Scroll compressor and refrigeration cycle device

Abstract

Provided is a scroll compressor or the like that is highly efficient and has high reliability. An annular back pressure groove (G3) that communicates with a back pressure chamber is provided on an end plate face (21f) of a fixed scroll (21), and a first groove (G1) in the shape of a circular arc and a second groove (G2) in the shape of a circular arc are provided on the radially inner side of the back pressure groove (G3), a first hole and a second hole that guide lubricating oil from an oil supply path to the end plate face (21f) side of the fixed scroll (21) are provided on a revolving scroll, the first groove (G1) contains at least a portion of the movement locus of the opening of the first hole, the second groove (G2) contains at least a portion of the movement locus 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 Art

[0002] Regarding scroll compressors, as a technology for maintaining the thrust load (axial force) applied from one direction to the other on the fixed scroll and the orbiting scroll within an appropriate range, there is known a technology described in Patent Document 1, for example. Specifically, Patent Document 1 describes a structure in which an oil groove is provided, extending in the circumferential direction of the sliding surface of the fixed scroll, through which lubricating oil flows.

[0003] Prior art literature

[0004] Patent Literature

[0005] Patent Document 1: Japanese Patent Application Laid-Open No. 2016-17484 Summary of the Invention

[0006] Problems to be solved by the invention

[0007] For example, to reduce sliding losses between the fixed and orbiting scrolls during low loads, which significantly impact year-round energy efficiency, there's a tendency to set the force pushing the orbiting scroll upward toward the fixed scroll to a smaller value. In the technology described in Patent Document 1, for example, when a scroll compressor operates at a low compression ratio, high-pressure lubricating oil is introduced into the oil sump of the fixed scroll, potentially increasing the force exerted by this lubricating oil on the orbiting scroll. This results in the orbiting scroll oscillating, which not only reduces efficiency but also potentially compromises reliability.

[0008] Therefore, an object of the present invention is to provide a scroll compressor and the like that are highly efficient and reliable.

[0009] Solutions to Problems

[0010] In order to solve the above-mentioned problems, the scroll compressor of the present invention comprises: a sealed container; an electric motor having a stator and a rotor and housed in the above-mentioned sealed container; a shaft having an oil supply path for the flow of lubricating oil and rotating integrally with the above-mentioned rotor; a fixed scroll having a spiral fixed scroll plate; a revolving scroll having a spiral revolving scroll plate, a compression chamber being formed between the above-mentioned fixed scroll plate and the above-mentioned revolving scroll plate; and a frame having an insertion hole for the above-mentioned shaft, supporting the above-mentioned fixed scroll, a back pressure chamber being provided between the above-mentioned revolving scroll and the above-mentioned frame, and a back pressure chamber being provided on the end plate surface of the above-mentioned fixed scroll. The back-pressure chamber is connected to an annular back-pressure groove, and a first arc-shaped groove and a second arc-shaped groove are provided radially inwardly of the back-pressure groove, the distance between the second groove and the back-pressure groove being shorter than the distance between the first groove and the back-pressure groove. The orbiting scroll is provided with a first hole and a second hole for guiding lubricating oil from the oil supply passage to the end plate surface side of the fixed scroll, the first groove including at least a portion of the movement trajectory of the opening of the first hole, the second groove including at least a portion of the movement trajectory of the opening of the second hole, and the first groove and the second groove at least partially overlap in the radial direction. Other embodiments are described in the embodiments.

[0011] The effects of the invention are as follows.

[0012] According to the present invention, a scroll compressor and the like having high efficiency and high reliability can be provided. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] Figure 1 It is a longitudinal sectional view of the scroll compressor according to the first embodiment.

[0014] Figure 2 It is a longitudinal sectional view of the orbiting scroll included in the scroll compressor according to the first embodiment.

[0015] Figure 3 It is a perspective view of the orbiting scroll included in the scroll compressor according to the first embodiment.

[0016] Figure 4 It is a bottom view of the fixed scroll included in the scroll compressor according to the first embodiment.

[0017] Figure 5 The scroll compressor of the first embodiment is partially enlarged. Figure 4 The diagram is an explanatory diagram showing the movement trajectory of the opening of the first hole and the movement trajectory of the opening of the second hole.

[0018] Figure 6 It is a bottom view of a fixed scroll included in a scroll compressor according to a second embodiment.

[0019] Figure 7In the scroll compressor of the second embodiment, the Figure 6 The area K2 is an explanatory diagram showing the movement trajectory of the opening of the first hole and the movement trajectory of the opening of the second hole.

[0020] Figure 8 It is a bottom view of a fixed scroll included in a scroll compressor according to a third embodiment.

[0021] Figure 9 The scroll compressor of the third embodiment is partially enlarged. Figure 8 The area K3 is an explanatory diagram showing the movement trajectory of the opening of the first hole and the movement trajectory of the opening of the second hole.

[0022] Figure 10 This is a structural diagram including a refrigerant circuit of an air conditioner according to a fourth embodiment.

[0023] Explanation of symbols

[0024] 1—Sealed container, 2—Compression mechanism, 21, 21A, 21B—Stationary scroll, 21a—Base plate, 21b—Stationary scroll plate, 21f—End plate surface, 22—Orbiting scroll, 22a—End plate, 22b—Orbiting scroll plate, 23—Frame, 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—Recesses, G3—Back pressure groove, G1—First groove, G2, GA2 , GB2—second groove, H1—through hole, H2—connecting hole, H4—first hole, H5—second 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 (opening of the first hole), J5—opening (opening of the first hole), M4—moving trajectory (moving trajectory of the opening of the first hole), M5—moving trajectory (moving trajectory of the opening of the second hole), W1—air conditioner (refrigeration cycle device). DETAILED DESCRIPTION

[0025] First Implementation Method

[0026] Scroll Compressor Structure

[0027] Figure 1 It is a longitudinal sectional view of the scroll compressor 100 according to the first embodiment.

[0028] The scroll compressor 100 is a device for compressing gaseous refrigerant. Figure 1As shown, scroll compressor 100 includes a sealed container 1, a compression mechanism 2, a crankshaft 3 (shaft), an electric motor 4, a main bearing 5, and a rotary bearing 6. In addition to the above-mentioned components, scroll compressor 100 also includes an Oldham ring 7, balance weights 8a and 8b, and a subframe 9.

[0029] The sealed container 1 is a substantially airtight shell-shaped container that houses the compression mechanism 2, crankshaft 3, motor 4, and the like. Lubricating oil for lubricating the compression mechanism 2 and the bearings is enclosed in the sealed container 1 and stored as an oil reservoir R1 at the bottom of the sealed container 1. The sealed container 1 includes a cylindrical barrel chamber 1a, a cover chamber 1b that blocks the upper side of the barrel chamber 1a, and a bottom chamber 1c that blocks the lower side of the barrel chamber 1a.

[0030] An intake pipe P1 is inserted and fixed into the lid chamber 1b of the sealed container 1. The intake pipe P1 guides the refrigerant to the suction port J1 of the compression mechanism 2. Furthermore, a discharge pipe P2 is inserted and fixed into the cylinder chamber 1a of the sealed container 1. The discharge pipe P2 guides the refrigerant compressed in the compression mechanism 2 to the outside of the scroll compressor 100.

[0031] The compression mechanism 2 compresses the gaseous refrigerant 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 of the closed container 1.

[0032] The fixed scroll 21 is a component that forms the compression chamber S1 together with the orbiting scroll 22. The fixed scroll 21 is provided on the upper side of the frame 23 and is fastened to the frame 23 with bolts (not shown). Figure 1 As shown, the fixed scroll 21 includes a base plate 21 a and a fixed wrap plate 21 b .

[0033] The base plate 21a is a thick-walled component that is circular when viewed from above. Furthermore, to ensure an area S2 (the bottom portion of the fixed scroll plate 21b) where the orbiting scroll plate 22b orbits relative to the fixed scroll plate 21b, the area between the inner and outer lines of the fixed scroll plate 21b is recessed upward in a predetermined manner when viewed from above. Furthermore, the base plate 21a is provided with a suction port J1, into which refrigerant is introduced via a suction pipe P1.

[0034] The fixed scroll plate 21b is spiral (see also Figure 4 ), extending downward from the base plate 21a in the aforementioned region S2. Furthermore, the lower surface of the base plate 21a (the lower surface of the radially outer portion of the region S2) is substantially coplanar with the tooth tips of the fixed scroll plate 21b. Furthermore, the lower surface of the base plate 21a is referred to as the end plate surface 21f of the fixed scroll 21 (also see Figure 4 ). In addition to the annular back pressure groove G3 (see also Figure 4 ) is provided with an arc-shaped first groove G1 (see also Figure 4 ), the second groove G2 (see also Figure 4 ), which is described in detail below.

[0035] The orbiting scroll 22 is a member that forms a compression chamber S1 between the fixed scroll 21 and the orbiting scroll 22 by its movement (or rotation), and is provided between the fixed scroll 21 and the frame 23. The orbiting scroll 22 includes a circular end plate 22a, a spiral orbiting wrap plate 22b (also see FIG. Figure 3 ), and a cylindrical protrusion 22c that engages with the eccentric portion 3b of the crankshaft 3. Figure 1 As shown, the orbiting scroll plate 22b extends toward the upper side of the end plate 22a, while the boss 22c extends toward the lower side of the end plate 22a.

[0036] The revolving scroll plate 22b is a component that forms the compression chamber S1 together with the fixed scroll plate 21b. That is, the spiral fixed scroll plate 21b is meshed with the spiral revolving scroll plate 22b to form a plurality of compression chambers S1 between the fixed scroll plate 21b and the revolving scroll plate 22b. In addition, the compression chamber S1 is a space for compressing the gaseous refrigerant, and is formed on the outer line side and the inner line side of the revolving scroll plate 22b. In addition, 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 on the upper side of the compression mechanism 2.

[0037] The frame 23 supports the fixed scroll 21. The frame 23 has a substantially rotationally symmetrical shape and is fixed to the inner peripheral wall of the cylindrical chamber 1a of the closed container 1 by welding or the like. The frame 23 is provided with an insertion hole H1 through which the crankshaft 3 is inserted.

[0038] 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 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.

[0039] Furthermore, as the volume of the compression chamber S1 decreases and the gaseous refrigerant is compressed, a downward force is generated that tends to pull the orbiting scroll 22 away from the fixed scroll 21. If the orbiting scroll 22 is pulled away from the fixed scroll 21, the tooth tips of the fixed scroll plate 21b will separate from the orbiting scroll 22, and the tooth tips of the orbiting scroll plate 22b will separate from the fixed scroll 21, causing refrigerant to leak from the compression chamber S1, thereby reducing the efficiency of the scroll compressor 100.

[0040] To prevent the orbiting scroll 22 from being pulled away from the fixed scroll 21, a space (not shown) with a pressure substantially equal to the discharge pressure is provided near the center of the back side of the orbiting scroll 22 (radially inward of the protrusion 22c). This space also includes the aforementioned back-pressure chamber S4. Furthermore, the pressure in the back-pressure chamber S4 is typically set to a predetermined intermediate pressure between the suction pressure and the discharge pressure of the scroll compressor 100. This generates an upward force that appropriately presses the orbiting scroll 22 toward the fixed scroll 21.

[0041] 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 generally between the suction pressure and the discharge pressure, but may temporarily be approximately equal to the discharge pressure depending on the situation.

[0042] Figure 1 The crankshaft 3 (shaft) shown is a shaft that rotates integrally with the rotor 4b of the motor 4 and extends in the vertical direction. Figure 1 As shown, 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 member 3c provided at the lower end of the main shaft portion 3a.

[0043] The main shaft portion 3a is coaxially fixed 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 relative to the main shaft portion 3a and, as described above, engages with the boss 22c of the orbiting scroll 22. The eccentric rotation of the eccentric portion 3b causes the orbiting scroll 2 to orbit.

[0044] The oil supply member 3c is a portion that draws lubricating oil from the oil reservoir R1 of the sealed container 1 and is located at the lower end of the main shaft portion 3a. Alternatively, a positive displacement pump, a centrifugal pump, or the like may be provided in the oil supply member 3c. Furthermore, the crankshaft 3 has an oil supply passage 3d through which the lubricating oil flows. Furthermore, the lubricating oil stored in the sealed container 1 as the oil reservoir R1 rises through the oil supply passage 3d. Furthermore, the oil supply passage 3d branches in a predetermined manner to supply lubricating oil to the main bearing 5, slewing bearing 6, and other components described below.

[0045] The motor 4 is a driving source for rotating the crankshaft 3 and is provided between the frame 23 and the sub-frame 9. Figure 1 As shown, the motor 4 includes a stator 4a and a rotor 4b. The stator 4a is fixed to the inner circumferential wall of the cylindrical chamber 1a. The rotor 4b is rotatably arranged radially inward of the stator 4a. The crankshaft 3 is fixed to the rotor 4b by press-fitting or the like, coaxially with its central axis Z1.

[0046] The main bearing 5 rotatably supports the upper portion of the main shaft portion 3 a relative to the frame 23 , and is provided on a peripheral wall surface of a hole (not shown) in the frame 23 .

[0047] The orbiting bearing 6 rotatably supports the eccentric portion 3 b relative to the boss 22 c of the orbiting scroll 22 and is provided on the inner peripheral wall of the boss 22 c.

[0048] The Oldham ring 7 is an annular member that receives the eccentric rotation of the eccentric portion 3b and rotates the orbiting scroll 2 without rotating on its own. The Oldham ring 7 is mounted in a groove (not shown) provided on the lower surface of the orbiting scroll 22 and a groove (not shown) provided in the frame 23.

[0049] The balance weights 8a and 8b are components for suppressing vibration of the scroll compressor 100. Figure 1 In the example, one balance weight 8a is provided in the main shaft portion 3a and on the upper side of the rotor 4b, and another balance weight 8b is provided on the lower surface of the rotor 4b.

[0050] The sub-frame 9 is a member that rotatably supports the lower portion of the main shaft portion 3a. Figure 1 As shown, the subframe 9 is fixed to the sealed container 1 in a state of being arranged below the motor 4. The subframe 9 has a hole (not shown) through which the crankshaft 3 is inserted. A subbearing 9a is provided on the peripheral wall surface of the hole of the subframe 9.

[0051] When the crankshaft 3 rotates due to the drive of the electric motor 4, the revolving scroll 2 also rotates. In this way, the compression chamber S1 formed continuously shrinks, and the gaseous refrigerant is compressed. The compressed refrigerant is discharged to the space S3 on the upper side of the compression mechanism 2 through the discharge port J2 of the fixed scroll 21. The refrigerant discharged into the space S3 in this way is guided to the motor chamber S5 through the flow path (not shown) between the compression mechanism 2 and the closed container 1, and further discharged to the outside through the discharge pipe P2.

[0052] The lubricating oil stored as the oil reservoir R1 at the bottom of the sealed container 1 rises through the oil supply passage 3d of the crankshaft 3 to lubricate the auxiliary bearing 9a, the main bearing 5, the rotary bearing 6, etc. The lubricating oil reaching the opening (not shown) at the upper end of the oil supply passage 3d is guided to the communication hole H2 of the rotary scroll 22 described below (see also FIG. Figure 2 Next, the detailed structures of the fixed scroll 21 and the orbiting scroll 22 will be described, and the flow of lubricating oil will also be described.

[0053] Figure 2 It is a longitudinal sectional view of the orbiting scroll 22 included in the scroll compressor.

[0054] like Figure 2 As shown in FIG. 2 , a communication hole H2 is provided in the end plate 22a of the orbiting scroll 22 in a lateral direction (in a direction parallel to the upper and lower surfaces of the end plate 22a). Figure 2In the example shown in FIG. 2 , the communicating holes H2 are provided in the radial direction of the disk-shaped end plate 22 a . However, the communicating holes H2 may be provided in the lateral direction and in a direction different from the radial direction.

[0055] The communicating hole H2 is a hole for connecting the oil supply passage 3d (see Figure 1 ) The high-pressure lubricating oil flowing is guided to the fixed scroll 21 (refer to Figure 1 The communication hole H2 is formed by, for example, performing predetermined cutting work on the circumferential wall surface of the end plate 22a inward in the radial direction. Figure 2 The sealing plug N1 shown is a component that seals the end portion of the outer peripheral side of the communicating hole H2. Figure 2 As shown, the upstream side (radially inner side) of the communication hole H2 communicates with the radially inner space of the protrusion 22c via a short flow path H3 in the vertical direction. In addition, the downstream side (radially outer side) of the communication hole H2 communicates with the second hole H5 in addition to the first hole H4.

[0056] The first hole H4 is used to guide the high-pressure lubricating oil to the arc-shaped first groove G1 (see Figure 4 The second hole H5 is to guide the high-pressure lubricating oil to the arc-shaped second groove G2 (refer to Figure 4 ) of the flow path, and is provided in the vertical direction. Figure 1 ) A portion of the lubricating oil that flows out passes through Figure 2 The flow path H3, the communicating hole H2, and the first hole H4 shown are guided to the first groove G1 (see Figure 4 ), and is also guided to the second groove G2 (refer to Figure 4 ). That is, the communication hole H2 is connected to the oil supply passage 3d and is connected to both the first hole H4 and the second hole H5. In addition, the second hole H5 is provided radially outward of the first hole H4.

[0057] Figure 3 It is a perspective view of the orbiting scroll 22 included in the scroll compressor.

[0058] As described above, the orbiting scroll 22 includes a circular end plate 22a, a spiral orbiting volute 22b, and a cylindrical boss 22c. Figure 2 ) and the second hole H5 (refer to Figure 2 ) The corresponding portion is provided with a sealing plug N1 for sealing the end portion of the outer peripheral side of the communicating hole H2. In addition, an opening J4 of the first hole H4 and an opening J5 of the second hole H5 are provided on the upper surface of the end plate 22a. Figure 3As shown, the opening J5 of the second hole H5 is located radially outward from 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.

[0059] As described above, the back pressure chamber S4 (see Figure 1 ) pushes the orbiting scroll 22 toward the fixed scroll 21 due to the back pressure of the fixed scroll 21. However, for example, under high compression ratio operating conditions, if the force pushing the orbiting scroll 22 toward the fixed scroll 21 becomes too large, there is a possibility of increased friction loss and heat sticking on the sliding surface between the fixed scroll 21 and the orbiting scroll 22. Therefore, the end plate surface 21f of the fixed scroll 21 (see Figure 4 ) and an annular back pressure groove G3 (see Figure 4 ), the arc-shaped first groove G1 (refer to Figure 4 ). When the orbiting scroll 22 swings, the end plate surface 21f of the fixed scroll 21 (see Figure 4 ) Set the arc-shaped second groove G2 (refer to Figure 4 ), but this is explained in detail below.

[0060] Figure 4 It is a bottom view of the fixed scroll 21 included in the scroll compressor.

[0061] As described above, the fixed scroll 21 is constructed by providing a spiral fixed scroll plate 21b on a base plate 21a. Figure 4 As shown, an annular back pressure groove G3 is provided near the periphery of the end plate surface 21f of the fixed scroll 21. The back pressure groove G3 is located at the orbiting scroll 22 (refer to Figure 1 ) and frame 23 (refer to Figure 1 ) between the back pressure chamber S4 (refer to Figure 1 ) connected to the groove. Figure 4 In the example of FIG, 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 a reference (the center of the circle).

[0062] Furthermore, in the orbiting scroll 22 (refer to Figure 1 ) during the rotation of the orbiting scroll 22, the lubricating oil having a pressure substantially equal to that of the back pressure chamber S4 is guided to the back pressure groove G3. More specifically, the lubricating oil enters the annular back pressure groove G3 and the end plate 22a of the orbiting scroll 22 (see Figure 1 ) between the upper surfaces of the rotating scroll 22 and the fixed scroll 21. In addition to preventing the force of the rotating scroll 22 from pushing up the fixed scroll 21 from becoming too large, the lubricating oil in the back pressure groove G3 also acts as a seal, thereby preventing the compressed refrigerant from leaking out of the space S3 (see Figure 1 ) inflow.

[0063] like Figure 4 As shown, the first groove G1 and the second groove G2 are provided on the end plate surface 21f of the fixed scroll 21. The first groove G1 and the second groove G2 are provided radially inward of the annular back pressure groove G3, and are formed into a predetermined arc shape with the vicinity of the center of the back pressure groove G3 as a reference (the center of the arc). On the other hand, as described above, the orbiting scroll 22 (refer to Figure 2 ) is provided with an oil supply passage 3d (refer to Figure 1 ) is guided to the first hole H4 on the end plate surface 21f side of the fixed scroll 21 (see Figure 2 ) and the second hole H5 (refer to Figure 2 ).

[0064] Figure 4 The first groove G1 shown is associated with the orbiting scroll 22 (see Figure 1 ) moves (rotates) and the first hole H4 (refer to Figure 2 ) is a groove intermittently connected. The first groove G1 is provided so as to include, for example, the end plate 22a (refer to FIG. 2 ) of the orbiting scroll 22 when a force (the resultant force of centrifugal force and gas load) that causes the orbiting scroll 22 to tilt relative to the end plate surface 21f of the fixed scroll 21 acts. Figure 1 ) is the area where the first groove G1 most strongly contacts the end plate surface 21f of the fixed scroll 21 (also referred to as the eccentric load area). Specifically, the first groove G1 is formed into an arc shape with a central angle of 90° to 180°, with the vicinity of the center of the circular end plate surface 21f as the reference (the center of the circle). Alternatively, the eccentric load area may be located near the circumferential center of the first groove G1.

[0065] Furthermore, along with the orbiting scroll 22 (see Figure 1 ) moves, the first groove G1 and the first hole H4 (refer to Figure 2 ) is intermittently connected, and the high-pressure lubricating oil having a discharge pressure substantially equal to that of the first groove G1 is guided. As a result, the high-pressure lubricating oil enters the end plate 22a of the orbiting scroll 22 (see Figure 1 ) easily and strongly with the end plate surface 21f of the fixed scroll 21 (refer to Figure 1 As a result, a force that pulls the orbiting scroll 22 away from the fixed scroll 21 acts in the first groove G1, thereby preventing the thrust load (pressing force) from one side of the orbiting scroll 22 and the fixed scroll 21 from becoming excessive.

[0066] Figure 4 The second groove G2 shown is associated with the orbiting scroll 22 (see Figure 1 ) moves (rotates) and the second hole H5 (refer to Figure 2As described above, the first groove G1 and the back pressure groove G3 are provided on the end plate surface 21f of the fixed scroll 21 to control the thrust load from one side to the other side of the fixed scroll 21 and the orbiting scroll 22 within an appropriate range. However, it is sometimes difficult to prevent the orbiting scroll 22 from swinging under all operating conditions.

[0067] Therefore, in the first embodiment, when the orbiting scroll 22 swings, the high-pressure lubricating oil in the second groove G2 flows to the back-pressure chamber S4 (see FIG. 1 ) via the annular back-pressure groove G3. Figure 1 ) flows in. This causes high-pressure lubricating oil, equal to the discharge pressure, to flow into the back-pressure chamber S4, temporarily increasing the pressure in the back-pressure chamber S4. As a result, the force pushing up the orbiting scroll 22 against the fixed scroll 21 increases, thereby suppressing the oscillation of the orbiting scroll 22.

[0068] exist Figure 4 In the example of the embodiment, 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 (the 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. Thus, one of the main features of the first embodiment is that the second groove G2, which is separated from the first groove G1, is provided radially outward relative to the first groove G1. In addition, the "distance" between the second groove G2 and the back-pressure groove G3 refers to the length of the shortest line segment connecting the second groove G2 and the back-pressure groove G3 (the same applies to other distances such as L1a).

[0069] As described above, since the distance between the second groove G2 and the back-pressure groove G3 is short, when the orbiting scroll 22 swings and tilts, the high-pressure lubricating oil in the second groove G2 generally 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. Since the high-pressure lubricating oil flows into the back-pressure groove G3, the back-pressure chamber S4 (see Figure 1 ) temporarily increases, thereby suppressing the swinging of the orbiting scroll 22.

[0070] 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. Thus, since the distance between the inner edge 21fa of the end plate surface 21f and the first groove G1 is shorter, the end plate surface 21f of the fixed scroll 21 and the end plate 22a of the orbiting scroll 22 (see FIG. Figure 1 ) between the small gap, moderately to the compression chamber S1 (refer to Figure 1 ) supplies high pressure lubricating oil existing in the first groove G1. Thus, the fixed scroll plate 21b is lubricated (see Figure 1 )、Revolving scroll plate 22b (refer to Figure 1 ), thereby suppressing wear and seizure. Furthermore, the high-pressure lubricating oil in the arcuate first groove G1 also acts as a seal between the fixed scroll 21 and the orbiting scroll 22, thereby achieving high efficiency in the scroll compressor 100. Furthermore, during refrigerant compression, the pressure in the compression chamber S1 is lower than the discharge pressure (the pressure of the lubricating oil in the first groove G1) and lower than the pressure in the back-pressure chamber S4.

[0071] Next, the circumferential length of the second groove G2 will be described. Figure 4 As shown, the circumferential length of the arcuate second groove G2 is preferably shorter than the circumferential length of the arcuate first groove G1. This structure prevents excessive flow of high-pressure lubricating oil into the second groove G2, thereby appropriately suppressing the force that attempts to separate the orbiting scroll 22 from the fixed scroll 21. Furthermore, the circumferential length of the arcuate second groove G2 is preferably shorter than half the circumferential length of the arcuate first groove G1. This structure appropriately reduces the amount of high-pressure lubricating oil present in the second groove G2.

[0072] Furthermore, the center angle θ1 of the arc-shaped second groove G2 (the center angle of the imaginary fan with the center of the base plate 21a as the reference) is preferably 10° or more and 30° or less. According to such a structure, the second groove G2 and the end plate 22a of the orbiting scroll 22 (see FIG. 21 ) can be appropriately suppressed. Figure 1 ) between the arc-shaped gap volume. Therefore, it is possible to suppress the force that is intended to pull the orbiting scroll 22 away from the fixed scroll 21 from becoming excessive.

[0073] Furthermore, the first groove G1 and the second groove G2 at least partially overlap in diameter. Figure 4 In the example of , substantially the entire area of ​​the second groove G2 overlaps with the first groove G1 in the radial direction. Figure 5 The reason for such a structure is explained in the partially enlarged view.

[0074] Figure 5 It is a local magnification Figure 4 The diagram is an explanatory diagram showing a movement trajectory M4 of the opening J4 of the first hole and a movement trajectory M5 of the opening J5 of the second hole in the area K1.

[0075] also, Figure 5 The first hole H4 (see Figure 2 ) of the opening J4 is shown by a dot-dash line, and the second hole H5 (refer to Figure 2 )'s movement trajectory M5 of the opening J5 is shown by a dotted line.

[0076] As described above, the oil supply passage 3d from the crankshaft 3 (see Figure 1 ) of high pressure lubricating oil through the first hole H4 (refer to Figure 2 ) is intermittently supplied to the first groove G1. Also, the oil supply passage 3d (refer to Figure 1 ) of high pressure lubricating oil through the second hole H5 (refer to Figure 2 ) is intermittently supplied to the second tank G2.

[0077] exist Figure 5 In the example of the orbiting scroll 22 (refer to Figure 2 ) rotation, the first hole H4 (refer to Figure 2 ) moves along the circular trajectory M4 and before returning to its original position, the first hole H4 communicates with the first groove G1 twice. Thus, an appropriate amount of lubricating oil is supplied to the first groove G1 through the first hole H4. Similarly, the second hole H5 (refer to Figure 2 ) moves along the circular movement trajectory M5 and before returning to its original position, the second hole H5 communicates with the second groove G2 twice. As a result, an appropriate amount of lubricating oil is supplied to the second groove G2 through the second hole H5.

[0078] Furthermore, the high-pressure lubricating oil supplied to the first groove G1 and the second groove G2 does not remain in the first groove G1 and the second groove G2, but flows through the end plate surface 21f of the fixed scroll 21 and the orbiting scroll 22 (see FIG. Figure 1 ) flows out through the tiny gap between the end plates 22a. Therefore, as described above, lubricating oil is supplied twice in each movement of the openings J4 and J5. In addition, by making the distance between the second groove G2 and the back pressure groove G3 narrow, it is easy to flow from the second groove G2 to the back pressure chamber S4 (see FIG. 1 ) via the back pressure groove G3 during normal operation. Figure 1 ) lubricating oil is supplied. Thus, the European ring 7 and the like provided in the back pressure chamber S4 can be fully lubricated (see Figure 1 ).

[0079] exist Figure 5 In the example shown, the circumferential length of the arcuate second groove G2 is longer than the diameter of the circular trajectory M5 of the opening J5 of the second hole H5. Furthermore, the arcuate second groove G2 intersects with the circular trajectory M5 of the opening J5 of the second hole H5 at two locations. With this structure, lubricating oil is supplied twice per movement of the opening J5, allowing a sufficient amount of lubricating oil to be supplied to the second groove G2 of the fixed scroll 21, compared to a case where lubricating oil is supplied only once.

[0080] Furthermore, as described above, the second groove G2 overlaps with the first groove G1 in the radial direction. Thus, the first hole H4 intermittently communicating with the first groove G1 and the second hole H5 intermittently communicating with the second groove G2 can be formed in a manner arranged in the radial direction (see also Figure 2 、 Figure 3 As a result, the oil supply passage 3d of the crankshaft 3 (see Figure 1 ) to the first hole H4 (refer to Figure 2 ) and the second hole H5 (refer to Figure 2 ) respectively guide the lubricating oil through the connecting hole H2 (refer to Figure 2 Therefore, it is possible to reduce the labor and time required for forming the communication hole H2 in the orbiting scroll 22 by cutting or the like.

[0081] Furthermore, since the second groove G2 overlaps the first groove G1 in the radial direction, the high-pressure lubricating oil in one of the first groove G1 and the second groove G2 acts like a wall against the high-pressure lubricating oil in the other. As a result, it is easier to flow into the compression chamber S1 (see FIG. 1 ) than the back pressure groove G3. Figure 1 ) supplies high pressure lubricating oil to the first groove G1. On the other hand, compared to the compression chamber S1 (refer to Figure 1 ) It is easier to supply the high-pressure lubricating oil in the second groove G1 to the back pressure groove G3.

[0082] also, Figure 4 While the example in which the second groove G2 is provided circumferentially near one end of the first groove G1 (the end on the suction port J1 side) is shown, the present invention is not limited to this. For example, the second groove G2 may be provided circumferentially near the end opposite the first groove G1, or near the circumferential center of the first groove G1. In either case, when the orbiting scroll 22 oscillates and tilts, high-pressure lubricating oil is supplied from the second groove G2 to the back-pressure groove G3.

[0083] <Effect>

[0084] According to the first embodiment, the arc-shaped first groove G1 (see Figure 4 ) High-pressure lubricating oil is supplied. This can prevent the end plate 22a of the orbiting scroll 22 from strongly contacting the fixed scroll 21 near the first groove G1.

[0085] Furthermore, the distance L2a between the second groove G2 and the back pressure groove G3 (see Figure 4 ) is greater than the distance L1a between the first groove G1 and the back pressure groove G3 (refer to Figure 4 Thus, even when the orbiting scroll 22 swings and tilts, the back pressure chamber S4 (see FIG. Figure 1) supplies high-pressure lubricating oil. As a result, the pressure in the back-pressure chamber S4 temporarily increases, quickly suppressing the swinging of the orbiting scroll 22 and restoring the compressor to a proper operating state. In other words, the reduction in efficiency associated with the overturning of the orbiting scroll 22 can be prevented. This ensures both the reliability of the scroll compressor 100 and improved performance (higher efficiency) across a wide range of operating conditions.

[0086] Furthermore, since the first groove G1 and the second groove G2 at least partially overlap in the radial direction, a communicating hole 2 communicating with both the first hole H4 and the second hole H5 can be provided (see FIG. Figure 2 That is, the connecting hole H2 (see FIG. 1 ) guides high-pressure lubricating oil from the oil supply passage 3d of the crankshaft 3 to the first hole H4 and the second hole H5. Figure 2 Therefore, the workload and time of forming the communicating hole H2 by cutting or the like can be reduced, thereby reducing the manufacturing cost of the scroll compressor 100.

[0087] Second Implementation Method

[0088] The second embodiment is different from the first embodiment in that the fixed scroll 21A (see Figure 6 ) is provided on the end plate surface 21f with a second hole H5 (refer to Figure 2 ) opening J5 (refer to Figure 2 ) is always connected to the recess E2 (refer to Figure 6 ), this point. In addition, other structures (the overall structure of the scroll compressor 100, etc.: refer to Figure 1 ) is the same as the first embodiment. Therefore, the parts different from the first embodiment will be described, and the description of the overlapping parts will be omitted.

[0089] Figure 6 It is a bottom view of the fixed scroll 21A included in the scroll compressor according to the second embodiment.

[0090] like Figure 6 As shown, a recess E2 communicating with the second groove GA2 is provided on the end plate surface 21f of the fixed scroll 21A and radially outside the first groove G1. In addition, the circumferential length of the second groove GA2 is longer than that of the first embodiment (see Figure 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 of the first embodiment.

[0091] exist Figure 6 In the example, a recess E2 is provided at one end side (the end side closer to the suction port J1) of the arc-shaped second groove GA2. The recess E2 is aligned with the orbiting scroll 22 (see Figure 2 ) of the second hole H5 (refer to Figure 2 The recess E2 is recessed upward from the end plate surface 21f and is circular when viewed from above.

[0092] In addition, the circumferential position of the recess E2 is not limited to Figure 6 As described below, if the second hole H5 (refer to Figure 2 ) of the circular movement trajectory M5 of the opening J5 (refer to Figure 7 ) is included in the region S6 of the recess E2 (refer to Figure 7 ), a recess E2 may be provided on the other end side of the second groove GA2, and a recess E2 may be provided near the circumferential center of the second groove GA2. In addition to the second groove GA2, the circular recess E2 also overlaps with the first groove G1 in the radial direction. Figure 7 The reason for adopting such an arrangement will be described.

[0093] Figure 7 It is a local magnification Figure 6 The diagram is an explanatory diagram showing a movement trajectory M4 of the opening J4 of the first hole and a movement trajectory M5 of the opening J5 of the second hole.

[0094] like Figure 7 As shown, the second hole H5 (see Figure 2 ) The movement trajectory M5 of the opening J5 is included in the area S6 of the recess E2. Figure 7 In the example, the first hole H4 (refer to Figure 2 ) and a movement trajectory M4 of the opening J4 partially overlaps with the first groove G1 and is not included in the area S6 of the recess E2.

[0095] According to such a structure, the orbiting scroll 22 (refer to Figure 2 ) moves (rotates), the second hole H5 (refer to Figure 2 ) is always connected to the recess E2 and the second groove GA2. Thus, the amount of high-pressure lubricating oil supplied to the recess E2 and the second groove GA2 per unit time can be increased compared to the first embodiment.

[0096] <Effect>

[0097] According to the second embodiment, during the operation of the scroll compressor, the second hole H5 is always in communication with the recess E2 and the second groove GA2. Figure 1 ) swings and tilts, it is possible to make the back pressure groove G3 (refer to Figure 6 ) flows into the back pressure chamber S4 (refer to Figure 1 ) of the high-pressure lubricating oil is greater than that of the first embodiment, thereby enabling the orbiting scroll 22 (refer to Figure 1) quickly return to its proper state.

[0098] Third Implementation Method

[0099] The third embodiment differs from the second embodiment in that a fixed scroll 21B (see Figure 8 ) of the end plate surface 21f of the recessed portion E3 (refer to Figure 9 ) and the second hole H5 (refer to Figure 2 ) opening J5 (refer to Figure 9 ) is intermittently connected and is also connected to the first hole H4 (refer to Figure 2 ) opening J4 (refer to Figure 9 ) is intermittently connected. In addition, the other structures are the same as those of the second embodiment. Therefore, the parts different from the second embodiment are described, and the description of the repeated parts is omitted.

[0100] Figure 8 It is a bottom view of the fixed scroll 21B included in the scroll compressor according to the third embodiment.

[0101] like Figure 8 As shown, a recess E3 communicating with the second groove GB2 is provided on the end plate surface 21f of the fixed scroll 21B and on the radially outer side of the fixed scroll plate 21b. In addition, the distance between the recess E3 and the first groove G1 is greater than that of the second embodiment (see Figure 6 ) is shorter. Also, the diameter of the circular recess E3 is smaller than that of the second embodiment (refer to Figure 6 Furthermore, in addition to the second groove GB2, the circular recess E3 also overlaps with the first groove G1 in the radial direction.

[0102] Figure 9 It is a local magnification Figure 8 The diagram is an explanatory diagram showing the movement trajectory M4 of the opening J4 of the first hole and the movement trajectory M5 of the opening J5 of the second hole.

[0103] like Figure 9 As shown, on the end plate surface 21f of the fixed scroll 21B, the second hole H5 (refer to Figure 2 ) is included in the region S7 of the recess E3. On the other hand, the second hole H5 (refer to Figure 2 ) The remaining portion of the movement trajectory M5 of the opening J5 is separated from the area S7 of the recess E3. Due to space limitations, it is difficult to achieve the always connected structure of the second embodiment (the structure in which the opening J5 and the recess E2 are always connected: refer to Figure 7 ) can also become Figure 9 structure.

[0104] Furthermore, the first hole H4 (see Figure 2 ) is also included in the area S7 of the recess E3. According to such a structure, in addition to the movement trajectory M4 of the opening J4 through the second hole H5 (refer to Figure 2 ) intermittently supplies high-pressure lubricating oil to the recess E3, and also supplies lubricating oil to the recess E3 through the first hole H4 (see Figure 2 ) intermittently supplies high-pressure lubricating oil to the recess E3. Figure 2 ) in a structure in which the movement trajectory M5 of the opening J5 is partially separated from the region S7 of the recess E3, the amount of high-pressure lubricating oil supplied to the recess E3 and the second groove GB2 per unit time can be sufficiently ensured.

[0105] <Effect>

[0106] According to the third embodiment, in the driving of the scroll compressor, in addition to the second hole H5 (refer to Figure 2 ) and recess E3 (refer to Figure 9 ) is intermittently connected, the first hole H4 (refer to Figure 2 ) is also intermittently connected to the recess E3. Therefore, in the orbiting scroll 22 (refer to Figure 1 ) swings and tilts, it is possible to make the back pressure groove G3 (refer to Figure 8 ) flows into the back pressure chamber S4 (refer to Figure 1 ) of the high-pressure lubricating oil is greater than that of the first embodiment, thereby enabling the orbiting scroll 22 (refer to Figure 1 ) quickly return to its proper state.

[0107] Fourth Implementation Method

[0108] In the fourth embodiment, the scroll compressor 100 (see FIG. Figure 1 ) of air conditioner W1 (refrigeration cycle device: refer to Figure 10 ) for explanation.

[0109] Figure 10 This is a configuration diagram including a refrigerant circuit Q1 of an air conditioner W1 according to a fourth embodiment.

[0110] also, Figure 10 The solid arrows indicate the flow of the refrigerant during the heating operation.

[0111] on the other hand, Figure 10 The dotted arrows indicate the flow of the refrigerant during cooling operation.

[0112] The air conditioner W1 is a device that performs air conditioning such as cooling and heating. Figure 10As shown, 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 .

[0113] exist Figure 10 In the example of FIG, 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. On the other hand, the indoor heat exchanger 75 and the indoor fan 76 are provided in the indoor unit U2.

[0114] The scroll compressor 100 is a device for compressing gaseous refrigerant, and has, for example, the same Figure 1 )Same structure.

[0115] The outdoor heat exchanger 71 is a heat exchanger that exchanges heat between the refrigerant flowing through a heat transfer pipe (not shown) thereof and the outside air blown in by the outdoor fan 72 .

[0116] The outdoor fan 72 is a fan that blows outside air into the outdoor heat exchanger 71. The outdoor fan 72 includes an outdoor fan motor 72a as a driving source, and is provided near the outdoor heat exchanger 71.

[0117] The indoor heat exchanger 75 is a heat exchanger that exchanges heat between the refrigerant flowing through a heat transfer pipe (not shown) thereof and the indoor air (air in the air-conditioned room) blown in by the indoor fan 76 .

[0118] The indoor fan 76 is a fan that blows indoor air into the indoor heat exchanger 75. The indoor fan 76 includes an indoor fan motor 76a as a driving source, and is provided near the indoor heat exchanger 75.

[0119] The expansion valve 73 is a valve that reduces the pressure of the refrigerant condensed by 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 directed to the "evaporator" (the other of the outdoor heat exchanger 71 and the indoor heat exchanger 75).

[0120] The four-way valve 74 is a valve that switches the flow path of the refrigerant according to the operation mode of the air conditioner W1. Figure 10 In the refrigerant circuit Q1, 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). Figure 10 ), in the refrigerant circuit Q1, 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).

[0121] <Effect>

[0122] According to the fourth embodiment, the air conditioner W1 includes a scroll compressor 100 having high performance and reliability at low manufacturing cost. This can reduce the overall manufacturing cost of the air conditioner W1 and improve its performance and reliability.

[0123] Modification

[0124] As mentioned above, the scroll compressor 100 and the air conditioner W1 of the present invention have been described in each embodiment. However, the present invention is not limited to the above description, and various modifications are possible.

[0125] For example, in each embodiment, the second groove G2 (see Figure 4 ) is radially aligned with the first groove G1 (see Figure 4 ) is described above, but the present invention is not limited to this. That is, a structure in which the first groove G1 and the second groove G2 at least partially overlap in the radial direction may also be adopted.

[0126] Furthermore, in each embodiment, the first hole H4 (see Figure 2 ) of the opening J4 of the moving track M4 (refer to Figure 5 ) is included in the first groove G1, but it is not limited to this. That is, it can also be the first hole H4 (refer to Figure 2 ) of the opening J4 of the moving track M4 (refer to Figure 5 ) is included in the first groove G1. In this case, a circular recess (not shown) communicating with the first hole H4 may be provided. The first hole H4 (see Figure 2 ) is included in the concave portion. That is, the first groove G1 may also include at least a portion of the movement trajectory M4 of the opening J4 of the first hole H4. Similarly, the second groove G2 may also include the second hole H5 (refer to Figure 2 ) at least a portion of the movement trajectory M5 of the opening J5.

[0127] Furthermore, in each embodiment, the second groove G2 (see Figure 4 While the number of second grooves G2 is described as one, the present invention is not limited thereto. For example, a plurality of second grooves G2 may be provided, each having a substantially equal radial distance from the back-pressure groove G3. In this case, a plurality of second holes H5 may be provided in association with the plurality of second grooves G2, and a single second hole H5 may alternately communicate with the plurality of second grooves G2.

[0128] Furthermore, in the third embodiment, the second hole H5 (see Figure 2 ) of the opening J5 of the moving track M5 (refer to Figure 9) is contained in the recess E3 (refer to Figure 9 ) and the first hole H4 (refer to Figure 2 ) of the opening J4 of the moving track M4 (refer to Figure 9 While a configuration has been described in which a portion of the second groove G2 is contained within the recess E3, the present invention is not limited thereto. For example, the recess E3 may not be specifically provided, and the following configuration may be employed. Specifically, the second groove G2 may contain at least a portion of the movement trajectory M5 of the opening J5 of the second hole H5 and also contain at least a portion of the movement trajectory M4 of the opening J4 of the first hole H4. Even with such a configuration, a sufficient amount of lubricating oil can be supplied to the second groove G2.

[0129] Furthermore, as described in the first embodiment, the first groove G1 (see Figure 5 ) includes the first hole H4 (refer to Figure 2 ) of the opening J4 of the moving track M4 (refer to Figure 5 ) without including at least a portion of the second hole H5 (refer to Figure 2 ) of the opening J5 of the moving track M5 (refer to Figure 5 In such a structure, when the orbiting scroll 22 swings and tilts, the back pressure chamber S4 (see FIG. 1 ) can be fed from the second groove G2 via the back pressure groove G3. Figure 1 ) supplies high-pressure lubricating oil, thereby suppressing the orbiting scroll 22 (refer to Figure 1 ) swing.

[0130] Furthermore, each embodiment can be combined appropriately. For example, the second embodiment and the fourth embodiment can be combined to form the following structure. That is, the air conditioner can also be configured as follows: having a second hole H5 (see Figure 2 ) is always connected to the recess E2 (refer to Figure 7 ) of the scroll compressor (second embodiment), and equipped with an outdoor heat exchanger 71 (see Figure 10 ), the expansion valve 73, the indoor heat exchanger 75, etc. (fourth embodiment). In addition, the third embodiment and the fourth embodiment can also be combined.

[0131] Furthermore, the air conditioner W1 described in the fourth embodiment (see Figure 10 ) can be applied not only to room air conditioners and package air conditioners, but also to various types of air conditioners such as multi-split air conditioners for buildings. Furthermore, while the fourth embodiment describes an air conditioner W1 (refrigeration cycle device) equipped with a scroll compressor 100, the present invention is not limited thereto. For example, the fourth embodiment can also be applied to other "refrigeration cycle devices" such as freezers, water heaters, air conditioners and hot water supply devices, coolers, and refrigerators.

[0132] Furthermore, in each embodiment, the case where the scroll compressor 100 compresses the refrigerant is described, but the present invention is not limited thereto. That is, each embodiment is also applicable when the scroll compressor 100 compresses a predetermined gas other than the refrigerant.

[0133] Furthermore, each embodiment is described in detail to explain the present invention in an easy-to-understand manner, and is not necessarily limited to having all the structures described. Furthermore, other structures may be added, deleted, or replaced as appropriate for a portion of the structure of each embodiment.

[0134] Furthermore, the above-mentioned mechanisms and structures are those considered necessary for the description, and are not necessarily all necessary to show in terms of the product.

Claims

1. A scroll compressor, characterized in that: have: 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 scroll plate; an orbiting scroll having a spiral orbiting scroll plate, wherein a compression chamber is formed between the fixed scroll plate and the orbiting scroll plate; and A frame having a through hole for the shaft and supporting the fixed scroll. A back pressure chamber is provided between the revolving scroll and the frame. An annular back pressure groove communicating with the back pressure chamber is provided on the end plate surface of the fixed scroll, and an arc-shaped first groove and an arc-shaped second groove are provided radially inwardly of the back pressure groove. The distance between the second groove and the back pressure groove is shorter than the distance between the first groove and the back pressure groove. The orbiting scroll is provided with a first hole and a second hole for guiding lubricating oil from the oil supply passage to the end plate surface side of the fixed scroll. The first groove includes at least a portion of the movement trajectory of the opening of the first hole. The second groove includes at least a portion of the movement trajectory of the opening of the second hole. The first groove and the second groove at least partially overlap in the radial direction.

2. A scroll compressor, characterized in that: have: 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 scroll plate; an orbiting scroll having a spiral orbiting scroll plate, wherein a compression chamber is formed between the fixed scroll plate and the orbiting scroll plate; and A frame having a through hole for the shaft and supporting the fixed scroll. A back pressure chamber is provided between the revolving scroll and the frame. An annular back pressure groove communicating with the back pressure chamber is provided on the end plate surface of the fixed scroll, and an arc-shaped first groove and an arc-shaped second groove are provided radially inwardly of the back pressure groove. The distance between the second groove and the back pressure groove is shorter than the distance between the first groove and the back pressure groove. The orbiting scroll is provided with a first hole and a second hole for guiding lubricating oil from the oil supply passage to the end plate surface side of the fixed scroll. The first groove includes at least a portion of the movement trajectory of the opening of the first hole. The second groove includes at least a portion of the movement trajectory of the opening of the second hole. The orbiting scroll is provided with a communication hole that communicates with the oil supply passage and communicates with both the first hole and the second hole.

3. The scroll compressor according to claim 1 or 2, characterized in that: The circumferential length of the arc-shaped second groove is shorter than the circumferential length of the arc-shaped first groove.

4. The scroll compressor according to claim 1 or 2, characterized in that: The circumferential length of the arc-shaped second groove is longer than the diameter of the circular movement trajectory of the opening of the second hole. The arc-shaped second groove intersects the circular movement trajectory of the opening of the second hole at two locations.

5. The scroll compressor according to claim 1 or 2, characterized in that: The central angle of the arc-shaped second groove is greater than or equal to 10° and less than or equal to 30°.

6. The scroll compressor according to claim 1 or 2, characterized in that: The end plate surface of the fixed scroll is provided with a recessed portion communicating with the second groove. The region of the recess includes a movement trajectory of the opening of the second hole.

7. The scroll compressor according to claim 1 or 2, characterized in that: The end plate surface of the fixed scroll is provided with a recessed portion communicating with the second groove. The region of the recess includes a portion of a movement trajectory of the opening of the second hole, and also includes a portion of a movement trajectory of the opening of the first hole.

8. The scroll compressor according to claim 1 or 2, characterized in that: The second groove includes at least a portion of a movement trajectory of the opening of the second hole, and also includes at least a portion of a movement trajectory of the opening of the first hole.

9. The scroll compressor according to claim 1 or 2, characterized in that: The first groove includes at least a portion of a movement trajectory of the opening of the first hole, but does not include a movement trajectory of the opening of the second hole.

10. A refrigeration cycle device, characterized in that: A scroll compressor according to any one of claims 1 to 9, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger.

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