Scroll compressor and refrigeration cycle device

Abstract

To provide a highly efficient and reliable scroll compressor, etc. [Solution] A circular back pressure groove G3 communicating with the back pressure chamber is provided on the mirror plate surface 21f of the fixed scroll 21 of the scroll compressor, and a first groove G1 and a second groove G2 are provided radially inside the back pressure groove G3, the orbiting scroll is provided with a first hole and a second hole that guide lubricating oil from the oil supply passage to the mirror plate surface 21f of the fixed scroll 21, the first groove G1 includes at least a part of the movement trajectory of the opening of the first hole, the second groove G2 includes at least a part of the movement trajectory of the opening of the second hole, and the first groove G1 and the second groove G2 at least partially overlap in the radial direction.

Description

[Technical Field]

[0001] The present invention relates to a scroll compressor and the like. [Background technology]

[0002] As a technique for keeping the thrust load (axial force) from one side of the fixed scroll and the other side of the orbiting scroll within an appropriate range in a scroll compressor, for example, the technique described in Patent Document 1 is known. That is, Patent Document 1 describes the provision of an oil groove formed to extend in the circumferential direction of the sliding surface of the fixed scroll, through which lubricating oil flows. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Laid-Open No. 2016-17484 Summary of the Invention [Problem to be solved by the invention]

[0004] For example, in order to reduce the sliding loss between the fixed scroll and the orbiting scroll during low load periods, which has a significant impact on year-round energy consumption efficiency, the force pushing the orbiting scroll toward the fixed scroll tends to be set to a small value. In the technology described in Patent Document 1, for example, when the scroll compressor is operated at a low compression ratio, high-pressure lubricating oil is introduced into the oil groove of the fixed scroll, which can cause an excessively large force pushing down on the orbiting scroll. As a result, the orbiting scroll may oscillate, leading to reduced efficiency and reduced reliability.

[0005] Therefore, an object of the present invention is to provide a highly efficient and reliable scroll compressor or the like. [Means for solving the problem]

[0006] In order to solve the above-mentioned problems, a scroll compressor according to the present invention comprises a sealed container, an electric motor having a stator and a rotor and housed in the sealed container, a shaft having an oil supply passage through which lubricating oil flows and rotating integrally with the rotor, a fixed scroll having a spiral fixed wrap, an orbiting scroll having a spiral orbiting wrap and a compression chamber formed between the fixed wrap and the orbiting wrap, and a frame having an insertion hole for the shaft and supporting the fixed scroll, and a back pressure chamber is provided between the orbiting scroll and the frame. The end plate surface of the fixed scroll is provided with an annular back pressure groove communicating with the back pressure chamber, and first and second grooves are provided radially inside the back pressure groove, the orbiting scroll is provided with a first hole and a second hole that guide lubricating oil from the oil supply passage to the end plate surface side of the fixed scroll, the first groove includes at least a part of a movement locus of an opening of the first hole, the second groove includes at least a part of a movement locus of an opening of the second hole, and the first groove and the second groove at least partially overlap in the radial direction. Other details will be described in the embodiments. [Effects of the Invention]

[0007] According to the present invention, a highly efficient and reliable scroll compressor or the like can be provided. [Brief explanation of the drawings]

[0008] [Figure 1] 1 is a vertical cross-sectional view of a scroll compressor according to a first embodiment. [Figure 2] 1 is a vertical cross-sectional view of an orbiting scroll included in a scroll compressor according to a first embodiment. FIG. [Figure 3] FIG. 2 is a perspective view of an orbiting scroll included in the scroll compressor according to the first embodiment. [Figure 4] FIG. 2 is a bottom view of a fixed scroll included in the scroll compressor according to the first embodiment. [Figure 5]5 is an explanatory diagram showing a movement locus of the opening of the first hole and a movement locus of the opening of the second hole in the scroll compressor according to the first embodiment, with a region K1 in FIG. 4 partially enlarged. FIG. [Figure 6] FIG. 10 is a bottom view of a fixed scroll included in the scroll compressor according to the second embodiment. [Figure 7] 7 is an explanatory diagram showing a movement locus of the opening of the first hole and a movement locus of the opening of the second hole in a scroll compressor according to a second embodiment, with a region K2 in FIG. 6 partially enlarged. FIG. [Figure 8] FIG. 10 is a bottom view of a fixed scroll included in the scroll compressor according to the third embodiment. [Figure 9] 9 is an explanatory diagram showing a movement locus of the opening of the first hole and a movement locus of the opening of the second hole in the scroll compressor according to the third embodiment, with a region K3 in FIG. 8 partially enlarged. [Figure 10] FIG. 10 is a configuration diagram including a refrigerant circuit of an air conditioner according to a fourth embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0009] First Embodiment <Scroll compressor configuration> FIG. 1 is a vertical cross-sectional view of a scroll compressor 100 according to a first embodiment. The scroll compressor 100 is a device that compresses a gaseous refrigerant. As shown in Fig. 1, the scroll compressor 100 includes a sealed container 1, a compression mechanism 2, a crankshaft 3, an electric motor 4, a main bearing 5, and an orbiting bearing 6. In addition to the above-described components, the scroll compressor 100 also includes an Oldham ring 7, balance weights 8a and 8b, and a subframe 9.

[0010] The sealed container 1 is a shell-shaped container that houses the compression mechanism 2, crankshaft 3, electric motor 4, etc., and is substantially sealed. Lubricating oil for lubricating the compression mechanism 2 and each bearing is sealed in the sealed container 1, and is stored as an oil reservoir R1 at the bottom of the sealed container 1. The sealed container 1 includes a cylindrical chamber 1a, a lid chamber 1b that closes the upper side of the cylindrical chamber 1a, and a bottom chamber 1c that closes the lower side of the cylindrical chamber 1a.

[0011] A suction pipe P1 is inserted into and fixed to the cover chamber 1b of the sealed container 1. The suction pipe P1 is a pipe that guides the refrigerant to the suction port J1 of the compression mechanism 2. Furthermore, a discharge pipe P2 is inserted into and fixed to the cylindrical chamber 1a of the sealed container 1. The discharge pipe P2 is a pipe that guides the refrigerant compressed by the compression mechanism 2 to the outside of the scroll compressor 100.

[0012] The compression mechanism 2 is a mechanism that compresses gaseous refrigerant as the crankshaft 3 rotates. The compression mechanism 2 includes a fixed scroll 21, an orbiting scroll 22, and a frame 23, and is disposed in the upper space within the sealed container 1.

[0013] The fixed scroll 21 is a member that forms a compression chamber S1 together with the orbiting scroll 22. The fixed scroll 21 is installed on the upper side of a frame 23 and fastened to the frame 23 with bolts (not shown). As shown in FIG. 1, the fixed scroll 21 includes a base plate 21a and a fixed wrap 21b.

[0014] The base plate 21a is a thick member having a circular shape in a plan view. To ensure an area S2 (the bottom surface of the fixed wrap 21b) where the orbiting wrap 22b orbits relative to the fixed wrap 21b, the area between the inner and outer lines of the fixed wrap 21b is recessed upward by a predetermined amount in a bottom view. The base plate 21a is also provided with a suction port J1 through which the refrigerant is introduced via a suction pipe P1.

[0015] The fixed wrap 21b has a spiral shape (see also FIG. 4) and extends downward from the base plate 21a in the aforementioned region S2. The lower surface of the base plate 21a (the lower surface of the radially outer portion of region S2) and the tooth tip of the fixed wrap 21b are substantially flush with each other. The lower surface of the base plate 21a is referred to as the end plate surface 21f (see also FIG. 4) of the fixed scroll 21. This end plate surface 21f is provided with an annular back pressure groove G3 (see also FIG. 4), as well as arc-shaped first groove G1 (see also FIG. 4) and second groove G2 (see also FIG. 4), the details of which will be described later.

[0016] The orbiting scroll 22 is a member that forms a compression chamber S1 between itself and the fixed scroll 21 by its movement (orbiting), and is provided between the fixed scroll 21 and the frame 23. The orbiting scroll 22 includes a disk-shaped end plate 22a, a spiral orbiting wrap 22b (see also FIG. 3) that stands on the end plate 22a, and a cylindrical boss portion 22c that is fitted onto the eccentric portion 3b of the crankshaft 3. As shown in FIG. 1, the orbiting wrap 22b extends above the end plate 22a, while the boss portion 22c extends below the end plate 22a.

[0017] The orbiting wrap 22b is a member that forms the compression chamber S1 together with the fixed wrap 21b. That is, the spiral-shaped fixed wrap 21b and the spiral-shaped orbiting wrap 22b mesh together to form multiple compression chambers S1 between the fixed wrap 21b and the orbiting wrap 22b. The compression chambers S1 are spaces that compress gaseous refrigerant and are formed on the outer and inner line sides of the orbiting wrap 22b. A discharge port J2 is provided near the center of the base plate 21a of the fixed scroll 21. The discharge port J2 is an opening that guides the refrigerant compressed in the compression chamber S1 to the space S3 above the compression mechanism 2.

[0018] The frame 23 is a member that supports the fixed scroll 21. The frame 23 has a roughly rotationally symmetric shape and is fixed by welding or the like to the inner peripheral wall of the cylindrical chamber 1a of the sealed container 1. The frame 23 is provided with an insertion hole H1 through which the crankshaft 3 is inserted.

[0019] A back pressure chamber S4 is provided between the orbiting scroll 22 and the frame 23. The back pressure chamber S4 is a space on the back side of the orbiting scroll 22 (the side where the boss portion 22c extends from the end plate 22a). In other words, the space between the orbiting scroll 22 and the frame 23 is the back pressure chamber S4.

[0020] When the gaseous refrigerant is compressed as the volume of the compression chamber S1 decreases, a downward force is generated that tries to separate the orbiting scroll 22 from the fixed scroll 21. If the orbiting scroll 22 were to separate from the fixed scroll 21, the tooth tips of the fixed wrap 21b would separate from the orbiting scroll 22, and the tooth tips of the orbiting wrap 22b would separate from the fixed scroll 21, causing refrigerant to leak from the compression chamber S1, resulting in a decrease in the efficiency of the scroll compressor 100.

[0021] Therefore, in order to prevent the orbiting scroll 22 from being pulled away from the fixed scroll 21, a space (not shown) having a pressure substantially equal to the discharge pressure is provided near the center of the back side of the orbiting scroll 22 (radially inside the boss portion 22c), and the back pressure chamber S4 is also provided. The pressure in the back pressure chamber S4 is normally set to a predetermined intermediate pressure between the suction pressure and discharge pressure of the scroll compressor 100. This generates an upward force that presses the orbiting scroll 22 against the fixed scroll 21 to an appropriate degree.

[0022] The term "back pressure" in the back pressure chamber S4 does not particularly limit the pressure in the back pressure chamber S4. The pressure in the back pressure chamber S4 is often between the suction pressure and the discharge pressure, but in some cases, it may temporarily become approximately equal to the discharge pressure.

[0023] The crankshaft 3 (shaft) shown in Fig. 1 is a shaft that rotates integrally with the rotor 4b of the electric motor 4 and extends in the vertical direction. As shown in Fig. 1, the crankshaft 3 includes a main shaft portion 3a, an eccentric portion 3b extending upward from the main shaft portion 3a, and an oil supply piece 3c installed at the lower end of the main shaft portion 3a. The main shaft portion 3a is fixed coaxially to the rotor 4b of the electric motor 4 and rotates integrally with the rotor 4b. The eccentric portion 3b is a shaft that rotates eccentrically with respect to the main shaft portion 3a, and as described above, is fitted into the boss portion 22c of the orbiting scroll 22. The eccentric rotation of the eccentric portion 3b causes the orbiting scroll 22 to orbit.

[0024] The oil supply piece 3c is a part that draws up lubricating oil from the oil reservoir R1 in the sealed container 1, and is installed at the lower end of the main shaft portion 3a. Note that a positive displacement pump, a centrifugal pump, or the like may be installed in the oil supply piece 3c. The crankshaft 3 also has an oil supply passage 3d through which the lubricating oil flows. The lubricating oil stored in the oil reservoir R1 in the sealed container 1 rises via the oil supply passage 3d. Note that the oil supply passage 3d branches in a predetermined manner so that the lubricating oil can also be supplied to the main bearing 5, the slewing bearing 6, and the like, which will be described next.

[0025] The electric motor 4 is a drive source that rotates the crankshaft 3 and is installed between the frame 23 and the subframe 9. As shown in FIG. 1, the electric motor 4 includes a stator 4a and a rotor 4b. The stator 4a is fixed to the inner peripheral wall of the cylindrical chamber 1a. The rotor 4b is rotatably disposed radially inside the stator 4a. The crankshaft 3 is fixed to the rotor 4b by press fitting or the like so that it is coaxial with the central axis Z1 of the rotor 4b.

[0026] The main bearing 5 rotatably supports the upper part of the main shaft portion 3a relative to the frame 23, and is provided on the peripheral wall surface of a hole (reference number not shown) in the frame 23. The orbiting bearing 6 rotatably supports the eccentric portion 3b relative to the boss portion 22c of the orbiting scroll 22, and is provided on the inner peripheral wall of the boss portion 22c.

[0027] The Oldham ring 7 is a ring-shaped member that receives the eccentric rotation of the eccentric portion 3b and orbits the orbiting scroll 22 without rotating on its axis. The Oldham ring 7 is attached to a groove (not shown) provided on the underside of the orbiting scroll 22 and a groove (not shown) provided in the frame 23.

[0028] The balance weights 8a and 8b are members for suppressing vibration of the scroll compressor 100. In the example of Fig. 1, one balance weight 8a is installed above the rotor 4b in the main shaft portion 3a, and the other balance weight 8b is installed on the underside of the rotor 4b. The subframe 9 is a member that rotatably supports the lower part of the main shaft portion 3a. As shown in FIG. 1, the subframe 9 is fixed to the sealed container 1 while being disposed below the electric motor 4. The subframe 9 is provided with a hole (reference number not shown) through which the crankshaft 3 is inserted. In addition, a sub-bearing 9a is provided on the peripheral wall surface of the hole in the subframe 9.

[0029] When the crankshaft 3 is rotated by the drive of the electric motor 4, the orbiting scroll 22 orbits accordingly. As a result, the compression chambers S1 formed one after another shrink, and the gaseous refrigerant is compressed. The compressed refrigerant is discharged into the space S3 above the compression mechanism 2 through the discharge port J2 of the fixed scroll 21. The refrigerant discharged into the space S3 in this manner is guided to the motor chamber S5 through a flow path (not shown) between the compression mechanism 2 and the sealed container 1, and further discharged to the outside through the discharge pipe P2.

[0030] Furthermore, the lubricating oil stored in the oil reservoir R1 at the bottom of the sealed container 1 rises through the oil supply passage 3d of the crankshaft 3 and lubricates the sub-bearing 9a, main bearing 5, orbiting bearing 6, etc. Furthermore, the lubricating oil that reaches an opening (reference number not shown) at the upper end of the oil supply passage 3d is guided to a communication hole H2 (see also FIG. 2) of the orbiting scroll 22, which will be described later. Next, the detailed configurations of the fixed scroll 21 and the orbiting scroll 22 will be described, and the flow of the lubricating oil will also be described.

[0031] FIG. 2 is a vertical cross-sectional view of an orbiting scroll 22 provided in the scroll compressor. 2, one communication hole H2 is provided in the horizontal direction (a direction parallel to the upper and lower surfaces of the end plate 22a) in the end plate 22a of the orbiting scroll 22. In the example of FIG. 2, the communication hole H2 is provided in the radial direction of the disk-shaped end plate 22a, but the communication hole H2 may be provided in a horizontal direction different from the radial direction.

[0032] The communication hole H2 is a flow path that guides high-pressure lubricating oil flowing through the oil supply passage 3d (see FIG. 1) of the crankshaft 3 to the fixed scroll 21 (see FIG. 1). This communication hole H2 is formed, for example, by performing a predetermined cutting process from the peripheral wall surface of the end plate 22a to the radially inward direction. The seal plug N1 shown in FIG. 2 is a member that seals the outer peripheral end of the communication hole H2. As shown in FIG. 2, the upstream side (radially inner side) of the communication hole H2 communicates with the space radially inner of the boss portion 22c via a relatively short vertical flow path H3. Furthermore, the downstream side (radially outer side) of the communication hole H2 communicates with the first hole H4 and also with the second hole H5.

[0033] The first hole H4 is a flow path that guides high-pressure lubricating oil to the arc-shaped first groove G1 (see FIG. 4) and is provided in the vertical direction. The second hole H5 is a flow path that guides high-pressure lubricating oil to the arc-shaped second groove G2 (see FIG. 4) and is provided in the vertical direction. A portion of the lubricating oil flowing out from the oil supply passage 3d (see FIG. 1) of the crankshaft 3 is guided to the first groove G1 (see FIG. 4) via the flow path H3, the communication hole H2, and the first hole H4 shown in FIG. 2, in that order, and is also guided to the second groove G2 (see FIG. 4) via the second hole H5. In other words, the communication hole H2 communicates with the oil supply passage 3d and with both the first hole H4 and the second hole H5. The second hole H5 is provided radially outward of the first hole H4.

[0034] FIG. 3 is a perspective view of the orbiting scroll 22 provided in the scroll compressor. As described above, the orbiting scroll 22 includes the disk-shaped end plate 22a, the spiral orbiting wrap 22b, and the cylindrical boss portion 22c. On the peripheral wall surface of the end plate 22a of the orbiting scroll 22, seal plugs N1 are provided at locations corresponding to the first hole H4 (see FIG. 2) and the second hole H5 (see FIG. 2) to close the outer peripheral end of the communication hole H2. Furthermore, on the upper surface of the end plate 22a, an opening J4 of the first hole H4 and an opening J5 of the second hole H5 are provided. As shown in FIG. 3, the opening J5 of the second hole H5 is located radially outward of the opening J4 of the first hole H4. As the orbiting scroll 22 orbits, the opening J4 of the first hole H4 and the opening J5 of the second hole H5 move in a predetermined manner.

[0035] As described above, the back pressure in the back pressure chamber S4 (see FIG. 1) exerts a force pressing the orbiting scroll 22 against the fixed scroll 21. However, if the force pressing the orbiting scroll 22 against the fixed scroll 21 becomes too large, for example, under operating conditions with a high compression ratio, this may increase friction loss or cause seizure at the sliding surfaces between the fixed scroll 21 and the orbiting scroll 22. Therefore, the annular back pressure groove G3 (see FIG. 4) and the arc-shaped first groove G1 (see FIG. 4), which will be described below, are provided on the end plate surface 21f (see FIG. 4) of the fixed scroll 21, outside the fixed wrap 21b. In addition, as will be described in detail later, the arc-shaped second groove G2 (see FIG. 4) is provided on the end plate surface 21f (see FIG. 4) of the fixed scroll 21 in preparation for the occurrence of rocking of the orbiting scroll 22.

[0036] FIG. 4 is a bottom view of the fixed scroll 21 provided in the scroll compressor. As described above, the fixed scroll 21 has a configuration in which the spiral fixed wrap 21b is provided on the base plate 21a. As shown in Fig. 4, an annular back pressure groove G3 is provided near the periphery of the end plate surface 21f of the fixed scroll 21. This back pressure groove G3 is a groove that communicates with the back pressure chamber S4 (see Fig. 1) between the orbiting scroll 22 (see Fig. 1) and the frame 23 (see Fig. 1). In the example of Fig. 4, the back pressure groove G3 is formed as a circular groove with the vicinity of the center of the circular end plate surface 21f as the base (center of the circle).

[0037] During orbiting of the orbiting scroll 22 (see FIG. 1), lubricating oil at a pressure substantially equal to the pressure in the back pressure chamber S4 is introduced into the back pressure groove G3. More specifically, the lubricating oil flows from the back pressure chamber S4 into the gap between the annular back pressure groove G3 and the upper surface of the end plate 22a (see FIG. 1) of the orbiting scroll 22. This prevents the force with which the orbiting scroll 22 pushes up the fixed scroll 21 from becoming excessive, and the lubricating oil in the back pressure groove G3 acts as a seal, preventing the compressed refrigerant from flowing in from the space S3 (see FIG. 1).

[0038] As shown in Fig. 4, a first groove G1 and a second groove G2 are provided in the end plate surface 21f of the fixed scroll 21. These first groove G1 and second groove G2 are provided radially inside the annular back pressure groove G3 and are formed, for example, in a predetermined arc shape with the vicinity of the center of the back pressure groove G3 as a reference (center of the arc). Meanwhile, as described above, the orbiting scroll 22 (see Fig. 2) is provided with a first hole H4 (see Fig. 2) and a second hole H5 (see Fig. 2) that guide lubricating oil from the oil supply passage 3d (see Fig. 1) of the crankshaft 3 (shaft) to the end plate surface 21f side of the fixed scroll 21.

[0039] The first groove G1 shown in FIG. 4 is a groove that intermittently communicates with the first hole H4 (see FIG. 2) of the orbiting scroll 22 (see FIG. 1) as the orbiting scroll 22 moves (orbits). The first groove G1 is provided so as to include a region (also referred to as an offset load region) where the end plate 22a (see FIG. 1) of the orbiting scroll 22 most strongly contacts the end plate surface 21f of the fixed scroll 21 when, for example, a force (a resultant force of centrifugal force or gas load) acts to tilt the orbiting scroll 22 relative to the end plate surface 21f of the fixed scroll 21. Specifically, the first groove G1 is formed in an arc shape with a central angle of 90° or more and 180° or less, with the vicinity of the center of the circular end plate surface 21f as the reference (center of the circle). The offset load region may be located near the center of the first groove G1 in the circumferential direction.

[0040] As the orbiting scroll 22 (see FIG. 1) moves, the first groove G1 intermittently communicates with the first hole H4 (see FIG. 2), and high-pressure lubricating oil substantially equal to the discharge pressure is introduced into the first groove G1. This allows the high-pressure lubricating oil to enter an area (near the first groove G1) where the end plate 22a (see FIG. 1) of the orbiting scroll 22 is likely to strongly come into contact with the end plate surface 21f (see FIG. 1) of the fixed scroll 21. As a result, a force acts in the first groove G1 to separate the orbiting scroll 22 from the fixed scroll 21, preventing the thrust load (pressing force) from being excessively large from one side of the orbiting scroll 22 and the fixed scroll 21 to the other side.

[0041] 4 is a groove that intermittently communicates with the second hole H5 (see FIG. 2) of the orbiting scroll 22 (see FIG. 1) as the orbiting scroll 22 moves (orbits). As described above, by providing the first groove G1 and the back pressure groove G3 on the end plate surface 21f of the fixed scroll 21, the thrust load from one side of the fixed scroll 21 to the other side of the orbiting scroll 22 is kept within an appropriate range. However, it may be difficult to prevent the orbiting scroll 22 from swinging under all operating conditions.

[0042] Therefore, in the first embodiment, when the orbiting scroll 22 swings, the high-pressure lubricating oil in the second groove G2 flows into the back pressure chamber S4 (see FIG. 1) via the annular back pressure groove G3. In this way, the high-pressure lubricating oil equal to the discharge pressure flows into the back pressure chamber S4, temporarily increasing the pressure in the back pressure chamber S4. As a result, the force pushing the orbiting scroll 22 up against the fixed scroll 21 increases, thereby suppressing the swing of the orbiting scroll 22.

[0043] In the example of FIG. 4, an arc-shaped second groove G2, with the vicinity of the center of the base plate 21a of the fixed scroll 21 as a reference (center of the arc), is provided between the first groove G1 and the back pressure groove G3. In other words, the distance L2a between the second groove G2 and the back pressure groove G3 is shorter than the distance L1a between the first groove G1 and the back pressure groove G3. In this way, one of the main features of the first embodiment is that the second groove G2, which is separate from the first groove G1, is provided radially outward of the first groove G1. Note that the "distance" between the second groove G2 and the back pressure groove G3 refers to the length of the line segment connecting the second groove G2 and the back pressure groove G3 at the shortest distance (the same applies to other distances such as L1a).

[0044] As described above, because the distance between the second groove G2 and the back pressure groove G3 is relatively short, when the orbiting scroll 22 swings and tilts, most of the high-pressure lubricating oil present in the second groove G2 flows into the back pressure groove G3. As described above, the pressure of the lubricating oil in the second groove G2 is approximately equal to the discharge pressure and is higher than the pressure of the lubricating oil in the back pressure groove G3. When the high-pressure lubricating oil flows into the back pressure groove G3 in this way, the pressure in the back pressure chamber S4 (see FIG. 1) temporarily increases, thereby suppressing the swing of the orbiting scroll 22.

[0045] Furthermore, the distance L1b between the inner edge 21fa of the end plate surface 21f of the fixed scroll 21 and the first groove G1 is shorter than the distance L2b between the inner edge 21fa of the end plate surface 21f and the second groove G2. Because the distance between the inner edge 21fa of the end plate surface 21f and the first groove G1 is relatively short, high-pressure lubricating oil present in the first groove G1 is appropriately supplied to the compression chamber S1 (see FIG. 1) through the small gap between the end plate surface 21f of the fixed scroll 21 and the end plate 22a of the orbiting scroll 22 (see FIG. 1). This lubricates the fixed wrap 21b (see FIG. 1) and the orbiting wrap 22b (see FIG. 1), thereby suppressing wear and seizure. Furthermore, the high-pressure lubricating oil present in the arc-shaped first groove G1 also functions as a seal between the fixed scroll 21 and the orbiting scroll 22, thereby improving the efficiency of the scroll compressor 100. Incidentally, during the compression of the refrigerant, the pressure in the compression chamber S1 is lower than the discharge pressure (pressure of the lubricating oil in the first groove G1) and is even lower than the pressure in the back pressure chamber S4.

[0046] Next, the circumferential length of the second groove G2 will be described. As shown in FIG. 4, it is preferable that the circumferential length of the arc-shaped second groove G2 is shorter than the circumferential length of the arc-shaped first groove G1. This configuration prevents excessive high-pressure lubricating oil from flowing into the second groove G2, thereby appropriately suppressing the force that tries to separate the orbiting scroll 22 from the fixed scroll 21. It is also more preferable that the circumferential length of the arc-shaped second groove G2 is shorter than half the circumferential length of the arc-shaped first groove G1. This configuration appropriately suppresses the amount of high-pressure lubricating oil present in the second groove G2.

[0047] Furthermore, the central angle θ1 of the arc-shaped second groove G2 (the central angle of an imaginary sector with the center of the base plate 21a as the reference) is preferably 10° or more and 30° or less. With this configuration, the volume of the arc-shaped gap between the second groove G2 and the end plate 22a (see FIG. 1) of the orbiting scroll 22 can be appropriately reduced. Therefore, it is possible to prevent the force that tries to separate the orbiting scroll 22 from the fixed scroll 21 from becoming excessive.

[0048] Furthermore, the first groove G1 and the second groove G2 at least partially overlap in the radial direction. In the example of Fig. 4, almost the entire area of ​​the second groove G2 overlaps with the first groove G1 in the radial direction. The reason for this configuration will be explained using the partially enlarged view of Fig. 5.

[0049] FIG. 5 is an explanatory diagram showing a partial enlargement of the region K1 in FIG. 4, illustrating the movement locus M4 of the opening J4 of the first hole and the movement locus M5 of the opening J5 of the second hole. In Figure 5, the movement trajectory M4 of the opening J4 of the first hole H4 (see Figure 2) provided on the upper surface of the orbiting scroll 22 is shown by a dotted line, and the movement trajectory M5 of the opening J5 of the second hole H5 (see Figure 2) is shown by a dashed line. As described above, high-pressure lubricating oil from the oil supply passage 3d (see FIG. 1) of the crankshaft 3 is intermittently supplied to the first groove G1 via the first hole H4 (see FIG. 2). Also, high-pressure lubricating oil from the oil supply passage 3d (see FIG. 1) of the crankshaft 3 is intermittently supplied to the second groove G2 via the second hole H5 (see FIG. 2).

[0050] In the example of FIG. 5, as the orbiting scroll 22 (see FIG. 2) orbits, the opening J4 of the first hole H4 (see FIG. 2) moves along a circular movement trajectory M4 and returns to its original position, causing the first hole H4 and the first groove G1 to communicate with each other twice. As a result, an appropriate amount of lubricating oil is supplied to the first groove G1 via the first hole H4. Similarly, as the opening J5 of the second hole H5 (see FIG. 2) moves along a circular movement trajectory M5 and returns to its original position, the second hole H5 and the second groove G2 communicate with each other twice. As a result, an appropriate amount of lubricating oil is supplied to the second groove G2 via the second hole H5.

[0051] The high-pressure lubricating oil supplied to the first groove G1 and the second groove G2 does not remain in these grooves but flows out through the small gap between the end plate surface 21f of the fixed scroll 21 and the end plate 22a of the orbiting scroll 22 (see FIG. 1). Therefore, as described above, lubricating oil is supplied twice per movement of each of the openings J4 and J5. Furthermore, by making the distance between the second groove G2 and the back pressure groove G3 relatively small, lubricating oil is more likely to be supplied from the second groove G2 to the back pressure chamber S4 (see FIG. 1) via the back pressure groove G3 even during normal operation. This ensures sufficient lubrication of the Oldham ring 7 and other components (see FIG. 1) provided in the back pressure chamber S4.

[0052] 5, the circumferential length of the arc-shaped second groove G2 is longer than the diameter of the circular movement locus M5 of the opening J5 of the second hole H5. The arc-shaped second groove G2 and the circular movement locus M5 of the opening J5 of the second hole H5 intersect at two locations. With this configuration, lubricating oil is supplied twice per movement of the opening J5, so a sufficient amount of lubricating oil can be supplied to the second groove G2 of the fixed scroll 21 compared to supplying lubricating oil only once.

[0053] As described above, the second groove G2 overlaps the first groove G1 in the radial direction. This allows the first hole H4, which intermittently communicates with the first groove G1, and the second hole H5, which intermittently communicates with the second groove G2, to be aligned in the radial direction (see also FIGS. 2 and 3). As a result, only one communication hole H2 (see FIG. 2) is required to guide lubricating oil from the oil supply passage 3d (see FIG. 1) of the crankshaft 3 to each of the first hole H4 (see FIG. 2) and the second hole H5 (see FIG. 2). This reduces the time and effort required to form the communication hole H2 in the orbiting scroll 22 by cutting or other processes.

[0054] Furthermore, because the second groove G2 overlaps the first groove G1 in the radial direction, the high-pressure lubricating oil present in one of the first groove G1 and the second groove G2 acts like a wall against the high-pressure lubricating oil present in the other. As a result, the high-pressure lubricating oil in the first groove G1 is more likely to be supplied to the compression chamber S1 (see FIG. 1) than to the backpressure groove G3. On the other hand, the high-pressure lubricating oil in the second groove G2 is more likely to be supplied to the backpressure groove G3 than to the compression chamber S1 (see FIG. 1). 4 shows an example in which the second groove G2 is provided near one end of the first groove G1 in the circumferential direction (the end on the suction port J1 side), but this is not limiting. For example, the second groove G2 may be provided near the end on the opposite side of the first groove G1 in the circumferential direction, or the second groove G2 may be provided near the center of the first groove G1 in the circumferential direction. In either case, when the orbiting scroll 22 swings and tilts, high-pressure lubricating oil is supplied from the second groove G2 to the backpressure groove G3.

[0055] <Effects> According to the first embodiment, high-pressure lubricating oil is supplied to the arc-shaped first groove G1 (see FIG. 4) provided in the end plate surface 21f of the fixed scroll 21. This makes it possible to prevent the end plate 22a of the orbiting scroll 22 from strongly hitting the fixed scroll 21 near the first groove G1. Furthermore, the distance L2a (see FIG. 4) between the second groove G2 and the back pressure groove G3 is shorter than the distance L1a (see FIG. 4) between the first groove G1 and the back pressure groove G3. This allows high-pressure lubricating oil to be supplied from the second groove G2 to the back pressure chamber S4 (see FIG. 1) via the back pressure groove G3 even when the orbiting scroll 22 swings and tilts. As a result, the pressure in the back pressure chamber S4 temporarily increases, quickly suppressing the swing of the orbiting scroll 22 and allowing the scroll compressor 100 to return to an appropriate operating state. In other words, it is possible to prevent a decrease in efficiency due to the orbiting scroll 22 overturning. This allows the scroll compressor 100 to achieve both reliable operation and improved performance (high efficiency) over a wide range of operating conditions.

[0056] Furthermore, because the first groove G1 and the second groove G2 at least partially overlap in the radial direction, it is possible to provide a communication hole H2 (see FIG. 2) that communicates with both the first hole H4 and the second hole H5. That is, only one communication hole H2 (see FIG. 2) is required to guide high-pressure lubricating oil from the oil supply passage 3d of the crankshaft 3 to the first hole H4 and the second hole H5. This reduces the number of steps and time required to form the communication hole H2 by cutting or the like, thereby reducing the manufacturing cost of the scroll compressor 100.

[0057] Second Embodiment The second embodiment differs from the first embodiment in that a recess E2 (see FIG. 6) that is always in communication with the opening J5 (see FIG. 2) of the second hole H5 (see FIG. 2) is provided in the end plate surface 21f of the fixed scroll 21A (see FIG. 6). Note that the other configurations (such as the overall configuration of the scroll compressor 100: see FIG. 1) are the same as those of the first embodiment. Therefore, only the parts that differ from the first embodiment will be described, and a description of the overlapping parts will be omitted.

[0058] FIG. 6 is a bottom view of a fixed scroll 21A included in the scroll compressor according to the second embodiment. As shown in Fig. 6, a recess E2 communicating with the second groove GA2 is provided on the end plate surface 21f of the fixed scroll 21A radially outward of the first groove G1. The circumferential length of the second groove GA2 is shorter than that in the first embodiment (see Fig. 4). However, the circumferential length of the entire region of the second groove GA2 and the recess E2 is the same as the circumferential length of the second groove G2 in the first embodiment.

[0059] In the example of Fig. 6, a recess E2 is provided on one end side (the end side closer to the suction port J1) of the arc-shaped second groove GA2. This recess E2 is a portion that is constantly in communication with the second hole H5 (see Fig. 2) of the orbiting scroll 22 (see Fig. 2). The recess E2 is recessed upward from the end plate surface 21f and has a circular shape when viewed from below.

[0060] The circumferential position of the recess E2 is not limited to the example shown in FIG. 6. As will be explained next, as long as the circular movement locus M5 (see FIG. 7) of the opening J5 of the second hole H5 (see FIG. 2) is included in the region S6 (see FIG. 7) of the recess E2, the recess E2 may be provided on the other end side of the second groove GA2, or may be provided near the center of the second groove GA2 in the circumferential direction. In addition to the second groove GA2, the circular recess E2 also overlaps with the first groove G1 in the radial direction. The reason for this arrangement will be explained using FIG. 7.

[0061] FIG. 7 is an explanatory diagram showing a partial enlargement of the region K2 in FIG. 6, illustrating the movement locus M4 of the opening J4 of the first hole and the movement locus M5 of the opening J5 of the second hole. As shown in Fig. 7, on the end plate surface 21f of the fixed scroll 21A, the movement locus M5 of the opening J5 of the second hole H5 (see Fig. 2) is included in the region S6 of the recessed portion E2. Note that in the example of Fig. 7, the movement locus M4 of the opening J4 of the first hole H4 (see Fig. 2) partially overlaps with the first groove G1, but is not included in the region S6 of the recessed portion E2.

[0062] According to this configuration, when the orbiting scroll 22 (see FIG. 2) is moving (orbiting), the second hole H5 (see FIG. 2) is constantly in communication with the recessed portion E2 and the second groove GA2, which allows the amount of high-pressure lubricating oil supplied to the recessed portion E2 and the second groove GA2 per unit time to be greater than in the first embodiment.

[0063] <Effects> According to the second embodiment, the second hole H5 is always in communication with the recess E2 and the second groove GA2 while the scroll compressor is operating. Therefore, when the orbiting scroll 22 (see FIG. 1) swings and tilts, the amount of high-pressure lubricating oil flowing into the back pressure chamber S4 (see FIG. 1) via the back pressure groove G3 (see FIG. 6) is increased compared to the first embodiment, and the orbiting scroll 22 (see FIG. 1) can be quickly returned to an appropriate state.

[0064] Third Embodiment The third embodiment differs from the second embodiment in that the recess E3 (see FIG. 9) provided in the end plate surface 21f of the fixed scroll 21B (see FIG. 8) intermittently communicates with the opening J5 (see FIG. 9) of the second hole H5 (see FIG. 2) and also intermittently communicates with the opening J4 (see FIG. 9) of the first hole H4 (see FIG. 2). Note that the other configurations are the same as those of the second embodiment. Therefore, only the parts that are different from the second embodiment will be described, and a description of the overlapping parts will be omitted.

[0065] FIG. 8 is a bottom view of a fixed scroll 21B included in the scroll compressor according to the third embodiment. As shown in Fig. 8, a recess E3 communicating with the second groove GB2 is provided on the end plate surface 21f of the fixed scroll 21B radially outward of the fixed wrap 21b. The distance between the recess E3 and the first groove G1 is shorter than in the second embodiment (see Fig. 6). The diameter of the circular recess E3 is also shorter than in the second embodiment (see Fig. 6). In addition to the second groove GB2, the circular recess E3 also overlaps with the first groove G1 in the radial direction.

[0066] FIG. 9 is an explanatory diagram showing a partial enlargement of the region K3 in FIG. 8, illustrating the movement locus M4 of the opening J4 of the first hole and the movement locus M5 of the opening J5 of the second hole. As shown in Fig. 9, on the end plate surface 21f of the fixed scroll 21B, a portion of the movement locus M5 of the opening J5 of the second hole H5 (see Fig. 2) is included in the region S7 of the recess E3. Meanwhile, the remainder of the movement locus M5 of the opening J5 of the second hole H5 (see Fig. 2) is outside the region S7 of the recess E3. When it is difficult to achieve constant communication as in the second embodiment (a configuration in which the opening J5 is constantly in communication with the recess E2: see Fig. 7) due to space limitations, a configuration as shown in Fig. 9 can also be used.

[0067] Furthermore, on the end plate surface 21f of the fixed scroll 21B, a portion of the movement locus M4 of the opening J4 of the first hole H4 (see FIG. 2) is also included in the region S7 of the recessed portion E3. With this configuration, high-pressure lubricating oil is intermittently supplied to the recessed portion E3 via the second hole H5 (see FIG. 2), and high-pressure lubricating oil is intermittently supplied to the recessed portion E3 via the first hole H4 (see FIG. 2). Therefore, even with a configuration in which the movement locus M5 of the opening J5 of the second hole H5 (see FIG. 2) is partially outside the region S7 of the recessed portion E3, a sufficient amount of high-pressure lubricating oil can be supplied per unit time to the recessed portion E3 and the second groove GB2.

[0068] <Effects> According to the third embodiment, while the scroll compressor is operating, the second hole H5 (see FIG. 2) intermittently communicates with the recess E3 (see FIG. 9), and the first hole H4 (see FIG. 2) also intermittently communicates with the recess E3. Therefore, when the orbiting scroll 22 (see FIG. 1) swings and tilts, the amount of high-pressure lubricating oil flowing into the back pressure chamber S4 (see FIG. 1) via the back pressure groove G3 (see FIG. 8) is increased compared to the first embodiment, and the orbiting scroll 22 (see FIG. 1) can be quickly returned to an appropriate state.

[0069] Fourth Embodiment In the fourth embodiment, an air conditioner W1 (refrigeration cycle device: see FIG. 10) including the scroll compressor 100 (see FIG. 1) described in the first embodiment will be described.

[0070] FIG. 10 is a configuration diagram including a refrigerant circuit Q1 of an air conditioner W1 according to the fourth embodiment. The solid arrows in FIG. 10 indicate the flow of the refrigerant during heating operation. On the other hand, the dashed arrows in FIG. 10 indicate the flow of the refrigerant during cooling operation. The air conditioner W1 is a device that performs air conditioning such as cooling and heating. As shown in Fig. 10, the air conditioner W1 includes a scroll compressor 100, an outdoor heat exchanger 71, an outdoor fan 72, an expansion valve 73, a four-way valve 74, an indoor heat exchanger 75, and an indoor fan 76.

[0071] 10, the scroll compressor 100, the outdoor heat exchanger 71, the outdoor fan 72, the expansion valve 73, and the four-way valve 74 are provided in the outdoor unit U1, while the indoor heat exchanger 75 and the indoor fan 76 are provided in the indoor unit U2.

[0072] The scroll compressor 100 is a device that compresses a gaseous refrigerant, and has, for example, the same configuration as that of the first embodiment (see FIG. 1). The outdoor heat exchanger 71 is a heat exchanger in which heat is exchanged between a refrigerant flowing through its heat transfer tubes (not shown) and outside air sent in from an outdoor fan 72 . The outdoor fan 72 is a fan that sends outside air to the outdoor heat exchanger 71. The outdoor fan 72 includes an outdoor fan motor 72a that serves as a drive source, and is installed near the outdoor heat exchanger 71.

[0073] The indoor heat exchanger 75 is a heat exchanger in which heat is exchanged between the refrigerant flowing through its heat transfer pipes (not shown) and the indoor air (air in the air-conditioned room) sent in from the indoor fan 76. The indoor fan 76 is a fan that sends indoor air to the indoor heat exchanger 75. The indoor fan 76 is provided with an indoor fan motor 76a that serves as a drive source, and is installed near the indoor heat exchanger 75.

[0074] The expansion valve 73 is a valve that reduces the pressure of the refrigerant condensed in the "condenser" (one of the outdoor heat exchanger 71 and the indoor heat exchanger 75). The refrigerant reduced in pressure by the expansion valve 73 is introduced to the "evaporator" (the other of the outdoor heat exchanger 71 and the indoor heat exchanger 75).

[0075] The four-way valve 74 is a valve that switches the refrigerant flow path depending on the operation mode of the air conditioner W1. For example, during cooling operation (see the dashed arrow in FIG. 10), the refrigerant circulates in the refrigerant circuit Q1 sequentially through the scroll compressor 100, the outdoor heat exchanger 71 (condenser), the expansion valve 73, and the indoor heat exchanger 75 (evaporator). On the other hand, during heating operation (see the solid arrow in FIG. 10), the refrigerant circulates in the refrigerant circuit Q1 sequentially through the scroll compressor 100, the indoor heat exchanger 75 (condenser), the expansion valve 73, and the outdoor heat exchanger 71 (evaporator).

[0076] <Effects> According to the fourth embodiment, the air conditioner W1 is equipped with the scroll compressor 100, which has low manufacturing costs and high performance and reliability. This reduces the manufacturing costs of the air conditioner W1 as a whole and also improves its performance and reliability.

[0077] <<Variations>> Although the scroll compressor 100 and the air conditioner W1 according to the present invention have been described in the above in relation to the various embodiments, the present invention is not limited to these descriptions and various modifications can be made. For example, in each embodiment, the second groove G2 (see FIG. 4) overlaps with the first groove G1 (see FIG. 4) over substantially the entire area in the radial direction, but the present invention is not limited to this. That is, the first groove G1 and the second groove G2 may overlap with each other at least partially in the radial direction.

[0078] Furthermore, in each embodiment, a case has been described in which a portion of the movement locus M4 (see FIG. 5) of the opening J4 of the first hole H4 (see FIG. 2) is included in the first groove G1. However, this is not limiting. That is, the entire area of ​​the movement locus M4 (see FIG. 5) of the opening J4 of the first hole H4 (see FIG. 2) may be included in the first groove G1. In this case, a circular recess (not shown) communicating with the first hole H4 may be provided, and the entire area of ​​the movement locus M4 of the opening J4 of the first hole H4 (see FIG. 2) may be included in this recess. That is, the first groove G1 may include at least a portion of the movement locus M4 of the opening J4 of the first hole H4. Similarly, the second groove G2 may include at least a portion of the movement locus M5 of the opening J5 of the second hole H5 (see FIG. 2).

[0079] Furthermore, in each embodiment, the case where the number of second grooves G2 (see FIG. 4) is one has been described, but this is not limited thereto. For example, a plurality of second grooves G2 may be provided that are approximately equal in radial distance to the back pressure groove G3. In this case, a plurality of second holes H5 may be provided corresponding to the plurality of second grooves G2, and one second hole H5 may be configured to alternately communicate with the plurality of second grooves G2.

[0080] Furthermore, in the third embodiment, a configuration has been described in which a portion of the movement locus M5 (see FIG. 9) of the opening J5 of the second hole H5 (see FIG. 2) is included in the recess E3 (see FIG. 9), and a portion of the movement locus M4 (see FIG. 9) of the opening J4 of the first hole H4 (see FIG. 2) is included in the recess E3. However, this is not limiting. For example, the following configuration may be adopted without providing the recess E3. That is, the second groove G2 may include at least a portion of the movement locus M5 of the opening J5 of the second hole H5, and may also include at least a portion of the movement locus M4 of the opening J4 of the first hole H4. Even with this configuration, a sufficient amount of lubricating oil can be supplied to the second groove G2.

[0081] Furthermore, as described in the first embodiment, the first groove G1 (see FIG. 5) may be configured to include at least a portion of the movement trajectory M4 (see FIG. 5) of the opening J4 of the first hole H4 (see FIG. 2), but not include the movement trajectory M5 (see FIG. 5) of the opening J5 of the second hole H5 (see FIG. 2). Even with this configuration, when the orbiting scroll 22 swings and tilts, high-pressure lubricating oil is supplied from the second groove G2 to the back pressure chamber S4 (see FIG. 1) via the back pressure groove G3, thereby suppressing swing of the orbiting scroll 22 (see FIG. 1).

[0082] Furthermore, the respective embodiments can be combined as appropriate. For example, the second embodiment and the fourth embodiment may be combined to form the following configuration. That is, the air conditioner may be configured to include a scroll compressor provided with a recess E2 (see FIG. 7) that is always in communication with the opening J5 of the second hole H5 (see FIG. 2) (second embodiment), as well as an outdoor heat exchanger 71 (see FIG. 10), an expansion valve 73, an indoor heat exchanger 75, etc. (fourth embodiment). It is also possible to combine the third embodiment and the fourth embodiment.

[0083] The air conditioner W1 (see FIG. 10) described in the fourth embodiment can be applied to various types of air conditioners, such as room air conditioners, packaged air conditioners, and multi-air conditioners for buildings. The fourth embodiment describes the air conditioner W1 (refrigeration cycle device) equipped with the scroll compressor 100, but the present invention is not limited to this. For example, the fourth embodiment can also be applied to other "refrigeration cycle devices" such as freezers, hot water heaters, air-conditioning hot water heaters, chillers, and refrigerators.

[0084] In addition, in each embodiment, a case where a refrigerant is compressed by the scroll compressor 100 has been described, but this is not limitative. That is, each embodiment can also be applied to a case where a predetermined gas other than a refrigerant is compressed by the scroll compressor 100.

[0085] Furthermore, each embodiment has been described in detail to clearly explain the present invention, and is not necessarily limited to having all of the configurations described. Furthermore, part of the configuration of each embodiment can be appropriately added to, deleted from, or replaced with other configurations. Furthermore, the mechanisms and configurations described above are those that are considered necessary for the explanation, and do not necessarily represent all mechanisms and configurations of the product. [Explanation of symbols]

[0086] 1. Airtight container 2 Compression mechanism 21, 21A, 21B Fixed scroll 21a Base plate 21b fixed wrap 21f mirror surface 22 Rotating Scroll 22a Headboard 22b Circling Wrap 23 frames 3 Crankshaft (shaft) 4 Electric motor 4a stator 4b Rotor 71 Outdoor heat exchanger 73 Expansion valve 75 Indoor heat exchanger 100 Scroll Compressor E2,E3 recess G3 Back pressure groove G1 1st groove G2,GA2,GB2 2nd groove H1 insertion hole H2 communication hole H4 1st hole H5 2nd hole L1a distance (distance between the first groove and the back pressure groove) L2a distance (distance between the second groove and the back pressure groove) S1 compression chamber S4 Back pressure chamber J4 opening (first hole opening) J5 opening (first hole opening) M4 movement trajectory (movement trajectory of the first hole opening) M5 movement trajectory (movement trajectory of the opening of the second hole) W1 Air conditioner (refrigeration cycle device)

Claims

1. A sealed container and an electric motor having a stator and a rotor and housed in the sealed container; a shaft having an oil supply passage through which lubricating oil flows and rotating integrally with the rotor; a fixed scroll having a spiral-shaped fixed wrap; an orbiting scroll having a spiral orbiting wrap, wherein a compression chamber is formed between the fixed wrap and the orbiting wrap; a frame having an insertion hole for the shaft and supporting the fixed scroll, A back pressure chamber is provided between the orbiting scroll and the frame, an annular back pressure groove communicating with the back pressure chamber is provided in an end plate surface of the fixed scroll, and a first groove and a second groove are provided radially inward of the back pressure groove; The orbiting scroll is provided with a first hole and a second hole that guide the lubricating oil from the oil supply passage toward the end plate surface of the fixed scroll, the first groove includes at least a part of a movement locus of the opening of the first hole; the second groove includes at least a part of a movement locus of the opening of the second hole; The scroll compressor has the first groove and the second groove at least partially overlapping in the radial direction.

2. A sealed container and an electric motor having a stator and a rotor and housed in the sealed container; a shaft having an oil supply passage through which lubricating oil flows and rotating integrally with the rotor; a fixed scroll having a spiral-shaped fixed wrap; an orbiting scroll having a spiral orbiting wrap, wherein a compression chamber is formed between the fixed wrap and the orbiting wrap; a frame having an insertion hole for the shaft and supporting the fixed scroll, A back pressure chamber is provided between the orbiting scroll and the frame, an annular back pressure groove communicating with the back pressure chamber is provided in an end plate surface of the fixed scroll, and a first groove and a second groove are provided radially inward of the back pressure groove; The orbiting scroll is provided with a first hole and a second hole that guide the lubricating oil from the oil supply passage toward the end plate surface of the fixed scroll, the first groove includes at least a part of a movement locus of the opening of the first hole; the second groove includes at least a part of a movement locus of the opening of the second hole; a communication hole communicating with the oil supply passage and communicating with both the first hole and the second hole is provided in the orbiting scroll, a distance between the second groove and the back pressure groove being shorter than a distance between the first groove and the back pressure groove;

3. A refrigeration cycle device comprising: the scroll compressor according to claim 1 or 2; an outdoor heat exchanger; an expansion valve; and an indoor heat exchanger.

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