WO2023144953A1 - 圧縮機及び冷凍サイクル装置 - Google Patents

圧縮機及び冷凍サイクル装置 Download PDF

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Publication number
WO2023144953A1
WO2023144953A1 PCT/JP2022/003014 JP2022003014W WO2023144953A1 WO 2023144953 A1 WO2023144953 A1 WO 2023144953A1 JP 2022003014 W JP2022003014 W JP 2022003014W WO 2023144953 A1 WO2023144953 A1 WO 2023144953A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
compressor
injection pipe
stator
pipe
Prior art date
Application number
PCT/JP2022/003014
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English (en)
French (fr)
Japanese (ja)
Inventor
大輔 堀口
浩平 達脇
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2022/003014 priority Critical patent/WO2023144953A1/ja
Priority to JP2023576476A priority patent/JPWO2023144953A1/ja
Publication of WO2023144953A1 publication Critical patent/WO2023144953A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil

Definitions

  • the present disclosure relates to a compressor that compresses refrigerant, and a refrigeration cycle device that includes the compressor.
  • a refrigeration cycle device used in a refrigeration system, an air conditioner, etc. is equipped with a compressor that compresses a refrigerant.
  • Compressors equipped with various types of compression units, such as scroll compressors, rotary compressors, and vane compressors, are known as compressors used in refrigeration cycle apparatuses.
  • a compressor used in a refrigeration cycle apparatus includes an electric motor unit, a drive shaft rotated by the power of the electric motor unit, and a compression unit that compresses a refrigerant by the power of the electric motor unit transmitted by the drive shaft.
  • a compressor used in a refrigeration cycle apparatus includes a container that accommodates an electric motor unit, a drive shaft, and a compression unit inside.
  • the container is provided with a suction pipe for supplying refrigerant to be compressed in the compression unit inside the container. That is, the compressor has a configuration in which the refrigerant supplied from the suction pipe to the inside of the container is compressed by the compression unit.
  • refrigerating machine oil which serves as lubricating oil, is stored in the lower portion of the container. The refrigerating machine oil stored in the lower portion of the container is supplied to sliding portions of the compressor, such as between the drive shaft and bearings that rotatably support the drive shaft.
  • Patent Literature 1 discloses a scroll compressor.
  • the scroll compressor described in Patent Document 1 allows part of the refrigerant supplied from the suction pipe into the container to flow to the electric motor unit side to cool the stator of the electric motor unit.
  • the scroll compressor described in Patent Document 1 attempts to expand the operable range of the compressor by cooling the stator of the electric motor unit.
  • the scroll compressor described in Patent Document 1 uses part of the refrigerant supplied from the suction pipe into the container to cool the stator of the electric motor unit. Therefore, when the refrigeration cycle device is in an operating state with a small refrigerant circulation amount, the scroll compressor described in Patent Document 1 cannot flow sufficient refrigerant to the electric motor unit. Therefore, when the refrigeration cycle device is in an operating state with a small refrigerant circulation amount, the scroll compressor described in Patent Document 1 cannot sufficiently cool the stator of the electric motor unit.
  • the scroll compressor described in Patent Document 1 is sufficiently cooled to cool the electric motor unit.
  • the present disclosure has been made to solve the above-described problems, and a primary object thereof is to obtain a compressor capable of expanding the operable range compared to conventional compressors.
  • a second object of the present disclosure is to obtain a refrigeration cycle apparatus including such a compressor.
  • a compressor includes an electric motor unit having a rotor and a stator, a drive shaft fixed to the rotor and rotated by power of the electric motor unit, and the electric motor connected to the drive shaft and transmitted by the drive shaft.
  • a compression unit that compresses a refrigerant by the power of an electric motor unit; a container that accommodates the electric motor unit, the drive shaft, and the compression unit therein and stores refrigerating machine oil at the bottom;
  • Refrigerant flow path section including a suction pipe for supplying refrigerant compressed by the compression unit, a plurality of flow path sections penetrating the stator, and a pipe connecting at least two of the flow path sections. and a supply pipe that is connected to the refrigerant flow path and supplies the refrigerant from the outside of the container to the refrigerant flow path.
  • a refrigeration cycle device includes a compressor according to the present disclosure, a radiator in which refrigerant compressed by the compressor releases heat, a first expansion section that expands the refrigerant flowing out from the radiator, an evaporator in which the refrigerant flowing out from the first expansion part evaporates; and an injection pipe in which the refrigerant flowing out from the radiator flows in from one end and the other end is connected to the supply pipe of the compressor. and a second expansion section that expands the refrigerant flowing through the injection pipe, and a control device that controls the flow rate of the refrigerant flowing from the injection pipe to the supply pipe and the compressor.
  • the stator of the electric motor unit is cooled by the refrigerant supplied from the supply pipe to the refrigerant flow path. That is, the compressor according to the present disclosure uses a refrigerant different from the refrigerant supplied from the suction pipe into the container as the refrigerant for cooling the stator of the electric motor unit. Therefore, the compressor according to the present disclosure can cool the stator of the electric motor unit regardless of the amount of refrigerant supplied from the suction pipe into the container, that is, regardless of the amount of refrigerant circulating through the refrigeration cycle device. can.
  • the compressor according to the present disclosure can prevent the stator of the electric motor unit from being sufficiently cooled, and can also prevent the refrigerating machine oil stored in the bottom of the container from being diluted with the refrigerant. Therefore, the compressor according to the present disclosure can expand the operable range as compared with the conventional compressor.
  • FIG. 1 is a circuit diagram showing a refrigeration cycle device according to an embodiment;
  • FIG. It is a longitudinal section showing a compressor concerning an embodiment.
  • FIG. 4 is a diagram for explaining a refrigerant flow path portion and a supply pipe according to the embodiment, and is a vertical cross-sectional view showing the vicinity of the electric motor unit of the compressor according to the embodiment;
  • FIG. 3 is a diagram for explaining a refrigerant flow path portion and a supply pipe according to the embodiment, and is a side view showing the electric motor unit of the compressor according to the embodiment;
  • FIG. FIG. 4 is a diagram for explaining a refrigerant flow path portion and a supply pipe according to the embodiment, and is a plan view showing the stator of the electric motor unit of the compressor according to the embodiment;
  • FIG. 10 is a diagram for explaining a refrigerant flow path portion and a supply pipe in another example of the compressor according to the embodiment, and is a plan view showing the stator of the electric motor unit of the compressor; It is a figure for demonstrating another example of the compressor which concerns on embodiment, and is a longitudinal cross-sectional view which shows the motor unit vicinity of the said compressor. It is a figure for demonstrating another example of the compressor which concerns on embodiment, and is a longitudinal cross-sectional view which shows the motor unit vicinity of the said compressor.
  • FIG. 1 is a circuit diagram showing a refrigeration cycle apparatus according to an embodiment.
  • the refrigeration cycle device 1 includes a compressor 100 that compresses refrigerant, a radiator that releases heat from the refrigerant compressed by the compressor 100, a first expansion section 300 that expands the refrigerant flowing out from the radiator, and a first expansion section. and an evaporator in which the refrigerant flowing out from 300 evaporates.
  • the refrigeration cycle device 1 also includes an injection pipe 800 and a second expansion section 600 .
  • the injection pipe 800 has one end into which the refrigerant that has flowed out from the radiator flows, and the other end is connected to the later-described supply pipe 52 of the compressor 100 .
  • the second expansion section 600 is provided in the injection pipe 800 and expands the refrigerant flowing through the injection pipe 800 .
  • the refrigeration cycle device 1 also includes a control device 70 .
  • Control device 70 controls the flow rate of refrigerant flowing from injection pipe 800 to supply pipe 52 .
  • the control device 70 controls the compressor 100 .
  • the compressor 100 includes an electric motor unit 30 having a stator 31 and a rotor 32 as described below.
  • the control device 70 controls the rotation speed of the rotor 32 of the electric motor unit 30 .
  • the control device 70 is composed of dedicated hardware or a CPU (Central Processing Unit) that executes programs stored in memory. Note that the CPU is also called a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microcomputer, or a processor.
  • CPU Central Processing Unit
  • control device 70 When the control device 70 is dedicated hardware, the control device 70 may be, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field-Programmable Gate Array), or a combination thereof. Applicable. Each functional unit implemented by the control device 70 may be implemented by separate hardware, or each functional unit may be implemented by one piece of hardware.
  • ASIC Application Specific Integrated Circuit
  • FPGA Field-Programmable Gate Array
  • each function executed by the control device 70 is implemented by software, firmware, or a combination of software and firmware.
  • Software and firmware are written as programs and stored in memory.
  • the CPU implements each function of the control device 70 by reading and executing programs stored in the memory.
  • the memory is, for example, non-volatile or volatile semiconductor memory such as RAM, ROM, flash memory, EPROM or EEPROM.
  • control device 70 may be realized by dedicated hardware, and part of them may be realized by software or firmware.
  • the refrigeration cycle device 1 is used for various purposes such as refrigeration equipment and air conditioners.
  • FIG. 1 shows an example using a refrigeration cycle device 1 according to an embodiment as an air conditioner capable of cooling operation. Therefore, as shown in FIG. 1, the refrigeration cycle device 1 includes an outdoor unit 1a and an indoor unit 1b.
  • the outdoor unit 1 a is provided with, for example, a compressor 100 , an outdoor heat exchanger 200 , an outdoor fan 201 , a first expansion section 300 , an injection pipe 800 and a second expansion section 600 .
  • the indoor unit 1b is provided with an indoor heat exchanger 400 and an indoor fan 401, for example.
  • the refrigeration cycle device 1 uses, for example, a fluorocarbon-based refrigerant such as R32 as a refrigerant.
  • natural refrigerants such as a carbon dioxide, may be used for the refrigerating-cycle apparatus 1 as a refrigerant
  • a refrigerant circuit 500 is configured by connecting the compressor 100, the outdoor heat exchanger 200, the first expansion section 300, and the indoor heat exchanger 400 by refrigerant piping.
  • the compressor 100 sucks a low-temperature, low-pressure refrigerant, compresses the sucked-in refrigerant, and discharges it as a high-temperature, high-pressure gaseous refrigerant.
  • Compressor 100 can be a compressor with various types of compression units, such as scroll compressors, rotary compressors, and vane compressors. As will be described later, a scroll compressor is used as the compressor 100 in this embodiment.
  • the outdoor heat exchanger 200 functions as a radiator, into which the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 100 flows. That is, the high-temperature and high-pressure gaseous refrigerant flowing inside the outdoor heat exchanger 200 is condensed while radiating heat to a medium having a lower temperature than the refrigerant, and becomes a high-pressure liquid refrigerant.
  • the outdoor heat exchanger 200 is an air-cooled heat exchanger. Therefore, the high-temperature and high-pressure gaseous refrigerant flowing inside the outdoor heat exchanger 200 is condensed while radiating heat to the outdoor air supplied to the outdoor heat exchanger 200 from the outdoor fan 201, and becomes a high-pressure liquid refrigerant.
  • the radiator may be referred to as a condenser.
  • the first expansion section 300 is a pressure reducing valve or an expansion valve that reduces the pressure of the high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 200 to expand it.
  • the first expansion section 300 is, for example, an expander, a thermal automatic expansion valve, or a linear electronic expansion valve whose opening is adjusted.
  • the first expansion portion 300 is controllable, such as when the opening degree of the first expansion portion 300 is controllable, the first expansion portion 300 is controlled by the control device 70 .
  • the indoor heat exchanger 400 functions as an evaporator, into which the low-temperature, low-pressure gas-liquid two-phase refrigerant flowing out from the first expansion section 300 flows.
  • the low-temperature, low-pressure gas-liquid two-phase refrigerant flowing inside the indoor heat exchanger 400 evaporates while absorbing heat from a medium having a higher temperature than the refrigerant, and becomes a low-pressure gaseous refrigerant.
  • the indoor heat exchanger 400 is an air-cooled heat exchanger. Therefore, the low-temperature, low-pressure gas-liquid two-phase refrigerant flowing inside the indoor heat exchanger 400 evaporates while absorbing heat from the indoor air supplied from the indoor fan 401 to the indoor heat exchanger 400, and becomes a low-pressure gas. refrigerant.
  • the injection pipe 800 has one end into which the refrigerant that has flowed out from the radiator flows, and the other end is connected to the later-described supply pipe 52 of the compressor 100 .
  • one end of injection pipe 800 is connected to refrigerant pipe 501 connecting outdoor heat exchanger 200 functioning as a radiator and first expansion section 300 . That is, the high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 200 flows into the injection pipe 800 .
  • the injection pipe 800 is provided with the second expansion portion 600 .
  • the second expansion section 600 is a pressure reducing valve or an expansion valve that decompresses and expands the high-pressure liquid refrigerant flowing through the injection pipe 800 .
  • the second expansion section 600 is, for example, an expansion machine, a thermal automatic expansion valve, or a linear electronic expansion valve whose opening is adjusted.
  • the opening degree of the second inflation portion 600 is controllable, the second inflation portion 600 is controlled by the control device 70 . That is, the liquid refrigerant or gas-liquid two-phase refrigerant decompressed by the second expansion section 600 flows through the injection pipe 800 into the later-described supply pipe 52 of the compressor 100 .
  • the compressor 100 supplies the refrigerant depressurized by the second expansion section 600 flowing through the injection pipe 800 to the compression chamber 11, and therefore corresponds to the compressor-side injection pipe.
  • An injection pipe 49 is provided. Therefore, in the present embodiment, the other end of injection pipe 800 on the side of compressor 100 is branched into two.
  • a first branch portion which is one of the branch portions, is connected to the supply pipe 52 of the compressor 100 .
  • a second branch portion which is the other of the branch portions, is connected to the injection pipe 49 of the compressor 100 .
  • an on-off valve 54 is provided at the first branch portion, which is one of the branch portions.
  • An on-off valve 55 is provided at the second branch portion, which is the other of the branch portions.
  • the on-off valve 54 and the on-off valve 55 may be valves that can only be opened and closed, or may be flow control valves that can change the degree of opening in an open state to a plurality of degrees of opening.
  • the control device 70 controls the flow rate of refrigerant flowing from the injection pipe 800 into the supply pipe 52 of the compressor 100 by controlling the opening/closing state of the on-off valve 54 . Further, the control device 70 controls the flow rate of refrigerant flowing from the injection pipe 800 into the injection pipe 49 of the compressor 100 by controlling the open/close state of the on-off valve 55 .
  • the control device 70 may control the opening degree of the second expansion section 600 together with the opening/closing state of the on-off valve 54 to control the flow rate of the refrigerant flowing from the injection pipe 800 into the supply pipe 52 of the compressor 100 .
  • the control device 70 controls the opening degree of the second expansion section 600 to compress the refrigerant from the injection pipe 800.
  • the flow rate of refrigerant entering the supply line 52 of the machine 100 may be controlled.
  • even when the injection pipe 800 is connected only to the supply pipe 52 of the compressor 100 it is not necessary to provide the on-off valve 54 and the on-off valve 55 in the injection pipe 800 .
  • injection pipe 800 is provided with heat exchanger 700 at a position on the downstream side of second expansion section 600 in the flow direction of the refrigerant.
  • the heat exchanger 700 exchanges heat between the refrigerant decompressed by the second expansion section 600 flowing through the heat exchanger 700 and a medium having a higher temperature than the refrigerant.
  • the heat exchanger 700 is, for example, an air-cooled heat exchanger that exchanges heat between the refrigerant decompressed by the second expansion section 600 flowing through the heat exchanger 700 and the outdoor air.
  • the heat exchanger 700 may be a double-tube heat exchanger.
  • the refrigerant flowing into the heat exchanger 700 from the second expansion section 600 and the high-pressure liquid or gas-liquid two-phase state flowing into the heat exchanger 700 from the outdoor heat exchanger 200 are mixed.
  • Heat is exchanged with the refrigerant. That is, the heat exchanger 700 exchanges heat between the refrigerant flowing between the outdoor heat exchanger 200 and the first expansion section 300 in the refrigerant circuit 500 and the refrigerant flowing downstream of the second expansion section 600 in the injection pipe 800.
  • It may be a supercooler that allows Note that the heat exchanger 700 may be omitted from the injection pipe 800 .
  • FIG. 2 is a vertical cross-sectional view showing the compressor according to the embodiment.
  • the compressor 100 is a hermetic scroll compressor.
  • the compressor 100 includes an electric motor unit 30 , a drive shaft 33 , a scroll-type compression unit 10 , a container 40 and a suction pipe 44 .
  • the compressor 100 includes a frame 46, a subframe 47, a discharge pipe 45, a boss portion 27, an Oldham ring 22a, a sleeve 34, a discharge valve 5, a valve guard 6, a discharge muffler 7, an oil pump 51 , an oil drain pipe 50, an injection pipe 49, and the like.
  • the container 40 is a closed container that constitutes the outer shell of the compressor 100 .
  • the container 40 has a cylindrical shape. Inside the container 40, the electric motor unit 30, the drive shaft 33, the compression unit 10, and the like are accommodated. In the container 40, the compression unit 10 is arranged above and the electric motor unit 30 is arranged below.
  • the container 40 has a bottom portion 43 , a body portion 42 and a lid portion 41 .
  • the bottom portion 43 constitutes the bottom portion of the container 40 and is a dish-shaped member in which the oil reservoir 2 that stores the refrigerator oil is formed. That is, the container 40 has a structure in which the refrigerating machine oil is stored in the bottom.
  • the trunk portion 42 is a cylindrical member extending upward from the bottom portion 43 .
  • a suction pipe 44 is provided in the body portion 42 .
  • the lid portion 41 is a dome-shaped member provided on the upper portion of the body portion 42 .
  • a discharge pipe 45 is provided in the lid portion 41 .
  • the suction pipe 44 supplies refrigerant compressed by the compression unit 10 to the inside of the container 40 .
  • the suction pipe 44 is connected to the indoor heat exchanger 400 by refrigerant piping. That is, the low-pressure gaseous refrigerant that has flowed out of the indoor heat exchanger 400 is supplied to the inside of the container 40 via the suction pipe 44 . Further, in this embodiment, the suction pipe 44 communicates with the low-pressure space 8 inside the container 40 . Refrigerant compressed in the compression unit 10 is supplied to the low-pressure space 8 . In this embodiment, the space formed between the electric motor unit 30 and the compression unit 10 serves as the low-pressure space 8. As shown in FIG.
  • the discharge pipe 45 guides the high-temperature and high-pressure gaseous refrigerant compressed by the compression unit 10 to the outside of the container 40 .
  • the discharge pipe 45 communicates with the high pressure space 9 inside the container 40 .
  • the high-pressure space 9 is a space in which the high-temperature and high-pressure gaseous refrigerant compressed by the compression unit 10 is stored. In this embodiment, a high pressure space 9 is formed above the compression unit 10 .
  • the discharge pipe 45 is connected to the outdoor heat exchanger 200 by refrigerant piping. That is, the high-temperature and high-pressure gaseous refrigerant compressed by the compression unit 10 flows into the outdoor heat exchanger 200 via the discharge pipe 45 .
  • the frame 46 is fixed to the inner peripheral portion of the body portion 42 of the container 40 by shrink fitting, welding, or the like.
  • the frame 46 holds the compression unit 10 from below.
  • the frame 46 also includes a main bearing 46a, and rotatably supports the drive shaft 33 via the main bearing 46a.
  • the frame 46 is arranged above the electric motor unit 30 and positioned between the electric motor unit 30 and the compression unit 10 .
  • a plurality of suction ports 36 communicating with the low pressure space 8 are formed in the frame 46 . Refrigerant in the low pressure space 8 flows into the compression unit 10 through the plurality of suction ports 36 .
  • the space between the frame 46 and the electric motor unit 30 serves as the low pressure space 8 .
  • a space is formed above the frame 46 so as to be positioned on the outer peripheral side of the first spiral tooth 24 and the second spiral tooth 26 of the compression unit 10 .
  • the plurality of suction ports 36 are through holes that communicate between the space above the frame 46 located on the outer peripheral side of the first spiral tooth 24 and the second spiral tooth 26 and the low pressure space 8 located below the frame 46. It has become.
  • the subframe 47 is arranged at a position below the electric motor unit 30 inside the container 40 .
  • the subframe 47 is fixed to the inner peripheral portion of the body portion 42 of the container 40 by shrink fitting, welding, or the like.
  • the sub-frame 47 also includes a sub-bearing 48 which is, for example, a ball bearing, and rotatably supports the drive shaft 33 via the sub-bearing 48 .
  • a hole 47 a is formed in the sub-frame 47 . Refrigerant oil flowing down toward the oil sump 2 passes through the hole 47a.
  • the frame 46 and the sub-frame 47 are fixed inside the container 40 so as to face each other with the electric motor unit 30 interposed therebetween.
  • the drive shaft 33 is fixed to a later-described rotor 32 of the electric motor unit 30 and is rotated by the power of the electric motor unit 30 .
  • the drive shaft 33 is connected to the compression unit 10 and transmits power of the electric motor unit 30 to the compression unit 10 .
  • the drive shaft 33 is a rod-shaped crankshaft that extends vertically in the center of the container 40 .
  • the drive shaft 33 has a main shaft portion 33b, a sub shaft portion 33c, and an eccentric shaft portion 33a.
  • the main shaft portion 33b is rotatably supported by a main bearing 46a of the frame 46.
  • a sleeve 34 is provided between the main bearing 46a and the main shaft portion 33b.
  • the sleeve 34 absorbs the tilted state between the frame 46 and the drive shaft 33 .
  • the secondary shaft portion 33c is provided at the end of the main shaft portion 33b opposite to the compression unit 10 . That is, the secondary shaft portion 33c is provided at the lower end portion of the main shaft portion 33b. Further, the axis of the secondary shaft portion 33c is arranged coaxially with the axis of the main shaft portion 33b.
  • the sub-shaft portion 33c is rotatably supported by a sub-bearing 48 of the sub-frame 47.
  • the eccentric shaft portion 33a is provided at the end portion of the main shaft portion 33b on the compression unit 10 side. That is, the eccentric shaft portion 33a is provided at the upper end portion of the main shaft portion 33b.
  • the axis of the eccentric shaft portion 33a is arranged eccentrically with respect to the axis of the main shaft portion 33b.
  • the eccentric shaft portion 33a is rotatably accommodated in the swing bearing 27a.
  • the outer peripheral portion of the eccentric shaft portion 33a is in close contact with the inner peripheral portion of the swing bearing 27a via the refrigerator oil.
  • an oil passage 33d is formed through which refrigerating machine oil passes.
  • the compression unit 10 is connected to the drive shaft 33 and compresses the refrigerant supplied from the suction pipe 44 to the low pressure space 8 with the power of the electric motor unit 30 transmitted by the drive shaft 33 .
  • the compression unit 10 then discharges the gaseous refrigerant, which has been compressed to a high temperature and high pressure, to the high pressure space 9 .
  • This compression unit 10 has a fixed scroll 21 and an orbiting scroll 22 .
  • the fixed scroll 21 is fixed to the frame 46 above the orbiting scroll 22 .
  • the fixed scroll 21 has a first base plate 23 and first spiral teeth 24 .
  • the first base plate 23 is a plate-like member and constitutes the upper surface portion of the compression unit 10 .
  • the first spiral tooth 24 is a spiral protrusion extending downward from the lower surface of the first base plate 23 .
  • a discharge port 3 is formed in the center of the first base plate 23 of the fixed scroll 21, and is a space through which compressed and high-pressure refrigerant is discharged.
  • the orbiting scroll 22 has a second base plate 25 and second spiral teeth 26 .
  • the second base plate 25 is a plate-like member that is movably arranged above the frame 46 .
  • the second spiral tooth 26 is a spiral protrusion extending upward from the upper surface of the second base plate 25 .
  • the fixed scroll 21 and the orbiting scroll 22 are provided in the container 40 with the first spiral tooth 24 and the second spiral tooth 26 meshing with each other.
  • the first spiral tooth 24 and the second spiral tooth 26 are formed following an involute curve.
  • a plurality of compression chambers 11 are formed between the second spiral tooth 26 and the second spiral tooth 26 .
  • the boss portion 27 is provided at the center of the surface of the second base plate 25 of the orbiting scroll 22 opposite to the surface on which the second spiral teeth 26 are formed, and has a hollow cylindrical shape.
  • a rocking bearing 27 a is provided on the inner peripheral side of the boss portion 27 .
  • the swing bearing 27a covers the outer peripheral portion of the eccentric shaft portion 33a and supports the eccentric shaft portion 33a rotatably.
  • the axis of the eccentric shaft portion 33a is eccentric with respect to the axis of the main shaft portion 33b. Therefore, when the drive shaft 33 rotates around the axis of the main shaft portion 33b, the orbiting scroll 22 rotates eccentrically.
  • the Oldham ring 22a is provided on the surface of the second base plate 25 of the orbiting scroll 22 opposite to the surface on which the second spiral teeth 26 are formed.
  • the Oldham ring 22a prevents the orbiting scroll 22 from rotating on its axis during the eccentric orbiting motion, and allows the orbiting scroll 22 to revolve.
  • the upper and lower surfaces of the Oldham ring 22a are provided with claws (not shown) protruding perpendicularly to each other. The claws of the Oldham ring 22a are inserted into Oldham grooves (not shown) formed in the orbiting scroll 22 and the frame 46. As shown in FIG.
  • the discharge valve 5 is a plate spring member that covers the discharge port 3 and prevents the refrigerant from flowing backward.
  • the refrigerant When the refrigerant is compressed to a predetermined pressure in the compression chamber 11 , the refrigerant lifts the discharge valve 5 against the elastic force of the discharge valve 5 . Then, the compressed refrigerant is discharged from the discharge port 3 into the high-pressure space 9 and discharged outside the compressor 100 through the discharge pipe 45 .
  • the valve guard 6 regulates the movable range of the discharge valve 5 .
  • the discharge muffler 7 covers the discharge valve 5 and suppresses pulsation of the refrigerant discharged from the discharge port 3 .
  • the oil pump 51 is housed in the bottom portion 43 of the container 40 and sucks up the refrigerator oil from the oil sump 2 .
  • the oil pump 51 is attached to the lower portion of the drive shaft 33 .
  • the oil pump 51 sucks up the refrigerating machine oil stored in the oil sump 2 into the oil passage 33 d formed inside the drive shaft 33 .
  • the refrigerator oil sucked into the oil passage 33d is supplied to sliding portions of the compressor 100 such as the sub-bearing 48, the main bearing 46a and the rocking bearing 27a through the oil passage 33d.
  • the oil drain pipe 50 is a pipe that connects the space between the frame 46 and the orbiting scroll 22 and the space between the frame 46 and the subframe 47 .
  • the oil drain pipe 50 drains excess refrigerating machine oil out of the refrigerating machine oil circulating in the space between the frame 46 and the orbiting scroll 22 to the space between the frame 46 and the subframe 47 .
  • Refrigerant oil that has flowed out into the space between the frame 46 and the subframe 47 passes through the hole 47a of the subframe 47 and returns to the oil reservoir 2 .
  • the electric motor unit 30 is provided in the low pressure space 8 inside the container 40 .
  • the electric motor unit 30 drives the orbiting scroll 22 of the compression unit 10 . That is, the electric motor unit 30 compresses the refrigerant in the compression unit 10 by rotationally driving the orbiting scroll 22 via the drive shaft 33 .
  • the electric motor unit 30 has a rotor 32 and a stator 31 .
  • the stator 31 also includes a winding portion 31a through which current flows.
  • the rotor 32 is provided on the inner peripheral side of the stator 31 . Also, the rotor 32 is held with a small gap from the stator 31 .
  • the rotor 32 is rotationally driven by energizing the winding portion 31 a of the stator 31 . That is, the drive shaft 33 fixed to the rotor 32 rotates together with the rotor 32 by energizing the winding portion 31 a of the stator 31 .
  • the injection pipe 49 is provided in the lid portion 41 of the container 40, for example. As described above, the injection pipe 49 supplies the compression chamber 11 with the refrigerant depressurized by the second expansion section 600 flowing through the injection pipe 800 . That is, the injection pipe 49 is connected to the injection pipe 800 and supplies the refrigerant flowing from the injection pipe 800 to the compression unit 10 . In the present embodiment, the refrigerant that flows through the injection pipe 800 and is decompressed by the second expansion section 600 is supplied to the compression chamber 11 as follows. Specifically, the first base plate 23 of the fixed scroll 21 is formed with an injection pipe insertion port 28 that communicates with the space located on the outer peripheral side of the first spiral tooth 24 and the second spiral tooth 26 of the compression unit 10 . .
  • An injection pipe 49 is connected to the injection pipe insertion port 28 .
  • the refrigerant decompressed by the second expansion section 600 flowing through the injection pipe 800 passes through the injection pipe 49 and enters the space located on the outer peripheral side of the first spiral tooth 24 and the second spiral tooth 26 of the compression unit 10. influx.
  • This refrigerant is sucked into the compression chamber 11 when the compression chamber 11 communicates with the space located on the outer peripheral side of the first spiral tooth 24 and the second spiral tooth 26 of the compression unit 10 .
  • the low-pressure gaseous refrigerant that has flowed out of the indoor heat exchanger 400 is sucked into the low-pressure space 8 of the container 40 through the suction pipe 44 . Also, the low-pressure gaseous refrigerant sucked into the low-pressure space 8 passes through the intake port 36 of the frame 46 and flows into the space located on the outer peripheral side of the first spiral tooth 24 and the second spiral tooth 26 of the compression unit 10. do. Then, the low-pressure gaseous refrigerant that has flowed into the space is taken into the compression chamber 11 among the plurality of compression chambers 11 that communicates with the space.
  • the compression chamber 11 which has taken in the low-pressure gaseous refrigerant, reduces its own volume and expands from the outer peripheral side of the first spiral tooth 24 and the second spiral tooth 26 to the first spiral tooth. It moves toward the center of the spiral tooth 24 and the second spiral tooth 26 .
  • the low-pressure gaseous refrigerant in the compression chamber 11 is compressed into a high-temperature, high-pressure gaseous refrigerant.
  • the compressed high-temperature and high-pressure gaseous refrigerant deforms the discharge valve 5. It flows out into the high pressure space 9 .
  • the high-temperature and high-pressure gaseous refrigerant that has flowed out to the high-pressure space 9 passes through the discharge muffler 7 and is discharged from the discharge pipe 45 to the outside of the container 40 .
  • the high-temperature and high-pressure gaseous refrigerant discharged from the discharge pipe 45 flows into the outdoor heat exchanger 200 .
  • part of the refrigerant sucked into the low-pressure space 8 from the suction pipe 44 passes through the suction port 36 of the frame 46 and enters the space located on the outer peripheral side of the first spiral tooth 24 and the second spiral tooth 26. It enters and is sucked into the compression unit 10 .
  • the refrigerant that has not flowed into the space located on the outer peripheral side of the first spiral tooth 24 and the second spiral tooth 26 cools the electric motor unit 30 and the oil pool 2 .
  • the space located on the outer peripheral side of the first spiral tooth 24 and the second spiral tooth 26 passes through the injection pipe 49, A liquid refrigerant or a gas-liquid two-phase refrigerant that has been decompressed by the second expansion section 600 flowing through the injection pipe 800 also flows. That is, the liquid refrigerant decompressed by the second expansion section 600 flowing through the injection pipe 800 is also sucked into the compression chamber 11 of the compression unit 10 . As a result, the liquid refrigerant cools the gaseous refrigerant in the compression chamber 11 during compression. Therefore, the temperature of the refrigerant sucked into the compression chamber 11 of the compression unit 10 is lowered. Therefore, since the thermal expansion of the fixed scroll 21 and the orbiting scroll 22 can be suppressed, the behavior of the compression unit 10 can be stabilized.
  • the refrigerant sucked into the compressor 100 is compressed by the compressor 100 and discharged in a high-temperature and high-pressure gas state.
  • the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 100 flows into the outdoor heat exchanger 200 acting as a radiator.
  • the high-temperature and high-pressure gaseous refrigerant that has flowed into the outdoor heat exchanger 200 condenses while dissipating heat to the outdoor air sent by the outdoor fan 201, and becomes a high-pressure liquid refrigerant.
  • This high-pressure liquid refrigerant flows out from the outdoor heat exchanger 200 and flows into the first expansion section 300 .
  • the high-pressure liquid refrigerant that has flowed into the first expansion section 300 is expanded and decompressed to become a low-temperature, low-pressure gas-liquid two-phase refrigerant.
  • This low-temperature, low-pressure gas-liquid two-phase refrigerant flows out from the first expansion section 300 and flows into the indoor heat exchanger 400 that functions as an evaporator.
  • the low-temperature, low-pressure gas-liquid two-phase refrigerant that has flowed into the indoor heat exchanger 400 evaporates while absorbing heat from the indoor air sent by the indoor fan 401 to become a low-pressure gaseous refrigerant. At this time, the indoor air is cooled, and cooling is performed in the room.
  • This low-pressure gaseous refrigerant flows out of the indoor heat exchanger 400 and is sucked into the compressor 100 .
  • the refrigerant discharged from the discharge pipe 45 becomes hot.
  • Such a phenomenon occurs in high compression ratio operation in which the difference between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side in the refrigeration cycle device 1 increases.
  • the liquid refrigerant decompressed by the second expansion section 600 flowing through the injection pipe 800 is sucked into the compression chamber 11 via the injection pipe 49. be.
  • the liquid refrigerant cools the gaseous refrigerant in the compression chamber 11 during compression. Therefore, in compressor 100 according to the present embodiment, the temperature of the refrigerant discharged from discharge pipe 45 can be lowered.
  • the operating range of the compressor is limited based on the temperature of the stator of the electric motor unit. That is, the compressor cannot be operated when the temperature of the stator of the electric motor unit exceeds a preset upper limit value.
  • the refrigeration cycle apparatus 1 according to the present embodiment is also configured to stop the operation of the compressor 100 when the temperature of the stator 31 of the electric motor unit 30 becomes equal to or higher than the specified temperature.
  • the specified temperature is set to 120° C., for example.
  • stator 31 of electric motor unit 30 is cooled using part of the refrigerant sucked into low-pressure space 8 from suction pipe 44 as described above.
  • the refrigerating cycle device 1 when the refrigerating cycle device 1 is in an operating state with a small refrigerant circulation amount, in order to cool the electric motor unit 30, a sufficient amount of refrigerant for cooling the electric motor unit 30 is supplied from the suction pipe 44 to the container. It is also conceivable to feed 40 low-pressure spaces 8 .
  • the refrigeration cycle device 1 when the refrigeration cycle device 1 is in an operating state with a small refrigerant circulation amount, the flow rate of the refrigerant sucked from the low-pressure space 8 into the compression unit 10 is small. As a result, part of the refrigerant in the low-pressure space 8 settles in the container 40 as liquid refrigerant, and the refrigerating machine oil stored in the oil reservoir 2 of the container 40 is diluted by the liquid refrigerant.
  • the diluted refrigerating machine oil stored in the oil reservoir 2 of the container 40 is supplied to the sliding portion of the compressor 100 . Excessive wear etc. may occur in the sliding part of For this reason, the method of cooling the stator 31 of the electric motor unit 30 using only the refrigerant supplied from the suction pipe 44 into the container 40 cannot actually sufficiently expand the operable range of the compressor 100 .
  • the compressor 100 includes the refrigerant flow path portion 60 and the supply pipe 52 as a structure for cooling the stator 31 of the electric motor unit 30.
  • FIG. 3 is a diagram for explaining the refrigerant flow path portion and the supply pipe according to the embodiment, and is a longitudinal sectional view showing the vicinity of the electric motor unit of the compressor according to the embodiment.
  • FIG. 4 is a diagram for explaining a refrigerant flow path portion and a supply pipe according to the embodiment, and is a side view showing the electric motor unit of the compressor according to the embodiment.
  • FIG. 5 is a diagram for explaining a refrigerant flow path portion and a supply pipe according to the embodiment, and is a plan view showing the stator of the electric motor unit of the compressor according to the embodiment.
  • the black-tipped arrow shown in FIG. 5 indicates the flow direction of the coolant.
  • the compressor 100 includes a supply pipe 52 and a refrigerant channel portion 60.
  • the supply pipe 52 is connected to the coolant channel portion 60 and supplies the coolant outside the container 40 to the coolant channel portion 60 .
  • the supply pipe 52 is provided, for example, in the body portion 42 of the container 40 .
  • the coolant channel portion 60 cools the stator 31 of the electric motor unit 30 with coolant supplied from the supply pipe 52 .
  • supply pipe 52 is connected to injection pipe 800 in the present embodiment. Therefore, the liquid state refrigerant or the gas-liquid two-phase state refrigerant decompressed by the second expansion portion 600 is supplied to the refrigerant flow path portion 60 .
  • the coolant channel portion 60 includes a plurality of channel portions 61 penetrating the stator 31 of the electric motor unit 30 and a pipe 62 connecting at least two of the channel portions 61 .
  • the flow path portion 61 is a real portion forming the outer peripheral portion of the through hole formed in the stator 31 .
  • each flow path portion 61 penetrates stator 31 along rotation axis O of rotor 32 in the present embodiment.
  • the arrangement position of each of the flow passages 61 is also not particularly limited, but in the present embodiment, each of the flow passages 61 is arranged on a virtual circle centered on the rotation axis O of the rotor 32 while being spaced apart. ing.
  • channel portion 61 the pipe 62 connects the ends of the adjacent channel portions 61 .
  • connection point between the supply pipe 52 and the refrigerant channel portion 60 is not particularly limited, but in the present embodiment, the supply pipe 52 is connected to one end portion of the channel portion 61 . That is, the end portion of the channel portion 61 to which the supply pipe 52 is connected serves as the coolant inlet 60 a of the coolant channel portion 60 .
  • an outlet pipe 63 is connected to the end of one flow path portion 61 . This outlet pipe 63 serves as a coolant outlet 60 b of the coolant channel portion 60 .
  • the liquid refrigerant or the gas-liquid two-phase refrigerant pressure-reduced by the second expansion section 600 is supplied from the inlet 60 a to the refrigerant passage section 60 through the injection pipe 800 and the It is supplied via the supply pipe 52 .
  • the coolant that has flowed into the coolant channel portion 60 flows from the inlet 60a toward the outlet 60b. At this time, the coolant flowing through the flow path portion 61 of the coolant flow path portion 60 cools the stator 31 of the electric motor unit 30 .
  • the refrigerant discharged from the compressor 100 may pass through the refrigerant circuit 500 and the injection pipe 800 and flow from the supply pipe 52 into the refrigerant flow path portion 60 .
  • the refrigerating machine oil that has flowed into the refrigerant flow path portion 60 in this way also contributes to the cooling of the stator 31 .
  • the refrigerating machine oil that has flowed out of the refrigerant flow path portion 60 is returned to the oil reservoir 2 .
  • provision of the supply pipe 52 and the refrigerant flow path portion 60 improves the effect of returning the refrigerating machine oil that has flowed out of the compressor 100 back to the compressor 100 .
  • the refrigerant oil may not flow into the refrigerant passage portion 60 by providing an oil separator downstream of the second expansion portion 600 in the injection pipe 800 .
  • the compressor 100 according to the present embodiment uses a refrigerant different from the refrigerant supplied from the suction pipe 44 into the container 40 as a refrigerant for cooling the stator 31 of the electric motor unit 30 . Therefore, compressor 100 according to the present embodiment operates stator 31 regardless of the amount of refrigerant supplied from suction pipe 44 into container 40, that is, regardless of the amount of refrigerant circulating in refrigeration cycle device 1. Allow to cool. Further, the liquid refrigerant or gas-liquid two-phase refrigerant flowing through the refrigerant flow path portion 60 evaporates when the stator 31 is cooled. Therefore, the gaseous refrigerant flows out from the outlet 60 b of the refrigerant flow path portion 60 .
  • the compressor 100 can expand the operable range as compared with the conventional one.
  • the outflow port 60b of the coolant channel portion 60 is preferably provided below the stator 31. If the liquid refrigerant flows out from the outflow port 60b of the refrigerant flow path portion 60, the outflow port 60b is provided in the lower portion of the stator 31, so that the outflow port 60b is provided in the upper portion of the stator 31. This is because the suction of the liquid refrigerant flowing out of the outflow port 60b into the compression chamber 11 can be suppressed. That is, it is possible to suppress excessive supply of the liquid refrigerant depressurized by the second expansion section 600 flowing through the injection pipe 800 to the compression chamber 11 .
  • the outflow port 60b is provided in the lower portion of the stator 31, so that the outflow port 60b is provided in the upper portion of the stator 31. This is because the suction of the refrigerating machine oil flowing out of the outflow port 60b into the compression chamber 11 can be suppressed. This is because the amount of refrigerating machine oil discharged from the compressor 100 can be suppressed.
  • the flow rate of refrigerant flowing from the injection pipe 800 to the supply pipe 52 is controlled by the control device 70 of the refrigeration cycle device 1 .
  • the control device 70 controls the flow rate of refrigerant flowing from the injection pipe 800 to the supply pipe 52 as follows.
  • the rotation speed of the rotor 32 of the electric motor unit 30 of the compressor 100 is low. That is, the state in which the rotational speed of the rotor 32 is low is a state in which the temperature of the stator 31 tends to increase. Note that the low rotation speed is, for example, 5 rps to 30 rps. Therefore, for example, the control device 70 causes the refrigerant to flow from the injection pipe 800 into the supply pipe 52 when the rotation speed of the rotor 32 is equal to or less than the specified rotation speed.
  • the stator 31 can be cooled by the coolant flowing through the coolant flow path portion 60 under conditions where the temperature of the stator 31 tends to rise. Therefore, the compressor 100 can expand the operable range as compared with the conventional one.
  • the specified rotation speed is set to 30 rps.
  • the refrigeration cycle device 1 is operated under various operating conditions, and the temperature of the stator 31 is measured. Then, an operating condition of the refrigeration cycle apparatus 1 that makes the temperature of the stator 31 equal to or higher than the specified temperature is obtained in advance. For example, an operating condition of the refrigeration cycle apparatus 1 that makes the motor temperature 120° C. or higher is obtained in advance. Then, for example, when the operating conditions of the refrigeration cycle device 1 are the specified operating conditions, the control device 70 causes the refrigerant to flow from the injection pipe 800 into the supply pipe 52 . As a result, the stator 31 can be cooled by the coolant flowing through the coolant flow path portion 60 under conditions where the temperature of the stator 31 tends to rise. Therefore, the compressor 100 can expand the operable range as compared with the conventional one.
  • the electric motor unit 30 has the effect of suppressing the demagnetization of the permanent magnet of the rotor 32 as the temperature becomes lower. Therefore, the control device 70 may cause the refrigerant to always flow from the injection pipe 800 into the supply pipe 52 while the compressor 100 is being driven. That is, the control device 70 may cause the refrigerant to flow from the injection pipe 800 into the supply pipe 52 at all times while the rotor 32 of the electric motor unit 30 is rotating.
  • the refrigerant decompressed by the second expansion section 600 flowing through the injection pipe 800 is supplied to the supply pipe 52, and is supplied to the injection pipe 49 of the compressor 100. is also supplied. Therefore, when the refrigerant is always flowed from the injection pipe 800 to the supply pipe 52 while the compressor 100 is being driven, the on-off valve 54 provided at the first branch of the injection pipe 800 is used to adjust the flow rate.
  • the control device 70 may control the degree of opening of the on-off valve 54, which is the flow control valve, in the open state as follows.
  • the control device 70 reduces the degree of opening of the on-off valve 54, which is the flow control valve, in the open state compared to when the on-off valve 55 is not open. good too.
  • the control device 70 reduces the degree of opening of the on-off valve 54, which is the flow control valve, in the open state compared to when the on-off valve 55 is not open. good too.
  • the amount of refrigerant supplied from the injection pipe 800 to the supply pipe 52 is lower than when the refrigerant is not supplied from the injection pipe 800 to the injection pipe 49.
  • Flow rate decreases. Therefore, it is possible to prevent a shortage of the refrigerant supplied from the injection pipe 800 to the injection pipe 49 .
  • compressor 100 described above is an example of the compressor 100 including the supply pipe 52 and the refrigerant flow path portion 60 .
  • Compressor 100 may be configured as follows, for example.
  • FIG. 6 is a diagram for explaining a refrigerant channel portion and a supply pipe in another example of the compressor according to the embodiment, and is a plan view showing the stator of the electric motor unit of the compressor. 6 indicates the direction of flow of the coolant.
  • the compressor 100 described with reference to FIGS. 1 to 5 has one refrigerant flow path section 60 .
  • the compressor 100 may include a plurality of refrigerant passage portions 60 as shown in FIG. 6 .
  • FIG. 6 illustrates a case where the compressor 100 includes three refrigerant flow path portions 60 .
  • each of the refrigerant passage portions 60 is centered on the rotation axis O of the rotor 32. , are arranged in different angular ranges.
  • the stator 31 is a clock whose hour hand rotates around the rotation axis O of the rotor 32
  • the arrangement position of each coolant channel portion 60 will be described.
  • one of the three coolant channel portions 60 is provided in the angular range from 10 o'clock to 2 o'clock.
  • One of the remaining two coolant channel portions 60 is provided in the angular range from 2 o'clock to 5 o'clock.
  • the remaining one coolant channel portion 60 is provided in the angular range from 6 o'clock to 10 o'clock.
  • the temperature of the coolant flowing through the coolant channel portion 60 rises as it cools the stator 31 .
  • the length of the refrigerant flow path portion 60 is long, so the stator 31 may have a large temperature difference depending on the location. Specifically, the temperature of the portion of the stator 31 that is cooled at the downstream side of the coolant flow in the coolant flow path portion 60 and the temperature of the stator 31 that is cooled at the upstream side of the coolant flow in the coolant flow channel portion 60 The difference from the temperature of the portion of the stator 31 where the temperature is high may become large.
  • the compressor 100 when the compressor 100 includes a plurality of refrigerant flow path sections 60, the length of each refrigerant flow path section 60 can be made shorter than when only one refrigerant flow path section 60 is provided. Therefore, when the compressor 100 includes a plurality of refrigerant flow path portions 60, the temperature difference depending on the location of the stator 31 can be suppressed compared to when only one refrigerant flow path portion 60 is provided. In other words, when the compressor 100 includes a plurality of refrigerant flow path portions 60, the cooling performance of the stator 31 can be improved compared to when only one refrigerant flow path portion 60 is provided. Therefore, when the compressor 100 includes a plurality of refrigerant flow path sections 60, the operable range of the compressor 100 can be further expanded compared to when only one refrigerant flow path section 60 is provided.
  • FIGS. 7 and 8 are diagrams for explaining another example of the compressor according to the embodiment, and are longitudinal sectional views showing the vicinity of the electric motor unit of the compressor.
  • the compressor 100 may include a temperature detection device 80 that measures the temperature of the stator 31.
  • FIG. 7 and 8 are diagrams for explaining another example of the compressor according to the embodiment, and are longitudinal sectional views showing the vicinity of the electric motor unit of the compressor.
  • the compressor 100 may include a temperature detection device 80 that measures the temperature of the stator 31.
  • the temperature detection device 80 When directly detecting the temperature of the stator 31, the temperature detection device 80 is attached to the stator 31 as shown in FIG. At this time, among the stators 31, the winding portions 31a of the stator 31 tend to have the highest temperature. Therefore, when directly detecting the temperature of the stator 31 , the temperature detection device 80 is preferably attached to the winding portion 31 a of the stator 31 .
  • the temperature detection device 80 for directly detecting the temperature of the stator 31 is not particularly limited, for example, a thermocouple can be used as the temperature detection device 80 .
  • the wiring connected to the temperature detecting device 80 must be pulled out of the container 40 . Although there is no particular limitation on the location where the wiring connected to the temperature detection device 80 is led out, the wiring is led out of the container 40 from the bottom portion 43 of the container 40 in the present embodiment.
  • the temperature detection device 80 for indirectly detecting the temperature of the stator 31 is not particularly limited, for example, a thermistor can be used as the temperature detection device 80 .
  • the thermistor is attached to the outer peripheral surface of the container 40 via, for example, a thermistor holder. In other words, the thermistor holder is attached to the outer peripheral surface of the container 40, and the thermistor is attached to the thermistor holder.
  • the control device 70 causes the refrigerant to flow from the injection pipe 800 into the supply pipe 52, for example, when the temperature detected by the temperature detection device 80 is equal to or higher than a specified temperature. .
  • the stator 31 can be cooled by the coolant flowing through the coolant channel portion 60 before the temperature of the stator 31 reaches the upper limit. Therefore, the compressor 100 can expand the operable range as compared with the conventional one.
  • the control device 70 may always cause the refrigerant to flow from the injection pipe 800 to the supply pipe 52 while the compressor 100 is being driven.
  • the control device 70 may control the flow rate of the refrigerant supplied from the injection pipe 800 to the supply pipe 52 based on the temperature detected by the temperature detection device 80 as follows. . Specifically, when the temperature detected by the temperature detection device 80 is equal to or higher than the specified temperature, the control device 70 controls the amount of fuel supplied from the injection pipe 800 to be lower than when the temperature detected by the temperature detection device 80 is lower than the specified temperature. The flow rate of the refrigerant flowing into the pipe 52 may be increased. As a result, the temperature rise of the stator 31 can be further suppressed in the configuration in which the refrigerant always flows from the injection pipe 800 into the supply pipe 52 while the compressor 100 is being driven.
  • the compressor 100 includes the electric motor unit 30, the drive shaft 33, the compression unit 10, the container 40, and the suction pipe 44.
  • the electric motor unit 30 has a rotor 32 and a stator 31 .
  • the drive shaft 33 is fixed to the rotor 32 and rotated by the power of the electric motor unit 30 .
  • the compression unit 10 is connected to the drive shaft 33 and compresses the refrigerant with the power of the electric motor unit 30 transmitted by the drive shaft 33 .
  • the container 40 accommodates the electric motor unit 30, the drive shaft 33, and the compression unit 10 therein, and the refrigerating machine oil is stored in the bottom portion 43 thereof.
  • the suction pipe 44 is provided in the container 40 and supplies the refrigerant compressed by the compression unit 10 to the inside of the container 40 .
  • the compressor 100 according to the present embodiment includes the refrigerant flow path portion 60 and the supply pipe 52 .
  • the coolant channel portion 60 includes a plurality of channel portions 61 penetrating the stator 31 and a pipe 62 connecting at least two of the channel portions 61 .
  • the supply pipe 52 is connected to the coolant channel portion 60 and supplies the coolant outside the container 40 to the coolant channel portion 60 .
  • the compressor 100 according to the present embodiment uses a refrigerant different from the refrigerant supplied from the suction pipe 44 into the container 40 as a refrigerant for cooling the stator 31 of the electric motor unit 30 . Therefore, compressor 100 according to the present embodiment operates stator 31 regardless of the amount of refrigerant supplied from suction pipe 44 into container 40, that is, regardless of the amount of refrigerant circulating in refrigeration cycle device 1. Allow to cool. Therefore, compressor 100 according to the present embodiment can expand the operable range as described above.
  • the compressor 100 according to the present embodiment is a compressor provided with the scroll-type compression unit 10 .
  • the compressor according to the present disclosure may be a compressor provided with a compression unit other than the scroll type.

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PCT/JP2022/003014 2022-01-27 2022-01-27 圧縮機及び冷凍サイクル装置 WO2023144953A1 (ja)

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CN117895703A (zh) * 2024-03-15 2024-04-16 常州天安尼康达电器有限公司 一种具有智能化可调节式散热功能的交流电机

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JPS4718006U (enrdf_load_stackoverflow) * 1971-03-31 1972-10-31
JPS6240284U (enrdf_load_stackoverflow) * 1985-08-29 1987-03-10
JPH0370062U (enrdf_load_stackoverflow) * 1989-11-08 1991-07-12
JPH03119581U (enrdf_load_stackoverflow) * 1990-03-23 1991-12-10
JP2009284755A (ja) * 2008-04-18 2009-12-03 Abb Oy 電気機械のための冷却要素
JP2013042588A (ja) * 2011-08-12 2013-02-28 Daikin Ind Ltd 電動機
CN209134205U (zh) * 2018-12-27 2019-07-19 珠海格力电器股份有限公司 压缩机电机及其电机冷却结构

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JPS5949781B2 (ja) * 1976-10-21 1984-12-05 株式会社東芝 回転電機
JP5387121B2 (ja) * 2009-05-11 2014-01-15 富士電機株式会社 回転電機

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Publication number Priority date Publication date Assignee Title
JPS4718006U (enrdf_load_stackoverflow) * 1971-03-31 1972-10-31
JPS6240284U (enrdf_load_stackoverflow) * 1985-08-29 1987-03-10
JPH0370062U (enrdf_load_stackoverflow) * 1989-11-08 1991-07-12
JPH03119581U (enrdf_load_stackoverflow) * 1990-03-23 1991-12-10
JP2009284755A (ja) * 2008-04-18 2009-12-03 Abb Oy 電気機械のための冷却要素
JP2013042588A (ja) * 2011-08-12 2013-02-28 Daikin Ind Ltd 電動機
CN209134205U (zh) * 2018-12-27 2019-07-19 珠海格力电器股份有限公司 压缩机电机及其电机冷却结构

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117895703A (zh) * 2024-03-15 2024-04-16 常州天安尼康达电器有限公司 一种具有智能化可调节式散热功能的交流电机
CN117895703B (zh) * 2024-03-15 2024-05-14 常州天安尼康达电器有限公司 一种具有智能化可调节式散热功能的交流电机

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