US20150267709A1 - Motor-driven turbo compressor - Google Patents

Motor-driven turbo compressor Download PDF

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Publication number
US20150267709A1
US20150267709A1 US14/631,985 US201514631985A US2015267709A1 US 20150267709 A1 US20150267709 A1 US 20150267709A1 US 201514631985 A US201514631985 A US 201514631985A US 2015267709 A1 US2015267709 A1 US 2015267709A1
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US
United States
Prior art keywords
chamber
impeller
housing
refrigerant
motor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US14/631,985
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English (en)
Inventor
Nobuaki Hoshino
Toshiro Fujii
Hajime Kurita
Hironao Yokoi
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
Toyota Industries Corp
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Filing date
Publication date
Application filed by Toyota Industries Corp filed Critical Toyota Industries Corp
Assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI reassignment KABUSHIKI KAISHA TOYOTA JIDOSHOKKI ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KURITA, HAJIME, FUJII, TOSHIRO, HOSHINO, NOBUAKI, YOKOI, HIRONAO
Publication of US20150267709A1 publication Critical patent/US20150267709A1/en
Abandoned legal-status Critical Current

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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3223—Cooling devices using compression characterised by the arrangement or type of the compressor
    • 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5846—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling by injection
    • 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
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/167—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings
    • H02K5/1672—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings radially supporting the rotary shaft at both ends of the rotor
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans
    • 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
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K2205/00—Specific aspects not provided for in the other groups of this subclass relating to casings, enclosures, supports
    • H02K2205/03—Machines characterised by thrust bearings

Definitions

  • the present invention relates to a motor-driven turbo compressor.
  • Japanese Patent No. 4947405 discloses a conventional motor-driven turbo compressor (hereinafter referred to as compressor).
  • the compressor is adopted in a refrigeration circuit of an air-conditioning apparatus.
  • the compressor includes a housing, a rotating shaft, an electric motor, a first impeller, and a second impeller.
  • a first impeller chamber, a second impeller chamber, and a motor chamber are formed in this order in the axial direction from one end side toward the other end side.
  • first and second diffusers and first and second discharge chambers are formed.
  • the first discharge chamber communicates with the first impeller chamber via the first diffuser.
  • the second discharge chamber communicates with the second impeller chamber via the second diffuser.
  • first and second suction ports and a gas injection portion are formed.
  • the first suction port extends in the axial direction on the one end side of the housing and communicates with the first impeller chamber.
  • the second suction port communicates with the first discharge chamber on one end side and communicates with the second impeller chamber on the other end side.
  • the second suction port does not communicate with the motor chamber.
  • the gas injection portion communicates with the second suction port.
  • the refrigeration circuit includes, besides the compressor, a condenser, first and second expansion valves, an economizer, and an evaporator, which are connected by pipes to enable a refrigerant to circulate therethrough.
  • the economizer is arranged between the first expansion valve and the second expansion valve. While temporarily storing the refrigerant decompressed by the first expansion valve, the economizer cools the stored refrigerant.
  • the economizer is connected to the gas injection portion of the compressor by a pipe.
  • the rotating shaft is rotatably supported by the housing.
  • the electric motor is provided in the motor chamber and drives to rotate the rotating shaft.
  • the first impeller is coupled to one end of the rotating shaft.
  • the first impeller rotates in the first impeller chamber to thereby increase kinetic energy of a refrigerant in the first impeller chamber.
  • the first impeller converts the kinetic energy of the refrigerant into pressure energy through the first diffuser, and compresses the refrigerant, and discharges the compressed refrigerant to the first discharge chamber.
  • the second impeller is coupled to the other end of the rotating shaft.
  • the second impeller rotates in the second impeller chamber to thereby increase kinetic energy of the refrigerant in the second impeller chamber.
  • the second impeller converts the kinetic energy of the refrigerant into pressure energy through the second diffuser, and compresses the refrigerant, and discharges the compressed refrigerant to the second discharge chamber.
  • the compressor compresses the refrigerant in two stages. Specifically, the refrigerant is sucked from the first suction port. The refrigerant is discharged to the first discharge chamber through the first impeller chamber and the first diffuser, and circulates through the second suction port. Further, in the compressor, a gas-phase refrigerant in the economizer is supplied from the gas injection portion to the second suction port. In this way, in the compressor, the refrigerant discharged to the first discharge chamber and the gas-phase refrigerant in the economizer are mixed in the second suction port, and discharged to the second discharge chamber through the second impeller chamber and the second diffuser.
  • the electric motor can drive to rotate the rotating shaft at high speed. Therefore, deterioration in durability of the electric motor due to heat generation is concerned.
  • the refrigerant circulating through the second suction port is unnecessarily heated by passing from the electric motor having high temperature through the housing. Therefore, the temperature of the refrigerant rises when the refrigerant flows into the second impeller chamber from the second suction port. As a result, efficiency of the refrigeration circuit adopting the compressor is deteriorated.
  • the present invention has been devised in view of the circumstances in the past and an object of the invention is to provide a motor-driven turbo compressor that has high durability and is capable of surely improving efficiency of a refrigeration circuit.
  • the motor-driven turbo compressor of the invention is used in a refrigeration cycle and comprises: a housing; an electric motor provided in the housing; a rotating shaft driven to rotate by the electric motor; and a first impeller and a second impeller arranged on the rotating shaft at an interval in an axial direction of the rotating shaft.
  • a refrigerant is sucked from a first suction port, compressed by rotation of the first impeller, and discharged to a first discharge chamber provided on a radially outer circumference side of the first impeller.
  • the refrigerant through the first discharge chamber is sucked from a second suction port, compressed by rotation of the second impeller, and discharged to a second discharge chamber provided on a radially outer circumference side of the second impeller.
  • the first impeller, the second impeller, and the electric motor are arranged in the axial direction of the rotating shaft in this order.
  • a first chamber and a second chamber are formed at both ends in the axial direction of the electric motor in the housing and communicate with each other via a gap in the electric motor, and the first chamber is located close to the second impeller in the axial direction of the electric motor.
  • An intermediate pressure port is formed in the housing and connects the first chamber and the first discharge chamber.
  • An injection port connected to a gas-liquid separator of the refrigeration cycle is formed in the housing and communicates with the second chamber.
  • FIG. 1 is a sectional view showing a compressor in an embodiment.
  • FIG. 2 is a sectional view from a II-II direction in FIG. 1 according to the compressor of embodiment.
  • FIG. 3 is a sectional view from a III-III direction in FIG. 1 according to the compressor of embodiment.
  • FIG. 4 is a sectional view from the direction same as the direction in FIG. 2 according to the compressor of embodiment.
  • FIG. 5 is a sectional view from a V-V direction in FIG. 1 according to the compressor of embodiment.
  • a compressor in the embodiment is a motor-driven turbo compressor for a vehicle.
  • the compressor is mounted on a vehicle and used in a refrigeration cycle of an air conditioner for a vehicle.
  • the compressor in the embodiment includes a housing 1 , a rotating shaft 3 , an electric motor 5 , a first impeller 7 , and a second impeller 9 .
  • the housing 1 includes a front housing 11 , an end plate 13 , and a rear housing 15 .
  • the front housing 11 includes a first front housing 11 a, a second front housing 11 b, a third front housing 11 c, and a fourth front housing 11 d.
  • the first front housing 11 a, the second front housing 11 b, the third front housing 11 c, and the fourth front housing 11 d are joined in this order from the front end side toward the rear end side.
  • the front housing 11 is formed into a substantially cylindrical shape as a whole.
  • first and second impeller chambers 17 and 19 In the front housing 11 , first and second impeller chambers 17 and 19 , first and second diffusers 21 and 23 , first and second discharge chambers 25 and 27 , a motor chamber 29 , an intermediate pressure port 31 , a first boss 33 , first and second suction ports 35 and 37 , first and second communication paths 39 a and 39 b, a guide wall 41 , an injection port 43 , and a discharge port 45 are formed.
  • the first impeller chamber 17 is formed on the front end side of the front housing 11 . More specifically, the front end side of the first impeller chamber 17 is formed in the first front housing 11 a. The rear end side of the first impeller chamber 17 is formed in the second front housing 11 b. The first impeller chamber 17 is formed in a shape gradually expanding in diameter from the front end side toward the rear end side. The first impeller 7 is provided in the first impeller chamber 17 .
  • the second impeller chamber 19 is formed behind the first impeller chamber 17 in the front housing 11 . More specifically, the front end side of the second impeller chamber 17 is formed in the second front housing 11 b. The rear end side of the second impeller chamber 17 is formed in the third front housing 11 c.
  • the second impeller chamber 19 has a shape symmetric to the first impeller chamber 17 .
  • the second impeller chamber 19 is formed in a shape gradually contracting in diameter from the front end side toward the rear end side.
  • the second impeller 9 is provided in the second impeller chamber 19 .
  • a first shaft hole 47 a extending in the axial direction of the housing 1 is formed.
  • the first diffuser 21 is formed on the front end side of the second front housing 11 b and located on the outer circumference side of the first impeller chamber 17 .
  • the first diffuser 21 communicates with the first impeller chamber 17 in a largest diameter part of the first impeller chamber 17 .
  • the second diffuser 23 is formed on the front end side of the third front housing 11 c and located on the outer circumference side of the second impeller chamber 19 .
  • the second diffuser 23 communicates with the second impeller chamber 19 in a largest diameter part of the second impeller chamber 19 .
  • the second diffuser 23 is formed smaller in diameter than the first diffuser 21 .
  • the front end side of the first discharge chamber 25 is formed in the first front housing 11 a.
  • the rear end side of the first discharge chamber 25 is formed in the second front housing 11 b.
  • the first discharge chamber 25 is provided on a radially outer circumference side of the first impeller 7 .
  • the first discharge chamber 25 is located on the outer circumference side of the first diffuser 21 and communicates with the first diffuser 21 . Consequently, the first impeller chamber 17 and the first discharge chamber 25 communicate with each other through the first diffuser 21 .
  • the first discharge chamber 25 is formed into a spiral shape.
  • the first discharge chamber 25 is formed such that flow passage area gradually increases.
  • the front side of the second discharge chamber 27 is formed in the second front housing 11 b.
  • the rear end side of the second discharge chamber 27 is formed in the third front housing 11 c.
  • the second discharge chamber 27 is provided on a radially outer circumference side of the second impeller 9 .
  • the second discharge chamber 27 is located on the outer circumference side of the second diffuser 23 and communicates with the second diffuser 23 . Consequently, the second impeller chamber 19 and the second discharge chamber 27 communicate with each other through the second diffuser 23 .
  • the second discharge chamber 27 is formed into a spiral shape.
  • the second discharge chamber 27 is formed such that flow passage area gradually increases.
  • the second diffuser 23 is smaller in diameter than the first diffuser 21 . Therefore, as shown in FIG. 4 , the second discharge chamber 27 is located closer to the inner circumference of the front housing 11 than the first discharge chamber 25 . Further, as shown in FIG. 3 , the second discharge chamber 27 communicates with the discharge port 45 on the outer circumference side. The discharge port 45 extends in the radial direction of the housing 1 .
  • the motor chamber 29 is formed in the fourth front housing 11 d. Consequently, in the front housing 11 , the first impeller chamber 17 , the second impeller chamber 19 , and the motor chamber 29 are formed in this order from the front end side toward the rear end side.
  • the motor chamber 29 extends in the axial direction of the housing 1 and defined by the end plate 13 on the rear end side of the fourth front housing 11 d.
  • the intermediate pressure port 31 is formed to extend across the second to fourth front housings 11 b to 11 d in the axial direction of the housing 1 .
  • the front end side of the intermediate pressure port 31 communicates with the outer circumference side of the first discharge chamber 25 .
  • the rear end side of the intermediate pressure port 31 communicates with the motor chamber 29 .
  • the intermediate pressure port 31 and the discharge port 45 are formed in positions shifted in the radial direction.
  • the first boss 33 is formed on the front end side of the motor chamber 29 in the fourth front housing 11 d and extends toward the rear end side of the motor chamber 29 in the axial direction of the housing 1 .
  • a second shaft hole 47 b extending in the axial direction of the housing 1 is formed.
  • a first radial foil bearing 49 a is provided in the second shaft hole 47 b.
  • the first suction port 35 is formed on the front end side of the first front housing 11 a. That is, the first suction port 35 is located on the front end side of the housing 1 .
  • the first suction port 35 extends in the axial direction of the housing 1 .
  • the front end side of the first suction port 35 opens on the front end face of the first front housing 11 a.
  • the rear end side of the first suction port 35 communicates with the first impeller chamber 17 .
  • the second suction port 37 is formed to extend across the rear end side of the third front housing 11 c and the front end side of the fourth front housing 11 d.
  • the rear end side of the second suction port 37 communicates with the motor chamber 29 on the front end side of the first boss 33 .
  • the front end side of the second suction port 37 communicates with the second impeller chamber 19 .
  • the second suction port 37 communicates with the second shaft hole 47 b.
  • the second suction port 37 faces the rotating shaft 3 such that the refrigerant is brought into contact with the rotating shaft 3 .
  • Both of the first communication path 39 a and the second communication path 39 b are formed in the fourth front housing 11 d and extend from the front end side toward the rear end side of the motor chamber 29 in the axial direction of the housing 1 . More specifically, the first communication path 39 a and the second communication path 39 b are respectively located between the inner wall of the motor chamber 29 and a stator 5 a explained below. As shown in FIG. 5 , the first communication path 39 a and the second communication path 39 b are arranged to face each other across the electric motor 5 in the motor chamber 29 . It is possible to form only one of the first communication path 39 a and the second communication path 39 b in the fourth front housing 11 d. Further, three or more communication paths may be formed in the fourth front housing 11 d.
  • the guide wall 41 is formed on the front end side of the motor chamber 29 in the fourth front housing 11 d.
  • the guide wall 41 is formed further on the outer circumference side than the first boss 33 in the fourth front housing 11 d.
  • the guide wall 41 extends toward the rear end side of the motor chamber 29 in the axial direction of the housing 1 .
  • the injection port 43 is formed on the rear end side of the fourth front housing 11 d. As shown in FIG. 5 , the injection port 43 extends in the radial direction of the housing 1 with respect to the fourth front housing 11 d. That is, in the compressor, the first and second communication paths 39 a and 39 b extending in the axial direction of the housing 1 and the injection port 43 extending in the radial direction of the housing 1 do not face each other. Further, the injection port 43 is located at a position different from the intermediate pressure port 31 and the first and second communication paths 39 a and 39 b around the axis of the rotating shaft 3 .
  • the endplate 13 is joined to the rear end of the fourth front housing 11 d, that is, the rear end of the front housing 11 .
  • the rear end of the motor chamber 29 is defined by the end plate 13 .
  • a second boss 51 extending toward the motor chamber 29 in the axial direction of the housing 1 is formed.
  • a third shaft hole 47 c extending in the axial direction of the housing 1 is formed.
  • a second radial foil bearing 49 b is provided in the third shaft hole 47 c.
  • the rear housing 15 is located in the rear of the housing 1 and joined to the end plate 13 . That is, the rear housing 15 sandwiches the end plate 13 in conjunction with the front housing 11 .
  • first and second thrust foil bearings 53 a and 53 b and a support plate 55 are provided in the rear housing 15 .
  • the first thrust foil bearing 53 a is located on the front end side of the support plate 55 and sandwiched by the end plate 13 and the support plate 55 .
  • the second thrust foil bearing 53 b is located on the rear end side of the support plate 55 and sandwiched by the support plate 55 and the rear housing 15 .
  • the rotating shaft 3 includes a rotating shaft main body 30 a, a first small diameter portion 30 b located on the front end side of the rotating shaft main body 30 a, and a second small diameter portion 30 c located on the rear end side of the rotating shaft main body 30 .
  • the rotating shaft main body 30 a is formed in a largest diameter in the rotating shaft 3 .
  • both of the first and second small diameter portions 30 b and 30 c are formed smaller in diameter than the rotating shaft main body 30 a.
  • the first small diameter portion 30 b is formed in diameter smaller than the second small diameter portion 30 c.
  • the rotating shaft 3 is inserted through the housing 1 and is capable of rotating in the housing 1 .
  • the front end side of the rotating shaft main body 30 a is inserted through the second shaft hole 47 b and rotatably supported by the first radial foil bearing 49 a.
  • the rear end side of the rotating shaft main body 30 a is inserted through the third shaft hole 47 c and rotatably supported by the second radial foil bearing 49 b.
  • the first small diameter portion 30 b is inserted through the first shaft hole 47 a.
  • the rear end side of the first small diameter portion 30 b is located in the second suction port 37 .
  • the second small diameter portion 30 c is inserted through the support plate 55 in the rear housing 15 . Consequently, the second small diameter portion 30 c and further, the rotating shaft 3 are supported by the first and second thrust foil bearings 53 a and 53 b via the support plate 55 .
  • the electric motor 5 is provided in the motor chamber 29 .
  • the electric motor 5 includes a stator 5 a and a rotor 5 b. Since the electric motor 5 is provided in this way, the motor chamber 29 is defined into a first chamber 29 a and a second chamber 29 b respectively located at the axial direction both ends of the electric motor 5 .
  • the first chamber 29 a is located on the front end side in the axial direction of the electric motor 5 and is located closer to the second impeller chamber 19 than the stator 5 a and the rotor 5 b.
  • the second chamber 29 b is located on the rear end side in the axial direction of the electric motor 5 and is located on the opposite side of the second impeller chamber 19 with respect to the stator 5 a and the rotor 5 b, that is, closer to the end plate 13 than the stator 5 a and the rotor 5 b.
  • the first chamber 29 a communicates with the first discharge chamber 25 in the axial direction through the intermediate pressure port 31 . Further, the first chamber 29 a communicates with the second shaft hole 47 b and the second impeller chamber 19 through the second suction port 37 .
  • the second chamber 29 b communicates with the injection port 43 .
  • the stator 5 a is fixed to the inner wall of the motor chamber 29 .
  • the stator 5 a is electrically connected to a not-shown battery.
  • the rotor 5 b is located on the inner circumference side of the stator 5 a.
  • the rotor 5 b is arranged between the first boss 33 and the second boss 51 .
  • the rotor 5 b is fixed to the rotating shaft main body 30 a. Consequently, the rotor 5 b is capable of rotating integrally with the rotating shaft 3 on the inner circumference side of the stator 5 a.
  • a gap 5 c is provided between the stator 5 a and the rotor 5 b.
  • the first chamber 29 a and the second chamber 29 b communicate with each other through the gap 5 c.
  • the shapes of the stator 5 a and the rotor 5 b are shown in a simplified form in order to facilitate explanation.
  • the first impeller 7 is press-fitted into the front end side of the first small diameter portion 30 b and provided in the first impeller chamber 17 . Consequently, the first impeller 7 is capable of rotating in the first impeller chamber 17 according to the rotation of the rotating shaft 3 .
  • the first impeller 7 is formed in diameter smaller than the inner diameter of the motor chamber 29 .
  • the first impeller 7 is formed in a shape gradually expanding in diameter from the front end side toward the rear end side.
  • the rear end side of the first impeller 7 is formed as a large diameter portion 7 a. Further, a plurality of blades 70 are provided at a predetermined interval on the surface of the first impeller 7 .
  • the second impeller 9 is press-fitted into the rear end side of the first small diameter portion 30 b and provided in the second impeller chamber 19 . Consequently, the second impeller 9 is capable of rotating in the second impeller chamber 19 according to the rotation of the rotating shaft 3 .
  • the first impeller 7 , the second impeller 9 , and the electric motor 5 are arranged in this order in the axial direction of the rotating shaft 3 from the front end side toward the rear end side.
  • the second impeller 9 is also formed in diameter smaller than the inner diameter of the motor chamber 29 . Further, the second impeller 9 is formed to have the same size as the first impeller 7 .
  • the second impeller 9 is provided in the first small diameter portion 30 b such that a large diameter portion 9 a of the second impeller 9 is located on the front end side of the front housing 11 . Consequently, in the compressor, in the front housing 11 , the first impeller 7 and the second impeller 9 are arranged with the large diameter portion 7 a and the large diameter portion 9 a faced to each other. Further, a plurality of blades 90 are provided at a predetermined interval on the surface of the second impeller 9 . Note that the second impeller 9 may be formed in a smaller diameter than the first impeller 7 .
  • the refrigeration cycle 10 is configured by a condenser 101 , an expansion valve 102 , a receiver 103 , an evaporator 104 , and pipes 201 to 206 besides the compressor.
  • the receiver 103 corresponds to the gas-liquid separator in the present invention.
  • the receiver 103 includes a gas-liquid separation chamber 103 a.
  • an inlet 103 b, an outlet 103 c, and a gas outlet 103 d are formed in the receiver 103 .
  • the gas-liquid separation chamber 103 a separates a refrigerant flown into from the inlet 103 b into a gas-phase refrigerant and a liquid-phase refrigerant, and temporarily stores the liquid-phase refrigerant.
  • the liquid-phase refrigerant in the gas-liquid separation chamber 103 a flows out from the inside of the gas-liquid separation chamber 103 a through the outlet 103 c.
  • the gas-phase refrigerant in the gas-liquid separation chamber 103 a that is, an injection refrigerant flows out from the inside of the gas-liquid separation chamber 103 a through the gas outlet 103 d.
  • the refrigeration cycle 10 since the refrigeration cycle 10 is mounted on a vehicle, there is a strong demand for a reduction in the size of the refrigeration cycle 10 . Therefore, in the refrigeration cycle 10 , a device such as an economizer is not adopted to perform the gas-liquid separation of the refrigerant. Instead, the receiver 103 is adopted to perform the gas-liquid separation of the refrigerant.
  • the discharge port 45 of the compressor and the condenser 101 are connected by a pipe 201 .
  • the condenser 101 is connected to the expansion valve 102 by a pipe 202 .
  • the expansion valve 102 is connected to the inlet 103 b of the receiver 103 by a pipe 203 .
  • the outlet 103 c of the receiver 103 is connected to the evaporator 104 by a pipe 204 .
  • the evaporator 104 is connected to the first suction port 35 of the compressor by a pipe 205 .
  • the gas outlet 103 d of the receiver 103 is connected to the injection port 43 of the compressor by a pipe 206 . In this way, the gas-liquid separation chamber 103 a and the second chamber 29 b communicate with each other.
  • the stator 5 a rotates the rotor 5 b by electricity of motor 5 . Consequently, the rotating shaft 3 is driven to rotate around a rotational axis O in the housing 1 . Therefore, the first impeller 7 rotates in the first impeller chamber 17 . The second impeller 9 rotates in the second impeller chamber 19 .
  • a low-pressure refrigerant that passes through the evaporator 104 is sucked into the first suction port 35 through the pipe 205 and reaches the inside of the first impeller chamber 17 .
  • the first impeller 7 rotating in the first impeller chamber 17 increases kinetic energy of the refrigerant in the first impeller chamber 17 .
  • the first impeller 7 converts the kinetic energy of the refrigerant into pressure energy through the first diffuser 21 , and compresses the refrigerant, and discharges the compressed refrigerant to the first discharge chamber 25 . Consequently, the pressure of the refrigerant in the first discharge chamber 25 changes to an intermediate pressure.
  • the refrigerant having the intermediate pressure that is, an intermediate pressure refrigerant circulates from the first discharge chamber 25 to the first chamber 29 a through the intermediate pressure port 31 as indicated by a solid line arrow in the FIG. 1 .
  • the intermediate pressure port 31 extends in the axial direction of the housing 1 . Therefore, in the compressor, it is possible to reduce a body diameter even if the intermediate pressure port 31 is provided to cause the first discharge chamber 25 and the first chamber 29 a to communicate with each other.
  • the intermediate pressure refrigerant flown into the first chamber 29 a is guided to the first communication path 39 a and the second communication path 39 b by the guide wall 41 .
  • the intermediate pressure refrigerant circulates through the first communication path 39 a and the second communication path 39 b toward the second chamber 29 b.
  • the intermediate pressure refrigerant circulates from the first chamber 29 a to the second chamber 29 b in the axial direction of the housing 1 while cooling the stator 5 a.
  • the injection refrigerant separated by the gas-liquid separation chamber 103 a of the receiver 103 circulates through the pipe 206 and flows into the second chamber 29 b through the injection port 43 as indicated by an arrow in the FIG. 1 .
  • the injection port 43 extends in the radial direction of the housing 1
  • the injection refrigerant flows into the second chamber 29 b in the radial direction of the housing 1 , that is, a direction orthogonal to the intermediate pressure refrigerant circulating through the first and second communication paths 39 a and 39 b.
  • the compressor it is possible to suitably suppress a collision of the intermediate pressure refrigerant circulating through the first and second communication paths 39 a and 39 b and flowing into the second chamber 29 b and the injection refrigerant flowing into the second chamber 29 b from the injection port 43 . Consequently, in the compressor, the intermediate pressure refrigerant and the injection refrigerant suitably flow into the second chamber 29 b.
  • the intermediate pressure refrigerant and the injection refrigerant are mixed in the second chamber 29 b to be a mixed refrigerant.
  • the mixed refrigerant circulates through the gap 5 c between the stator 5 a and the rotor 5 b and circulates toward the first chamber 29 a.
  • the stator 5 a and the rotor 5 b are also cooled by the mixed refrigerant circulating through the gap 5 c.
  • the mixed refrigerant reaching the first chamber 29 a flows into the second suction port 37 .
  • the mixed refrigerant circulating through the second suction port 37 is sucked into the second impeller chamber 19 while coming into contact with the first small diameter portion 30 b of the rotating shaft 3 .
  • the compressor it is possible to cool the rotating shaft 3 with the mixed refrigerant circulating through the second suction port 37 .
  • the second impeller 9 rotating in the second impeller chamber 19 increases kinetic energy of the mixed refrigerant in the second impeller chamber 19 . Thereafter, the second impeller 9 converts the kinetic energy of the refrigerant into pressure energy through the second diffuser 23 , and compresses the refrigerant, and discharges the compressed refrigerant to the second discharge chamber 27 . In this way, in the compressor, the refrigerant sucked from the first suction port 35 is compressed in two stages, and the injection refrigerant as the mixed refrigerant also is compressed.
  • the electric motor 5 is cooled by the intermediate pressure refrigerant and the injection refrigerant.
  • the intermediate pressure refrigerant and the injection refrigerant circulate through the second suction port 37 as the mixed refrigerant.
  • the injection refrigerant since the injection refrigerant has low temperature, in the compressor, it is possible to suitably suppress a temperature rise of the mixed refrigerant when the mixed refrigerant flows into the second impeller chamber 19 from the second suction port 37 .
  • the injection refrigerant has high pressure compared with the refrigerant flowing into the first impeller chamber 17 from the first suction port 35 through the evaporator 104 . Therefore, in the compressor, it is possible to increase the pressure of the mixed refrigerant flowing into the second suction port 37 from the first chamber 29 a.
  • the compressor in the embodiment has high durability and can surely improve efficiency of the refrigeration circuit.
  • the first and second communication paths 39 a and 39 b are formed in the axial direction of the housing 1 . Therefore, in the compressor, even if the first and second communication paths 39 a and 39 b are provided to cause the first chamber 29 a and the second chamber 29 b to communicate with each other, it is possible to reduce a body diameter of the compressor. Further, in the compressor, the guide wall 41 is formed in the fourth front housing 11 d.
  • the compressor it is possible to suitably guide the intermediate pressure refrigerant to the first and second communication paths 39 a and 39 b while suitably preventing the intermediate pressure refrigerant from directly flowing into the second suction port 37 after flowing into the first chamber 29 a from the intermediate pressure port 31 .
  • both of the first impeller 7 and the second impeller 9 have diameters smaller than the inner diameter of the motor chamber 29 , it is possible to reduce the body diameter.
  • the first impeller 7 and the second impeller 9 are arranged with the large diameter portions 7 a and 9 a faced to each other. Therefore, in the compressor, a first thrust force generated on the first impeller 7 side and a second thrust force generated on the second impeller 9 side act to offset each other. A resultant force of the first and second thrust forces decreases. Therefore, in the compressor, it is possible to adopt the first and second thrust foil bearings 53 a and 53 b small in size and increase durability.

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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)
US14/631,985 2014-03-19 2015-02-26 Motor-driven turbo compressor Abandoned US20150267709A1 (en)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180328634A1 (en) * 2017-05-11 2018-11-15 Lg Electronics Inc. Turbo compressor
US20190055954A1 (en) * 2015-10-20 2019-02-21 Kabushiki Kaisha Toyota Jidoshokki Centrifugal compressor
US11359642B2 (en) 2018-07-20 2022-06-14 Ihi Corporation Electric compressor
US20230052135A1 (en) * 2021-08-16 2023-02-16 Turbowin Co., Ltd. Two-stage gas compressing apparatus with compressed-gas pressure-difference-use optimizing cooling unit to perform cooling using pressure difference
US20230167829A1 (en) * 2021-11-30 2023-06-01 Kabushiki Kaisha Toyota Jidoshokki Turbo fluid machine
US11698074B2 (en) 2020-05-08 2023-07-11 Lg Electronics Inc. Turbo compressor and turbo chiller including the same

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105736424B (zh) * 2016-04-19 2019-01-25 同济大学 一种车用燃料电池发动机的单级直驱增压离心式空压机
JP7103263B2 (ja) * 2019-02-20 2022-07-20 株式会社豊田自動織機 ターボ式流体機械
CN114641618B (zh) * 2019-09-23 2024-02-23 热力学公司 具有被构造成减小冷却流体压力的冷却回路和减压系统的集成式电机-压缩机单元

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2921446A (en) * 1956-11-02 1960-01-19 Carrier Corp Refrigeration machine
US3022638A (en) * 1959-05-06 1962-02-27 Carrier Corp Controls for refrigeration apparatus
JPH11294879A (ja) * 1998-02-16 1999-10-29 Daikin Ind Ltd 冷凍装置
US7591147B2 (en) * 2006-11-01 2009-09-22 Honeywell International Inc. Electric motor cooling jacket resistor
US7704056B2 (en) * 2007-02-21 2010-04-27 Honeywell International Inc. Two-stage vapor cycle compressor
WO2013011939A1 (ja) * 2011-07-21 2013-01-24 株式会社Ihi 電動モータ及びターボ圧縮機
WO2014038202A1 (ja) * 2012-09-07 2014-03-13 三菱重工業株式会社 輸送機械用の電動圧縮機

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3733701B2 (ja) * 1997-06-26 2006-01-11 ダイキン工業株式会社 ターボ機械
KR100279599B1 (ko) * 1997-12-26 2001-02-01 구자홍 터보압축기
JP4947405B2 (ja) * 2005-12-28 2012-06-06 株式会社Ｉｈｉ ターボ圧縮機
JP4973976B2 (ja) * 2006-02-13 2012-07-11 株式会社Ｉｈｉ 密閉型ターボ圧縮冷凍機
US8061151B2 (en) * 2009-05-18 2011-11-22 Hamilton Sundstrand Corporation Refrigerant compressor
WO2012131770A1 (ja) * 2011-03-30 2012-10-04 川崎重工業株式会社 ターボ冷凍機
JP2013011939A (ja) 2011-06-28 2013-01-17 Mitsubishi Motors Corp 運転支援装置
JP6056270B2 (ja) 2012-08-28 2017-01-11 ダイキン工業株式会社 ターボ圧縮機及びターボ冷凍機

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2921446A (en) * 1956-11-02 1960-01-19 Carrier Corp Refrigeration machine
US3022638A (en) * 1959-05-06 1962-02-27 Carrier Corp Controls for refrigeration apparatus
JPH11294879A (ja) * 1998-02-16 1999-10-29 Daikin Ind Ltd 冷凍装置
US7591147B2 (en) * 2006-11-01 2009-09-22 Honeywell International Inc. Electric motor cooling jacket resistor
US7704056B2 (en) * 2007-02-21 2010-04-27 Honeywell International Inc. Two-stage vapor cycle compressor
WO2013011939A1 (ja) * 2011-07-21 2013-01-24 株式会社Ihi 電動モータ及びターボ圧縮機
US20140127050A1 (en) * 2011-07-21 2014-05-08 Ihi Corporation Electrical motor and turbo compressor
WO2014038202A1 (ja) * 2012-09-07 2014-03-13 三菱重工業株式会社 輸送機械用の電動圧縮機

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20190055954A1 (en) * 2015-10-20 2019-02-21 Kabushiki Kaisha Toyota Jidoshokki Centrifugal compressor
US20180328634A1 (en) * 2017-05-11 2018-11-15 Lg Electronics Inc. Turbo compressor
US11002287B2 (en) * 2017-05-11 2021-05-11 Lg Electronics Inc. Turbo compressor having an inner passage for cooling the motor
US11359642B2 (en) 2018-07-20 2022-06-14 Ihi Corporation Electric compressor
US11698074B2 (en) 2020-05-08 2023-07-11 Lg Electronics Inc. Turbo compressor and turbo chiller including the same
US20230052135A1 (en) * 2021-08-16 2023-02-16 Turbowin Co., Ltd. Two-stage gas compressing apparatus with compressed-gas pressure-difference-use optimizing cooling unit to perform cooling using pressure difference
US20230167829A1 (en) * 2021-11-30 2023-06-01 Kabushiki Kaisha Toyota Jidoshokki Turbo fluid machine

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CN104929956B (zh) 2017-04-12
CN104929956A (zh) 2015-09-23
KR101720855B1 (ko) 2017-03-28
JP2015178790A (ja) 2015-10-08
KR20150109275A (ko) 2015-10-01
EP2921707A1 (en) 2015-09-23

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