CN110645191A - Centrifugal compressor - Google Patents

Centrifugal compressor Download PDF

Info

Publication number
CN110645191A
CN110645191A CN201910480193.8A CN201910480193A CN110645191A CN 110645191 A CN110645191 A CN 110645191A CN 201910480193 A CN201910480193 A CN 201910480193A CN 110645191 A CN110645191 A CN 110645191A
Authority
CN
China
Prior art keywords
rotary shaft
rotor
housing
resolver
support portion
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.)
Pending
Application number
CN201910480193.8A
Other languages
Chinese (zh)
Inventor
冈崎和贵
铃木润也
森英文
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.)
Toyota Industries Corp
Original Assignee
Toyoda Automatic Loom Works 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 Toyoda Automatic Loom Works Ltd filed Critical Toyoda Automatic Loom Works Ltd
Publication of CN110645191A publication Critical patent/CN110645191A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/001—Testing thereof; Determination or simulation of flow characteristics; Stall or surge detection, e.g. condition monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/004—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by varying driving speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/053—Shafts
    • 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
    • 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
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/058—Bearings magnetic; electromagnetic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M8/00—Fuel cells; Manufacture thereof
    • H01M8/04—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/96—Preventing, counteracting or reducing vibration or noise
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/30—Hydrogen technology
    • Y02E60/50—Fuel cells

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Sustainable Development (AREA)
  • Electrochemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Manufacturing & Machinery (AREA)
  • Fluid Mechanics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

The invention provides a centrifugal compressor, which restrains vibration of a rotating shaft. The radius of the 2 nd radial support part (14b) is made larger than the rotation radius of the resolver rotor (31). Therefore, even if the motor rotor (17) and the resolver rotor (31) are fixed to the rotating shaft (14) before the rotating shaft (14) is assembled to the housing (13), the resolver rotor (31) can pass through the inside of the 2 nd radial bearing (22) when the rotating shaft (14) is assembled to the housing (13). Therefore, before the rotating shaft (14) is assembled to the housing (13), the motor rotor (17) and the resolver rotor (31) can be fixed to the rotating shaft (14), and the weight distribution of the motor rotor (17) or the resolver rotor (31) in the circumferential direction can be adjusted, thereby adjusting the rotation balance of the rotating shaft (14).

Description

Centrifugal compressor
Technical Field
The present invention relates to a centrifugal compressor.
Background
In recent years, a vehicle equipped with a fuel cell system including a fuel cell stack that generates electric power by chemically reacting hydrogen as a fuel gas with oxygen contained in air as an oxidant gas has been put to practical use. As disclosed in patent document 1, for example, the fuel cell system includes a centrifugal compressor that compresses air to be supplied to a fuel cell stack. The centrifugal compressor includes a housing, a rotating shaft housed in the housing, an electric motor housed in the housing and rotating the rotating shaft, an impeller coupled to one end of the rotating shaft and driven by the rotation of the rotating shaft to compress air, and a radial bearing supporting the rotating shaft to be rotatable in a radial direction of the rotating shaft with respect to the housing. The electric motor has a motor rotor fixed to the rotating shaft and a motor stator fixed to the housing. In order to detect the rotation angle of the motor rotor of the electric motor, for example, a resolver (resolver) as described in patent document 2 is used. The resolver includes a resolver rotor fixed to the rotating shaft and a resolver stator fixed to the housing.
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent application No. 2010-144537
Patent document 2: japanese patent laid-open publication No. 2017-158395
Disclosure of Invention
Problems to be solved by the invention
Since the rotary shaft of the centrifugal compressor rotates at a high speed of, for example, 8 ten thousand rpm or more, if a resolver is provided to the rotary shaft of the centrifugal compressor, the rotational balance of the rotary shaft is easily lost, and vibration is easily generated.
In a centrifugal compressor, a resolver may be disposed in a casing at an end portion opposite to an impeller in an axial direction of a rotating shaft in order to facilitate arrangement of resolver wiring drawn from a coil of a resolver stator in the casing. In this case, the resolver rotor is fixed to the other end portion of the rotating shaft opposite to the impeller. Here, when the resolver rotor is fixed to the rotating shaft before the rotating shaft is assembled to the housing, there are cases where: when the rotary shaft is assembled to the housing, the resolver rotor interferes with the radial bearing, and the rotary shaft cannot be assembled to the housing. Therefore, the resolver rotor is fixed to the other end portion of the rotating shaft opposite to the impeller after the rotating shaft is assembled to the housing.
For example, it is conceivable to adjust the rotational balance of the rotating shaft in advance by adjusting the variation in the weight distribution in the circumferential direction of the motor rotor in a state where the motor rotor is fixed to the rotating shaft before the rotating shaft is assembled to the housing. However, if the resolver rotor is fixed to the rotating shaft after the rotating shaft is assembled to the housing, even if the rotational balance of the rotating shaft is adjusted by adjusting the weight distribution of the motor rotor in the circumferential direction before the rotating shaft is assembled to the housing, the rotational balance of the rotating shaft is broken by the resolver rotor, and vibration of the rotating shaft is likely to occur.
The present invention has been made to solve the above problems, and an object thereof is to provide a centrifugal compressor capable of suppressing vibration of a rotary shaft.
Means for solving the problems
A centrifugal compressor for solving the above problems includes: a housing; a rotating shaft housed in the housing; an electric motor having a motor rotor fixed to the rotary shaft and a motor stator fixed to the housing, and rotating the rotary shaft; an impeller coupled to one end of the rotating shaft and driven by rotation of the rotating shaft to compress a fluid; a radial bearing that supports the rotary shaft to be rotatable in a radial direction of the rotary shaft with respect to the housing; and a resolver having a resolver rotor fixed to the rotating shaft and a resolver stator fixed to the casing, the resolver rotor being fixed to the other end portion of the rotating shaft on the opposite side to the impeller, and detecting a rotation angle of the motor rotor, wherein the rotating shaft has a radial support portion rotatably supported by the radial bearing, and a radius of the radial support portion is larger than a rotation radius of the resolver rotor.
Thus, even if the motor rotor is fixed to the rotary shaft and the resolver rotor is fixed to the other end portion of the rotary shaft opposite to the impeller before the rotary shaft is assembled to the housing, the resolver rotor can pass through the inside of the radial bearing when the rotary shaft is assembled to the housing. Therefore, before the rotating shaft is assembled to the housing, the rotating balance of the rotating shaft can be adjusted by fixing the motor rotor to the rotating shaft and fixing the resolver rotor to the rotating shaft, and adjusting the weight distribution of the motor rotor or the resolver rotor in the circumferential direction. Therefore, since the rotating shaft can be assembled to the housing after the rotational balance of the rotating shaft is adjusted in a state where the resolver rotor is fixed to the rotating shaft, vibration of the rotating shaft can be suppressed.
In the above centrifugal compressor, preferably: the rotary shaft is provided with a thrust bearing that rotatably supports the rotary shaft in an axial direction of the rotary shaft with respect to the housing, the rotary shaft has a thrust support portion rotatably supported by the thrust bearing, the thrust support portion is located closer to the impeller than the resolver rotor, the motor rotor, and the radial support portion in the axial direction of the rotary shaft, and an outer diameter of the radial support portion is larger than an outer diameter of a motor rotor core of the motor rotor and smaller than an inner diameter of a motor stator core of the motor stator.
Thus, even if the motor rotor is fixed to the rotary shaft and the resolver rotor is fixed to the rotary shaft before the rotary shaft is assembled to the housing, the radial support portion can pass through the inside of the motor stator core and the motor rotor core can pass through the inside of the radial bearing when the rotary shaft is assembled to the housing. Therefore, when the rotary shaft is assembled to the housing, the rotary shaft can be passed through the inside of the radial bearing and the inside of the motor stator core from the end portion on the resolver rotor side. Further, since the thrust support portion is located closer to the impeller than the resolver rotor, the motor rotor, and the radial support portion in the axial direction of the rotating shaft, the rotating shaft can be assembled to the housing even if the rotating shaft has the thrust support portion before the rotating shaft is assembled to the housing. Therefore, before the rotating shaft is assembled to the housing, the weight distribution in the circumferential direction of the motor rotor or the resolver rotor can be adjusted in a state where the motor rotor and the resolver rotor are fixed to the rotating shaft and the rotating shaft has the thrust bearing portion, thereby adjusting the rotation balance of the rotating shaft.
In the above centrifugal compressor, preferably: the shaft multiple angle of the rotary transformer rotor is 1 multiple angle or 2 multiple angle.
When the shaft multiple angle of the resolver rotor is set to 1 multiple angle (1X) or 2 multiple angle (2X), the rotation angle of the motor rotor of the electric motor can be detected with high accuracy. Since the resolver rotor has a shape in which the weight distribution in the circumferential direction of the resolver rotor becomes unbalanced as the shaft multiple angle of the resolver rotor becomes smaller, the rotation balance is easily broken in the rotating shaft to which the resolver rotor having a shaft multiple angle of 1 multiple angle (1X) or 2 multiple angle (2X) is fixed. However, by applying the present invention, vibration of the rotating shaft can be suppressed even if the shaft multiple angle of the resolver rotor is 1 multiple angle (1X) or 2 multiple angle (2X).
ADVANTAGEOUS EFFECTS OF INVENTION
According to the present invention, vibration of the rotating shaft can be suppressed.
Drawings
Fig. 1 (a) is a schematic configuration diagram of a fuel cell system according to embodiment 1, and fig. 1 (b) is a front view of a resolver rotor.
Fig. 2 (a) is a view schematically showing a state before the rotary shaft is assembled to the housing, and fig. 2 (b) is a view schematically showing a state after the rotary shaft is assembled to the housing.
Fig. 3 is a schematic configuration diagram of the fuel cell system in embodiment 2.
Fig. 4 (a) is a view schematically showing a state before the rotary shaft is assembled to the housing, and fig. 4 (b) is a view schematically showing a state after the rotary shaft is assembled to the housing.
Description of the reference numerals
12 … centrifugal compressor, 13 … casing, 14 … rotating shaft, 14a … radial bearing 1 as radial bearing, 14b … radial bearing 2 as radial bearing, 15 … electric motor, 16 … impeller, 17 … motor rotor, 17a … motor rotor core, 18 … motor stator, 18a … motor stator core, 21 … radial bearing 1 as radial bearing, 22 … radial bearing 2 as radial bearing, 23 … thrust bearing, 24 … thrust bearing, 30 … resolver, 31 … resolver rotor, 32 … resolver stator.
Detailed Description
(embodiment 1)
Hereinafter, embodiment 1 in which the centrifugal compressor is embodied will be described with reference to fig. 1 and 2. The centrifugal compressor compresses air, which is a fluid to be supplied to a fuel cell stack of the fuel cell system, as an oxidant gas. The fuel cell system of the present embodiment is mounted on a vehicle such as a fuel cell vehicle, for example.
As shown in fig. 1 (a), the fuel cell system 10 includes a fuel cell stack 11 and a centrifugal compressor 12 that compresses air. Air compressed by the centrifugal compressor 12 is supplied to the fuel cell stack 11. The fuel cell stack 11 has, for example, a plurality of unit cells (cells). Each unit cell is formed by laminating an oxygen electrode, a hydrogen electrode, and an electrolyte membrane disposed between the two electrodes. The fuel cell stack 11 chemically reacts hydrogen as a fuel gas with oxygen contained in air to generate electric power. The oxidizing gas may be any gas as long as it contains oxygen.
The fuel cell stack 11 is electrically connected to a running motor, not shown. The running motor is driven by electric power generated by the fuel cell stack 11 as an electric power source. The power of the travel motor is transmitted to the axle via a power transmission mechanism, not shown, and the vehicle travels at a vehicle speed corresponding to the accelerator opening degree of the accelerator pedal.
Since only about 2 oxygen is present in the air, which is useful for power generation of the fuel cell stack 11, about 8 oxygen of the air supplied to the fuel cell stack 11 is not useful for power generation of the fuel cell stack 11 and is discharged from the fuel cell stack 11 as exhaust gas.
The fuel cell stack 11 has a supply port 11a to which air is supplied, an exhaust port 11b through which air is exhausted as exhaust gas, and an air flow path 11c connecting the supply port 11a and the exhaust port 11 b. In the air flow path 11c, the air supplied from the supply port 11a flows toward the discharge port 11 b.
The centrifugal compressor 12 includes a casing 13, a rotary shaft 14 housed in the casing 13, an electric motor 15 housed in the casing 13 and rotating the rotary shaft 14, and an impeller 16 housed in the casing 13 and coupled to the rotary shaft 14 and driven by the rotation of the rotary shaft 14 to compress air. The impeller 16 is connected to one end of the rotary shaft 14 and rotates integrally with the rotary shaft 14. The rotary shaft 14 of the centrifugal compressor 12 rotates at a high speed of, for example, 8 ten thousand rpm or more.
The electric motor 15 includes a cylindrical motor rotor 17 fixed to the rotary shaft 14 and a cylindrical motor stator 18 fixed to the housing 13. The motor rotor 17 is disposed inside the motor stator 18 and rotates integrally with the rotating shaft 14. The motor rotor 17 includes a cylindrical motor rotor core 17a attached to and stopped by the rotary shaft 14, and a plurality of permanent magnets (not shown) provided on the motor rotor core 17 a. The motor stator 18 surrounds the motor rotor 17. The motor stator 18 includes a cylindrical motor stator core 18a fixed to the housing 13, and a coil 18b wound around the motor stator core 18 a. Then, when a current flows from a battery, not shown, to the coil 18b, the motor rotor 17 rotates integrally with the rotary shaft 14. Thereby, the impeller 16 rotates integrally with the rotary shaft 14, and the impeller 16 compresses air.
The housing 13 has an intake port 13a for taking in air and an exhaust port 13b for exhausting air. The fuel cell system 10 further includes a compressor flow path 20 a. The compressor flow path 20a is constituted by, for example, piping. One end of the compressor flow path 20a is open to the atmosphere, and the other end of the compressor flow path 20a is connected to the suction port 13 a. Then, air from the outside flows through the compressor flow path 20a and is sucked into the suction port 13 a. The impeller 16 compresses air sucked from the suction port 13 a. Then, the air compressed by the impeller 16 is discharged from the discharge port 13 b.
The fuel cell system 10 includes a supply flow path 20b connecting the centrifugal compressor 12 and the fuel cell stack 11. The supply channel 20b is constituted by a pipe, for example. One end of the supply channel 20b is connected to the discharge port 13b, and the other end of the supply channel 20b is connected to the supply port 11 a. The air discharged from the discharge port 13b flows through the supply passage 20b and is supplied to the supply port 11 a.
The fuel cell system 10 includes a discharge flow path 20 c. The discharge flow path 20c is formed of, for example, a pipe. One end of the discharge flow path 20c is connected to the discharge port 11b, and the other end of the discharge flow path 20c is open to the atmosphere. The exhaust gas discharged from the discharge port 11b flows through the discharge flow path 20c and is discharged to the atmosphere.
The centrifugal compressor 12 includes a 1 st radial bearing 21 and a 2 nd radial bearing 22 as cylindrical radial bearings that support the rotary shaft 14 so as to be rotatable in the radial direction of the rotary shaft 14 with respect to the housing 13. In the present embodiment, the 1 st radial bearing 21 and the 2 nd radial bearing 22 are disposed on both sides across the electric motor 15 in the axial direction of the rotating shaft 14. The 1 st radial bearing 21 is located closer to the impeller 16 than the electric motor 15. The 2 nd radial bearing 22 is located on the opposite side of the electric motor 15 from the impeller 16.
The rotary shaft 14 includes a 1 st radial support portion 14a as a cylindrical radial support portion rotatably supported by the 1 st radial bearing 21. The rotary shaft 14 has a 2 nd radial support portion 14b as a cylindrical radial support portion rotatably supported by the 2 nd radial bearing 22. The 1 st radial support portion 14a and the 2 nd radial support portion 14b are provided on both sides of the rotary shaft 14 across the electric motor 15. The 1 st and 2 nd radial support portions 14a and 14b are a part of the rotation shaft 14, and rotate integrally with the rotation shaft 14. The 1 st radial bearing 21 is fixed to the housing 13 in a state of surrounding the 1 st radial support portion 14a, and the 2 nd radial bearing 22 is fixed to the housing 13 in a state of surrounding the 2 nd radial support portion 14 b. The outer diameter R1 of the 1 st radial support portion 14a is the same as the outer diameter R2 of the 2 nd radial support portion 14 b. Thus, the radius of the 1 st radial support portion 14a is the same as the radius of the 2 nd radial support portion 14 b.
The 1 st radial bearing 21 supports the rotary shaft 14 in contact with the 1 st radial support portion 14a until the rotation speed of the electric motor 15 (the rotary shaft 14) reaches a predetermined value, and the 2 nd radial bearing 22 supports the rotary shaft 14 in contact with the 2 nd radial support portion 14b until the rotation speed of the electric motor 15 reaches a predetermined value. When the rotation speed of the electric motor 15 reaches a predetermined value, the 1 st radial support portion 14a floats up with respect to the 1 st radial bearing 21 due to the dynamic pressure generated between the 1 st radial support portion 14a and the 1 st radial bearing 21, and the 1 st radial bearing 21 supports the rotary shaft 14 without contacting the 1 st radial support portion 14 a. When the rotation speed of the electric motor 15 reaches a predetermined value, the 2 nd radial support portion 14b floats up with respect to the 2 nd radial bearing 22 due to the dynamic pressure generated between the 2 nd radial support portion 14b and the 2 nd radial bearing 22, and the 2 nd radial bearing 22 supports the rotary shaft 14 without contacting the 2 nd radial support portion 14 b.
The centrifugal compressor 12 further includes a flat annular thrust bearing 23 that supports the rotary shaft 14 so as to be rotatable in the axial direction of the rotary shaft 14 with respect to the housing 13. The thrust bearings 23 are disposed two by two on the impeller 16 side of the electric motor 15 in the axial direction of the rotary shaft 14 and between the 1 st radial bearing 21 and the impeller 16. Two thrust bearings 23 are supported by the housing 13.
The rotary shaft 14 has a flat annular thrust support portion 24 rotatably supported by two thrust bearings 23. The thrust bearing portion 24 is provided between the impeller 16 and the 1 st radial bearing portion 14a of the rotary shaft 14. The thrust support portion 24 is sandwiched between the two thrust bearings 23 in the axial direction of the rotating shaft 14. Therefore, the two thrust bearings 23 are disposed so as to sandwich the thrust support portion 24 in the axial direction of the rotary shaft 14. In the present embodiment, the thrust support portion 24 is a ring member that is a separate member from the rotary shaft 14. The thrust support portion 24 is fixed by being press-fitted to the rotary shaft 14, for example, and rotates integrally with the rotary shaft 14.
Until the rotation speed of the electric motor 15 (the rotary shaft 14) reaches a predetermined value, each thrust bearing 23 supports the rotary shaft 14 in contact with the thrust support portion 24. When the rotation speed of the electric motor 15 reaches a predetermined value, the thrust support portion 24 floats up on the thrust bearings 23 due to the dynamic pressures generated between the thrust support portion 24 and the thrust bearings 23, and the thrust bearings 23 support the rotary shaft 14 without coming into contact with the thrust support portion 24.
The centrifugal compressor 12 includes a resolver 30 that detects a rotation angle of the motor rotor 17. The resolver 30 includes a cylindrical resolver rotor 31 fixed to the rotary shaft 14 and a cylindrical resolver stator 32 fixed to the housing 13.
The resolver rotor 31 is fixed to the other end of the rotary shaft 14 opposite to the impeller 16. In the present embodiment, the impeller 16, the thrust support portion 24, the 1 st radial support portion 14a, the motor rotor core 17a, the 2 nd radial support portion 14b, and the resolver rotor 31 are arranged in this order from one end portion to the other end portion of the rotary shaft 14. Therefore, the thrust bearing portion 24 is located closer to the impeller 16 than the rotary transformer rotor 31, the motor rotor 17, the 1 st radial bearing portion 14a, and the 2 nd radial bearing portion 14b in the axial direction of the rotary shaft 14.
The resolver rotor 31 is disposed inside the resolver stator 32 and rotates integrally with the rotating shaft 14. The resolver stator 32 surrounds the resolver rotor 31. The resolver stator 32 includes a cylindrical resolver stator core 32a fixed to the case 13, and a coil 32b wound around the resolver stator core 32 a. A resolver wiring 32c is drawn from the coil 32b of the resolver stator 32. The resolver wiring 32c is electrically connected to a control device not shown. Then, by the rotation of the resolver rotor 31, a resolver signal formed by a 2-phase output in which the rotation of the resolver rotor 31 is detected is sent from the coil 32b to the control device via the resolver wiring 32 c.
The control device calculates a target current value for setting the rotation speed of the electric motor 15 to a target rotation speed based on the resolver signal. The target rotation speed means: the command rotational speed transmitted from the fuel cell system 10 to the control device is determined in accordance with the required amount of power generation required for the fuel cell stack 11 based on the operation state of the accelerator pedal or the like. Then, the control device controls the driving of the electric motor 15 so that the rotation speed of the electric motor 15 becomes the target rotation speed.
As shown in fig. 1 (b), the resolver rotor 31 has an insertion hole 31a through which the rotary shaft 14 is inserted. The insertion hole 31a has a perfect circular shape. The axial center of the insertion hole 31a coincides with the axial center L1 of the rotary shaft 14. Therefore, the insertion hole 31a has a circular hole shape centered on the axial center L1 of the rotary shaft 14.
The outer peripheral surface of the resolver rotor 31 includes a separating portion 31b farthest from the axial center L1 of the rotary shaft 14 in the radial direction of the rotary shaft 14, and an approaching portion 31c closest to the axial center L1 of the rotary shaft 14 in the radial direction of the rotary shaft 14. The separated portion 31b and the adjacent portion 31c are circumferentially separated from each other by 180 degrees. The outer peripheral surface of the resolver rotor 31 is formed in a non-perfect circular shape in which the radius from the axial center L1 of the rotation shaft 14 gradually decreases from the separated portion 31b toward the approaching portion 31 c. Therefore, the separated portion 31b is a portion of the outer peripheral surface of the resolver rotor 31 having the largest radius from the axial center L1 of the rotating shaft 14, and the adjacent portion 31c is a portion of the outer peripheral surface of the resolver rotor 31 having the smallest radius from the axial center L1 of the rotating shaft 14. The thickness of the resolver rotor 31 decreases from the separation portion 31b toward the approach portion 31 c. The resolver rotor 31 having the above-described configuration has an axial multiple angle of 1 (1X).
The outer diameter R1 of the 1 st radial support portion 14a and the outer diameter R2 of the 2 nd radial support portion 14b are larger than the outer diameter R3 of a virtual circle C1 passing through the separation portion 31b and centered on the axial center L1 of the rotary shaft 14. The radius of the imaginary circle C1 is the rotation radius of the resolver rotor 31. Therefore, the radius of the 1 st radial support portion 14a and the radius of the 2 nd radial support portion 14b are larger than the rotation radius of the resolver rotor 31. Further, the outer diameter R3 of the imaginary circle C1 is smaller than the outer diameter R4 of the motor rotor core 17 a. Further, the outer diameter R1 of the 1 st radial support portion 14a and the outer diameter R2 of the 2 nd radial support portion 14b are smaller than the outer diameter R4 of the motor rotor core 17 a.
Next, the operation of embodiment 1 will be described.
As shown in fig. 2 (a), in the centrifugal compressor 12 having the above-described configuration, before the rotary shaft 14 is assembled to the housing 13, the rotational balance of the rotary shaft 14 is adjusted in a state where the motor rotor 17 is fixed to the rotary shaft 14 and the resolver rotor 31 is fixed to the other end portion of the rotary shaft 14. The rotation balance of the rotating shaft 14 is adjusted by adjusting the variation in the weight distribution in the circumferential direction of the motor rotor 17 and the variation in the weight distribution in the circumferential direction of the resolver rotor 31. After the rotational balance of the rotary shaft 14 is adjusted, the rotary shaft 14 is assembled to the housing 13.
The 1 st radial bearing 21 is fixed in advance to the inside of the 1 st housing component 41 constituting a part of the housing 13, and the motor stator 18 and the 2 nd radial bearing 22 are fixed in advance to the inside of the 2 nd housing component 42 constituting a part of the housing 13 and coupled to the 1 st housing component 41.
As shown in fig. 2 (b), when the rotary shaft 14 is assembled to the housing 13, the end of the rotary shaft 14 opposite to the resolver rotor 31 is inserted into the first housing component 41. At this time, the end of the rotary shaft 14 opposite to the resolver rotor 31 passes through the inside of the 1 st radial bearing 21. The rotary shaft 14 is assembled to the 1 st housing component 41 in a state where the 1 st radial support portion 14a is surrounded by the 1 st radial bearing 21.
The end of the rotary shaft 14 on the resolver rotor 31 side is inserted into the 2 nd housing assembly 42. At this time, since the outer diameter R3 of the imaginary circle C1 passing through the separating portion 31b and centered on the axial center L1 of the rotary shaft 14 is smaller than the outer diameter R4 of the motor rotor core 17a, the resolver rotor 31 passes inside the motor stator core 18 a. Further, since the outer diameter R2 of the 2 nd radial support portion 14b is smaller than the outer diameter R4 of the motor rotor core 17a, the 2 nd radial support portion 14b passes through the inside of the motor stator core 18 a. Further, the outer diameter R2 of the 2 nd radial support portion 14b is larger than the outer diameter R3 of a virtual circle C1 passing through the separation portion 31b and centered on the axial center L1 of the rotary shaft 14, that is, the radius of the 2 nd radial support portion 14b is larger than the rotation radius of the resolver rotor 31, and therefore, the resolver rotor 31 passes inside the 2 nd radial bearing 22. The rotary shaft 14 is assembled to the 2 nd housing component 42 in a state where the motor rotor 17 is surrounded by the motor stator 18 and the 2 nd radial support portion 14b is surrounded by the 2 nd radial bearing 22. Thus, the rotary shaft 14 is assembled to the housing 13.
In the present embodiment, the impeller 16 and the thrust support portion 24 are fixed to the rotary shaft 14 after the rotary shaft 14 is assembled to the housing 13. A not-shown case constituent constituting a part of the case 13 and having the resolver stator 32 fixed thereto in advance is coupled to an end of the 2 nd case constituent 42 opposite to the 1 st case constituent 41 in a state where the resolver rotor 31 is surrounded by the resolver stator 32.
In embodiment 1, the following effects can be obtained.
(1-1) since the rotary shaft 14 of the centrifugal compressor 12 rotates at a high speed of 8 ten thousand rpm or more, in order to detect the rotation angle of the motor rotor 17 with high accuracy, the resolver 30 of the present embodiment sets the axial multiple angle of the resolver rotor 31 to 1 multiple angle. Since the resolver rotor 31 has a shape in which the weight distribution in the circumferential direction of the resolver rotor 31 becomes unbalanced as the shaft multiple angle of the resolver rotor 31 becomes smaller, the rotation balance is easily broken and vibration is easily generated in the rotary shaft 14 to which the resolver rotor 31 having a small shaft multiple angle is fixed.
Then, the radius of the 2 nd radial support portion 14b is made larger than the rotation radius of the resolver rotor 31. Thus, even if the motor rotor 17 is fixed to the rotary shaft 14 and the resolver rotor 31 is fixed to the other end portion of the rotary shaft 14 opposite to the impeller 16 before the rotary shaft 14 is assembled to the housing 13, the resolver rotor 31 can pass through the inside of the 2 nd radial bearing 22 when the rotary shaft 14 is assembled to the housing 13. Therefore, before the rotary shaft 14 is assembled to the housing 13, the rotational balance of the rotary shaft 14 can be adjusted by fixing the motor rotor 17 to the rotary shaft 14 and fixing the resolver rotor 31 to the rotary shaft 14 to adjust the weight distribution of the motor rotor 17 or the resolver rotor 31 in the circumferential direction. Therefore, since the rotary shaft 14 can be assembled to the housing 13 after the rotational balance of the rotary shaft 14 is adjusted in a state where the resolver rotor 31 is fixed to the rotary shaft 14, the vibration of the rotary shaft 14 can be suppressed.
(embodiment 2)
Hereinafter, embodiment 2 in which the centrifugal compressor is embodied will be described with reference to fig. 3 and 4. In the embodiments described below, the same components as those in embodiment 1 described above are denoted by the same reference numerals, and the redundant description thereof will be omitted or simplified.
As shown in fig. 3, the outer diameter R1 of the 1 st radial support portion 14a and the outer diameter R2 of the 2 nd radial support portion 14b are larger than the outer diameter R4 of the motor rotor core 17a and smaller than the inner diameter R5 of the motor stator core 18 a.
Next, the operation of embodiment 2 will be described.
As shown in fig. 4 (a), in the centrifugal compressor 12 having the above-described configuration, before the rotary shaft 14 is assembled to the housing 13, the rotational balance of the rotary shaft 14 is adjusted in a state where the motor rotor 17 and the resolver rotor 31 are fixed to the rotary shaft 14 and the thrust support portion 24 is further fixed to the rotary shaft 14. Further, the two thrust bearings 23 are supported by the thrust support portion 24. After the rotational balance of the rotary shaft 14 is adjusted, the rotary shaft 14 is assembled to the housing 13. The 1 st radial bearing 21, the motor stator 18, and the 2 nd radial bearing 22 are fixed in advance inside a housing forming body 43 that forms a part of the housing 13.
As shown in fig. 4 (b), when the rotary shaft 14 is assembled to the housing 13, the end of the rotary shaft 14 on the resolver rotor 31 side is inserted into the housing assembly 43. At this time, the outer diameter R1 of the 1 st radial support portion 14a is larger than the outer diameter R3 of the virtual circle C1 passing through the separating portion 31b and centered on the axial center L1 of the rotary shaft 14, that is, the radius of the 1 st radial support portion 14a is larger than the rotation radius of the resolver rotor 31, and therefore, the resolver rotor 31 passes inside the 1 st radial bearing 21. Further, since the outer diameter R3 of the imaginary circle C1 is smaller than the outer diameter R4 of the motor rotor core 17a, the resolver rotor 31 passes through the inside of the motor stator core 18 a. Further, since the outer diameter R2 of the 2 nd radial support portion 14b is larger than the outer diameter R3 of the virtual circle C1, that is, the radius of the 2 nd radial support portion 14b is larger than the rotation radius of the resolver rotor 31, the resolver rotor 31 passes through the inside of the 2 nd radial bearing 22.
In addition, the 2 nd radial support portion 14b passes through the inside of the 1 st radial bearing 21. Further, since the outer diameter R2 of the 2 nd radial support portion 14b is larger than the outer diameter R4 of the motor rotor core 17a and smaller than the inner diameter R5 of the motor stator core 18a, the 2 nd radial support portion 14b passes through the inside of the motor stator core 18 a. Further, since the outer diameter R1 of the 1 st radial support portion 14a is larger than the outer diameter R4 of the motor rotor core 17a, the motor rotor core 17a passes through the inside of the 1 st radial bearing 21. The rotary shaft 14 is assembled to the housing assembly 43 in a state where the 1 st radial support portion 14a is surrounded by the 1 st radial bearing 21, the motor rotor 17 is surrounded by the motor stator 18, and the 2 nd radial support portion 14b is surrounded by the 2 nd radial bearing 22. Thus, the rotary shaft 14 is assembled to the housing 13.
In the present embodiment, the impeller 16 is fixed to the rotary shaft 14 after the rotary shaft 14 is assembled to the housing 13. A casing structure, not shown, which constitutes a part of the casing 13 and to which the resolver stator 32 is fixed in advance is coupled to an end of the casing structure 43 opposite to the impeller 16 in a state where the resolver rotor 31 is surrounded by the resolver stator 32.
In embodiment 2, the following effects can be obtained in addition to the effects similar to effect (1-1) of embodiment 1.
(2-1) the outer diameter R1 of the 1 st radial bearing 14a and the outer diameter R2 of the 2 nd radial bearing 14b are larger than the outer diameter R4 of the motor rotor core 17a and smaller than the inner diameter R5 of the motor stator core 18 a. Thus, even if the motor rotor 17 and the resolver rotor 31 are fixed to the rotary shaft 14 before the rotary shaft 14 is assembled to the housing 13, the 2 nd radial support portion 14b can pass through the inside of the motor stator core 18a and the motor rotor core 17a can pass through the inside of the 1 st radial bearing 21 when the rotary shaft 14 is assembled to the housing 13. Therefore, when the rotary shaft 14 is assembled to the housing 13, the rotary shaft 14 can be passed through the inside of the 1 st radial bearing 21, the inside of the motor stator core 18a, and the inside of the 2 nd radial bearing 22 from the end portion on the resolver rotor 31 side. The thrust support portion 24 is located closer to the impeller 16 than the rotary transformer rotor 31, the motor rotor 17, the 1 st radial support portion 14a, and the 2 nd radial support portion 14b in the axial direction of the rotary shaft 14. Therefore, even if the rotary shaft 14 has the thrust support portion 24 before the rotary shaft 14 is assembled to the housing 13, the rotary shaft 14 can be assembled to the housing 13. Therefore, before the rotary shaft 14 is assembled to the housing 13, the weight distribution in the circumferential direction of the motor rotor 17 or the resolver rotor 31 can be adjusted in a state where the motor rotor 17 and the resolver rotor 31 are fixed to the rotary shaft 14 and the rotary shaft 14 has the thrust bearing portion 24, thereby adjusting the rotation balance of the rotary shaft 14.
The above embodiments may be modified and implemented as follows. The above embodiments and the following modifications can be combined and implemented within a range not technically contradictory to each other.
In each of the above embodiments, the axial multiple angle of the resolver rotor 31 may be 2 multiple angles (2X), and may be 3 multiple angles (3X) or more.
In each of the above embodiments, the 1 st and 2 nd radial bearings 21 and 22 may be a sliding bearing or a rolling bearing.
In each of the above embodiments, the centrifugal compressor 12 may not be a compressor that compresses the oxidant gas to be supplied to the fuel cell stack 11 of the fuel cell system 10, and may be a compressor that compresses a refrigerant as a fluid, for example, used in an air conditioner.
In each of the above embodiments, the fuel cell system 10 may be mounted on a vehicle or other than the vehicle.

Claims (3)

1. A centrifugal compressor is provided with:
a housing;
a rotating shaft housed in the housing;
an electric motor having a motor rotor fixed to the rotary shaft and a motor stator fixed to the housing, and rotating the rotary shaft;
an impeller coupled to one end of the rotating shaft and driven by rotation of the rotating shaft to compress a fluid;
a radial bearing that supports the rotary shaft to be rotatable in a radial direction of the rotary shaft with respect to the housing; and
a resolver having a resolver rotor fixed to the rotating shaft and a resolver stator fixed to the housing, and detecting a rotation angle of the motor rotor,
the resolver rotor is fixed to the other end portion of the rotating shaft opposite to the impeller,
the centrifugal compressor is characterized in that it is provided with,
the rotating shaft has a radial support portion rotatably supported by the radial bearing, and the radial support portion has a radius larger than a rotation radius of the resolver rotor.
2. The centrifugal compressor according to claim 1,
a thrust bearing for rotatably supporting the rotary shaft in the axial direction of the rotary shaft with respect to the housing,
the rotary shaft has a thrust support portion rotatably supported by the thrust bearing, the thrust support portion being located closer to the impeller than the resolver rotor, the motor rotor, and the radial support portion in an axial direction of the rotary shaft,
the radial support portion has an outer diameter larger than an outer diameter of a motor rotor core of the motor rotor and smaller than an inner diameter of a motor stator core of the motor stator.
3. The centrifugal compressor according to claim 1 or 2,
the shaft multiple angle of the rotary transformer rotor is 1 multiple angle or 2 multiple angle.
CN201910480193.8A 2018-06-07 2019-06-04 Centrifugal compressor Pending CN110645191A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-109452 2018-06-07
JP2018109452A JP2019210899A (en) 2018-06-07 2018-06-07 Centrifugal compressor

Publications (1)

Publication Number Publication Date
CN110645191A true CN110645191A (en) 2020-01-03

Family

ID=68651907

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201910480193.8A Pending CN110645191A (en) 2018-06-07 2019-06-04 Centrifugal compressor

Country Status (4)

Country Link
US (1) US20190376521A1 (en)
JP (1) JP2019210899A (en)
CN (1) CN110645191A (en)
DE (1) DE102019115088A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7484767B2 (en) 2021-02-22 2024-05-16 日本精工株式会社 Direct Drive Motor

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070178345A1 (en) * 2006-02-02 2007-08-02 Kenji Takeda Fuel cell module
US20070246002A1 (en) * 2006-03-30 2007-10-25 Jtekt Corporation Compressor for fuel cell
US20110194954A1 (en) * 2008-10-14 2011-08-11 Takatoshi Sakata Electric pump unit
US20120243177A1 (en) * 2011-03-21 2012-09-27 Hamilton Sundstrand Corporation Indirect bleed air cooling of a fan motor controller
US8461953B1 (en) * 2009-08-18 2013-06-11 Marvin W. Ward System, method and apparatus for transformer cooling
US20130343927A1 (en) * 2012-06-22 2013-12-26 Aktiebolaget Skf Electric centrifugal compressor for vehicles
CN103758766A (en) * 2012-06-22 2014-04-30 Skf磁性机械技术公司 Compact electric centrifugal compressor
US9013179B2 (en) * 2011-03-28 2015-04-21 Minebea Co., Ltd. Angle detecting device
CN107035703A (en) * 2016-02-04 2017-08-11 江苏亿美电器有限公司 A kind of electronic sensor fills air releasing device automatically
CN107508407A (en) * 2017-08-24 2017-12-22 江苏韩森自动车股份有限公司 A kind of high pressure wheel hub motor waterproof management system used for electric vehicle

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070178345A1 (en) * 2006-02-02 2007-08-02 Kenji Takeda Fuel cell module
US20070246002A1 (en) * 2006-03-30 2007-10-25 Jtekt Corporation Compressor for fuel cell
US20110194954A1 (en) * 2008-10-14 2011-08-11 Takatoshi Sakata Electric pump unit
US8461953B1 (en) * 2009-08-18 2013-06-11 Marvin W. Ward System, method and apparatus for transformer cooling
US20120243177A1 (en) * 2011-03-21 2012-09-27 Hamilton Sundstrand Corporation Indirect bleed air cooling of a fan motor controller
US9013179B2 (en) * 2011-03-28 2015-04-21 Minebea Co., Ltd. Angle detecting device
US20130343927A1 (en) * 2012-06-22 2013-12-26 Aktiebolaget Skf Electric centrifugal compressor for vehicles
CN103758766A (en) * 2012-06-22 2014-04-30 Skf磁性机械技术公司 Compact electric centrifugal compressor
CN107035703A (en) * 2016-02-04 2017-08-11 江苏亿美电器有限公司 A kind of electronic sensor fills air releasing device automatically
CN107508407A (en) * 2017-08-24 2017-12-22 江苏韩森自动车股份有限公司 A kind of high pressure wheel hub motor waterproof management system used for electric vehicle

Also Published As

Publication number Publication date
US20190376521A1 (en) 2019-12-12
DE102019115088A1 (en) 2019-12-12
JP2019210899A (en) 2019-12-12

Similar Documents

Publication Publication Date Title
CN108884757B (en) Pressure booster
JP4788351B2 (en) Fuel cell supercharger
EP2719875B1 (en) Structure and method for adjusting balance of supercharger built into electric motor
US8376722B2 (en) Electric compressor
CN104976146B (en) A kind of fuel battery engines directly drive air compressor with two-step supercharging
US7700207B2 (en) Turbocompressor shutdown mechanism
JP2007092646A (en) Supercharger for fuel cell
US20110164974A1 (en) Compressor and Method for Operating a Compressor and Fuel Cell Device with a Compressor
CN105829728B (en) The pressure charging system of multi-stage motor centrifugal compressor and internal combustion engine
KR102013371B1 (en) Bearing system for a turbocharger with an internal electric motor
CN111936754B (en) Thrust magnetic bearing and turbo compressor comprising same
US7559751B2 (en) Supercharger with electric motor
KR20100109720A (en) Permanent magnetic motor and fluid charger comprising the same
JP2007095485A (en) Fuel cell apparatus
JP2010144537A (en) Compressor for fuel cell
JP2010055816A (en) Fuel cell system
JP5108911B2 (en) Centrifugal compressor with thrust canceller mechanism
CN110645191A (en) Centrifugal compressor
JP2007270647A (en) Compressor for fuel cell
JP2006194221A (en) Anti-friction bearing fitment
US5501583A (en) Turbo vacuum pump
JP7190467B2 (en) fuel cell system
JP2007270651A (en) Compressor for fuel cell
JP2015048812A (en) Electric centrifugal compressor device and compressor motor control method
JP2019160726A (en) Fuel cell system

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
WD01 Invention patent application deemed withdrawn after publication

Application publication date: 20200103

WD01 Invention patent application deemed withdrawn after publication