Scroll compressor

Abstract

To ensure the reliability of a scroll compressor without making the scroll compressor large, a stable throttling effect is obtained in an oil passage. An oil passage (80) extends in a circumferential direction in a first seal portion (71) and is bent radially at a connecting portion of the first seal portion (71) to a second seal portion (72). Thus, pressure loss of oil flowing in the oil passage (80) is generated. Therefore, it is not necessary to, for example, extend the oil passage (80) in order to obtain a stable throttling effect in the oil passage (80), and it is also not necessary to reduce the flow cross-sectional area of the oil passage (80).

Description

Technical Field

[0001] This invention relates to scroll compressors. Background Technology

[0002] For example, as disclosed in Patent Document 1, a scroll compressor has a compression mechanism consisting of a fixed scroll and a rotating scroll. The scroll compressor has a housing that houses the compression mechanism. The scroll compressor also has a discharge housing, which is part of the housing. The discharge housing divides the discharge chamber and the oil reservoir into a discharge chamber by engaging with the fixed scroll. Refrigerant compressed by the compression mechanism is discharged into the discharge chamber. The oil reservoir stores oil separated from the refrigerant in the discharge chamber. The scroll compressor has a gasket. The gasket is in close contact with the mating surface between the fixed scroll and the discharge housing. Furthermore, the scroll compressor has an oil passage. The oil passage allows oil in the oil reservoir to flow to the compression mechanism.

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: Japanese Patent Application Publication No. 2020-165362 Summary of the Invention

[0006] The problem that the invention aims to solve

[0007] In such scroll compressors, increasing the throttling flow rate of the oil passage is desirable in order to ensure a stable flow of oil from the oil reservoir to the compression mechanism. However, if the oil passage is lengthened, for example, to increase the throttling flow rate, the compressor itself will become larger. Furthermore, if the cross-sectional area of ​​the oil passage is reduced, for example, to increase the throttling flow rate, foreign objects may easily clog the oil passage, potentially reducing the reliability of the scroll compressor. Therefore, a technical solution is desired that achieves a stable throttling effect in the oil passage without increasing the size of the scroll compressor while ensuring its reliability.

[0008] Technical solutions for solving the problem

[0009] A scroll compressor that solves the above-mentioned problems includes: a compression mechanism consisting of a fixed scroll and a rotating scroll; a housing housing the compression mechanism; a discharge housing, which is part of the housing and divides a discharge chamber and an oil reservoir by its engagement with the fixed scroll, wherein refrigerant compressed by the compression mechanism is discharged into the discharge chamber, and the oil reservoir stores oil separated from the refrigerant in the discharge chamber; a sealing gasket tightly attached to the mating surface of the fixed scroll and the discharge housing; and an oil passage that allows oil in the oil reservoir to flow to the compression mechanism, wherein at least one of the discharge housing and the fixed scroll... One side has a partition wall that divides the discharge chamber and the oil storage chamber. The sealing gasket has an annular first sealing portion that surrounds the discharge chamber and the oil storage chamber and seals to the outside, and a second sealing portion that is in close contact with the partition wall and seals between the discharge chamber and the oil storage chamber. The end of the second sealing portion is connected to the first sealing portion. The oil passage is formed by closing the gap formed in the first sealing portion by the fixed vortex member and the discharge housing. The oil passage extends circumferentially in the first sealing portion and bends radially at the connection point between the first sealing portion and the second sealing portion.

[0010] Therefore, by extending the oil passage circumferentially in the first seal and bending it radially at the connection point between the first and second seals, a pressure loss of the oil flowing in the oil passage can be generated. Thus, it is unnecessary to lengthen the oil passage to achieve a stable throttling effect, nor is it necessary to reduce the flow path cross-sectional area of ​​the oil passage. The connection point between the first and second seals easily provides space for the radial bending of the oil passage. Therefore, the connection point between the first and second seals is suitable as the space for the radial bending of the oil passage. Therefore, the configuration of the radial bending of the oil passage at the connection point between the first and second seals is suitable as a configuration that achieves a stable throttling effect in the oil passage without increasing the size of the scroll compressor. Therefore, a stable throttling effect in the oil passage can be achieved while ensuring the reliability of the scroll compressor without increasing its size.

[0011] In the aforementioned scroll compressor, the fixed scroll component or the discharge housing may have a groove recessed at the mating surface that engages with the sealing gasket. The groove is part of the oil passage. The slit has an upstream slit connected to the groove on the upstream side and a downstream slit connected to the groove on the downstream side. The upstream slit, the groove, and the downstream slit form the radially curved oil passage. The oil in the oil reservoir flows to the compression mechanism in the order of the upstream slit, the groove, and the downstream slit. The flow direction of the oil flowing circumferentially along the upstream slit is changed to radial or the opposite direction of the circumferential direction by the groove.

[0012] Therefore, for example, compared to the case where the flow direction of oil flowing circumferentially along the upstream gap changes to the radial or circumferential opposite direction through a portion of the gap, the manufacturing of the gasket can be made easier. Thus, the configuration of the scroll compressor can be simplified.

[0013] In the aforementioned scroll compressor, the upstream gap may be branched, including a first upstream gap and a second upstream gap connected to the tank at different locations. The flow of oil from the second upstream gap into the tank becomes a resistance relative to the flow of oil from the first upstream gap into the tank and into the downstream gap.

[0014] Therefore, by making the flow of oil from the second upstream gap into the tank a resistance relative to the flow of oil from the first upstream gap into the tank and into the downstream gap, it is easier to generate pressure loss of the oil flowing in the oil passage. Thus, a more stable throttling effect can be obtained in the oil passage.

[0015] Invention Effects

[0016] According to the present invention, a stable throttling effect can be obtained in the oil passage without increasing the size of the scroll compressor and ensuring its reliability. Attached Figure Description

[0017] Figure 1 This is a cross-sectional view of the scroll compressor in the implementation method.

[0018] Figure 2 This is an exploded perspective view showing a portion of a scroll compressor.

[0019] Figure 3 This is an exploded perspective view showing a portion of a scroll compressor.

[0020] Figure 4 It is a top view showing a portion of the sealing gasket in magnified form.

[0021] Figure 5It is a cross-sectional view showing an enlarged portion of the sealing gasket and the fixed scroll member.

[0022] Figure 6 This is a top view showing an enlarged portion of the sealing gasket in other embodiments.

[0023] Figure 7 This is a top view showing an enlarged portion of the sealing gasket in other embodiments.

[0024] Figure 8 This is a top view showing an enlarged portion of the sealing gasket in other embodiments.

[0025] Figure 9 This is a top view showing an enlarged portion of the sealing gasket in other embodiments.

[0026] Explanation of reference numerals in the attached figures

[0027] C1…Compression mechanism, 10…Scroll compressor, 11…Casing, 14…Discharge casing, 25…Fixed scroll, 26…Rotating scroll, 40…Discharge chamber, 50…Oil reservoir, 55…Blocking wall, 70…Sealing gasket, 71…First sealing part, 72…Second sealing part, 80…Oil passage, 81…Gap, 82…Gutter, 91…Upstream gap, 91a…First upstream gap, 91b…Second upstream gap, 92…Downstream gap. Detailed Implementation

[0028] The following is based on Figures 1-5 An embodiment of a scroll compressor will be described. This scroll compressor is used, for example, in a vehicle air conditioning system.

[0029] <Basic Components of a Scroll Compressor 10>

[0030] like Figure 1 As shown, the scroll compressor 10 has a cylindrical housing 11. The housing 11 includes a motor housing 12, a shaft support housing 13, and a discharge housing 14. Therefore, the discharge housing 14 is part of the housing 11. The motor housing 12, shaft support housing 13, and discharge housing 14 are made of a metallic material, such as aluminum. Additionally, the scroll compressor 10 includes a rotating shaft 15. The rotating shaft 15 is housed within the housing 11.

[0031] The motor housing 12 has a plate-shaped end wall 12a and a cylindrical peripheral wall 12b. The peripheral wall 12b extends cylindrically from the outer periphery of the end wall 12a. The axial direction of the peripheral wall 12b is aligned with the axial direction of the rotating shaft 15. A plurality of internally threaded holes 12c are formed at the open end of the peripheral wall 12b. Furthermore, in... Figure 1For ease of explanation, only one internal threaded hole 12c is shown in the diagram. Additionally, the motor housing 12 has a refrigerant intake port 12h. The intake port 12h is formed in the portion of the peripheral wall 12b located on the end wall 12a side. The intake port 12h connects the inside and outside of the motor housing 12.

[0032] A cylindrical hub 12d protrudes from the inner surface of the end wall 12a. One axial end of the rotating shaft 15, namely the first end, is inserted into the hub 12d. A rolling bearing 16 is provided between the inner circumferential surface of the hub 12d and the outer circumferential surface of the first end of the rotating shaft 15. Furthermore, the first end of the rotating shaft 15 is supported by the motor housing 12 via the rolling bearing 16 to enable rotation.

[0033] The shaft support housing 13 has a plate-shaped end wall 17 and a cylindrical peripheral wall 18. The peripheral wall 18 extends cylindrically from the outer periphery of the end wall 17. The axial direction of the peripheral wall 18 is aligned with the axial direction of the rotating shaft 15. In addition, the shaft support housing 13 has an annular flange wall 19. The flange wall 19 extends radially outward from the end of the outer peripheral surface of the peripheral wall 18 opposite to the end wall 17 toward the rotating shaft 15.

[0034] A plurality of bolt insertion holes 19a are formed on the outer periphery of the flange wall 19. Each bolt insertion hole 19a penetrates the flange wall 19 in the thickness direction. Each bolt insertion hole 19a of the flange wall 19 communicates with each internal threaded hole 12c of the motor housing 12. Furthermore, in Figure 1 For ease of explanation, only one bolt insertion hole 19a is shown in the figure.

[0035] The motor housing 12 and the shaft support housing 13 define the motor chamber 20 formed within the housing 11. Therefore, the motor housing 12 and the shaft support housing 13 together define the motor chamber 20. Refrigerant from the suction port 12h is drawn into the motor chamber 20. Therefore, the motor chamber 20 is a suction pressure region.

[0036] A circular through-hole 17a is formed in the center of the end wall 17. The through-hole 17a extends through the end wall 17 in the thickness direction. A rotating shaft 15 is inserted into the through-hole 17a. The end face 15e, located on the other side of the axial direction of the rotating shaft 15, i.e., the second end face, is located inside the peripheral wall 18. A rolling bearing 21 is provided between the inner peripheral surface of the peripheral wall 18 and the outer peripheral surface of the rotating shaft 15. The rotating shaft 15 is supported by the shaft support housing 13 via the rolling bearing 21 and is rotatable. Therefore, the shaft support housing 13 supports the rotating shaft 15 so that it can rotate. The rotating shaft 15 is supported by the housing 11 so that it can rotate.

[0037] The scroll compressor 10 includes an electric motor 22. The electric motor 22 is housed within a motor chamber 20. The electric motor 22 has a cylindrical stator 23 and a cylindrical rotor 24. The rotor 24 is disposed inside the stator 23. The rotor 24 rotates integrally with a rotating shaft 15. The stator 23 surrounds the rotor 24. The rotor 24 has a rotor core 24a fixed to the rotating shaft 15 and a plurality of permanent magnets (not shown) disposed on the rotor core 24a.

[0038] The stator 23 has a cylindrical stator core 23a and a motor coil 23b. The stator core 23a is fixed to the inner circumferential surface of the peripheral wall 12b of the motor housing 12. The motor coil 23b is wound around the stator core 23a. The rotor 24 rotates by supplying power controlled by a converter (not shown) to the motor coil 23b. As a result, the rotating shaft 15 rotates integrally with the rotor 24. Therefore, the electric motor 22 rotates the rotating shaft 15.

[0039] The scroll compressor 10 has a compression mechanism C1. The compression mechanism C1 consists of a fixed scroll member 25 and a rotating scroll member 26. Therefore, the compression mechanism C1 is scroll-type. The rotating scroll member 26 revolves relative to the fixed scroll member 25 as the rotating shaft 15 rotates. The housing 11 houses the compression mechanism C1.

[0040] like Figure 1 and Figure 2 As shown, the fixed vortex member 25 has a fixed base plate 25a, a fixed vortex wall 25b, and an outer peripheral wall 25c. The fixed base plate 25a is circular. A discharge port 25h is formed in the center of the fixed base plate 25a. The discharge port 25h is circular. The discharge port 25h penetrates the fixed base plate 25a in the thickness direction. The fixed vortex wall 25b rises from the fixed base plate 25a. The outer peripheral wall 25c rises from the outer periphery of the fixed base plate 25a. The outer peripheral wall 25c surrounds the fixed vortex wall 25b.

[0041] like Figure 1 and Figure 3 As shown, the fixed vortex member 25 has a first discharge chamber forming recess 41 and a first oil reservoir forming recess 51. The first discharge chamber forming recess 41 and the first oil reservoir forming recess 51 are formed on the end face 25e of the fixed substrate 25a. The end face 25e of the fixed substrate 25a has a first annular end face 251 and a first connecting end face 252. The first annular end face 251 is annular and extends along the outer periphery of the fixed substrate 25a. The first connecting end face 252 is elongated and strip-shaped. The first connecting end face 252 is connected to the first annular end face 251 and extends between the first discharge chamber forming recess 41 and the first oil reservoir forming recess 51.

[0042] The discharge port 25h has an opening on the bottom surface of the recess 41 formed in the first discharge chamber. For example... Figure 1As shown, the scroll compressor 10 includes a valve mechanism 25v. The valve mechanism 25v is mounted on the bottom surface of the recess 41 formed in the first discharge chamber. The valve mechanism 25v is configured to open and close the discharge port 25h.

[0043] The rotating scroll member 26 has a rotating base plate 26a and a rotating scroll wall 26b. The rotating base plate 26a is circular. The rotating base plate 26a faces the fixed base plate 25a. The rotating scroll wall 26b stands upright from the rotating base plate 26a toward the fixed base plate 25a. The rotating scroll wall 26b engages with the fixed scroll wall 25b. The rotating scroll member 26 is located inside the outer peripheral wall 25c. The rotating scroll member 26 revolves inside the outer peripheral wall 25c. The front end face of the fixed scroll wall 25b contacts the rotating base plate 26a. The front end face of the rotating scroll wall 26b contacts the fixed base plate 25a. Furthermore, the fixed base plate 25a, the fixed scroll wall 25b, the rotating base plate 26a, and the rotating scroll wall 26b define a compression chamber 27. The compression chamber 27 compresses the refrigerant.

[0044] The rotating substrate 26a has a cylindrical hub 26c. The hub 26c protrudes from the end face 26e of the rotating substrate 26a opposite to the fixed substrate 25a. The axial direction of the hub 26c is aligned with the axial direction of the rotating shaft 15. Furthermore, the rotating substrate 26a has a plurality of grooves 26d. The plurality of grooves 26d are respectively formed around the hub 26c in the end face 26e of the rotating substrate 26a. The plurality of grooves 26d are arranged at predetermined intervals in the circumferential direction of the rotating shaft 15. Moreover, in... Figure 1 For ease of explanation, only one groove 26d is shown in the diagram. A ring-shaped member 28 is fitted into each groove 26d. A pin 29 is inserted into each ring member 28. Each pin 29 protrudes from the end face 13e of the rotating scroll member 26 in the shaft support housing 13.

[0045] The scroll compressor 10 includes an eccentric shaft 31. The eccentric shaft 31 protrudes from the end face 15e of the rotating shaft 15 at an off-center position relative to the axis L1 of the rotating shaft 15 toward the rotating scroll member 26. The eccentric shaft 31 is integrally formed with the rotating shaft 15. The axial direction of the eccentric shaft 31 is aligned with the axial direction of the rotating shaft 15. The eccentric shaft 31 is inserted into the hub 26c.

[0046] The scroll compressor 10 includes a counterweight 32 and a bushing 33. The bushing 33 is fitted into the outer peripheral surface of the eccentric shaft 31. The counterweight 32 and the bushing 33 are integrally formed. The counterweight 32 is housed within the peripheral wall 18 of the shaft support housing 13. The rotating scroll member 26 is supported by the eccentric shaft 31 via the bushing 33 and rolling bearings 34, enabling it to rotate relative to the eccentric shaft 31.

[0047] The rotation of the rotating shaft 15 is transmitted to the rotating scroll member 26 via the eccentric shaft 31, bushing 33, and rolling bearing 34. Furthermore, the rotation of the rotating scroll member 26 is prevented by the contact between each pin 29 and the inner circumferential surface of each ring member 28, allowing only its revolution. Thus, the rotating scroll member 26 revolves while the rotating scroll wall 26b is in contact with the fixed scroll wall 25b. Furthermore, the refrigerant is compressed by the reduction in the volume of the compression chamber 27 due to the revolution of the rotating scroll member 26. The rotating scroll member 26 revolves inside the outer circumferential wall 25c as the rotating shaft 15 rotates. The counterweight 32 counteracts the centrifugal force acting on the rotating scroll member 26 during its revolution. This reduces the imbalance of the rotating scroll member 26.

[0048] like Figure 1 and Figure 2 As shown, the discharge housing 14 has a plate-shaped end wall 14a and a cylindrical peripheral wall 14b. The peripheral wall 14b extends cylindrically from the outer periphery of the end wall 14a. The axial direction of the peripheral wall 14b is aligned with the axial direction of the rotating shaft 15. The peripheral wall 14b surrounds the fixed volute member 25. A plurality of bolt insertion holes 14c are formed in the peripheral wall 14b. Furthermore, in Figure 1 For ease of explanation, only one bolt insertion hole 14c is shown in the diagram. Each bolt insertion hole 14c is connected to each bolt insertion hole 19a of the flange wall 19.

[0049] Bolts B1, passing through the bolt insertion holes 14c, are threaded into the internal threaded holes 12c of the motor housing 12 via the bolt insertion holes 19a of the flange wall 19. Thus, the shaft support housing 13 is connected to the peripheral wall 12b of the motor housing 12, and the discharge housing 14 is connected to the flange wall 19 of the shaft support housing 13. Therefore, the motor housing 12, shaft support housing 13, and discharge housing 14 are arranged in this order along the axial direction of the rotation shaft 15. The fixed scroll member 25 is clamped between the end wall 14a of the discharge housing 14 and the shaft support housing 13. Therefore, the discharge housing 14 is connected to the fixed scroll member 25.

[0050] like Figure 2 As shown, the discharge housing 14 has a second discharge chamber forming recess 42 and a second oil reservoir forming recess 52. The second discharge chamber forming recess 42 and the second oil reservoir forming recess 52 are formed on the inner end face 14e of the end wall 14a. The second discharge chamber forming recess 42 has a substantially the same shape as the first discharge chamber forming recess 41. The second oil reservoir forming recess 52 has a substantially the same shape as the first oil reservoir forming recess 51.

[0051] The inner end face 14e of the end wall 14a has a second annular end face 141 and a second connecting end face 142. The second annular end face 141 is annular and extends along the outer periphery of the inner end face 14e of the end wall 14a. The second connecting end face 142 is elongated and strip-shaped. The second connecting end face 142 is connected to the second annular end face 141 and extends between the second discharge chamber forming recess 42 and the second oil reservoir forming recess 52.

[0052] like Figure 2 and Figure 3 As shown, the second annular end face 141 extends along the first annular end face 251. The first annular end face 251 and the second annular end face 141 are the mating surfaces for fixing the vortex member 25 and the discharge housing 14. The second connecting end face 142 extends along the first connecting end face 252. The first connecting end face 252 and the second connecting end face 142 are the mating surfaces for fixing the vortex member 25 and the discharge housing 14.

[0053] like Figure 1 As shown, the scroll compressor 10 includes a suction passage 35. The suction passage 35 has a first groove 36, a first hole 37, a second groove 38, and a second hole 39. The first groove 36 is formed on a portion of the inner circumferential surface of the peripheral wall 12b of the motor housing 12. The first groove 36 opens at the open end of the peripheral wall 12b. The first hole 37 is formed on the outer circumferential portion of the flange wall 19 of the shaft support housing 13. The first hole 37 penetrates the flange wall 19 in the thickness direction. The first hole 37 communicates with the first groove 36. The second groove 38 is formed on a portion of the inner circumferential surface of the peripheral wall 14b of the discharge housing 14. The second groove 38 communicates with the first hole 37. The second hole 39 is formed on the outer circumferential wall 25c of the fixed scroll member 25. The second hole 39 penetrates the outer circumferential wall 25c in the thickness direction. The second hole 39 communicates with the second groove 38. The second hole 39 communicates with the outermost circumferential portion of the compression chamber 27.

[0054] Refrigerant in the motor chamber 20 is drawn into the compression chamber 27 through the first slot 36, the first hole 37, the second slot 38, and the second hole 39. Therefore, the first slot 36, the first hole 37, the second slot 38, and the second hole 39 form the suction pressure region for the refrigerant drawn into the compression chamber 27. The refrigerant drawn into the compression chamber 27 is compressed within the compression chamber 27 by the revolution of the rotating scroll member 26. In this way, the compression mechanism C1 compresses the refrigerant drawn into the housing 11.

[0055] <Sealing gasket 70>

[0056] like Figure 2 and Figure 3 As shown, the scroll compressor 10 has a plate-shaped sealing gasket 70. The sealing gasket 70 is a thin metal plate. The sealing gasket 70 is annular. The sealing gasket 70 seals the end wall 14a of the discharge housing 14 with the fixed base plate 25a.

[0057] The sealing gasket 70 has a discharge chamber communication hole 70a and an oil reservoir communication hole 70b. The discharge chamber communication hole 70a is substantially the same shape as the first discharge chamber forming recess 41 and the second discharge chamber forming recess 42. The oil reservoir communication hole 70b is substantially the same shape as the first oil reservoir forming recess 51 and the second oil reservoir forming recess 52.

[0058] The sealing gasket 70 has a first sealing portion 71 and a second sealing portion 72. The first sealing portion 71 is annular. The first sealing portion 71 extends along the first annular end face 251 and the second annular end face 141. The first sealing portion 71 is located between the first annular end face 251 and the second annular end face 141. The first sealing portion 71 is in close contact with the first annular end face 251 and the second annular end face 141. The first sealing portion 71 seals the space between the first annular end face 251 and the second annular end face 141. Therefore, the first sealing portion 71 seals the space between the fixed vortex member 25 and the discharge housing 14.

[0059] The second sealing portion 72 is connected to the first sealing portion 71. The second sealing portion 72 is an elongated strip. The second sealing portion 72 extends along the first connecting end face 252 and the second connecting end face 142. The second sealing portion 72 is located between the first connecting end face 252 and the second connecting end face 142. The second sealing portion 72 is in close contact with the first connecting end face 252 and the second connecting end face 142. Therefore, the sealing gasket 70 is in close contact with the mating surface of the fixed scroll member 25 and the discharge housing 14. The second sealing portion 72 seals the space between the first connecting end face 252 and the second connecting end face 142. Therefore, the sealing gasket 70 seals the space between the fixed scroll member 25 and the discharge housing 14. The second sealing portion 72 separates the discharge chamber communication hole 70a and the oil reservoir communication hole 70b. A through hole 73 is formed in the second sealing portion 72.

[0060] The first sealing portion 71 has a first bend 71a and a second bend 71b. The first bend 71a is the portion that, together with the second sealing portion 72, demarcates the discharge chamber communication hole 70a in the first sealing portion 71. The second bend 71b is the portion that, together with the second sealing portion 72, demarcates the oil reservoir communication hole 70b in the first sealing portion 71.

[0061] The first sealing portion 71 has a pair of connecting portions 74. One of the connecting portions 74 is the portion in the first sealing portion 71 that connects the first end of the first bent portion 71a, the first end of the second bent portion 71b, and the first end of the second sealing portion 72. The other of the connecting portions 74 is the portion in the first sealing portion 71 that connects the second end of the first bent portion 71a, the second end of the second bent portion 71b, and the second end of the second sealing portion 72. Therefore, the end of the second sealing portion 72 is connected to the first sealing portion 71.

[0062] exist Figure 4 In the diagram, the boundary between the connecting portion 74 and the first curved portion 71a is represented by an imaginary line L11. Additionally, in... Figure 4 In the diagram, the boundary between the connecting portion 74 and the second curved portion 71b is represented by an imaginary line L12. Furthermore, in... Figure 4 In the diagram, the boundary between the connecting portion 74 and the second sealing portion 72 is represented by an imaginary line L13. Thus, each connecting portion 74 is a connection point between the first sealing portion 71 and the second sealing portion 72.

[0063] <Exhaust Chamber 40>

[0064] like Figure 2 and Figure 3 As shown, the first discharge chamber forming recess 41 and the second discharge chamber forming recess 42 are connected via a discharge chamber communication hole 70a. Furthermore, the first discharge chamber forming recess 41 and the second discharge chamber forming recess 42 divide the area to form a discharge chamber 40. Therefore, the scroll compressor 10 includes a discharge chamber 40. Refrigerant compressed by the compression mechanism C1 is discharged into the discharge chamber 40.

[0065] <Oil Storage Chamber 50>

[0066] The first oil reservoir forming recess 51 and the second oil reservoir forming recess 52 are connected via an oil reservoir connecting hole 70b. Furthermore, the first oil reservoir forming recess 51 and the second oil reservoir forming recess 52 divide the oil reservoir 50. Therefore, the scroll compressor 10 includes an oil reservoir 50. The oil reservoir 50 stores oil separated from the refrigerant in the discharge chamber 40. The discharge chamber 40 and the oil reservoir 50 are divided by the fixed scroll member 25 and the discharge housing 14. The discharge housing 14 divides the discharge chamber 40 and the oil reservoir 50 by engaging with the fixed scroll member 25. The wall forming the first connecting end face 252 and the wall forming the second connecting end face 142 are partition walls 55 that divide the discharge chamber 40 and the oil reservoir 50. Therefore, the discharge housing 14 and the fixed scroll member 25 have partition walls 55 that divide the discharge chamber 40 and the oil reservoir 50.

[0067] The first sealing part 71 surrounds the discharge chamber 40 and the oil reservoir 50 and seals against the outside. The second sealing part 72 is in close contact with the partition wall 55 to seal between the discharge chamber 40 and the oil reservoir 50. In this embodiment, the scroll compressor 10 is mounted in a vehicle with the oil reservoir 50 located below the discharge chamber 40.

[0068] like Figure 1 As shown, the scroll compressor 10 includes an oil separation chamber 60. The oil separation chamber 60 is formed inside the discharge housing 14. The oil separation chamber 60 is formed inside an elongated cylindrical outer cylinder 61, which is part of the end wall 14a of the discharge housing 14. The first end of the outer cylinder 61 becomes a discharge port 62 for discharging refrigerant to the outside. The discharge port 62 communicates with the oil separation chamber 60.

[0069] An inner cylinder 63 is embedded within the oil separation chamber 60. The axial direction of the inner cylinder 63 is aligned with the radial direction of the rotating shaft 15. The first end of the inner cylinder 63 communicates with the outlet 62. The second end of the inner cylinder 63 communicates with the side of the oil separation chamber 60 opposite to the outlet 62. Additionally, as... Figure 1 and Figure 2 As shown, an inlet hole 64 is formed in the outer cylinder 61. The inlet hole 64 connects the discharge chamber 40 and the oil separation chamber 60. The inlet hole 64 guides the refrigerant discharged into the discharge chamber 40 into the oil separation chamber 60.

[0070] An oil drain hole 65 is formed in the discharge housing 14. The first end of the oil drain hole 65 communicates with the side of the oil separation chamber 60 opposite to the discharge outlet 62. For example... Figure 2 As shown, the second end of the oil drain hole 65 opens at the second connecting end face 142 of the discharge housing 14. The oil drain hole 65 communicates with the through hole 73 of the sealing gasket 70. Furthermore, the oil separation chamber 60 communicates with the first oil storage chamber through the oil drain hole 65 and the through hole 73 to form a recess 51. Therefore, the oil separation chamber 60 communicates with the oil storage chamber 50 through the oil drain hole 65 and the through hole 73.

[0071] like Figure 1 As shown, the refrigerant, compressed in the compression chamber 27 and discharged into the discharge chamber 40 via the discharge port 25h, is introduced into the oil separation chamber 60 via the inlet port 64. The refrigerant introduced into the oil separation chamber 60 rotates around the inner cylinder 63. This imparts centrifugal force to the oil contained in the refrigerant, separating the oil from the refrigerant within the oil separation chamber 60. Therefore, the oil separation chamber 60 separates the oil contained in the refrigerant discharged into the discharge chamber 40.

[0072] The refrigerant, after oil separation, flows into and passes through the inner cylinder 63. Then, the refrigerant remaining in the inner cylinder 63 flows out through the outlet 62 into an external refrigerant circuit (not shown). The oil separated from the refrigerant in the oil separation chamber 60 flows towards the oil drain hole 65 by its own weight. Furthermore, the oil flowing towards the oil drain hole 65 is discharged into the oil storage chamber 50 through the oil drain hole 65 and the through hole 73, and is stored in the oil storage chamber 50.

[0073] <Oil Channel 80>

[0074] like Figure 3 As shown, the scroll compressor 10 has an oil passage 80. The oil passage 80 allows oil in the oil reservoir 50 to flow to the compression mechanism C1. The scroll compressor 10 has a slit 81 and a groove 82. The slit 81 is formed in the gasket 70. The slit 81 is formed in the first sealing portion 71. The slit 81 extends along the first sealing portion 71 of the gasket 70. The slit 81 penetrates the gasket 70 in the thickness direction. The oil passage 80 is formed by closing the slit 81 with the fixed scroll member 25 and the discharge housing 14.

[0075] A groove 82 is formed on the end face 25e of the fixing substrate 25a. Therefore, the fixing scroll member 25 has a groove 82 recessed at the mating surface with the sealing gasket 70. The groove 82 is part of the oil passage 80. The groove 82 is an elongated hole when viewed from above. The groove 82 is provided in the end face 25e of the fixing substrate 25a at the portion overlapping one of the pair of connecting portions 74. Therefore, the groove 82 is provided in the end face 25e of the fixing substrate 25a at the portion corresponding to one of the pair of connecting portions 74. Therefore, the groove 82 is provided at the portion corresponding to the connection portion of the first sealing portion 71 and the second sealing portion 72.

[0076] like Figure 4 As shown, the groove 82 extends in the same direction as the second sealing portion 72 extending from the first sealing portion 71. Specifically, the groove 82 is formed on the end face 25e of the fixed substrate 25a such that, when viewed from above, the length direction of the groove 82 is aligned with the extension direction of the second sealing portion 72 extending from the first sealing portion 71. The opening of the groove 82 is closed by the connecting portion 74 of the sealing gasket 70. The groove 82 is the portion of the oil passage 80 with a larger flow path cross-sectional area compared to the gap 81.

[0077] like Figure 4 and Figure 5 As shown, the slot 81 has an upstream slot 91 and a downstream slot 92. The upstream slot 91 is connected to the slot 82 on the upstream side. The downstream slot 92 is connected to the slot 82 on the downstream side.

[0078] like Figure 2 and Figure 3 As shown, the upstream slit 91 extends from the lower end of the second bend 71b toward one of the pair of connecting portions 74. The first end of the upstream slit 91 is located at the lower end of the second bend 71b. The first end of the upstream slit 91 communicates with the space below in the oil reservoir 50.

[0079] like Figure 4 As shown, the second end of the upstream gap 91 is located on one of the pair of connecting portions 74. The second end of the upstream gap 91 communicates with the groove 82. Specifically, the second end of the upstream gap 91 communicates with the portion of the groove 82 opposite to the second sealing portion 72 in the length direction of the groove 82. The upstream gap 91 extends in a manner that overlaps with the groove 82 in a direction orthogonal to the length direction of the groove 82 when viewed from above. Therefore, the upstream gap 91 extends in a manner that overlaps with the groove 82 in a direction intersecting the length direction of the groove 82 when viewed from above.

[0080] like Figure 2 and Figure 3As shown, the downstream gap 92 extends from one of the pair of connecting portions 74 along the first bend 71a and toward the other of the pair of connecting portions 74. The first end of the downstream gap 92 is located at one of the pair of connecting portions 74. The second end of the downstream gap 92 is located above the first bend 71a. Specifically, the second end of the downstream gap 92 is separated from the first end of the upstream gap 91 by more than 180 degrees in the circumferential direction of the sealing gasket 70.

[0081] like Figure 4 As shown, the first end of the downstream slit 92 communicates with the groove 82. Specifically, the first end of the downstream slit 92 communicates with the portion of the groove 82 on the side of the second sealing portion 72 in the length direction of the groove 82. The downstream slit 92 extends in a direction that overlaps with the groove 82 in an inclined direction relative to the length direction of the groove 82 when viewed from above. Therefore, the downstream slit 92 extends in a direction that intersects with the groove 82 in a direction that crosses the length direction of the groove 82 when viewed from above.

[0082] like Figure 1 and Figure 3 As shown, a connecting passage 25d is formed on the outer periphery of the fixed substrate 25a. A first end of the connecting passage 25d opens at the end face 25e of the fixed substrate 25a. Furthermore, the first end of the connecting passage 25d communicates with a second end of the downstream gap 92. The second end of the connecting passage 25d communicates with the outermost peripheral portion of the compression chamber 27. Therefore, the oil reservoir 50 and the outermost peripheral portion of the compression chamber 27 are connected via the oil passage 80 and the connecting passage 25d.

[0083] In the scroll compressor 10 of this embodiment, an oil passage 80 is formed by an upstream slit 91, a groove 82, and a downstream slit 92, which curves radially. Oil in the oil reservoir 50 flows to the compression mechanism C1 in the order of the upstream slit 91, the groove 82, and the downstream slit 92. The oil passage 80 extends circumferentially in the first sealing part 71 and curves radially at the connection between the first sealing part 71 and the second sealing part 72.

[0084] <Function>

[0085] Next, the function of this embodiment will be explained.

[0086] like Figure 4 As shown, oil flowing from the upstream gap 91 flows into the channel 82. At this time, the upstream gap 91 extends in a direction orthogonal to the length direction of the channel 82 when viewed from above, overlapping with the channel 82. Therefore, the oil flowing from the upstream gap 91 into the channel 82... Figure 4 The oil flows into the groove 82 in the direction indicated by arrow A1. As a result, the oil flowing into the groove 82 collides with the inner circumferential surface of the groove 82.

[0087] By causing the oil flowing into the groove 82 to collide with the inner circumferential surface of the groove 82, a pressure loss is generated in the oil flowing in the oil passage 80. Furthermore, the oil flow direction is bent along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the upstream gap 91. More specifically, as... Figure 4 As shown by the middle arrow A2, the flow direction of the oil is bent at approximately a 90-degree angle along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the upstream gap 91 (the direction of arrow A1). In this way, the flow direction of the oil flowing circumferentially along the upstream gap 91 is changed to radial by the groove 82.

[0088] Subsequently, the oil flows downstream towards the slit 92 in the channel 82. At this point, the downstream slit 92 extends in a direction that overlaps with the channel 82 when viewed from above, inclined relative to its length. Therefore, the oil flowing in the channel 82 collides again with the inner circumferential surface of the channel 82 just before flowing into the downstream slit 92. This second collision between the oil flowing in the channel 82 and the inner circumferential surface of the channel 82 creates a pressure loss in the oil flowing in the oil passage 80.

[0089] Furthermore, the oil flow direction is curved along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the groove 82. Specifically, as... Figure 4 As indicated by arrow A3, the oil flow direction bends at approximately 90 degrees along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the groove 82 (the direction of arrow A2). The oil then flows from the groove 82 into the downstream gap 92. The oil flowing in the downstream gap 92 then flows back to the outermost peripheral portion of the compression chamber 27 via the connecting passage 25d.

[0090] Thus, the groove 82 bends along the surface of the sealing gasket 70 in the oil passage 80, functioning as a bend that causes pressure loss in the oil flowing in the oil passage 80. Therefore, the oil passage 80 has a bend that bends along the surface of the sealing gasket 70, causing pressure loss in the oil flowing in the oil passage 80. In this embodiment, the bend is formed by the groove 82. Therefore, the bend is provided at the portion corresponding to the connection point between the first sealing portion 71 and the second sealing portion 72. Furthermore, the bend extends in a direction consistent with the extending direction of the second sealing portion 72 from the first sealing portion 71.

[0091] <Effect>

[0092] The following effects can be obtained from the above embodiments.

[0093] (1) The oil passage 80 extends circumferentially in the first sealing part 71 and bends radially at the connection point between the first sealing part 71 and the second sealing part 72, thereby generating a pressure loss of the oil flowing in the oil passage 80. Therefore, it is not necessary to lengthen the oil passage 80, for example, to obtain a stable throttling effect in the oil passage 80, nor is it necessary to reduce the flow path cross-sectional area of ​​the oil passage 80. The connection point between the first sealing part 71 and the second sealing part 72 easily ensures space for the radial bending of the oil passage 80. Therefore, the connection point between the first sealing part 71 and the second sealing part 72 is suitable as a space for the radial bending of the oil passage 80. Therefore, the configuration of the oil passage 80 being radially bent at the connection point between the first sealing part 71 and the second sealing part 72 is suitable as a configuration that allows a stable throttling effect to be obtained in the oil passage 80 without increasing the size of the scroll compressor 10. Therefore, a stable throttling effect can be achieved in the oil passage 80 without increasing the size of the scroll compressor 10 while ensuring its reliability.

[0094] (2) The slit 81 has an upstream slit 91 connected to the groove 82 on the upstream side and a downstream slit 92 connected to the groove 82 on the downstream side, forming a radially curved oil passage 80. The flow direction of the oil flowing circumferentially along the upstream slit 91 is changed to radial through the groove 82. Thus, for example, compared to the case where the flow direction of the oil flowing circumferentially along the upstream slit 91 is changed to radial through a part of the slit 81, the manufacturing of the sealing gasket 70 can be made easier. Therefore, the configuration of the scroll compressor 10 can be simplified.

[0095] (3) Consider the case where a groove 82 extends in the same direction as the second sealing portion 72 extending from the first sealing portion 71, as in this embodiment. In this case, by providing the groove 82 as a bend at the portion corresponding to the connection between the first sealing portion 71 and the second sealing portion 72, it is easy to extend the groove 82 in the same direction as the second sealing portion 72 extending from the first sealing portion 71. Therefore, while effectively utilizing space, a groove 82 as a bend can be provided in the oil passage 80, thus achieving a stable throttling effect in the oil passage 80 without increasing the size of the scroll compressor 10.

[0096] <Example of Change>

[0097] Furthermore, the above-described embodiments can be modified as follows. The above-described embodiments and the following modifications can be combined with each other within the scope of technical inconsistency.

[0098] < Figure 6 The structure of the example change shown >

[0099] ○ For example Figure 6 As shown, alternatively, the upstream gap 91 may connect to the portion of the groove 82 along its length direction to the side of the second sealing portion 72, and the downstream gap 92 may connect to the portion of the groove 82 opposite to the second sealing portion 72 along its length direction. In this case, the same function and effect as the above-described embodiment can be achieved. Therefore, the flow direction of the oil flowing circumferentially along the upstream gap 91 is changed to radial through the groove 82.

[0100] < Figure 7 The structure of the example change shown >

[0101] ○ For example Figure 7 As shown, the groove 82 can also be formed on the end face 25e of the fixed substrate 25a in such a way that the length direction of the groove 82 is orthogonal to the extension direction of the second sealing portion 72 from the first sealing portion 71 when viewed from above. In short, the groove 82 may not extend in a direction consistent with the extension direction of the second sealing portion 72 from the first sealing portion 71.

[0102] In this case, for example, the upstream gap 91 extends in a manner that overlaps with the groove 82 in the extending direction from the first seal portion 71 of the second seal portion 72 when viewed from above. The upstream gap 91 extends relative to the groove 82 in a manner that overlaps with the groove 82 from the side opposite to the second seal portion 72. The upstream gap 91 communicates with the portion of the groove 82 on the side of the first bend 71a in the length direction of the groove 82.

[0103] The downstream gap 92 extends in a manner that overlaps with the groove 82 in the extending direction from the first seal portion 71 of the second seal portion 72 when viewed from above. The downstream gap 92 extends relative to the groove 82 in a manner that overlaps with the groove 82 from the side of the second seal portion 72. The downstream gap 92 communicates with the portion of the groove 82 on the side of the second bend 71b in the length direction of the groove 82.

[0104] < Figure 7 The effect of the example change shown >

[0105] Oil flowing in the upstream gap 91 flows into the groove 82. At this time, the upstream gap 91 extends in a manner that overlaps with the groove 82 in the direction extending from the first seal portion 71 of the second seal portion 72 when viewed from above. That is, the upstream gap 91 extends in a manner that overlaps with the groove 82 in a direction orthogonal to the length direction of the groove 82 when viewed from above. Therefore, the oil flowing into the groove 82 from the upstream gap 91... Figure 7 The oil flows into the groove 82 in the direction indicated by the middle arrow A11. As a result, the oil flowing into the groove 82 collides with the inner circumferential surface of the groove 82.

[0106] Pressure loss occurs in the oil flowing through the oil passage 80 due to the collision between the oil flowing into the groove 82 and the inner circumferential surface of the groove 82. Furthermore, the oil flow direction bends along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the upstream gap 91. Specifically, as... Figure 7 As indicated by the middle arrow A12, the flow direction of the oil is bent at approximately a 90-degree angle along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the upstream gap 91 (the direction of arrow A11). In this way, the flow direction of the oil flowing circumferentially along the upstream gap 91 is changed to the opposite circumferential direction by the groove 82.

[0107] Then, the oil flows towards the downstream gap 92 in the groove 82. At this time, the downstream gap 92 extends in a manner that overlaps with the groove 82 in the direction extending from the first seal 71 of the second seal 72 when viewed from above. That is, the downstream gap 92 extends in a manner that overlaps with the groove 82 in a direction orthogonal to the length direction of the groove 82 when viewed from above. Therefore, the oil flowing in the groove 82 collides again with the inner circumferential surface of the groove 82 just before flowing into the downstream gap 92. By the oil flowing in the groove 82 colliding again with the inner circumferential surface of the groove 82, pressure loss of the oil flowing in the oil passage 80 is generated again.

[0108] Furthermore, the oil flow direction is curved along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the groove 82. Specifically, as... Figure 7 As indicated by arrow A13, the oil flow direction bends at approximately 90 degrees along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the groove 82 (the direction of arrow A12). The oil then flows from the groove 82 into the downstream gap 92. Furthermore, the oil flowing in the downstream gap 92 returns to the outermost peripheral portion of the compression chamber 27 via the connecting passage 25d. Thus, the same effect as in the embodiment described above can be achieved.

[0109] < Figure 8 The structure of the example change shown >

[0110] ○ For example Figure 8 As shown, the upstream slot 91 can also be branched into a first upstream slot 91a and a second upstream slot 91b, which communicate with the groove 82 at different locations. Furthermore, in Figure 8 In the embodiments shown, with Figure 7 Similarly, in the embodiment shown, the groove 82 is formed on the end face 25e of the fixed substrate 25a such that, when viewed from above, the length direction of the groove 82 is orthogonal to the extension direction of the second sealing portion 72 from the first sealing portion 71.

[0111] The first upstream slit 91a communicates with the groove 82. The first upstream slit 91a extends in a manner that overlaps with the groove 82 in the extending direction from the first sealing portion 71 of the second sealing portion 72 when viewed from above. The first upstream slit 91a extends relative to the groove 82 in a manner that overlaps with the groove 82 from the side opposite to the second sealing portion 72. The first upstream slit 91a communicates with the portion of the groove 82 on the side of the first bend 71a in the length direction of the groove 82.

[0112] The second upstream slit 91b branches off from the first upstream slit 91a and merges with the groove 82. The second upstream slit 91b extends in a direction orthogonal to the extension direction of the second sealing portion 72 from the first sealing portion 71 when viewed from above, overlapping the groove 82. The second upstream slit 91b extends relative to the groove 82 in a manner overlapping the groove 82 from the side of the second bend 71b. The second upstream slit 91b communicates with the portion of the groove 82 on the side of the second bend 71b along the length of the groove 82.

[0113] The downstream gap 92 extends in a manner that overlaps with the groove 82 in the extending direction from the first seal portion 71 of the second seal portion 72 when viewed from above. The downstream gap 92 extends relative to the groove 82 in a manner that overlaps with the groove 82 from the side of the second seal portion 72. The downstream gap 92 communicates with the center portion of the groove 82 in the longitudinal direction.

[0114] < Figure 8 The effect of the example change shown >

[0115] The oil flowing in the upstream gap 91 branches into the first upstream gap 91a and the second upstream gap 91b. The oil flowing in the first upstream gap 91a flows into the groove 82 from the first upstream gap 91a. At this time, the first upstream gap 91a extends in a manner that overlaps with the groove 82 in the extending direction from the first sealing portion 71 of the second sealing portion 72 when viewed from above. That is, the first upstream gap 91a extends in a manner that overlaps with the groove 82 in a direction orthogonal to the length direction of the groove 82 when viewed from above. Therefore, the oil flowing into the groove 82 from the first upstream gap 91a... Figure 8 The oil flows into the groove 82 in the direction indicated by the middle arrow A21. As a result, the oil flowing into the groove 82 collides with the inner circumferential surface of the groove 82.

[0116] Pressure loss occurs in the oil flowing in the oil passage 80 due to the collision between the oil flowing into the groove 82 and the inner circumferential surface of the groove 82. Furthermore, the oil flow direction bends along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the first upstream gap 91a. Specifically, as... Figure 8As indicated by arrow A22, the oil flow direction bends at approximately 90 degrees along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the first upstream gap 91a (the direction of arrow A21). Then, the oil flows towards the downstream gap 92 in the groove 82. Thus, the flow direction of the oil flowing circumferentially along the first upstream gap 91a is changed to the opposite circumferential direction by the groove 82.

[0117] On the other hand, the oil flowing in the second upstream slit 91b flows into the tank 82. Then, the oil flowing into the tank 82 from the second upstream slit 91b flows towards the center of the tank 82 in the longitudinal direction. Here, the oil flowing into the tank 82 from the first upstream slit 91a and the oil flowing into the tank 82 from the second upstream slit 91b collide with each other at the center of the tank 82 in the longitudinal direction. Therefore, the flow of the oil flowing into the tank 82 from the second upstream slit 91b becomes a resistance relative to the flow of the oil flowing into the tank 82 from the first upstream slit 91a and towards the downstream slit 92.

[0118] Furthermore, the oil that has collided with each other at the center of the longitudinal direction of the groove 82 flows downstream toward the gap 92. That is, as... Figure 8 As indicated by arrow A23, the oil flow direction bends at approximately 90 degrees along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing along the length of the groove 82 (the direction of arrow A22). The oil then flows from the groove 82 into the downstream gap 92. Furthermore, the oil flowing in the downstream gap 92 returns to the outermost peripheral portion of the compression chamber 27 via the connecting passage 25d.

[0119] < Figure 8 The effect of the change example shown >

[0120] Therefore, the flow of oil flowing into the tank 82 from the second upstream slit 91b becomes a resistance relative to the flow of oil flowing into the tank 82 from the first upstream slit 91a and into the downstream slit 92. Consequently, it is easier for pressure loss to occur in the oil flowing in the oil passage 80. Therefore, a more stable throttling effect can be obtained in the oil passage 80.

[0121] < Figure 9 The structure of the example change shown >

[0122] ○ For example Figure 9 As shown, alternatively, the first upstream slit 91a may communicate with the central portion of the groove 82 along its length, and the downstream slit 92 may communicate with the portion of the groove 82 on the side of the first bend 71a along its length. The first upstream slit 91a and... Figure 8Similarly, in the embodiment shown, the second sealing portion 72 extends in a manner that overlaps with the groove 82 from the extending direction of the first sealing portion 71 when viewed from above. The first upstream gap 91a extends relative to the groove 82 in a manner that overlaps with the groove 82 from the side opposite to the second sealing portion 72. The downstream gap 92 and Figure 8 Similarly, in the embodiment shown, the second sealing portion 72 extends in a manner that overlaps with the groove 82 from the extending direction of the first sealing portion 71 when viewed from above. The downstream gap 92 extends relative to the groove 82 in a manner that overlaps with the groove 82 from the side of the second sealing portion 72. Furthermore, regarding the respective configurations of the groove 82 and the second upstream gap 91b, and... Figure 8 The embodiments shown are identical in configuration, therefore their description is omitted.

[0123] < Figure 9 The effect of the example change shown >

[0124] The oil flowing in the upstream gap 91 branches into the first upstream gap 91a and the second upstream gap 91b. The oil flowing in the first upstream gap 91a flows into the groove 82 from the first upstream gap 91a. At this time, the first upstream gap 91a extends in a manner that overlaps with the groove 82 in the extending direction from the first sealing part 71 of the second sealing part 72 when viewed from above. That is, the first upstream gap 91a extends in a manner that overlaps with the groove 82 in a direction orthogonal to the length direction of the groove 82 when viewed from above. Therefore, the oil flowing into the groove 82 from the first upstream gap 91a flows from... Figure 9 The oil flows into the groove 82 in the direction indicated by the middle arrow A31. As a result, the oil flowing into the groove 82 collides with the inner circumferential surface of the groove 82.

[0125] Pressure loss of the oil flowing in the oil passage 80 is generated by the collision between the oil flowing into the groove 82 and the inner circumferential surface of the groove 82. Furthermore, the flow direction of the oil is bent along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the first upstream gap 91a. Specifically, as... Figure 9 As indicated by arrow A32, the oil flow direction bends at approximately 90 degrees along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the first upstream gap 91a (the direction of arrow A31). The oil then flows towards the downstream gap 92 in the groove 82.

[0126] On the other hand, the oil flowing in the second upstream slit 91b flows into the tank 82. Then, the oil flowing into the tank 82 from the second upstream slit 91b flows towards the center of the tank 82 in the longitudinal direction. Here, the oil flowing into the tank 82 from the first upstream slit 91a and the oil flowing into the tank 82 from the second upstream slit 91b collide with each other at the center of the tank 82 in the longitudinal direction. Therefore, the flow of the oil flowing into the tank 82 from the second upstream slit 91b becomes a resistance relative to the flow of the oil flowing into the tank 82 from the first upstream slit 91a and towards the downstream slit 92.

[0127] Then, the oil that has collided with each other at the center of the longitudinal direction of the groove 82 flows toward the downstream gap 92. At this time, the downstream gap 92 extends in a manner that overlaps with the groove 82 in the extension direction from the first seal 71 of the second seal 72 when viewed from above. That is, the downstream gap 92 extends in a manner that overlaps with the groove 82 in a direction orthogonal to the longitudinal direction of the groove 82 when viewed from above. Therefore, the oil flowing in the groove 82 collides again with the inner circumferential surface of the groove 82 just before it flows into the downstream gap 92. By the oil flowing in the groove 82 colliding again with the inner circumferential surface of the groove 82, pressure loss of the oil flowing in the oil passage 80 is generated again.

[0128] Furthermore, the oil flow direction is curved along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the groove 82. Specifically, as... Figure 9 As indicated by arrow A33, the oil flow direction bends at approximately a 90-degree angle along the surface of the sealing gasket 70 relative to the flow direction of the oil flowing in the groove 82 (the direction of arrow A32). Then, the oil flows from the groove 82 into the downstream gap 92. The oil flowing in the downstream gap 92 then returns to the outermost peripheral portion of the compression chamber 27 via the connecting passage 25d. This allows it to function in conjunction with... Figure 8 The implementation shown achieves the same effect.

[0129] <Other examples of changes>

[0130] In one embodiment, at least one of the discharge housing 14 and the fixed vortex member 25 may have a partition wall 55 that divides the discharge chamber 40 and the oil storage chamber 50.

[0131] In another embodiment, instead of the fixed vortex member 25 having a groove 82, the discharge housing 14 may have a groove 82.

[0132] In this embodiment, the scroll compressor 10 is used in a vehicle air conditioning system, but is not limited thereto. In short, the scroll compressor 10 can be used to compress refrigerant, and its application can be appropriately changed.

Claims

1. A scroll compressor, characterized in that, have: The compression mechanism consists of a fixed scroll component and a rotating scroll component; A housing that accommodates the compression mechanism; The discharge housing, which is part of the housing, divides the discharge chamber and the oil storage chamber by its engagement with the fixed scroll member. The refrigerant compressed by the compression mechanism is discharged into the discharge chamber, and the oil storage chamber stores the oil separated from the refrigerant in the discharge chamber. A sealing gasket, which is in close contact with the mating surface between the fixed vortex member and the discharge housing; and An oil passage that allows oil in the oil reservoir to flow to the compression mechanism. At least one of the discharge housing and the fixed vortex member has a partition wall that divides the discharge chamber and the oil storage chamber. The sealing gasket has an annular first sealing portion surrounding the discharge chamber and the oil storage chamber and sealing the outside, and a second sealing portion that is in close contact with the partition wall and seals the discharge chamber and the oil storage chamber. The end of the second sealing part is connected to the first sealing part. The oil passage is formed by closing the gap in the first sealing part with the fixed vortex member and the discharge housing. The oil passage extends circumferentially in the first sealing part and bends radially at the connection point between the first sealing part and the second sealing part. The fixed vortex member or the discharge housing has a groove recessed at the mating surface that engages with the sealing gasket. The groove is part of the oil passage. The gap has an upstream gap communicating with the channel on the upstream side and a downstream gap communicating with the channel on the downstream side. The upstream gap, the groove, and the downstream gap form a radially curved oil passage. Oil in the oil reservoir flows to the compression mechanism in the order of the upstream gap, the groove, and the downstream gap. The flow direction of oil flowing circumferentially along the upstream gap is changed to radial or the opposite direction of the circumferential direction by the groove.

2. The scroll compressor according to claim 1, characterized in that, The upstream gap is branched, including a first upstream gap and a second upstream gap that communicate with the groove at different locations. The flow of oil from the second upstream gap into the tank becomes a resistance relative to the flow of oil from the first upstream gap into the tank and into the downstream gap.

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