Compressor and refrigeration cycle device

Abstract

This compressor comprises: a sealed container; a compression mechanism that is disposed in the sealed container and compresses a combustible refrigerant in which an odorant is mixed; an electric motor having a stator that has a stator core and a coil, and a rotor that is disposed inside the stator, the electric motor being disposed above the compression mechanism inside the sealed container; a rotary shaft that connects the compression mechanism and the rotor; and an oil separator that is provided so as to rotate together with the rotary shaft above the electric motor, and that separates a refrigerating machine oil from a mixed gas obtained by mixing the refrigerating machine oil and the combustible refrigerant in which the odorant is mixed, the mixed gas being fed above the electric motor. The oil separator includes an annular flat surface part extending radially outward with respect to the rotary shaft, and an annular lower extension part formed extending downward from the outer periphery of the flat surface part, the lower end of which is positioned above the coil end protruding from the axial end part of the stator core in the coil of the stator.

Description

Compressor and refrigeration cycle device

[0001] The present disclosure relates to a compressor and a refrigeration cycle device whose interior is lubricated by refrigeration oil.

[0002] A typical compressor has an electric motor with a rotor and a stator arranged in the upper part of a sealed container, and a compression mechanism that is driven by the rotating shaft of the electric motor and compresses a refrigerant arranged in the lower part of the sealed container. The compressor stores refrigeration oil at the bottom of the sealed container to smoothly lubricate each part, and a pump installed at the bottom of the rotating shaft draws up the refrigeration oil and supplies it to the sliding parts of the compression mechanism to lubricate them.

[0003] In the compressor of Patent Document 1, the refrigerant compressed by the compression mechanism and discharged into the sealed container flows into the space above the motor in the sealed container together with gasified refrigeration oil through the air gap between the rotor and stator and through air holes provided in the rotor. The gas mixture of refrigeration oil and refrigerant that has flowed into the space above the motor hits an oil separator fixed to the upper end of the rotor and is separated into refrigeration oil and refrigerant. The separated refrigeration oil returns to the bottom of the sealed container by its own weight, and the refrigerant is discharged outside the sealed container.

[0004] The oil separator of Patent Document 1 has a configuration in which a cut-and-raised portion is formed by cutting and raising a portion of a disk-shaped plate-like member. In the oil separator of Patent Document 1, a gas mixture of refrigerating machine oil and refrigerant collides with the cut-and-raised portion, and the colliding gas mixture is scattered in all directions by centrifugal force caused by the rotation of the oil separator. The oil separator of Patent Document 1 increases the number and amount of collisions of the gas mixture with surrounding components such as the stator as it scatters in all directions, thereby improving the separation effect of refrigerating machine oil contained in the refrigerant.

[0005] Japanese Patent Application Laid-Open No. 2005-351122

[0006] The compressor of Patent Document 1 is said to enhance the separation effect of refrigeration oil contained in the refrigerant by using the cut-and-raised portion of the oil separator. However, in the oil separator of the compressor of Patent Document 1, the refrigerant containing refrigeration oil passes from the bottom to the top through the opening adjacent to the cut-and-raised portion. In other words, in the compressor of Patent Document 1, the refrigerant containing refrigeration oil passes through the opening and is discharged from the refrigerant discharge pipe at the top of the sealed container, which may result in insufficient separation of the refrigerant oil from the refrigerant.

[0007] Recently, the use of flammable refrigerants such as R290 (propane) with a low GWP has been considered for compressors. GWP stands for Global Warming Potential, and is a value that indicates the value of a gas compared to carbon dioxide, which is set to 1.

[0008] In the technical field of compressors, when a flammable refrigerant is used as the refrigerant, mixing an odorant into the refrigerant has been considered so that a person can recognize a refrigerant leak from the compressor to the outside. However, if the odorant mixed into the refrigerant dissolves in the refrigerant oil, the amount of odorant contained in the refrigerant decreases. If the compressor discharges a refrigerant with a low amount of odorant mixed in the refrigerant, it becomes difficult for a person to recognize a refrigerant leak from the compressor. Therefore, it is important for the compressor to separate the mixed gas, which is a mixture of refrigerant oil, odorant, and refrigerant present inside the compressor, into the refrigerant oil and the flammable refrigerant mixed with the odorant.

[0009] The present disclosure has been made in consideration of the above circumstances, and aims to provide a compressor and a refrigeration cycle device that can suitably separate a mixed gas into refrigerating machine oil and a flammable refrigerant mixed with an odorant.

[0010] The compressor according to the present disclosure comprises a sealed container, a compression mechanism disposed within the sealed container and compressing a flammable refrigerant mixed with an odorant, a stator having a stator core and a coil, and a rotor disposed within the stator, an electric motor disposed above the compression mechanism within the sealed container, a rotating shaft connecting the compression mechanism and the rotor, and an oil separator disposed above the electric motor so as to rotate together with the rotating shaft, and configured to separate refrigeration oil from a mixed gas of the flammable refrigerant mixed with the odorant and the refrigeration oil, which is fed above the electric motor, wherein the oil separator comprises an annular flat portion extending radially outward relative to the rotating shaft, and an annular downward extension portion extending downward from the outer periphery of the flat portion, the lower end of which is located above a coil end of the stator coil that protrudes from the axial end of the stator core.

[0011] A refrigeration cycle device according to the present disclosure includes the above-described compressor, a condenser, a pressure reducer, and an evaporator.

[0012] In the compressor and refrigeration cycle apparatus according to the present disclosure, the oil separator has an annular downward extension portion that extends downward from the outer periphery of the flat portion and has a lower end located above the coil end, and the downward extension portion can guide the mixed gas that is sent above the motor and hits the flat portion to the coil end. This allows the compressor and refrigeration cycle apparatus to increase the amount of mixed gas that hits the coil end compared to a configuration in which the oil separator does not have a downward extension portion, and can effectively separate the mixed gas into refrigeration oil and a flammable refrigerant mixed with an odorant.

[0013] FIG. 1 is a schematic cross-sectional view of a compressor according to embodiment 1. FIG. 2 is a schematic cross-sectional view of an electric motor taken along line A-A in FIG. 1. FIG. 3 is a plan view of a balancer for the compressor according to embodiment 1. FIG. 4 is a perspective view of the balancer for the compressor according to embodiment 1. FIG. 5 is a schematic cross-sectional view of the surrounding portion including the oil separator for the compressor according to embodiment 1. FIG. 6 is a plan view of the oil separator for the compressor according to embodiment 1. FIG. 7 is an explanatory diagram of the dimensional setting of the oil separator for the compressor according to embodiment 1. FIG. 8 is an explanatory diagram of the operation based on the relationship T1<T2 in the oil separator for the compressor according to embodiment 1. FIG. 9 is an explanatory diagram of the operation based on the relationship H1<H2 in the oil separator for the compressor according to embodiment 1. FIG. 10 is a schematic cross-sectional view of a compressor according to embodiment 2. FIG. 11 is a refrigerant circuit diagram showing the schematic configuration of a refrigeration cycle device according to embodiment 3.

[0014] Hereinafter, embodiments will be described with reference to the drawings. Note that the present disclosure is not limited to the embodiments described below. In addition, in the following drawings including FIG. 1, the relative dimensional relationships and shapes of each component may differ from the actual ones. In addition, in the following drawings, items with the same reference numerals are the same or equivalent, and this applies throughout the entire specification.

[0015] Embodiment 1. [Configuration of compressor 100] Fig. 1 is a schematic cross-sectional view of compressor 100 according to embodiment 1. Fig. 2 is a schematic cross-sectional view of electric motor 30 taken along line A-A in Fig. 1. Fig. 3 is a plan view of balancer 39 of compressor 100 according to embodiment 1. Fig. 4 is a perspective view of balancer 39 of compressor 100 according to embodiment 1. The overall configuration of compressor 100 will be described using Figs. 1 to 4.

[0016] As shown in Fig. 1, the compressor 100 according to the first embodiment is a one-cylinder rotary compressor having one cylinder 23, i.e., a single rotary compressor, as an example of a hermetic compressor 100. The compressor 100 is not limited to a single rotary compressor, and may be a rotary compressor having multiple cylinders. The compressor 100 may be a compressor having another structure, such as a twin rotary compressor having two cylinders.

[0017] The compressor 100 is arranged within a sealed container 10. The compressor 100 includes a compression mechanism 20 that compresses refrigerant gas, an electric motor 30 that drives the compression mechanism 20, and a rotating shaft 21 that connects the compression mechanism 20 to a rotor 31 (described below) of the electric motor 30. The compressor 100 is arranged such that the compression mechanism 20 is housed below the sealed container 10 and the electric motor 30 is housed above the sealed container 10. The compression mechanism 20 is disposed below the electric motor 30 within the sealed container 10, and the electric motor 30 is disposed above the compression mechanism 20 within the sealed container 10. In the following description, the direction in which the rotating shaft 21 extends is referred to as the axial direction, and the direction perpendicular to this axial direction is referred to as the radial direction. The axial direction on the page is referred to as the upward direction, and the bottom of the page is referred to as the downward direction. The radially axial center side is referred to as the inner side, and the side opposite the radially axial center side is referred to as the outer side.

[0018] The compression mechanism 20 and the electric motor 30 are connected by a rotating shaft 21. The rotating shaft 21 transmits the rotational motion of the electric motor 30 to the compression mechanism 20. The compression mechanism 20 compresses the refrigerant gas by the transmitted rotational force and discharges the compressed refrigerant gas into the sealed container 10.

[0019] The sealed container 10 is filled with high-temperature, high-pressure refrigerant gas compressed by the compression mechanism 20. An oil reservoir 10a is formed below, i.e., at the bottom of, the sealed container 10 to store refrigerating machine oil 300. The refrigerating machine oil 300 is used to lubricate the compression mechanism 20 and the like. The refrigerating machine oil 300 in the oil reservoir 10a is pumped up from the bottom of the rotating shaft 21 by the centrifugal pump action caused by the rotation of the rotating shaft 21, and is supplied to each sliding part of the compression mechanism 20 through an oil supply hole formed axially inside the rotating shaft 21. In the compressor 100, the mechanical lubrication of the compression mechanism 20 is ensured by supplying the refrigerating machine oil 300 to each sliding part of the compression mechanism 20.

[0020] The refrigerant in the first embodiment is a flammable refrigerant mixed with an odorant 301. Therefore, the sealed container 10 is filled with the flammable refrigerant gas mixed with the odorant 301. The odorant 301 is dissolved in the refrigeration oil 300 stored in the oil reservoir 10a. For example, R290 (propane) or R600a is used as the flammable refrigerant, but the refrigerant is not limited to these refrigerants.

[0021] The odorant 301 may be, for example, a sulfur-based odorant such as a mercaptan, a sulfide, or a thiophene, but is not limited to these odorants. Examples of mercaptans include methyl mercaptan (MM), ethyl mercaptan (EM), normal propyl mercaptan (NPM), isopropyl mercaptan (IPM), or tertiary butyl mercaptan (TBM). Examples of sulfides include dimethyl sulfide (DMS), diethyl sulfide (DES), or methyl ethyl sulfide (MES). Examples of thiophenes include tetrahydrothiophene (THT). These sulfur-based odorants are compounds that have been used in fuel gases and have an unpleasant odor. These sulfur-based odorants may be used alone or in combination of two or more.

[0022] A suction connecting pipe 101a communicating with a suction muffler 101 is connected to the sealed container 10, and the flammable refrigerant mixed with the odorant 301 is taken into the sealed container 10 from the suction muffler 101. A discharge pipe 61 is connected to the top of the sealed container 10, and the refrigerant compressed by the compression mechanism 20 is discharged from the discharge pipe 61.

[0023] The rotating shaft 21 has a main shaft portion 21a, an eccentric shaft portion 21b, and a counter shaft portion 21c, which are formed in this order from top to bottom in the axial direction. The main shaft portion 21a is fixed to the center of the rotor 31 of the electric motor 30 by shrink fitting or press fitting. The eccentric shaft portion 21b is slidably fitted inside the rolling piston 22, which will be described later.

[0024] The compression mechanism 20 includes a cylinder 23, a rolling piston 22, an upper bearing 24, a lower bearing 25, and a vane 26. The cylinder 23 is annular, with a through-hole formed in the approximate center in the vertical direction. Openings at both axial ends of the through-hole are closed by the upper bearing 24 and the lower bearing 25, forming a cylindrical space, i.e., a cylinder chamber 23a, within the cylinder 23. The eccentric shaft portion 21b of the rotating shaft 21, the rolling piston 22, and the vane 26 are housed within the cylinder chamber 23a. The vane 26 is slidably disposed in a vane groove (not shown) formed in the cylinder 23, and divides the cylinder chamber 23a into a suction chamber and a compression chamber.

[0025] The rolling piston 22 is formed in a ring shape, and the inner periphery of the rolling piston 22 is slidably fitted onto the outer periphery of the eccentric shaft portion 21b of the rotary shaft 21. The rolling piston 22 rotates eccentrically within the cylinder chamber 23a as the rotary shaft 21 rotates.

[0026] The upper bearing 24 is fitted onto the main shaft portion 21a of the rotary shaft 21 and rotatably supports the main shaft portion 21a. The upper bearing 24 also closes the axially upper opening of the cylinder chamber 23a. The upper bearing 24 is provided with a discharge port (not shown) that discharges the refrigerant gas compressed in the cylinder chamber 23a to the outside of the cylinder chamber 23a. The upper bearing 24 is formed in a substantially inverted T-shape in side view.

[0027] A discharge valve is provided in the discharge port of the upper bearing 24, and controls the discharge timing of the high-temperature, high-pressure refrigerant gas discharged from the cylinder chamber 23a through the discharge port. That is, the discharge valve closes the discharge port until the refrigerant gas compressed in the cylinder chamber 23a reaches a predetermined pressure, and opens the discharge port once the pressure reaches or exceeds the predetermined pressure, thereby discharging the high-temperature, high-pressure refrigerant gas out of the cylinder chamber 23a.

[0028] The lower bearing 25 is fitted onto the countershaft portion 21c of the rotary shaft 21 and rotatably supports the countershaft portion 21c. The lower bearing 25 closes the axially lower opening of the cylinder chamber 23a. The lower bearing 25 is formed in a substantially T-shape in side view.

[0029] The cylinder chamber 23a repeatedly sucks, compresses, and discharges refrigerant gas. As a result, the refrigerant gas is intermittently discharged from the discharge port, generating noise such as pulsating sounds. To reduce this noise, a discharge muffler 27 is attached to the outer side of the upper bearing 24, i.e., on the motor 30 side, so as to cover the upper bearing 24. The discharge muffler 27 has a discharge hole (not shown) that connects the space formed by the discharge muffler 27 and the upper bearing 24 to the inside of the sealed container 10.

[0030] A suction muffler 101 is provided next to the sealed container 10. The suction muffler 101 prevents liquid refrigerant from being directly drawn into the cylinder chamber 23a of the cylinder 23. A mixture of low-pressure refrigerant gas and liquid refrigerant is sent to the compressor 100 from an external circuit connected to the compressor 100. When the liquid refrigerant flows into the cylinder chamber 23a and is compressed by the compression mechanism 20, a load is placed on the compression mechanism 20. Therefore, the suction muffler 101 separates the liquid refrigerant from the refrigerant gas and sends only the refrigerant gas to the cylinder chamber 23a. The suction muffler 101 is connected to the upper bearing 24 via a suction connecting pipe 101a. The upper bearing 24 has a suction hole 24a that connects the open end of the suction connecting pipe 101a within the upper bearing 24 to the cylinder chamber 23a. Refrigerant sent from the suction muffler 101 via the suction connecting pipe 101a is supplied to the cylinder chamber 23a via the suction hole 24a.

[0031] An oil separator 50 that separates the refrigerating machine oil 300 from a gas mixture (hereinafter referred to as a mixed gas) of the refrigerating machine oil 300 and the flammable refrigerant having the odorant 301 dissolved therein is fixed to the upper part of the rotating shaft 21. The configuration and operation of the oil separator 50 will be described later.

[0032] The electric motor 30 includes a substantially cylindrical rotor 31 fixed to the rotary shaft 21, and a substantially cylindrical stator 32 fixedly held within the sealed container 10. The rotor 31 is disposed inside the stator 32.

[0033] 2, rotor 31 is composed of rotor core 42 formed by laminating rotor core sheets punched from thin electromagnetic steel sheets. Rotor 31 can be configured in two ways: one that uses permanent magnets 34 like a brushless DC motor, and one that uses a secondary winding like an induction motor.

[0034] 2, the rotor 31 has a configuration in which permanent magnets 34 such as ferrite magnets or rare earth magnets are inserted into magnet insertion holes 33 formed in the rotor core 42 and extending in the axial direction. When the motor 30 is a brushless DC motor, the permanent magnets 34 form magnetic poles on the rotor 31, and the rotor 31 is rotated by the interaction of the magnetic flux created by the magnetic poles on the rotor 31 and the magnetic flux created by the stator 32 windings of the stator 32.

[0035] When the electric motor 30 is an induction motor (not shown), the rotor 31 has a configuration in which a secondary winding is provided on the rotor core 42 instead of the permanent magnet 34. When the electric motor 30 is an induction motor, the stator 32 winding of the stator 32 induces magnetic flux in the secondary winding on the rotor 31 side to generate a rotational force, causing the rotor 31 to rotate.

[0036] A shaft hole 35 through which the rotating shaft 21 passes is provided in the center of the rotor core 42, and the main shaft portion 21a of the rotating shaft 21 is inserted into the shaft hole 35 and fixed by shrink fitting or the like. By fixing the rotating shaft 21 to the rotor core 42, the rotational motion of the rotor 31 is transmitted to the rotating shaft 21. The rotor core 42 is formed with air holes 36 that pass through in the axial direction. A plurality of air holes 36 are formed around the shaft hole 35 at intervals. In the illustrated example, a plurality of air holes 36 are formed at intervals in the circumferential direction, but the number and arrangement of the air holes 36 can be set as desired.

[0037] The air holes 36 serve to guide the high-pressure, high-temperature refrigerant gas discharged from the compression mechanism 20 disposed below the motor 30 to the top of the sealed container 10, and also to allow the refrigeration oil 300 guided to the top of the sealed container 10 together with the refrigerant gas to fall to the bottom of the sealed container 10. In addition to the air holes 36, the high-pressure, high-temperature refrigerant gas discharged from the compression mechanism 20 also passes through the air gap between the rotor 31 and the stator 32 or the gaps in the coils 38 of the stator 32, which will be described later.

[0038] 2, the stator 32 includes a plurality of stator cores 37 formed by laminating stator core sheets punched from thin electromagnetic steel plates, and coils 38. The stator core 37 includes arc-shaped yoke portions 37a, teeth portions 37b protruding inward from the inner peripheral surface of the yoke portions 37a, and arc-shaped shoe portions 37c protruding on both circumferential sides from the inner tips of the teeth portions 37b.

[0039] The coil 38 is formed by winding an electric wire around the stator core 37 from the outside of insulating members 41 installed on the upper and lower surfaces of the stator core 37. As shown in FIG. 5 (described later), the insulating members 41 include an outer flange 41a, tooth end surface covering portions 41b, and an inner flange 41c. The outer flange 41a is provided facing the yoke portion 37a of the stator core 37, the tooth end surface covering portions 41b are provided facing the teeth portions 37b of the stator core 37, and the inner flange 41c is a portion provided facing the shoe portion 37c of the stator core 37. The coil 38 is formed by winding an electric wire around the stator core 37 from the outside of the tooth end surface covering portions 41b of the insulating members 41, thereby forming coil ends 38a that protrude from the axial end surfaces of the rotor core 42 as shown in FIG. 1. The coil end 38 a is a collective portion of the electric wires of the coil 38 that protrudes from the axial end face of the rotor core 42 .

[0040] The rotor 31 may be provided with a balancer to counterbalance the imbalance caused by the eccentric rotational motion of the rolling piston 22. FIG. 1 shows an example in which balancers 39 and 40 are provided on the rotor 31. Balancer 39 is fixed to the upper end of the rotor 31, and balancer 40 is fixed to the lower end of the rotor 31. Balancer 39 has a configuration in which an annular base portion 39a having a through hole 39c at its center through which the rotating shaft 21 passes, and an arc-shaped eccentric portion 39b protruding in an arc shape in the axial direction from the upper surface of base portion 39a are integrally formed. Balancer 39 has a through hole 39d penetrating in the axial direction at a position opposite the air hole 36 provided in the rotor 31. Balancer 40 has the same external shape as balancer 39 and, like balancer 39, has a through hole 40a (see FIG. 5) extending in the axial direction at a position opposite the air hole 36 provided in the rotor 31.

[0041] Next, the operation of the compressor 100 configured as described above will be described. When the electric motor 30 is driven, the rotational force of the electric motor 30 is transmitted to the main shaft portion 21a. The rotational force transmitted to the main shaft portion 21a is then transmitted to the eccentric shaft portion 21b attached to the main shaft portion 21a, and the rolling piston 22 rotates eccentrically together with the eccentric shaft portion 21b within the cylinder chamber 23a.

[0042] In the compression mechanism 20, the rolling piston 22 rotates eccentrically within the cylinder chamber 23a, thereby drawing refrigerant from the suction connecting pipe 101a into the suction chamber of the cylinder chamber 23a, and compressing the refrigerant in the compression chamber of the cylinder chamber 23a as the rolling piston 22 rotates. When the high-pressure, high-temperature refrigerant gas in the compression chamber reaches a predetermined pressure, a discharge valve provided in a discharge port of the upper bearing 24 opens, and the refrigerant is temporarily discharged through the discharge valve into a discharge muffler 27 outside the compression chamber.

[0043] The refrigerant discharged into the discharge muffler 27 is discharged from the discharge hole of the discharge muffler 27 into the internal space of the sealed container 10. The high-pressure, high-temperature refrigerant gas discharged into the internal space of the sealed container 10 passes through the air holes 36 formed in the motor 30, the air gap between the rotor 31 and the stator 32, and the gaps in the coils 38 of the stator 32, and flows into the space above the motor 30.

[0044] The refrigerant gas flowing into the space above the motor 30 contains refrigerant oil 300 and odorant 301. As described above, the refrigerant gas is a flammable refrigerant, and the refrigerant gas flowing into the space above the motor 30 is a mixed gas of refrigerant oil 300 and the flammable refrigerant mixed with odorant 301. The mixed gas is separated into refrigerant oil 300 and the flammable refrigerant mixed with odorant 301 by an oil separator 50, which will be described in detail below. The flammable refrigerant mixed with odorant 301 is discharged from a discharge pipe 61 to the outside of the sealed container 10. A refrigerant circuit through which the refrigerant flows is configured outside the sealed container 10, and the refrigerant mixed with odorant 301 discharged to the outside of the sealed container 10 circulates through the refrigerant circuit and returns to the suction muffler 101. Meanwhile, the refrigerant oil 300 returns to the bottom of the sealed container 10 by gravity.

[0045] [Configuration of Oil Separator 50] Next, the oil separator 50 will be described in detail.

[0046] Fig. 5 is a schematic cross-sectional view of the oil separator 50 and its surroundings of the compressor 100 according to the first embodiment. Fig. 6 is a plan view of the oil separator 50 of the compressor 100 according to the first embodiment.

[0047] The oil separator 50 is fixed to the rotating shaft 21 above the rotor 31 of the electric motor 30. The oil separator 50 separates refrigeration oil 300 from the refrigerant sent above the electric motor 30. The oil separator 50 has a cylindrical portion 51 extending in the axial direction, a flat portion 52 formed by an annular disk extending radially outward from the upper end of the cylindrical portion 51, and a downward extending portion 53 formed by an annular disk extending downward from the outer periphery of the flat portion 52. The cylindrical portion 51, the flat portion 52, and the downward extending portion 53 may be formed integrally or joined to one another.

[0048] The oil separator 50 has a cylindrical portion 51 inserted into the rotating shaft 21 and is fixed to the rotating shaft 21, and rotates together with the rotating shaft 21. The oil separator 50 is not limited to being fixed to the rotating shaft 21, and may be fixed to the rotor 31. The oil separator 50 may be provided so as to rotate together with the rotating shaft 21.

[0049] The flat surface portion 52 is formed to a size such that all of the air holes 36 formed in the rotor 31 fit within the outer periphery of the flat surface portion 52 when viewed in the axial direction. The flat surface portion 52 faces all of the air holes 36 formed in the rotor 31 in the axial direction. The outer periphery of the flat surface portion 52 corresponds to the two-dot chain circle C1 in Figure 2, and all of the air holes 36 are located inside the circle C1.

[0050] The downward extension 53 extends radially outward from the outer periphery of the flat portion 52 downward. The downward extension 53 is inclined when viewed in a cross section along the axial direction. The lower end 53b of the downward extension 53 is located above the coil end 38a. The positional relationship between the downward extension 53 and the coil end 38a is set so that the coil end 38a is located on an extension line 1 of the lower surface 53a of the downward extension 53.

[0051] In the illustrated example, the downward extension portion 53 is inclined when viewed in a cross section along the axial direction, but it may be formed to extend in the axial direction. In this case, the outer diameter of the flat portion 52 is formed to be larger than the outer diameter shown, and the downward extension portion 53 is configured to extend vertically downward along the axial direction from the outer periphery of the flat portion 52. In short, the downward extension portion 53 is configured so that the lower end 53b of the downward extension portion 53 is located above the coil end 38a. Here, the lower end 53b of the downward extension portion 53 is only required to be located above any portion of the coil end 38a in the radial direction, and does not have to be above the upper end of the coil end 38a.

[0052] [Dimensional Setting of Oil Separator 50] The dimensional setting of each part of the oil separator 50 will be described below.

[0053] 7 is an explanatory diagram illustrating the dimensioning of the oil separator 50 of the compressor 100 according to the first embodiment. The oil separator 50 is configured so that its diameter D2 is larger than the diameter D1 of the rotor 31 and smaller than the diameter D3 of the outer periphery of the coil end 38a. Note that the stator 32 may have coils 38 of either distributed winding or concentrated winding, and in the case of distributed winding, the diameter D3 of the coil end 38a is the diameter of an imaginary circle connecting the radially outer end faces of the multiple coil ends 38a.

[0054] Furthermore, in the oil separator 50, the axial distance T1 between the outer peripheral end 39b3 of the eccentric portion 39b of the balancer 39 and the oil separator 50 is smaller than the axial height T2 of the eccentric portion 39b of the balancer 39. The distance T1 is the distance between the outer peripheral end 39b3 of the eccentric portion 39b of the balancer 39 and a portion 50a of the oil separator 50 that faces the outer peripheral end 39b3 of the eccentric portion 39b of the balancer 39 in the axial direction. The height T2 is the height of the eccentric portion 39b from the upper surface of the base portion 39a.

[0055] In addition, the axial height position H1 (see Figure 9 described below) of the lower end 53b of the downward extension portion 53 of the oil separator 50 is located lower than the axial height position H2 of the upper end surface 39b1 of the eccentric portion 39b of the balancer 39.

[0056] [Explanation of Operation] The operation of the above configuration will be explained.

[0057] (Basic Operation) The gas mixture that rises through the air holes 36 of the rotor 31 and flows out from the air holes 36 collides with the oil separator 50. The gas mixture collides with the flat surface 52 of the oil separator 50. Due to this collision, a portion of the flammable refrigerant in the gas mixture is separated from the refrigeration oil 300 in which the odorant 301 is dissolved, and rises within the sealed container 10 and is discharged to the outside of the sealed container 10 via the discharge pipe 61. The remaining gas mixture flows along the lower surface 53a of the downward extension portion 53, moves radially outward, and collides with the coil 38, particularly the coil end 38a.

[0058] The coil end 38a is the part of the coil 38 that is most likely to become hot within the stator 32, and when the mixed gas collides with the coil end 38a, the heat of the coil end 38a causes the gas mixture to separate into refrigerating machine oil 300 and flammable refrigerant mixed with odorant 301.

[0059] More specifically, the refrigerating machine oil temperature, the odorant boiling point, and the winding temperature have the following relationship: refrigerating machine oil temperature < odorant boiling point < winding temperature. The refrigerating machine oil temperature is, for example, about 60°C to 70°C, the boiling point of the odorant 301 is, for example, about 100°C to 120°C, and the winding temperature is, for example, about 110°C to 140°C. Therefore, when the refrigerating machine oil with the odorant 301 dissolved therein and the refrigerant collide with the winding of the coil end 38a, the oil temperature rises and exceeds the boiling point of the odorant 301. When the oil temperature rises and exceeds the boiling point of the odorant 301, the odorant 301 vaporizes, and the vaporized odorant 301 and the flammable refrigerant are remixed, resulting in separation into the refrigerating machine oil 300 and the flammable refrigerant mixed with the odorant 301. By remixing the vaporized odorant 301 with the flammable refrigerant, the flammable refrigerant mixed with the odorant 301 can have a sufficient odor.

[0060] The flammable refrigerant mixed with the odorant 301 and having a sufficient odor rises within the sealed container 10 and is discharged to the outside of the sealed container 10 through the discharge pipe 61. On the other hand, the refrigerating machine oil 300 is returned to the bottom of the sealed container 10 by gravity.

[0061] Here, the oil separator 50 includes a downward extension 53, and a lower end 53b of the downward extension 53 is located above the coil end 38a, so that the gas mixture that collides with the flat surface 52 can be guided to the coil end 38a by the downward extension 53. In other words, the oil separator 50 can guide the gas mixture that collides with the flat surface 52 to the coil end 38a by the downward extension 53, rather than scattering the gas mixture in all directions. Therefore, the compressor 100 can increase the amount of gas mixture that collides with the coil end 38a compared to a configuration in which the oil separator 50 does not include the downward extension 53, and as a result, the refrigerant can be suitably separated into the refrigeration oil 300 and the flammable refrigerant mixed with the odorant 301.

[0062] (Function Based on the Size of the Flat Portion 52) In the oil separator 50, the flat portion 52 is formed to have a size such that all of the air holes 36 fit within the outer periphery of the flat portion 52 when viewed in the axial direction. By having the flat portion 52 have the above size, the oil separator 50 can cause the mixed gas flowing out of all of the air holes 36 to collide with the flat portion 52. That is, the oil separator 50 can receive the mixed gas flowing out of all of the air holes 36 at the flat portion 52. Therefore, the oil separator 50 can prevent the mixed gas flowing out of the air holes 36 from being discharged to the outside of the sealed container 10 via the discharge pipe 61 without separating the mixed gas. Therefore, the compressor 100 can increase the amount of mixed gas that collide with the coil end 38 a compared to a configuration in which the flat portion 52 does not axially face the air holes 36, thereby improving the separation effect.

[0063] (Action Based on the Positional Relationship Between the Extension Line 1 of the Downward Extending Portion 53 and the Coil Ends 38a) In the compressor 100, the coil ends 38a are arranged on the extension line 1 of the downward extending portion 53 of the oil separator 50. This allows the compressor 100 to move the mixed gas that has collided with the flat portion 52 along the downward extending portion 53 of the oil separator 50, and to efficiently collide with the coil ends 38a. The compressor 100 can cause the mixed gas to collide with the coil ends 38a, which are likely to have the highest temperature within the stator 32, and therefore can efficiently separate the mixed gas into the refrigerating machine oil 300 and the flammable refrigerant mixed with the odorant 301.

[0064] (Function of D2<D1<D3) The diameter D1 of the oil separator 50 is larger than the diameter D2 of the rotor 31 and smaller than the diameter D3 of the outer periphery of the coil end 38a. This allows the compressor 100 to make the mixed gas that collides with the flat surface 52 of the oil separator 50 flow along the flat surface 52 and move to the downward extension 53, and then make it collide with the coil end 38a. The compressor 100 can make the mixed gas easily collide with the coil end 38a, which is the part of the stator 32 that is most likely to have a high temperature, and therefore can efficiently separate the mixed gas into the refrigeration oil 300 and the flammable refrigerant mixed with the odorant 301.

[0065] 8 is a diagram illustrating the operation of the oil separator 50 of the compressor 100 according to the first embodiment, based on the relationship T1<T2. The mixed gas flowing out from the air holes 36 is retained in the form of mist in the space S surrounded by the inner circumferential surface 39b2 of the eccentric portion 39b of the balancer 39, the rotating shaft 21, and the flat surface portion 52 of the oil separator 50, due to the balancer 39 having the eccentric portion 39b. Meanwhile, the mixed gas flowing out from the air holes 36 is diffused by the flow of mixed gas that continuously rises from the air holes 36.

[0066] Here, the compressor 100 has a configuration in which the distance T1 between the oil separator 50 and the balancer 39 in the axial direction is smaller than the height T2 of the eccentric portion 39b of the balancer 39. In other words, the outlet of the oil separator 50 for the gas mixture is narrowed, so to speak, to obtain the following effect. By narrowing the outlet of the oil separator 50, the compressor 100 can converge the gas mixture, which tends to diffuse and scatter in all directions within the space S, as shown by the arrows in FIG. 8 , and guide it to the coil end 38a. In other words, the oil separator 50 has a relationship T1<T2, so that the compressor 100 can increase the convergence of the gas mixture and cause it to collide with the coil end 38a. As a result, the compressor 100 can efficiently separate the gas mixture into the refrigeration oil 300 and the flammable refrigerant mixed with the odorant 301.

[0067] (Action Based on the Height Position H1 Being Lower than the Height Position H2 (hereinafter, H1<H2)) FIG. 9 is a diagram illustrating the action based on the relationship H1<H2 in the oil separator 50 of the compressor 100 according to the first embodiment. Here, if the height position H3 of the lower end 530a of the downward extension portion 530 is higher than the height position H2 of the upper end surface 39b1 of the eccentric portion 39b of the balancer 39, as shown by the dotted line, the mixed gas will flow in a way that does not collide with the coil end 38a, as indicated by the dotted arrow. In this case, the mixed gas will not be separated into the refrigerating machine oil 300 and the flammable refrigerant mixed with the odorant 301.

[0068] In contrast, the compressor 100 has the relationship H1<H2, so that the gas mixture that flows out from the gap between the downward extension 53 and the eccentric portion 39b of the balancer 39 can be intentionally created to flow toward the coil end 38a, as shown by the solid arrow. Therefore, the compressor 100 can efficiently cause the gas mixture to collide with the coil end 38a.

[0069] The relationship H1<H2 is particularly effective for a configuration in which the height position of the upper end of the coil end 38a is located below the height position of the upper end surface 39b1 of the eccentric portion 39b of the balancer 39. Note that the coil end 38a is not limited to a configuration in which the height position of the upper end of the coil end 38a is located below the height position of the upper end surface 39b1 of the eccentric portion 39b of the balancer 39, and may be located above.

[0070] [Effects of Compressor 100 of First Embodiment] As described above, the compressor 100 of the first embodiment includes the sealed container 10 and the compression mechanism 20 that is disposed within the sealed container 10 and compresses the flammable refrigerant mixed with the odorant 301. The compressor 100 includes the electric motor 30 that has the stator 32 having the stator core 37 and the coil 38 and the rotor 31 disposed within the stator 32 and is disposed above the compression mechanism 20 within the sealed container 10, and the rotating shaft 21 that connects the compression mechanism 20 and the rotor 31. The compressor 100 is disposed above the electric motor 30 so as to rotate together with the rotating shaft 21, and includes the oil separator 50 that separates the refrigerating machine oil 300 from a mixed gas that is fed above the electric motor 30 and that is a mixture of the flammable refrigerant mixed with the odorant 301 and the refrigerating machine oil 300. The oil separator 50 comprises an annular flat portion 52 extending radially outward relative to the rotating shaft 21, and an annular downward extension portion 53 formed by extending downward from the outer periphery of the flat portion 52, with its lower end 53b positioned above the coil end 38a of the coil 38 of the stator 32 protruding from the axial end of the stator core 37.

[0071] With the above configuration, the compressor 100 can increase the amount of mixed gas that collides with the coil ends 38a compared to a configuration in which the oil separator 50 does not include the downward extension portion 53. The coil ends 38a are the part of the coil 38 that is most likely to become hot within the stator 32, and when the mixed gas collides with the coil ends 38a, the mixed gas can be separated into the refrigerating machine oil 300 and the flammable refrigerant mixed with the odorant 301. Therefore, by increasing the amount of mixed gas that collides with the coil ends 38a, the compressor 100 can enhance the separation effect and preferably separate the mixed gas into the refrigerating machine oil 300 and the flammable refrigerant mixed with the odorant 301.

[0072] The flat surface portion 52 of the oil separator 50 faces the air holes 36 that are provided axially penetrating the rotor 31. A plurality of the air holes 36 are formed in the rotor 31, and the flat surface portion 52 is formed to a size such that all of the air holes 36 fit within the outer periphery of the flat surface portion 52 when viewed in the axial direction.

[0073] With the above-described configuration, the compressor 100 can cause the mixed gas that has passed through the air holes 36 to collide with the flat surface portion 52. In other words, the compressor 100 can receive the mixed gas that has flowed out from the air holes 36 at the flat surface portion 52, and can increase the amount of mixed gas that collides with the coil end 38 a compared to a configuration in which the flat surface portion 52 does not axially face the air holes 36, thereby improving the separation effect.

[0074] The downward extension 53 of the oil separator 50 is formed so as to extend radially outward as it extends downward. The coil end 38 a of the stator 32 is disposed on an extension line of the downward extension 53 of the oil separator 50.

[0075] With the above-described configuration, the compressor 100 can move the gas mixture that has collided with the flat surface portion 52 of the oil separator 50 along the downward extension portion 53 and efficiently collide with the coil end 38a.

[0076] The diameter D1 of the oil separator 50 is larger than the diameter D2 of the rotor 31 and smaller than the diameter D3 of the outer periphery of the coil end 38a.

[0077] With the above configuration, the compressor 100 can make the gas mixture that collides with the flat surface portion 52 flow along the flat surface portion 52 and move to the downward extending portion 53, and then make it easier for the gas mixture to collide with the coil end 38a.

[0078] The compressor 100 includes a balancer 39 fixed to the upper end of the rotor 31. The balancer 39 has a base portion 39a having a through hole 39c at its center through which the rotating shaft 21 passes, and an eccentric portion 39b that protrudes in an arc shape in the axial direction from the upper surface of the base portion 39a. An axial distance T1 between an outer peripheral end 39b3 of the eccentric portion 39b and the oil separator 50 is smaller than an axial height T2 of the eccentric portion 39b of the balancer 39.

[0079] With the above configuration, the compressor 100 can increase the convergence of the mixed gas that has diffused within the space S surrounded by the inner surface 39b2 of the eccentric portion 39b of the balancer 39, the rotating shaft 21, and the flat portion 52 of the oil separator 50, causing it to collide with the coil end 38a.

[0080] The compressor 100 includes a balancer 39 fixed to the upper end of the rotor 31. The balancer 39 has a base portion 39a having a through hole 39c at its center through which the rotating shaft 21 passes, and an eccentric portion 39b that protrudes in an arc shape in the axial direction from the upper surface of the base portion 39a. A height position H1 of the lower end 53b of the downward extension portion 53 is located below a height position H2 of an upper end surface 39b1 of the eccentric portion 39b of the balancer 39.

[0081] With the above configuration, the compressor 100 can intentionally create a flow toward the coil end 38 a of the gas mixture that flows out from the gap between the downward extension portion 53 and the eccentric portion 39 b of the balancer 39. Therefore, the compressor 100 can efficiently cause the gas mixture to collide with the coil end 38 a.

[0082] Embodiment 2. Embodiment 2 differs from Embodiment 1 in the configuration of the oil separator 50. The following description will focus on the differences between Embodiment 2 and Embodiment 1, and configurations not described in Embodiment 2 are the same as those in Embodiment 1.

[0083] 10 is a schematic cross-sectional view of a compressor 100 according to embodiment 2. An oil separator 50 according to embodiment 2 has an inclined portion 54 between an upper end of a cylindrical portion 51 and an inner peripheral portion of a flat portion 52. When viewed in a cross section perpendicular to the axial direction, the inclined portion 54 has an inclination that slopes radially outward as it extends upward.

[0084] With the above configuration, oil separator 50 can direct the mixed gas flowing out from air holes 36 radially outward along flat portion 52 and inclined portion 54, as shown by the dotted arrows in the figure. As a result, compressor 100 can suppress diffusion of the mixed gas and allow the mixed gas to efficiently collide with coil end 38 a, compared to a configuration in which inclined portion 54 is not provided and the upper end of cylindrical portion 51 and the inner circumferential portion of flat portion 52 are connected perpendicularly.

[0085] [Effects of Compressor 100 of Embodiment 2] The compressor 100 of Embodiment 2 not only provides the same effects as those of Embodiment 1, but also provides the following effects by providing the inclined portion 54 between the upper end of the cylindrical portion 51 and the inner circumferential portion of the flat portion 52. The compressor 100 can suppress diffusion of the mixed gas and efficiently cause the mixed gas to collide with the coil end 38a, and can more effectively separate the refrigerating machine oil 300 from the flammable refrigerant mixed with the odorant 301.

[0086] Third Embodiment The third embodiment relates to a refrigeration cycle apparatus such as an air conditioner in which the compressor 100 according to the first or second embodiment is mounted.

[0087] 11 is a refrigerant circuit diagram showing a schematic configuration of a refrigeration cycle apparatus 200 according to a third embodiment. The refrigeration cycle apparatus 200 includes a refrigerant circuit in which a compressor 100, a suction muffler 101, a four-way switching valve 102, an outdoor heat exchanger 103, a pressure reducer 104, and an indoor heat exchanger 105 are connected by piping. The outdoor heat exchanger 103 and the indoor heat exchanger 105 function as a condenser or an evaporator depending on the switching of the four-way switching valve 102. The four-way switching valve 102 can be omitted from the refrigeration cycle apparatus 200. Therefore, the refrigeration cycle apparatus 200 may include only the compressor 100, the condenser, the pressure reducer 104, and the evaporator. In the air conditioner, the indoor heat exchanger 105 is mounted in the indoor device, and the remaining compressor 100, four-way switching valve 102, outdoor heat exchanger 103, and pressure reducer 104 are mounted in the outdoor device.

[0088] The compressor 100 is the compressor 100 according to any one of the first and second embodiments. The four-way switching valve 102 is connected to the discharge side of the compressor 100 and switches the flow of refrigerant from the compressor 100. The outdoor heat exchanger 103 is, for example, a fin-tube type heat exchanger formed including a pipe through which the refrigerant flows and fins into which the pipe is inserted. The pressure reducer 104 expands the refrigerant. The pressure reducer 104 is, for example, formed of an electronic expansion valve or a thermostatic expansion valve whose opening degree can be adjusted, but may also be formed of a capillary tube whose opening degree cannot be adjusted. The indoor heat exchanger 105 is, for example, a fin-tube type heat exchanger formed including a pipe through which the refrigerant flows and fins into which the pipe is inserted.

[0089] In heating operation when the refrigeration cycle apparatus 200 is applied to an air conditioner, the four-way switching valve 102 is connected to the solid line side in FIG. 11 . High-temperature, high-pressure refrigerant compressed by the compressor 100 flows to the indoor heat exchanger 105, where it condenses and liquefies. The liquefied refrigerant is decompressed by the pressure reducer 104, becomes a two-phase refrigerant with low temperature and low pressure, flows to the outdoor heat exchanger 103, evaporates, gasifies, and returns to the compressor 100 through the four-way switching valve 102. In other words, the refrigerant circulates as shown by the solid arrows in FIG. 11 . Through this circulation, the refrigerant exchanges heat with outside air in the outdoor heat exchanger 103, which serves as an evaporator, and absorbs heat. The refrigerant that has absorbed heat is sent to the indoor heat exchanger 105, which serves as a condenser, where it exchanges heat with indoor air and warms the indoor air.

[0090] In cooling operation, the four-way switching valve 102 is connected to the dashed line side in FIG. 11 . When switching from heating operation to cooling operation, the indoor heat exchanger 105 changes from a condenser to an evaporator, and the outdoor heat exchanger 103 changes from an evaporator to a condenser. High-temperature, high-pressure refrigerant compressed by the compressor 100 flows to the outdoor heat exchanger 103, where it condenses and liquefies. The liquefied refrigerant is decompressed by the pressure reducer 104 and becomes a low-temperature, low-pressure two-phase refrigerant. The low-temperature, low-pressure two-phase refrigerant flows to the indoor heat exchanger 105, evaporates, and gasifies, passing through the four-way switching valve 102 and returning to the compressor 100. In other words, the refrigerant circulates as shown by the dashed arrows in FIG. 11 . Through this circulation, the refrigerant exchanges heat with the indoor air in the indoor heat exchanger 105, which serves as an evaporator, absorbing heat and cooling the indoor air. The refrigerant that has absorbed heat is sent to the outdoor heat exchanger 103, which is a condenser, and exchanges heat with the outside air, releasing the heat to the outside air.

[0091] [Effects of the refrigeration cycle apparatus 200 of embodiment 3] The refrigeration cycle apparatus 200 of embodiment 3 includes the compressor 100 of any one of embodiments 1 and 2, and is therefore able to suitably separate the mixed gas into the refrigerating machine oil 300 and the flammable refrigerant mixed with the odorant 301 in the compressor 100. Therefore, the refrigeration cycle apparatus 200 can circulate the flammable refrigerant sufficiently mixed with the odorant 301 through the refrigerant circuit, making it easier for a person to recognize that the flammable refrigerant has leaked to the outside from the compressor 100 or the refrigerant circuit, improving reliability.

[0092] The refrigeration cycle device 200 can be applied to refrigeration cycle devices used for refrigeration and air conditioning purposes, such as refrigerators, freezers, vending machines, refrigeration devices, and water heaters.

[0093] 10 Sealed container, 10a Oil reservoir, 20 Compression mechanism, 21 Rotating shaft, 21a Main shaft, 21b Eccentric shaft, 21c Sub-shaft, 22 Rolling piston, 23 Cylinder, 23a Cylinder chamber, 24 Upper bearing, 24a Suction hole, 25 Lower bearing, 26 Vane, 27 Discharge muffler, 30 Electric motor, 31 Rotor, 32 Stator, 33 Magnet insertion hole, 34 Permanent magnet, 35 Shaft hole, 36 Air hole, 37 Stator core, 37a Yoke portion, 37b Teeth portion, 37c Shoe portion, 38 Coil, 38a Coil end, 39 Balancer, 39a Base portion, 39b Eccentric portion, 39b1 Upper end surface, 39b2 Inner peripheral surface, 39b3 Outer peripheral end, 39c Through hole, 39d 1. Through hole, 40 balancer, 40a through hole, 41 insulating member, 41a outer flange, 41b tooth end surface covering portion, 41c inner flange, 42 rotor core, 50 oil separator, 50a portion of oil separator axially facing the outer peripheral end of the eccentric portion of the balancer, 51 cylindrical portion, 52 flat portion, 53 downward extension portion, 53a lower surface, 53b lower end, 54 inclined portion, 61 discharge pipe, 100 compressor, 101 suction muffler, 101a suction connecting pipe, 102 four-way switching valve, 103 outdoor heat exchanger, 104 pressure reducer, 105 indoor heat exchanger, 200 refrigeration cycle device, 300 refrigerating machine oil, 301 odorant, 530 downward extension portion, 530a lower end.

Claims

1. A sealed container and a compression mechanism disposed in the sealed container and configured to compress a flammable refrigerant mixed with an odorant; an electric motor including a stator having a stator core and a coil, and a rotor disposed within the stator, the electric motor being disposed above the compression mechanism within the sealed container; a rotating shaft connecting the compression mechanism and the rotor; an oil separator that is provided above the electric motor so as to rotate together with the rotary shaft and that separates the refrigerating machine oil from a mixed gas of the flammable refrigerant and the odorant mixed therein, the mixed gas being fed above the electric motor; The oil separator includes an annular flat portion extending radially outward relative to the rotating shaft, and an annular downward extension portion extending downward from the outer periphery of the flat portion, the lower end of which is located above a coil end of the stator coil that protrudes from an axial end of the stator core.

2. 2. The compressor according to claim 1, wherein the flat surface of the oil separator faces, in the axial direction, a vent hole provided to penetrate the rotor in the axial direction.

3. 3. The compressor according to claim 2, wherein a plurality of the air holes are formed in the rotor, and the flat surface portion is formed to a size such that all of the air holes are contained within a range of the outer periphery of the flat surface portion when viewed in the axial direction.

4. The compressor according to any one of claims 1 to 3, wherein the downward extension portion of the oil separator is formed so as to extend radially outward as it extends downward.

5. The compressor according to any one of claims 1 to 3, wherein the coil end of the stator is arranged on an extension line of the downward extending portion of the oil separator.

6. The compressor according to any one of claims 1 to 3, wherein a diameter D1 of the oil separator is larger than a diameter D2 of the rotor and smaller than a diameter D3 of the outer periphery of the coil end.

7. a balancer fixed to an upper end of the rotor; The compressor according to any one of claims 1 to 3, wherein the balancer has a base portion having a through hole at its center through which the rotating shaft is passed, and an eccentric portion protruding in an arc shape in the axial direction from an upper surface of the base portion.

8. 8. The compressor according to claim 7, wherein the axial distance T1 between the outer peripheral end of the eccentric portion and the oil separator is smaller than the axial height T2 of the eccentric portion of the balancer.

9. 8. The compressor according to claim 7, wherein a height position H1 of the lower end of the downward extension portion is located below a height position H2 of the upper end surface of the eccentric portion of the balancer.

10. 4. The compressor according to claim 1, wherein the oil separator includes a cylindrical portion extending in the axial direction and having the rotating shaft passed therethrough and fixed thereto, an upper end of the cylindrical portion and an inner peripheral portion of the flat portion connected via an inclined portion, and the inclined portion has an inclination that slopes radially outward as it extends upward.

11. A compressor described in any one of claims 1 to 3, wherein the flammable refrigerant is R290 (propane) or R600a.

12. A refrigeration cycle device comprising the compressor according to any one of claims 1 to 3, a condenser, a pressure reducer, and an evaporator.