WO2002050481A1 - Turbocompresseur monolithique - Google Patents

Turbocompresseur monolithique Download PDF

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Publication number
WO2002050481A1
WO2002050481A1 PCT/RU2001/000561 RU0100561W WO0250481A1 WO 2002050481 A1 WO2002050481 A1 WO 2002050481A1 RU 0100561 W RU0100561 W RU 0100561W WO 0250481 A1 WO0250481 A1 WO 0250481A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
evaporator
stage
cooling
refrigerating system
Prior art date
Application number
PCT/RU2001/000561
Other languages
English (en)
Inventor
Vladimir Leonidovich Kondakov
Mikhail Petrovich Vereschagin
Original Assignee
Turbosystem 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
Application filed by Turbosystem Ltd. filed Critical Turbosystem Ltd.
Priority to AU2002230324A priority Critical patent/AU2002230324A1/en
Publication of WO2002050481A1 publication Critical patent/WO2002050481A1/fr

Links

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/10—Arrangements for cooling or ventilating by gaseous cooling medium flowing in closed circuit, a part of which is external to the machine casing
    • H02K9/12—Arrangements for cooling or ventilating by gaseous cooling medium flowing in closed circuit, a part of which is external to the machine casing wherein the cooling medium circulates freely within the casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • F04D25/0653—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump the motor having a plane air gap, e.g. disc-type
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression

Definitions

  • the field of the invention is refrigeration technology, more particularly, turbocompressors.
  • a known refrigerating system comprising a condenser, an evaporator, and a two-stage centrifugal compressor assembly with a built-in electrical motor between the stages.
  • the motor is provided with a cooling system that has coolant feed and discharge ducts connected to the internal cavity of its housing.
  • the condenser inlet is connected to the compressor assembly outlet, and the condenser outlet is connected by one line to the evaporator inlet via the first choke element, and by a second line to the electrical motor cooling system via the second choke element.
  • the evaporator outlet communicates with the compressor assembly inlet, and the gas coolant discharge duct is connected to the outlet of the compressor assembly's second stage (1).
  • centrifugal compressor assembly for a refrigerating system comprising two centrifugal compressor stages with rotors, diffuser ducts, collection chambers, inlet and outlet tubing for the second stage, and a built-in electrical motor between the compressor assembly's first and second stages.
  • the rotor of the electrical motor is positioned with the centrifugal stage rotors on one shaft, which is mounted on bearings, and the stator is fixed inside its housing, forming a cooling skirt between them.
  • the motor housing is provided with gas coolant feed and discharge ducts which are connected to the outlet tubing of the compressor assembly's second stage (1).
  • a condenser inlet is connected to a compressor assembly outlet, while a condenser outlet is connected via first and second choke elements to an inlet of the evaporator and to the cooling system.
  • the evaporator outlet communicates with the compressor assembly inlet, and the cooling system outlet communicates with the inlet of the second stage of the assembly.
  • the cooling system is provide with a cooling skirt having a cavity of the cooling system lying between a stator and a housing.
  • the refrigerating system has a separator vessel, a recuperative heat exchanger, and a heat-regulating valve controlled by the coolant pressure and temperature at the cooling skirt inlet, and also fitted in series with the separator vessel in the line connecting the condenser inlet to the evaporator.
  • the separator vessel is connected by a gas phase to the coolant feed duct.
  • the heat exchanger is connected by the coolant to a line connecting the condenser outlet to the evaporator inlet via the separator vessel.
  • the second choke element is a heat-controlled valve regulated by the pressure and temperature of the coolant in the coolant discharge line from the cooling skirt.
  • This system shows a number of disadvantages related to the efficiency and the cooling system.
  • the present invention relates to a refrigerating system comprising: an evaporator, a condenser, two diffusers, and a two stage centrifugal compressor assembly with a built-in valve disk coUectorless motor between the compressor stages.
  • the present invention relates to a refrigerating system comprising: an evaporator, a condenser, two diffusers, and a two stage centrifugal compressor assembly with a built-in valve disk coUectorless motor between the compressor stages; wherein the flowing gas flowing from the first stage of the compressor to the second stage of the compressor, flows through spaces in said motor, and thus effectively cools said motor.
  • the present invention relates to a refrigerating system as defined above, wherein said system is equipped with a drosseling valve, which controls the temperature and the pressure of the cooling agent upon leaving the evaporator.
  • the present invention relates to a refrigerating system as defined above, which is automated in such a way that provides a smooth start and stop of the compressor.
  • the present invention relates to a refrigerating system as defined above, which is equipped with means of changing the engine speed which controls the temperature of the air on the exit of the evaporator.
  • the present invention relates to a refrigerating system comprising: an evaporator, a condenser; two diffusers; and a two stage centrifugal compressor assembly with a built-in valve disk coUectorless motor between the compressor stages; said sprockets and diffusers designed to improve their efficiency.
  • the present invention relates to a novel, efficient sprocket and diffuser.
  • Fig. 1 represents a scheme of an air conditioning system.
  • Fig. 2 represents a longitudinal sections of the turbocompressor of the present invention
  • Fig. 3 represents thumbnails of a blading section (sprocket and diffuser).
  • Figs. 4, 5, 6, and 7 represent an illustration of the motor, mainly the rotor. Note, the numerals in Figs. 4-7 do not necessarily comply with the numerals in figs. 1-3. In the event of a contradiction between the two in the specification, the latter should be considered.
  • the system of air conditioning comprises: the condenser, evaporator and centrifugal compressor with the built-in electric motor equipped with an effective system of cooling of the engine.
  • the cooling system is executed inside the compressor casings.
  • the entrance of the condenser is bridged to the exit of the compressor, and the exit of the condenser through the first and second drosselling valves is attached to the entrance of the evaporator.
  • the exit of the evaporator is connected with the compressor's inlet.
  • the air conditioning system includes a vessel- separator.
  • the vessel-separator is placed on a main line connecting the exit of the condenser to the entrance of the evaporator, between the first and second drosselling valves.
  • the turbocompressor of the present invention can be utilized in industrial and household air conditioning systems, and also in low-power chillers.
  • the described air conditioning system consists of a condenser, an evaporator and a two-stage centrifugal compressor with a built-in disk electric motor installed directly on the shaft of the compressor between the stages.
  • the engine is equipped with a cooling system.
  • the cooling of the electric motor utilizes the total flow of the cooling agent, pumped through shank bore of the compressor through special channels made in the body and bearing shields.
  • the cooling agent through the first, second drosselling units and the vessel-separator moves on to the entrance of the evaporator.
  • the exit of the evaporator is bridged to the compressor's inlet.
  • the described centrifugal compressor included in the structure of an air conditioning system consists of two stages of compression installed in opposition on one shaft; two diffusers; two covers - collectors of gas; details forming internal passages for cooling agent transfer; two radial graphite seals; bearing assemblies; input and output pipe lines; the built-in disk electric motor set on the shaft of the compressor; a stator fixed in the compressor casing.
  • turbocompressor of the present invention allows to troubleshoot the problem of transition to environment-friendly ozone-safe cooling agents, simultaneously, guaranteeing, as a minimum, the same efficiency (COP) that exists with the present systems that utilize the forbidden and transient cooling agents (Montreal Protocol). Simultaneously, the overall dimensions and weight of the system is decreased (up to 20 %) at the expense of reducing the overall dimensions of heat exchangers and exclusion of the oil system.
  • the decrease of the overall dimensions of heat exchangers is possible because of absence of oil in the system: there is no necessity to expand the area of heat interchange. The oil does not hinder the process of heat interchange. In addition to the above, the absence of low frequency noise simplifies the problem of sound insulation. Due to frequency start and variable-frequency control of the compressor, the system has no starting currents and, most important, the control band of cooling output comprises 20 - 100 %.
  • the air conditioning system with the pressurized integral centrifugal compressor stated in the given patent consists of the condenser, evaporator and a two-stage centrifugal compressor with the built-in disk electric motor installed between the stages. The compressor has a cooling system of the electric motor by a total flow of gas executed inside the compressor.
  • the exit of the compressor is bridged to an entrance of the condenser.
  • the exit of the condenser through two drosselling valves is attached to the entrance of the evaporator.
  • the exit of the evaporator is bridged to the compressor inlet.
  • the supply system of a cooling agent in shank bore of the compressor is formed by channels made directly in the body, shields of bearings and is specially constructed of the insert of the second stage. Through these channels, the gas leaves the first stage of compression and moves directly into the cooled cavity, and then to the entrance of the second stage of compression.
  • the vessel-separator in which the incomplete intermediate cooling implements, is set on the main line connecting the exit of the condenser to the entrance of the evaporator, between the two drosselling valves.
  • the drosselling valves are, in the essence, thermostatic expansion valves (TEN), which control the pressure and temperature of the cooling agent passing through them, opening and being closed at a returning signal that comes from sensors.
  • the sensor of the first drosselling valve is established directly on the exit of a drosselling unit. It controls intermediate pressure in cycle P *, which is determined by value calculated by conventionally for cycles with two-stage compression and incomplete intermediate cooling.
  • the sensor of the second drosselling valve is set on the main line of the exit of the cooling agent from the evaporator.
  • the vessel-separator is necessary for separation of the vapor-liquid mixture, which enters it after the first throttle into a coolant fluid and gas phase.
  • the air conditioning system is equipped with the device for the control of the speed of rotation of the engine depending on the temperature of the air coming out of the evaporator. Magnifying or reducing revolutions, we, thus, change the compression ratio of the compressor, implementing a necessary difference of pressure dependent on a difference between temperature of evaporation and condensing temperature.
  • the centrifugal compressor included in an air conditioning system consists of: two stages of compression installed in opposition on the unified shaft; two diffusers; two covers - gas collectors; details forming internal passages for the transfer of the cooling agent; two radial graphite seals; bearing assemblies; input and output of pipe lines; the built-in disk electric motor set on the shaft of the compressor; a stator fixed in the compressor casing.
  • the first and second stage of the compressor are bridged among themselves directly through channels in shank bore of the compressor, thus the external connection pipes are eliminated.
  • the disk electric motor is installed between the stages.
  • the disks of the rotor are set on the shaft of the compressor between the stages.
  • the shaft rests on bearing assemblies assembled on the basis of radial thrust bearings of rolling.
  • the stator is captured in the compressor casing and is set in relation to the shield of the bearing through a special assembly detail.
  • the special channels for passing of gas are made in the rotor and stator disks, and also in the stator frame.
  • the axle-load on the shaft of the compressor produced by the gas-dynamic of forces, is partially compensated for by a special design of seals.
  • the shaft is set free from thrusts with the help of advanced load executed at assembly on a floating support.
  • the preliminary load is formed by spiral pressured springs.
  • Air conditioning system (Fig.l) consists of the condenser 1, evaporator 2 and a two-stage centrifugal compressor (5) with the built-in disk electric motor (6) between stages (3) and (4).
  • the compressor (5) has a built-in cooling system of the electric motor (6).
  • the cooling of the engine (6) utilizes the total rate of gas flow that is sucked through the shank bore of the body (9) of the compressor (5).
  • the exit of the compressor, main line (14), is bridged to the entrance of the condenser (1).
  • the overcooled vapor-liquid mix moves through the pipe lines (15 and 18) and the first drosselling valve (16) into the vessel-separator (19).
  • the first drosselling valve (16) - TEN controls the intermediate pressure in the vessel-separator (19).
  • the cooled liquid moves through the second diOsselling valve (21) through the pipe lines (20 and 23) to the entrance of the evaporator (2).
  • the second drosselling valve (21) controls the degree of vapor overheating at the exit (26) of the evaporator (2).
  • the superheated steam moves through the pipe line (10) to the compressor inlet (5).
  • the air conditioning system is equipped with the device (24), that controls the rotation rate of the engine (6) according to the temperature of the air from the evaporator (2) according to the signal from the temperature sensor (25).
  • the centrifugal compressor (5) for an air conditioning system (Fig. 2) consists of two centrifugal stages of compression (3 and 4) with sprockets of a pump type (29 and 30) and channel diffusers (31 and 32), two covers - collectors (10 and 11) with nipples of entrance and exit (26 and 14).
  • the gas leaving the diffuser (31) of the first stage of compression (3) gathers in a cover - collector (10) and, then, on channels (13), made in a shield (35) of the first stage (3) and body (9) move in shank bore of the body (9), where the electric motor (6) is installed.
  • the stages of compression (3 and 4) are bridged among themselves without usage of external pipes.
  • the sprockets (29 and 30) are set on the shaft (37) oppositely.
  • the rotor disks (7) of the electric motor (6) are set on slide fit on the shaft (37) between sprockets (29 and 30).
  • the shaft (37) is established on radial thrust bearings (38), assembled in bearing assemblies.
  • the bearing (38) of the first stage (3) is firmly fixed in the shield of the first stage (35).
  • the bearing (38) of the second stage (4) is a floating support.
  • the inner ring of the bearing (38) of the second stage (4) is firmly fixed on the shaft, and preliminary load is applied to the outer ring, created at the expense of contraction of spiral springs (40) assembled in a sleeve (39). Because of this preliminary load and the thrust arising from it, the working angle of the radial thrust bearing is set. Besides, the preliminary load compensates for the axial thrust produced by the compressor's operation and directed against the preliminary load.
  • the stator (8) is fixed with adjusting screws in the body (9) and is set in relation to the shield by means of an additional adjusting ring.
  • the channels for passage of the refrigerating gas are made in the rotor and stator disks (7 and 8), and also in the stator frame (8).
  • the design of the compressor is accomplished in such a manner that the gas sucked through the body (9) removes the heat not only from the engine, but also from the bearing assemblies.
  • the installation diagram of seals (41 and 42) is selected.
  • the radial grooves of the seal (42) of the second stage (4) are made with a larger diameter, than radial grooves of the seal (41) of the first stages (41).
  • redistribution is reached of the axial and radial component of the moment of the forces which act on the shaft (37) being produced by the sprocket (42) towards the increase of the axial component, which compensates for the axle-load produced by the first stage (3).
  • the air conditioning system with the centrifugal compressor works as follows: The unit automatically generates a signal going on the electric motor (6) of the centrifugal compressor (5), the electric power is made, and a compressor's (5) rotor (7) with sprockets (29 and 30) start to be spun.
  • the vapor of a coolant from the evaporator (2) go through the pipe-line (24) on an entrance of a first stages wheel (29), where they are pressed, and warmed. Vapor of a coolant from a sprocket (29) fall in the first stages diffuser (31), in which the kinetic energy will be converted in potential, thus pressure is increased.
  • the coolant compressed in a second stage (4) compressors (5), through a nipple (14) is pumped in the condenser (1), in which the heat is drawn off from the coolant at constant pressure.
  • the condenser happen condensation and sub-cooling of refrigerant.
  • the drosseling valve is controlled by a signal coming from the sensor (17), placed on the exit of the vessel-separator (19).
  • the setup of the drosseling valve (16) is made so that it maintains the necessary intermediate pressure in the cycle.
  • the vessel-separator there is a process of the vapor-liquid mixture into liquid and gaseous phases.
  • the coolant fluid by the pipelines (20 and 23) through the second drosseling valve (21) moves into the evaporator (2).
  • the evaporator In the evaporator there is a heat interchange between the coolant fluid and cooled environment (air, water, or other heat transfer medium). There transpires boiling and overheating of the cooling agent.
  • the vapor of the cooling agent is pumped out from the evaporator by the compressor (5). Thus, the cycle closes.
  • the power of the refrigerating system is smoothly regulated by the change of the consumption of the cooling agent through the system and variation of the rotation speed of the rotor (37) of the compressor (5).
  • the change of the consumption is controlled by the drosseling valve, while the temperature of the cooling agent on escaping of the evaporator serves as the pilot signal for the valve.
  • the signal comes from the temperature sensor (22).
  • the alteration of the speed of rotation of the rotor is controlled by the device (25), while the temperature of the air on leaving the evaporator serves as the pilot signal for it (2), this temperature is defined by the temperature sensor (26).
  • the pressurized integral centrifugal compressor with the built-in disk electric motor of the present invention due to the high efficiency of stages of compression, electric motor, effective system of cooling, simplicity of the design and utilization of high speed rolling contact bearings, can be applied, ter alia in the following fields: 1 ) air conditioning systems with the power of 7- 10 kW;
  • the compressor can be used as an air compressor, including for turbo-supercharging.
  • Figs. 4, 5, 6, and 7 represent an illustration of the motor. The openings, or spaces through which the cooling gas may flow are marked therein by arrows.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Power Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention porte sur un système de réfrigération comportant un condenseur (1), un détendeur (21), un évaporateur (2) et un compresseur (5) centrifuge à deux étages entraîné par un moteur (6) électrique sans collecteur à disque de soupape intégré. Le gaz réfrigérant passant du premier étage (3) au deuxième étage (4) du compresseur emprunte des passages intérieurs au moteur (6) ce qui en assure le refroidissement. Le détendeur (21) est régulé par la pression et la température du réfrigérant quittant l'évaporateur (2) et la vitesse du moteur (6) est régulée par la température de l'air à la sortie de l'évaporateur (2).
PCT/RU2001/000561 2000-12-19 2001-12-18 Turbocompresseur monolithique WO2002050481A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2002230324A AU2002230324A1 (en) 2000-12-19 2001-12-18 Refrigerating system with an integrated turbocompressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IL140407 2000-12-19
IL14040700A IL140407A0 (en) 2000-12-19 2000-12-19 Integrated turbocompressor

Publications (1)

Publication Number Publication Date
WO2002050481A1 true WO2002050481A1 (fr) 2002-06-27

Family

ID=11074948

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/RU2001/000561 WO2002050481A1 (fr) 2000-12-19 2001-12-18 Turbocompresseur monolithique

Country Status (3)

Country Link
AU (1) AU2002230324A1 (fr)
IL (1) IL140407A0 (fr)
WO (1) WO2002050481A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1544409A1 (fr) * 2002-08-20 2005-06-22 Honda Giken Kogyo Kabushiki Kaisha Dispositif de moteur-generateur
EP1612916A1 (fr) * 2004-06-28 2006-01-04 General Electric Company Machine électrique tournante refroidie à l'air pressurisé et méthode pour actionner la machine
WO2011014934A1 (fr) 2009-08-03 2011-02-10 Atlas Copco Airpower Système de turbocompresseur
US8156757B2 (en) 2006-10-06 2012-04-17 Aff-Mcquay Inc. High capacity chiller compressor
US8397534B2 (en) 2008-03-13 2013-03-19 Aff-Mcquay Inc. High capacity chiller compressor
CN103312087A (zh) * 2012-03-16 2013-09-18 珠海格力电器股份有限公司 电机及包括该电机的空调
CN110768446A (zh) * 2019-11-19 2020-02-07 珠海格力电器股份有限公司 一种轮毂电机散热装置、轮毂电机散热系统及车辆
US11274679B2 (en) 2017-02-14 2022-03-15 Danfoss A/S Oil free centrifugal compressor for use in low capacity applications

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3447335A (en) * 1967-09-22 1969-06-03 John D Ruff Variable capacity centrifugal heat pump
US3859815A (en) * 1973-10-12 1975-01-14 Maekawa Seisakusho Kk Two-stage compression apparatus
US5334898A (en) * 1991-09-30 1994-08-02 Dymytro Skybyk Polyphase brushless DC and AC synchronous machines
US5396779A (en) * 1990-09-14 1995-03-14 Nartron Corporation Environmental control system
WO1999065133A1 (fr) * 1998-06-10 1999-12-16 Smith Technology Development Llc Machine electrique a champ axial
US6070421A (en) 1996-04-18 2000-06-06 Samjin Co., Ltd. 5 or 8 kW refrigerating system and centrifugal compressor assembly for said system
WO2000049296A1 (fr) * 1999-02-18 2000-08-24 Nauchno-Issledovatelsky Institut Nizkikh Temperatur Pri Mai (Moskovskom Aviatsionnom Institute-Technicheskom Universitete) Unite de compresseur centrifuge et moteur electrique

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3447335A (en) * 1967-09-22 1969-06-03 John D Ruff Variable capacity centrifugal heat pump
US3859815A (en) * 1973-10-12 1975-01-14 Maekawa Seisakusho Kk Two-stage compression apparatus
US5396779A (en) * 1990-09-14 1995-03-14 Nartron Corporation Environmental control system
US5334898A (en) * 1991-09-30 1994-08-02 Dymytro Skybyk Polyphase brushless DC and AC synchronous machines
US6070421A (en) 1996-04-18 2000-06-06 Samjin Co., Ltd. 5 or 8 kW refrigerating system and centrifugal compressor assembly for said system
WO1999065133A1 (fr) * 1998-06-10 1999-12-16 Smith Technology Development Llc Machine electrique a champ axial
WO2000049296A1 (fr) * 1999-02-18 2000-08-24 Nauchno-Issledovatelsky Institut Nizkikh Temperatur Pri Mai (Moskovskom Aviatsionnom Institute-Technicheskom Universitete) Unite de compresseur centrifuge et moteur electrique

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1544409A1 (fr) * 2002-08-20 2005-06-22 Honda Giken Kogyo Kabushiki Kaisha Dispositif de moteur-generateur
EP1544409A4 (fr) * 2002-08-20 2005-10-05 Honda Motor Co Ltd Dispositif de moteur-generateur
EP1612916A1 (fr) * 2004-06-28 2006-01-04 General Electric Company Machine électrique tournante refroidie à l'air pressurisé et méthode pour actionner la machine
US8156757B2 (en) 2006-10-06 2012-04-17 Aff-Mcquay Inc. High capacity chiller compressor
US8397534B2 (en) 2008-03-13 2013-03-19 Aff-Mcquay Inc. High capacity chiller compressor
WO2011014934A1 (fr) 2009-08-03 2011-02-10 Atlas Copco Airpower Système de turbocompresseur
US9470238B2 (en) 2009-08-03 2016-10-18 Atlas Copco Airpower, Naamloze Vennootschap Electric motor having segmented stator windings
CN103312087A (zh) * 2012-03-16 2013-09-18 珠海格力电器股份有限公司 电机及包括该电机的空调
US11274679B2 (en) 2017-02-14 2022-03-15 Danfoss A/S Oil free centrifugal compressor for use in low capacity applications
EP3361104B1 (fr) * 2017-02-14 2022-03-30 Danfoss A/S Compresseur centrifuge sans huile à utiliser dans des applications de faible capacité
CN110768446A (zh) * 2019-11-19 2020-02-07 珠海格力电器股份有限公司 一种轮毂电机散热装置、轮毂电机散热系统及车辆

Also Published As

Publication number Publication date
IL140407A0 (en) 2002-02-10
AU2002230324A1 (en) 2002-07-01

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