WO2023248325A1 - 圧縮機、および冷凍サイクル装置 - Google Patents

圧縮機、および冷凍サイクル装置 Download PDF

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Publication number
WO2023248325A1
WO2023248325A1 PCT/JP2022/024655 JP2022024655W WO2023248325A1 WO 2023248325 A1 WO2023248325 A1 WO 2023248325A1 JP 2022024655 W JP2022024655 W JP 2022024655W WO 2023248325 A1 WO2023248325 A1 WO 2023248325A1
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WIPO (PCT)
Prior art keywords
blade
cylinder
injection
groove
refrigerant
Prior art date
Application number
PCT/JP2022/024655
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English (en)
French (fr)
Japanese (ja)
Inventor
裕瑞希 川島
知秀 四至本
Original Assignee
東芝キヤリア株式会社
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.)
Filing date
Publication date
Application filed by 東芝キヤリア株式会社 filed Critical 東芝キヤリア株式会社
Priority to CN202280093809.6A priority Critical patent/CN118891447A/zh
Priority to PCT/JP2022/024655 priority patent/WO2023248325A1/ja
Priority to JP2024528132A priority patent/JPWO2023248325A1/ja
Publication of WO2023248325A1 publication Critical patent/WO2023248325A1/ja
Priority to US18/990,756 priority patent/US20250122876A1/en

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Classifications

    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid

Definitions

  • Embodiments of the present invention relate to a compressor and a refrigeration cycle device equipped with the compressor.
  • a refrigeration cycle device such as an air conditioner is configured to include a compressor, a condenser, an expansion valve, and an evaporator as main elements.
  • the compressor includes as main elements, for example, an electric motor unit that rotates a rotating shaft, a compression mechanism unit that is connected to the electric motor unit via the rotating shaft, and an airtight container that houses the electric motor unit and the compression mechanism unit.
  • the electric motor section includes, for example, a so-called inner rotor type motor, and includes a rotor fixed to a rotating shaft and a stator fixed to the inner circumference of the closed container.
  • the rotating shaft has a crank pin portion (eccentric portion).
  • the compression mechanism section includes, for example, a cylinder that forms a cylinder chamber, and a roller that is fitted onto an eccentric portion of a rotating shaft and rotates eccentrically within the cylinder chamber.
  • the cylinder chamber is divided into a refrigerant suction chamber and a compression chamber by a blade.
  • the rotating shaft is rotatably supported by a bearing disposed in the compression mechanism section.
  • an air conditioner absorbs heat from outside air with an evaporator, and supplies the heat to indoor air or hot water with a condenser.
  • the amount of heat absorbed by the evaporator increases, and the temperature and pressure of the refrigerant sucked into the compressor rise. If the compressor becomes overheated due to this, there is a possibility that the temperature of the refrigerant discharged from the compressor will rise excessively. Therefore, as a measure to suppress such a temperature rise in the compressor, a compressor equipped with an injection mechanism is known.
  • the injection mechanism has a flow path (injection flow path) that branches the refrigerant downstream of the condenser, for example, in the refrigerant circulation path.
  • the injection flow path is connected to the compression chamber of the compressor via a connecting pipe or a passage formed in the compression mechanism section.
  • Known injection mechanisms include mechanisms in which an injection port is opened and closed by the end face of a roller that rotates eccentrically within a compression chamber, and mechanisms in which a cylinder is provided with an operating mechanism such as an injection piston or a valve to control timing.
  • an injection piston or a valve to control timing.
  • the compression chamber and suction chamber may be connected within the cylinder chamber via the injection mechanism. There is a risk of communication. This causes re-expansion losses and reduces the efficiency of the compressor.
  • the structure becomes complicated due to a large number of parts, leading to an increase in manufacturing costs.
  • an increase in the number of moving parts increases the risk of failure, which may lead to a decrease in reliability.
  • the compressor includes a plurality of cylinders, depending on the route of the injection flow path within each cylinder, for example, there is a possibility that the compression chambers of these cylinders may communicate with each other via the injection mechanism. If these communications occur, there is a risk that the cooling effect of the compressor will be reduced.
  • the present invention has been made based on this, and its purpose is to provide an injection method that is low-cost, can suppress the decline in the cooling effect of the compressor, and improve the reliability of the compressor and refrigeration cycle.
  • An object of the present invention is to provide a compressor equipped with a mechanism.
  • the compressor includes a cylinder, a rotating shaft, a roller, a blade, and an injection flow path.
  • the cylinder has an annular shape and forms a cylinder chamber having a suction chamber that sucks in the refrigerant and a compression chamber that compresses the refrigerant.
  • the rotating shaft has an eccentric portion disposed within the cylinder chamber.
  • the roller is fitted into the eccentric portion and rotates eccentrically within the cylinder chamber with respect to the axis of the rotating shaft.
  • the blade has a flat shape, moves back and forth into the cylinder chamber with eccentric rotation of the roller, and divides the cylinder chamber into the suction chamber and the compression chamber.
  • the injection flow path branches from a circulation circuit in which the refrigerant circulates and guides a portion of the refrigerant circulating in the circulation circuit to the compression chamber.
  • the injection flow path includes at least a blade groove formed in a surface portion facing the compression chamber among side portions of the blade that form a pair and face in a circumferential direction with respect to the axis of the rotating shaft, and the injection flow path includes at least a blade groove formed in a surface portion facing the compression chamber.
  • a surface into which a portion of the refrigerant flows and a surface through which a portion of the refrigerant is discharged from the blade groove into the compression chamber are on the same plane.
  • FIG. 1 is a circuit diagram schematically showing the configuration of an air conditioner according to a first embodiment.
  • FIG. 1 is a longitudinal cross-sectional view of a compressor according to a first embodiment.
  • FIG. 3 is a vertical cross-sectional view schematically showing a part of the compressor shown in FIG. 2 on an enlarged scale.
  • FIG. 2 is a diagram schematically showing the compression mechanism section of the compressor according to the first embodiment from above.
  • FIG. 6 is a diagram schematically showing the positional relationship between the blade groove and the spring insertion hole in a state where the blade is most retracted with respect to the cylinder chamber in the first embodiment.
  • FIG. 1 is a first diagram schematically showing a state transition of an injection mechanism in a cylinder during a refrigerant compression process in the first embodiment.
  • FIG. 1 is a first diagram schematically showing a state transition of an injection mechanism in a cylinder during a refrigerant compression process in the first embodiment.
  • FIG. 2 is a second diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the first embodiment.
  • FIG. 3 is a third diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the first embodiment.
  • FIG. 4 is a fourth diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the first embodiment.
  • FIG. 5 is a diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the first embodiment.
  • FIG. 6 is a sixth diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the first embodiment.
  • a transition is made between a state in which the injection hole and the compression chamber communicate through the blade groove and injection is possible (injection open state), and a state in which they do not communicate and injection is impossible (injection closed state).
  • injection open state a state in which the injection hole and the compression chamber communicate through the blade groove and injection is possible
  • injection closed state a state in which they do not communicate and injection is impossible
  • FIG. 6 is a diagram showing the transition between an injection open state and an injection closed state in a case where there are three cylinders for each cylinder according to the rotation angle.
  • FIG. 7 is a vertical cross-sectional view schematically showing an enlarged portion of a compressor according to a second embodiment.
  • FIG. 7 is a diagram schematically showing a blade according to a second embodiment from a circumferential direction.
  • FIG. 1 is a first diagram schematically showing a state transition of an injection mechanism in a cylinder during a refrigerant compression process in a second embodiment.
  • FIG. 2 is a second diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the second embodiment.
  • FIG. 3 is a third diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the second embodiment.
  • FIG. 4 is a fourth diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the second embodiment.
  • FIG. 5 is a diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the second embodiment.
  • FIG. 6 is a diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the second embodiment.
  • FIG. 7 is a diagram showing a trajectory of the relationship between the rotation angle, the compression load ratio, and the groove cross-sectional area ratio in the second embodiment.
  • FIG. 7 is a diagram showing the relationship among the injection state, rotation angle, and groove cross-sectional area ratio in the second embodiment.
  • FIG. 7 is a longitudinal sectional view schematically showing an enlarged portion of a compressor according to a third embodiment.
  • FIG. 7 is a diagram schematically showing a blade according to a third embodiment from a circumferential direction.
  • FIG. 7 is a first diagram schematically showing state transitions of an injection mechanism in a cylinder during a refrigerant compression process in a third embodiment.
  • FIG. 2 is a second diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the third embodiment.
  • FIG. 3 is a third diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the third embodiment.
  • FIG. 4 is a fourth diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the third embodiment.
  • FIG. 5 is a diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the third embodiment.
  • FIG. 6 is a diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process in the third embodiment. It is a figure which shows the relationship between an injection state, a rotation angle, and a groove
  • FIG. 1 is a refrigeration cycle circuit diagram of an air conditioner 1 according to the present embodiment.
  • the air conditioner 1 is a device that performs air conditioning using such a refrigeration cycle, and is an example of a refrigeration cycle device.
  • the air conditioner 1 includes a compressor 2, a four-way valve 3, an outdoor heat exchanger 4, an outdoor blower 400, an expansion device 5, an indoor heat exchanger 6, and an indoor blower 600 as main elements.
  • the discharge side of the compressor 2 is connected to the first port 3a of the four-way valve 3.
  • the second port 3b of the four-way valve 3 is connected to the outdoor heat exchanger 4.
  • Outdoor heat exchanger 4 is connected to indoor heat exchanger 6 via expansion device 5 .
  • the indoor heat exchanger 6 is connected to the third port 3c of the four-way valve 3.
  • a fourth port 3d of the four-way valve 3 is connected to the suction side of the compressor 2 via an accumulator 8.
  • the refrigerant circulates through the circulation circuit 7 from the discharge side of the compressor 2 to the suction side via the outdoor heat exchanger 4, expansion device 5, indoor heat exchanger 6, and accumulator 8.
  • the refrigerant is preferably a refrigerant that does not contain chlorine, and for example, R32, R448A, R449A, R449B, R407G, R407H, R449C, R454A, R454B, R454C, R456A, R516A, R460B, R463A, R744, HC refrigerant, etc. are applicable. It is.
  • the four-way valve 3 is switched so that the first port 3a communicates with the second port 3b and the third port 3c communicates with the fourth port 3d.
  • the air conditioner 1 starts operating in the cooling mode, the high temperature and high pressure gas phase refrigerant compressed by the compressor 2 is discharged to the circulation circuit 7.
  • the discharged gas phase refrigerant is guided via the four-way valve 3 to the outdoor heat exchanger 4 which functions as a condenser (radiator).
  • the gas phase refrigerant guided to the outdoor heat exchanger 4 condenses through heat exchange with the air (outside air) sucked in by the outdoor blower 400, and changes into a high-pressure liquid phase refrigerant.
  • the high-pressure liquid phase refrigerant is depressurized in the process of passing through the expansion device 5 and changes into a low-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant is guided to the indoor heat exchanger 6 that functions as an evaporator (heat absorber), and exchanges heat with the air (inside air) sucked in by the indoor blower 600 during the process of passing through the indoor heat exchanger 6. do.
  • the gas-liquid two-phase refrigerant takes heat from the air and evaporates, changing into a low-temperature, low-pressure gas-phase refrigerant.
  • the air passing through the indoor heat exchanger 6 is cooled by the latent heat of vaporization of the liquid phase refrigerant, and is sent as cold air to a place to be air-conditioned (cooled) by the indoor blower 600.
  • the low-temperature, low-pressure gas phase refrigerant that has passed through the indoor heat exchanger 6 is guided to the accumulator 8 via the four-way valve 3. If the refrigerant contains liquid-phase refrigerant that has not completely evaporated, it is separated into liquid-phase refrigerant and gas-phase refrigerant here.
  • the low-temperature, low-pressure gas-phase refrigerant separated from the liquid-phase refrigerant is sucked into the compressor 2 from the accumulator 8, and is again compressed into high-temperature, high-pressure gas-phase refrigerant by the compressor 2 and discharged into the circulation circuit 7. .
  • the four-way valve 3 is switched so that the first port 3a communicates with the third port 3c and the second port 3b communicates with the fourth port 3d.
  • the air conditioner 1 starts operating in the heating mode, the high-temperature, high-pressure gas phase refrigerant discharged from the compressor 2 is guided to the indoor heat exchanger 6 via the four-way valve 3, and is used for indoor heat exchange. Heat is exchanged with the air passing through the vessel 6.
  • the indoor heat exchanger 6 functions as a condenser.
  • the gas-phase refrigerant passing through the indoor heat exchanger 6 condenses by exchanging heat with the air (inside air) sucked in by the indoor blower 600, and changes into a high-pressure liquid-phase refrigerant.
  • the air passing through the indoor heat exchanger 6 is heated by heat exchange with the gas-phase refrigerant, and is sent as warm air to a place to be air-conditioned (heated) by the indoor blower 600.
  • the high-temperature liquid-phase refrigerant that has passed through the indoor heat exchanger 6 is led to the expansion device 5, and is depressurized in the process of passing through the expansion device 5, changing into a low-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant is led to the outdoor heat exchanger 4 that functions as an evaporator, and is evaporated by exchanging heat with the air (outside air) sucked in by the outdoor blower 400, and becomes a low-temperature, low-pressure gas-phase refrigerant. Change.
  • the low-temperature, low-pressure gas-phase refrigerant that has passed through the outdoor heat exchanger 4 is sucked into the compressor 2 via the four-way valve 3 and the accumulator 8, and is again compressed into high-temperature, high-pressure gas-phase refrigerant by the compressor 2. and is discharged into the circulation circuit 7.
  • the air conditioner 1 can be operated in both the cooling mode and the heating mode, but the air conditioner 1 is, for example, a cooling-only machine or a cooling-only machine that can be operated only in either the cooling mode or the heating mode. It may also be a heating-only machine.
  • the circulation circuit 7 includes a flow path (hereinafter referred to as an injection flow path) 7a that branches the refrigerant on the downstream side of the condenser.
  • the injection flow path 7a branches a part of the refrigerant flowing from the condenser to the evaporator (hereinafter referred to as injection refrigerant) downstream of the condenser and upstream of the evaporator, and branches the refrigerant flowing into the compressor 2 (specifically, the compressor described later). This is a bypass path (injection path) leading to the chambers 23b, 24b).
  • the injection refrigerant is, for example, a liquid phase refrigerant or a gas-liquid two-phase refrigerant. In the example shown in FIG.
  • the injection flow path 7a is branched between the outdoor heat exchanger 4 and the expansion device 5, and is connected to the compressor 2 via a connecting pipe 7b.
  • the injection flow path 7a may have, for example, a solenoid valve, an expansion valve, a check valve, etc. (all not shown) on its path.
  • FIG. 2 is a vertical cross-sectional view schematically showing the compressor 2.
  • FIG. 3 is a longitudinal sectional view schematically showing a part of the compressor 2 shown in FIG. 2 in an enlarged manner.
  • the compressor 2 is a so-called vertical rotary compressor (rotary compressor), and includes an airtight container 10, a compression mechanism section 11, and an electric motor section 12 as main elements. ing.
  • the side where the compression mechanism part 11 is located is referred to as the lower side, based on the relative positional relationship between the compression mechanism part 11 and the electric motor part 12 that are lined up along the central axis O1 of the airtight container 10, which will be described later.
  • the side where the electric motor section 12 is located is the top.
  • the closed container 10 has a cylindrical peripheral wall 10a and stands perpendicular to the installation surface.
  • the installation surface is, for example, the bottom plate of the outdoor unit.
  • a discharge pipe 10b is provided at the upper end of the closed container 10.
  • the discharge pipe 10b is connected to the first port 3a of the four-way valve 3 via the circulation circuit 7.
  • An oil reservoir 10c for storing lubricating oil is provided at the bottom of the closed container 10.
  • the compression mechanism section 11 is a mechanism section that compresses refrigerant.
  • the compression mechanism section 11 is housed in the lower part of the closed container 10 so as to be immersed in lubricating oil.
  • the compression mechanism section 11 has a twin cylinder structure and includes a first cylinder 13, a second cylinder 14, and a rotating shaft 15 as main elements.
  • the first cylinder 13 and the second cylinder 14 are annular and have cylinder chambers 23, 24 having suction ports 23c, 24c for sucking refrigerant and discharge ports for discharging compressed refrigerant, as described later.
  • the first cylinder 13 and the second cylinder 14 each have rollers (rolling pistons) 16, 17 and blades 18, 19 therein. Note that the number of cylinders in the compression mechanism section is not limited to two, and may be one or three or more.
  • the first cylinder 13 is fixed to the inner peripheral surface of the peripheral wall 10a of the closed container 10 via a first bearing 21 or a frame.
  • the second cylinder 14 is fixed to the lower surface of the first cylinder 13 via a partition plate 20.
  • a first bearing 21 is fixed above the first cylinder 13.
  • the first bearing 21 covers the inner diameter portion of the first cylinder 13 from above and protrudes upward from the first cylinder 13 .
  • a space surrounded by the inner diameter portion of the first cylinder 13, the partition plate 20, and the first bearing 21 constitutes a first cylinder chamber 23.
  • the partition plate 20 corresponds to a closing member that defines the lower surface of the first cylinder chamber 23, and the first bearing 21 corresponds to a closing member that defines the upper surface of the first cylinder chamber 23.
  • a second bearing 22 is fixed below the second cylinder 14.
  • the second bearing 22 covers the inner diameter portion of the second cylinder 14 from below and protrudes downward from the second cylinder 14 .
  • a space surrounded by the inner diameter portion of the second cylinder 14, the partition plate 20, and the second bearing 22 constitutes a second cylinder chamber 24.
  • the partition plate 20 corresponds to a closing member that defines the upper surface of the second cylinder chamber 24, and the second bearing 22 corresponds to a closing member that defines the lower surface of the second cylinder chamber 24.
  • the first cylinder chamber 23 and the second cylinder chamber 24 are arranged concentrically with the central axis O1 of the closed container 10.
  • the first cylinder chamber 23 and the second cylinder chamber 24 are connected to the accumulator 8 via suction pipes 10d and 10e that are part of the circulation circuit 7.
  • the gas phase refrigerant from which the liquid phase refrigerant has been separated in the accumulator 8 is led to the first cylinder chamber 23 and the second cylinder chamber 24 from the suction ports 23c, 24c through the suction pipes 10d, 10e.
  • the rotating shaft 15 has an axial center located coaxially with the central axis O1 of the closed container 10, and passes through the first cylinder chamber 23, the second cylinder chamber 24, and the partition plate 20.
  • the rotating shaft 15 has a first journal portion 27a, a second journal portion 27b, and a pair of crank pin portions (eccentric portions) 28a and 28b. That is, the rotating shaft 15 is configured as a crankshaft.
  • the first journal portion 27a is rotatably supported by the first bearing 21.
  • the second journal portion 27b is rotatably supported by the second bearing 22.
  • the rotating shaft 15 has an extension part 27c extending coaxially from the first journal part 27a.
  • the extension part 27c penetrates the first bearing 21 and projects above the compression mechanism part 11.
  • a rotor 33 of the electric motor section 12, which will be described later, is fixed to the extension section 27c.
  • the eccentric parts 28a and 28b are located between the first journal part 27a and the second journal part 27b.
  • the eccentric portions 28a and 28b are equally spaced in the circumferential direction with a phase difference of, for example, 180 degrees, and have the same amount of eccentricity with respect to the central axis O1 of the closed container 10.
  • One eccentric portion (hereinafter referred to as a first eccentric portion) 28 a is arranged within the first cylinder chamber 23 .
  • the other eccentric portion (hereinafter referred to as a second eccentric portion) 28b is arranged within the second cylinder chamber 24.
  • FIG. 4 is a diagram schematically showing the compression mechanism section 11 from above.
  • FIG. 4 shows the internal configuration of the first cylinder 13.
  • the internal configuration of the first cylinder 13 and the internal configuration of the second cylinder 14 are substantially equivalent to each other, except for a portion that differs depending on the phase difference between the first eccentric portion 28a and the second eccentric portion 28b. Therefore, the internal configuration of the second cylinder 14 corresponds to the configuration shown in FIG. 4.
  • the cylindrical first roller 16 is fitted onto the outer peripheral surface 29a of the first eccentric portion 28a.
  • a slight gap is provided between the inner circumferential surface 16a of the first roller 16 and the outer circumferential surface 29a of the first eccentric part 28a to allow rotation of the first roller 16 with respect to the first eccentric part 28a. ing.
  • the first roller 16 rotates eccentrically with respect to the axis (center axis O1) of the rotating shaft 15 within the first cylinder chamber 23, and the first roller 16 A part of the outer circumferential surface 16b of is in contact with the inner circumferential surface of the first cylinder chamber 23.
  • the cylindrical second roller 17 is fitted onto the outer peripheral surface 29b of the second eccentric portion 28b.
  • a slight gap is provided between the inner circumferential surface 17a of the second roller 17 and the outer circumferential surface 29b of the second eccentric part 28b to allow rotation of the second roller 17 with respect to the second eccentric part 28b. ing.
  • the second roller 17 rotates eccentrically with respect to the axis (center axis O1) of the rotating shaft 15 within the second cylinder chamber 24, and the second roller 17 A part of the outer circumferential surface 17b of is in contact with the inner circumferential surface of the second cylinder chamber 24.
  • the first blade 18 is arranged in the first cylinder 13, and the second blade 19 is arranged in the second cylinder 14.
  • the first blade 18 and the second blade 19 have a substantially flat shape.
  • the cylinders 13 and 14 have blade holes 13a and 14a that are open in their inner peripheral portions, extend outward in the radial direction, and accommodate the blades 18 and 19.
  • the first blade 18 is supported in the first blade hole 13a while being biased radially inward by a spring 13b.
  • the second blade 19 is supported in the second blade hole 14a while being biased radially inward by a spring 14b.
  • the springs 13b, 14b are arranged in the spring insertion holes 13c, 14c of the cylinders 13, 14, and press the blades 18, 19 toward the rollers 16, 17 in the blade holes 13a, 14a.
  • the spring insertion holes 13c, 14c are spaces formed between the blade holes 13a, 14a and the outer peripheral surfaces of the cylinders 13, 14, and communicate with the outside of the cylinders 13, 14 in the internal space of the closed container 10. .
  • the tip portions 18a, 19a of each blade 18, 19 are pressed against the outer peripheral surfaces 16b, 17b of the rollers 16, 17 by the pressing force of springs 13b, 14b.
  • These blades 18, 19 cooperate with the rollers 16, 17 to partition the cylinder chambers 23, 24 into suction chambers 23a, 24a and compression chambers 23b, 24b, respectively, and also respond to the eccentric rotation of each roller 16, 17. Accordingly, it moves in the direction of entering (progressing) into the cylinder chambers 23, 24 or in the direction of leaving (retreating) from the cylinder chambers 23, 24, that is, moves forward and backward. As the blades 18, 19 move forward and backward with respect to the cylinder chambers 23, 24 in this way, the volumes of the suction chambers 23a, 24a and the compression chambers 23b, 24b of the cylinder chambers 23, 24 change, and from the suction pipes 10d, 10e. The gas phase refrigerant sucked into the cylinder chambers 23 and 24 is compressed.
  • the high-temperature, high-pressure gas phase refrigerant compressed in the first cylinder chamber 23 and the second cylinder chamber 24 is discharged into the closed container 10 via a discharge valve mechanism (not shown).
  • the discharged gas phase refrigerant rises inside the closed container 10.
  • the lubricating oil (refrigerating machine oil) stored in the oil reservoir 10c of the closed container 10 is stirred and becomes a mist, and the flow of the gas phase refrigerant is used to move the lubricating oil (refrigeration oil) into the closed container 10.
  • the inside of the pipe rises toward the discharge pipe 10b.
  • the electric motor section 12 is a mechanism section that drives the compression mechanism section 11 and, in short, the rotating shaft 15.
  • the electric motor section 12 is housed in an intermediate portion along the central axis O1 of the closed container 10 so as to be located between the compression mechanism section 11 and the discharge pipe 10b.
  • the electric motor section 12 includes a so-called inner rotor type motor, and includes a rotor 33 fixed to the rotating shaft 15 and a stator 34 fixed to the inner peripheral surface of the peripheral wall 10a of the closed container 10.
  • the rotor 33 includes, for example, a cylindrical rotor core coaxially fixed to the rotating shaft 15, a plurality of permanent magnets arranged on the rotor core, and the like.
  • the rotor 33 is arranged coaxially with the stator 34 with a slight air gap left inside the stator 34.
  • the stator 34 includes, for example, a cylindrical stator core and a winding (coil) wound around the stator core, and is arranged to surround the rotor 33.
  • a winding coil
  • the compressor 2 having such a configuration is equipped with an injection mechanism. Therefore, the compression mechanism section 11 has a part of the injection flow path 7a of the circulation circuit 7 as an injection mechanism.
  • the compression mechanism section 11, specifically the injection mechanism in the cylinders 13 and 14, will be described in detail. Note that in this embodiment, as described above, the internal configuration of the first cylinder 13 and the internal configuration of the second cylinder 14 differ depending on the phase difference between the first eccentric part 28a and the second eccentric part 28b. They are almost identical to each other except for the parts.
  • the injection flow path 7a has flow paths 40, 50, and 60 formed in the compressor 2, respectively. These flow paths 40 , 50 , and 60 constitute a part of the injection flow path 7 a in the compressor 2 , and compress a portion of the liquid phase refrigerant (injection refrigerant) separated from the circulation circuit 7 into the cylinders 13 and 14 . It leads to chambers 23b and 24b.
  • the flow path 40 is formed inside the partition plate 20 and connects the connecting pipe 7b and the flow path 50.
  • the flow path 50 is formed inside the cylinders 13 and 14 and connects the flow path 40 and the flow path 60.
  • the flow path 60 is formed on the side surfaces of the blades 18 and 19, and connects the flow path 50 and the compression chambers 23b and 24b.
  • Each flow path 40, 50, 60 will be further explained below.
  • the flow path (hereinafter referred to as an injection communication path) 40 opens at the outer peripheral surface 20a of the partition plate 20, extends in the radial direction, further extends along the central axis O1, and opens at the upper surface 20b and the lower surface 20c, respectively.
  • the radial direction of the partition plate 20 is a direction toward the central axis O1 along the normal to the outer peripheral surface 20a.
  • the injection refrigerant flows into the injection communication path 40 from the opening 41 on the outer peripheral surface 20a, and is guided to the opening 42a on the upper surface 20b and the opening 42b on the lower surface 20c.
  • the injection communication passage 40 includes a partition plate inlet side flow path (horizontal flow path) 40a extending in the radial direction, and two partition plate outlet side flows that branch vertically from the partition plate inlet side flow path 40a along the central axis O1.
  • Channels (vertical flow channels) 40b and 40c are constructed continuously.
  • the opening 41 communicates with the connecting pipe 7b.
  • the opening 42a communicates with an opening 53 of the cylinder 13, which will be described later.
  • the opening 42b communicates with an opening 55 of the cylinder 14, which will be described later.
  • the flow path 50 includes a flow path 51 formed inside the first cylinder 13 (hereinafter referred to as a first cylinder flow path) and a flow path formed inside the second cylinder 14 (hereinafter referred to as a second cylinder flow path). 52 (referred to as a cylinder flow path).
  • the first cylinder flow path 51 opens on the lower surface 13d of the first cylinder 13, and the second cylinder flow path 52 opens on the upper surface 14d of the second cylinder 14, and extends along the central axis O1.
  • the first and second cylinder flow paths 51 and 52 are bent and further extended in a direction intersecting the central axis O1, and open in the side walls 13e and 14e of the first and second blade holes 13a and 14a. ing.
  • the side walls 13e, 14e are located in the first and second cylinder chambers 23, 24 among a pair of side walls 13e, 13f and 14e, 14f that face each other along the circumferential direction of the first and second blade holes 13a, 14a.
  • the walls on the compression chambers 23b and 24b side in other words, the walls on the side opposite to the refrigerant suction side (suction chambers 23a and 24a) in the first and second cylinder chambers 23 and 24, that is, on the discharge side.
  • the side walls 13e and 14e are walls that face surfaces (side surfaces 18b and 19b) facing the compression chambers 23b and 24b of the blades 18 and 19, which will be described later, in the first and second blade holes 13a and 14a.
  • the injection refrigerant flows into the first and second cylinder flow paths 51 and 52 from the openings 53 and 54, and is guided to the openings (hereinafter referred to as injection holes) 54 and 56 in the side walls 13e and 14e.
  • first and second cylinder flow paths 51 and 52 include inlet side flow paths (vertical flow paths) 51a and 52a extending along the center axis O1, and inlet side flow paths 51a and 52a extending from the inlet side flow paths 51a and 52a to intersect with the center axis O1.
  • Outlet side channels (horizontal channels) 51b and 52b which extend in a bent direction are continuously formed.
  • the openings 53 and 55 communicate with the openings 42a and 42b of the partition plate outlet side flow paths 40b and 40c of the injection communication path 40.
  • the injection holes 54 and 56 can communicate with grooves of first and second blades 18 and 19, which will be described later.
  • the flow path 60 includes a flow path 61 formed in the first blade 18 (hereinafter referred to as a first blade groove) and a flow path formed in the second blade 19 (hereinafter referred to as a second blade groove). 62.
  • the first blade groove 61 and the second blade groove 62 are both formed in the shape of a groove extending along the direction in which the blades 18 and 19 move toward and away from the cylinder chambers 23 and 24 .
  • the direction in which the blades 18 and 19 move is along the radial direction of the cylinders 13 and 14.
  • the first blade groove 61 and the second blade groove 62 have substantially the same form. However, the shapes of these blade grooves 61 and 62 may be different.
  • the first and second blade grooves 61 and 62 are grooves formed in the side surfaces 18b and 19b of the first and second blades 18 and 19, and are grooves in the forward and backward directions of the first and second blades 18 and 19. It extends as a long side.
  • the side portions 18b, 19b are the compression chambers 23b, 23b of the first and second cylinder chambers 23, 24, among the side portions 18b, 18c of the first and second blades 18, 19, which form a pair and face in the circumferential direction. 24b, in other words, the surface portion of the first and second cylinder chambers 23, 24 opposite to the refrigerant suction side (suction chambers 23a, 24a), that is, the surface portion on the discharge side.
  • the first and second blade grooves 61 and 62 do not communicate with the refrigerant suction ports 23c and 24c from the suction pipes 10d and 10e in the suction chambers 23a and 24a.
  • the injection refrigerant flows into the first and second blade grooves 61 and 62 near the retreating end portions 61a and 62a, and is guided to the advancing end portions 61b and 62b.
  • the direction of movement of the first and second blades 18 and 19 toward the cylinder chambers 23 and 24 corresponds to the flow direction of the injection refrigerant in the first and second blade grooves 61 and 62.
  • the vicinity of the retreating end portions 61a and 62a can communicate with the injection holes 54 and 56 of the first and second cylinder channels 51 and 52.
  • the vicinity of the advancing side ends 61b and 62b can communicate with the compression chambers 23b and 24b, that is, can be opened toward the compression chambers 23b and 24b.
  • FIG. 5 is a diagram schematically showing the positional relationship between the blade grooves 61, 62 and the spring insertion holes 13c, 14c when the blades 18, 19 are most retracted with respect to the cylinder chambers 23, 24.
  • the groove cross-sectional area of the first blade groove 61 and the second blade groove 62 is the entire length of the groove (the dimension indicated by L in FIG. 5, hereinafter, the groove length In other words, it is substantially constant over the entire length in the longitudinal direction.
  • the groove length L is a dimension between the groove ends (between the ends 61a, 62a and the ends 61b, 62b) of each of the blade grooves 61, 62 in the advancing and retracting direction of the blades 18, 19.
  • the groove length L is the total length of the groove along the direction in which the blades 18 and 19 advance and retreat in the blade holes 13a and 14a.
  • the groove cross-sectional area is the area of a cross section perpendicular to the longitudinal direction of each blade groove 61, 62.
  • the longitudinal direction of each blade groove 61, 62 is the advancing and retreating direction of the blades 18, 19, that is, the flow direction of the injection refrigerant. Therefore, the larger the groove cross-sectional area, the larger the maximum flow rate of the injection refrigerant in each blade groove 61, 62.
  • the groove cross-sectional area is roughly estimated by the groove width and groove depth (groove depth) of the blade grooves 61 and 62.
  • the groove width is a dimension indicated by W in FIG. 5, and is the distance between the groove walls 61c, 62c and the groove walls 61d, 62d that face each other along the central axis O1 of each blade groove 61, 62.
  • the groove depth (groove depth) is the dimension shown by D in FIG. 62d) is the distance to 61e and 62e.
  • the groove cross-sectional area (W ⁇ D) of the first blade groove 61 is less than or equal to the opening area (S1) of the opening (injection hole) 54 of the first cylinder flow path 51 (W ⁇ D ⁇ S1). Further, the groove cross-sectional area (W ⁇ D) of the second blade groove 62 is set to be less than or equal to the opening area (S2) of the opening (injection hole) 56 of the second cylinder flow path 52 (W ⁇ D ⁇ S2 ).
  • the groove cross-sectional area of the first blade groove 61 and the groove cross-sectional area of the second blade groove 62 are approximately equal, but they may be different. Further, although the opening area (S1) of the injection hole 54 and the opening area (S2) of the injection hole 56 are approximately equal, they may be different.
  • the first blade groove 61 and the second blade groove 62 having such groove width W, groove depth D, and groove length L are formed in the side surfaces 18b and 19b of the blades 18 and 19. .
  • the cylinders 13 and 14 have spring insertion holes 13c and 14c in which springs 13b and 14b are arranged.
  • the blades 18 and 19 are supported in the blade holes 13a and 14a while being biased by springs 13b and 14b.
  • side portions 18b, 19b of the blades 18, 19 and side walls 13e, 14e of the blade holes 13a, 14a are positioned opposite to each other. That is, in this state, the blade grooves 61, 62 and the injection holes 54, 56 are positioned so as to be able to face each other.
  • the first blade groove 61 and the second blade groove 62 can communicate with the injection holes 54, 56 near the retreating side ends 61a, 62a, and the compression chambers 23b, 56 near the advancing side ends 61b, 62b. 24b.
  • the first blade groove 61 and the second blade groove 62 are not able to communicate with the spring insertion holes 13c and 14c. That is, within the range in which the blades 18 and 19 move forward and backward in the blade holes 13a and 14a, the blade grooves 61 and 62 cannot communicate with the spring insertion holes 13c and 14c, that is, they are arranged so that they cannot be opened toward the spring insertion holes 13c and 14c. has been done.
  • the state in which the blades 18, 19 are most regressed with respect to the cylinder chambers 23, 24 is, for example, when the first eccentric portion 28a (first roller 16) or the second eccentric portion 28b (second roller 17) is at the top dead end. It is in a state where it is located at a point.
  • the first blade groove 61 is arranged so that when the blades 18, 19 are most retracted with respect to the cylinder chambers 23, 24, the retracted end portions 61a, 62a do not overlap the spring insertion holes 13c, 14c in the circumferential direction.
  • the position of the second blade groove 62 for example, the groove length L, is set.
  • the retreating end portions 61a, 62a do not reach the retreating end surface portions 18d, 19d of the blades 18, 19, and end in front of the end surface portions 18d, 19d. Therefore, in the state where the blades 18, 19 are most retracted with respect to the cylinder chambers 23, 24, the retracted end portions 61a, 62a are located closer to the axis of the rotating shaft 15 (center axis O1) than the spring insertion holes 13c, 14c. ) located closer to
  • the first eccentric part 28a and the second eccentric part 28b of the rotating shaft 15, and the first roller 16 and the second roller 17 are connected to the rotating shaft 15 with a phase difference ( ⁇ ) of 180°. It is located. Therefore, the first blade groove 61 and the second blade groove 62 are formed in the injection hole 54 within a range in which the rotational phase (angle) of the eccentric portions 28a, 28b of the rotating shaft 15 is smaller than 180° across the bottom dead center. , 56 and the compression chambers 23b, 24b, but not in communication with the spring insertion holes 13c, 14c. Further, the first blade groove 61 and the second blade groove 62 are arranged and have a groove length L such that they do not communicate with the space behind the blade holes 13a, 14a at the top dead center.
  • FIGS. 6A to 6F are diagrams schematically showing the state transition of the injection mechanism in the cylinders 13 and 14 during the refrigerant compression process.
  • the first blade groove 61 and the second blade groove 62 are arranged so that the injection hole 54, 56, that is, can communicate with the compression chambers 23b and 24b.
  • the rotation direction of the rollers 16 and 17 is the direction shown by arrow A in FIGS. 6A to 6F.
  • the rotation angle (crank angle) of the eccentric parts 28a, 28b (rollers 16, 17) from the top dead center is 91° to 269°, that is, the rotational phase ( ⁇ ) is 178°.
  • the first blade groove 61 and the second blade groove 62 communicate with the injection holes 54, 56 and the compression chambers 23b, 24b.
  • the injection holes 54 and 56 and the compression chambers 23b and 24b communicate with each other via the blade grooves 61 and 62. That is, the rotational phase ( ⁇ ) of the eccentric portions 28a, 28b (rollers 16, 17) through which the injection refrigerant is injected into the compression chambers 23b, 24b is 178°. Therefore, the rotational phase ( ⁇ ) that allows injection is smaller than the equidistant angle of the eccentric portions 28a, 28b (rollers 16, 17) on the rotating shaft 15, that is, the phase difference ( ⁇ ) ( ⁇ ).
  • the compression chambers 23b, 24b, the blade grooves 61, 62, and the injection holes 54, 56 are arranged equidistantly on the eccentric parts 28a, 28b during one revolution of the rotating shaft 15. They communicate through an angle, that is, an angular range ( ⁇ ) smaller than the phase difference ( ⁇ ).
  • the phase difference ( ⁇ ) between the eccentric portions 28a and 28b (rollers 16 and 17) on the rotating shaft 15 is 180°. Therefore, for example, if the position of the first blade 18 when the rotation angle of the eccentric parts 28a, 28b and the rollers 16, 17 is 0° is the top dead center, the position of the second blade 19 at that time is the bottom dead center. It becomes the dead point. Therefore, although the injection mechanisms in the cylinders 13 and 14 have different injection states at the start time depending on the phase difference, the state transition cycles are the same.
  • FIG. 7A shows the transition between a state where the injection holes 54 and 56 and the compression chambers 23b and 24b communicate via the blade grooves 61 and 62 (injection open state) and a state where they do not communicate (injection closed state).
  • 28 is a diagram showing each cylinder 13 and 14 according to the rotation angle of 28a and 28b and rollers 16 and 17.
  • the first blade 18 is positioned at the top dead center, and the first blade 18 It is not communicating with either. That is, the compression chamber 23b, simply the first cylinder 13, is in a state in which no injection refrigerant is injected (hereinafter referred to as an injection closed state). At this time, the second blade groove 62 is in communication with both the compression chamber 24b and the injection hole 56. That is, the compression chamber 24b, briefly the second cylinder 14, is in a state into which the injection refrigerant is injected (hereinafter referred to as an injection open state).
  • the injection closed state in the first cylinder 13 continues until the rotation angle of the eccentric portion 28a and the roller 16 is from 0° to a predetermined rotation angle.
  • the injection open state continues.
  • the first blade groove 61 communicates with the injection hole 54 and further begins to communicate with the compression chamber 23b.
  • the state will be as follows. That is, the first cylinder 13 is in a state into which the injection refrigerant is injected (injection open state).
  • the second blade groove 62 is in a state where it does not communicate with either the compression chamber 24b or the injection hole 56. That is, the compression chamber 24b, briefly the second cylinder 14, is in a state in which no injection refrigerant is injected (injection closed state).
  • both the first cylinder 13 and the second cylinder 14 enter the injection closed state. Even if the rotation angle of the eccentric portion 28a and the roller 16 reaches 91°, the second cylinder 14 continues to be in the injection closed state.
  • the first blade 18 is positioned at the bottom dead center.
  • the blade groove 61 continues to communicate with both the compression chamber 23b and the injection hole 54. That is, the first cylinder 13 continues to be in the injection open state. Further, the second cylinder 14 continues to be in the injection closed state.
  • the injection open state in the first cylinder 13 continues until the rotation angle of the eccentric portion 28a and the roller 16 is from 180° to a predetermined rotation angle.
  • the injection closed state continues.
  • the first cylinder 13 continues to be in the injection closed state, but the second cylinder 14 is in communication with the injection hole 56, Furthermore, it enters a state in which it begins to communicate with the compression chamber 24b. That is, the second cylinder 14 transitions to the injection open state. Then, the rotation angle of the eccentric portion 28a and the roller 16 becomes 360°, and when these rotate once, the first cylinder 13 continues to have an injection closed state, and the second cylinder 14 continues to have an injection open state. .
  • the cylinders 13, 14 are both in the injection closed state twice, specifically when the rotation angle is 90° and 270°. There is.
  • the rotation angle is other than that, one of the cylinders 13 and 14 is in the injection closed state, and the other is in the injection open state. Therefore, the first cylinder 13 and the second cylinder 14 do not communicate with each other via the injection mechanism (flow paths 40, 50, 60).
  • both the injection closed state of the first cylinder 13 and the injection open state of the second cylinder 14 continue. Even when the rotation angle reaches 450 degrees, the injection open state of the first cylinder 13 continues. On the other hand, when the rotation angle reaches 450 degrees, the second cylinder 14 transitions to the injection closed state. That is, at this time, both the first cylinder 13 and the second cylinder 14 are in the injection closed state.
  • the number of cylinders is not limited to this.
  • the transition between injection enablement and non-injection in each cylinder is as follows.
  • the rotating shaft has three eccentric parts arranged at equal intervals (phase difference of 120°). These eccentrics are equipped with rollers located within each cylinder. When the rotating shaft rotates, these eccentric parts and rollers rotate eccentrically with respect to the rotating shaft with a phase difference of 120°.
  • the three cylinders are equipped with an injection mechanism having flow paths that are substantially the same as the flow paths 40, 50, and 60 of the injection mechanism described above.
  • the refrigeration cycle circuit of the air conditioner 1 communicates with the compression mechanism section 11 via the injection flow path 7a and the connecting pipe 7b, and within the compression mechanism section 11, the first, second, and third cylinders are connected. It has a flow path that branches and communicates with each other.
  • FIG. 7B shows an example of the transition between the injection open state and the injection closed state depending on the rotation angle of the eccentric part and the roller when the compressor is equipped with three cylinders (first cylinder, second cylinder). cylinder, third cylinder).
  • each of the three eccentric parts is eccentric at an angle of 120 degrees, and the compression process progresses in the order of the first cylinder, the second cylinder, and the third cylinder as the rotating shaft rotates.
  • the third cylinder transitions to the injection closed state.
  • the first cylinder and the second cylinder continue to be in the injection closed state. That is, at this time, all cylinders are in the injection closed state.
  • the first cylinder transitions to the injection open state.
  • the second cylinder and the third cylinder continue to be in the injection closed state. Thereafter, even when the rotation angle becomes 180° or even 238°, the first cylinder continues to be in the injection open state, and the second cylinder and the third cylinder continue to be in the injection closed state.
  • the first cylinder transitions to the injection closed state.
  • the second cylinder and the third cylinder continue to be in the injection closed state. That is, at this time, all cylinders are in the injection closed state.
  • the second cylinder transitions to the injection open state.
  • the first cylinder and the third cylinder continue to be in the injection closed state. Thereafter, even when the rotation angle becomes 300° or even 358°, the first cylinder and the third cylinder continue to be in the injection closed state, and the second cylinder continues to be in the injection open state.
  • the second cylinder transitions to the injection closed state.
  • the first cylinder and the third cylinder continue to be in the injection closed state. That is, at this time, all cylinders are in the injection closed state.
  • the third cylinder transitions to the injection open state.
  • the first cylinder and the second cylinder continue to be in the injection closed state. Thereafter, even when the rotation angle becomes 420° or even 478°, the first cylinder and the second cylinder continue to be in the injection closed state, and the third cylinder continues to be in the injection open state.
  • the third cylinder transitions to the injection closed state.
  • the first cylinder and the second cylinder continue to be in the injection closed state. That is, at this time, all cylinders are in the injection closed state.
  • the third cylinder transitions to the injection open state.
  • the second cylinder and the third cylinder continue to be in the injection closed state.
  • the first cylinder continues to be in the injection closed state, and the second cylinder and the third cylinder continue to be in the injection closed state.
  • the first cylinder transitions to the injection closed state.
  • the second cylinder and the third cylinder continue to be in the injection closed state. That is, at this time, all cylinders are in the injection closed state.
  • the second cylinder transitions to the injection open state.
  • the first cylinder and the third cylinder continue to be in the injection closed state. Thereafter, even when the rotation angle becomes 660° or even 718°, the first cylinder and the third cylinder continue to be in the injection closed state, and the second cylinder continues to be in the injection open state.
  • the second cylinder transitions to the injection closed state.
  • the first cylinder and the third cylinder continue to be in the injection closed state. That is, at this time, all cylinders are in the injection closed state.
  • the blade grooves 61 and 62 cannot communicate with the spring insertion holes 13c and 14c within the range where the blades 18 and 19 move forward and backward in the blade holes 13a and 14a. 14c so that it cannot be opened. Therefore, it is possible to prevent the blade grooves 61 and 62 from communicating with the inside of the closed container 10 filled with lubricating oil (refrigerating machine oil). Therefore, the compressor 2 can be cooled by appropriately injecting the injection refrigerant into the compression chambers 23b and 24b. As a result, it is possible to suppress a decrease in the cooling effect of the compressor 2 and improve reliability.
  • lubricating oil refrigerating machine oil
  • the rotational phase ( ⁇ ) of the eccentric parts 28a, 28b (rollers 16, 17) that can be injected is the phase difference ( ⁇ ) of the eccentric parts 28a, 28b (rollers 16, 17) on the rotating shaft 15. ( ⁇ ). Therefore, it is possible to prevent the blade grooves 61 and 62, the cylinder flow paths 51 and 52, and the injection communication path 40 from communicating with each other. Therefore, the compression chamber 23b of the first cylinder 13 and the compression chamber 24b of the second cylinder 14 are prevented from communicating through the blade grooves 61, 62, the cylinder flow paths 51, 52, and the injection communication path 40. can. Thereby, it becomes possible to suppress a decrease in compression performance in the compressor 2.
  • the blade grooves 61 and 62 are provided in the side surfaces 18b and 19b. That is, the blade grooves 61 and 62 are arranged on the opposite side of the refrigerant suction side (suction chambers 23a and 24a) in the cylinder chambers 23 and 24, that is, on the discharge side. Therefore, the blade grooves 61 and 62 can be made incommunicable with the refrigerant suction ports 23c and 24c in the suction chambers 23a and 24a. Therefore, a decrease in the amount of refrigerant sucked due to communication between the blade grooves 61 and 62 and the suction ports 23c and 24c can be suppressed.
  • a compressor having two cylinders and a compressor having three cylinders have been described, but in both compressors, the injection flow path is opened to a plurality of cylinders at the same time.
  • the middle part of the injection circuit that communicates with multiple cylinders is common, even if a pressure difference occurs due to a difference in the compression process of multiple cylinders, backflow from each cylinder to the injection flow path is prevented. It can be prevented.
  • performance deterioration can be suppressed and a high COP can be maintained.
  • the groove cross-sectional area (W ⁇ D) of the first blade groove 61 and the second blade groove 62 is substantially constant over the groove length L.
  • the groove cross-sectional area of the blade groove is not substantially constant over the groove length, and may have a plurality of portions with different groove cross-sectional areas.
  • such a groove configuration will be described as a second embodiment.
  • the basic configuration of the compressor 2a according to the second embodiment is the same as that of the compressor 2 of the first embodiment shown in FIG. Therefore, in the second embodiment, for each configuration of the compressor 2a that is the same as or similar to the compressor 2, the configuration of the compressor 2 shown in FIG. 2 will be referred to, and the same reference numerals will be used and the description will be omitted.
  • the compressor 2a like the compressor 2, can be applied as one of the components of the air conditioner 1 (FIG. 1) of the first embodiment.
  • FIG. 8 is a longitudinal sectional view schematically showing an enlarged part of the compressor 2a.
  • the first blade groove 63 and the second blade groove 64 of this embodiment have two portions with different groove cross-sectional areas. However, there may be three or more such parts.
  • the configurations of the first blade groove 63 and the second blade groove 64 are substantially the same.
  • FIG. 9 is a diagram schematically showing the blade according to the second embodiment from the circumferential direction.
  • the blade grooves 63 and 64 have two portions having different groove cross-sectional areas, a first groove portion 71 and a second groove portion 72.
  • the first groove portion 71 and the second groove portion 72 are continuous in the entire length direction of the blade grooves 63 and 64, and constitute the respective blade grooves 63 and 64.
  • the first groove portion 71 is arranged on the advancing side of the blades 18 and 19 in the advancing and retreating direction toward the cylinder chambers 23 and 24.
  • the second groove portion 72 is arranged on the retreating side of the direction in which the blades 18 and 19 move toward and away from the cylinder chambers 23 and 24 . That is, in the advance/retreat direction, the first groove part 71 is located closer to the advancing direction than the second groove part 72, and conversely, the second groove part 72 is located closer to the retreating direction than the first groove part 71 is.
  • the first groove portion 71 and the second groove portion 72 have substantially the same groove depth, but have different groove widths. As a result, the first groove portion 71 and the second groove portion 72 have different groove cross-sectional areas.
  • the groove width of the first groove portion 71 (dimension indicated by W1 in FIG. 9) is smaller than the groove width W2 of the second groove portion 72 (W1 ⁇ W2).
  • the groove depths of the first groove portion 71 and the second groove depth are equivalent to the groove depth D of the blade grooves 61 and 62 of the first embodiment.
  • the groove width W1 of the first groove part 71 is smaller than the groove width W of the blade grooves 61 and 62 of the first embodiment
  • the groove width W2 of the second groove part 72 is smaller than the groove width W of the blade grooves 61 and 62 of the first embodiment. It is larger than the groove width W of the blade grooves 61 and 62. Therefore, the groove cross-sectional area (W1 ⁇ D) of the first groove portion 71 is smaller than the groove cross-sectional area (W ⁇ D) of the blade grooves 61 and 62
  • the groove cross-sectional area (W2 ⁇ D) of the second groove portion 72 is smaller than that of the blade grooves 61 and 62. It is larger than the groove cross-sectional area of the blade grooves 61 and 62. That is, the blade grooves 63 and 64 are tapered in the direction in which the blades 18 and 19 move toward the cylinder chambers 23 and 24.
  • the groove length of the blade grooves 63 and 64 may be the same as the groove length L of the blade grooves 61 and 62 according to the first embodiment. , may be different.
  • the groove length La of the blade grooves 63, 64 is such that when the blades 18, 19 are most retracted with respect to the cylinder chambers 23, 24, the retracted end, that is, the end 72a of the second groove 72 is It is sufficient if the dimensions are set so as not to overlap the insertion holes 13c and 14c in the circumferential direction.
  • the groove length La of the blade grooves 63 and 64 is equal to the groove length L of the blade grooves 61 and 62.
  • FIGS. 10A to 10F are diagrams schematically showing the state transition of the injection mechanism in the cylinders 13 and 14 during the refrigerant compression process.
  • the first eccentric part 28a and the first roller 16 of the first cylinder 13 and the second eccentric part 28b of the second cylinder 14 and the second roller 17 have a phase difference of 180°. and is arranged on the rotating shaft 15. Therefore, for example, if the position of the first blade 18 when the rotation angle of the eccentric parts 28a, 28b and the rollers 16, 17 is 0° is the top dead center, the position of the second blade 19 at that time is the bottom dead center. It becomes the dead point. Therefore, although the injection mechanisms in the cylinders 13 and 14 have different injection states at the start time depending on the phase difference, the state transition cycles are the same.
  • the first blade 18 is positioned at the top dead center.
  • the first blade groove 63 is in a state where it does not communicate with either the compression chamber 23b or the injection hole 54. That is, the first cylinder 13 is in the injection closed state.
  • the second blade groove 62 is in communication with both the compression chamber 24b and the injection hole 56. That is, the second cylinder 14 is in the injection open state.
  • the injection closed state in the first cylinder 13 continues until the rotation angle of the eccentric portion 28a and the roller 16 is from 0° to a predetermined rotation angle.
  • the injection open state continues.
  • the first blade groove 63 is in communication with the injection hole 54 and has started to communicate with the compression chamber 23b. becomes. That is, the first cylinder 13 is in the injection open state. At this time, the first blade groove 63 communicates with the compression chamber 23b through the first groove portion 71, and does not communicate with the compression chamber 23b through the second groove portion 72. In other words, the first blade groove 63 communicates with the compression chamber 23b only through the first groove 71, which has a smaller groove cross-sectional area than the second groove 72.
  • the second blade groove 64 is in a state where it does not communicate with either the compression chamber 24b or the injection hole 56. That is, the second cylinder 14 is in the injection closed state. Therefore, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 90 degrees, both the first cylinder 13 and the second cylinder 14 enter the injection closed state. Even if the rotation angle of the eccentric portion 28a and the roller 16 reaches 91°, the second cylinder 14 continues to be in the injection closed state.
  • the first blade 18 is positioned at the bottom dead center.
  • the blade groove 63 continues to communicate with both the compression chamber 23b and the injection hole 54. That is, the first cylinder 13 continues to be in the injection open state.
  • the first blade groove 63 communicates with the compression chamber 23b through the first groove portion 71 and also communicates with the compression chamber 23b through the second groove portion 72. Further, the second cylinder 14 continues to be in the injection closed state.
  • the injection open state in the first cylinder 13 continues until the rotation angle of the eccentric portion 28a and the roller 16 is from 180° to a predetermined rotation angle.
  • the injection closed state continues.
  • the first blade groove 63 communicates with the injection hole 54 but does not communicate with the compression chamber 23b. That is, the first cylinder 13 is in the injection closed state.
  • the second cylinder 14 continues to be in the injection closed state. Therefore, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 270 degrees, the first cylinder 13 and the second cylinder 14 are both in the injection closed state.
  • the first cylinder 13 continues to be in the injection closed state, but the second cylinder 14 is in communication with the injection hole 56, Furthermore, it enters a state in which it begins to communicate with the compression chamber 24b. That is, the second cylinder 14 transitions to the injection open state. Then, the rotation angle of the eccentric portion 28a and the roller 16 becomes 360°, and when these rotate once, the first cylinder 13 continues to have an injection closed state, and the second cylinder 14 continues to have an injection open state. .
  • the cylinders 13, 14 are both in the injection closed state twice, specifically when the rotation angle is 90° and 270°. There is.
  • the rotation angle is other than that, one of the cylinders 13 and 14 is in the injection closed state, and the other is in the injection open state. Therefore, the first cylinder 13 and the second cylinder 14 do not communicate with each other via the injection mechanism (flow paths 40, 50, 60).
  • FIG. 11 is a diagram showing the locus of the relationship between the rotation angle, the compression load ratio, and the groove cross-sectional area ratio.
  • FIG. 12 is a diagram showing the relationship among the injection state, rotation angle, and groove cross-sectional area ratio.
  • the rotation angle is the rotation angle of the eccentric portion and the roller from the top dead center.
  • the compression load ratio is a locus shown by a solid line in FIG. 11, and is a value in which the state where the refrigerant is not compressed in the compression chamber of the cylinder is set to 0.
  • the groove cross-sectional area ratio is the locus shown by the broken line in FIG.
  • the injection state is either an open injection state or a closed injection state in the compression chamber of the cylinder.
  • the compression load ratio is 0 when the rotation angle is 0°, gradually increases from there, reaches a peak at about 200°, gradually decreases, and returns again at 360°. It becomes 0.
  • the groove cross-sectional area ratio is 0.
  • the injection is in an open state until the rotation angle reaches 135° and reaches 160°.
  • the first blade groove 63 communicates with the compression chamber 23b only through the first groove 71, which has a smaller cross-sectional area than the second groove 72. Therefore, the groove cross-sectional area ratio is a value smaller than 1, here 0.9.
  • the first blade groove 63 communicates with the compression chamber 23b through the first groove portion 71, and also communicates with the compression chamber 23b through the second groove portion 72. That is, the first blade groove 63 communicates with the compression chamber 23b through the second groove portion 72, which has a larger cross-sectional area than the blade grooves 61 and 62. Therefore, the groove cross-sectional area ratio has a value greater than 1, here 1.8.
  • the injection open state continues until the rotation angle reaches 200° and reaches 225°.
  • the first blade groove 63 does not communicate with the second groove part 72, but communicates with the compression chamber 23b only with the first groove part 71. Therefore, the groove cross-sectional area ratio is a value smaller than 1, here 0.9.
  • the groove cross-sectional area of the first groove portion 71 enters the injection open state.
  • the second groove 72 having a larger groove cross-sectional area than the first groove 71 enters an injection open state in communication with the compression chambers 23b and 24b.
  • the open injection state in which the second groove portion 72 communicates with the compression chambers 23b and 24b ends.
  • the first groove 71 communicates with the compression chambers 23b and 24b, and the injection open state in the cross-sectional area of the first groove 71 continues.
  • the first groove portion 71 also ceases to communicate with the compression chambers 23b and 24b, resulting in the injection closed state.
  • the blade grooves 63, 64 start communicating with the compression chambers 23b, 24b and the injection holes 54, 56 from this state, the injection is opened again at the groove cross-sectional area of the first groove portion 71. Thereafter, such a transition between the injection open state and the injection closed state is repeated.
  • the first groove part 71 by making the groove cross-sectional areas of the first groove part 71 and the second groove part 72 different, the first groove part 71
  • the groove cross-sectional area of the blade grooves 63 and 64 can be expanded from the groove cross-sectional area of the second groove portion 72 to the groove cross-sectional area of the second groove portion 72.
  • the amount of injection refrigerant injected into the compression chambers 23b, 24b can be suppressed at the start and end of compression of the refrigerant, and the amount of injection refrigerant can be increased even more when compression has progressed. That is, the amount of injection refrigerant can be increased during the progress of compression, which requires cooling, than at the start of compression or the end of compression.
  • the groove cross-sectional area of the blade grooves 63 and 64 can be expanded in a short section corresponding to the entire length of the grooves.
  • the switching time between the open state and the closed state of the injection can be shortened, the pressure in the compression chambers 23b and 24b is higher than the pressure in the injection flow path 7a, and the time in which the injection is in the open state can be shortened.
  • the groove cross-sectional area of the blade grooves 63, 64 can be made smaller than the groove cross-sectional area of the blade grooves 61, 62. .
  • backflow of the refrigerant being compressed into the injection flow path 7a can be suppressed. Therefore, it is possible to suppress a decrease in the cooling effect of the compressor 2a and improve reliability. In addition, it is possible to prevent the refrigerant from flowing backward, suppressing performance deterioration, and maintaining a high COP.
  • the first blade 18 and the second blade 19 each have one blade groove 61, 62.
  • each blade may have multiple blade grooves.
  • such a groove configuration will be described as a third embodiment.
  • the basic configuration of the compressor 2b is the same as that of the compressor 2 of the first embodiment shown in FIG. Therefore, in the third embodiment, for each configuration of the compressor 2b that is the same as or similar to the compressor 2, the configuration of the compressor 2 shown in FIG. 2 will be referred to, and the same reference numerals will be used and the description will be omitted.
  • the compressor 2b like the compressor 2, can be applied as one of the components of the air conditioner 1 (FIG. 1) of the first embodiment.
  • FIG. 13 is a longitudinal sectional view schematically showing an enlarged part of the compressor 2b.
  • the first blade 18 has two blade grooves 651, 652, and the second blade 19 has two blade grooves 661, 662.
  • the number of blade grooves may be three or more, or may be different between the first blade 18 and the second blade 19.
  • the configurations of the blade groove 651 and the blade groove 661 and the configurations of the blade groove 652 and the blade groove 662 are substantially the same.
  • FIG. 14 is a diagram schematically showing the blade according to the third embodiment from the circumferential direction.
  • the blade grooves 651, 661 and the blade grooves 652, 662 have different groove lengths.
  • the groove length L1 of the blade grooves 651 and 661 is longer than the groove length L2 of the blade grooves 652 and 662 (L1>L2).
  • the blade grooves 651, 661 are arranged on one side (lower side) in the direction along the central axis O1, and the blade grooves 652, 662 are arranged on the other side (upper side) in the direction.
  • the blade grooves 651, 661 will be referred to as lower blade grooves 651, 661
  • the blade grooves 652, 662 will be referred to as upper blade grooves 652, 662.
  • the positions of the retreating side ends 651a and 661a and the ends 652a and 662a of the lower blade grooves 651 and 661 and the upper blade grooves 652 and 662 are the same, and the positions of the advancing side ends are the same.
  • the positions of the ends 651b, 661b and the ends 652b, 662b are different.
  • the advancing side ends 651b, 661b of the lower blade grooves 651, 661 are closer to the center axis O1 (leftward in FIG. 14) than the advancing side ends 652b, 662b of the upper blade grooves 652, 662. It is located in
  • the groove length L1 of the lower blade grooves 651, 661 and the groove length L2 of the upper blade grooves 652, 662 are such that when the blades 18, 19 are most retracted with respect to the cylinder chambers 23, 24, the retracted end 651a, It is only necessary that the dimensions of the spring insertion holes 661a, 652a, and 662a are set so that they do not overlap with the spring insertion holes 13c and 14c in the circumferential direction.
  • the groove length L1 of the lower blade grooves 651, 661 is longer than the groove length L2 of the upper blade grooves 652, 662.
  • the length of the groove may be reversed from the illustrated example.
  • the groove length may be different between the first blade 18 and the second blade 19, but in one blade, the upper blade groove and the lower blade groove are made to have different groove lengths.
  • the groove widths of the lower blade grooves 651 and 661 and the groove widths of the upper blade grooves 652 and 662 are approximately the same.
  • the groove depths of the lower blade grooves 651 and 661 and the groove depths of the upper blade grooves 652 and 662 are approximately the same. Therefore, the groove cross-sectional area of the lower blade grooves 651, 661 and the groove cross-sectional area of the upper blade grooves 652, 662 are approximately equal.
  • the groove width and groove depth of the lower blade grooves 651 and 661 may be different from the groove width and groove depth of the upper blade grooves 652 and 662.
  • the groove cross-sectional area of the lower blade grooves 651, 661 and the groove cross-sectional area of the upper blade grooves 652, 662 are the groove cross-sectional area of the blade grooves 61, 62 of the first embodiment (W ⁇ D ) is smaller than.
  • the sum of the groove cross-sectional areas of the lower blade grooves 651, 661 and the upper blade grooves 652, 662 is larger than the groove cross-sectional area (W ⁇ D) of the blade grooves 61, 62.
  • the first cylinder flow path 51 is configured with an inlet side flow path (vertical flow path) 51a and two outlet side flow paths 511b and 512b. ing. That is, the inlet side flow path 51a is branched into two outlet side flow paths 511b and 512b.
  • One outlet side flow path 511b communicates with the opening (injection hole 54a) of the side wall 13e of the first blade hole 13a.
  • the other outlet side flow path 512b communicates with the opening (injection hole 54b) of the side wall 13e of the first blade hole 13a.
  • the injection hole 54a and the injection hole 54b open at different locations on the side wall 13e.
  • the injection refrigerant After flowing into the inlet side flow path 51a, the injection refrigerant is divided into two outlet side flow paths 511b and 512b and guided to the injection holes 54a and 54b, respectively.
  • the injection hole 54a can communicate with the lower blade groove 651 of the first blade 18, and the injection hole 54b can communicate with the upper blade groove 652 of the first blade 18.
  • the second cylinder flow path 52 includes an inlet side flow path (vertical flow path) 52a and two outlet side flow paths 521b and 522b that are continuous. That is, the inlet side flow path 52a is branched into two outlet side flow paths 521b and 522b.
  • One outlet side flow path 521b communicates with the opening (injection hole 56a) of the side wall 14e of the second blade hole 14a.
  • the other outlet side flow path 512b communicates with the opening (injection hole 56b) of the side wall 14e of the second blade hole 14a.
  • the injection hole 56a and the injection hole 56b open at different locations on the side wall 14e.
  • the injection refrigerant After flowing into the inlet side flow path 52a, the injection refrigerant is divided into two outlet side flow paths 521b and 522b and guided to the injection holes 56a and 56b, respectively.
  • the injection hole 56a can communicate with the lower blade groove 661 of the second blade 19
  • the injection hole 56b can communicate with the upper blade groove 662 of the second blade 19.
  • FIGS. 15A to 15F are diagrams schematically showing the state transition of the injection mechanism in the cylinders 13 and 14 during the refrigerant compression process.
  • the first eccentric part 28a and the first roller 16 of the first cylinder 13 and the second eccentric part 28b of the second cylinder 14 and the second roller 17 have a phase difference of 180°. and is arranged on the rotating shaft 15. Therefore, for example, if the position of the first blade 18 when the rotation angle of the eccentric parts 28a, 28b and the rollers 16, 17 is 0° is the top dead center, the position of the second blade 19 at that time is the bottom dead center. It becomes the dead point. Therefore, although the injection mechanisms in the cylinders 13 and 14 have different injection states at the start time depending on the phase difference, the state transition cycles are the same.
  • the first blade 18 is positioned at the top dead center.
  • the lower blade groove 651 is in a state where it does not communicate with either the compression chamber 23b or the injection hole 54a.
  • the upper blade groove 652 is in a state where it does not communicate with either the compression chamber 23b or the injection hole 54b. That is, the first cylinder 13 is in the injection closed state.
  • the lower blade groove 651 continues to be in a state where it does not communicate with either the compression chamber 23b or the injection hole 54a.
  • the upper blade groove 652 continues to be in a state where it does not communicate with either the compression chamber 23b or the injection hole 54b. Therefore, the injection closed state in the first cylinder 13 continues.
  • the lower blade groove 651 communicates with the injection hole 54a and further begins to communicate with the compression chamber 23b. Become. That is, the first cylinder 13 is in the injection open state.
  • the upper blade groove 652 continues to be in a state where it does not communicate with either the compression chamber 23b or the injection hole 54b.
  • the lower blade groove 651 continues to be in communication with both the compression chamber 23b and the injection hole 54a until the rotation angle of the eccentric portion 28a and the roller 16 is from 180° to a predetermined rotation angle. . That is, the first cylinder 13 continues to be in the injection open state.
  • the rotation angle of the eccentric portion 28a and the roller 16 reaches, for example, 200 degrees
  • the upper blade groove 652 communicates with the injection hole 54b but does not communicate with the compression chamber 23b. At the rotation angle shown in FIG. 15E, the upper blade groove 652 continues in this state.
  • the lower blade groove 651 communicates with the injection hole 54a but does not communicate with the compression chamber 23b. That is, the first cylinder 13 transitions to the injection closed state.
  • the lower blade groove 651 communicates with the injection hole 54a, but continues not to communicate with the compression chamber 23b.
  • the upper blade groove 652 is in a state where it does not communicate with either the compression chamber 23b or the injection hole 54b. That is, the first cylinder 13 continues to be in the injection closed state.
  • the rotation angle of the eccentric portion 28a and the roller 16 becomes 360°, and when these rotate once, the lower blade groove 651 is in a state where it does not communicate with either the compression chamber 23b or the injection hole 54a. Further, the upper blade groove 652 continues to be in a state where it does not communicate with either the compression chamber 23b or the injection hole 54b.
  • FIG. 16 is a diagram showing the relationship among the injection state, rotation angle, and groove cross-sectional area ratio.
  • the injection state is either an open injection state or a closed injection state in the compression chamber of the cylinder.
  • the rotation angle is the rotation angle of the eccentric portion and the roller from the top dead center.
  • the compression load ratio is a value expressed as 0 when the refrigerant is not compressed in the compression chamber of the cylinder.
  • the groove cross-sectional area ratio is the sum of the upper groove cross-sectional area ratio and the lower groove cross-sectional area ratio.
  • the upper groove cross-sectional area ratio is the ratio of the groove cross-sectional areas of the upper blade grooves 652 and 662 according to this embodiment when the groove cross-sectional area of the blade grooves 61 and 62 according to the first embodiment is 1.
  • the lower groove cross-sectional area ratio is the ratio of the groove cross-sectional areas of the lower blade grooves 651 and 661 according to this embodiment when the groove cross-sectional area of the blade grooves 61 and 62 according to the first embodiment is 1.
  • the compression load ratio is 0 when the rotation angle is 0°, gradually increases from there, reaches a peak at about 200°, gradually decreases, and becomes 0 again at 360°.
  • the compression load ratio is a value expressed as 0 when the refrigerant is not compressed in the compression chamber of the cylinder.
  • the injection is closed until the rotation angle changes from 0° to 135°, so the upper groove cross-sectional area ratio, lower groove cross-sectional area ratio, and groove cross-sectional area ratio are all 0. There is.
  • the injection is in an open state until the rotation angle reaches 135° and reaches 160°.
  • the compression chamber 23b, the lower blade groove 651, and the injection hole 54a are in communication with each other.
  • the groove cross-sectional area of the lower blade groove 651 is smaller than the groove cross-sectional area (W ⁇ D) of the blade grooves 61 and 62. Therefore, the lower groove cross-sectional area ratio is a value smaller than 1, here 0.9.
  • the compression chamber 23b, the upper blade groove 652, and the injection hole 54b do not communicate with each other. Therefore, the upper groove cross-sectional area ratio is zero. Therefore, the groove cross-sectional area ratio is 0.9. In this way, the first cylinder 13 is in the injection open state only through the lower blade groove 651.
  • the injection open state continues until the rotation angle reaches 160° and reaches 200°. At this time, for example, the compression chamber 23b, the lower blade groove 651, and the injection hole 54a continue to communicate with each other. Therefore, the lower groove cross-sectional area ratio is 0.9.
  • the compression chamber 23b, the upper blade groove 652, and the injection hole 54b are in communication with each other.
  • the groove cross-sectional area of the upper blade groove 652 is smaller than the groove cross-sectional area (W ⁇ D) of the blade grooves 61 and 62. Therefore, the upper groove cross-sectional area ratio has a value smaller than 1, here 0.9. Therefore, the groove cross-sectional area ratio is 1.8. In this way, the first cylinder 13 is in the injection open state via both the upper blade groove 652 and the lower blade groove 651.
  • the injection open state continues until the rotation angle reaches 200° and reaches 225°.
  • the compression chamber 23b, the lower blade groove 651, and the injection hole 54a continue to communicate with each other. Therefore, the lower groove cross-sectional area ratio is 0.9.
  • the compression chamber 23b, the upper blade groove 652, and the injection hole 54b do not communicate with each other. Therefore, the upper groove cross-sectional area ratio is zero. Therefore, the groove cross-sectional area ratio is 0.9. In this way, the first cylinder 13 is in the injection open state only through the lower blade groove 651.
  • the rotation angle becomes 225°, and until it reaches 360°, the injection is in the closed state again. Therefore, the upper groove cross-sectional area ratio, the lower groove cross-sectional area ratio, and the groove cross-sectional area ratio all become 0 again.
  • the pressure in the compression chambers 23b, 24b increases before the pressure rises to the refrigerant discharge pressure.
  • the amount of injection refrigerant injected into the compression chambers 23b, 24b can be suppressed at the start and end of compression of the refrigerant, and the amount of injection refrigerant can be increased even more when compression has progressed.
  • the amount of injection refrigerant can be increased during the progress of compression, which requires cooling, than at the start of compression or the end of compression.
  • the groove cross-sectional area contributing to injection can be expanded in a short section corresponding to the groove length.
  • the switching time between the open state and the closed state of the injection can be shortened, the pressure in the compression chambers 23b and 24b is higher than the pressure in the injection flow path 7a, and the time in which the injection is in the open state can be shortened.
  • the cross-sectional area of the groove contributing to injection can be made smaller than in other states.
  • backflow of the injection refrigerant to the injection flow path 7a can be suppressed. Therefore, it is possible to suppress a decrease in the cooling effect of the compressor 2b and improve reliability.
  • the opening/closing timing of the injection flow path in each cylinder is such that a plurality of cylinders are not opened at the same time, and only a single cylinder is opened. That is, when the injection passage in the first cylinder is in an open state, the injection passages in the second and third cylinders are in a closed state. Similarly, when the injection passage in the second cylinder is open, the injection passages in the first and third cylinders are closed, and when the injection passage in the third cylinder is open, the injection passages in the first and third cylinders are closed. In the second cylinder, the injection flow path is in a closed state.
  • the shapes of the blade grooves in the embodiments described above may be varied as long as the effects of the invention are achieved. For example, the cross-sectional area may be gradually tapered, round, or a combination of these shapes.
  • SYMBOLS 1 Air conditioner, 2... Compressor, 7a... Injection channel, 7b... Connection pipe, 10... Sealed container, 10a... Peripheral wall, 10b... Discharge pipe, 10c... Oil reservoir, 10d, 10e...
  • Suction chamber first 2 suction chamber
  • 24b...compression chamber second compression chamber
  • 24c...suction port 27a...first journal part, 27b...second journal part, 27c...extension part
  • 28a...first eccentricity 28b...Second eccentric part, 29a...Outer circumferential surface of first eccentric part, 29b...Outer circumferential surface of second eccentric part, 33...Rotor, 34...Stator, 40...Flow path of partition plate ( injection communication passage), 40a...partition plate inlet side passage (horizontal passage), 40b, 40c...partition plate outlet side passage (vertical passage), 41, 42a, 42b...opening, 50...cylinder passage, 51 ...First cylinder flow path, 51a...Inlet side flow path (vertical flow path), 51b, 511b, 512b...Outlet side flow path (horizontal flow path), 52...Second cylinder flow path, 52a...Inlet side flow path (vertical flow path), 52b, 521b, 522b...outlet side flow path (

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PCT/JP2022/024655 2022-06-21 2022-06-21 圧縮機、および冷凍サイクル装置 WO2023248325A1 (ja)

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CN202280093809.6A CN118891447A (zh) 2022-06-21 2022-06-21 压缩机及冷冻循环装置
PCT/JP2022/024655 WO2023248325A1 (ja) 2022-06-21 2022-06-21 圧縮機、および冷凍サイクル装置
JP2024528132A JPWO2023248325A1 (enrdf_load_stackoverflow) 2022-06-21 2022-06-21
US18/990,756 US20250122876A1 (en) 2022-06-21 2024-12-20 Compressor and refrigeration cycle device

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Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5232712U (enrdf_load_stackoverflow) * 1975-08-30 1977-03-08
JPS5263210U (enrdf_load_stackoverflow) * 1975-11-05 1977-05-10
JPS543365Y1 (enrdf_load_stackoverflow) * 1970-11-18 1979-02-16
JPS578394U (enrdf_load_stackoverflow) * 1980-06-16 1982-01-16
JPS6397895A (ja) * 1986-10-09 1988-04-28 Daikin Ind Ltd ヘリウム圧縮機
JP2013024159A (ja) * 2011-07-22 2013-02-04 Panasonic Corp ロータリー圧縮機
CN104806522A (zh) * 2015-05-13 2015-07-29 广东美芝制冷设备有限公司 旋转式压缩机及具有其的冷冻装置
CN205876715U (zh) * 2016-07-25 2017-01-11 清华大学 一种带中间补气结构的单缸滚动转子压缩机
JP2018105136A (ja) * 2016-12-22 2018-07-05 東芝キヤリア株式会社 回転式圧縮機および冷凍サイクル装置

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS543365Y1 (enrdf_load_stackoverflow) * 1970-11-18 1979-02-16
JPS5232712U (enrdf_load_stackoverflow) * 1975-08-30 1977-03-08
JPS5263210U (enrdf_load_stackoverflow) * 1975-11-05 1977-05-10
JPS578394U (enrdf_load_stackoverflow) * 1980-06-16 1982-01-16
JPS6397895A (ja) * 1986-10-09 1988-04-28 Daikin Ind Ltd ヘリウム圧縮機
JP2013024159A (ja) * 2011-07-22 2013-02-04 Panasonic Corp ロータリー圧縮機
CN104806522A (zh) * 2015-05-13 2015-07-29 广东美芝制冷设备有限公司 旋转式压缩机及具有其的冷冻装置
CN205876715U (zh) * 2016-07-25 2017-01-11 清华大学 一种带中间补气结构的单缸滚动转子压缩机
JP2018105136A (ja) * 2016-12-22 2018-07-05 東芝キヤリア株式会社 回転式圧縮機および冷凍サイクル装置

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