Co-rotating scroll compressor

Abstract

A co-rotating scroll compressor (10) includes a protruding portion (34) that protrudes from a housing end wall (17). A lubricating oil flow passage through which lubricating oil (37) separated from fluid flows is provided inside the protruding portion (34). An inflow passage (35) that connects a suction pressure region and the lubricating oil flow passage is formed in the housing (11). An outflow passage that causes the lubricating oil (37) in the lubricating oil flow passage to flow out to the exterior of the protruding portion (34) is formed in a support shaft (22). The opening area of the outflow passage to the lubricating oil flow passage is smaller than the opening area of the inflow passage (35) to the lubricating oil flow passage. A stator (41) is fixed to an outer surface of a base end portion (36), and the lubricating oil flow passage and the stator (41) are connected so as to allow heat transfer.

Description

Dual-rotation scroll compressor

[0001] The present disclosure relates to a dual-rotation scroll compressor.

[0002] For example, as disclosed in Patent Document 1, a dual-rotation scroll compressor includes a sealed container serving as a housing, a driving scroll and a driven scroll housed inside the sealed container, and an electric element serving as a motor. A rotor of the electric element is rotatably supported by the sealed container via a ball bearing serving as a drive bearing. The driving scroll is fixed to the rotor so as to be aligned with the rotor in an axial direction of the driving scroll. Further, the driving scroll is rotatably supported by the sealed container via a ball bearing serving as a drive bearing on a side opposite to the axial direction with respect to a portion supported by the aforementioned ball bearing. The driven scroll is coupled to the rotor via an Oldham coupling and supported by a needle bearing serving as a driven bearing.

[0003] Japanese Patent Laid-Open No. 7-229480

[0004] In a dual-rotation scroll compressor as disclosed in Patent Document 1, sliding portions of the driving scroll and the driven scroll, such as the drive bearing and the driven bearing, are present. The sliding portions of the dual-rotation scroll compressor are lubricated by lubricating oil present inside the housing. However, for example, an increase in viscosity of the lubricating oil caused by a temperature drop during cold weather may impair the supply of lubricating oil to the sliding portions.

[0005] A dual-rotation scroll compressor according to one aspect of the present disclosure comprises a housing whose interior is an intake pressure region, a compression mechanism housed within the housing and configured to compress a fluid, and a motor configured to drive the compression mechanism. The compression mechanism comprises a drive substrate and a drive scroll having a drive spiral wall rising from the drive substrate and rotating within the housing, and a driven substrate facing the drive substrate and a driven scroll having a driven spiral wall rising from the driven substrate toward the drive substrate and meshing with the drive spiral wall. The driven scroll rotates with respect to the rotation center of the drive scroll as the drive scroll rotates. The drive substrate, the drive spiral wall, the driven substrate, and the driven spiral wall partition a compression chamber for compressing the fluid. The motor comprises a stator extending cylindrically in the thrust direction and a rotor rotating on the outer circumference of the stator at the same rotation center as the rotation center of the drive scroll. The housing has a housing end wall and a projection that protrudes from the housing end wall toward the drive scroll and the driven scroll. The projection has a base end and a support shaft that protrudes from the base end toward the drive scroll and the driven scroll and rotatably supports the drive scroll via a drive bearing. The driven scroll is rotatably supported on the support shaft via a driven bearing. A lubricating oil flow passage is provided inside the projection through which lubricating oil separated from the fluid flows. An inlet passage is formed in the housing that connects the suction pressure region and the lubricating oil flow passage. An outlet passage is formed in the support shaft that allows the lubricating oil from the lubricating oil flow passage to flow out of the projection. The opening area of ​​the outlet passage to the lubricating oil flow passage is smaller than the opening area of ​​the inlet passage to the lubricating oil flow passage. The stator is fixed to the outer surface of the base end, and the lubricating oil flow passage and the stator are connected in a heat-transferable manner.

[0006] Figure 1 is a cross-sectional view showing a bidirectional scroll compressor according to an embodiment. Figure 2 is a cross-sectional view showing the oil storage chamber of the bidirectional scroll compressor of Figure 1 from the cover plate. Figure 3 is a partially enlarged cross-sectional view of the bidirectional scroll compressor of Figure 1. Figure 4 is a partially enlarged cross-sectional view of a modified bidirectional scroll compressor. Figure 5 shows the cover plate of another modified example. Figure 6 is a partially enlarged cross-sectional view showing the outlet passage of a further modified example.

[0007] The following describes one embodiment of a double-rotation scroll compressor. The double-rotation scroll compressor is mounted on a vehicle (not shown). The double-rotation scroll compressor compresses refrigerant as a fluid and is used, for example, in a vehicle air conditioning system.

[0008] <Housing> As shown in Figure 1, the double-rotating scroll compressor 10 is equipped with a cylindrical housing 11. The housing 11 has a housing body member 12 and a housing cover member 16. The housing body member 12 and the housing cover member 16 are each made of a metal material. The housing body member 12 and the housing cover member 16 are made of aluminum, for example. The housing body member 12 has an end wall 13 and a housing peripheral wall 14. The end wall 13 is disc-shaped. The housing peripheral wall 14 extends cylindrically from the outer circumference of the end wall 13. The housing body member 12 has a boss portion 13b. The boss portion 13b protrudes cylindrically from the inner surface of the end wall 13 on the side to which the housing peripheral wall 14 extends. The axis of the boss portion 13b coincides with the axis of the housing peripheral wall 14. In the following description, the direction in which the axis of the housing peripheral wall 14 extends may be referred to as the "thrust direction X".

[0009] The housing 11 has a discharge port 13a. The discharge port 13a penetrates the end wall 13 in the thickness direction of the end wall 13. The discharge port 13a is formed in the center of the end wall 13. The axis of the discharge port 13a coincides with the axis of the housing peripheral wall 14.

[0010] The housing cover member 16 has a housing end wall 17 and a cover cylinder wall 18. Therefore, the housing 11 including the housing cover member 16 has a housing end wall 17. The housing end wall 17 is disc-shaped. The housing cover member 16 is connected to the housing body member 12 with the housing end wall 17 closing the opening in the housing peripheral wall 14. The end wall 13, the housing peripheral wall 14, and the housing end wall 17 partition the housing chamber 33. Therefore, the housing 11 partitions the housing chamber 33.

[0011] The cover cylindrical wall 18 protrudes cylindrically from the housing end wall 17. The cover cylindrical wall 18 is located inside the housing peripheral wall 14. The axis of the cover cylindrical wall 18 coincides with the axis of the housing peripheral wall 14. The cover cylindrical wall 18 has a communication hole 18a. In the following description, the straight line passing through the axis of the housing peripheral wall 14, the axis of the boss portion 13b, and the axis of the cover cylindrical wall 18 may be referred to as the "first axis L1".

[0012] The housing 11 has an intake port 14a. The intake port 14a is formed in the portion of the housing peripheral wall 14 located on the opening side of the housing peripheral wall 14. The intake port 14a communicates with the containment chamber 33. The intake port 14a draws in refrigerant as a fluid into the containment chamber 33. Therefore, the containment chamber 33 is an intake pressure region. Thus, the inside of the housing 11 is an intake pressure region.

[0013] The housing 11 has a support 19. The support 19 is made of metal. For example, the support 19 is made of steel. The support 19 has a support cylindrical wall 20 and a support shaft 22. The support shaft 22 protrudes cylindrically from the inner circumference of the support cylindrical wall 20 on the opposite side from the support cylindrical wall 20. The support cylindrical wall 20 extends cylindrically from the outer circumference of the support shaft 22. The inner diameter of the support cylindrical wall 20 is larger than the outer diameter of the cover cylindrical wall 18. The axis of the support shaft 22 coincides with the axis of the support cylindrical wall 20. The support 19 is positioned opposite the housing end wall 17 with the support cylindrical wall 20 surrounding the cover cylindrical wall 18. The axis of the support cylindrical wall 20 coincides with the axis of the cover cylindrical wall 18.

[0014] Multiple elastic bodies 23 are interposed between the inner circumferential surface of the support cylinder wall 20 and the outer circumferential surface of the cover cylinder wall 18. Each elastic body 23 is made of rubber. Each elastic body 23 is annular in shape. The multiple elastic bodies 23 are arranged in a line with spacing in the axial direction of the cover cylinder wall 18. The support body 19 is fixed to the housing cover member 16 by the support cylinder wall 20 being fitted into the cover cylinder wall 18 via the multiple elastic bodies 23. Each elastic body 23 absorbs vibrations generated by vehicle vibrations and vibrations generated by the operation of the double-rotating scroll compressor 10, thereby suppressing vibrations of the support body 19.

[0015] The support shaft 22 closes the space defined inside the cover cylinder wall 18 and the support cylinder wall 20 from the tip side of the support cylinder wall 20. An oil storage chamber 24 is formed within the space enclosed by the cover cylinder wall 18 and the support body 19. The cover cylinder wall 18 and the support body 19 extend cylindrically in the thrust direction X and form the oil storage chamber 24.

[0016] The support cylinder wall 20 has an inlet 20a. The inlet 20a is formed in the support cylinder wall 20 at a position close to the housing end wall 17 in the thrust direction X. The inlet 20a opens to the outer and inner surfaces of the support cylinder wall 20. The inlet 20a is provided at a position facing the communication hole 18a of the cover cylinder wall 18, and the inlet 20a communicates with the communication hole 18a.

[0017] The housing 11 has a protruding portion 34 consisting of a cover cylinder wall 18 and a support 19. The protruding portion 34 protrudes from the housing end wall 17. An inflow passage 35 consisting of a communication hole 18a and an inlet 20a is formed in the protruding portion 34.

[0018] The protruding portion 34 has a base end portion 36 and a support shaft 22 that protrudes from the base end portion 36. The base end portion 36 is a cylindrical body consisting of a cover cylinder wall 18 and a support cylinder wall 20. Inside the protruding portion 34, there is an oil storage chamber 24 for storing lubricating oil 37. As will be described in detail later, since lubricating oil 37 flows through the oil storage chamber 24, the oil storage chamber 24 is an example of a lubricating oil flow passage through which lubricating oil 37 separated from the refrigerant flows, and the lubricating oil flow passage has an oil storage chamber 24 inside the base end portion 36 for storing lubricating oil 37. The oil storage chamber 24 is formed by closing the space inside the base end portion 36 with the support shaft 22. Lubricating oil 37 separated from the refrigerant is stored in the oil storage chamber 24.

[0019] Furthermore, an inflow passage 35 is formed at the base end 36 of the protruding portion 34, that is, in the housing 11, connecting the storage chamber 33 and the oil storage chamber 24. The housing 11 has a protruding body 15 that protrudes from the inside of the boss portion 13b. The protruding body 15 has a protruding body wall portion 15a and an insertion portion 15b. The insertion portion 15b protrudes from the central part of the protruding body wall portion 15a. The insertion portion 15b is cylindrical. The insertion portion 15b protrudes from the protruding body wall portion 15a in the thrust direction X.

[0020] A discharge shaft path 15c is formed in the protruding body 15. The discharge shaft path 15c extends in the thrust direction X. The discharge shaft path 15c extends inside the insertion portion 15b and penetrates the wall portion 15a of the protruding body. The discharge shaft path 15c is in communication with the discharge port 13a.

[0021] <Motor> The double-rotating scroll compressor 10 is equipped with a motor 40. The motor 40 is housed in a housing chamber 33. The motor 40 comprises a cylindrical stator 41 and a cylindrical rotor 42. The stator 41 extends cylindrically in the thrust direction X. The stator 41 has a cylindrical stator core 41a and a motor coil 41b. The stator core 41a is fixed to the outer circumferential surface of the support cylinder wall 20. In other words, the stator 41 is fixed to the outer surface of the base end portion 36 of the protrusion 34. The stator 41 and the oil storage chamber 24, which is an example of a lubricating oil flow passage, are connected in a way that allows for heat transfer.

[0022] The inner circumferential surface of the stator core 41a is in contact with the outer surface of the base end 36, specifically the outer circumferential surface of the support cylinder wall 20, over the entire axial and circumferential directions of the stator 41. This allows the stator 41 to be heat-transferably connected to the base end 36 at the projection 34, and more specifically, to the support cylinder wall 20. For example, the stator 41 is connected to the support cylinder wall 20 by shrink-fitting. Furthermore, the end face of the stator core 41a is positioned at the boundary between the support cylinder wall 20 and the support shaft 22, so as close to the support shaft 22 as possible. The position of the stator core 41a may be changed to any position in the thrust direction X on the support cylinder wall 20. The motor coil 41b is wound around the stator core 41a.

[0023] The rotor 42 is positioned on the outer circumference of the stator 41. The rotor 42 surrounds the stator 41. Bolt insertion holes 42a are formed in the rotor 42. The bolt insertion holes 42a penetrate the rotor 42 in the axial direction.

[0024] <Compression Mechanism> The double-rotating scroll compressor 10 is equipped with a compression mechanism 30. The compression mechanism 30 is housed in a housing chamber 33. Therefore, the compression mechanism 30 is housed in the housing 11. The compression mechanism 30 compresses the refrigerant. The compression mechanism 30 is driven by a motor 40.

[0025] The compression mechanism 30 comprises a drive scroll 50 and a driven scroll 80. The drive scroll 50 has a drive substrate 51 and a drive spiral wall 52. The drive scroll 50 also has a drive outer peripheral wall 53. The drive substrate 51 is disc-shaped. A discharge port 51c is formed in the center of the drive substrate 51. The discharge port 51c is a circular hole. The discharge port 51c penetrates the drive substrate 51 in the thickness direction of the drive substrate 51. The drive spiral wall 52 rises from the drive substrate 51. The drive outer peripheral wall 53 rises from the outer periphery of the drive substrate 51. The drive outer peripheral wall 53 surrounds the drive spiral wall 52. A female screw hole 53c is formed on the end face of the drive outer peripheral wall 53 opposite to the drive substrate 51.

[0026] A valve housing recess 51a is formed on the end face of the drive substrate 51 opposite to the drive spiral wall 52. The inside of the valve housing recess 51a communicates with the discharge port 51c. The discharge port 51c opens to the bottom surface of the valve housing recess 51a. A female screw hole 51b is formed on the outer circumference of the end face of the drive substrate 51 opposite to the drive spiral wall 52.

[0027] The double-rotating scroll compressor 10 is equipped with a valve mechanism 57. The valve mechanism 57 is located within a valve housing recess 51a. The valve mechanism 57 is attached to the bottom surface of the valve housing recess 51a. The valve mechanism 57 is configured to open and close the discharge port 51c.

[0028] The compression mechanism 30 includes a first cover body 64. The first cover body 64 has a cover end wall 65 and a cover peripheral wall 66. Inside the first cover body 64, a housing portion 68 is formed, surrounded by the cover end wall 65 and the cover peripheral wall 66. The coil end of the stator 41 is housed in the housing portion 68. The cover end wall 65 is disc-shaped. An axial hole 65c is formed in the cover end wall 65. The axial hole 65c penetrates the cover end wall 65 in the thickness direction of the cover end wall 65. The axial hole 65c is formed in the central part of the cover end wall 65. The cover peripheral wall 66 extends from the outer circumference of the cover end wall 65. The axis of the cover peripheral wall 66 coincides with the axis of the axial hole 65c.

[0029] The first cover body 64 has bolt insertion holes 66a. The bolt insertion holes 66a penetrate the cover end wall 65 and the cover peripheral wall 66. The first end of the bolt insertion hole 66a opens to the end face of the cover peripheral wall 66 opposite to the cover end wall 65. The second end of the bolt insertion hole 66a opens to the end face of the cover end wall 65 opposite to the cover peripheral wall 66.

[0030] The compression mechanism 30 includes a sliding plate 60. The sliding plate 60 is a thin metal plate. The sliding plate 60 has a circular through hole 61. The through hole 61 penetrates the sliding plate 60 in the thickness direction of the sliding plate 60. The through hole 61 is formed in the center of the sliding plate 60. The sliding plate 60 has a bolt insertion hole 60c. The bolt insertion hole 60c penetrates the sliding plate 60 in the thickness direction of the sliding plate 60.

[0031] The sliding plate 60 is positioned opposite the protruding end face of the drive spiral wall 52 on the drive outer wall 53, and also opposite the cover end wall 65, with the bolt insertion hole 60c communicating with the bolt insertion hole 66a of the cover peripheral wall 66 and the female screw hole 53c of the drive outer peripheral wall 53. Both sides of the sliding plate 60 in the thickness direction are coated to reduce sliding resistance.

[0032] The first cover body 64 is positioned in the housing chamber 33 such that the first end of the bolt insertion hole 66a communicates with the bolt insertion hole 42a of the rotor 42, and the second end of the bolt insertion hole 66a communicates with the female screw hole 53c of the drive outer peripheral wall 53 via the bolt insertion hole 60c of the sliding plate 60. The rotor 42, the first cover body 64, the sliding plate 60, and the drive scroll 50 are integrated by a bolt 69 that passes through the bolt insertion hole 42a of the rotor 42, the bolt insertion hole 66a of the cover outer peripheral wall 66, and the bolt insertion hole 60c of the sliding plate 60 in that order and is screwed into the female screw hole 53c. In this way, the drive scroll 50 is integrated with the rotor 42. The first cover body 64 and the sliding plate 60 are sandwiched in the thrust direction X by the drive scroll 50 and the rotor 42.

[0033] As shown in Figure 3, the support shaft 22 of the protruding portion 34 is inserted inside the shaft hole 65c. The support shaft 22 is inserted inside the shaft hole 65c with its axis aligned with the axes of the shaft hole 65c and the through hole 61. A first radial bearing 26, which serves as a drive bearing, is provided between the shaft hole 65c and the support shaft 22. The first radial bearing 26 is a rolling bearing. The first radial bearing 26 has an inner ring 26a, an outer ring 26b, and rolling elements 26c. The rolling elements 26c are spherical. The inner ring 26a of the first radial bearing 26 is mounted on the support shaft 22 and is integral with the support shaft 22. The outer ring 26b is positioned on the outer circumference of the inner ring 26a and is press-fitted into the cover end wall 65. The outer ring 26b rotates integrally with the drive scroll 50 via the first cover body 64. The rolling element 26c is interposed between the inner ring 26a and the outer ring 26b. The first cover body 64 is rotatably supported on the support shaft 22 in the projection 34 via the first radial bearing 26. Therefore, the projection 34 has a support shaft 22 that rotatably supports the drive scroll 50 via the first radial bearing 26.

[0034] The first cover body 64 has an intake passage 65e. The intake passage 65e penetrates the cover end wall 65 in the thickness direction of the cover end wall 65. The intake passage 65e is located on the outer circumference side of the cover end wall 65, relative to the axial hole 65c. The intake passage 65e communicates with the housing 68 inside the cover peripheral wall 66.

[0035] As shown in Figure 1, the compression mechanism 30 includes a second cover body 70. The second cover body 70 is a circular block. An annular chamber-forming recess 71 is formed on one end face of the second cover body 70 in the thickness direction. The chamber-forming recess 71 extends around the axis of the second cover body 70. The second cover body 70 has bolt insertion holes 76a. The bolt insertion holes 76a are located on the outer circumference side of the chamber-forming recess 71. The bolt insertion holes 76a penetrate the second cover body 70 in the thickness direction of the second cover body 70.

[0036] A recess 72 is formed on the other end face of the second cover body 70 in the thickness direction. The recess 72 is circular in shape. The recess 72 is formed in the central part of the second cover body 70. The recess 72 penetrates the second cover body 70 in the thickness direction. The axis of the recess 72 coincides with the axis of the second cover body 70.

[0037] The compression mechanism 30 is equipped with a gasket 54. The gasket 54 is in the shape of a thin plate. The gasket 54 has a plurality of gasket holes 54a. The gasket holes 54a penetrate the gasket 54 in the thickness direction of the gasket 54. The gasket 54 has bolt insertion holes 54b. The bolt insertion holes 54b penetrate the gasket 54 in the thickness direction of the gasket 54.

[0038] The gasket 54 is positioned opposite the end face of the drive substrate 51 to the drive spiral wall 52, with the bolt insertion hole 54b and the female screw hole 51b communicating, and each gasket hole 54a communicating with the inside of the valve housing recess 51a. The second cover body 70 is positioned opposite the gasket 54, with the bolt insertion hole 76a and the bolt insertion hole 54b of the gasket 54 communicating. The bolts 77, passing through the bolt insertion hole 76a of the second cover body 70 and then the bolt insertion hole 54b of the gasket 54, are screwed into the female screw hole 51b, thereby integrating the second cover body 70, the gasket 54, and the drive scroll 50. In this way, the second cover body 70 is integrated with the drive scroll 50. The second cover body 70 is fixed to the end face of the drive substrate 51 to the end face of the drive substrate 51 to the drive spiral wall 52 via the gasket 54.

[0039] The opening of the chamber-forming recess 71 is closed by the gasket 54. The chamber-forming recess 71 and the gasket 54 form an annular discharge chamber 78. Thus, the second cover body 70 has a discharge chamber 78. The inside of the valve housing recess 51a and the discharge chamber 78 are in communication through the gasket holes 54a.

[0040] The boss portion 13b and the projection 15 are inserted into the inside of the recess 72. A second radial bearing 25 is provided between the outer circumferential surface of the insertion portion 15b and the circumferential surface located radially inward in the recess 72. The second radial bearing 25 is a rolling bearing. The second radial bearing 25 has an inner ring 25a, an outer ring 25b, and rolling elements 25c. The second cover body 70 is rotatably supported on the projection 15 via the second radial bearing 25. The inner ring 25a is fixed to the outer circumferential surface of the insertion portion 15b. The outer ring 25b is fixed to the circumferential surface located radially inward in the recess 72.

[0041] The drive scroll 50 is integrated with the rotor 42, the sliding plate 60, the first cover body 64, the gasket 54, and the second cover body 70. The drive scroll 50 is rotatably supported on the projection 34 via the first radial bearing 26 and on the projection 15 via the second radial bearing 25. Therefore, the drive scroll 50 is rotatably supported within the housing 11 with the first axis L1 as the center of rotation by both the projection 34 and the projection 15.

[0042] The area around the rotor 42, first cover body 64, drive scroll 50, gasket 54, and second cover body 70 in the containment chamber 33 is an intake pressure region. The driven scroll 80 has a driven substrate 81 and a driven spiral wall 82. The driven substrate 81 is disc-shaped. The driven substrate 81 faces the drive substrate 51. The driven spiral wall 82 stands upright from the driven substrate 81 toward the drive substrate 51. The driven spiral wall 82 meshes with the drive spiral wall 52. The drive substrate 51, drive spiral wall 52, driven substrate 81, and driven spiral wall 82 form a compression chamber 91. The compression chamber 91 compresses the refrigerant.

[0043] The driven scroll 80 is located inside the drive outer peripheral wall 53. The driven spiral wall 82 is located inside the drive outer peripheral wall 53. The space between the driven spiral wall 82 and the drive outer peripheral wall 53 forms an intake chamber 92, which is part of the intake pressure region. The intake chamber 92 is in communication with the intake passage 65e.

[0044] The driven base plate 81 has an accommodation recess 84. The accommodation recess 84 is cylindrically recessed from an end surface of the driven base plate 81 located on the opposite side from a driven spiral wall 82. The driven base plate 81 has a plurality of groove portions 55. The plurality of groove portions 55 are each formed around the accommodation recess 84 on the end surface of the driven base plate 81 on the opposite side from the driven spiral wall 82. The plurality of groove portions 55 are arranged at predetermined intervals in the circumferential direction of the driven base plate 81. An annular ring member 89 is fitted into each groove portion 55. A pin 67 is inserted into each ring member 89. Each pin 67 is protrudingly provided on an end surface of a cover end wall 65 of a first cover body 64 on the opposite side from a cover peripheral wall 66.

[0045] The protruding portion 34 protrudes from the housing end wall 17 toward the driving scroll 50 and the driven scroll 80. A shaft passage 27 is formed in the support shaft 22 of the protruding portion 34. The shaft passage 27 penetrates the support shaft 22 in the axial direction. The shaft passage 27 opens toward the oil storage chamber 24 at a first axial end of the support shaft 22, and opens toward the accommodation recess 84 at a second axial end thereof. An eccentric shaft 87 is provided on the support shaft 22. The eccentric shaft 87 is fitted into the shaft passage 27. The eccentric shaft 87 protrudes from the distal end of the support shaft 22. The eccentric shaft 87 extends parallel to the support shaft 22 at a position eccentric with respect to the axis of the support shaft 22. The eccentric shaft 87 protrudes from the distal end of the support shaft 22 toward the driven scroll 80. The eccentric shaft 87 is inserted into the accommodation recess 84.

[0046] The double-rotary scroll compressor 10 includes a cylindrical bush 86. The bush 86 has a fitting hole 86a. The fitting hole 86a penetrates the bush 86 in the axial direction of the bush 86 at a position eccentric with respect to the axis of the bush 86. The eccentric shaft 87 is fitted into the fitting hole 86a. The bush 86 is arranged inside the accommodation recess 84. The bush 86 can swing about the eccentric shaft 87.

[0047] As shown in FIG. 3, a third radial bearing 83 serving as a driven bearing is provided between the inner circumferential surface of the accommodating recess 84 and the outer circumferential surface of the bush 86. The third radial bearing 83 is a rolling bearing. The third radial bearing 83 includes an inner ring 83a, an outer ring 83b, and rolling elements 83c. The rolling elements 83c are spherical. The inner ring 83a is fixed to the outer circumferential surface of the bush 86. The outer ring 83b is fixed to the inner circumferential surface of the accommodating recess 84. The third radial bearing 83 is aligned with the first radial bearing 26 in the thrust direction X with the sliding plate 60 interposed therebetween. Therefore, the first radial bearing 26 and the third radial bearing 83 are arranged side by side in the thrust direction X.

[0048] As shown in FIG. 1, the driven scroll 80 is rotatably supported by the support shaft 22 via the third radial bearing 83. Therefore, the driven scroll 80 is rotatable about the axis of the bush 86 as the center of rotation. In the following description, a straight line passing through the axis of the bush 86 may be referred to as "second axis L2".

[0049] Electric power controlled by an inverter (not shown) is supplied to the motor coil 41b, thereby rotating the rotor 42. Accordingly, the first cover body 64, the driving scroll 50, the gasket 54, and the second cover body 70 integrally rotate about the first axis L1 as the rotation center. Therefore, the rotor 42 rotates about the same rotation center as that of the driving scroll 50. In this manner, the driving scroll 50 rotates within the housing 11. When the first cover body 64 rotates integrally with the driving scroll 50, each pin 67 presses each ring member 89 in the rotation direction of the first cover body 64. Accordingly, torque from the rotor 42 is transmitted to the driven scroll 80 via the first cover body 64, and the driven scroll 80 rotates about the second axis L2 as the rotation center. As described above, the driven scroll 80 rotates about a rotation center that is eccentric with respect to the rotation center of the driving scroll 50 as the driving scroll 50 rotates. The driven scroll 80 rotates in a state where the driven spiral wall 82 is positioned inside the driving outer peripheral wall 53.

[0050] Since the driven scroll 80 rotates on a center of rotation that is eccentric to the center of rotation of the drive scroll 50, the driven scroll 80 is restricted from rotating on its own axis relative to the drive scroll 50. The driven scroll 80 then revolves relative to the drive scroll 50. The volume of the compression chamber 91 changes as a result of the revolving motion of the driven scroll 80 relative to the drive scroll 50.

[0051] The refrigerant drawn into the containment chamber 33 from the intake port 14a passes between the rotor 42 and the stator 41 and flows inside the cover peripheral wall 66 of the first cover body 64. The refrigerant that has flowed inside the cover peripheral wall 66 flows into the intake chamber 92 via the intake passage 65e. The refrigerant that has flowed into the intake chamber 92 is drawn into the compression chamber 91. Therefore, the first cover body 64 of the compression mechanism 30 has an intake passage 65e formed therein that allows the refrigerant from the containment chamber 33 to be drawn into the compression chamber 91. The refrigerant drawn into the compression chamber 91 is compressed in the compression chamber 91 as the volume of the compression chamber 91 decreases due to the relative orbital motion of the driven scroll 80 with respect to the drive scroll 50. The refrigerant compressed in the compression chamber 91 is discharged from the discharge port 51c into the valve housing recess 51a and also discharged into the discharge chamber 78 via the gasket hole 54a. In this way, the refrigerant compressed in the compression chamber 91 is discharged into the discharge chamber 78. The refrigerant discharged into the discharge chamber 78 is discharged to the outside of the housing 11 through the discharge shaft 15c and the discharge port 13a.

[0052] <Details of the oil storage chamber> As shown in Figures 2 and 3, the support shaft 22 has a guide groove 28. The guide groove 28 is recessed in the inner surface 22c of the support shaft 22 that defines the oil storage chamber 24. The guide groove 28 communicates with the shaft path 27 at its upper end and extends vertically downward from the shaft path 27 along the radial direction of the support shaft 22. The upper end of the guide groove 28, that is, the part of the guide groove 28 that communicates with the shaft path 27, is designated as the outlet 28a, and the lower end of the guide groove 28 is designated as the inlet 28b.

[0053] A cover plate 32 is attached to the inner surface 22c of the support shaft 22 that defines the oil storage chamber 24. The cover plate 32 is disc-shaped and slightly smaller than the inner diameter of the support cylinder wall 20. The cover plate 32 is fixed to the support shaft 22 by a plurality of bolts 31. The cover plate 32 covers almost the entire inner surface 22c of the support shaft 22. The opening in the guide groove 28 toward the oil storage chamber 24 is closed by the cover plate 32. As a result, a guide passage 29 is formed in the protruding portion 34. In other words, the guide passage 29 is formed by closing the guide groove 28 recessed in the inner surface 22c of the support shaft 22 with the cover plate 32.

[0054] A notch 32a is formed in the cover plate 32. The notch 32a is formed at the lower end of the cover plate 32. The inlet 28b of the guide groove 28 faces the notch 32a. As a result, the inlet 28b communicates with the oil storage chamber 24 through the notch 32a. On the other hand, the outlet 28a communicates with the shaft 27 as the outlet of the guide passage 29.

[0055] The guide passage 29 is connected to the shaft passage 27 and the oil storage chamber 24. The guide passage 29 has an outlet 28a that communicates with the shaft passage 27 and an inlet 28b that is located vertically below the oil storage chamber 24 and communicates with the oil storage chamber 24, relative to the shaft passage 27 and the outlet 28a. Therefore, the shaft passage 27 communicates with the oil storage chamber 24 through the guide passage 29 and the notch 32a.

[0056] The guide passage 29 formed in the support shaft 22 is an outlet passage that allows the lubricating oil 37 from the oil storage chamber 24 to flow out of the protruding portion 34. The opening area of ​​the guide passage 29 to the oil storage chamber 24 is the opening area at the inlet 28b of the guide passage 29. Note that the opening area of ​​the guide passage 29 is the cross-sectional area along the direction perpendicular to the vertical direction in which the guide passage 29 extends.

[0057] The opening to the oil storage chamber 24 in the inflow passage 35 is the opening to the oil storage chamber 24 in the communication hole 18a. The area of ​​the opening to the oil storage chamber 24 in the inflow passage 35 is the area of ​​the opening to the oil storage chamber 24 in the communication hole 18a. The opening area of ​​the guide passage 29 described above is smaller than the opening area of ​​the inflow passage 35. If the opening area of ​​the guide passage 29, that is, the opening area of ​​the outflow passage to the oil storage chamber 24, is too large, a large amount of lubricating oil 37 will flow out of the oil storage chamber 24, making it difficult to store lubricating oil 37 in the oil storage chamber 24. For this reason, the opening area of ​​the guide passage 29 is narrowed to be smaller than the opening area of ​​the inflow passage 35. The flow path cross-sectional area of ​​the inflow passage 35 in the direction perpendicular to the vertical direction in which the inflow passage 35 extends is constant throughout the entire vertical direction.

[0058] The containment chamber 33 is in communication with the intake port 14a. Therefore, refrigerant is drawn into the containment chamber 33 from outside the housing 11 through the intake port 14a. Thus, the containment chamber 33, defined inside the housing 11, is in the refrigerant suction pressure region. The oil storage chamber 24 is in communication with the containment chamber 33 through the inflow passage 35. Furthermore, the inflow passage 35 connects the containment chamber 33 and the oil storage chamber 24, resulting in approximately the same pressure inside the containment chamber 33 and the oil storage chamber 24. The oil storage chamber 24 stores the lubricating oil 37 contained in the refrigerant drawn into the containment chamber 33. Thus, the inflow passage 35 connects the containment chamber 33, which is in the suction pressure region, and the oil storage chamber 24. Therefore, the housing 11 has an inflow passage 35 that connects the containment chamber 33 and the oil storage chamber 24.

[0059] <Lubricating Oil Passage> A lubricating oil passage 100 is connected to the oil storage chamber 24, which circulates the lubricating oil 37 stored in the oil storage chamber 24 toward the intake passage 65e. The lubricating oil passage 100 is formed by a guide passage 29, an axial passage 27, a fitting hole 86a formed in the bush 86, a receiving recess 84, an axial hole 65c, and a receiving section 68.

[0060] <Flow of Lubricating Oil> The refrigerant drawn into the containment chamber 33 contains lubricating oil 37. The refrigerant drawn into the containment chamber 33 is affected by the centrifugal force of the rotating drive scroll 50 and rotor 42. The lubricating oil 37 contained in the refrigerant is centrifuged. The lubricating oil 37 separated from the refrigerant flows into the oil storage chamber 24 through the inflow passage 35.

[0061] Furthermore, the refrigerant drawn into the containment chamber 33 passes through the refrigerant passage 45 between the stator 41 and the rotor 42 and flows inside the cover peripheral wall 66 of the first cover body 64. The refrigerant that has flowed inside the cover peripheral wall 66 flows into the intake chamber 92 via the intake passage 65e. The refrigerant that reaches the containment section 68 is drawn into the compression chamber 91 via the intake passage 65e and the intake chamber 92. In addition, a portion of the refrigerant drawn into the containment chamber 33 flows into the oil storage chamber 24 through the inflow passage 35.

[0062] In the dual-rotation scroll compressor 10, the refrigerant passage 45 functions as a throttling passage for the refrigerant. In other words, the refrigerant passage 45 circulates the refrigerant while reducing its pressure. As a result, the refrigerant that has circulated through the refrigerant passage 45 and reached the suction passage 65e is at a lower pressure than before it circulated through the refrigerant passage 45. Therefore, the pressure of the refrigerant drawn into the suction passage 65e is lower than the pressure in the oil storage chamber 24.

[0063] The lubricating oil passage 100 described above circulates the lubricating oil 37 in the oil storage chamber 24 toward the intake passage 65e due to the difference between the pressure of the refrigerant drawn into the intake passage 65e and the pressure inside the oil storage chamber 24. In other words, the lubricating oil 37 separated from the refrigerant circulates in the oil storage chamber 24. In the lubricating oil passage 100, the lubricating oil 37 in the oil storage chamber 24 circulates toward the intake passage 65e as follows.

[0064] The lubricating oil 37 stored in the oil storage chamber 24 flows from the notch 32a of the cover plate 32 to the inlet 28b of the guide passage 29. The passage area at the point where the inlet 28b communicates with the oil storage chamber 24 is smaller than the passage area at the point where the outlet 28a communicates with the shaft passage 27. As a result, the guide passage 29 guides the lubricating oil 37 to the shaft passage 27 by the flow rate difference pressure between the outlet 28a and the inlet 28b. Specifically, in the guide passage 29, the lubricating oil 37 is drawn up by the flow rate difference pressure between the outlet 28a and the inlet 28b. The lubricating oil 37 that has reached the shaft passage 27 through the guide passage 29 flows between the inner circumferential surface of the shaft passage 27 and the circumferential surface of the eccentric shaft 87, and through the fitting hole 86a of the bush 86 to reach the housing recess 84.

[0065] The lubricating oil 37 that reaches the housing recess 84 flows between the third radial bearing 83 and the housing recess 84, through the inside of the third radial bearing 83 and the inside of the first radial bearing 26, and reaches the housing section 68. As a result, the sliding parts such as the third radial bearing 83 and the first radial bearing 26 are lubricated by the lubricating oil 37. Furthermore, the lubricating oil 37 that reaches the housing recess 84 flows between the sliding plate 60 and the driven substrate 81, and the sliding parts between the sliding plate 60 and the driven substrate 81 are lubricated by the lubricating oil 37. The lubricating oil 37 that reaches the housing section 68 flows through the intake passage 65e and is drawn into the compression chamber 91 via the intake chamber 92.

[0066] <Operation of the Embodiment> When the double-rotating scroll compressor 10 is in operation, heat is generated in the stator 41 as power is supplied to the motor 40. The heat generated in the stator 41 is directly transferred to the support cylinder wall 20 of the fixed base end 36 of the stator 41. The heat transferred to the support cylinder wall 20 is then transferred to the support shaft 22. Furthermore, the heat transferred to the support shaft 22 is transferred to the lubricating oil 37 flowing through the oil reservoir 24, thereby warming the oil reservoir 24 and, consequently, the lubricating oil 37 flowing through the guide passage 29.

[0067] According to the above embodiment, the following effects can be obtained: (1) The lubricating oil 37 flowing through the oil reservoir 24 is warmed by the heat transmitted to the support shaft 22. As a result, the decrease in the temperature of the lubricating oil 37 is suppressed, and the increase in the viscosity of the lubricating oil 37 can be suppressed. As a result, even if the opening area to the oil reservoir 24 in the guide passage 29 is smaller than the opening area to the oil reservoir 24 in the inflow passage 35, the lubricating oil 37 can be efficiently discharged to the outside of the protrusion 34 through the guide passage 29. As a result, for example, even in cold weather, the lubricating oil 37 discharged from the protrusion 34 can lubricate the third radial bearing 83 and the first radial bearing 26, and can also lubricate the sliding part between the sliding plate 60 and the driven scroll 80.

[0068] (2) The base end 36 of the protrusion 34 is cylindrical. The oil storage chamber 24 is provided inside the base end 36. The heat transmitted from the stator 41 to the base end 36 is transmitted to the lubricating oil 37 stored in the oil storage chamber 24, and the lubricating oil 37 stored in the oil storage chamber 24 is warmed by the heat generated by the motor 40. For this reason, even if lubricating oil 37 is stored in the oil storage chamber 24, the lubricating oil 37 can be efficiently drained out of the protrusion 34 through the guide passage 29.

[0069] (3) The stator 41 is fixed to the support cylinder wall 20 which forms the base end portion 36 of the protrusion 34. The support shaft 22 which forms the guide passage 29 is integrally formed with the support cylinder wall 20. In other words, the support body 19 is a single piece in which the support shaft 22 and the support cylinder wall 20 are continuous without any breaks. Therefore, compared to the case in which the support cylinder wall 20 and the support shaft 22 are formed separately, the heat transferred from the stator 41 to the support cylinder wall 20 is efficiently transferred to the support shaft 22. As a result, the double-rotating scroll compressor 10 can efficiently heat the lubricating oil 37 flowing through the guide passage 29.

[0070] (4) The guide passage 29 is formed by a guide groove 28 formed on the inner surface 22c of the support shaft 22 that defines the oil storage chamber 24, and a cover plate 32 that closes the guide groove 28 from the inside of the oil storage chamber 24. For this reason, the guide passage 29 can be easily formed.

[0071] (5) In the guide passage 29, the lubricating oil 37 is drawn up using the flow rate difference pressure between the outlet 28a and the inlet 28b. The viscosity increase of the lubricating oil 37 is suppressed by the heat from the support shaft 22. For this reason, even though the double-rotating scroll compressor 10 is configured to draw up the lubricating oil 37 against gravity using the flow rate difference pressure, the viscosity increase of the lubricating oil 37 is suppressed, allowing the lubricating oil 37 to flow smoothly through the guide passage 29.

[0072] (6) The opening area at the inlet 28b of the guide passage 29 is formed to be small enough to store lubricating oil 37 in the oil storage chamber 24, while preventing the stored lubricating oil 37 from easily flowing out of the oil storage chamber 24. For this reason, an increase in the viscosity of the lubricating oil 37 is a factor that hinders the outflow of the lubricating oil 37. However, the double-rotating scroll compressor 10 can efficiently heat the lubricating oil 37 with the heat from the stator 41 and suppress the increase in viscosity, so even with a guide passage 29 having a small opening area, the lubricating oil 37 can be efficiently discharged to the outside of the protrusion 34.

[0073] (7) The base end portion 36 defining the oil storage chamber 24 comprises a cover cylinder wall 18 and a support cylinder wall 20 fixed to its outer circumference. Furthermore, an elastic body 23 is interposed between the cover cylinder wall 18 and the support cylinder wall 20. For this reason, heat from the stator 41 is not easily transferred to the cover cylinder wall 18. However, in the double-rotation scroll compressor 10, the support cylinder wall 20 of the support body 19 is fixed to the cover cylinder wall 18, and the stator 41 is fixed to the support cylinder wall 20. For this reason, heat from the stator 41 is directly transferred to the support shaft 22 which is integrated with the support cylinder wall 20. As a result, by using a support body 19 separate from the cover cylinder wall 18 as the protruding portion 34, the lubricating oil 37 in the oil storage chamber 24 can be efficiently heated by the support shaft 22.

[0074] <Examples of Modifications> This embodiment can be implemented with the following modifications. This embodiment and the following examples of modifications can be combined with each other to the extent that they do not contradict each other technically.

[0075] As shown in Figure 4, the base end portion 36 of the protrusion 34 may be formed from the cover cylinder wall 18 and the support cylinder wall 20 in the thrust direction X, while the portion closer to the support shaft 22 in the thrust direction X may be formed from the support cylinder wall 20 alone. This portion of the support cylinder wall 20 closer to the support shaft 22 is a heat transfer section in which the lubricating oil 37 directly contacts the inner surface of the protrusion 34 that defines the oil storage chamber 24. Therefore, the protrusion 34 has a heat transfer section at a position that overlaps with the stator 41 in the radial direction of the stator 41. In this configuration, the portion of the base end portion 36 formed from the support cylinder wall 20 alone forms the oil storage chamber 24. The lubricating oil 37 in the oil storage chamber 24 is directly in contact with the tip end portion (heat transfer section) of the support cylinder wall 20 and is directly heated by the heat from that tip end portion. As a result, the lubricating oil 37 in the oil storage chamber 24 is heated efficiently.

[0076] ○As shown in Figure 5, the cover plate 32 may have an exposure opening 301 that exposes the inner surface 22c of the support shaft 22 toward the oil storage chamber 24. The exposure opening 301 is, for example, a long groove extending from the periphery of the cover plate 32 toward the center of the cover plate 32. When the cover plate 32 is fixed to the support shaft 22, a portion of the inner surface 22c of the support shaft 22 is exposed toward the oil storage chamber 24 through the exposure opening 301 of the cover plate 32. As a result, the cover plate 32 and the portion of the inner surface 22c of the support shaft 22 that faces the exposure opening 301 are exposed to the oil storage chamber 24. This allows the lubricating oil 37 in the oil storage chamber 24 to receive heat directly from the portion of the inner surface 22c of the support shaft 22 that faces the exposure opening 301. As a result, the lubricating oil 37 in the oil storage chamber 24 and the lubricating oil 37 flowing through the guide passage 29 can be heated efficiently.

[0077] ○The guide groove 28 does not necessarily have to be formed on the support shaft 22, in which case the double-rotating scroll compressor 10 also does not have a cover plate 32. As shown in Figure 6, the outlet passage 39 for draining the lubricating oil 37 from the oil storage chamber 24 is formed within the thickness of the support shaft 22 (for example, the flange-shaped portion extending radially from the base end of the support shaft 22 toward the support cylinder wall 20). Specifically, the inlet 39a of the outlet passage 39 that communicates with the oil storage chamber 24 opens on the inner surface 22c of the support shaft 22 so as to be located vertically below the oil storage chamber 24. The outlet passage 39 then penetrates the flange-shaped portion of the support shaft 22 in its thickness direction and opens to the outside of the support shaft 22. In this case, the outlet 39b of the outlet passage 39 opens toward the first radial bearing 26.

[0078] The first radial bearing 26 and the third radial bearing 83 are arranged side by side in the thrust direction X. Therefore, the first radial bearing 26 can be efficiently lubricated by the lubricating oil 37 that has flowed out of the oil reservoir 24. In addition, the lubricating oil 37 supplied to the first radial bearing 26 flows along the first radial bearing 26 in the thrust direction X. Furthermore, the lubricating oil 37 supplied to the first radial bearing 26 is sent to the outer circumference of the first radial bearing 26 by the centrifugal force generated by the rotation of the first cover body 64. As a result, the lubricating oil 37 is efficiently supplied from the first radial bearing 26 to the third radial bearing 83, and also efficiently supplied to the sliding part of the driven scroll 80.

[0079] Furthermore, the outflow passage 39 formed in the support shaft 22 may bend inside the support shaft 22 and extend to communicate with the shaft path 27. ○The passage communicating with the guide passage 29 is not limited to the shaft path 27. For example, a passage may be formed in the eccentric shaft 87 that penetrates the eccentric shaft 87 axially and connects the inside of the shaft path 27 with the housing recess 84, and a passage communicating with the guide passage 29 may be formed from this passage and the shaft path 27.

[0080] Alternatively, the passage communicating with the guide passage 29 may be as follows: A separate passage may be formed in the support shaft 22, separate from the shaft passage 27, and a bush passage may be formed in the bush 86 to communicate with this separate passage. The lubricating oil 37 may then be supplied from the guide passage 29 to the third radial bearing 83 via the separate passage and the bush passage.

[0081] Alternatively, the passage communicating with the guide path 29 may be as follows: A through passage is formed in the support shaft 22, passing through the support shaft 22 in the axial direction, with the first end of the through passage communicating with the guide path 29, and the second end of the through passage opening at the axial end surface of the support shaft 22 and facing the third radial bearing 83.

[0082] ○ The guide path 29 may extend above the shaft path 27. ○ The projection 34 may be formed without using the support 19. In this case, the projection 34 is formed from a cover cylinder wall 18 as a base end 36 and a support shaft 22 that protrudes from the cover cylinder wall 18 toward the drive scroll 50 and the driven scroll 80. The support shaft 22 is fixed to the cover cylinder wall 18 by welding or bolting.

[0083] ○ At least one of the first radial bearing 26 and the third radial bearing 83 may be a sliding bearing. ○ At least one of the first radial bearing 26 and the third radial bearing 83 may be a needle bearing in which the rolling elements are needles.

[0084] ○The base end 36 of the protruding portion 34 does not have to be cylindrical. In this case, a lubricating oil flow passage extending in the thrust direction X is formed inside the base end 36 of the protruding portion 34. The first end of the lubricating oil flow passage communicates with an outflow passage 39 shown in Figure 6, which is formed to penetrate the support shaft 22 in the thrust direction X. The second end of the lubricating oil flow passage opens toward the housing end wall 17. A communication passage is formed within the thickness of the housing end wall 17, and the second end of the lubricating oil flow passage communicates with this communication passage. The communication passage communicates with the housing chamber 33. As a result, a lubricating oil flow passage through which lubricating oil 37 separated from the refrigerant flows is provided inside the protruding portion 34. Furthermore, the housing 11 has a connecting passage that connects the storage chamber 33 and the lubricating oil flow passage, and the support shaft 22 has a guide passage 29 that allows the lubricating oil 37 from the lubricating oil flow passage to flow out of the protruding portion 34.

Claims

1. A double-rotating scroll compressor comprising: a housing whose interior is an intake pressure region; a compression mechanism housed within the housing and configured to compress a fluid; and a motor configured to drive the compression mechanism, wherein the compression mechanism comprises: a drive substrate and a drive scroll having a drive spiral wall rising from the drive substrate and rotating within the housing; a driven substrate facing the drive substrate and a driven scroll having a driven spiral wall rising from the driven substrate toward the drive substrate and meshing with the drive spiral wall, wherein the driven scroll rotates with respect to the rotation center of the drive scroll as the drive scroll rotates, and a compression chamber for compressing the fluid is partitioned by the drive substrate, the drive spiral wall, the driven substrate, and the driven spiral wall, and the motor comprises: a stator extending cylindrically in the thrust direction; and a rotor rotating on the outer circumference of the stator at the same rotation center as the rotation center of the drive scroll, wherein the housing comprises: housing end walls, A double-rotating scroll compressor having a projection that protrudes from the end wall of the housing toward the drive scroll and the driven scroll, the projection having a base end and a support shaft that protrudes from the base end toward the drive scroll and the driven scroll and rotatably supports the drive scroll via a drive bearing, the driven scroll being rotatably supported on the support shaft via a driven bearing, a lubricating oil passage through which lubricating oil separated from the fluid flows is provided inside the projection, an inlet passage is formed in the housing that connects the suction pressure region and the lubricating oil passage, an outlet passage is formed in the support shaft that allows the lubricating oil from the lubricating oil passage to flow out of the projection, the opening area of ​​the outlet passage toward the lubricating oil passage is smaller than the opening area of ​​the inlet passage toward the lubricating oil passage, the stator being fixed to the outer surface of the base end, and the lubricating oil passage and the stator being connected in a heat-transferable manner.

2. The double-rotating scroll compressor according to claim 1, wherein the base end is a cylindrical body, and the lubricating oil flow passage has an oil storage chamber inside the base end for storing the lubricating oil.

3. The double-rotation scroll compressor according to claim 2, wherein the outlet of the outflow passage that communicates with the oil storage chamber opens below the oil storage chamber, and the outlet of the outflow passage opens toward the drive bearing.

4. The drive bearing comprises an inner ring integral with the support shaft, an outer ring disposed on the outer circumference of the inner ring and rotating integrally with the drive scroll, and rolling elements interposed between the inner ring and the outer ring; the driven bearing comprises an inner ring supported by the protrusion, an outer ring disposed on the outer circumference of the inner ring and rotating integrally with the driven scroll, and rolling elements interposed between the inner ring and the outer ring; and the drive bearing and the driven bearing are arranged side by side in the thrust direction, as described in claim 2.

5. The compression mechanism has an intake passage for drawing the fluid in the intake pressure region into the compression chamber, and the oil storage chamber is connected to a lubricating oil passage for circulating the lubricating oil in the oil storage chamber toward the intake passage by the difference between the pressure of the fluid drawn into the intake passage and the pressure in the oil storage chamber, the lubricating oil passage includes an axial path that penetrates the support shaft in the axial direction, the axial path opening toward the oil storage chamber at a first end in the axial direction and opening toward a housing recess housing the driven bearing in the driven scroll at a second end in the axial direction, and a guide path as an outflow passage connecting the axial path and the oil storage chamber, the guide path has an outlet communicating with the axial path and an inlet located below the axial path and the outlet and communicating with the oil storage chamber, and the guide path guides the lubricating oil in the oil storage chamber toward the axial path by the flow rate difference pressure between the outlet and the inlet, the double-rotating scroll compressor according to claim 2.

6. The double-rotation scroll compressor according to claim 5, wherein the guide path is formed by closing a guide groove recessed in the inner surface of the support shaft that defines the oil storage chamber with a cover plate fixed to the support shaft.

7. The double-rotating scroll compressor according to claim 6, wherein the cover plate has an exposure opening formed therein that exposes the inner surface toward the oil storage chamber.

8. The double-rotation scroll compressor according to claim 1, wherein the protrusion has a heat transfer portion at a position overlapping with the stator in the radial direction of the stator, where the lubricating oil directly contacts the inner surface of the protrusion that defines the lubricating oil flow passage.

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