US20150267709A1 - Motor-driven turbo compressor - Google Patents
Motor-driven turbo compressor Download PDFInfo
- 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
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 89
- 238000002347 injection Methods 0.000 claims abstract description 34
- 239000007924 injection Substances 0.000 claims abstract description 34
- 238000005057 refrigeration Methods 0.000 claims description 14
- 239000007788 liquid Substances 0.000 claims description 13
- 238000000926 separation method Methods 0.000 description 10
- 239000011888 foil Substances 0.000 description 9
- 239000012071 phase Substances 0.000 description 4
- 239000007791 liquid phase Substances 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
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
-
- 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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Abstract
In the compressor of the present invention, an intermediate pressure port through which a first discharge chamber and a first chamber communicate with each other is formed in a front housing. In the front housing, an injection port through which a receiver and a second chamber communicate with each other is formed. An intermediate pressure refrigerant discharged to the first discharge chamber flows into the first chamber through an intermediate pressure port. An injection refrigerant separated by the receiver flows into the second chamber. In the compressor, it is possible to cool an electric motor with the intermediate pressure refrigerant and the injection refrigerant. The intermediate pressure refrigerant and the injection refrigerant circulate through a second suction port as a mixed refrigerant.
Description
- 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.
- In the housing, 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. Further, in the housing, 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. Further, in the housing, 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. Thereafter, 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. Thereafter, 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.
- However, in the compressor as explained above, 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. In the compressor, 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.
- Other aspects and advantages of the present invention will be apparent from the embodiments disclosed in the following description and the attached drawings, the illustrations exemplified in the drawings, and the concept of the invention disclosed in the entire description and drawings.
-
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 inFIG. 1 according to the compressor of embodiment. -
FIG. 4 is a sectional view from the direction same as the direction inFIG. 2 according to the compressor of embodiment. -
FIG. 5 is a sectional view from a V-V direction inFIG. 1 according to the compressor of embodiment. - An embodiment embodying the present invention is explained below with reference to the drawings. 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.
- As shown in
FIG. 1 , the compressor in the embodiment includes ahousing 1, a rotatingshaft 3, anelectric motor 5, afirst impeller 7, and asecond impeller 9. - The
housing 1 includes afront housing 11, anend plate 13, and arear housing 15. - The
front housing 11 includes afirst front housing 11 a, asecond front housing 11 b, athird front housing 11 c, and afourth front housing 11 d. In thefront housing 11, thefirst front housing 11 a, the secondfront housing 11 b, thethird front housing 11 c, and thefourth front housing 11 d are joined in this order from the front end side toward the rear end side. Thefront housing 11 is formed into a substantially cylindrical shape as a whole. - In the
front housing 11, first andsecond impeller chambers second diffusers second discharge chambers motor chamber 29, anintermediate pressure port 31, afirst boss 33, first andsecond suction ports second communication paths guide wall 41, aninjection port 43, and adischarge port 45 are formed. - The
first impeller chamber 17 is formed on the front end side of thefront housing 11. More specifically, the front end side of thefirst impeller chamber 17 is formed in thefirst front housing 11 a. The rear end side of thefirst impeller chamber 17 is formed in the secondfront housing 11 b. Thefirst impeller chamber 17 is formed in a shape gradually expanding in diameter from the front end side toward the rear end side. Thefirst impeller 7 is provided in thefirst impeller chamber 17. - The
second impeller chamber 19 is formed behind thefirst impeller chamber 17 in thefront housing 11. More specifically, the front end side of thesecond impeller chamber 17 is formed in the secondfront housing 11 b. The rear end side of thesecond impeller chamber 17 is formed in the thirdfront housing 11 c. Thesecond impeller chamber 19 has a shape symmetric to thefirst impeller chamber 17. Thesecond impeller chamber 19 is formed in a shape gradually contracting in diameter from the front end side toward the rear end side. Thesecond impeller 9 is provided in thesecond impeller chamber 19. In the secondfront housing 11 b, afirst shaft hole 47 a extending in the axial direction of thehousing 1 is formed. - The
first diffuser 21 is formed on the front end side of the secondfront housing 11 b and located on the outer circumference side of thefirst impeller chamber 17. Thefirst diffuser 21 communicates with thefirst impeller chamber 17 in a largest diameter part of thefirst impeller chamber 17. Thesecond diffuser 23 is formed on the front end side of the thirdfront housing 11 c and located on the outer circumference side of thesecond impeller chamber 19. Thesecond diffuser 23 communicates with thesecond impeller chamber 19 in a largest diameter part of thesecond impeller chamber 19. Thesecond diffuser 23 is formed smaller in diameter than thefirst diffuser 21. - The front end side of the
first discharge chamber 25 is formed in the firstfront housing 11 a. The rear end side of thefirst discharge chamber 25 is formed in the secondfront housing 11 b. Thefirst discharge chamber 25 is provided on a radially outer circumference side of thefirst impeller 7. As shown inFIG. 2 , thefirst discharge chamber 25 is located on the outer circumference side of thefirst diffuser 21 and communicates with thefirst diffuser 21. Consequently, thefirst impeller chamber 17 and thefirst discharge chamber 25 communicate with each other through thefirst diffuser 21. Thefirst discharge chamber 25 is formed into a spiral shape. Thefirst discharge chamber 25 is formed such that flow passage area gradually increases. - As shown in
FIG. 1 , the front side of thesecond discharge chamber 27 is formed in the secondfront housing 11 b. The rear end side of thesecond discharge chamber 27 is formed in the thirdfront housing 11 c. Thesecond discharge chamber 27 is provided on a radially outer circumference side of thesecond impeller 9. As shown inFIG. 3 , thesecond discharge chamber 27 is located on the outer circumference side of thesecond diffuser 23 and communicates with thesecond diffuser 23. Consequently, thesecond impeller chamber 19 and thesecond discharge chamber 27 communicate with each other through thesecond diffuser 23. Like thefirst discharge chamber 25, thesecond discharge chamber 27 is formed into a spiral shape. Thesecond discharge chamber 27 is formed such that flow passage area gradually increases. - Here, as explained above, the
second diffuser 23 is smaller in diameter than thefirst diffuser 21. Therefore, as shown inFIG. 4 , thesecond discharge chamber 27 is located closer to the inner circumference of thefront housing 11 than thefirst discharge chamber 25. Further, as shown inFIG. 3 , thesecond discharge chamber 27 communicates with thedischarge port 45 on the outer circumference side. Thedischarge port 45 extends in the radial direction of thehousing 1. - As shown in
FIG. 1 , themotor chamber 29 is formed in the fourthfront housing 11 d. Consequently, in thefront housing 11, thefirst impeller chamber 17, thesecond impeller chamber 19, and themotor chamber 29 are formed in this order from the front end side toward the rear end side. Themotor chamber 29 extends in the axial direction of thehousing 1 and defined by theend plate 13 on the rear end side of the fourthfront housing 11 d. - The
intermediate pressure port 31 is formed to extend across the second to fourthfront housings 11 b to 11 d in the axial direction of thehousing 1. As shown inFIG. 2 , in the secondfront housing 11 b, the front end side of theintermediate pressure port 31 communicates with the outer circumference side of thefirst discharge chamber 25. On the other hand, as shown inFIG. 1 , in the fourthfront housing 11 d, the rear end side of theintermediate pressure port 31 communicates with themotor chamber 29. Further, as shown inFIG. 4 , in thefront housing 11, theintermediate pressure port 31 and thedischarge port 45 are formed in positions shifted in the radial direction. - As shown in
FIG. 1 , thefirst boss 33 is formed on the front end side of themotor chamber 29 in the fourthfront housing 11 d and extends toward the rear end side of themotor chamber 29 in the axial direction of thehousing 1. In thefirst boss 33, asecond shaft hole 47 b extending in the axial direction of thehousing 1 is formed. In thesecond shaft hole 47 b, a first radial foil bearing 49 a is provided. - The
first suction port 35 is formed on the front end side of the firstfront housing 11 a. That is, thefirst suction port 35 is located on the front end side of thehousing 1. Thefirst suction port 35 extends in the axial direction of thehousing 1. The front end side of thefirst suction port 35 opens on the front end face of the firstfront housing 11 a. The rear end side of thefirst suction port 35 communicates with thefirst impeller chamber 17. - The
second suction port 37 is formed to extend across the rear end side of the thirdfront housing 11 c and the front end side of the fourthfront housing 11 d. The rear end side of thesecond suction port 37 communicates with themotor chamber 29 on the front end side of thefirst boss 33. On the other hand, the front end side of thesecond suction port 37 communicates with thesecond impeller chamber 19. Further, thesecond suction port 37 communicates with thesecond shaft hole 47 b. Thesecond suction port 37 faces therotating shaft 3 such that the refrigerant is brought into contact with therotating shaft 3. - Both of the
first communication path 39 a and thesecond communication path 39 b are formed in the fourthfront housing 11 d and extend from the front end side toward the rear end side of themotor chamber 29 in the axial direction of thehousing 1. More specifically, thefirst communication path 39 a and thesecond communication path 39 b are respectively located between the inner wall of themotor chamber 29 and astator 5 a explained below. As shown inFIG. 5 , thefirst communication path 39 a and thesecond communication path 39 b are arranged to face each other across theelectric motor 5 in themotor chamber 29. It is possible to form only one of thefirst communication path 39 a and thesecond communication path 39 b in the fourthfront housing 11 d. Further, three or more communication paths may be formed in the fourthfront housing 11 d. - As shown in
FIG. 1 , theguide wall 41 is formed on the front end side of themotor chamber 29 in the fourthfront housing 11 d. Theguide wall 41 is formed further on the outer circumference side than thefirst boss 33 in the fourthfront housing 11 d. Theguide wall 41 extends toward the rear end side of themotor chamber 29 in the axial direction of thehousing 1. - The
injection port 43 is formed on the rear end side of the fourthfront housing 11 d. As shown inFIG. 5 , theinjection port 43 extends in the radial direction of thehousing 1 with respect to the fourthfront housing 11 d. That is, in the compressor, the first andsecond communication paths housing 1 and theinjection port 43 extending in the radial direction of thehousing 1 do not face each other. Further, theinjection port 43 is located at a position different from theintermediate pressure port 31 and the first andsecond communication paths rotating shaft 3. - The
endplate 13 is joined to the rear end of the fourthfront housing 11 d, that is, the rear end of thefront housing 11. The rear end of themotor chamber 29 is defined by theend plate 13. In theend plate 13, asecond boss 51 extending toward themotor chamber 29 in the axial direction of thehousing 1 is formed. In thesecond boss 51, athird shaft hole 47 c extending in the axial direction of thehousing 1 is formed. In thethird shaft hole 47 c, a second radial foil bearing 49 b is provided. - The
rear housing 15 is located in the rear of thehousing 1 and joined to theend plate 13. That is, therear housing 15 sandwiches theend plate 13 in conjunction with thefront housing 11. In therear housing 15, first and secondthrust foil bearings support plate 55 are provided. The first thrust foil bearing 53 a is located on the front end side of thesupport plate 55 and sandwiched by theend plate 13 and thesupport plate 55. The second thrust foil bearing 53 b is located on the rear end side of thesupport plate 55 and sandwiched by thesupport plate 55 and therear housing 15. - The
rotating shaft 3 includes a rotating shaftmain body 30 a, a firstsmall diameter portion 30 b located on the front end side of the rotating shaftmain body 30 a, and a secondsmall diameter portion 30 c located on the rear end side of the rotating shaft main body 30. The rotating shaftmain body 30 a is formed in a largest diameter in therotating shaft 3. On the other hand, both of the first and secondsmall diameter portions main body 30 a. The firstsmall diameter portion 30 b is formed in diameter smaller than the secondsmall diameter portion 30 c. - The
rotating shaft 3 is inserted through thehousing 1 and is capable of rotating in thehousing 1. Specifically, the front end side of the rotating shaftmain body 30 a is inserted through thesecond shaft hole 47 b and rotatably supported by the first radial foil bearing 49 a. On the other hand, the rear end side of the rotating shaftmain body 30 a is inserted through thethird shaft hole 47 c and rotatably supported by the second radial foil bearing 49 b. Further, the firstsmall diameter portion 30 b is inserted through thefirst shaft hole 47 a. The rear end side of the firstsmall diameter portion 30 b is located in thesecond suction port 37. The secondsmall diameter portion 30 c is inserted through thesupport plate 55 in therear housing 15. Consequently, the secondsmall diameter portion 30 c and further, therotating shaft 3 are supported by the first and secondthrust foil bearings support plate 55. - The
electric motor 5 is provided in themotor chamber 29. Theelectric motor 5 includes astator 5 a and arotor 5 b. Since theelectric motor 5 is provided in this way, themotor chamber 29 is defined into afirst chamber 29 a and asecond chamber 29 b respectively located at the axial direction both ends of theelectric motor 5. Thefirst chamber 29 a is located on the front end side in the axial direction of theelectric motor 5 and is located closer to thesecond impeller chamber 19 than thestator 5 a and therotor 5 b. Thesecond chamber 29 b is located on the rear end side in the axial direction of theelectric motor 5 and is located on the opposite side of thesecond impeller chamber 19 with respect to thestator 5 a and therotor 5 b, that is, closer to theend plate 13 than thestator 5 a and therotor 5 b. Thefirst chamber 29 a communicates with thefirst discharge chamber 25 in the axial direction through theintermediate pressure port 31. Further, thefirst chamber 29 a communicates with thesecond shaft hole 47 b and thesecond impeller chamber 19 through thesecond suction port 37. On the other hand, thesecond chamber 29 b communicates with theinjection port 43. - The
stator 5 a is fixed to the inner wall of themotor chamber 29. Thestator 5 a is electrically connected to a not-shown battery. Therotor 5 b is located on the inner circumference side of thestator 5 a. In themotor chamber 29, therotor 5 b is arranged between thefirst boss 33 and thesecond boss 51. Therotor 5 b is fixed to the rotating shaftmain body 30 a. Consequently, therotor 5 b is capable of rotating integrally with therotating shaft 3 on the inner circumference side of thestator 5 a. Here, agap 5 c is provided between thestator 5 a and therotor 5 b. Thefirst chamber 29 a and thesecond chamber 29 b communicate with each other through thegap 5 c. Note that, inFIGS. 1 and 5 , the shapes of thestator 5 a and therotor 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 firstsmall diameter portion 30 b and provided in thefirst impeller chamber 17. Consequently, thefirst impeller 7 is capable of rotating in thefirst impeller chamber 17 according to the rotation of therotating shaft 3. Thefirst impeller 7 is formed in diameter smaller than the inner diameter of themotor chamber 29. Thefirst 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 thefirst impeller 7 is formed as alarge diameter portion 7 a. Further, a plurality ofblades 70 are provided at a predetermined interval on the surface of thefirst impeller 7. - The
second impeller 9 is press-fitted into the rear end side of the firstsmall diameter portion 30 b and provided in thesecond impeller chamber 19. Consequently, thesecond impeller 9 is capable of rotating in thesecond impeller chamber 19 according to the rotation of therotating shaft 3. In this way, in the compressor, thefirst impeller 7, thesecond impeller 9, and theelectric motor 5 are arranged in this order in the axial direction of therotating 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 themotor chamber 29. Further, thesecond impeller 9 is formed to have the same size as thefirst impeller 7. Thesecond impeller 9 is provided in the firstsmall diameter portion 30 b such that alarge diameter portion 9 a of thesecond impeller 9 is located on the front end side of thefront housing 11. Consequently, in the compressor, in thefront housing 11, thefirst impeller 7 and thesecond impeller 9 are arranged with thelarge diameter portion 7 a and thelarge diameter portion 9 a faced to each other. Further, a plurality ofblades 90 are provided at a predetermined interval on the surface of thesecond impeller 9. Note that thesecond impeller 9 may be formed in a smaller diameter than thefirst impeller 7. - The
refrigeration cycle 10 is configured by acondenser 101, anexpansion valve 102, areceiver 103, anevaporator 104, andpipes 201 to 206 besides the compressor. Thereceiver 103 corresponds to the gas-liquid separator in the present invention. Thereceiver 103 includes a gas-liquid separation chamber 103 a. In thereceiver 103, aninlet 103 b, anoutlet 103 c, and agas outlet 103 d are formed. The gas-liquid separation chamber 103 a separates a refrigerant flown into from theinlet 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 theoutlet 103 c. On the other hand, 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 thegas outlet 103 d. - Here, since the
refrigeration cycle 10 is mounted on a vehicle, there is a strong demand for a reduction in the size of therefrigeration cycle 10. Therefore, in therefrigeration cycle 10, a device such as an economizer is not adopted to perform the gas-liquid separation of the refrigerant. Instead, thereceiver 103 is adopted to perform the gas-liquid separation of the refrigerant. - The
discharge port 45 of the compressor and thecondenser 101 are connected by apipe 201. Thecondenser 101 is connected to theexpansion valve 102 by apipe 202. Theexpansion valve 102 is connected to theinlet 103 b of thereceiver 103 by apipe 203. Theoutlet 103 c of thereceiver 103 is connected to theevaporator 104 by apipe 204. Theevaporator 104 is connected to thefirst suction port 35 of the compressor by apipe 205. Further, thegas outlet 103 d of thereceiver 103 is connected to theinjection port 43 of the compressor by apipe 206. In this way, the gas-liquid separation chamber 103 a and thesecond chamber 29 b communicate with each other. - In the compressor configured as explained above, the
stator 5 a rotates therotor 5 b by electricity ofmotor 5. Consequently, therotating shaft 3 is driven to rotate around a rotational axis O in thehousing 1. Therefore, thefirst impeller 7 rotates in thefirst impeller chamber 17. Thesecond impeller 9 rotates in thesecond impeller chamber 19. - Further, a low-pressure refrigerant that passes through the
evaporator 104 is sucked into thefirst suction port 35 through thepipe 205 and reaches the inside of thefirst impeller chamber 17. Thefirst impeller 7 rotating in thefirst impeller chamber 17 increases kinetic energy of the refrigerant in thefirst impeller chamber 17. Thereafter, thefirst impeller 7 converts the kinetic energy of the refrigerant into pressure energy through thefirst diffuser 21, and compresses the refrigerant, and discharges the compressed refrigerant to thefirst discharge chamber 25. Consequently, the pressure of the refrigerant in thefirst discharge chamber 25 changes to an intermediate pressure. The refrigerant having the intermediate pressure, that is, an intermediate pressure refrigerant circulates from thefirst discharge chamber 25 to thefirst chamber 29 a through theintermediate pressure port 31 as indicated by a solid line arrow in theFIG. 1 . Here, in the compressor, in thefront housing 11, theintermediate pressure port 31 extends in the axial direction of thehousing 1. Therefore, in the compressor, it is possible to reduce a body diameter even if theintermediate pressure port 31 is provided to cause thefirst discharge chamber 25 and thefirst chamber 29 a to communicate with each other. - The intermediate pressure refrigerant flown into the
first chamber 29 a is guided to thefirst communication path 39 a and thesecond communication path 39 b by theguide wall 41. The intermediate pressure refrigerant circulates through thefirst communication path 39 a and thesecond communication path 39 b toward thesecond chamber 29 b. In this case, the intermediate pressure refrigerant circulates from thefirst chamber 29 a to thesecond chamber 29 b in the axial direction of thehousing 1 while cooling thestator 5 a. - Further, in the compressor, the injection refrigerant separated by the gas-
liquid separation chamber 103 a of thereceiver 103 circulates through thepipe 206 and flows into thesecond chamber 29 b through theinjection port 43 as indicated by an arrow in theFIG. 1 . In this case, since theinjection port 43 extends in the radial direction of thehousing 1, the injection refrigerant flows into thesecond chamber 29 b in the radial direction of thehousing 1, that is, a direction orthogonal to the intermediate pressure refrigerant circulating through the first andsecond communication paths second communication paths second chamber 29 b and the injection refrigerant flowing into thesecond chamber 29 b from theinjection port 43. Consequently, in the compressor, the intermediate pressure refrigerant and the injection refrigerant suitably flow into thesecond 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 thegap 5 c between thestator 5 a and therotor 5 b and circulates toward thefirst chamber 29 a. In this case, thestator 5 a and therotor 5 b are also cooled by the mixed refrigerant circulating through thegap 5 c. The mixed refrigerant reaching thefirst chamber 29 a flows into thesecond suction port 37. - The mixed refrigerant circulating through the
second suction port 37 is sucked into thesecond impeller chamber 19 while coming into contact with the firstsmall diameter portion 30 b of therotating shaft 3. In this case, in the compressor, it is possible to cool therotating shaft 3 with the mixed refrigerant circulating through thesecond suction port 37. - The
second impeller 9 rotating in thesecond impeller chamber 19 increases kinetic energy of the mixed refrigerant in thesecond impeller chamber 19. Thereafter, thesecond impeller 9 converts the kinetic energy of the refrigerant into pressure energy through thesecond diffuser 23, and compresses the refrigerant, and discharges the compressed refrigerant to thesecond discharge chamber 27. In this way, in the compressor, the refrigerant sucked from thefirst suction port 35 is compressed in two stages, and the injection refrigerant as the mixed refrigerant also is compressed. - As explained above, in the compressor, 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 thesecond suction port 37 as the mixed refrigerant. Here, 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 thesecond impeller chamber 19 from thesecond suction port 37. - The injection refrigerant has high pressure compared with the refrigerant flowing into the
first impeller chamber 17 from thefirst suction port 35 through theevaporator 104. Therefore, in the compressor, it is possible to increase the pressure of the mixed refrigerant flowing into thesecond suction port 37 from thefirst chamber 29 a. - Therefore, the compressor in the embodiment has high durability and can surely improve efficiency of the refrigeration circuit.
- In particular, in the compressor, in the fourth
front housing 11 d, the first andsecond communication paths housing 1. Therefore, in the compressor, even if the first andsecond communication paths first chamber 29 a and thesecond chamber 29 b to communicate with each other, it is possible to reduce a body diameter of the compressor. Further, in the compressor, theguide wall 41 is formed in the fourthfront housing 11 d. Therefore, in the compressor, it is possible to suitably guide the intermediate pressure refrigerant to the first andsecond communication paths second suction port 37 after flowing into thefirst chamber 29 a from theintermediate pressure port 31. - Further, in the compressor, since both of the
first impeller 7 and thesecond impeller 9 have diameters smaller than the inner diameter of themotor chamber 29, it is possible to reduce the body diameter. Further, in the compressor, thefirst impeller 7 and thesecond impeller 9 are arranged with thelarge diameter portions first impeller 7 side and a second thrust force generated on thesecond 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 secondthrust foil bearings - The present invention is explained above according to the embodiment. However, the present invention is not limited to the embodiment. It goes without saying that the present invention can be changed and applied as appropriate without departing from the gist of the present invention.
Claims (6)
1. A motor-driven turbo compressor used in a refrigeration cycle, comprising:
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,
wherein 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, and
wherein 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;
wherein the first impeller, the second impeller, and the electric motor are arranged in the axial direction of the rotating shaft in this order,
wherein 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, the first chamber is located close to the second impeller in the axial direction of the electric motor, and
wherein an intermediate pressure port is formed in the housing and connects the first chamber and the first discharge chamber; and
wherein an injection port connected to a gas-liquid separator of the refrigeration cycle is formed in the housing and communicates with the second chamber.
2. The motor-driven turbo compressor according to claim 1 , wherein
the electric motor includes a rotor fixed to the rotating shaft and a stator fixed to the housing,
a communication path is formed between the housing and the stator and connects the first chamber and the second chamber in the axial direction, and
a guide wall that guides the refrigerant passed through the intermediate pressure port to the communication path is formed in the housing.
3. The motor-driven turbo compressor according to claim 2 , wherein the injection port is configured not to face the communication path.
4. The motor-driven turbo compressor according to claim 3 , wherein the injection port extends in a radial direction of the housing.
5. The motor-driven turbo compressor according to claim 3 , wherein the injection port is located at a position different from the intermediate pressure port and the communication path around the axis of the rotating shaft.
6. The motor-driven turbo compressor according to claim 1 , wherein the second suction port is configured to lead the refrigerant to make contact with the rotating shaft.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014-056133 | 2014-03-19 | ||
JP2014056133A JP6011571B2 (en) | 2014-03-19 | 2014-03-19 | Electric turbo compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20150267709A1 true US20150267709A1 (en) | 2015-09-24 |
Family
ID=52633133
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/631,985 Abandoned US20150267709A1 (en) | 2014-03-19 | 2015-02-26 | Motor-driven turbo compressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US20150267709A1 (en) |
EP (1) | EP2921707A1 (en) |
JP (1) | JP6011571B2 (en) |
KR (1) | KR101720855B1 (en) |
CN (1) | CN104929956B (en) |
Cited By (6)
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)
Publication number | Priority date | Publication date | Assignee | Title |
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CN105736424B (en) * | 2016-04-19 | 2019-01-25 | 同济大学 | A kind of direct-drive supercharged centrifugal air compressor of the single-stage of vehicle fuel battery engine |
JP7103263B2 (en) * | 2019-02-20 | 2022-07-20 | 株式会社豊田自動織機 | Turbo fluid machine |
CN114641618B (en) * | 2019-09-23 | 2024-02-23 | 热力学公司 | Integrated motor-compressor unit with a cooling circuit configured to reduce cooling fluid pressure and a pressure relief system |
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- 2015-03-09 EP EP15158179.0A patent/EP2921707A1/en not_active Withdrawn
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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 |
Also Published As
Publication number | Publication date |
---|---|
KR20150109275A (en) | 2015-10-01 |
CN104929956A (en) | 2015-09-23 |
JP2015178790A (en) | 2015-10-08 |
KR101720855B1 (en) | 2017-03-28 |
CN104929956B (en) | 2017-04-12 |
EP2921707A1 (en) | 2015-09-23 |
JP6011571B2 (en) | 2016-10-19 |
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