WO2025099790A1 - 圧縮機 - Google Patents

圧縮機 Download PDF

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Publication number
WO2025099790A1
WO2025099790A1 PCT/JP2023/039811 JP2023039811W WO2025099790A1 WO 2025099790 A1 WO2025099790 A1 WO 2025099790A1 JP 2023039811 W JP2023039811 W JP 2023039811W WO 2025099790 A1 WO2025099790 A1 WO 2025099790A1
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WO
WIPO (PCT)
Prior art keywords
groove
labyrinth
spiral
refrigerant
tip seal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
PCT/JP2023/039811
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English (en)
French (fr)
Japanese (ja)
Inventor
大輔 堀口
浩平 達脇
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2023/039811 priority Critical patent/WO2025099790A1/ja
Priority to JP2025556039A priority patent/JPWO2025099790A1/ja
Publication of WO2025099790A1 publication Critical patent/WO2025099790A1/ja
Anticipated expiration legal-status Critical
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents

Definitions

  • This disclosure relates to a compressor having a fixed scroll and an orbiting scroll.
  • Scroll compressors have been known as compressors that compress refrigerants for refrigeration or air conditioning applications.
  • Scroll compressors have a compression unit that combines a fixed scroll and an oscillating scroll, and an electric motor unit that orbits the oscillating scroll.
  • Each of the fixed scroll and the oscillating scroll is provided with spiral teeth.
  • a compression chamber is formed by meshing the spiral teeth of the fixed scroll with the spiral teeth of the oscillating scroll. When the oscillating scroll orbits relative to the fixed scroll, the refrigerant is compressed in the compression chamber.
  • the high-pressure compression chamber and the low-pressure compression chamber are adjacent in the thickness direction of the spiral teeth. If refrigerant leaks from the high-pressure side to the low-pressure side, the compression efficiency decreases, and the performance of the compressor decreases. Conventionally, in order to prevent refrigerant leaking from the high-pressure side to the low-pressure side, it is known to form a tip seal groove on the tip surface of the spiral teeth and fit a tip seal into the tip seal groove (see, for example, Patent Document 1).
  • each of the spiral teeth of the fixed scroll and the orbiting scroll that do not have a tip seal.
  • a tip seal cannot be provided at the end of the spiral teeth of the fixed scroll because there is a part that does not overlap with the base plate of the orbiting scroll.
  • a tip seal cannot be provided at the beginning of the spiral teeth of the fixed scroll because there is a part that overlaps with the seat cavity of the orbiting scroll.
  • a tip seal cannot be provided at the beginning of the spiral teeth of the orbiting scroll because there is a part that overlaps with the discharge port of the fixed scroll.
  • chip seals are sometimes provided in pieces to avoid overlapping with the injection port. For these reasons, even if chip seals are provided on the spiral teeth, there is an issue of refrigerant leakage in the thickness direction of the spiral teeth.
  • This disclosure has been made to solve the problems described above, and aims to provide a compressor that can reduce refrigerant leakage in the thickness direction of the spiral teeth.
  • the compressor according to the present disclosure includes a fixed scroll and an orbiting scroll that orbits relative to the fixed scroll, the fixed scroll having a first base plate and a first spiral tooth formed on the first base plate, the orbiting scroll having a second base plate and a second spiral tooth formed on the second base plate and meshing with the first spiral tooth, a chip seal groove into which a chip seal is fitted is formed on each of the tip surfaces of the first and second spiral teeth, and a labyrinth groove is formed in a portion of the tip surface of at least one of the first and second spiral teeth that does not have the chip seal groove, which increases the flow resistance of the tip surface in the thickness direction of the at least one of the first and second spiral teeth.
  • FIG. 1 is a circuit diagram showing a configuration of a refrigeration cycle device including a compressor according to a first embodiment.
  • 1 is a cross-sectional view showing a configuration of a compressor according to a first embodiment.
  • FIG. 2 is a plan view showing the configuration of a fixed scroll of the compressor according to the first embodiment.
  • FIG. 2 is a plan view showing the configuration of an orbiting scroll of the compressor according to the first embodiment.
  • 4 is an enlarged cross-sectional view showing the configuration of a labyrinth groove of the compressor according to the first embodiment.
  • FIG. FIG. 4 is a plan view showing a configuration of a fixed scroll of a compressor according to a modified example of the first embodiment.
  • FIG. 4 is a plan view showing a configuration of an orbiting scroll of a compressor according to a modified example of the first embodiment.
  • FIG. 11 is a plan view showing the configuration of an orbiting scroll of a compressor according to a second embodiment.
  • FIG. 11 is a plan view showing the configuration of an orbiting scroll of a compressor according to embodiment 3.
  • the compressor according to the present disclosure will be described with reference to the drawings.
  • the present disclosure is not limited to the following embodiments, and various modifications can be made without departing from the spirit of the present disclosure.
  • the present disclosure also includes all combinations of the configurations shown in the following embodiments that can be combined.
  • the combination of components is not limited to the combinations in each embodiment, and components described in one embodiment can be applied to another embodiment.
  • terms indicating directions e.g., “up,” “down,” “right,” “left,” “front,” “rear,” etc.
  • the same reference numerals are assigned to the same or equivalent parts, and this is common throughout the entire specification.
  • the relative dimensional relationship or shape of each component may differ from the actual one.
  • FIG. 1 is a circuit diagram showing the configuration of a refrigeration cycle device including a compressor according to the embodiment.
  • the refrigeration cycle device is used, for example, in an air conditioner that conditions indoor air.
  • the refrigeration cycle device 1 includes an outdoor unit 1a, an indoor unit 1b, and a control device 80.
  • the outdoor unit 1a includes a compressor 100, an outdoor heat exchanger 200, an outdoor blower 201, an expansion section 300, and an intermediate injection circuit 800.
  • the indoor unit 1b includes an indoor heat exchanger 400 and an indoor blower 401.
  • the compressor 100, the outdoor heat exchanger 200, the expansion section 300, and the indoor heat exchanger 400 are connected by a refrigerant pipe 501.
  • the compressor 100, the outdoor heat exchanger 200, the expansion section 300, the indoor heat exchanger 400, and the refrigerant pipe 501 form a refrigerant circuit 500.
  • a refrigerant circulates through the refrigerant circuit 500.
  • a fluorocarbon refrigerant such as R32, or a natural refrigerant such as carbon dioxide (CO 2 ) is used as the refrigerant.
  • the compressor 100 is a fluid machine that compresses a refrigerant.
  • the compressor 100 draws in low-temperature, low-pressure gas refrigerant, compresses the drawn-in gas refrigerant to a high-temperature, high-pressure state, and discharges the compressed gas refrigerant.
  • the compressor 100 in this embodiment is a scroll compressor.
  • the outdoor heat exchanger 200 is a heat exchanger that exchanges heat between the gas refrigerant flowing inside the outdoor heat exchanger 200 and an external fluid passing through the outdoor heat exchanger 200.
  • the outdoor heat exchanger 200 is an air-refrigerant heat exchanger that uses outdoor air as the external fluid.
  • the high-temperature, high-pressure gas refrigerant flowing inside the outdoor heat exchanger 200 is cooled and condensed by heat exchange with the low-temperature outdoor air. In this way, the outdoor heat exchanger 200 acts as a condenser.
  • the outdoor blower 201 is a device that sends outdoor air to the outdoor heat exchanger 200.
  • the expansion section 300 is configured to reduce the pressure of the high-pressure liquid refrigerant and expand it.
  • an expansion machine, a thermostatic automatic expansion valve, or a linear electronic expansion valve with an adjustable opening degree is used for the expansion section 300.
  • the high-pressure liquid refrigerant expanded by the expansion section 300 becomes a low-pressure refrigerant in a liquid state or a two-phase gas-liquid state.
  • the indoor heat exchanger 400 is a heat exchanger that exchanges heat between the refrigerant in a liquid state or in a two-phase gas-liquid state flowing inside the indoor heat exchanger 400 and an external fluid that passes through the indoor heat exchanger 400.
  • the indoor heat exchanger 400 is an air-refrigerant heat exchanger that uses indoor air as the external fluid.
  • the low-temperature, low-pressure liquid refrigerant or two-phase gas-liquid refrigerant flowing inside the indoor heat exchanger 400 is heated and evaporated by heat exchange with the high-temperature outdoor air. In this way, the indoor heat exchanger 400 acts as an evaporator.
  • the indoor blower 401 is a device that sends indoor air to the indoor heat exchanger 400.
  • the intermediate injection circuit 800 connects the refrigerant piping 501 between the outdoor heat exchanger 200 and the expansion section 300 to the injection piping 49 provided in the compressor 100.
  • the refrigerant flowing out from the outdoor heat exchanger 200 flows in the intermediate injection circuit 800.
  • the intermediate injection circuit 800 is provided with the injection expansion section 600 and the cooler 700.
  • the intermediate injection circuit 800 is provided to allow low-temperature, low-pressure liquid refrigerant or gas-liquid two-phase refrigerant to flow into the inside of the compression unit 10 of the compressor 100.
  • the injection expansion section 600 is configured to reduce the pressure of the high-pressure liquid refrigerant flowing through the intermediate injection circuit 800 and expand it.
  • an expansion machine for example, an expansion machine, a thermostatic automatic expansion valve, or a linear electronic expansion valve with an adjustable opening degree is used for the injection expansion section 600.
  • the cooler 700 is a heat exchanger that exchanges heat between a low-temperature, low-pressure liquid refrigerant or two-phase gas-liquid refrigerant flowing inside the cooler 700 and an external fluid passing through the cooler 700.
  • the cooler 700 of this embodiment is an air-refrigerant heat exchanger that uses high-temperature indoor air as the external fluid.
  • the cooler 700 may be a double-pipe subcooling heat exchanger. In this case, the cooler 700 exchanges heat between the low-temperature, low-pressure two-phase gas-liquid refrigerant flowing out of the injection expansion section 600 and the high-pressure liquid refrigerant or two-phase gas-liquid refrigerant flowing out of the outdoor heat exchanger 200.
  • the cooler 700 may be omitted from the intermediate injection circuit 800.
  • the control device 80 has, for example, a microcomputer and a memory.
  • the control device 80 is configured to control each device of the refrigeration cycle device 1.
  • the control device 80 is configured to adjust the opening of the injection expansion section 600 and adjust the amount of refrigerant flowing into the intermediate injection circuit 800.
  • FIG. 2 is a cross-sectional view showing the configuration of a compressor according to this embodiment.
  • a hermetic scroll compressor is exemplified as the compressor.
  • the compressor 100 has a container 40, a frame 46, a subframe 47, a main shaft 33, a main bearing 46a, a sub-bearing 48, a suction pipe 44, a discharge pipe 45, and a compression unit 10.
  • the compressor 100 also has a boss portion 27, an Oldham ring 22a, a sleeve 34, a discharge valve 5, a valve guard 6, an oil pump 51, an oil drain pipe 50, and an electric motor unit 30.
  • the container 40 is a sealed container that forms the outer shell of the compressor 100.
  • the container 40 has an overall cylindrical shape.
  • the compression unit 10, the electric motor unit 30, the frame 46, the subframe 47, and other parts are housed inside the container 40.
  • the compression unit 10 is disposed at the top inside the container 40.
  • the electric motor unit 30 is disposed below the compression unit 10 inside the container 40.
  • the container 40 has a bottom 43, a body 42, and a lid 41.
  • the bottom 43 is a dish-shaped member in which an oil reservoir 2 is formed to store refrigeration oil.
  • the body 42 is a cylindrical member extending upward from the bottom 43.
  • a suction pipe 44 is connected to the body 42. Low-pressure refrigerant flowing out of the indoor heat exchanger 400 is sucked into the container 40 through the suction pipe 44.
  • the lid 41 is a dome-shaped member provided on the upper part of the body 42.
  • a discharge pipe 45 is connected to the lid 41. High-pressure refrigerant compressed in the compression unit 10 is discharged to the outside of the compressor 100 through the discharge pipe 45.
  • the frame 46 is fixed inside the container 40.
  • the compression unit 10 is housed in the frame 46.
  • the frame 46 is disposed above the motor unit 30.
  • the frame 46 is located inside the container 40, between the motor unit 30 and the compression unit 10.
  • the frame 46 rotatably supports the main shaft 33 via the main bearing 46a.
  • the main bearing 46a is provided in the center of the frame 46.
  • the frame 46 is formed with a plurality of suction ports 36.
  • Each suction port 36 is a through hole that connects the space between the frame 46 and the motor unit 30 to a space in the compression unit 10 that is outside the outer periphery of the first and second spiral teeth 24 and 26.
  • the refrigerant that flows into the container 40 is supplied to the compression unit 10 through the plurality of suction ports 36.
  • the subframe 47 is fixed inside the container 40.
  • the subframe 47 is disposed below the motor unit 30 inside the container 40.
  • the subframe 47 rotatably supports the main shaft 33 via a secondary bearing 48.
  • the secondary bearing 48 is provided in the center of the subframe 47.
  • the secondary bearing 48 is, for example, a ball bearing.
  • the secondary bearing 48 is fixed to the subframe 47 by press fitting.
  • a hole 47a is formed in the subframe 47. Refrigeration oil flows down toward the oil reservoir 2 through the hole 47a.
  • the frame 46 and the subframe 47 are arranged in the container 40 so as to face each other with the motor unit 30 in between.
  • Each of the frame 46 and the subframe 47 is fixed to the inner surface of the body 42 by shrink fitting, welding, etc.
  • the main shaft 33 is a rod-shaped crankshaft.
  • the main shaft 33 extends vertically along the central axis of the container 40.
  • the main shaft 33 connects the electric motor unit 30 and the compression unit 10. The rotational force of the electric motor unit 30 is transmitted to the compression unit 10 via the main shaft 33.
  • the main shaft 33 has an eccentric shaft portion 33a, a main shaft portion 33b, and a counter shaft portion 33c.
  • the eccentric shaft portion 33a is formed at the upper end of the main shaft 33, i.e., above the main shaft portion 33b.
  • the eccentric shaft portion 33a is rotatably accommodated in a rocking bearing 27a provided in the boss portion 27.
  • the outer periphery of the eccentric shaft portion 33a is in close contact with the inner periphery of the rocking bearing 27a via a layer of refrigeration oil.
  • the axis of the eccentric shaft portion 33a is eccentric with respect to the axis of the main shaft portion 33b.
  • the main shaft portion 33b is supported by a main bearing 46a.
  • a sleeve 34 is provided between the main bearing 46a and the main shaft portion 33b.
  • the counter shaft portion 33c is formed below the main shaft portion 33b.
  • the counter shaft portion 33c is supported by a counter bearing 48.
  • An oil passage 33d through which oil passes is formed inside the main shaft 33.
  • a low pressure space 8 below the compression unit 10 and a high pressure space 9 above the compression unit 10 are formed inside the container 40.
  • the suction pipe 44 is connected to the low pressure space 8 at the side of the container 40.
  • Low pressure gas refrigerant in the refrigerant circuit 500 is sucked into the low pressure space 8 through the suction pipe 44.
  • the discharge pipe 45 is connected to the high pressure space 9 at the top of the container 40. The high pressure refrigerant compressed by the compression unit 10 is discharged from the high pressure space 9 to the outside of the compressor 100 through the discharge pipe 45.
  • the injection pipe 49 is connected to the compression chamber 11 of the compression unit 10 at the top of the container 40.
  • the injection pipe 49 introduces the refrigerant in a liquid state or in a two-phase gas-liquid state flowing through the intermediate injection circuit 800 into the compression chamber 11.
  • the compression chamber 11 has a suction chamber 12 connected to the suction port 36 and a discharge chamber 13 connected to the discharge port 3.
  • the compression unit 10 compresses the refrigerant sucked through the suction pipe 44 and discharges it into the high-pressure space 9.
  • the compression unit 10 has a fixed scroll 21 and an orbiting scroll 22.
  • the fixed scroll 21 is fixed to the container 40 via a frame 46 above the orbiting scroll 22.
  • the fixed scroll 21 has a first base plate 23 and a first spiral tooth 24.
  • the first base plate 23 is a plate-shaped member and forms the upper surface of the compression unit 10.
  • the first spiral tooth 24 is a spiral-shaped protrusion formed on the lower surface of the first base plate 23. The first spiral tooth 24 protrudes downward from the lower surface of the first base plate 23.
  • the oscillating scroll 22 is disposed below the fixed scroll 21 so as to face the fixed scroll 21.
  • the oscillating scroll 22 is configured to oscillate relative to the fixed scroll 21.
  • the oscillating scroll 22 has a second base plate 25 and a second spiral tooth 26.
  • the second base plate 25 is a plate-shaped member disposed above the frame 46.
  • the second spiral tooth 26 is a spiral-shaped protrusion formed on the upper surface of the second base plate 25.
  • the second spiral tooth 26 protrudes upward from the upper surface of the second base plate 25.
  • the second spiral tooth 26 is engaged with the first spiral tooth 24.
  • the fixed scroll 21 and the oscillating scroll 22 are provided in the container 40 with the first spiral teeth 24 and the second spiral teeth 26 meshing with each other.
  • Each of the first spiral teeth 24 and the second spiral teeth 26 is formed following an involute curve.
  • a discharge port 3 is formed in the center of the fixed scroll 21.
  • the discharge port 3 is a passage through which the compressed and high-pressure refrigerant is discharged.
  • a discharge muffler 7 is provided on the outlet side of the discharge port 3.
  • An injection port 28 is formed in the first base plate 23 of the fixed scroll 21.
  • An injection pipe 49 is connected to the injection port 28. The refrigerant in a liquid state or in a two-phase gas-liquid state that flows in from the injection pipe 49 flows out through the injection port 28 into the compression chamber 11 where the refrigerant is in the middle of the compression process.
  • the boss portion 27 is provided at the center of the surface of the second base plate 25 opposite the surface on which the second spiral teeth 26 are formed.
  • the boss portion 27 is formed in a hollow cylindrical shape.
  • An oscillating bearing 27a is provided between the oscillating scroll 22 and the boss portion 27.
  • the oscillating bearing 27a rotatably supports the eccentric shaft portion 33a of the main shaft 33.
  • the eccentric shaft portion 33a rotates the oscillating scroll 22 eccentrically.
  • the Oldham ring 22a is provided on the thrust surface of the orbiting scroll 22, which is opposite to the surface on which the second spiral teeth 26 are formed.
  • the Oldham ring 22a prevents the orbiting scroll 22 from rotating on its axis during its eccentric orbital motion, and enables the orbiting scroll 22 to revolve.
  • the upper and lower surfaces of the Oldham ring 22a are provided with claws (not shown) that protrude perpendicular to each other.
  • the claw on the upper surface of the Oldham ring 22a is slidably inserted into an Oldham groove (not shown) formed in the orbiting scroll 22.
  • the claw on the lower surface of the Oldham ring 22a is slidably inserted into an Oldham groove (not shown) formed in the frame 46.
  • the sleeve 34 is a cylindrical member provided between the frame 46 and the main bearing 46a.
  • the sleeve 34 absorbs the tilt between the frame 46 and the main shaft 33.
  • the discharge valve 5 is a leaf spring member that covers the discharge port 3 and prevents the refrigerant from flowing back.
  • the valve retainer 6 regulates the range of movement of the discharge valve 5.
  • the refrigerant compressed in the compression chamber 11 pushes up the discharge valve 5 and flows out into the high-pressure space 9 through the space in the discharge muffler 7.
  • the refrigerant in the high-pressure space 9 is discharged to the outside of the compressor 100 through the discharge pipe 45.
  • the oil pump 51 draws up oil from the oil reservoir 2.
  • the oil pump 51 is housed in the bottom 43 of the container 40.
  • the oil pump 51 is fixed to the lower part of the main shaft 33.
  • the oil pump 51 draws up oil from the oil reservoir 2 and supplies the oil to the auxiliary bearing 48, the main bearing 46a, and the oscillating bearing 27a via the oil passage 33d.
  • the oil drain pipe 50 is a pipe that connects the space between the frame 46 and the orbiting scroll 22 and the space between the frame 46 and the subframe 47.
  • the oil drain pipe 50 allows excess oil circulating in the space between the frame 46 and the orbiting scroll 22 to flow out into the space between the frame 46 and the subframe 47.
  • the oil that flows out into the space between the frame 46 and the subframe 47 passes through the subframe 47 and returns to the oil reservoir 2.
  • the motor unit 30 is provided in the low-pressure space 8 inside the container 40.
  • the motor unit 30 drives the oscillating scroll 22 via the main shaft 33.
  • the oscillating scroll 22 is driven by the motor unit 30, causing the refrigerant to be compressed in the compression unit 10.
  • the motor unit 30 has a stator 31 and a rotor 32.
  • the stator 31 is fixed to the inner peripheral surface of the container 40.
  • the rotor 32 is provided on the inner peripheral side of the stator 31.
  • the outer peripheral surface of the rotor 32 faces the inner peripheral surface of the stator 31 with a gap therebetween.
  • the rotor 32 is fixed to the outer periphery of the main shaft portion 33b.
  • the low-pressure refrigerant flowing out from the indoor heat exchanger 400 is sucked into the low-pressure space 8 of the container 40 through the suction pipe 44.
  • the refrigerant sucked into the low-pressure space 8 is taken into the suction chamber 12 on the outer periphery of the multiple compression chambers 11.
  • each compression chamber 11 gradually moves from the outer periphery to the center while reducing its volume.
  • the refrigerant taken into the suction chamber 12 moves to the discharge chamber 13 while being compressed.
  • the compressed refrigerant flows from the discharge chamber 13 through the discharge port 3 and the discharge muffler 7 into the high-pressure space 9, and is discharged from the discharge pipe 45 to the outside of the container 40.
  • the high-pressure refrigerant discharged from the discharge pipe 45 flows into the outdoor heat exchanger 200.
  • the refrigerant sucked from the suction pipe 44 flows into the frame 46 through the suction port 36 of the frame 46 and is sucked into the compression unit 10.
  • the refrigerant that does not flow into the frame 46 cools the motor unit 30 and the oil reservoir 2.
  • the refrigerant sucked into the compression unit 10 mixes with the refrigerant flowing in from the injection pipe 49, thereby lowering the temperature of the refrigerant sucked into the compression unit 10. Therefore, the thermal expansion of the fixed scroll 21 and the oscillating scroll 22 can be suppressed, and the behavior of the compression unit 10 can be stabilized.
  • the refrigerant sucked into the compressor 100 is compressed by the compressor 100 and discharged in a high-temperature, high-pressure gas state.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 100 flows into the outdoor heat exchanger 200 acting as a condenser, where it exchanges heat with the outdoor air sent by the outdoor blower 201, condenses and liquefies.
  • the condensed liquid refrigerant flows into the expansion section 300, where it expands and is decompressed to become a low-temperature, low-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant then flows into the indoor heat exchanger 400 acting as an evaporator, where it exchanges heat with the indoor air sent by the indoor blower 401, evaporates and gasifies. At this time, the indoor air is cooled, and cooling is performed in the room. The evaporated low-temperature, low-pressure gas refrigerant is sucked into the compressor 100.
  • the refrigerant discharged from the discharge pipe 45 becomes hot.
  • an operation in which the difference between the intake temperature and the discharge temperature is large refers to a high compression ratio operation in which the pressure difference between high pressure and low pressure is large.
  • the discharge temperature is lowered by injecting the liquid state or gas-liquid two-phase state refrigerant flowing on the outlet side of the outdoor heat exchanger 200 into the compression chamber 11 of the compressor 100.
  • the high-pressure refrigerant flowing out of the outdoor heat exchanger 200 is reduced to an intermediate pressure by controlling the throttling expansion rate and flow rate by the injection expansion section 600.
  • the liquid state refrigerant reduced to an intermediate pressure flows into the inside of the compressor 100 from the injection pipe 49.
  • the liquid state refrigerant that flows into the inside of the compressor 100 is injected into the compression chamber 11 from the injection port 28.
  • the liquid state refrigerant cools the gas state refrigerant in the middle of compression in the compression chamber 11.
  • FIG. 3 is a plan view showing the configuration of the fixed scroll of the compressor according to this embodiment.
  • FIG. 3 shows the configuration of the fixed scroll 21 viewed from the first spiral teeth 24 side.
  • the first spiral teeth 24 of the fixed scroll 21 are formed on the surface of the first base plate 23.
  • the first spiral teeth 24 extend along an involute curve.
  • the first spiral teeth 24 have a start portion 24a and an end portion 24b.
  • the start portion 24a is the end portion located on the center side of the spiral among both ends in the extension direction of the first spiral teeth 24.
  • the start portion 24a is located in a position adjacent to the discharge port 3.
  • the end portion 24b is the end portion located on the outer periphery side of the spiral among both ends in the extension direction of the first spiral teeth 24.
  • the first spiral tooth 24 has a tip surface 24c.
  • the tip surface 24c faces the second base plate 25 of the oscillating scroll 22.
  • a tip seal groove 60 is formed in the tip surface 24c.
  • the tip seal groove 60 is formed following an involute curve, similar to the first spiral tooth 24.
  • the tip seal groove 60 is formed in a portion of the tip surface 24c excluding the winding start portion 24a and the winding start portion 24b in the extension direction of the first spiral tooth 24.
  • a chip seal 61 is fitted into the chip seal groove 60.
  • the chip seal 61 slides against the second base plate 25 as the orbiting scroll 22 orbits.
  • the chip seal 61 has the function of preventing refrigerant leakage in the thickness direction of the first scroll tooth 24.
  • a labyrinth groove 62a is formed at the start of winding 24a of the tip surface 24c of the first spiral tooth 24.
  • a labyrinth groove 62b is formed at the end of winding 24b of the tip surface 24c of the first spiral tooth 24.
  • the labyrinth groove 62a and labyrinth groove 62b are formed in a portion of the first spiral tooth 24 in the extension direction where there is no tip seal groove 60.
  • the labyrinth groove 62a and labyrinth groove 62b are not connected to the tip seal groove 60, and are formed with a space between them.
  • Both the labyrinth groove 62a and the labyrinth groove 62b form a labyrinth structure that increases the flow resistance of the tip surface 24c in the thickness direction of the first spiral tooth 24.
  • Each of the labyrinth groove 62a and the labyrinth groove 62b is composed of multiple grooves parallel to each other. Each of the multiple grooves is formed following an involute curve, similar to the tip seal groove 60, and extends perpendicular to the thickness direction of the first spiral tooth 24. In this embodiment, each of the multiple grooves has a groove width narrower than the groove width of the tip seal groove 60.
  • One or both of the labyrinth groove 62a and the labyrinth groove 62b may be composed of a single groove.
  • FIG. 4 is a plan view showing the configuration of the orbiting scroll of the compressor according to this embodiment.
  • FIG. 4 shows the configuration of the orbiting scroll 22 viewed from the second spiral tooth 26 side.
  • the second spiral tooth 26 of the orbiting scroll 22 is formed on the surface of the second base plate 25.
  • the second spiral tooth 26 extends following an involute curve.
  • the second spiral tooth 26 has a start portion 26a and an end portion 26b.
  • the start portion 26a is the end portion located on the center side of the spiral among both ends in the extension direction of the second spiral tooth 26.
  • the start portion 26a is located at a position where it can overlap with the discharge port 3 on the fixed scroll 21 side depending on the orbiting position of the orbiting scroll 22.
  • the end portion 26b is the end portion located on the outer periphery side of the spiral among both ends in the extension direction of the second spiral tooth 26.
  • the second spiral tooth 26 has a tip surface 26c.
  • the tip surface 26c faces the first base plate 23 of the fixed scroll 21.
  • a tip seal groove 70 is formed in the tip surface 26c.
  • the tip seal groove 70 is formed following an involute curve, similar to the second spiral tooth 26.
  • the tip seal groove 70 is formed in a portion of the tip surface 26c excluding the winding start portion 26a and the winding start portion 26b in the extension direction of the second spiral tooth 26.
  • a chip seal 71 is fitted into the chip seal groove 70.
  • the chip seal 71 slides against the first base plate 23 as the orbiting scroll 22 orbits.
  • the chip seal 71 has the function of preventing refrigerant leakage in the thickness direction of the second scroll teeth 26.
  • a labyrinth groove 72a is formed at the start of winding 26a of the tip surface 26c of the second spiral tooth 26.
  • a labyrinth groove 72b is formed at the end of winding 26b of the tip surface 26c of the second spiral tooth 26.
  • the labyrinth groove 72a and labyrinth groove 72b are formed in a portion of the second spiral tooth 26 in the extension direction where there is no tip seal groove 70.
  • the labyrinth groove 72a and labyrinth groove 72b are not connected to the tip seal groove 70, and are formed with a space between them.
  • Both the labyrinth groove 72a and the labyrinth groove 72b form a labyrinth structure that increases the flow resistance of the tip surface 26c in the thickness direction of the second spiral tooth 26.
  • Each of the labyrinth groove 72a and the labyrinth groove 72b is composed of multiple grooves parallel to each other. Each of the multiple grooves is formed following an involute curve, similar to the tip seal groove 70, and extends perpendicular to the thickness direction of the second spiral tooth 26. In this embodiment, each of the multiple grooves has a groove width narrower than the groove width of the tip seal groove 60.
  • One or both of the labyrinth groove 72a and the labyrinth groove 72b may be composed of a single groove.
  • FIG. 5 is an enlarged cross-sectional view showing the configuration of the labyrinth groove of the compressor according to this embodiment.
  • FIG. 5 shows a cross section perpendicular to the extension direction of the spiral teeth.
  • the left-right direction in FIG. 5 represents the thickness direction of the spiral teeth.
  • FIG. 5 shows the labyrinth groove 72b of the second spiral tooth 26 as an example, but the labyrinth groove 72a of the second spiral tooth 26 and the labyrinth groove 62a and labyrinth groove 62b of the first spiral tooth 24 also have the same configuration.
  • the labyrinth groove 72b has multiple grooves 72b1, 72b2 arranged in parallel in the thickness direction of the second spiral tooth 26.
  • the labyrinth groove 72b has a configuration in which convex portions 73 and concave portions 74 are arranged alternately in parallel in the thickness direction of the second spiral tooth 26.
  • the convex portions 73 function as throttling pieces that narrow the flow path for fluid flowing in the thickness direction of the second spiral tooth 26.
  • the concave portions 74 function as expansion chambers for fluid flowing in the same direction.
  • the expansion chambers are spaces formed between two adjacent throttling pieces.
  • the protrusions 73 face the first base plate 23 with a gap of distance ⁇ between them.
  • the width of the protrusions 73 in the thickness direction of the second spiral tooth 26 is ⁇ .
  • the spacing between the protrusions 73 in the same direction, i.e., the width of the recesses 74, is S.
  • the height of the protrusions 73, i.e., the depth of the recesses 74, is h.
  • the amount of fluid leakage is calculated by the following formula (1): G0: Leakage amount [kgf/s], F: cross-sectional area of the aperture [m 2 ], ⁇ : flow coefficient, ⁇ : blow-through coefficient, ⁇ 0: labyrinth function, P0: Fluid pressure at the labyrinth inlet [kg/m 2 ], ⁇ 0: specific fluid volume at the labyrinth inlet.
  • the optimal labyrinth structure is obtained when the above-mentioned convex portion 73 and concave portion 74 satisfy ⁇ / ⁇ 4.8, ⁇ / ⁇ >8.0, and 0.15 ⁇ h/S ⁇ 0.3.
  • the spacing S between the convex portions 73 is 1 mm
  • the depth h of the concave portion 74 is set to 0.15 mm or more and 0.3 mm or less.
  • the dimensions of the labyrinth structure are not limited to the above example.
  • the magnitude relationship between ⁇ , ⁇ , h, and S can also be changed as appropriate.
  • FIG. 6 is a plan view showing the configuration of a fixed scroll of a compressor according to a modified embodiment of the present invention.
  • the labyrinth groove 62a is connected to the end 60a of the tip seal groove 60 on the side of the beginning of the winding 24a.
  • the labyrinth groove 62b is connected to the end 60b of the tip seal groove 60 on the side of the end of the winding 24b.
  • This increases the length of the labyrinth groove 62a and the labyrinth groove 62b, and expands the formation range of the labyrinth groove 62a and the labyrinth groove 62b in the extension direction of the first spiral tooth 24. This further reduces the leakage of refrigerant from the high pressure side to the low pressure side, and prevents the performance of the compressor 100 from deteriorating due to refrigerant leakage.
  • FIG. 7 is a plan view showing the configuration of the oscillating scroll of the compressor according to a modified example of this embodiment.
  • the labyrinth groove 72a is connected to the end 70a of the tip seal groove 70 on the side of the beginning of the winding 26a.
  • the labyrinth groove 72b is connected to the end 70b of the tip seal groove 70 on the side of the end of the winding 26b.
  • This increases the length of the labyrinth groove 72a and the labyrinth groove 72b, and expands the formation range of the labyrinth groove 72a and the labyrinth groove 72b in the extension direction of the second spiral tooth 26. This further suppresses leakage of refrigerant from the high pressure side to the low pressure side, and prevents a decrease in performance of the compressor 100 due to refrigerant leakage.
  • the compressor 100 includes a fixed scroll 21 and an oscillating scroll 22.
  • the oscillating scroll 22 is configured to oscillate relative to the fixed scroll 21.
  • the fixed scroll 21 has a first base plate 23 and a first spiral tooth 24.
  • the first spiral tooth 24 is formed on the first base plate 23.
  • the oscillating scroll 22 has a second base plate 25 and a second spiral tooth 26.
  • the second spiral tooth 26 is formed on the second base plate 25.
  • the second spiral tooth 26 is meshed with the first spiral tooth 24.
  • a tip seal groove 60 is formed in the tip surface 24c of the first spiral tooth 24.
  • a tip seal 61 is fitted into the tip seal groove 60.
  • a tip seal 70 is formed in the tip surface 26c of the second spiral tooth 26.
  • a tip seal 71 is fitted into the tip seal groove 70.
  • Labyrinth grooves 62a, 62b that increase the flow resistance of the tip surface 24c in the thickness direction of the first spiral tooth 24 are formed in the portion of the tip surface 24c of the first spiral tooth 24 that does not have the tip seal groove 60.
  • Labyrinth grooves 72a, 72b that increase the flow resistance of the tip surface 26c in the thickness direction of the second spiral tooth 26 are formed in the portion of the tip surface 26c of the second spiral tooth 26 that does not have the tip seal groove 70.
  • the labyrinth grooves 62a, 62b are formed, so that the flow resistance of the tip surface 24c in the thickness direction of the first spiral tooth 24 can be increased even in the portion where the tip seal 61 is not formed. This makes it possible to suppress refrigerant leakage in the thickness direction of the first spiral tooth 24.
  • the labyrinth grooves 72a, 72b are formed, so that the flow resistance of the tip surface 26c in the thickness direction of the second spiral tooth 26 can be increased even in the portion where the tip seal 71 is not formed. This makes it possible to suppress refrigerant leakage in the thickness direction of the second spiral tooth 26. Therefore, with this configuration, it is possible to prevent a decrease in the performance of the compressor 100 due to refrigerant leakage.
  • the labyrinth grooves 62a, 62b are formed in the start portion 24a and end portion 24b of the first spiral tooth 24.
  • the labyrinth grooves 72a, 72b are formed in the start portion 26a and end portion 26b of the second spiral tooth 26.
  • the labyrinth groove in a cross section perpendicular to the extension direction of at least one of the first and second spiral teeth 24 and 26, the labyrinth groove has a configuration in which the convex portion 73 and the concave portion 74 are arranged in parallel in the thickness direction of each spiral tooth.
  • the convex portion 73 faces the first base plate 23 or the second base plate 25 across a gap of distance ⁇ .
  • the width of the convex portion 73 in the thickness direction of each spiral tooth is ⁇
  • the width of the concave portion 74 in the thickness direction of each spiral tooth is S
  • the depth of the concave portion 74 is h
  • the relationships ⁇ / ⁇ 4.8, ⁇ / ⁇ >8.0, and 0.15 ⁇ h/S ⁇ 0.3 are satisfied.
  • the labyrinth groove has multiple grooves arranged in parallel in the thickness direction of each spiral tooth.
  • Each of the multiple grooves has a groove width narrower than the groove width of the tip seal groove.
  • FIG. 8 is a plan view showing the configuration of the orbiting scroll of the compressor according to the present embodiment. This embodiment differs from the first embodiment in the position where the labyrinth groove is formed. The other configuration is the same as that of the first embodiment. Below, the labyrinth groove of the orbiting scroll 22 will be described, but a similar labyrinth groove is also formed in the fixed scroll 21.
  • each of the labyrinth grooves 72c, 72d is formed along the tip seal groove 70 on the tip surface 26c of the second spiral tooth 26.
  • the labyrinth groove 72c is formed between the tip seal groove 70 and the outward surface 26d of the second spiral tooth 26, i.e., on one side of the tip seal groove 70.
  • the labyrinth groove 72d is formed between the tip seal groove 70 and the inward surface 26e of the second spiral tooth 26, i.e., on the other side of the tip seal groove 70.
  • each of the labyrinth grooves 72c, 72d is formed in a portion of the second spiral tooth 26 where there is no tip seal groove 70 in the thickness direction.
  • the tip seal groove 70 is sandwiched on both sides by the labyrinth groove 72c and the labyrinth groove 72d in the thickness direction of the second spiral tooth 26.
  • each of the labyrinth grooves 72c and 72d extends seamlessly along the entire section from end 70a to end 70b of the tip seal groove 70.
  • labyrinth groove 72c and labyrinth groove 72d each consist of a single groove, but may consist of multiple grooves.
  • the labyrinth grooves 72c, 72d are each formed along the tip seal groove 70.
  • the labyrinth grooves 72a, 72b are formed, so that the flow path resistance of the tip surface 24c in the thickness direction of the first spiral tooth 24 can be increased. Therefore, in addition to sealing by the tip seal 71, sealing by the labyrinth structure can also be performed. Therefore, compared to sealing by only the tip seal 71, refrigerant leakage in the thickness direction of the first spiral tooth 24 can be further suppressed.
  • FIG. 9 is a plan view showing the configuration of the orbiting scroll of the compressor according to this embodiment. This embodiment differs from the first and second embodiments in the position where the labyrinth groove is formed. The other configurations are the same as those of the first and second embodiments. Note that the winding direction of the second spiral tooth 26 shown in Fig. 9 is opposite to that of the second spiral tooth 26 in the first embodiment, but it may of course be the same as the winding direction of the second spiral tooth 26 in the first embodiment.
  • the tip seal groove 70 is formed fragmentarily in the extension direction of the second spiral tooth 26. This is to avoid overlap between the tip seal 71 and the injection port of the fixed scroll 21.
  • the tip seal groove 70 is interrupted at two points in the extension direction of the second spiral tooth 26.
  • Labyrinth grooves 72e, 72f are formed in the portions where the tip seal groove 70 is interrupted. In other words, each of the labyrinth grooves 72e, 72f is formed in a portion where there is no tip seal groove 70 in the extension direction of the second spiral tooth 26.
  • the tip seal groove 70 is formed in a fragmentary manner.
  • the labyrinth grooves 72e and 72f are formed in the portions where the tip seal groove 70 is interrupted. With this configuration, it is possible to prevent refrigerant leakage in the portions where the tip seal 71 is not formed.
  • the compressor 100 according to the above embodiment can be modified as appropriate.
  • the above embodiment illustrates a case where the compressor 100 has one compression unit 10, but the compressor 100 may have multiple compression units 10.
  • the above embodiment illustrates a hermetic compressor 100, but the compressor 100 may be an open type or a semi-hermetic type.
  • labyrinth grooves are formed on both the tip surface 24c of the first spiral tooth 24 and the tip surface 26c of the second spiral tooth 26.
  • labyrinth grooves may be formed on only one of the tip surface 24c of the first spiral tooth 24 and the tip surface 26c of the second spiral tooth 26.
  • 1 refrigeration cycle device 1a outdoor unit, 1b indoor unit, 2 oil reservoir, 3 discharge port, 5 discharge valve, 6 valve retainer, 7 discharge muffler, 8 low pressure space, 9 high pressure space, 10 compression unit, 11 compression chamber, 12 suction chamber, 13 discharge chamber, 21 fixed scroll, 22 oscillating scroll, 22a Oldham ring, 23 first base plate, 24 first spiral tooth, 24a winding start portion, 24b winding end portion, 24c tip surface, 25 second base plate , 26 second spiral tooth, 26a winding start portion, 26b winding end portion, 26c tip surface, 26d outward surface, 26e inward surface, 27 boss portion, 27a rocking bearing, 28 injection port, 30 motor unit, 31 stator, 32 rotor, 33 main shaft, 33a eccentric shaft portion, 33b main shaft portion, 33c counter shaft portion, 33d oil passage, 34 sleeve, 36 suction port, 40 container, 41 lid portion, 42 body portion, 43 bottom portion, 44 Suction pipe, 45 discharge pipe, 46 frame, 46a main bearing, 47 subframe

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  • General Engineering & Computer Science (AREA)
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PCT/JP2023/039811 2023-11-06 2023-11-06 圧縮機 Pending WO2025099790A1 (ja)

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0421787U (https=) * 1990-06-14 1992-02-24
JPH04311692A (ja) * 1991-04-10 1992-11-04 Zexel Corp スクロール流体機械
JP2000170673A (ja) * 1998-12-09 2000-06-20 Fujitsu General Ltd スクロール圧縮機
JP2002527670A (ja) * 1998-10-13 2002-08-27 ミンド テック コーポレイション 真空ポンプ用スクロールタイプ流体容積形装置
JP2003254264A (ja) * 2002-03-06 2003-09-10 Matsushita Electric Ind Co Ltd スクロ−ル圧縮機
JP2012189005A (ja) * 2011-03-10 2012-10-04 Mitsubishi Heavy Ind Ltd スクロール流体機械
WO2019043741A1 (ja) * 2017-08-28 2019-03-07 三菱電機株式会社 圧縮機

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0421787U (https=) * 1990-06-14 1992-02-24
JPH04311692A (ja) * 1991-04-10 1992-11-04 Zexel Corp スクロール流体機械
JP2002527670A (ja) * 1998-10-13 2002-08-27 ミンド テック コーポレイション 真空ポンプ用スクロールタイプ流体容積形装置
JP2000170673A (ja) * 1998-12-09 2000-06-20 Fujitsu General Ltd スクロール圧縮機
JP2003254264A (ja) * 2002-03-06 2003-09-10 Matsushita Electric Ind Co Ltd スクロ−ル圧縮機
JP2012189005A (ja) * 2011-03-10 2012-10-04 Mitsubishi Heavy Ind Ltd スクロール流体機械
WO2019043741A1 (ja) * 2017-08-28 2019-03-07 三菱電機株式会社 圧縮機

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