Scroll Compressor

Abstract

To attain stable diaphragm effect in an oil passage while securing reliability of a scroll type compressor without enlarging the scroll type compressor.SOLUTION: An oil passage 80 is bent in a radial direction at a connection portion with a second seal 72 in a first seal 71 while extending in a circumferential direction in the first seal 71. Thereby, pressure loss of oil flowing in the oil passage 80 occurs. Accordingly, in order to attain stable diaphragm effect in the oil passage 80, there is no need to elongate the oil passage 80, for example, and there is no need to reduce a flow passage cross-sectional area of the oil passage 80.SELECTED DRAWING: Figure 4

Description

[Technical field]

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

[0002] For example, as disclosed in Patent Document 1, the scroll compressor has a compression mechanism consisting of a fixed scroll and an orbiting scroll. The scroll compressor has a housing that accommodates the compression mechanism. The scroll compressor has a discharge housing. The discharge housing is a part of the housing. The discharge housing divides a discharge chamber and an oil storage chamber by joining with the fixed scroll. Refrigerant compressed by the compression mechanism is discharged into the discharge chamber. The oil storage chamber stores oil separated from the refrigerant in the discharge chamber. The scroll compressor has a gasket. The gasket is in close contact with the joining surface between the fixed scroll and the discharge housing. The scroll compressor also has an oil passage. The oil passage flows the oil in the oil storage chamber to the compression mechanism. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2020-165362 A Summary of the Invention [Problem to be solved by the invention]

[0004] In such a scroll compressor, it is desirable to increase the throttling amount of the oil passage in order to stably flow the oil in the oil storage chamber to the compression mechanism through the oil passage. However, if the oil passage is lengthened in order to increase the throttling amount of the oil passage, the compressor itself will become larger. Also, if the flow path cross-sectional area of ​​the oil passage is reduced in order to increase the throttling amount of the oil passage, the oil passage will become more likely to become clogged with foreign matter, which may reduce the reliability of the scroll compressor. Therefore, there is a need for a means for obtaining a stable throttling effect in the oil passage while ensuring the reliability of the scroll compressor without increasing the size of the scroll compressor. [Means for solving the problem]

[0005] A scroll-type compressor that solves the above problem includes a compression mechanism consisting of a fixed scroll and a revolving scroll, a housing that accommodates the compression mechanism, a discharge housing that is a part of the housing and partitions, by joining with the fixed scroll, a discharge chamber from which refrigerant compressed by the compression mechanism is discharged and an oil storage chamber that stores oil separated from the refrigerant in the discharge chamber, a gasket that is in close contact with a joining surface between the fixed scroll and the discharge housing, and an oil passage that flows the oil in the oil storage chamber to the compression mechanism, wherein at least one of the discharge housing and the fixed scroll is a front scroll. The gasket has a partition wall that separates the discharge chamber and the oil storage chamber, and has an annular first seal portion that surrounds the discharge chamber and the oil storage chamber and seals them from the outside, and a second seal portion that fits tightly against the partition wall to seal between the discharge chamber and the oil storage chamber, an end of the second seal portion is connected to the first seal portion, and the oil passage is formed by blocking a slit formed in the first seal portion by the fixed scroll and the discharge housing, and the oil passage extends circumferentially in the first seal portion and is bent radially at a connection portion of the first seal portion with the second seal portion.

[0006] According to this, the oil passage extends in the circumferential direction in the first seal portion and bends in the radial direction at the connection portion of the first seal portion with the second seal portion, so that a pressure loss can be generated in the oil flowing through the oil passage. Therefore, in order to obtain a stable throttling effect in the oil passage, for example, it is not necessary to lengthen the oil passage, and further, it is not necessary to reduce the flow path cross-sectional area of ​​the oil passage. The connection portion of the first seal portion with the second seal portion makes it easy to secure a space for bending the oil passage in the radial direction. Therefore, the connection portion of the first seal portion with the second seal portion is suitable as a space for bending the oil passage in the radial direction. Therefore, the configuration in which the oil passage is bent in the radial direction at the connection portion of the first seal portion with the second seal portion is suitable as a configuration for obtaining a stable throttling effect in the oil passage without increasing the size of the scroll compressor. Therefore, it is possible to obtain a stable throttling effect in the oil passage without increasing the size of the scroll compressor, while ensuring the reliability of the scroll compressor.

[0007] In the above scroll-type compressor, the fixed scroll or the discharge housing has a groove recessed in the joint surface with the gasket, the groove being part of the oil passage, and the slit has an upstream slit communicating with the groove on the upstream side and a downstream slit communicating with the groove on the downstream side, the upstream slit, the groove and the downstream slit form the oil passage that is bent in the radial direction, and the oil in the oil storage chamber flows through them in this order to the compression mechanism, and the oil flowing circumferentially along the upstream slit has its flow direction changed by the groove to the radial direction or in the opposite direction to the circumferential direction.

[0008] This makes it easier to manufacture the gasket than when, for example, the oil flowing in the circumferential direction along the upstream slit is redirected to the radial direction or the opposite circumferential direction by a part of the slit, and therefore simplifies the configuration of the scroll compressor.

[0009] In the above scroll compressor, the upstream slit is branched and includes a first upstream slit and a second upstream slit which communicate with the groove at different positions, and oil flowing from the second upstream slit into the groove provides resistance to the flow of oil flowing from the first upstream slit into the groove and into the downstream slit.

[0010] With this, the oil flowing from the second upstream slit into the groove creates resistance to the flow of oil flowing from the first upstream slit into the groove and then to the downstream slit, which makes it easier to generate pressure loss in the oil flowing through the oil passage, thereby achieving a more stable throttling effect in the oil passage. Effect of the Invention

[0011] 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 while ensuring the reliability of the scroll compressor. [Brief description of the drawings]

[0012] [Figure 1] 1 is a cross-sectional view of a scroll compressor according to an embodiment. [Diagram 2] FIG. 2 is an exploded perspective view showing a part of a scroll compressor. [Diagram 3] FIG. 2 is an exploded perspective view showing a part of a scroll compressor. [Figure 4] FIG. 4 is an enlarged plan view showing a portion of the gasket. [Diagram 5] 3 is an enlarged cross-sectional view showing a portion of a gasket and a fixed scroll. FIG. [Figure 6] FIG. 13 is an enlarged plan view showing a portion of a gasket in another embodiment. [Figure 7] FIG. 13 is an enlarged plan view showing a portion of a gasket in another embodiment. [Figure 8] FIG. 13 is an enlarged plan view showing a portion of a gasket in another embodiment. [Figure 9]FIG. 13 is an enlarged plan view showing a portion of a gasket in another embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0013] Hereinafter, a scroll type compressor according to one embodiment will be described with reference to Figures 1 to 5. The scroll type compressor of this embodiment is used in, for example, a vehicle air conditioner. <Basic configuration of scroll compressor 10> As shown in Fig. 1, the scroll compressor 10 has a cylindrical housing 11. The housing 11 has a motor housing 12, a support housing 13, and a discharge housing 14. Therefore, the discharge housing 14 is a part of the housing. The motor housing 12, the support housing 13, and the discharge housing 14 are made of a metal material, for example, aluminum. The scroll compressor 10 also has a rotating shaft 15. The rotating shaft 15 is accommodated in the housing 11.

[0014] 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 coincides with the axial direction of the rotating shaft 15. A plurality of female threaded holes 12c are formed in the open end of the peripheral wall 12b. For convenience of explanation, only one female threaded hole 12c is shown in FIG. 1. The motor housing 12 also has a suction port 12h for drawing in the refrigerant. The suction port 12h is formed in a portion of the peripheral wall 12b that is located on the end wall 12a side. The suction port 12h communicates between the inside and outside of the motor housing 12.

[0015] A cylindrical boss portion 12d is provided on the inner surface of the end wall 12a to protrude therefrom. A first end portion, which is one end portion in the axial direction of the rotating shaft 15, is inserted into the boss portion 12d. A rolling bearing 16 is provided between the inner peripheral surface of the boss portion 12d and the outer peripheral surface of the first end portion of the rotating shaft 15. The first end portion of the rotating shaft 15 is rotatably supported by the motor housing 12 via the rolling bearing 16.

[0016] The journal 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 coincides with the axial direction of the rotating shaft 15. The journal housing 13 also has an annular flange wall 19. The flange wall 19 extends from an end of the outer periphery of the peripheral wall 18 opposite the end wall 17 toward the radially outward direction of the rotating shaft 15.

[0017] A plurality of bolt insertion holes 19a are formed in 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 in the flange wall 19 communicates with each female threaded hole 12c of the motor housing 12. For convenience of explanation, only one bolt insertion hole 19a is shown in FIG. 1.

[0018] The motor housing 12 and the journal housing 13 define a motor chamber 20 formed within the housing 11. Thus, the motor housing 12 defines the motor chamber 20 together with the journal housing 13. Refrigerant is drawn into the motor chamber 20 from a suction port 12h. Thus, the motor chamber 20 is a suction pressure region.

[0019] A circular through hole 17a is formed in the center of the end wall 17. The through hole 17a penetrates the end wall 17 in the thickness direction. The rotary shaft 15 is inserted through the through hole 17a. An end face 15e located on the second end side, which is the other end in the axial direction of the rotary shaft 15, 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 rotary shaft 15. The rotary shaft 15 is rotatably supported by the journal housing 13 via the rolling bearing 21. Therefore, the journal housing 13 rotatably supports the rotary shaft 15. The rotary shaft 15 is rotatably supported by the housing 11.

[0020] The scroll compressor 10 includes an electric motor 22. The electric motor 22 is accommodated in the motor chamber 20. The electric motor 22 includes a cylindrical stator 23 and a cylindrical rotor 24. The rotor 24 is disposed inside the stator 23. The rotor 24 rotates integrally with the rotating shaft 15. The stator 23 surrounds the rotor 24. The rotor 24 includes a rotor core 24a fixed to the rotating shaft 15 and a plurality of permanent magnets (not shown) provided on the rotor core 24a.

[0021] 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 when power controlled by an inverter (not shown) is supplied to the motor coil 23b. This causes the rotating shaft 15 to rotate integrally with the rotor 24. The electric motor 22 therefore rotates the rotating shaft 15.

[0022] The scroll compressor 10 has a compression mechanism C1. The compression mechanism C1 is composed of a fixed scroll 25 and a rotating scroll 26. Therefore, the compression mechanism C1 is of a scroll type. The rotating scroll 26 revolves around the fixed scroll 25 as the rotating shaft 15 rotates. The housing 11 accommodates the compression mechanism C1.

[0023] As shown in Figs. 1 and 2, the fixed scroll 25 has a fixed base plate 25a, a fixed spiral wall 25b, and an outer peripheral wall 25c. The fixed base plate 25a is disk-shaped. A discharge port 25h is formed in the center of the fixed base plate 25a. The discharge port 25h is a circular hole. The discharge port 25h penetrates the fixed base plate 25a in the thickness direction. The fixed spiral wall 25b stands upright from the fixed base plate 25a. The outer peripheral wall 25c stands upright from the outer periphery of the fixed base plate 25a. The outer peripheral wall 25c surrounds the fixed spiral wall 25b.

[0024] As shown in FIG. 1 and FIG. 3, the fixed scroll 25 has a first discharge chamber forming recess 41 and a first oil storage chamber forming recess 51. The first discharge chamber forming recess 41 and the first oil storage chamber forming recess 51 are formed on an end face 25e of the fixed base plate 25a. The end face 25e of the fixed base plate 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 base plate 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 storage chamber forming recess 51.

[0025] The discharge port 25h opens to a bottom surface of the first discharge chamber forming recess 41. As shown in Fig. 1, the scroll compressor 10 includes a valve mechanism 25v. The valve mechanism 25v is attached to the bottom surface of the first discharge chamber forming recess 41. The valve mechanism 25v is configured to be able to open and close the discharge port 25h.

[0026] The orbiting scroll 26 has an orbiting base plate 26a and an orbiting spiral wall 26b. The orbiting base plate 26a is disk-shaped. The orbiting base plate 26a faces the fixed base plate 25a. The orbiting spiral wall 26b stands up from the orbiting base plate 26a toward the fixed base plate 25a. The orbiting spiral wall 26b meshes with the fixed spiral wall 25b. The orbiting scroll 26 is located inside the outer peripheral wall 25c. The orbiting scroll 26 revolves inside the outer peripheral wall 25c. The tip surface of the fixed spiral wall 25b is in contact with the orbiting base plate 26a. The tip surface of the orbiting spiral wall 26b is in contact with the fixed base plate 25a. The fixed base plate 25a, the fixed spiral wall 25b, the orbiting base plate 26a, and the orbiting spiral wall 26b define a compression chamber 27. The compression chamber 27 compresses the refrigerant.

[0027] The orbiting base plate 26a has a cylindrical boss portion 26c. The boss portion 26c protrudes from an end face 26e of the orbiting base plate 26a on the opposite side to the fixed base plate 25a. The axial direction of the boss portion 26c coincides with the axial direction of the rotating shaft 15. The orbiting base plate 26a also has a plurality of groove portions 26d. The plurality of groove portions 26d are formed around the boss portion 26c on the end face 26e of the orbiting base plate 26a. The plurality of groove portions 26d are arranged at predetermined intervals in the circumferential direction of the rotating shaft 15. For convenience of explanation, only one groove portion 26d is shown in FIG. 1. An annular ring member 28 is fitted into each groove portion 26d. A pin 29 is inserted into each ring member 28. Each pin 29 is provided to protrude from an end face 13e of the journal housing 13 on the orbiting scroll 26 side.

[0028] The scroll compressor 10 includes an eccentric shaft 31. The eccentric shaft 31 protrudes toward the orbiting scroll 26 from a position on the end face 15e of the rotating shaft 15 that is eccentric with respect to the axis L1 of the rotating shaft 15. The eccentric shaft 31 is formed integrally with the rotating shaft 15. The axial direction of the eccentric shaft 31 coincides with the axial direction of the rotating shaft 15. The eccentric shaft 31 is inserted into the boss portion 26c.

[0029] The scroll compressor 10 includes a balance weight 32 and a bush 33. The bush 33 is fitted to the outer circumferential surface of the eccentric shaft 31. The balance weight 32 is integrated with the bush 33. The balance weight 32 is formed integrally with the bush 33. The balance weight 32 is accommodated within the peripheral wall 18 of the support housing 13. The orbiting scroll 26 is supported by the eccentric shaft 31 via the bush 33 and a rolling bearing 34 so as to be rotatable relative to the eccentric shaft 31.

[0030] The rotation of the rotary shaft 15 is transmitted to the orbiting scroll 26 via the eccentric shaft 31, the bush 33, and the rolling bearing 34. As a result, the orbiting scroll 26 rotates on its axis. Then, the pins 29 come into contact with the inner peripheral surfaces of the ring members 28, preventing the orbiting scroll 26 from rotating on its axis and allowing only the orbiting scroll 26 to revolve. As a result, the orbiting scroll 26 revolves while the orbiting scroll wall 26b comes into contact with the fixed scroll wall 25b. As the orbiting scroll 26 revolves, the volume of the compression chamber 27 decreases, and the refrigerant is compressed in the compression chamber 27. As the rotary shaft 15 rotates, the orbiting scroll 26 revolves inside the outer peripheral wall 25c. The balance weight 32 offsets the centrifugal force acting on the orbiting scroll 26 when the orbiting scroll 26 revolves. As a result, the amount of imbalance of the orbiting scroll 26 is reduced.

[0031] As shown in Fig. 1 and Fig. 2, 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 coincides with the axial direction of the rotary shaft 15. The peripheral wall 14b surrounds the fixed scroll 25. A plurality of bolt insertion holes 14c are formed in the peripheral wall 14b. For convenience of explanation, only one bolt insertion hole 14c is shown in Fig. 1. Each bolt insertion hole 14c communicates with each bolt insertion hole 19a of the flange wall 19.

[0032] The bolts B1 passing through each bolt insertion hole 14c pass through each bolt insertion hole 19a of the flange wall 19 and are screwed into each female threaded hole 12c of the motor housing 12. As a result, the journal 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 journal housing 13. Therefore, the motor housing 12, the journal housing 13, and the discharge housing 14 are arranged in this order in the axial direction of the rotating shaft 15. The fixed scroll 25 is sandwiched between the end wall 14a of the discharge housing 14 and the journal housing 13. Therefore, the discharge housing 14 is connected to the fixed scroll 25.

[0033] 2, the discharge housing 14 has a second discharge chamber forming recess 42 and a second oil storage chamber forming recess 52. The second discharge chamber forming recess 42 and the second oil storage chamber forming recess 52 are formed on the inner end surface 14e of the end wall 14a. The second discharge chamber forming recess 42 has approximately the same shape as the first discharge chamber forming recess 41. The second oil storage chamber forming recess 52 has approximately the same shape as the first oil storage chamber forming recess 51.

[0034] The inner end surface 14e of the end wall 14a has a second annular end surface 141 and a second connecting end surface 142. The second annular end surface 141 is annular and extends along the outer periphery of the inner end surface 14e of the end wall 14a. The second connecting end surface 142 is elongated and strip-shaped. The second connecting end surface 142 is connected to the second annular end surface 141 and extends between the second discharge chamber forming recess 42 and the second oil storage chamber forming recess 52.

[0035] 2 and 3, 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 joint surfaces between the fixed scroll 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 joint surfaces between the fixed scroll 25 and the discharge housing 14.

[0036] As shown in FIG. 1, the scroll compressor 10 includes a suction passage 35. The suction passage 35 includes a first groove 36, a first hole 37, a second groove 38, and a second hole 39. The first groove 36 is formed in a part of the inner circumferential surface of the peripheral wall 12b of the motor housing 12. The first groove 36 opens at an open end of the peripheral wall 12b. The first hole 37 is formed in the outer circumferential portion of the flange wall 19 of the journal 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 in a part 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 in the outer circumferential wall 25c of the fixed scroll 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 peripheral portion of the compression chamber 27.

[0037] The refrigerant in the motor chamber 20 passes through the first groove 36, the first hole 37, the second groove 38, and the second hole 39, and is sucked into the compression chamber 27. Therefore, the first groove 36, the first hole 37, the second groove 38, and the second hole 39 form a suction pressure region through which the refrigerant sucked into the compression chamber 27 flows. The refrigerant sucked into the compression chamber 27 is compressed in the compression chamber 27 by the orbital motion of the orbiting scroll 26. In this manner, the compression mechanism C1 compresses the refrigerant sucked into the housing 11.

[0038] <Gasket 70> 2 and 3, the scroll compressor 10 has a plate-shaped gasket 70. The gasket 70 is a thin metal plate. The gasket 70 is annular. The gasket 70 provides a seal between the end wall 14a of the discharge housing 14 and the fixed base plate 25a.

[0039] The gasket 70 has a discharge chamber communication hole 70a and an oil-storage chamber communication hole 70b. The discharge chamber communication hole 70a has substantially the same shape as the first discharge chamber forming recess 41 and the second discharge chamber forming recess 42. The oil-storage chamber communication hole 70b has substantially the same shape as the first oil-storage chamber forming recess 51 and the second oil-storage chamber forming recess 52.

[0040] The gasket 70 has a first seal portion 71 and a second seal portion 72. The first seal portion 71 is annular. The first seal portion 71 extends along the first annular end face 251 and the second annular end face 141. The first seal portion 71 is interposed between the first annular end face 251 and the second annular end face 141. The first seal portion 71 is in close contact with the first annular end face 251 and the second annular end face 141. The first seal portion 71 seals between the first annular end face 251 and the second annular end face 141. Therefore, the first seal portion 71 seals between the fixed scroll 25 and the discharge housing 14.

[0041] The second seal portion 72 is connected to the first seal portion 71. The second seal portion 72 is in the shape of an elongated strip. The second seal portion 72 extends along the first connection end face 252 and the second connection end face 142. The second seal portion 72 is interposed between the first connection end face 252 and the second connection end face 142. The second seal portion 72 is in close contact with the first connection end face 252 and the second connection end face 142. Therefore, the gasket 70 is in close contact with the joint surface between the fixed scroll 25 and the discharge housing 14. The second seal portion 72 seals between the first connection end face 252 and the second connection end face 142. Therefore, the gasket 70 seals between the fixed scroll 25 and the discharge housing 14. The second seal portion 72 separates the discharge chamber communication hole 70a and the oil storage chamber communication hole 70b. A through hole 73 is formed in the second seal portion 72.

[0042] The first seal portion 71 has a first curved portion 71a and a second curved portion 71b. The first curved portion 71a is a portion of the first seal portion 71 that defines the discharge chamber communication hole 70a together with the second seal portion 72. The second curved portion 71b is a portion of the first seal portion 71 that defines the oil storage chamber communication hole 70b together with the second seal portion 72.

[0043] The first seal portion 71 has a pair of connecting portions 74. One of the pair of connecting portions 74 is a portion that connects a first end portion of the first curved portion 71a, a first end portion of the second curved portion 71b, and a first end portion of the second seal portion 72 in the first seal portion 71. The other of the pair of connecting portions 74 is a portion that connects a second end portion of the first curved portion 71a, a second end portion of the second curved portion 71b, and a second end portion of the second seal portion 72 in the first seal portion 71. Therefore, an end portion of the second seal portion 72 is connected to the first seal portion 71.

[0044] In Fig. 4, the boundary between the connection portion 74 and the first curved portion 71a is indicated by a virtual line L11. Also, in Fig. 4, the boundary between the connection portion 74 and the second curved portion 71b is indicated by a virtual line L12. Furthermore, in Fig. 4, the boundary between the connection portion 74 and the second seal portion 72 is indicated by a virtual line L13. In this manner, each connection portion 74 is a connection portion of the first seal portion 71 with the second seal portion 72.

[0045] <Discharge chamber 40> 2 and 3, the first discharge chamber forming recess 41 and the second discharge chamber forming recess 42 are communicated with each other via a discharge chamber communication hole 70a. The first discharge chamber forming recess 41 and the second discharge chamber forming recess 42 define a discharge chamber 40. Thus, the scroll compressor 10 includes a discharge chamber 40. A refrigerant compressed by the compression mechanism C1 is discharged into the discharge chamber 40.

[0046] <Oil storage room 50> The first oil-storage chamber forming recess 51 and the second oil-storage chamber forming recess 52 are communicated with each other through the oil-storage chamber communication hole 70b. The first oil-storage chamber forming recess 51 and the second oil-storage chamber forming recess 52 define an oil-storage chamber 50. Thus, the scroll compressor 10 includes an oil-storage chamber 50. The oil-storage chamber 50 stores oil separated from the refrigerant in the discharge chamber 40. The discharge chamber 40 and the oil-storage chamber 50 are defined by the fixed scroll 25 and the discharge housing 14. The discharge housing 14 defines the discharge chamber 40 and the oil-storage chamber 50 by joining with the fixed scroll 25. The wall defining the first connecting end surface 252 and the wall defining the second connecting end surface 142 are partition walls 55 that define the discharge chamber 40 and the oil-storage chamber 50. Thus, the discharge housing 14 and the fixed scroll 25 have partition walls 55 that define the discharge chamber 40 and the oil-storage chamber 50.

[0047] The first seal portion 71 surrounds the discharge chamber 40 and the oil storage chamber 50 and seals them from the outside. The second seal portion 72 comes into close contact with the partition wall 55 to seal between the discharge chamber 40 and the oil storage chamber 50. The scroll compressor 10 of this embodiment is mounted on a vehicle such that the oil storage chamber 50 is located below the discharge chamber 40.

[0048] As shown in Fig. 1, 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. A first end of the outer cylinder 61 serves as a discharge port 62 for discharging the refrigerant to the outside. The discharge port 62 is in communication with the oil separation chamber 60.

[0049] An inner cylinder 63 is fitted in the oil separation chamber 60. The axial direction of the inner cylinder 63 coincides with the radial direction of the rotating shaft 15. A first end of the inner cylinder 63 communicates with the discharge port 62. A second end of the inner cylinder 63 communicates with the side of the oil separation chamber 60 opposite the discharge port 62. As shown in Figs. 1 and 2, an introduction hole 64 is formed in the outer cylinder 61. The introduction hole 64 communicates between the discharge chamber 40 and the oil separation chamber 60. The introduction hole 64 introduces the refrigerant discharged into the discharge chamber 40 into the oil separation chamber 60.

[0050] An oil drain hole 65 is formed in the discharge housing 14. A first end of the oil drain hole 65 communicates with the oil separation chamber 60 on the opposite side to the discharge port 62. As shown in FIG. 2, a second end of the oil drain hole 65 opens to the second connecting end surface 142 of the discharge housing 14. The oil drain hole 65 communicates with a through hole 73 of the gasket 70. The oil separation chamber 60 communicates with the first oil storage chamber forming recess 51 via the oil drain hole 65 and the through hole 73. Thus, the oil separation chamber 60 communicates with the oil storage chamber 50 via the oil drain hole 65 and the through hole 73.

[0051] 1, the refrigerant compressed in the compression chamber 27 and discharged into the discharge chamber 40 through the discharge port 25h is introduced into the oil separation chamber 60 through the introduction hole 64. The refrigerant introduced into the oil separation chamber 60 swirls around the inner cylinder 63. As a result, centrifugal force is applied to the oil contained in the refrigerant, and the oil is separated from the refrigerant in the oil separation chamber 60. Therefore, the oil separation chamber 60 separates the oil contained in the refrigerant discharged into the discharge chamber 40.

[0052] The refrigerant from which the oil has been separated flows into and passes through the inner cylinder 63. Then, the refrigerant that has passed through the inner cylinder 63 flows out to an external refrigerant circuit (not shown) through the discharge port 62. The oil separated from the refrigerant in the oil separation chamber 60 flows by its own weight toward the oil drain hole 65. Then, the oil flowing toward 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.

[0053] <Oil passage 80> As shown in FIG. 3, the scroll compressor 10 has an oil passage 80. The oil passage 80 allows the oil in the oil storage chamber 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 seal portion 71. The slit 81 extends along the first seal portion 71 of the gasket 70. The slit 81 penetrates the gasket 70 in the thickness direction. The oil passage 80 is formed by blocking the slit 81 with the fixed scroll 25 and the discharge housing 14.

[0054] The groove 82 is formed in the end face 25e of the fixed base plate 25a. Therefore, the fixed scroll 25 has the groove 82 recessed in the joint surface with the gasket 70. The groove 82 is a part of the oil passage 80. The groove 82 is an oval hole in a plan view. The groove 82 is provided in a portion of the end face 25e of the fixed base plate 25a that overlaps with one of the pair of connecting portions 74. Therefore, the groove 82 is provided in a portion of the end face 25e of the fixed base plate 25a that corresponds to one of the pair of connecting portions 74. Therefore, the groove 82 is provided in a portion of the first seal portion 71 that corresponds to the connection portion with the second seal portion 72.

[0055] 4, the groove 82 extends in a direction that coincides with the extension direction of the second seal portion 72 from the first seal portion 71. Specifically, the groove 82 is formed in the end surface 25e of the fixed substrate 25a such that the longitudinal direction of the groove 82 coincides with the extension direction of the second seal portion 72 from the first seal portion 71 in a plan view. The opening of the groove 82 is closed by the connection portion 74 of the gasket 70. The groove 82 is a portion of the oil passage 80 that has a larger flow passage cross-sectional area than the slit 81.

[0056] 4 and 5, the slit 81 has an upstream slit 91 and a downstream slit 92. The upstream slit 91 communicates with the groove 82 on the upstream side. The downstream slit 92 communicates with the groove 82 on the downstream side.

[0057] 2 and 3, the upstream slit 91 extends from a lower end of the second curved portion 71b toward one of the pair of connecting portions 74. A first end of the upstream slit 91 is located at the lower end of the second curved portion 71b. The first end of the upstream slit 91 communicates with the lower space in the oil storage chamber 50.

[0058] As shown in FIG. 4, the second end of the upstream slit 91 is located at one of the pair of connecting portions 74. The second end of the upstream slit 91 communicates with the groove 82. Specifically, the second end of the upstream slit 91 communicates with a portion of the groove 82 on the opposite side from the second seal portion 72 in the longitudinal direction of the groove 82. In a plan view, the upstream slit 91 extends from a direction perpendicular to the longitudinal direction of the groove 82 so as to overlap with the groove 82. Therefore, in a plan view, the upstream slit 91 extends from a direction intersecting the longitudinal direction of the groove 82 so as to overlap with the groove 82.

[0059] 2 and 3, the downstream slit 92 extends from one of the pair of connecting portions 74 along the first curved portion 71a and toward the other of the pair of connecting portions 74. A first end of the downstream slit 92 is located at one of the pair of connecting portions 74. A second end of the downstream slit 92 is located at an upper portion of the first curved portion 71a. Specifically, the second end of the downstream slit 92 is separated from the first end of the upstream slit 91 by 180 degrees or more in the circumferential direction of the gasket 70.

[0060] 4, a first end of the downstream slit 92 communicates with the groove 82. Specifically, the first end of the downstream slit 92 communicates with a portion of the groove 82 on the second seal portion 72 side in the longitudinal direction of the groove 82. In plan view, the downstream slit 92 extends from a direction oblique to the longitudinal direction of the groove 82 so as to overlap with the groove 82. Therefore, in plan view, the downstream slit 92 extends from a direction intersecting the longitudinal direction of the groove 82 so as to overlap with the groove 82.

[0061] 1 and 3, a communication passage 25d is formed in the outer periphery of the fixed base plate 25a. A first end of the communication passage 25d opens to an end face 25e of the fixed base plate 25a. The first end of the communication passage 25d is connected to a second end of the downstream slit 92. The second end of the communication passage 25d is connected to the outermost peripheral portion of the compression chamber 27. Therefore, the oil storage chamber 50 and the outermost peripheral portion of the compression chamber 27 are connected to each other via the oil passage 80 and the communication passage 25d.

[0062] In the scroll compressor 10 of this embodiment, the upstream slit 91, the groove 82, and the downstream slit 92 form an oil passage 80 that is bent in the radial direction, and oil in the oil storage chamber 50 flows through them in this order to the compression mechanism C1. The oil passage 80 extends in the circumferential direction in the first seal portion 71, and is bent in the radial direction at a connection portion of the first seal portion 71 with the second seal portion 72.

[0063] <effect> Next, the operation of this embodiment will be described. As shown in Fig. 4, oil flowing through upstream slit 91 flows from upstream slit 91 into groove 82. At this time, in a plan view, upstream slit 91 extends so as to overlap groove 82 from a direction perpendicular to the longitudinal direction of groove 82. Therefore, oil flowing from upstream slit 91 into groove 82 flows into groove 82 from the direction indicated by arrow A1 in Fig. 4. As a result, the oil flowing into groove 82 collides with the inner circumferential surface of groove 82.

[0064] The oil that has flowed into the groove 82 collides with the inner peripheral surface of the groove 82, causing a pressure loss in the oil flowing through the oil passage 80. Then, the flow direction of the oil is bent along the surface of the gasket 70 with respect to the flow direction of the oil flowing through the upstream slit 91. In detail, as shown by arrow A2 in Fig. 4, the flow direction of the oil is bent at an angle of approximately 90 degrees along the surface of the gasket 70 with respect to the flow direction of the oil flowing through the upstream slit 91 (the direction of arrow A1). In this way, the flow direction of the oil flowing in the circumferential direction along the upstream slit 91 is changed to the radial direction by the groove 82.

[0065] The oil then flows through the groove 82 toward the downstream slit 92. At this time, the downstream slit 92 extends in a diagonal direction relative to the longitudinal direction of the groove 82 so as to overlap with the groove 82 in a plan view. Therefore, the oil flowing through the groove 82 collides again with the inner circumferential surface of the groove 82 just before flowing into the downstream slit 92. As the oil flowing through the groove 82 collides again with the inner circumferential surface of the groove 82, a pressure loss of the oil flowing through the oil passage 80 occurs again.

[0066] Then, the flow direction of the oil bends along the surface of gasket 70 with respect to the flow direction of the oil flowing in groove 82. More specifically, as shown by arrow A3 in Fig. 4, the flow direction of the oil bends at an angle of approximately 90 degrees along the surface of gasket 70 with respect to the flow direction of the oil flowing in groove 82 (the direction of arrow A2). The oil then flows from groove 82 into downstream slit 92. Then, the oil flowing through downstream slit 92 is returned to the outermost peripheral portion of compression chamber 27 via communicating passage 25d.

[0067] In this manner, the groove 82 functions as a bent portion in the oil passage 80 that bends along the surface of the gasket 70 and generates a pressure loss in the oil flowing through the oil passage 80. Therefore, the oil passage 80 has a bent portion that bends along the surface of the gasket 70 and generates a pressure loss in the oil flowing through the oil passage 80. The bent portion in this embodiment is formed by the groove 82. Therefore, the bent portion is provided in a portion corresponding to the connection portion of the first seal portion 71 with the second seal portion 72. The bent portion extends in a direction that coincides with the extension direction of the second seal portion 72 from the first seal portion 71.

[0068] <Effects> The above embodiment can provide the following effects. (1) The oil passage 80 extends in the circumferential direction in the first seal portion 71 and bends in the radial direction at the connection portion of the first seal portion 71 with the second seal portion 72, so that a pressure loss can be generated in the oil flowing through the oil passage 80. Therefore, in order to obtain a stable throttling effect in the oil passage 80, for example, it is not necessary to lengthen the oil passage 80, and further, it is not necessary to reduce the flow path cross-sectional area of ​​the oil passage 80. The connection portion of the first seal portion 71 with the second seal portion 72 is easy to secure a space for bending the oil passage 80 in the radial direction. Therefore, the connection portion of the first seal portion 71 with the second seal portion 72 is suitable as a space for bending the oil passage 80 in the radial direction. Therefore, the configuration in which the oil passage 80 is bent in the radial direction at the connection portion of the first seal portion 71 with the second seal portion 72 is suitable as a configuration for obtaining a stable throttling effect in the oil passage 80 without increasing the size of the scroll compressor 10. Therefore, the scroll compressor 10 does not become large, and the reliability of the scroll compressor 10 is ensured, and a stable throttling effect can be obtained in the oil passage 80.

[0069] (2) The slit 81 has an upstream slit 91 that communicates with the groove 82 on the upstream side and a downstream slit 92 that communicates with the groove 82 on the downstream side, and the upstream slit 91, the groove 82, and the downstream slit 92 form an oil passage 80 that is bent in the radial direction. The oil flowing in the circumferential direction along the upstream slit 91 has its flow direction changed in the radial direction by the groove 82. This makes it easier to manufacture the gasket 70 than, for example, a case in which the oil flowing in the circumferential direction along the upstream slit 91 has its flow direction changed in the radial direction by a part of the slit 81. This makes it possible to simplify the configuration of the scroll compressor 10.

[0070] (3) Consider the case of employing the groove 82 extending in the direction matching the extension direction of the second seal portion 72 from the first seal portion 71, as in this embodiment. In this case, by providing the groove 82 as a bent portion in a portion of the first seal portion 71 corresponding to the connection portion between the second seal portion 72 and the second seal portion 72, it is easy to extend the groove 82 in the direction matching the extension direction of the second seal portion 72 from the first seal portion 71. Therefore, the groove 82 as a bent portion can be provided in the oil passage 80 while effectively utilizing space, and a stable throttling effect can be obtained in the oil passage 80 without increasing the size of the scroll compressor 10.

[0071] <Example of change> The above embodiment can be modified as follows: The above embodiment and the following modifications can be combined with each other to the extent that no technical contradiction occurs.

[0072] <Configuration of the modified example shown in Figure 6> 6, the upstream slit 91 may be connected to a portion of the groove 82 on the second seal portion 72 side in the longitudinal direction of the groove 82, and the downstream slit 92 may be connected to a portion of the groove 82 on the opposite side to the second seal portion 72 in the longitudinal direction of the groove 82. Even in this case, the same effects and advantages as those of the above embodiment can be obtained. Therefore, the oil flowing in the circumferential direction along the upstream slit 91 is changed in flow direction to the radial direction by the groove 82.

[0073] <Configuration of the modified example shown in Figure 7> 7, the groove 82 may be formed in the end surface 25e of the fixed substrate 25a so that, in a plan view, the longitudinal direction of the groove 82 is perpendicular to the extension direction of the second seal portion 72 from the first seal portion 71. In short, the groove 82 does not have to extend in a direction that matches the extension direction of the second seal portion 72 from the first seal portion 71.

[0074] In this case, for example, in a plan view, the upstream slit 91 extends so as to overlap with the groove 82 from the extension direction of the second seal portion 72 from the first seal portion 71. The upstream slit 91 extends so as to overlap with the groove 82 from the side opposite to the second seal portion 72. The upstream slit 91 communicates with a portion of the groove 82 on the first curved portion 71a side in the longitudinal direction of the groove 82.

[0075] In a plan view, the downstream slit 92 extends in the extension direction of the second seal portion 72 from the first seal portion 71 so as to overlap with the groove 82. The downstream slit 92 extends from the second seal portion 72 side with respect to the groove 82 so as to overlap with the groove 82. The downstream slit 92 communicates with a portion of the groove 82 on the second curved portion 71b side in the longitudinal direction of the groove 82.

[0076] <Function of the modified example shown in Figure 7> Oil flowing through the upstream slit 91 flows from the upstream slit 91 into the groove 82. At this time, the upstream slit 91 extends so as to overlap with the groove 82 in the extension direction from the first seal portion 71 of the second seal portion 72 in a plan view. That is, the upstream slit 91 extends so as to overlap with the groove 82 in a direction perpendicular to the longitudinal direction of the groove 82 in a plan view. Therefore, the oil flowing from the upstream slit 91 into the groove 82 flows into the groove 82 from the direction indicated by the arrow A11 in FIG. 7. As a result, the oil flowing into the groove 82 collides with the inner circumferential surface of the groove 82.

[0077] The oil that has flowed into the groove 82 collides with the inner peripheral surface of the groove 82, causing a pressure loss in the oil flowing through the oil passage 80. Then, the flow direction of the oil is bent along the surface of the gasket 70 with respect to the flow direction of the oil flowing through the upstream slit 91. In detail, as shown by arrow A12 in Fig. 7, the flow direction of the oil is bent at an angle of approximately 90 degrees along the surface of the gasket 70 with respect to the flow direction of the oil flowing through the upstream slit 91 (the direction of arrow A11). In this way, the flow direction of the oil flowing in the circumferential direction along the upstream slit 91 is changed by the groove 82 to the opposite circumferential direction.

[0078] The oil then flows through the groove 82 toward the downstream slit 92. At this time, the downstream slit 92 extends in a plan view from the extension direction of the second seal portion 72 from the first seal portion 71 so as to overlap with the groove 82. That is, the downstream slit 92 extends in a direction perpendicular to the longitudinal direction of the groove 82 so as to overlap with the groove 82 in a plan view. Therefore, the oil flowing through the groove 82 collides again with the inner circumferential surface of the groove 82 just before flowing into the downstream slit 92. When the oil flowing through the groove 82 collides again with the inner circumferential surface of the groove 82, a pressure loss of the oil flowing through the oil passage 80 occurs again.

[0079] Then, the flow direction of the oil bends along the surface of the gasket 70 with respect to the flow direction of the oil flowing in the groove 82. More specifically, as shown by arrow A13 in Fig. 7, the flow direction of the oil bends at an angle of approximately 90 degrees along the surface of the gasket 70 with respect 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 slit 92. Then, the oil flowing in the downstream slit 92 is returned to the outermost peripheral portion of the compression chamber 27 via the communication passage 25d. This makes it possible to achieve the same effects as the above embodiment.

[0080] <Configuration of the modified example shown in Figure 8> As shown in Fig. 8, the upstream slit 91 may be branched to include a first upstream slit 91a and a second upstream slit 91b that communicate with the groove 82 at different positions. In the embodiment shown in Fig. 8, similar to the embodiment shown in Fig. 7, the groove 82 is formed in the end surface 25e of the fixed substrate 25a so that the longitudinal direction of the groove 82 is perpendicular to the extension direction of the second seal portion 72 from the first seal portion 71 in a plan view.

[0081] The first upstream slit 91a communicates with the groove 82. In a plan view, the first upstream slit 91a extends so as to overlap with the groove 82 from the extension direction of the second seal portion 72 from the first seal portion 71. The first upstream slit 91a extends so as to overlap with the groove 82 from the side opposite to the second seal portion 72. The first upstream slit 91a communicates with a portion of the groove 82 on the first curved portion 71a side in the longitudinal direction of the groove 82.

[0082] The second upstream slit 91b branches off from the first upstream slit 91a and merges with the groove 82. In a plan view, the second upstream slit 91b extends so as to overlap with the groove 82 from a direction perpendicular to the extension direction of the second seal portion 72 from the first seal portion 71. The second upstream slit 91b extends from the second curved portion 71b side of the groove 82 so as to overlap with the groove 82. The second upstream slit 91b communicates with a portion of the groove 82 on the second curved portion 71b side in the longitudinal direction of the groove 82.

[0083] In a plan view, the downstream slit 92 extends from the extension direction of the second seal portion 72 from the first seal portion 71 so as to overlap with the groove 82. The downstream slit 92 extends from the second seal portion 72 side with respect to the groove 82 so as to overlap with the groove 82. The downstream slit 92 communicates with the center portion of the groove 82 in the longitudinal direction.

[0084] <Function of the modified example shown in Figure 8> The oil flowing through the upstream slit 91 branches into the first upstream slit 91a and the second upstream slit 91b. The oil flowing through the first upstream slit 91a flows from the first upstream slit 91a into the groove 82. At this time, the first upstream slit 91a extends so as to overlap with the groove 82 from the extension direction from the first seal portion 71 in the second seal portion 72 in a plan view. That is, the first upstream slit 91a extends so as to overlap with the groove 82 from a direction perpendicular to the longitudinal direction of the groove 82 in a plan view. Therefore, the oil flowing from the first upstream slit 91a into the groove 82 flows into the groove 82 from the direction indicated by the arrow A21 in FIG. 8. As a result, the oil flowing into the groove 82 collides with the inner circumferential surface of the groove 82.

[0085] The oil flowing into the groove 82 collides with the inner peripheral surface of the groove 82, causing a pressure loss in the oil flowing through the oil passage 80. Then, the flow direction of the oil is bent along the surface of the gasket 70 with respect to the flow direction of the oil flowing through the first upstream slit 91a. In detail, as shown by an arrow A22 in FIG. 8, the flow direction of the oil is bent at an angle of approximately 90 degrees along the surface of the gasket 70 with respect to the flow direction of the oil flowing through the first upstream slit 91a (the direction of the arrow A21). Thereafter, the oil flows through the groove 82 toward the downstream slit 92. In this way, the flow direction of the oil flowing in the circumferential direction along the first upstream slit 91a is changed by the groove 82 to the opposite circumferential direction.

[0086] On the other hand, the oil flowing through the second upstream slit 91b flows from the second upstream slit 91b into the groove 82. Then, the oil that flows into the groove 82 from the second upstream slit 91b flows inside the groove 82 toward the center in the longitudinal direction. Here, the oil that flows into the groove 82 from the first upstream slit 91a and flows inside the groove 82 and the oil that flows into the groove 82 from the second upstream slit 91b and flows inside the groove 82 collide with each other at the center in the longitudinal direction of the groove 82. Therefore, the oil that flows into the groove 82 from the second upstream slit 91b provides resistance to the flow of the oil that flows from the first upstream slit 91a into the groove 82 and into the downstream slit 92.

[0087] Then, the oil that collides with each other in the center of the longitudinal direction of groove 82 flows toward downstream slit 92. That is, as shown by arrow A23 in Fig. 8, the flow direction of the oil is bent at an angle of approximately 90 degrees along the surface of gasket 70 with respect to the flow direction of the oil that was flowing in the longitudinal direction of groove 82 (the direction of arrow A22). The oil then flows from groove 82 into downstream slit 92. Then, the oil flowing through downstream slit 92 is returned to the outermost peripheral portion of compression chamber 27 via communicating passage 25d.

[0088] <Effects of the modification shown in Figure 8> According to this, the oil flowing from the second upstream slit 91b into the groove 82 creates resistance to the flow of oil flowing from the first upstream slit 91a into the groove 82 and into the downstream slit 92. This makes it easier to generate pressure loss in the oil flowing through the oil passage 80. Therefore, a more stable throttling effect can be obtained in the oil passage 80.

[0089] <Configuration of the modified example shown in Fig. 9> As shown in FIG. 9, the first upstream slit 91a may be connected to a central portion of the groove 82 in the longitudinal direction, and the downstream slit 92 may be connected to a portion of the groove 82 on the first curved portion 71a side in the longitudinal direction. As in the embodiment shown in FIG. 8, the first upstream slit 91a extends from the extension direction of the second seal portion 72 from the first seal portion 71 so as to overlap with the groove 82 in a plan view. The first upstream slit 91a extends from the opposite side of the second seal portion 72 to the groove 82 so as to overlap with the groove 82. As in the embodiment shown in FIG. 8, the downstream slit 92 extends from the extension direction of the second seal portion 72 from the first seal portion 71 so as to overlap with the groove 82 in a plan view. The downstream slit 92 extends from the second seal portion 72 side to the groove 82 so as to overlap with the groove 82. The configurations of the groove 82 and the second upstream slit 91b are similar to those in the embodiment shown in FIG. 8, and therefore will not be described.

[0090] <Function of the modified example shown in Figure 9> The oil flowing through the upstream slit 91 branches into the first upstream slit 91a and the second upstream slit 91b. The oil flowing through the first upstream slit 91a flows from the first upstream slit 91a into the groove 82. At this time, the first upstream slit 91a extends so as to overlap with the groove 82 from the extension direction from the first seal portion 71 in the second seal portion 72 in a plan view. That is, the first upstream slit 91a extends so as to overlap with the groove 82 from a direction perpendicular to the longitudinal direction of the groove 82 in a plan view. Therefore, the oil flowing from the first upstream slit 91a into the groove 82 flows into the groove 82 from the direction indicated by the arrow A31 in FIG. 9. As a result, the oil flowing into the groove 82 collides with the inner circumferential surface of the groove 82.

[0091] The oil that has flowed into the groove 82 collides with the inner circumferential surface of the groove 82, causing a pressure loss in the oil flowing through the oil passage 80. Then, the flow direction of the oil is bent along the surface of the gasket 70 with respect to the flow direction of the oil flowing through the first upstream slit 91a. In detail, as shown by arrow A32 in FIG. 9, the flow direction of the oil is bent at an angle of approximately 90 degrees along the surface of the gasket 70 with respect to the flow direction of the oil flowing through the first upstream slit 91a (the direction of arrow A31). The oil then flows through the groove 82 toward the downstream slit 92.

[0092] On the other hand, the oil flowing through the second upstream slit 91b flows from the second upstream slit 91b into the groove 82. Then, the oil that flows into the groove 82 from the second upstream slit 91b flows inside the groove 82 toward the center in the longitudinal direction. Here, the oil that flows into the groove 82 from the first upstream slit 91a and the oil that flows into the groove 82 from the second upstream slit 91b and flows inside the groove 82 collide with each other at the center in the longitudinal direction of the groove 82. Therefore, the oil that flows into the groove 82 from the second upstream slit 91b acts as a resistance to the flow of the oil that flows from the first upstream slit 91a into the groove 82 and into the downstream slit 92.

[0093] Then, the oils collide with each other at the center of the groove 82 in the longitudinal direction, and flow toward the downstream slit 92. At this time, the downstream slit 92 extends so as to overlap with the groove 82 in the extending direction from the first seal portion 71 of the second seal portion 72 in a plan view. That is, the downstream slit 92 extends so as to overlap with the groove 82 in a direction perpendicular to the longitudinal direction of the groove 82 in a plan view. Therefore, the oil flowing through the groove 82 collides again with the inner circumferential surface of the groove 82 just before flowing into the downstream slit 92. When the oil flowing through the groove 82 collides again with the inner circumferential surface of the groove 82, a pressure loss of the oil flowing through the oil passage 80 occurs again.

[0094] Then, the flow direction of the oil bends along the surface of the gasket 70 with respect to the flow direction of the oil flowing in the groove 82. More specifically, as shown by arrow A33 in Fig. 9, the flow direction of the oil bends at an angle of approximately 90 degrees along the surface of the gasket 70 with respect to the flow direction of the oil flowing in the groove 82 (the direction of arrow A32). The oil then flows from the groove 82 into the downstream slit 92. The oil flowing in the downstream slit 92 is returned to the outermost peripheral portion of the compression chamber 27 via the communication passage 25d. This can provide the same effect as the embodiment shown in Fig. 8.

[0095] <Other changes> In the above embodiment, the partition wall 55 separating the discharge chamber 40 and the oil storage chamber 50 may be provided in at least one of the discharge housing 14 and the fixed scroll 25 .

[0096] In the above embodiment, the grooves 82 may be formed in the discharge housing 14 instead of in the fixed scroll 25 . In the above embodiment, the scroll compressor 10 is used in a vehicle air conditioner, but the present invention is not limited to this. In short, the scroll compressor 10 may be used in any application as long as it compresses a refrigerant, and the application of the scroll compressor 10 may be changed as appropriate. [Explanation of symbols]

[0097] C1...compression mechanism, 10...scroll type compressor, 11...housing, 14...discharge housing, 25...fixed scroll, 26...orbiting scroll, 40...discharge chamber, 50...oil storage chamber, 55...partition wall, 70...gasket, 71...first seal portion, 72...second seal portion, 80...oil passage, 81...slit, 82...groove, 91...upstream slit, 91a...first upstream slit, 91b...second upstream slit, 92...downstream slit.

Claims

1. A compression mechanism including a fixed scroll and an orbiting scroll; a housing that accommodates the compression mechanism; a discharge housing that is a part of the housing and is joined to the fixed scroll to partition a discharge chamber from which the refrigerant compressed by the compression mechanism is discharged and an oil storage chamber that stores oil separated from the refrigerant in the discharge chamber; a gasket that is in close contact with a joint surface between the fixed scroll and the discharge housing; an oil passage for allowing the oil in the oil reservoir to flow to the compression mechanism, At least one of the discharge housing and the fixed scroll has a partition wall that separates the discharge chamber from the oil storage chamber, the gasket has an annular first seal portion that surrounds the discharge chamber and the oil storage chamber and seals them from the outside, and a second seal portion that comes into close contact with the partition wall and seals between the discharge chamber and the oil storage chamber, an end of the second seal portion is connected to the first seal portion; the oil passage is formed by closing a slit formed in the first seal portion between the fixed scroll and the discharge housing, a first seal portion that is in contact with the second seal portion and is bent in a radial direction at a connection portion between the first seal portion and the second seal portion;

2. the fixed scroll or the discharge housing has a groove recessed in a joint surface with the gasket, The groove is a part of the oil passage, The slit has an upstream slit communicating with the groove on an upstream side and a downstream slit communicating with the groove on a downstream side, The upstream slit, the groove, and the downstream slit form the oil passage that is bent in the radial direction, and the oil in the oil storage chamber flows through these in this order to the compression mechanism, 2. The scroll compressor according to claim 1, wherein the flow direction of the oil flowing in a circumferential direction along the upstream slit is changed by the groove to a radial direction or a direction opposite to the circumferential direction.

3. the upstream slit is branched and includes a first upstream slit and a second upstream slit communicating with the groove at different positions; 3. The scroll compressor according to claim 2, wherein the oil flowing from the second upstream slit into the groove acts as a resistance to a flow of the oil flowing from the first upstream slit into the groove and into the downstream slit.

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