Compressor

Abstract

This compressor comprises a fixed scroll and an orbiting scroll that orbits with respect to the fixed scroll. The fixed scroll has a first base plate and first spiral teeth that are formed in the first base plate. The orbiting scroll has a second base plate and second spiral teeth that are formed in the second base plate and that mesh with the first spiral teeth. Formed in the tip end surface of each of the first spiral teeth and the second spiral teeth is a tip seal groove in which a tip seal is fitted. A portion of the tip end surfaces of the first spiral teeth and / or the second spiral teeth in which the tip seal groove is not formed has formed therein a labyrinth groove which increases the flow path resistance of the tip end surface in the thickness direction of that tooth.

Description

Compressor

[0001] The present disclosure relates to a compressor having a fixed scroll and an orbiting scroll.

[0002] Conventionally, scroll compressors have been known as compressors for compressing refrigerants for refrigeration or air conditioning applications. The scroll compressor includes a compression unit that combines a fixed scroll and an orbiting scroll, and an electric motor unit that rotates the orbiting scroll. Each of the fixed scroll and the orbiting scroll is provided with spiral teeth. The spiral teeth of the fixed scroll and the spiral teeth of the orbiting scroll mesh with each other to form a compression chamber. When the orbiting scroll rotates relative to the fixed scroll, the refrigerant is compressed in the compression chamber.

[0003] In the compression unit, a high-pressure compression chamber and a 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, compression efficiency decreases, and compressor performance deteriorates. To prevent refrigerant leakage from the high-pressure side to the low-pressure side, a tip seal groove is formed on the tip surface of the spiral teeth and a tip seal is fitted into the tip seal groove (see, for example, Patent Document 1).

[0004] JP 2008-157121 A

[0005] However, each spiral tooth of the fixed scroll and the orbiting scroll has a portion without a tip seal. For example, the end of the spiral tooth of the fixed scroll has a portion that does not overlap with the base plate of the orbiting scroll, making it impossible to provide a tip seal. The beginning of the spiral tooth of the fixed scroll has a portion that overlaps with the seat cavity of the orbiting scroll, making it impossible to provide a tip seal. The beginning of the spiral tooth of the orbiting scroll has a portion that overlaps with the discharge port of the fixed scroll, making it impossible to provide a tip seal. In addition, tip seals are sometimes provided in fragments to avoid overlap with the injection port. For these reasons, even when tip seals are provided on the spiral teeth, there is a problem of refrigerant leakage in the thickness direction of the spiral teeth.

[0006] The present disclosure has been made to solve the above-mentioned problems, and has an object to provide a compressor that can suppress refrigerant leakage in the thickness direction of the spiral teeth.

[0007] A compressor according to the present disclosure includes a fixed scroll and an orbiting scroll that orbits relative to the fixed scroll, wherein the fixed scroll has a first base plate and first spiral teeth formed on the first base plate, and the orbiting scroll has a second base plate and second spiral teeth formed on the second base plate and meshing with the first spiral teeth, and tip surfaces of the first spiral teeth and the second spiral teeth are formed with chip seal grooves into which chip seals are fitted, and a labyrinth groove is formed in a portion of the tip surface of at least one of the first spiral teeth and the second spiral teeth that does not have the chip seal groove, which increases the flow path resistance of the tip surface in a thickness direction of the at least one of the first spiral teeth and the second spiral teeth.

[0008] According to the present disclosure, leakage of refrigerant in the thickness direction of the spiral teeth can be suppressed.

[0009] 1 is a circuit diagram showing the configuration of a refrigeration cycle device including a compressor according to embodiment 1. FIG. 2 is a cross-sectional view showing the configuration of a compressor according to embodiment 1. FIG. 3 is a plan view showing the configuration of a fixed scroll of the compressor according to embodiment 1. FIG. 4 is a plan view showing the configuration of an orbiting scroll of the compressor according to embodiment 1. FIG. 5 is an enlarged cross-sectional view showing the configuration of a labyrinth groove of the compressor according to embodiment 1. FIG. 6 is a plan view showing the configuration of a fixed scroll of a compressor according to a modified example of embodiment 1. FIG. 7 is a plan view showing the configuration of an orbiting scroll of a compressor according to a modified example of embodiment 1. FIG. 8 is a plan view showing the configuration of an orbiting scroll of a compressor according to embodiment 2. FIG. 9 is a plan view showing the configuration of an orbiting scroll of a compressor according to embodiment 3.

[0010] A compressor according to the present disclosure will be described below with reference to the drawings. The present disclosure is not limited to the following embodiments and may be modified in various ways without departing from the spirit and scope of the present disclosure. The present disclosure also includes all possible combinations of the configurations shown in the following embodiments. The combinations of components are not limited to those in the respective embodiments, and components described in one embodiment may be applied to another embodiment. In the following description, directional terms (e.g., "up," "down," "right," "left," "front," "rear," etc.) are used as appropriate to facilitate understanding. However, these terms are for explanatory purposes and do not limit the present disclosure. In the drawings, components designated with the same reference numerals are identical or equivalent, and this applies throughout the entire specification. The relative dimensions or shapes of components in the drawings may differ from those in actuality.

[0011] Embodiment 1. A compressor according to embodiment 1 will be described. Fig. 1 is a circuit diagram showing the configuration of a refrigeration cycle device including a compressor according to this embodiment. The refrigeration cycle device is used, for example, in an air conditioner that conditions indoor air.

[0012] 1, the refrigeration cycle apparatus 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.

[0013] 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 constitute a refrigerant circuit 500. A refrigerant circulates through the refrigerant circuit 500. In this embodiment, the refrigerant is a fluorocarbon refrigerant such as R32, or carbon dioxide (CO ２ Natural refrigerants such as refrigerants are used.

[0014] 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.

[0015] The outdoor heat exchanger 200 is a heat exchanger that exchanges heat between a 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 of this embodiment 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 functions as a condenser. The outdoor blower 201 is a device that sends outdoor air to the outdoor heat exchanger 200.

[0016] The expansion section 300 is configured to reduce the pressure of high-pressure liquid refrigerant and expand it. For example, an expander, a thermostatic automatic expansion valve, or a linear electronic expansion valve with adjustable opening is used for the expansion section 300. The high-pressure liquid refrigerant expanded by the expansion section 300 becomes low-pressure refrigerant in a liquid state or a two-phase gas-liquid state.

[0017] The indoor heat exchanger 400 is a heat exchanger that exchanges heat between a refrigerant in a liquid state or 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 of this embodiment 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 functions as an evaporator. The indoor blower 401 is a device that sends indoor air to the indoor heat exchanger 400.

[0018] The intermediate injection circuit 800 connects the refrigerant pipe 501 between the outdoor heat exchanger 200 and the expansion section 300 with the injection pipe 49 provided in the compressor 100. The refrigerant flowing out from the outdoor heat exchanger 200 flows through 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 compression unit 10 of the compressor 100.

[0019] Similar to the expansion section 300, 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. The injection expansion section 600 may be, for example, an expander, a thermostatic automatic expansion valve, or a linear electronic expansion valve whose opening is adjustable.

[0020] The cooler 700 is a heat exchanger that exchanges heat between a low-temperature, low-pressure liquid refrigerant or a gas-liquid two-phase 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 gas-liquid two-phase refrigerant flowing out of the injection expansion section 600 and the high-pressure liquid refrigerant or a gas-liquid two-phase refrigerant flowing out of the outdoor heat exchanger 200. The cooler 700 may also be omitted from the intermediate injection circuit 800.

[0021] The control device 80 includes, for example, a microcomputer and a memory, and is configured to control each device of the refrigeration cycle device 1. In this embodiment, the control device 80 is configured to adjust the opening degree of the injection expansion section 600 and adjust the amount of refrigerant flowing through the intermediate injection circuit 800.

[0022] FIG. 2 is a cross-sectional view showing the configuration of a compressor according to this embodiment. In this embodiment, a hermetic scroll compressor is used as the compressor. As shown in FIG. 2, the compressor 100 includes a container 40, a frame 46, a sub-frame 47, a main shaft 33, a main bearing 46a, an auxiliary bearing 48, a suction pipe 44, a discharge pipe 45, and a compression unit 10. The compressor 100 also includes a boss 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.

[0023] 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 container 40 houses the compression unit 10, the electric motor unit 30, a frame 46, a subframe 47, and other components. The compression unit 10 is disposed in an upper portion within the container 40. The electric motor unit 30 is disposed in a lower portion within the container 40 than the compression unit 10.

[0024] 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 for storing refrigeration oil is formed. 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 drawn 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.

[0025] 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 electric motor unit 30. The frame 46 is located inside the container 40 between the electric motor unit 30 and the compression unit 10. The frame 46 rotatably supports the main shaft 33 via a main bearing 46a. The main bearing 46a is provided in the center of the frame 46.

[0026] A plurality of suction ports 36 are formed in the frame 46. Each suction port 36 is a through-hole that connects the space between the frame 46 and the motor unit 30 with a space in the compression unit 10 that is located outside the outer contours of the first and second spiral teeth 24, 26. The refrigerant that has flowed into the container 40 is supplied to the compression unit 10 through the plurality of suction ports 36.

[0027] The subframe 47 is fixed within the container 40. The subframe 47 is disposed below the electric motor unit 30 within the container 40. The subframe 47 rotatably supports the main shaft 33 via an auxiliary bearing 48. The auxiliary bearing 48 is provided in the center of the subframe 47. The auxiliary bearing 48 is, for example, a ball bearing. The auxiliary bearing 48 is fixed to the subframe 47 by press fitting. A hole 47a is formed in the subframe 47. Refrigeration oil flowing down toward the oil reservoir 2 passes through the hole 47a.

[0028] The frame 46 and the sub-frame 47 are disposed inside the container 40 so as to face each other with the motor unit 30 in between. The frame 46 and the sub-frame 47 are each fixed to the inner circumferential surface of the body 42 by shrink fitting, welding, or the like.

[0029] The main shaft 33 is a rod-shaped crankshaft. The main shaft 33 extends in the vertical direction 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.

[0030] The main shaft 33 has an eccentric shaft portion 33a, a main shaft portion 33b, and a countershaft 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 refrigerating machine 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 countershaft portion 33c is formed below the main shaft portion 33b. The countershaft portion 33c is supported by a counterbearing 48. An oil passage 33d through which oil flows is formed inside the main shaft 33.

[0031] Within the container 40, a low-pressure space 8 below the compression unit 10 and a high-pressure space 9 above the compression unit 10 are formed. The suction pipe 44 is connected to the low-pressure space 8 at the side of the container 40. Low-pressure gas refrigerant from the refrigerant circuit 500 is drawn into the low-pressure space 8 through the suction pipe 44. The discharge pipe 45 is connected to the high-pressure space 9 at an upper part 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.

[0032] The injection pipe 49 is connected to the compression chamber 11 of the compression unit 10 at an upper part of the container 40. The injection pipe 49 introduces the refrigerant in a liquid state or a gas-liquid two-phase 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.

[0033] The compression unit 10 compresses the refrigerant drawn 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 first spiral teeth 24. The first base plate 23 is a plate-shaped member and forms the upper surface of the compression unit 10. The first spiral teeth 24 are spiral-shaped protrusions formed on the lower surface of the first base plate 23. The first spiral teeth 24 protrude downward from the lower surface of the first base plate 23.

[0034] The orbiting scroll 22 is disposed below the fixed scroll 21 so as to face the fixed scroll 21. The orbiting scroll 22 is configured to oscillate relative to the fixed scroll 21. The orbiting scroll 22 has a second base plate 25 and second spiral teeth 26. The second base plate 25 is a plate-shaped member disposed above the frame 46. The second spiral teeth 26 are spiral protrusions formed on the upper surface of the second base plate 25. The second spiral teeth 26 protrude upward from the upper surface of the second base plate 25. The second spiral teeth 26 are engaged with the first spiral teeth 24.

[0035] The fixed scroll 21 and the orbiting scroll 22 are provided in a 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 to follow an involute curve. By combining the first spiral teeth 24 and the second spiral teeth 26 in an meshed state, a plurality of compression chambers 11 are formed between the first spiral teeth 24 and the second spiral teeth 26.

[0036] A discharge port 3 is formed in the center of the fixed scroll 21. The discharge port 3 is a passage through which 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 a gas-liquid two-phase state that flows in from the injection pipe 49 flows out through the injection port 28 into the compression chamber 11 where the refrigerant in the middle of the compression process exists.

[0037] The boss portion 27 is provided at the center of the surface of the second base plate 25 opposite to the surface on which the second spiral teeth 26 are formed. The boss portion 27 is formed in a hollow cylindrical shape. A swing bearing 27a is provided between the swing scroll 22 and the boss portion 27. The swing bearing 27a rotatably supports an eccentric shaft portion 33a of the main shaft 33. The eccentric shaft portion 33a causes the swing scroll 22 to rotate eccentrically.

[0038] 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 rotation of the orbiting scroll 22 during eccentric orbital motion and allows orbital motion of the orbiting scroll 22. Pawls (not shown) protruding perpendicular to each other are provided on the upper and lower surfaces of the Oldham ring 22a. The pawls on the upper surface of the Oldham ring 22a are slidably inserted into Oldham grooves (not shown) formed in the orbiting scroll 22. The pawls on the lower surface of the Oldham ring 22a are slidably inserted into Oldham grooves (not shown) formed in the frame 46.

[0039] The sleeve 34 is a cylindrical member provided between the frame 46 and the main bearing 46 a. The sleeve 34 absorbs the tilt between the frame 46 and the main shaft 33.

[0040] The discharge valve 5 is a leaf spring member that covers the discharge port 3 and prevents backflow of the refrigerant. The valve guard 6 restricts the movable range 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.

[0041] The oil pump 51 sucks up oil from the oil sump 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 sucks up oil from the oil sump 2 and supplies the oil to the sub-bearing 48, the main bearing 46a, and the rocking bearing 27a via the oil passage 33d.

[0042] 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 sub-frame 47. The oil drain pipe 50 allows excess oil circulating in the space between the frame 46 and the orbiting scroll 22 to flow into the space between the frame 46 and the sub-frame 47. The oil that has flowed into the space between the frame 46 and the sub-frame 47 passes through the sub-frame 47 and returns to the oil reservoir 2.

[0043] The electric motor unit 30 is provided in the low-pressure space 8 inside the vessel 40. The electric motor unit 30 drives the orbiting scroll 22 via the main shaft 33. When the orbiting scroll 22 is driven by the electric motor unit 30, the refrigerant is compressed in the compression unit 10.

[0044] 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.

[0045] Next, the operation of the compressor 100 will be described. When electricity is applied to a power supply terminal (not shown) provided on the container 40, current flows through the coil of the stator 31, generating a magnetic field. The magnetic field generated in the stator 31 causes the rotor 32 and the main shaft portion 33b to rotate. The rotation of the main shaft portion 33b causes the eccentric shaft portion 33a to rotate eccentrically, causing the orbiting scroll 22 to orbit eccentrically. The rotation of the orbiting scroll 22 is restricted by the Oldham ring 22a.

[0046] The low-pressure refrigerant flowing out of the indoor heat exchanger 400 passes through the suction pipe 44 and is drawn into the low-pressure space 8 of the container 40. The refrigerant drawn into the low-pressure space 8 is taken into the suction chamber 12 on the outer periphery of the multiple compression chambers 11. As the orbiting scroll 22 eccentrically orbits, each compression chamber 11 gradually moves from the outer periphery toward the center while reducing its volume. As a result, the refrigerant drawn into the suction chamber 12 moves to the discharge chamber 13 while being compressed.

[0047] 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 then 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.

[0048] As described above, a portion of the refrigerant sucked through 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. Furthermore, 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, thermal expansion of the fixed scroll 21 and the orbiting scroll 22 can be suppressed, and the behavior of the compression unit 10 can be stabilized.

[0049] Next, the operation of the refrigeration cycle apparatus 1 will be described. Refrigerant drawn 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, which functions as a condenser. There, the refrigerant exchanges heat with outdoor air sent by the outdoor blower 201, condensing and liquefying. The condensed liquid refrigerant flows into the expansion section 300, where it expands and is decompressed to become a low-temperature, low-pressure, two-phase gas-liquid refrigerant. The two-phase gas-liquid refrigerant then flows into the indoor heat exchanger 400, which functions as an evaporator. There, the refrigerant exchanges heat with indoor air sent by the indoor blower 401, evaporating and gasifying. At this time, the indoor air is cooled, and the room is cooled. The evaporated low-temperature, low-pressure gas refrigerant is drawn into the compressor 100.

[0050] For example, when the difference between the suction temperature and discharge temperature of the refrigerant drawn into the compressor 100 is large, the refrigerant discharged from the discharge pipe 45 is hot. Note that operation with a large difference between the suction temperature and discharge temperature refers to high compression ratio operation, in which the pressure difference between high pressure and low pressure is large. In this case, the discharge temperature is lowered by injecting liquid or two-phase refrigerant flowing from 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 decompressed to an intermediate pressure by the injection expansion section 600, with its expansion rate and flow rate controlled. The liquid refrigerant decompressed to the intermediate pressure flows into the compressor 100 through the injection pipe 49. The liquid refrigerant flowing into the compressor 100 is injected into the compression chamber 11 through the injection port 28. As a result, the liquid refrigerant cools the gas refrigerant being compressed in the compression chamber 11.

[0051] Next, the detailed configuration of the spiral teeth of each of the fixed scroll and the orbiting scroll will be described. 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 as viewed from the first spiral teeth 24 side. As shown in FIG. 3, 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 spiral start portion 24a and a spiral end portion 24b. The spiral start portion 24a is the end portion located closer to the center of the spiral, of both end portions of the first spiral teeth 24 in the extension direction. The spiral start portion 24a is located adjacent to the discharge port 3. The spiral end portion 24b is the end portion located closer to the outer periphery of the spiral, of both end portions of the first spiral teeth 24 in the extension direction.

[0052] The first spiral tooth 24 has a tip surface 24c. The tip surface 24c faces the second base plate 25 of the orbiting 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 in the extension direction of the first spiral tooth 24, excluding the winding start portions 24a and 24b.

[0053] A tip seal 61 is fitted into the tip seal groove 60. The tip seal 61 slides against the second base plate 25 as the orbiting scroll 22 orbits. The tip seal 61 has a function of preventing refrigerant leakage in the thickness direction of the first spiral tooth 24.

[0054] A labyrinth groove 62a is formed in the spiral start portion 24a of the tip surface 24c of the first spiral tooth 24. A labyrinth groove 62b is formed in the spiral end portion 24b of the tip surface 24c of the first spiral tooth 24. The labyrinth grooves 62a and 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 grooves 62a and 62b are not connected to the tip seal groove 60, but are formed at a distance from the tip seal groove 60.

[0055] The labyrinth groove 62a and the labyrinth groove 62b each form a labyrinth structure that increases the flow path resistance of the tip end surface 24c in the thickness direction of the first spiral tooth 24. The labyrinth groove 62a and the labyrinth groove 62b are each composed of a plurality of grooves arranged parallel to one another. Like the tip seal groove 60, each of the plurality of grooves is formed to follow an involute curve and extends perpendicular to the thickness direction of the first spiral tooth 24. In this embodiment, each of the plurality of 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.

[0056] 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 as viewed from the second spiral tooth 26 side. As shown in FIG. 4, 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 along an involute curve. The second spiral tooth 26 has a spiral start portion 26a and a spiral end portion 26b. The spiral start portion 26a is the end portion located closer to the center of the spiral among both ends of the second spiral tooth 26 in the extension direction. The spiral start portion 26a is positioned so that it can overlap the discharge port 3 on the fixed scroll 21 side depending on the orbiting position of the orbiting scroll 22. The spiral end portion 26b is the end portion located closer to the outer periphery of the spiral among both ends of the second spiral tooth 26 in the extension direction.

[0057] 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 in the extension direction of the second spiral tooth 26, excluding the winding start portions 26a and 26b.

[0058] A tip seal 71 is fitted into the tip seal groove 70. The tip seal 71 slides against the first base plate 23 as the orbiting scroll 22 orbits. The tip seal 71 has a function of preventing refrigerant leakage in the thickness direction of the second spiral tooth 26.

[0059] A labyrinth groove 72a is formed in the spiral start portion 26a of the tip surface 26c of the second spiral tooth 26. A labyrinth groove 72b is formed in the spiral end portion 26b of the tip surface 26c of the second spiral tooth 26. The labyrinth grooves 72a and 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 grooves 72a and 72b are not connected to the tip seal groove 70, but are formed at a distance from the tip seal groove 70.

[0060] The labyrinth groove 72a and the labyrinth groove 72b each form a labyrinth structure that increases the flow path resistance of the tip end surface 26c in the thickness direction of the second spiral tooth 26. The labyrinth groove 72a and the labyrinth groove 72b each comprise a plurality of grooves arranged parallel to one another. Each of the plurality of grooves is formed to follow 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 plurality of 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 comprised of a single groove.

[0061] Fig. 5 is an enlarged cross-sectional view showing the configuration of the labyrinth grooves 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 illustrates the labyrinth groove 72b of the second spiral tooth 26, but the labyrinth groove 72a of the second spiral tooth 26 and the labyrinth grooves 62a and 62b of the first spiral tooth 24 also have the same configuration.

[0062] 5, the labyrinth groove 72b has a plurality of grooves 72b1, 72b2 arranged in parallel in the thickness direction of the second spiral tooth 26. As a result, 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 throttle 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 throttle pieces.

[0063] The protrusions 73 face the first base plate 23 with a gap of distance ε between them. The width of the protrusions 73 in the thickness direction of the second spiral tooth 26 is δ. The spacing between the protrusions 73 in the thickness 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.

[0064] The leakage amount of the fluid is calculated by the following formula (1): where, G0: leakage amount [kgf / s], F: cross-sectional area of ​​the throttle opening [m ２ ], α: flow coefficient, ν: blow-through coefficient, Φ0: labyrinth function, P0: fluid pressure at labyrinth inlet [kg / m ２ ], ν0: specific fluid volume at the labyrinth inlet.

[0065]

[0066] The flow coefficient α is said to be maximized when the ratio δ / ε of the width δ to the distance ε is between 4.8 and 8.0. Therefore, in order to reduce the amount of refrigerant leakage in the thickness direction of the spiral teeth, it is best to avoid the range of δ / ε = 4.8 to 8.0. The optimal ratio of the expansion chamber depth h to the throttling piece spacing S is h / S = 0.15 to 0.3. Increasing the expansion chamber depth h more than necessary does not necessarily reduce the amount of leakage. The amount of leakage can be reduced if the cross-sectional shape of the expansion chamber is a shallow rectangular cross section.

[0067] An optimal labyrinth structure is obtained when the convex portions 73 and concave portions 74 satisfy the conditions δ / ε<4.8, δ / ε>8.0, and 0.15≦h / S≦0.3. For example, to configure the convex portions 73 to satisfy δ / ε=10.0, when δ=1 mm, ε=0.1 mm. Furthermore, when the spacing S between the convex portions 73 is 1 mm, the depth h of the concave portions 74 should be 0.15 mm or more and 0.3 mm or less. However, since various types of compressors are applicable to the present disclosure, the dimensions of the labyrinth structure are not limited to the above example. For example, the magnitude relationships between δ, ε, h, and S can be changed as appropriate.

[0068] FIG. 6 is a plan view showing the configuration of a fixed scroll of a compressor according to a modified example of this embodiment. As shown in FIG. 6 , the labyrinth groove 62a is connected to the end 60a of the tip seal groove 60 at the winding start portion 24a. The labyrinth groove 62b is connected to the end 60b of the tip seal groove 60 at the winding end portion 24b. This increases the lengths of the labyrinth grooves 62a and 62b, and expands the ranges in which the labyrinth grooves 62a and 62b are formed in the extension direction of the first spiral tooth 24. This further reduces refrigerant leakage from the high-pressure side to the low-pressure side, preventing a decrease in performance of the compressor 100 due to refrigerant leakage.

[0069] FIG. 7 is a plan view showing the configuration of an orbiting scroll of a compressor according to a modified example of this embodiment. As shown in FIG. 7 , the labyrinth groove 72a is connected to the end 70a of the tip seal groove 70 at the winding start portion 26a. The labyrinth groove 72b is connected to the end 70b of the tip seal groove 70 at the winding end portion 26b. This increases the lengths of the labyrinth grooves 72a and 72b, and expands the ranges in which the labyrinth grooves 72a and 72b are formed in the extension direction of the second spiral tooth 26. This further reduces refrigerant leakage from the high-pressure side to the low-pressure side, preventing a decrease in performance of the compressor 100 due to refrigerant leakage.

[0070] As described above, the compressor 100 according to this embodiment includes the fixed scroll 21 and the orbiting scroll 22. The orbiting scroll 22 is configured to orbit relative to the fixed scroll 21. The fixed scroll 21 has a first base plate 23 and first spiral teeth 24. The first spiral teeth 24 are formed on the first base plate 23. The orbiting scroll 22 has a second base plate 25 and second spiral teeth 26. The second spiral teeth 26 are formed on the second base plate 25. The second spiral teeth 26 are meshed with the first spiral teeth 24.

[0071] A tip seal groove 60 is formed in the tip surface 24c of the first spiral tooth 24. A tip seal 61 is fitted in the tip seal groove 60. A tip seal groove 70 is formed in the tip surface 26c of the second spiral tooth 26. A tip seal 71 is fitted in the tip seal groove 70. Labyrinth grooves 62a, 62b are formed in the portion of the tip surface 24c of the first spiral tooth 24 where there is no tip seal groove 60, increasing the flow resistance of the tip surface 24c in the thickness direction of the first spiral tooth 24. Labyrinth grooves 72a, 72b are formed in the portion of the tip surface 26c of the second spiral tooth 26 where there is no tip seal groove 70, increasing the flow resistance of the tip surface 26c in the thickness direction of the second spiral tooth 26.

[0072] According to this configuration, the labyrinth grooves 62a, 62b increase the flow path resistance of the tip end surface 24c of the first spiral tooth 24 in the thickness direction, even in the portion where the tip seal 61 is not formed. This reduces refrigerant leakage in the thickness direction of the first spiral tooth 24. Similarly, the labyrinth grooves 72a, 72b increase the flow path resistance of the tip end surface 26c of the second spiral tooth 26 in the thickness direction, even in the portion where the tip seal 71 is not formed. This reduces refrigerant leakage in the thickness direction of the second spiral tooth 26. Therefore, according to this configuration, it is possible to prevent a decrease in performance of the compressor 100 due to refrigerant leakage.

[0073] In the compressor 100 according to this embodiment, the labyrinth grooves 62a, 62b are formed in the spiral start portion 24a and the spiral end portion 24b of the first spiral tooth 24. Generally, the spiral start portion 24a and the spiral end portion 24b of the first spiral tooth 24 have portions where the tip seal 61 is not formed. However, with the above-described configuration, it is possible to prevent refrigerant leakage from the portions where the tip seal 61 is not formed.

[0074] In the compressor 100 according to this embodiment, the labyrinth grooves 72a, 72b are formed at the spiral start portion 26a and the spiral end portion 26b of the second spiral tooth 26. Generally, there are portions at the spiral start portion 26a and the spiral end portion 26b of the second spiral tooth 26 where the tip seal 71 is not formed. However, with the above-described configuration, it is possible to prevent refrigerant leakage from the portions where the tip seal 71 is not formed.

[0075] In the compressor 100 according to this embodiment, 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 grooves have a configuration in which the convex portions 73 and the concave portions 74 are aligned in the thickness direction of each spiral tooth. The convex portions 73 face the first base plate 23 or the second base plate 25 across a gap of distance ε. When the width of the convex portions 73 in the thickness direction of each spiral tooth is δ, the width of the concave portions 74 in the thickness direction of each spiral tooth is S, and the depth of the concave portions 74 is h, the following relationships are satisfied: δ / ε<4.8, δ / ε>8.0, and 0.15≦h / S≦0.3. This configuration provides an optimal labyrinth structure, thereby effectively suppressing refrigerant leakage.

[0076] In the compressor 100 according to this embodiment, the labyrinth groove has a plurality of grooves arranged in parallel in the thickness direction of each spiral tooth. Each of the plurality of grooves has a groove width narrower than the groove width of the tip seal groove. This configuration provides a more suitable labyrinth structure, thereby effectively suppressing refrigerant leakage.

[0077] Second Embodiment A compressor according to a second embodiment will now be described. Fig. 8 is a plan view showing the configuration of the orbiting scroll of the compressor according to this 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.

[0078] As shown in Figure 8, the labyrinth grooves 72c, 72d are each formed along the tip seal groove 70 on the leading end 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. In other words, the labyrinth grooves 72c, 72d are each formed in a portion of the second spiral tooth 26 where there is no tip seal groove 70 in the thickness direction of the second spiral tooth 26. 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. For example, each of the labyrinth grooves 72c and 72d extends continuously along the entire section from the end 70a to the end 70b of the tip seal groove 70.

[0079] Although each of the labyrinth groove 72c and the labyrinth groove 72d in this embodiment is formed by one groove, they may be formed by a plurality of grooves.

[0080] As described above, in the compressor 100 according to this embodiment, the labyrinth grooves 72c, 72d are each formed along the tip seal groove 70. With this configuration, the labyrinth grooves 72a, 72b are formed, which increases the flow path resistance of the tip end surface 24c in the thickness direction of the first spiral tooth 24. Therefore, in addition to sealing by the tip seal 71, sealing by the labyrinth structure can also be performed. Therefore, compared to sealing by the tip seal 71 alone, refrigerant leakage in the thickness direction of the first spiral tooth 24 can be further suppressed.

[0081] Third Embodiment A compressor according to a third embodiment will now be described. 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.

[0082] As shown in Fig. 9, the tip seal groove 70 is formed fragmentarily in the extension direction of the second spiral tooth 26. This is to prevent overlap between the tip seal 71 and the injection port of the fixed scroll 21. In this embodiment, the tip seal groove 70 is interrupted at two locations in the extension direction of the second spiral tooth 26. Labyrinth grooves 72e and 72f are formed in the portions where the tip seal groove 70 is interrupted. In other words, the labyrinth grooves 72e and 72f are each formed in a portion of the extension direction of the second spiral tooth 26 where there is no tip seal groove 70.

[0083] As described above, in the compressor 100 according to this embodiment, the tip seal groove 70 is formed in segments. The labyrinth grooves 72e, 72f are formed in the portions where the tip seal groove 70 is interrupted. This configuration can prevent refrigerant leakage from the portions where the tip seal 71 is not formed.

[0084] The compressor 100 according to the above embodiment can be modified as appropriate. For example, although the above embodiment illustrates a case in which the compressor 100 has one compression unit 10, the compressor 100 may have multiple compression units 10. Furthermore, although the above embodiment illustrates a hermetic compressor 100, the compressor 100 may be an open type or a semi-hermetic type.

[0085] In the above embodiment, 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. However, 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.

[0086] REFRIGERATION CYCLE DEVICE, 1a outdoor unit, 1b indoor unit, 2 oil reservoir, 3 discharge port, 5 discharge valve, 6 valve guard, 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 swing 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 swing bearing, 28 injection port, 30 electric 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, 47a hole, 48 counter bearing, 49 injection piping, 50 oil drain pipe, 51 oil pump, 60 tip seal groove, 60a end, 60b end, 61 tip seal, 62a labyrinth groove, 62b labyrinth groove, 70 tip seal groove, 70a end, 70b end, 71 tip seal, 72a labyrinth groove, 72b labyrinth groove, 72b1 groove, 72b2 groove, 72c labyrinth groove, 72d labyrinth groove, 72e Labyrinth groove, 72f Labyrinth groove, 73 Convex portion, 74 Concave portion, 80 Control device, 100 Compressor, 200 Outdoor heat exchanger, 201 Outdoor blower, 300 Expansion section, 400 Indoor heat exchanger, 401 Indoor blower, 500 Refrigerant circuit, 501 Refrigerant piping, 600 Injection expansion section, 700 Cooler, 800 Intermediate injection circuit.

Claims

1. Fixed scrolling and an orbiting scroll that orbits relative to the fixed scroll; Equipped with the fixed scroll includes a first base plate and a first spiral tooth formed on the first base plate, the orbiting scroll has a second base plate and second spiral teeth formed on the second base plate and meshing with the first spiral teeth, a tip seal groove into which a tip seal is fitted is formed on a tip surface of each of the first spiral tooth and the second spiral tooth; a labyrinth groove is formed in a portion of the tip end surface of at least one of the first spiral tooth and the second spiral tooth, the portion not having the tip seal groove, the labyrinth groove increasing a flow path resistance of the tip end surface in a thickness direction of the at least one of the first spiral tooth and the second spiral tooth, In a cross section perpendicular to the at least one extension direction, the labyrinth groove has a configuration in which convex portions and concave portions are arranged in parallel in the thickness direction, the protrusion faces the first base plate or the second base plate with a gap of a distance ε therebetween, When the width of the convex portion in the thickness direction is δ, the width of the concave portion in the thickness direction is S, and the depth of the concave portion is h, A compressor in which the relationships δ / ε<4.8, δ / ε>8.0 and 0.15≦h / S≦0.3 are satisfied.

2. The compressor according to claim 1 , wherein the labyrinth groove is formed at a winding start portion and a winding end portion of the first spiral tooth.

3. 3. The compressor according to claim 1, wherein the labyrinth groove is formed at a winding start portion and a winding end portion of the second spiral tooth.

4. The compressor according to claim 1 , wherein the labyrinth groove is formed along the tip seal groove.

5. The tip seal groove is formed in a piecewise manner, 2. The compressor according to claim 1, wherein the labyrinth groove is formed in a portion where the tip seal groove is discontinued.

6. the labyrinth groove has a plurality of grooves arranged in parallel in the thickness direction, 3. The compressor according to claim 1, wherein each of the plurality of grooves has a groove width narrower than a groove width of the tip seal groove.