浮技术有限公司 磁悬浮内螺纹铜管加工设备的温度监控系统及方法、装置
US11835088B2 (en) 2021-05-28 2023-12-05 Rolls-Royce North American Technologies, Inc. Thrust bearing for a rotating machine
CN114623162A (zh) * 2022-02-28 2022-06-14 王超颖 一种轴承
CN116914976A (zh) * 2023-08-29 2023-10-20 采埃孚股份公司 同轴电驱动装置

Similar Documents

Publication Publication Date Title
WO2008032430A1 (fr) Dispositif à coussinet magnétique intégré à un moteur
JP2008283813A (ja) モータ一体型磁気軸受装置
JP2008190376A (ja) 空気サイクル冷凍機用タービンユニット
WO2008018167A1 (fr) Dispositif palier magnétique du type à moteur intégré
JP2007162723A (ja) モータ一体型磁気軸受装置
JP2009050066A (ja) モータ一体型の磁気軸受装置
JP2010043780A (ja) 空気サイクル冷凍ユニット
WO2008015776A1 (fr) Dispositif de palier magnétique intégral à un moteur
WO2008015777A1 (fr) Unité de turbine de machine refrigérante à cycle à air
JP2009062848A (ja) モータ一体型の磁気軸受装置
JP2007162726A (ja) モータ一体型磁気軸受装置
JP2007162725A (ja) モータ一体型磁気軸受装置
JP4969272B2 (ja) モータ一体型磁気軸受装置
JP2008072809A (ja) モータ一体型の磁気軸受装置
JP2008072810A (ja) モータ一体型の磁気軸受装置
JP2007162493A (ja) 圧縮膨張タービンシステム
JP2010007726A (ja) モータ一体型の磁気軸受装置
JP2009296750A (ja) モータ一体型の磁気軸受装置
JP2008082216A (ja) 圧縮膨張タービンシステム
JP4799159B2 (ja) モータ一体型磁気軸受装置
JP2008185110A (ja) 磁気軸受装置
WO2008018169A1 (fr) Dispositif de palier magnétique intégré dans un moteur
JP2008072808A (ja) モータ一体型の磁気軸受装置
JP2007162492A (ja) 圧縮膨張タービンシステム
JP2008283812A (ja) モータ一体型磁気軸受装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 07790383

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 07790383

Country of ref document: EP

Kind code of ref document: A1