Scroll compressor and refrigeration cycle device

Abstract

To provide a scroll compressor etc. which achieves high efficiency.SOLUTION: A scroll compressor includes: a closed vessel; an electric motor; a crank shaft; a fixed scroll 21; and a revolving scroll 22. A revolving inner line side compression chamber C1a and a revolving outer line side compression chamber C1b are formed between a fixed lap 21c and a revolving lap 22b. The revolving scroll 22 is provided with a first oil passage for guiding an oil supplied through an oil supply through hole to an end plate surface 21d side of the fixed scroll 21. The end plate surface 21d of the fixed scroll 21 is provided with an oil groove G1 for guiding an oil supplied through the first oil passage to a back pressure chamber. The scroll compressor further includes a third oil passage 33 which allows the back pressure chamber and the revolving inner line side compression chamber C1a to communicate with each other intermittently or constantly; and a fourth oil passage 34 which allows the oil groove G1 and the revolving outer line side compression chamber C1b to communicate with each other intermittently or constantly.SELECTED DRAWING: Figure 7

Description

[Technical Field]

[0001] The present disclosure relates to scroll compressors and the like. [Background technology]

[0002] Regarding scroll compressors, for example, the technology described in Patent Document 1 is known. Patent Document 1 describes a scroll compressor equipped with a "first oil leakage path," a "second oil leakage path," and a "third oil leakage path." In this scroll compressor, a portion of the oil in the first space (a space where the pressure is close to the discharge pressure) is led to the second space (a space where the pressure is between the discharge pressure and the suction pressure) via the "first oil leakage path." Furthermore, a portion of the oil in the second space is led to the suction chamber via the "second oil leakage path." The remaining oil in the second space is led to the compression chamber via the "third oil leakage path." [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Laid-Open No. 2016-70178 Summary of the Invention [Problem to be solved by the invention]

[0004] In the technology described in Patent Document 1, by providing a first oil leakage passage, a second oil leakage passage, and a third oil leakage passage, it is possible to independently adjust the amount of oil supplied to the bearing portion, the amount of oil supplied to the suction chamber, and the amount of oil supplied to the compression chamber.

[0005] However, the technology described in Patent Document 1 does not particularly consider the appropriate distribution of oil to the inner orbiting line compression chamber and the outer orbiting line compression chamber when supplying oil to the compression chambers via the third oil leakage path. If an appropriate amount of oil could be supplied to each of the inner orbiting line compression chamber and the outer orbiting line compression chamber when supplying oil to each part of the scroll compressor, further efficiency could be improved, but Patent Document 1 does not describe such technology.

[0006] Therefore, an object of the present disclosure is to provide a scroll compressor or the like that is highly efficient. [Means for solving the problem]

[0007] In order to solve the above-mentioned problems, the scroll compressor according to the present disclosure includes a sealed container in the bottom of which oil is stored, an electric motor installed inside the sealed container and having a stator and a rotor, a crankshaft having an oil supply through hole and rotating integrally with the rotor, a fixed scroll having a spiral-shaped fixed wrap, and an orbiting scroll having a spiral-shaped orbiting wrap and orbiting with the rotation of the crankshaft, and an inner orbiting line side compression chamber and an outer orbiting line side compression chamber are formed between the fixed wrap and the orbiting wrap. A line-side compression chamber is formed, the orbiting scroll is provided with a first oil flow passage that guides oil supplied through the oil supply through hole to the end plate surface side of the fixed scroll, the end plate surface of the fixed scroll is provided with an oil groove that guides oil supplied through the first oil flow passage to a back pressure chamber, a third oil flow passage that intermittently or constantly connects the back pressure chamber with the orbiting inner line-side compression chamber, and a fourth oil flow passage that intermittently or constantly connects the oil groove with the orbiting outer line-side compression chamber. [Effects of the Invention]

[0008] According to the present disclosure, a scroll compressor or the like with high efficiency can be provided. [Brief explanation of the drawings]

[0009] [Figure 1] 1 is a vertical cross-sectional view of a scroll compressor according to a first embodiment. [Figure 2] 2 is a longitudinal sectional view of the scroll compressor according to the first embodiment, in which the orbiting scroll is cut along a plane including a first oil flow path. 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] 3 is a vertical cross-sectional view of the scroll compressor according to the first embodiment, in which the orbiting scroll is cut along a plane including a third oil flow path. FIG. [Figure 5] FIG. 2 is a bottom view of a fixed scroll included in the scroll compressor according to the first embodiment. [Figure 6] FIG. 2 is an explanatory diagram regarding the flow of oil in the scroll compressor according to the first embodiment. [Figure 7] 2 is a cross-sectional view of the scroll compressor according to the first embodiment taken along the line II-II in FIG. 1, showing a state in which the crank angle of the orbiting scroll is 0°. [Figure 8] 2 is a cross-sectional view of the scroll compressor according to the first embodiment taken along the line II-II in FIG. 1, showing a state in which the crank angle of the orbiting scroll is 90°. [Figure 9] 2 is a cross-sectional view of the scroll compressor according to the first embodiment taken along the line II-II in FIG. 1, showing a state in which the crank angle of the orbiting scroll is 180°. [Figure 10] 2 is a cross-sectional view of the scroll compressor according to the first embodiment taken along the line II-II in FIG. 1, showing a state in which the crank angle of the orbiting scroll is 270°. [Figure 11] FIG. 10 is a configuration diagram of an air conditioner according to a second embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0010] 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 refrigerant gas. 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, an auxiliary bearing 6, an orbiting bearing 7, and an Oldham ring 8. In addition to the components described above, the scroll compressor 100 also includes balance weights 9a and 9b, a housing 10, a subframe 11, an oil supply pump 12, an oil supply pump case 13, and an oil return pipe 14.

[0011] The sealed container 1 is a container that houses the compression mechanism 2, crankshaft 3, electric motor 4, etc., and is substantially sealed. Oil (also called lubricating oil or refrigeration oil) for lubricating the compression mechanism 2 and each bearing is sealed in the sealed container 1, and is stored as an oil reservoir E1 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.

[0012] 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.

[0013] The compression mechanism 2 is a mechanism that compresses refrigerant gas in accordance with the rotation of the crankshaft 3. 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.

[0014] The fixed scroll 21 is a member that forms a compression chamber C1 together with the orbiting scroll 22. The fixed scroll 21 is installed on the upper side of a frame 23 and fixed to the frame 23 with bolts B1. As shown in FIG. 1, the fixed scroll 21 includes a base plate 21a, a support portion 21b, and a fixed wrap 21c, which are integrally formed.

[0015] The base plate 21a is a thick portion having a circular shape in a plan view. A suction port J1 is provided at a predetermined location near the periphery of the base plate 21a. The suction port J1 is a space into which refrigerant is guided via a suction pipe P1. A discharge port J2 is provided near the center of the base plate 21a. The discharge port J2 is an opening that guides the refrigerant compressed in the compression chamber C1 to a discharge space C3 above the compression mechanism 2.

[0016] The support portion 21b is a cylindrical portion that supports the base plate 21a and is provided on the peripheral edge of the base plate 21a so as to surround the fixed wrap 21c. The annular lower surface of the support portion 21b is referred to as the end plate surface 21d. The end plate surface 21d is the sliding surface where the support portion 21b of the fixed scroll 21 comes into contact with the end plate 22a of the orbiting scroll 22. The height position of the end plate surface 21d is approximately equal to the height position of the tooth tip of the fixed wrap 21c. An oil groove G1 (see also Figure 5) through which oil is supplied is provided on the end plate surface 21d. Details of the oil groove G1 will be described later.

[0017] The fixed wrap 21c is a part that forms the compression chamber C1 together with the orbiting wrap 22b. The fixed wrap 21c has a spiral shape (see also FIG. 5) and extends downward from the base plate 21a. The surface of the base plate 21a is also called the tooth bottom because it exists in the gap between the fixed wraps 21c.

[0018] The orbiting scroll 22 is a member that orbits in conjunction with the rotation of the crankshaft 3 and forms a compression chamber C1 between itself and the fixed scroll 21. The central axis of the orbiting scroll 22 is eccentric by a predetermined distance with respect to the central axis of the fixed scroll 21. The orbiting scroll 22 is disposed opposite the fixed scroll 21. As shown in FIG. 1, the orbiting scroll 22 includes an end plate 22a, an orbiting wrap 22b, and a boss portion 22c, which are integrally formed.

[0019] The end plate 22a is a disk-shaped portion that slides against the fixed scroll 21. The surface of the end plate 22a that comes into contact with the fixed scroll 21 is the end plate surface 22d of the orbiting scroll 22. The orbiting wrap 22b forms the compression chamber C1 together with the fixed wrap 21c. The orbiting wrap 22b is spiral-shaped (see also FIG. 3) and extends upward from the end plate 22a.

[0020] The portions of the surface of the end plate 22a that exist in the gaps between the orbiting wraps 22b are also called tooth bottoms. The tooth tips of the orbiting wraps 22b are arranged so that there is a small gap between them in the vertical direction and the tooth bottoms of the fixed wraps 21c. Similarly, the tooth tips of the fixed wraps 21c are arranged so that there is a small gap between them in the vertical direction and the tooth bottoms of the orbiting wraps 22b. The spiral orbiting wraps 22b are arranged so that they are offset from the spiral orbiting wraps 21c by a predetermined angle (e.g., 180°) in the circumferential direction (see also FIG. 7). A compression chamber C1 is formed between the fixed wraps 21c and the orbiting wraps 22b.

[0021] 1 is a portion that fits onto the eccentric portion 3b of the crankshaft 3. The boss portion 22c is cylindrical and extends downward from the center of the back surface of the end plate 22a.

[0022] The frame 23 is a member that supports the fixed scroll 21 and includes a frame main body 23a and a frame seal 23b. The frame main body 23a has a generally rotationally symmetric shape and is fixed to the inner circumferential surface of the cylindrical chamber 1a by welding or the like. The frame main body 23a is provided with an insertion hole H1 through which the crankshaft 3 is inserted. The frame main body 23a also has an oil return hole H2 in the lateral direction, into which the upstream end of the oil return pipe 14 is inserted.

[0023] The frame main body 23a has a cylindrical partition wall 231a that surrounds the boss portion 22c of the orbiting scroll 22. The partition wall 231a separates a space radially inside from a space radially outside. The upper end surface of the partition wall 231a is adjacent to the end plate 22a of the orbiting scroll 22. The partition wall 231a also has an annular groove (not shown) that is recessed downward from its upper end surface. A resin seal ring R1 is installed in this groove. The seal ring R1 is compressed between the lower surface of the end plate 22a of the orbiting scroll 22 and the wall surface of the groove in the frame main body 23a.

[0024] The space radially inside the partition wall 231a is a high-pressure space whose pressure is approximately equal to (or slightly lower than) the discharge pressure. On the other hand, the space radially outside the partition wall 231a is a back pressure chamber C2 whose pressure is a predetermined intermediate pressure between the suction pressure and the discharge pressure. The intermediate pressure in the back pressure chamber C2 pushes the orbiting scroll 22 upward toward the fixed scroll 21. This maintains the airtightness of the compression chamber C1, thereby suppressing gas leakage. The frame seal 23b is an annular sealing member that closes the insertion hole H1 of the frame main body 23a from below.

[0025] The crankshaft 3 is a shaft member that rotates integrally with the rotor 4b of the electric motor 4. The crankshaft 3 is disposed coaxially with the central axis of the fixed scroll 21 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 through hole 3c. 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 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. The oil supply through hole 3c is a hole that penetrates the crankshaft 3 in the axial direction.

[0026] The electric motor 4 is a driving source that rotates the crankshaft 3. The electric motor 4 is installed inside the sealed container 1, between the frame 23 and the subframe 11. As shown in FIG. 1, the electric motor 4 includes a stator 4a and a rotor 4b. The stator 4a has a stator core 41a and a winding 42a, and is fixed to the inner circumferential surface of the cylindrical chamber 1a by press-fitting or the like. The rotor 4b is rotatably disposed radially inside the stator 4a. The crankshaft 3 is fixed to the rotor 4b so as to be coaxial with its central axis.

[0027] The main bearing 5 rotatably supports the upper part of the main shaft portion 3a relative to the frame 23. The main bearing 5 is installed on the circumferential surface of the insertion hole H1 of the frame main body 23a. The sub-bearing 6 rotatably supports the lower part of the main shaft portion 3a relative to the sub-frame 11. The sub-bearing 6 is installed inside the housing 10, which will be described later. The orbiting bearing 7 rotatably supports the eccentric portion 3b relative to the boss portion 22c of the orbiting scroll 22, and is installed on the inner circumferential surface of the boss portion 22c.

[0028] The Oldham ring 8 is a ring-shaped member that receives the eccentric rotation of the eccentric portion 3b and orbits the orbiting scroll 22 while restraining it from rotating on its axis. The Oldham ring 8 is installed in a groove (not shown) on the underside of the orbiting scroll 22, and is also installed in a groove (not shown) in the frame 23.

[0029] The balance weights 9a and 9b are members for suppressing vibration of the scroll compressor 100. In the example of Fig. 1, the balance weight 9a is installed above the rotor 4b on the main shaft portion 3a of the crankshaft 3. In addition, another balance weight 9b is installed below the rotor 4b of the electric motor 4.

[0030] The housing 10 is a member that houses the auxiliary bearing 6. The housing 10 has a roughly rotationally symmetric shape and is mounted on a sub-frame 11. The sub-frame 11 is a member that fixes the position of the housing 10. As shown in FIG. 1 , the sub-frame 11 is fixed to the sealed container 1 while being disposed below the electric motor 4.

[0031] The oil supply pump 12 is a pump that draws up oil from an oil reservoir E1 at the bottom of the sealed container 1, and is installed at the lower end of the crankshaft 3. A positive displacement or centrifugal pump is used as this oil supply pump 12. A tubular oil suction port 13a extending in the vertical direction is provided at the bottom of the oil supply pump 12. The oil supply pump case 13 houses the oil supply pump 12, and is fixed to the underside of the housing 10 with bolts B2.

[0032] As the crankshaft 3 rotates, oil is sucked up from the oil reservoir E1 through the oil suction port 13a and the oil feed through hole 3c in this order. A horizontal hole 3d is provided in the oil feed through hole 3c at a location corresponding to the sub-bearing 6. Some of the oil flowing through the oil feed through hole 3c is guided to the sub-bearing 6 via the horizontal hole 3d.

[0033] The oil return pipe 14 is an inverted L-shaped pipe for returning oil that has lubricated the main bearing 5 to the oil reservoir E1. The oil return pipe 14 is elongated and extends vertically along the inner circumferential surface of the sealed container 1, with the upper end near the pipe bent laterally inward. As described above, the upstream end of the oil return pipe 14 (near the upper end in the height direction) is inserted into the oil return hole H2 of the frame body 23a.

[0034] When the crankshaft 3 is rotated by the drive of the electric motor 4, the orbiting scroll 22 orbits accordingly. That is, the orbiting scroll 22 orbits with a predetermined orbital radius around the central axis of the fixed scroll 21. Refrigerant gas is drawn into the suction chamber C5 (see FIG. 7) through the suction pipe P1 and the suction port J1 in this order, and after being compressed in the compression chamber C1, is discharged into the discharge space C3 above the compression mechanism 2 through the discharge port J2. The refrigerant discharged into the discharge space C3 is guided to the motor chamber C4 through flow paths (not shown) on the outer periphery of the fixed scroll 21 and the frame 23, and further discharged to the outside of the sealed container 1 (for example, to piping forming part of the refrigeration cycle) through the discharge pipe P2.

[0035] Furthermore, oil stored as oil sump E1 at the bottom of the sealed container 1 rises through the oil feed through hole 3c of the crankshaft 3. A portion of the oil flowing through the oil feed through hole 3c is guided to the sub-bearing 6 through the horizontal hole 3d, and after lubricating the sub-bearing 6 is returned to the oil sump E1. Most of the oil flowing through the oil feed through hole 3c is guided to the space radially inside the boss portion 22c through the opening at the upper end of the oil feed through hole 3c. Some of this oil flows through the vertical peripheral groove G4 provided on the outer peripheral surface of the eccentric portion 3b, and further lubricates the slewing bearing 7 and the main bearing 5 in that order, before being returned to the oil sump E1 through the oil return pipe 14.

[0036] FIG. 2 is a vertical cross-sectional view of the orbiting scroll 22 cut along a plane including the first oil passage 31. As shown in FIG. As shown in Fig. 2, a first oil flow passage 31 is provided in the end plate 22a of the orbiting scroll 22. The first oil flow passage 31 is a flow passage that guides oil supplied via the oil feed through hole 3c of the crankshaft 3 (see Fig. 1) to the end plate surface 21d side of the fixed scroll 21 (see Fig. 1). The first oil flow passage 31 includes flow passages 31a to 31c.

[0037] The flow passage 31a is a radial flow passage provided inside the head plate 22a. This flow passage 31a is formed, for example, by performing a predetermined drilling process from the peripheral surface of the head plate 22a to the radially inward direction. The outer end of the flow passage 31a is sealed with a seal plug N1. As shown in FIG. 2, the flow passage 31a communicates with the internal space of the boss portion 22c via a vertical flow passage 31b provided on the inner peripheral side. The internal space of the boss portion 22c is filled with high-pressure oil at a pressure approximately equal to the discharge pressure.

[0038] Furthermore, the flow path 31a communicates with a vertical flow path 31c provided on the outer periphery. This flow path 31c opens at the end plate surface 22d of the orbiting scroll 22. That is, the opening 31d of the first oil flow path 31 is provided at the end plate surface 22d. The opening 31d is provided at a location that intermittently communicates with the oil groove G1 (see FIG. 7) of the fixed scroll 21 as the orbiting scroll 22 orbits. High-pressure oil flowing through the oil feed through hole 3c (see FIG. 1) is intermittently supplied to the oil groove G1 (see FIG. 1) of the fixed scroll 21 via the flow paths 31a to 31c and the opening 31d in that order.

[0039] FIG. 3 is a perspective view of the orbiting scroll 22. As shown in FIG. As shown in Figure 3, the end plate surface 22d of the orbiting scroll 22 is provided with an opening 31d of the first oil flow path 31 (see also Figure 2) as well as a recess 32a, an opening 33d, and a recessed groove 34a.

[0040] The recess 32a is a circular recess provided in the end plate surface 22d of the orbiting scroll 22. The recess 32a functions as an oil pocket when oil is intermittently supplied from the back pressure chamber C2 (see FIG. 1) to the suction chamber C5 (see FIG. 7). The second oil flow path 32, which intermittently connects the back pressure chamber C2 and the suction chamber C5, is configured to include the recess 32a provided in the end plate surface 22d of the orbiting scroll 22.

[0041] The opening 33d is a location where one end of a third oil flow path 33 (see FIG. 4), which will be described later, opens on the end plate surface 22d. The recessed groove 34a is a radially elongated recess provided in the end plate surface 22d of the orbiting scroll 22. As the orbiting scroll 22 orbits, the oil groove G1 (see FIG. 7) of the fixed scroll 21 and the orbiting outer line side compression chamber C1b (see FIG. 7) are intermittently communicated with each other via the recessed groove 34a. The fourth oil flow path 34, which intermittently communicates the oil groove G1 (see FIG. 7) of the fixed scroll 21 and the orbiting outer line side compression chamber C1b (see FIG. 7), is configured to include the recessed groove 34a.

[0042] FIG. 4 is a vertical cross-sectional view of the orbiting scroll 22 cut along a plane including the third oil passage 33. As shown in FIG. As shown in Fig. 4, the orbiting scroll 22 is provided with a third oil flow path 33. The third oil flow path 33 is a flow path that passes through the inside of the end plate 22a of the orbiting scroll 22, and has the function of intermittently communicating the back pressure chamber C2 (see Fig. 1) with the inner orbiting compression chamber C1a (see Fig. 7). The inner orbiting compression chamber C1a (see Fig. 7) is a compression chamber on the inner circumferential side of the orbiting wrap 22b. On the other hand, the outer orbiting compression chamber C1b (see Fig. 7) is a compression chamber on the outer circumferential side of the orbiting wrap 22b.

[0043] As shown in FIG. 4, the third oil flow path 33 includes flow paths 33a to 33c. The flow path 33a is provided radially inside the end plate 22a. This flow path 33a is formed, for example, by performing a predetermined drilling process radially inward from the peripheral surface of the end plate 22a. The outer peripheral end of the flow path 33b is sealed with a seal plug N2. As shown in FIG. 4, the flow path 33a communicates with the vertical flow path 33b provided on the outer peripheral side. This flow path 33b opens at the end plate surface 22d of the orbiting scroll 22. That is, an opening 33d on one end side of the third oil flow path 33 is provided in the end plate surface 22d. The opening 33d is provided at a location that intermittently communicates with the back pressure chamber C2 (see FIG. 1) as the orbiting scroll 22 orbits.

[0044] The flow path 33a also communicates with a vertical flow path 33c provided on the inner peripheral side. This flow path 33c opens at the tooth bottom between the orbiting wraps 22b. That is, an opening 33e on the other end side of the third oil flow path 33 is provided at the tooth bottom between the orbiting wraps 22b. This opening 33e is provided at a location that communicates with the orbiting internal compression chamber C1a (see FIG. 7) as the orbiting scroll 22 orbits. In this way, the opening 33d (one end) of the third oil flow path 33 intermittently communicates with the back pressure chamber C2 (see FIG. 1), and another opening 33e (the other end) communicates with the orbiting internal compression chamber C1a (see FIG. 7).

[0045] FIG. 5 is a bottom view of the fixed scroll 21. FIG. As shown in Fig. 5, an oil groove G1 is provided in the end plate surface 21d of the fixed scroll 21. The oil groove G1 is a flow path that guides oil supplied via the first oil flow path 31 (see Fig. 2) of the orbiting scroll 22 (see Fig. 2) to the back pressure chamber C2 (see Fig. 1). As shown in Fig. 5, the oil groove G1 is configured to include an arc-shaped circumferential groove G1a, an introduction groove G1b connected to one end of the circumferential groove G1a, and an oil drain groove G1c connected to the other end of the circumferential groove G1a.

[0046] The circumferential groove G1a is an arc-shaped groove provided on the end plate surface 21d and is formed within a range of a predetermined central angle, for example, with the vicinity of the center of the fixed scroll 21 as a reference (center of the arc) when viewed from below.

[0047] The introduction groove G1b is formed in an arc shape so as to partially include the circular movement locus M1 (see FIG. 7) of the opening 31d (see FIG. 2) of the first oil passage 31 (see FIG. 2). When the opening 31d of the first oil passage 31 overlaps with the introduction groove G1b (see FIG. 9), the first oil passage 31 and the oil groove G1 communicate with each other. When the opening 31d of the first oil passage 31 does not overlap with the introduction groove G1b (see FIG. 7), the opening 31d is blocked by the end plate surface 21d of the fixed scroll 21.

[0048] In this way, the introduction groove G1b intermittently communicates with the opening 31d (see FIG. 7) of the first oil passage 31 (see FIG. 2) on the end plate surface 21d side of the fixed scroll 21. That is, as the orbiting scroll 22 (see FIG. 7) orbits, the first oil passage 31 and the oil groove G1 intermittently communicate with each other. As a result, high-pressure oil substantially equal to the discharge pressure is sequentially introduced into the circumferential groove G1a and the oil drain groove G1c via the introduction groove G1b.

[0049] The oil drain groove G1c is a throttle flow passage provided radially outward from the end of the circumferential groove G1a. The upstream end of the oil drain groove G1c is connected to the circumferential groove G1a, and the downstream end is connected to the annular groove G2. The annular groove G2 is an annular groove provided near the periphery of the end plate surface 21d of the fixed scroll 21. The space between the annular groove G2 and the frame 23 (see FIG. 1) forms part of the back pressure chamber C2 (see FIG. 1). Therefore, the oil drain groove G1c is in communication with the back pressure chamber C2.

[0050] The depth of the oil drain groove G1c is shallower than the depths of the circumferential groove G1a and the introduction groove G1b. The flow path area of ​​the oil drain groove G1c is smaller than the flow path area of ​​the circumferential groove G1a and the introduction groove G1b. The groove width of the oil drain groove G1c may be equal to or different from the groove width of the circumferential groove G1a or the introduction groove G1b.

[0051] The shallower the depth of the oil drain groove G1c, the smaller the amount of oil supplied to the back pressure chamber C2 (see FIG. 1) via the oil groove G1. Therefore, by appropriately adjusting the depth of the oil drain groove G1c and other factors at the design stage, the amount of oil supplied to the back pressure chamber C2 (see FIG. 1) via the oil groove G1 can be adjusted. In this way, the amount of oil supplied from the first oil passage 31 (see FIG. 2) via the oil groove G1 to the back pressure chamber C2 can be adjusted by the depth of the oil drain groove G1c.

[0052] The suction chamber C5 shown in Fig. 5 is a space into which the refrigerant is drawn through the suction port J1 (see also Fig. 1), and is provided in the fixed scroll 21. When the orbiting scroll 22 (see Fig. 7) orbits and the refrigerant is completely trapped in the suction chamber C5, a compression chamber C1 (see Fig. 7) is formed. As shown in Fig. 5, a suction groove G3 is connected to the circumferential end of the suction chamber C5.

[0053] The suction groove G3 is a groove that intermittently communicates with the recessed portion 32a (see FIG. 7) of the orbiting scroll 22 and is formed to include a portion of the circular movement locus M2 (see FIG. 7) of the recessed portion 32a. As shown in FIG. 5, the suction groove G3 is provided on the end plate surface 21d of the fixed scroll 21, on one circumferential side from the end of the suction chamber C5. As the orbiting scroll 22 orbits, the recessed portion 32a (see FIG. 7) alternately communicates with the annular groove G2 and the suction groove G3. This allows oil to be intermittently supplied from the back pressure chamber C2 (see FIG. 1) to the suction chamber C5.

[0054] The notch G2a shown in Fig. 5 is a portion cut out radially inward from the inner circumferential edge of the annular groove G2. The notch G2a is formed to partially include the circular movement locus M3 (see Fig. 7) of the opening 33d (see Fig. 4) of the third oil flow passage 33. When the opening 33d overlaps the area of ​​the notch G2a (see Fig. 10), the third oil flow passage 33 communicates with the back pressure chamber C2 (see Fig. 1) via the annular groove G2.

[0055] FIG. 6 is an explanatory diagram regarding the flow of oil in a scroll compressor (also see FIG. 1 as appropriate). In addition, the thickness of the multiple white arrows in FIG. 6 indicates the amount of oil supplied. The oil stored in the oil reservoir E1 of the scroll compressor 100 is pumped up by the oil supply pump 12, and some of it is guided to bearings such as the main bearing 5, the sub-bearing 6, and the orbiting bearing 7, and the rest is guided to the first oil flow path 31 (see Figure 2).

[0056] Then, as a result of the first oil flow passage 31 and the oil groove G1 (see also FIG. 5) intermittently communicating with each other, oil is supplied from the first oil flow passage 31 to the oil groove G1, and this oil is further guided to the back pressure chamber C2 via the oil drain groove G1c. As described above, part of the oil that has flowed into the back pressure chamber C2 is guided from the back pressure chamber C2 to the suction chamber C5 as the recess 32a (second oil flow passage 32: see also FIG. 3) alternately communicates with the annular groove G2 (see FIG. 7) and the suction groove G3 (see FIG. 7).

[0057] A part of the oil that has flowed into the back pressure chamber C2 is guided to the inner orbital line compression chamber C1a (see FIG. 7) via the third oil flow path 33 (see also FIG. 4).

[0058] When the suction chamber C5 is closed and the compression chamber C1 is formed, the oil in the suction chamber C5 is appropriately distributed to the inner and outer compression chambers C1a and C1b. The remaining oil supplied from the first oil passage 31 (see also FIG. 2) to the oil groove G1 (see also FIG. 5) is intermittently supplied to the outer compression chamber C1b via the recessed groove 34a (fourth oil passage 34: see also FIG. 3). The oil in the inner and outer compression chambers C1a and C1b is discharged to the discharge space C3 (see FIG. 1) via the discharge port J2 (see FIG. 1) and then returned to the oil reservoir E1.

[0059] If the amount of oil supplied to the suction chamber C5 or the compression chamber C1 is too small, poor lubrication will result in increased sliding loss between the fixed wrap 21c (see FIG. 7) and the orbiting wrap 22b (see FIG. 7). Furthermore, poor sealing of the gap between the fixed wrap 21c and the orbiting wrap 22b will also result in increased leakage loss. Furthermore, if the amount of oil supplied to the suction chamber C5 or the compression chamber C1 is too large, the oil will be hotter than the refrigerant gas, causing the refrigerant gas to heat and expand, resulting in increased heating loss.

[0060] In other words, there is an appropriate range for the amount of oil supplied to the suction chamber C5, the inner slewing compression chamber C1a, and the outer slewing compression chamber C1b, and this appropriate range is often different for each of the suction chamber C5, the inner slewing compression chamber C1a, and the outer slewing compression chamber C1b. Therefore, in the first embodiment, an appropriate amount of oil is supplied to the suction chamber C5, the inner slewing compression chamber C1a, and the outer slewing compression chamber C1b, as well as to the "bearings" such as the main bearing 5, the sub-bearing 6, and the slewing bearing 7.

[0061] FIG. 7 is a cross-sectional view taken along the line II-II in FIG. 1, showing a state in which the crank angle of the orbiting scroll 22 is 0°. The state in which the outer orbiting compression chamber C1b has completed suction of the refrigerant gas (i.e., confinement of the space) is defined as a crank angle of 0°. In addition, in Fig. 7, the periphery of the end plate 22a of the orbiting scroll 22 is indicated by a two-dot chain line (the same applies to Figs. 8 to 10).

[0062] Between the fixed wrap 21c and the orbiting wrap 22b, a plurality of crescent-shaped compression chambers C1 are formed, namely, an inner orbiting compression chamber C1a and an outer orbiting compression chamber C1b. As the orbiting scroll 22 orbits, the plurality of compression chambers C1 move toward the center, and the volumes of the inner orbiting compression chamber C1a and the outer orbiting compression chamber C1b continuously decrease.

[0063] The opening 31d of the first oil passage 31 (see FIG. 2) of the orbiting scroll 22 moves along a circular movement path M1 as the orbiting scroll 22 orbits. When the opening 31d and the introduction groove G1b of the oil groove G1 overlap (see also FIG. 9), high-pressure oil is introduced into the introduction groove G1b via the opening 31d. The high-pressure oil introduced into the introduction groove G1b flows sequentially through the circumferential groove G1a and the oil drain groove G1c, is decompressed and expanded in the oil drain groove G1c, and is then introduced into the back pressure chamber C2 (see FIG. 1) via the annular groove G2. The oil supplied to the back pressure chamber C2 lubricates the sliding parts of the Oldham ring 8 (see FIG. 1).

[0064] As the orbiting scroll 22 orbits, the recess 32a shown in FIG. 7 moves along a circular movement path M2, alternately communicating with the annular groove G2 and the suction groove G3. That is, the back pressure chamber C2 and the suction chamber C5 intermittently communicate with each other via the recess 32a. When the recess 32a communicates with the back pressure chamber C2 (see FIG. 1) via the annular groove G2, oil in the back pressure chamber C2 is stored in the recess 32a. Furthermore, when the recess 32a communicates with the suction chamber C5 via the suction groove G3, the oil in the recess 32a is released into the suction chamber C5 due to the pressure difference. This action is repeated, and oil in the back pressure chamber C2 is intermittently supplied to the suction chamber C5 via the recess 32a.

[0065] The oil supplied to the suction chamber C5 lubricates the sliding portions between the fixed scroll 21 and the orbiting scroll 22 and also seals gaps at the tips of the fixed wrap 21c and the orbiting wrap 22b. The larger the volume of the recess 32a, the greater the amount of oil supplied from the back pressure chamber C2 (see FIG. 1) to the suction chamber C5. Therefore, by appropriately adjusting the volume of the recess 32a during the design stage of the scroll compressor 100, the amount of oil supplied from the back pressure chamber C2 to the suction chamber C5 can be adjusted.

[0066] 7 is an opening on one end side of the third oil flow path 33 (see also FIG. 4), and is provided at a location that intermittently communicates with the back pressure chamber C2 (see FIG. 1) via the annular groove G2. Another opening 33e is an opening on the other end side of the third oil flow path 33 (see also FIG. 4), and is provided at a location that communicates with the inner orbiting line compression chamber C1a.

[0067] As the orbiting scroll 22 orbits, the opening 33d at one end of the third oil passage 33 moves along a circular movement path M3. When the opening 33d at one end of the third oil passage 33 communicates with the back pressure chamber C2 (see FIG. 1), the back pressure chamber C2 and the orbiting inner line compression chamber C1a communicate with each other via the third oil passage 33.

[0068] Furthermore, when the opening 33d is blocked by the end plate surface 21d of the fixed scroll 21, the third oil flow path 33 is not in communication with the inner orbiting compression chamber C1a. By intermittently communicating the back pressure chamber C2 with the inner orbiting compression chamber C1a in this manner, the so-called breathing loss can be reduced compared to when the chambers are constantly in communication. Here, the breathing loss refers to the pressure loss caused by the refrigerant gas moving back and forth between the back pressure chamber C2 and the inner orbiting compression chamber C1a. Incidentally, the third oil flow path 33 is intermittently in communication with the inner orbiting compression chamber C1a but is not in communication with the outer orbiting compression chamber C1b.

[0069] The pressure in the internal orbiting compression chamber C1a fluctuates as the orbiting scroll 22 orbits. That is, the pressure at the opening 33d on one end of the third oil passage 33 becomes higher or lower than the pressure at the opening 33e on the other end in accordance with the pressure fluctuations in the internal orbiting compression chamber C1a. For example, when the back pressure chamber C2 (see FIG. 1) is higher than the internal orbiting compression chamber C1a, oil and refrigerant gas (mainly oil) from the back pressure chamber C2 flow into the internal orbiting compression chamber C1a via the third oil passage 33.

[0070] Furthermore, when the back pressure chamber C2 (see FIG. 1) has a lower pressure than the interior rotation line compression chamber C1a, oil and refrigerant gas (mainly refrigerant gas) from the interior rotation line compression chamber C1a flow into the back pressure chamber C2 via the third oil flow path 33. In this way, depending on the difference between the pressure in the back pressure chamber C2 and the pressure in the interior rotation line compression chamber C1a, oil and refrigerant gas flow from one of the back pressure chamber C2 and the interior rotation line compression chamber C1a to the other. By repeating this process, the pressure in the back pressure chamber C2 (back pressure) settles to a value that roughly averages the pressure fluctuating in the interior rotation line compression chamber C1a, and oil in the back pressure chamber C2 is supplied to the interior rotation line compression chamber C1a.

[0071] The amount of oil supplied from the back pressure chamber C2 to the inner orbiting compression chamber C1a is the amount of oil flowing into the back pressure chamber C2 via the oil drain groove G1c provided in the oil groove G1 minus the amount of oil flowing out from the back pressure chamber C2 to the suction chamber C5 via the recess 32a of the orbiting scroll 22 (see FIG. 6). In other words, the amount of oil supplied to the inner orbiting compression chamber C1a can be adjusted by appropriately adjusting the depth of the oil drain groove G1c and the volume of the recess 32a of the orbiting scroll 22 at the design stage.

[0072] As described above, the recessed groove 34a shown in FIG. 7 is a long, narrow recess provided in the end plate surface 22d and is included in the fourth oil flow path 34. As the orbiting scroll 22 orbits, the recessed groove 34a moves along a circular path M4. When the recessed groove 34a spans both the oil groove G1 and the outer orbiting compression chamber C1b, the oil groove G1 and the outer orbiting compression chamber C1b communicate with each other via the recessed groove 34a. In other cases, the oil groove G1 and the outer orbiting compression chamber C1b do not communicate with each other. In this way, the oil groove G1 and the outer orbiting compression chamber C1b intermittently communicate with each other via the recessed groove 34a, allowing high-pressure oil from the oil groove G1 to be supplied to the outer orbiting compression chamber C1b. This promotes sealing and lubrication of the outer orbiting compression chamber C1b. Incidentally, the recessed groove 34a intermittently communicates with the turning outer line side compression chamber C1b but does not communicate with the turning inner line side compression chamber C1a.

[0073] The greater the groove width and depth of the recessed groove 34a (i.e., the greater the volume of the recessed groove 34a), the greater the amount of oil supplied from the oil groove G1 to the outer orbiting line side compression chamber C1b via the recessed groove 34a. Furthermore, the longer the communication section (i.e., communication time) between the oil groove G1 and the outer orbiting line side compression chamber C1b via the recessed groove 34a, the greater the amount of oil supplied to the outer orbiting line side compression chamber C1b. Therefore, by appropriately adjusting the volume, position, and shape of the recessed groove 34a during the design stage of the scroll compressor 100, the amount of oil supplied from the oil groove G1 to the outer orbiting line side compression chamber C1b can be adjusted.

[0074] FIG. 8 is a cross-sectional view taken along the line II-II in FIG. 1, showing a state in which the crank angle of the orbiting scroll 22 is 90°. 8, a portion of the recess 32a overlaps with the suction groove G3. This allows oil in the recess 32a (oil taken in from the back pressure chamber C2) to be supplied to the suction groove G3. The outer peripheral end of the recess 34a communicates with the oil groove G1, and the inner peripheral end communicates with the outer turning line compression chamber C1b. This allows oil to be supplied from the oil groove G1 to the outer turning line compression chamber C1b via the recess 34a.

[0075] FIG. 9 is a cross-sectional view taken along the line II-II in FIG. 1, showing a state in which the crank angle of the orbiting scroll 22 is 180°. In the state shown in Figure 9, the opening 31d of the first oil flow passage 31 (see Figure 2) overlaps with the introduction groove G1b. This allows high-pressure oil in the first oil flow passage 31 to be supplied to the oil groove G1 via the opening 31d. Furthermore, the recess 32a overlaps with the suction groove G3. This allows the oil in the recess 32a (oil taken in from the back pressure chamber C2) to be supplied to the suction groove G3.

[0076] FIG. 10 is a cross-sectional view taken along the line II-II in FIG. 1, showing a state in which the crank angle of the orbiting scroll 22 is 270°. In the state shown in Fig. 10, the opening 33d on one end side of the third oil flow passage 33 overlaps with the annular groove G2, and the opening 33e on the other end side overlaps with the inner orbiting compression chamber C1a. As a result, oil is supplied from the back pressure chamber C2 (see Fig. 1) to the inner orbiting compression chamber C1a via the third oil flow passage 33. Then, when the orbiting scroll 22 further orbits and the crank angle reaches 0°, the state returns to that shown in Fig. 7. Note that the configurations shown in Figs. 7 to 10 are merely examples and are not limited to these.

[0077] <Effects> According to the first embodiment, the scroll compressor 100 includes a first oil flow path 31, a second oil flow path 32, a third oil flow path 33, and a fourth oil flow path 34. This allows the amount of oil supplied to the main bearing 5, the auxiliary bearing 6, the orbiting bearing 7, the suction chamber C5, the inner orbiting line side compression chamber C1a, and the outer orbiting line side compression chamber C1b to be independently adjusted during the design stage. This ensures that the appropriate amount of oil is supplied to each of the aforementioned components, reducing the likelihood of an insufficient amount of oil being supplied to each component and reducing sliding loss and leakage loss. Furthermore, since the amount of oil supplied to each of the aforementioned components is less likely to be excessive, reducing heating loss due to the thermal expansion of the refrigerant gas. Thus, according to the first embodiment, the efficiency of the scroll compressor 100 can be improved.

[0078] Second Embodiment In the second embodiment, an air conditioner W1 (refrigeration cycle device: see FIG. 11) including the scroll compressor 100 (see FIG. 1) described in the first embodiment will be described.

[0079] FIG. 11 is a configuration diagram of an air conditioner W1 according to the second embodiment. The solid arrows in FIG. 11 indicate the flow of the refrigerant in the heating cycle. On the other hand, the dashed arrows in FIG. 11 indicate the flow of refrigerant in the cooling cycle. The air conditioner W1 is a device that performs air conditioning such as cooling operation and heating operation. As shown in Fig. 11, 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.

[0080] 11, 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.

[0081] The scroll compressor 100 is a device that compresses refrigerant gas, and has a configuration similar to that of the first embodiment (see FIG. 1). The outdoor heat exchanger 71 is a heat exchanger in which heat exchange occurs between the refrigerant flowing through its heat transfer tubes (not shown) and the outside air sent in from the outdoor fan 72. The outdoor fan 72 is a fan that sends the outside air to the outdoor heat exchanger 71. The outdoor fan 72 is provided with an outdoor fan motor 72a that serves as a drive source, and is installed near the outdoor heat exchanger 71.

[0082] 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 the 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.

[0083] 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).

[0084] 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. 11), the refrigerant circulates 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. 11), the refrigerant circulates sequentially through the scroll compressor 100, the indoor heat exchanger 75 (condenser), the expansion valve 73, and the outdoor heat exchanger 71 (evaporator).

[0085] <Effects> According to the second embodiment, the air conditioner W1 is equipped with a highly efficient scroll compressor 100, and therefore the efficiency of the air conditioner W1 as a whole can be improved.

[0086] <<Variations>> The scroll compressor 100 and the air conditioner W1 according to the present disclosure have been described above in relation to the various embodiments, but they are not limited to these descriptions and can be modified in various ways. For example, in the first embodiment, the first oil passage 31 and the oil groove G1 are intermittently in communication, but the present invention is not limited to this. That is, the first oil passage 31 and the oil groove G1 may be in constant communication. That is, the introduction groove G1b (see FIG. 7) may be in constant communication with the opening 31d (see FIG. 7) of the first oil passage 31 (see FIG. 2) on the end plate surface 21d side of the fixed scroll 21. In this case, the introduction groove G1b is formed as a predetermined hole or groove that includes the circular movement locus M1 (see FIG. 7) of the opening 31d of the first oil passage 31.

[0087] In the first embodiment, the back pressure chamber C2 and the suction chamber C5 are intermittently connected to each other via the recess 32a (second oil flow path 32: see FIG. 7). However, this is not limiting. The back pressure chamber C2 and the suction chamber C5 may be constantly connected to each other via the recess 32a (second oil flow path). In this case, the recess 32a is formed as a predetermined hole or groove of a size and position that allows constant communication between the back pressure chamber C2 and the suction chamber C5.

[0088] In the first embodiment, the case where one end (opening 33d) of the third oil flow path 33 intermittently communicates with the back pressure chamber C2 has been described, but this is not limiting. That is, one end (opening 33d) of the third oil flow path 33 may be constantly communicated with the back pressure chamber C2. That is, the back pressure chamber C2 and the inner orbital line compression chamber C1a may be constantly communicated with each other via the third oil flow path 33.

[0089] In the first embodiment, the oil groove G1 and the outer turning line side compression chamber C1b are intermittently connected to each other via the groove 34a (fourth oil flow path 34). However, the present invention is not limited to this. In other words, the oil groove G1 and the outer turning line side compression chamber C1b may be constantly connected to each other via the groove 34a (fourth oil flow path 34).

[0090] Furthermore, the number of each of the opening 31d of the first oil flow passage 31, the recess 32a, the openings 33d and 33e of the third oil flow passage, and the recessed groove 34a described in the first embodiment is not limited to one, but may be two or more. Furthermore, the arrangement and size of the opening 31d of the first oil flow passage 31, the recess 32a, the openings 33d and 33e of the third oil flow passage 33, and the recessed groove 34a can be changed as appropriate.

[0091] In the first embodiment, the recess 32a (second oil flow path 32) is provided to intermittently connect the back pressure chamber C2 and the suction chamber C5, but this is not limiting. That is, the recess 32a may be omitted, and the back pressure chamber C2 and the suction chamber C5 may not be connected to each other. Even with this configuration, an appropriate amount of oil can be supplied to each of the bearings (main bearing 5, sub-bearing 6, and orbiting bearing 7), the inner orbiting line compression chamber C1a, and the outer orbiting line compression chamber C1b, thereby achieving high efficiency of the scroll compressor.

[0092] In addition, in each embodiment, the oil drain groove G1c (see FIG. 5) is shallower than the circumferential groove G1a (see FIG. 5), but this is not limiting. For example, the groove width of the oil drain groove G1c may be narrower than the groove width of the circumferential groove G1a so that the flow path area of ​​the oil drain groove G1c is smaller than the flow path area of ​​the circumferential groove G1a. In this case, the depth of the oil drain groove G1c and the depth of the circumferential groove G1a may be equal to or different from each other.

[0093] The air conditioner W1 (see FIG. 11) described in the second embodiment can be applied to various types of air conditioners, such as multi-air conditioners for buildings, package air conditioners, and room air conditioners. The second 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 second embodiment can also be applied to other "refrigeration cycle devices" such as freezers, water heaters, air-conditioning water heaters, chillers, and refrigerators.

[0094] Furthermore, in the second embodiment, the air conditioner W1 (see FIG. 11) is described as being equipped with a four-way valve 74, but this is not limiting. That is, the four-way valve 74 may be omitted, and the air conditioner may be dedicated to cooling or heating. In the first embodiment, the scroll compressor 100 is installed vertically, but the present invention is not limited to this. For example, the scroll compressor 100 may be installed horizontally or obliquely. In the first embodiment, a case where a refrigerant gas is compressed by the scroll compressor 100 has been described, but the present invention is not limited to this. 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.

[0095] Furthermore, each embodiment has been described in detail to clearly explain the present disclosure, 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]

[0096] 1. Airtight container 2 Compression mechanism 3 crankshaft 3c Oil filler through hole 4 Electric motor 4a stator 4b Rotor 21 Fixed Scroll 21c fixed wrap 21d Mirror surface 22 Swivel Scroll 22a Headboard 22b Circling Wrap 23 frames 31 1st oil flow path 32 2nd oil flow path 32a Recess (second oil flow path) 33 Third oil flow path 33d Opening (one end of the third oil flow path) 33e Opening (other end of third oil flow path) 34 4th oil flow path 34a Concave groove (4th oil flow path) 71 Outdoor heat exchanger 72 Outdoor fan 73 Expansion valve 74 Four-way valve 75 Indoor heat exchanger 76 Indoor fan 100 Scroll Compressor C1 compression chamber C1a Compression chamber on inner side of turning C1b Compression chamber on outer track side C2 Back pressure chamber C5 Intake chamber E1 Oil reservoir G1 oil groove G1a Circumferential groove G1b Introduction groove G1c oil drain groove W1 Air conditioner (refrigeration cycle device)

Claims

1. a sealed container in the bottom of which oil is stored; an electric motor installed inside the sealed container and having a stator and a rotor; a crankshaft having an oil supply through hole and rotating integrally with the rotor; a fixed scroll having a spiral-shaped fixed wrap; an orbiting scroll having a spiral orbiting wrap and orbiting with the rotation of the crankshaft, An inner orbiting line side compression chamber and an outer orbiting line side compression chamber are formed between the fixed wrap and the orbiting wrap, The orbiting scroll is provided with a first oil flow path that guides oil supplied through the oil supply through hole toward the end plate surface of the fixed scroll, an oil groove is provided on the end plate surface of the fixed scroll to guide the oil supplied via the first oil flow path to a back pressure chamber; a third oil flow path that intermittently or constantly communicates the back pressure chamber with the rotation inner line side compression chamber; a fourth oil flow path that intermittently or constantly communicates the oil groove with the outer orbiting line side compression chamber;

2. The first oil flow path and the oil groove are in intermittent or constant communication with each other.

2. The scroll compressor according to claim 1,

3. The oil groove is The groove has an arc-shaped circumferential direction, an introduction groove connected to one end of the circumferential groove and intermittently or constantly communicating with an opening of the first oil flow path on the end plate surface side; an oil drain groove connected to the other end of the circumferential groove and communicating with the back pressure chamber; 3. The scroll compressor according to claim 2,

4. The depth of the oil drain groove is shallower than the depths of the circumferential groove and the introduction groove, The amount of oil supplied from the first oil flow path to the back pressure chamber via the oil groove is adjusted by the depth of the oil drain groove.

4. The scroll compressor according to claim 3,

5. Further provided is a second oil flow path that intermittently or constantly communicates the back pressure chamber with the suction chamber.

2. The scroll compressor according to claim 1,

6. The second oil flow path includes a recess provided in an end plate surface of the orbiting scroll, The back pressure chamber and the suction chamber are in intermittent or constant communication with each other via the recess.

6. The scroll compressor according to claim 5,

7. The third oil flow path is a flow path passing through the inside of the end plate of the orbiting scroll, one end of the third oil flow path intermittently or constantly communicates with the back pressure chamber, Oil flows from the back pressure chamber into the rotation inner line side compression chamber in accordance with the difference between the pressure in the back pressure chamber and the pressure in the rotation inner line side compression chamber.

2. The scroll compressor according to claim 1,

8. The fourth oil flow path includes a recessed groove provided in an end plate surface of the orbiting scroll, The oil groove and the outer turning line side compression chamber are in intermittent or constant communication with each other via the recessed groove.

2. The scroll compressor according to claim 1,

9. A refrigeration cycle apparatus comprising: the scroll compressor according to any one of claims 1 to 8; an outdoor heat exchanger; an expansion valve; and an indoor heat exchanger.

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