compressor

Abstract

The present application provides a compressor which suppresses pressure loss of refrigerant gas while improving oil separation performance. The small-diameter cylinder portion causes the refrigerant gas flowing in from the through hole to generate a swirling flow, and the refrigerant gas swirling around the small-diameter cylinder portion flows toward the annular gap between the large-diameter cylinder portion and the inner peripheral surface of the oil separation chamber. The large-diameter cylinder portion gradually increases in outer diameter as it moves away from the small-diameter cylinder portion. Thus, the refrigerant gas easily repeatedly swirls around the small-diameter cylinder portion until it reaches the annular gap. The refrigerant gas from which oil is separated passes through the gap, flows from the outside of the small-diameter cylinder bottom portion to the inside of the small-diameter cylinder bottom portion via the plurality of through holes, and flows toward the opening of the large-diameter cylinder portion. The total of the flow passage cross-sectional areas of the plurality of through holes is larger than the flow passage cross-sectional area in the radial direction of the small-diameter cylinder bottom portion, so the refrigerant gas easily flows from the outside of the small-diameter cylinder bottom portion to the inside of the small-diameter cylinder bottom portion via the plurality of through holes.

Description

Technical Field

[0001] This invention relates to compressors. Background Technology

[0002] The compressor comprises a housing, a rotating shaft, and a compression mechanism. The rotating shaft is rotatably supported by the housing. The compression mechanism is housed within the housing. The compression mechanism compresses refrigerant gas under the rotation of the rotating shaft. The housing has a discharge port. The discharge port allows the refrigerant gas compressed by the compression mechanism to exit the housing. The housing is divided into a discharge chamber and an oil separation chamber. The refrigerant gas compressed by the compression mechanism exits into the discharge chamber. The oil separation chamber separates the oil contained in the refrigerant gas discharged into the discharge chamber. The discharge chamber and the oil separation chamber are connected by a through-hole.

[0003] For example, as disclosed in Patent Document 1, an oil separation cylinder is provided in the oil separation chamber. The oil separation cylinder has a large-diameter cylindrical section and a small-diameter cylindrical section. The large-diameter cylindrical section is fixed to the inner peripheral wall of the oil separation chamber. The large-diameter cylindrical section faces the discharge port opening. The small-diameter cylindrical section has an outer diameter smaller than that of the large-diameter cylindrical section. The small-diameter cylindrical section extends from the large-diameter cylindrical section towards a side opposite to the discharge port relative to the large-diameter cylindrical section. Furthermore, the small-diameter cylindrical section causes the refrigerant gas flowing in from the through hole to generate a swirling flow. As a result, the oil contained in the refrigerant gas is separated from the refrigerant gas by centrifugal separation. The refrigerant gas separated from the oil passes through the inner side of the small-diameter cylindrical section and the inner side of the large-diameter cylindrical section and is discharged from the discharge port to the outside of the housing.

[0004] Existing technical documents

[0005] Patent documents

[0006] Patent Document 1: Japanese Patent Publication No. 2020-517858 Summary of the Invention

[0007] The problem that the invention aims to solve

[0008] However, for efficient separation of oil contained in the refrigerant gas, it is necessary to facilitate the generation of a swirling flow of the refrigerant gas flowing in from the through-hole under the action of the small-diameter cylinder. To facilitate this swirling flow, the outer diameter of the small-diameter cylinder is minimized. This increases the number of times the refrigerant gas swirls around the small-diameter cylinder, thus enabling efficient separation of the oil contained in the refrigerant gas. However, when the outer diameter of the small-diameter cylinder is reduced, the refrigerant gas separated from the oil has difficulty flowing into the inner part of the cylinder, resulting in increased pressure loss. Therefore, it is desirable to improve oil separation performance while simultaneously suppressing refrigerant gas pressure loss.

[0009] Solution for solving the problem

[0010] A compressor for solving the above-mentioned problems includes: a housing; a rotating shaft rotatably supported on the housing; and a compression mechanism housed within the housing, which compresses refrigerant gas under the rotation of the rotating shaft. The housing is divided into a discharge chamber and an oil separation chamber. The discharge chamber has a discharge port for discharging the refrigerant gas compressed by the compression mechanism to the outside of the housing, and discharges the refrigerant gas compressed by the compression mechanism into the discharge chamber. The oil separation chamber separates oil contained in the refrigerant gas discharged into the discharge chamber. The discharge chamber and the oil separation chamber are connected by a through hole. A bottomed cylindrical oil separation cylinder is provided in the oil separation chamber. The oil separation cylinder has: a large-diameter cylindrical portion fixed to the inner peripheral wall of the oil separation chamber and opening towards the discharge port; and a small-diameter cylindrical portion having an outer diameter smaller than that of the large-diameter cylindrical portion and opening towards the discharge port. The large-diameter cylindrical section extends from the side opposite to the discharge port, and the small-diameter cylindrical section causes the refrigerant gas flowing in from the through-hole to generate a swirling flow. The small-diameter cylindrical section has: an annular expansion section whose outer diameter gradually increases away from the large-diameter cylindrical section; and a small-diameter cylindrical bottom extending from the expansion section toward the side opposite to the large-diameter cylindrical section that sandwiches the expansion section in the middle. Multiple through-holes are provided at the bottom of the small-diameter cylindrical section to connect the outer side of the bottom of the small-diameter cylindrical section in the oil separation chamber with the opening of the large-diameter cylindrical section. An annular gap is formed between the expansion section and the inner circumferential surface of the oil separation chamber. The through-holes open between the portion of the large-diameter cylindrical section that fixes the large-diameter cylindrical section and the portion that divides the gap on the inner circumferential surface of the oil separation chamber. The total flow path cross-sectional area of ​​the multiple through-holes is larger than the radial flow path cross-sectional area of ​​the bottom of the small-diameter cylindrical section.

[0011] Accordingly, the small-diameter cylinder section causes the refrigerant gas flowing in from the through-hole to swirl, and while swirling around the small-diameter cylinder section, the refrigerant gas flows toward the annular gap between the expanding section and the inner circumferential surface of the oil separation chamber. At this time, the expanding section gradually increases in outer diameter as it moves away from the large-diameter cylinder section. Therefore, the refrigerant gas easily swirls repeatedly around the small-diameter cylinder section until it reaches the annular gap. As a result, the oil contained in the refrigerant gas can be efficiently separated from the refrigerant gas. Furthermore, the refrigerant gas separated from the oil flows through the gap from the outside of the bottom of the small-diameter cylinder through multiple through-holes to the inside of the bottom of the small-diameter cylinder and toward the opening of the large-diameter cylinder section. At this time, the total cross-sectional area of ​​the flow path of the multiple through-holes is larger than the radial cross-sectional area of ​​the flow path of the bottom of the small-diameter cylinder, thus facilitating the flow of refrigerant gas from the outside of the bottom of the small-diameter cylinder through the multiple through-holes to the inside of the bottom of the small-diameter cylinder. Therefore, pressure loss of the refrigerant gas can be suppressed. Based on the above, it is possible to improve oil separation performance while also suppressing refrigerant gas pressure loss.

[0012] In the compressor described above, it is preferable that the outer diameter of the bottom of the small-diameter cylinder is smaller than the outer diameter of the expanded-diameter section.

[0013] Accordingly, it is possible to easily suppress oil adhesion to the bottom end of the small-diameter cylinder in the expansion section. Therefore, it is possible to avoid the problem of oil adhesion obstructing the refrigerant gas from passing through the gaps. As a result, pressure loss of the refrigerant gas can be suppressed.

[0014] In the compressor described above, preferably, the outer diameter of the bottom of the small-diameter cylinder is equal to the outer diameter of the expanded-diameter section.

[0015] Therefore, the flow path cross-sectional area on the inner side of the bottom of the small-diameter cylinder can be maximized, making it easier for the refrigerant gas to flow on the inner side of the bottom of the small-diameter cylinder. As a result, the pressure loss of the refrigerant gas can be further suppressed.

[0016] In the compressor described above, it is preferable that the small-diameter cylinder portion has an annular diameter-reducing portion in which the outer diameter gradually decreases as it moves from the large-diameter cylinder portion toward the diameter-expanding portion.

[0017] Accordingly, the refrigerant gas from the through hole easily flows along the narrowed section and from the large-diameter section toward the expanding section. Therefore, the refrigerant gas easily swirls around the small-diameter section while flowing toward the annular gap, thus enabling efficient separation of the oil contained in the refrigerant gas.

[0018] In the compressor described above, preferably, the inner diameter of the expanding section gradually increases as it moves away from the large-diameter cylinder section, and the inner diameter of the reducing section gradually decreases as it moves away from the large-diameter cylinder section. This allows for improved oil separation performance due to the baffle effect.

[0019] In the compressor described above, it is preferable that the through hole is circular. A structure with a circular through hole is preferred in that multiple through holes are provided at the bottom of the small-diameter cylinder.

[0020] In the compressor described above, it is preferable that the through hole is elongated. This elongated through hole shape is preferred in that multiple through holes are provided at the bottom of the small-diameter cylinder.

[0021] In the compressor described above, it is preferable that the length direction of the through hole is aligned with the axial direction of the bottom of the small-diameter cylinder. This alignment of the length direction of the through hole with the axial direction of the bottom of the small-diameter cylinder is preferred in terms of facilitating flow from the outside of the bottom of the small-diameter cylinder through multiple through holes to the inside of the bottom of the small-diameter cylinder.

[0022] Invention Effects

[0023] According to the present invention, it is possible to improve oil separation performance while suppressing refrigerant gas pressure loss. Attached Figure Description

[0024] Figure 1 This is a cross-sectional view of the compressor in the implementation method.

[0025] Figure 2 It is a cross-sectional view showing an enlarged portion of the compressor.

[0026] Figure 3 This is a 3D view of the oil separator cylinder.

[0027] Figure 4 This is a side view of the oil separator in the modified example.

[0028] Figure 5 This is a cross-sectional view of the oil separator.

[0029] Figure 6 This is a side view of the oil separator in the modified example.

[0030] Explanation of reference numerals in the attached figures

[0031] 10: Compressor, 11: Housing, 15: Rotating shaft, 40: Discharge chamber, 42: Oil separation chamber, 42a: Inner peripheral wall, 44: Discharge hole, 46: Through hole, 50: Oil separation cylinder, 51: Large diameter cylinder section, 52: Small diameter cylinder section, 53: Reducing diameter section, 54: Expanding diameter section, 55: Bottom of small diameter cylinder, 58: Through hole, 59: Gap, C1: Compression mechanism. Detailed Implementation

[0032] The following is in accordance with Figures 1-3 This section describes one embodiment of a compressor. The compressor in this embodiment is used, for example, in a vehicle air conditioning system.

[0033] <Basic Structure of a Compressor>

[0034] like Figure 1 As shown, the compressor 10 has a cylindrical housing 11. The housing 11 includes a motor housing 12, a shaft support housing 13, and a discharge housing 14. The motor housing 12, shaft support housing 13, and discharge housing 14 are made of metal. For example, the motor housing 12, shaft support housing 13, and discharge housing 14 are made of aluminum. In addition, the compressor 10 has a rotating shaft 15. The rotating shaft 15 is housed within the housing 11.

[0035] The motor housing 12 has a plate-shaped end wall 12a and a cylindrical peripheral wall 12b. The peripheral wall 12b extends cylindrically from the outer periphery of the end wall 12a. The axial direction of the peripheral wall 12b is aligned with the axial direction of the rotating shaft 15. The motor housing 12 has a plurality of internally threaded holes 12c. Each internally threaded hole 12c is formed at the open end of the peripheral wall 12b. It should be noted that... Figure 1For ease of explanation, only one internal threaded hole 12c is shown in the diagram. Additionally, the motor housing 12 has a suction port 12h. The suction port 12h draws in refrigerant gas. The suction port 12h is formed in the portion of the peripheral wall 12b located on the end wall 12a side. The suction port 12h connects the inside and outside of the motor housing 12.

[0036] The motor housing 12 has a cylindrical bearing retainer 12d. The bearing retainer 12d protrudes from the center of the inner surface of the end wall 12a. The first end of the rotating shaft 15, which is one of the axial ends, is inserted into the bearing retainer 12d. The compressor 10 includes a bearing 16. The bearing 16 is, for example, a rolling bearing. The bearing 16 is disposed between the inner circumferential surface of the bearing retainer 12d and the outer circumferential surface of the first end of the rotating shaft 15. Furthermore, the first end of the rotating shaft 15 is rotatably supported on the motor housing 12 by means of the bearing 16.

[0037] The shaft support housing 13 has a plate-shaped end wall 17 and a cylindrical peripheral wall 18. The peripheral wall 18 extends cylindrically from the outer periphery of the end wall 17. The axial direction of the peripheral wall 18 is aligned with the axial direction of the rotating shaft 15. In addition, the shaft support housing 13 has an annular flange wall 19. The flange wall 19 extends radially outward from the end of the outer peripheral surface of the peripheral wall 18 on the side opposite to the end wall 17 toward the rotating shaft 15.

[0038] The shaft support housing 13 has a circular through hole 17a. The through hole 17a is formed in the center of the end wall 17. The through hole 17a passes through the end wall 17 in the thickness direction. A rotating shaft 15 is inserted into the through hole 17a. The front end face 15e of the rotating shaft 15, located on the second end side which is the other end in the axial direction, is located inside the peripheral wall 18.

[0039] The compressor 10 includes a bearing 21. The bearing 21 is, for example, a rolling bearing. The bearing 21 is disposed between the inner circumferential surface of the peripheral wall 18 and the outer circumferential surface of the rotating shaft 15. Furthermore, the rotating shaft 15 is rotatably supported on the shaft support housing 13 by means of the bearing 21. Therefore, the shaft support housing 13 supports the rotating shaft 15 so that it can rotate. In this way, the rotating shaft 15 is rotatably supported relative to the housing 11.

[0040] The shaft support housing 13 has a plurality of bolt through holes 19a. Each bolt through hole 19a is formed on the outer periphery of the flange wall 19. Each bolt through hole 19a penetrates the flange wall 19 along its thickness direction. Each bolt through hole 19a of the flange wall 19 communicates with each internal threaded hole 12c of the motor housing 12. It should be noted that, in Figure 1 For ease of explanation, only one bolt insertion hole 19a is shown in the figure.

[0041] The compressor 10 includes a motor chamber 20. The motor chamber 20 is defined by a motor housing 12 and a shaft support housing 13. The motor housing 12 and the shaft support housing 13 together define the motor chamber 20. Thus, the motor chamber 20 is formed within the housing 11. The motor chamber 20 is in communication with the suction port 12h. Refrigerant gas from the suction port 12h is drawn into the motor chamber 20.

[0042] The compressor 10 includes a motor 22. The motor 22 is housed within a motor chamber 20. The 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 has a rotor core 24a fixed to the rotating shaft 15 and a plurality of permanent magnets (not shown) disposed on the rotor core 24a.

[0043] 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. Furthermore, the rotor 24 rotates by supplying power controlled by an inverter (not shown) to the motor coil 23b. As a result, the rotating shaft 15 rotates integrally with the rotor 24. Therefore, the motor 22 causes the rotating shaft 15 to rotate.

[0044] The compressor 10 includes a compression mechanism C1. The compression mechanism C1 has a fixed scroll 25 and a rotary scroll 26. Therefore, the compressor 10 has a fixed scroll 25 and a rotary scroll 26. The compression mechanism C1 is a scroll type. Therefore, the compressor 10 is a scroll compressor. The rotary scroll 26 revolves relative to the fixed scroll 25 under the action of the rotation of the rotating shaft 15.

[0045] The fixed scroll 25 has a fixed base plate 25a and a fixed scroll wall 25b. The fixed base plate 25a is circular. A discharge port 25h is formed in the center of the fixed base plate 25a. The discharge port 25h is circular. The discharge port 25h passes through the fixed base plate 25a along its thickness direction. The fixed scroll wall 25b stands upright from the fixed base plate 25a. In addition, the fixed scroll 25 has an outer peripheral wall 25c. 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 scroll wall 25b.

[0046] The compressor 10 includes a valve mechanism 25v. The valve mechanism 25v is mounted on the side of the fixed base plate 25a opposite to the fixed vortex wall 25b. The valve mechanism 25v is configured to open and close the discharge port 25h.

[0047] The swirling scroll 26 has a swirling base plate 26a and a swirling scroll wall 26b. The swirling base plate 26a is circular. The swirling base plate 26a is opposite to the fixed base plate 25a. The swirling scroll wall 26b rises from the swirling base plate 26a toward the fixed base plate 25a. The swirling scroll wall 26b engages with the fixed scroll wall 25b. The swirling scroll 26 is located inside the outer peripheral wall 25c. The swirling scroll 26 revolves within the outer peripheral wall 25c. The front end face of the fixed scroll wall 25b contacts the swirling base plate 26a.

[0048] The compressor 10 includes a compression chamber 27. The compression chamber 27 is divided by a fixed base plate 25a, a fixed scroll wall 25b, a rotating base plate 26a, and a rotating scroll wall 26b. Therefore, the compression chamber 27 is formed between the fixed scroll 25a and the rotating scroll 26b. The compression chamber 27 draws in and compresses refrigerant gas from the outside.

[0049] The compressor 10 has a protrusion 28. The rotary base plate 26a has a cylindrical protrusion 28. The protrusion 28 protrudes cylindrically from the end face 26e of the rotary base plate 26a on the side opposite to the fixed base plate 25a. The axial direction of the protrusion 28 is aligned with the axial direction of the rotation shaft 15.

[0050] The rotary substrate 26a has a plurality of grooves 26d. The plurality of grooves 26d are respectively formed around the protrusions 28 in the end face 26e of the rotary substrate 26a. The plurality of grooves 26d are arranged at predetermined intervals along the circumferential direction of the rotation axis 15. It should be noted that... Figure 1 For ease of explanation, only one groove 26d is shown in the figure. A circular ring member 29 is embedded within each groove 26d. A pin 30 is inserted into each ring member 29. Each pin 30 protrudes from the end face 13e on the side of the vortex disk 26 within the shaft support housing 13.

[0051] The compressor 10 includes an elastic plate 31. The elastic plate 31 is annular. The elastic plate 31 is clamped between the end face 13e of the shaft support housing 13 and the open end face of the outer peripheral wall 25c. Furthermore, the elastic plate 31 constantly applies force to the rotating scroll 26 toward the fixed scroll 25.

[0052] The compressor 10 includes an eccentric shaft 32. The eccentric shaft 32 protrudes from the front end face 15e of the rotating shaft 15 at an eccentric position relative to the axis L1 of the rotating shaft 15 toward the rotary scroll 26. The eccentric shaft 32 is integrally formed with the rotating shaft 15. The axial direction of the eccentric shaft 32 is aligned with the axial direction of the rotating shaft 15. The eccentric shaft 32 is inserted into the protrusion 28.

[0053] The compressor 10 includes a counterweight 33 and a bushing 34. The bushing 34 is fitted into the outer peripheral surface of the eccentric shaft 32. The counterweight 33 and the bushing 34 are integrated. The counterweight 33 is housed within the peripheral wall 18 of the shaft support housing 13. The rotary scroll 26 is rotatably supported on the eccentric shaft 32 relative to the eccentric shaft 32 by means of the bushing 34 and the rolling bearing B2.

[0054] The rotation of the rotating shaft 15 is transmitted to the vortex disk 26 via the eccentric shaft 32, bushing 34, and rolling bearing B2. As a result, the vortex disk 26 rotates. Furthermore, each pin 30 contacts the inner circumferential surface of each ring member 29, thereby preventing the rotation of the vortex disk 26 and allowing only its revolution. Thus, the vortex disk 26 revolves while its vortex wall 26b is in contact with the fixed vortex wall 25b. Furthermore, with the revolution of the vortex disk 26, the volume of the compression chamber 27 decreases, thereby compressing the refrigerant gas. The vortex disk 26 revolves inside the outer circumferential wall 25c along with the rotation of the rotating shaft 15. The counterweight 33 counteracts the centrifugal force acting on the vortex disk 26 during its revolution. Therefore, the imbalance of the vortex disk 26 is reduced.

[0055] The discharge housing 14 has a plate-shaped end wall 14a and a cylindrical peripheral wall 14b. The peripheral wall 14b extends cylindrically from the outer periphery of the end wall 14a. The axial direction of the peripheral wall 14b is aligned with the axial direction of the rotation shaft 15. The peripheral wall 14b surrounds the fixed scroll 25. Therefore, the fixed scroll 25 is housed within the housing 11. Thus, the compression mechanism C1 is housed within the housing 11.

[0056] The discharge housing 14 has a plurality of bolt insertion holes 14c. Each bolt insertion hole 14c is formed in the peripheral wall 14b. It should be noted that, in Figure 1 For ease of explanation, only one bolt insertion hole 14c is shown in the figure. Each bolt insertion hole 14c communicates with each bolt insertion hole 19a of the flange wall 19.

[0057] Bolts B1, passing through bolt holes 14c, are screwed into internal threaded holes 12c of motor housing 12 via bolt holes 19a in flange wall 19. Thus, shaft support housing 13 is connected to the peripheral wall 12b of motor housing 12, and discharge housing 14 is connected to the flange wall 19 of shaft support housing 13. Therefore, motor housing 12, shaft support housing 13, and discharge housing 14 are arranged in this order along the axial direction of rotation shaft 15. Fixed scroll 25 is clamped between the end wall 14a of discharge housing 14 and shaft support housing 13. In this way, fixed scroll 25 is fixed to housing 11.

[0058] The compressor 10 includes a suction passage 35. The suction passage 35 has a first groove 36, a first hole 37, a second groove 38, and a second hole 39. The first groove 36 is formed on a portion of the inner circumferential surface of the peripheral wall 12b of the motor housing 12. The first groove 36 opens at the open end of the peripheral wall 12b. The first hole 37 is formed on the outer circumferential portion of the flange wall 19 of the shaft support housing 13. The first hole 37 penetrates the flange wall 19 along its thickness direction. The first hole 37 communicates with the first groove 36. The second groove 38 is formed on a portion of the inner circumferential surface of the peripheral wall 14b of the discharge housing 14. The second groove 38 communicates with the first hole 37. The second hole 39 is formed on the outer circumferential wall 25c of the fixed scroll 25. The second hole 39 penetrates the outer circumferential wall 25c along its thickness direction. The second hole 39 communicates with the second groove 38. The second hole 39 communicates with the outermost circumferential portion of the compression chamber 27.

[0059] The refrigerant gas in the motor chamber 20 is drawn into the compression chamber 27 through the first slot 36, the first hole 37, the second slot 38, and the second hole 39. The refrigerant gas drawn into the compression chamber 27 is compressed within it by the revolution of the vortex disk 26, which accompanies the rotation of the rotating shaft 15. Thus, the compression mechanism C1 compresses the refrigerant gas under the action of the rotation of the rotating shaft 15.

[0060] The compressor 10 includes a discharge chamber 40. The discharge chamber 40 is divided between the fixed base plate 25a and the end wall 14a of the discharge housing 14. Therefore, the housing 11 divides the discharge chamber 40. The discharge chamber 40 communicates with the discharge port 25h. Refrigerant gas compressed in the compression chamber 27 is discharged into the discharge chamber 40. Therefore, refrigerant gas compressed by the compression mechanism C1 is discharged into the discharge chamber 40. In addition, the compressor 10 includes an oil storage chamber 41. The oil storage chamber 41 is formed in the end wall 14a of the discharge housing 14. Oil is stored in the oil storage chamber 41.

[0061] The compressor 10 includes an oil separation chamber 42. The oil separation chamber 42 separates the oil contained in the refrigerant gas discharged into the discharge chamber 40. The oil separation chamber 42 is formed inside the discharge housing 14. Therefore, the housing 11 divides the oil separation chamber 42. The oil separation chamber 42 is formed within an elongated cylindrical outer cylinder 43, which is part of the end wall 14a of the discharge housing 14. The outer cylinder 43 extends radially along the rotation axis 15. Therefore, the oil separation chamber 42 extends radially along the rotation axis 15.

[0062] The first end of the outer cylinder 43 becomes a discharge port 44 for discharging the refrigerant gas compressed by the compression mechanism C1 to the outside of the housing 11. Therefore, the housing 11 has a discharge port 44. The discharge port 44 communicates with the oil separation chamber 42.

[0063] A through hole 46 is formed in the outer cylinder 43. The discharge chamber 40 and the oil separation chamber 42 are connected by the through hole 46. The through hole 46 guides the refrigerant gas discharged into the discharge chamber 40 into the oil separation chamber 42.

[0064] An oil drain hole 47 is formed in the discharge housing 14. The first end of the oil drain hole 47 communicates with the side of the oil separation chamber 42 opposite to the drain hole 44. The second end of the oil drain hole 47 communicates with the oil storage chamber 41. The oil separation chamber 42 is connected to the oil storage chamber 41 via the oil drain hole 47.

[0065] A back pressure chamber 48 is defined between the rotating base plate 26a of the rotating scroll 26 and the shaft support housing 13. The back pressure chamber 48 is formed within the housing 11 on the side opposite to the fixed base plate 25a, relative to the rotating base plate 26a. The shaft support housing 13 separates the back pressure chamber 48 from the motor chamber 20. The inner side of the peripheral wall 18 of the shaft support housing 13 is part of the back pressure chamber 48. Furthermore, the gap between the elastic plate 31 and the shaft support housing 13 is part of the back pressure chamber 48.

[0066] The compressor 10 includes an oil return passage 49. The oil return passage 49 extends from the oil reservoir 41 through the discharge housing 14 and the shaft support housing 13 to the back pressure chamber 48. Therefore, the oil return passage 49 connects the oil reservoir 41 and the back pressure chamber 48. Furthermore, the oil stored in the oil reservoir 41 returns to the back pressure chamber 48 via the oil return passage 49.

[0067] <Oil Separator>

[0068] like Figure 2 As shown, an oil separator 50 is provided in the oil separation chamber 42. The oil separator 50 is a bottomed cylindrical shape. The oil separator 50 has a large-diameter cylindrical portion 51 and a small-diameter cylindrical portion 52. The large-diameter cylindrical portion 51 is cylindrical. The large-diameter cylindrical portion 51 is fixed to the inner peripheral wall 42a of the oil separation chamber 42 by being pressed into it. The axis of the large-diameter cylindrical portion 51 is aligned with the axis of the outer cylinder 43. Therefore, the oil separator 50 is provided in the oil separation chamber 42 with the axial direction of the oil separator 50 aligned with the radial direction of the rotation shaft 15. The first end of the large-diameter cylindrical portion 51 opens toward the discharge hole 44.

[0069] The smaller diameter cylindrical section 52 is continuous with the second end of the larger diameter cylindrical section 51. The smaller diameter cylindrical section 52 extends from the larger diameter cylindrical section 51 toward the side opposite to the discharge hole 44 relative to the larger diameter cylindrical section 51. The smaller diameter cylindrical section 52 has an outer diameter smaller than that of the larger diameter cylindrical section 51. The axis of the smaller diameter cylindrical section 52 is aligned with the axis of the larger diameter cylindrical section 51.

[0070] like Figure 2 as well as Figure 3As shown, the small-diameter cylinder portion 52 has a reduced diameter portion 53, an expanded diameter portion 54, and a small-diameter cylinder bottom 55. The reduced diameter portion 53 is annular. The reduced diameter portion 53 extends from the second end of the large-diameter cylinder portion 51. The first end of the reduced diameter portion 53 is continuous with the second end of the large-diameter cylinder portion 51. The second end of the reduced diameter portion 53 is continuous with the first end of the expanded diameter portion 54. The outer diameter of the reduced diameter portion 53 gradually decreases as it moves from the large-diameter cylinder portion 51 toward the expanded diameter portion 54. The inner diameter of the reduced diameter portion 53 gradually decreases as it moves away from the large-diameter cylinder portion 51.

[0071] The expanding section 54 is annular. It extends from the second end of the contracting section 53. The outer diameter of the expanding section 54 gradually increases as it moves away from the large-diameter cylinder section 51. The end of the expanding section 54 located on the side opposite to the large-diameter cylinder section 51 is annular, extending around the axis of the small-diameter cylinder section 52. The boundary between the expanding section 54 and the contracting section 53 is the portion in the small-diameter cylinder section 52 where the outer diameter becomes the smallest. The inner diameter of the expanding section 54 is constant.

[0072] The small-diameter cylinder bottom 55 has a small-diameter peripheral wall 56 and a small-diameter bottom wall 57. The small-diameter peripheral wall 56 extends cylindrically from the enlarged diameter portion 54. Therefore, the small-diameter cylinder bottom 55 extends from the enlarged diameter portion 54 toward the side that sandwiches the enlarged diameter portion 54 in the middle and is opposite to the large-diameter cylinder portion 51. The outer diameter of the small-diameter peripheral wall 56 is constant. The inner diameter of the small-diameter peripheral wall 56 is constant. The inner diameter of the small-diameter peripheral wall 56 is equal to the inner diameter of the enlarged diameter portion 54. The outer diameter of the small-diameter peripheral wall 56 is smaller than the outer diameter of the enlarged diameter portion 54. In detail, the outer diameter of the small-diameter peripheral wall 56 is smaller than the outer diameter of the end of the enlarged diameter portion 54 located on the side opposite to the large-diameter cylinder portion 51. Thus, the outer diameter of the small-diameter cylinder bottom 55 is smaller than the outer diameter of the enlarged diameter portion 54. The small-diameter bottom wall 57 seals the end of the small-diameter peripheral wall 56 on the side opposite to the enlarged diameter portion 54. The small-diameter bottom wall 57 is plate-shaped.

[0073] Multiple through holes 58 are provided at the bottom 55 of the small-diameter cylinder. These through holes 58 penetrate the small-diameter peripheral wall 56. The through holes 58 connect the outer side of the bottom 55 of the small-diameter cylinder in the oil separation chamber 42 to the opening of the large-diameter cylinder section 51. The through holes 58 are circular. The total cross-sectional area of ​​the flow paths of the multiple through holes 58 is larger than the radial cross-sectional area of ​​the bottom 55 of the small-diameter cylinder. The total cross-sectional area of ​​the flow paths of the multiple through holes 58 is larger than the area of ​​the bottom wall 57 of the small-diameter cylinder.

[0074] like Figure 2As shown, an annular gap 59 is formed between the enlarged diameter section 54 and the inner circumferential surface of the oil separation chamber 42. Specifically, the gap 59 is an annular space formed in the enlarged diameter section 54 at the end opposite to the large-diameter cylindrical section 51 and between the end and the inner circumferential surface of the oil separation chamber 42. A through-hole 46 opens between the portion of the large-diameter cylindrical section 51 that fixes it and the portion that divides the gap 59 on the inner circumferential surface of the oil separation chamber 42. The through-hole 46 opens towards the small-diameter cylindrical section 52. The small-diameter cylindrical section 52 causes the refrigerant gas flowing in through the through-hole 46 to swirl.

[0075] [The Role of the Implementation Method]

[0076] Next, the function of the implementation method will be explained.

[0077] The refrigerant gas, compressed in the compression chamber 27 and discharged into the discharge chamber 40 via the discharge port 25h, flows into the oil separation chamber 42 through the guide hole 46. The refrigerant gas from the guide hole 46 flows along the narrowing section 53 and toward the expanding section 54. While swirling around the small-diameter cylinder 52, the refrigerant gas flows toward the annular gap 59 between the expanding section 54 and the inner circumferential surface of the oil separation chamber 42. At this time, the expanding section 54 gradually expands its outer diameter away from the large-diameter cylinder 51. Therefore, the refrigerant gas easily swirls repeatedly around the small-diameter cylinder 52 until it reaches the annular gap 59. Furthermore, centrifugal force is applied to the oil contained in the refrigerant gas, and the oil is separated from the refrigerant gas within the oil separation chamber 42.

[0078] The refrigerant gas separated from the oil flows through the gap 59 and into the inner side of the small-diameter cylinder bottom 55 via multiple through holes 58 from the outside of the small-diameter cylinder bottom 55, and then flows toward the opening of the large-diameter cylinder section 51. At this time, since the total cross-sectional area of ​​the multiple through holes 58 is larger than the cross-sectional area of ​​the small-diameter cylinder bottom 55, the refrigerant gas easily flows into the inner side of the small-diameter cylinder bottom 55 from the outside of the small-diameter cylinder bottom 55 via the multiple through holes 58. Therefore, the pressure loss of the refrigerant gas is suppressed.

[0079] Refrigerant gas flowing toward the opening of the large-diameter cylinder 51 flows into the outer cylinder 43 through the opening of the large-diameter cylinder 51 and passes through the outer cylinder 43. Furthermore, the refrigerant gas that has passed through the outer cylinder 43 flows out through the discharge port 44 into an external refrigerant circuit (not shown).

[0080] The oil separated from the refrigerant gas in the oil separation chamber 42 flows toward the oil drain hole 47. The oil flowing toward the oil drain hole 47 is then discharged into the oil storage chamber 41 and stored there. The oil stored in the oil storage chamber 41 flows back to the back pressure chamber 48 via the oil return passage 49.

[0081] [Effects of the Implementation Method]

[0082] The following effects can be achieved in the implementation method.

[0083] (1) The small-diameter cylinder 52 causes the refrigerant gas flowing in from the through hole 46 to swirl, and while swirling around the small-diameter cylinder 52, the refrigerant gas flows toward the annular gap 59 between the expanding diameter section 54 and the inner circumferential surface of the oil separation chamber 42. At this time, the outer diameter of the expanding diameter section 54 gradually increases as it moves away from the large-diameter cylinder 51. Therefore, the refrigerant gas easily swirls around the small-diameter cylinder 52 until it reaches the annular gap 59. As a result, the oil contained in the refrigerant gas can be efficiently separated from the refrigerant gas. Furthermore, the refrigerant gas separated from the oil flows through the gap 59 and into the inner side of the small-diameter cylinder bottom 55 through multiple through holes 58 from the outside of the small-diameter cylinder bottom 55 and toward the opening of the large-diameter cylinder 51. At this point, the total cross-sectional area of ​​the flow path of the multiple through holes 58 is larger than the radial cross-sectional area of ​​the flow path of the bottom 55 of the small-diameter cylinder. Therefore, refrigerant gas can easily flow from the outside of the bottom 55 of the small-diameter cylinder through the multiple through holes 58 to the inside of the bottom 55 of the small-diameter cylinder. Thus, the pressure loss of the refrigerant gas can be suppressed. Based on the above, it is possible to improve the oil separation performance while also suppressing the pressure loss of the refrigerant gas.

[0084] (2) The outer diameter of the small-diameter cylinder bottom 55 is smaller than the outer diameter of the expansion section 54. Therefore, it is easy to suppress oil from adhering to the end of the small-diameter cylinder bottom 55 side in the expansion section 54. Thus, it is possible to avoid the problem of oil adhering to the end of the small-diameter cylinder bottom 55 side in the expansion section 54, which would obstruct the refrigerant gas from passing through the gap 59. As a result, it is possible to suppress the pressure loss of the refrigerant gas.

[0085] (3) The small-diameter cylinder portion 52 has an annular diameter-reducing portion 53 whose outer diameter gradually decreases as it moves from the large-diameter cylinder portion 51 toward the expanding diameter portion 54. Accordingly, the refrigerant gas from the through hole 46 can easily flow along the diameter-reducing portion 53 and flow from the large-diameter cylinder portion 51 toward the expanding diameter portion 54. Therefore, the refrigerant gas can easily swirl around the small-diameter cylinder portion 52 while flowing toward the annular gap 59, thus enabling the oil contained in the refrigerant gas to be further separated from the refrigerant gas efficiently.

[0086] (4) The through hole 58 is round. The structure of the through hole 58 being round is preferred in that multiple through holes 58 are provided at the bottom 55 of the small diameter cylinder.

[0087] [Example of Change]

[0088] It should be noted that the above embodiments can be modified as follows. The above embodiments and the following modifications can be combined with each other within a technically compatible scope.

[0089] ○ For example Figure 4 as well asFigure 5 As shown, the outer diameter of the small-diameter cylinder bottom 55 can also be equal to the outer diameter of the expanding section 54. Specifically, the outer diameter of the small-diameter peripheral wall 56 is equal to the outer diameter of the end portion of the expanding section 54 located on the side opposite to the large-diameter cylinder section 51. Therefore, the flow path cross-sectional area inside the small-diameter cylinder bottom 55 can be maximized, thus facilitating the flow of refrigerant gas inside the small-diameter cylinder bottom 55. As a result, pressure loss of the refrigerant gas can be further suppressed.

[0090] In addition, such as Figure 5 As shown, the inner diameter of the expanding section 54 can also gradually increase as it moves away from the large-diameter cylinder section 51. Accordingly, the oil separation performance can be improved due to the baffle effect.

[0091] ○ For example Figure 6 As shown, the through hole 58 can also be elongated. The length direction of the through hole 58 is aligned with the axial direction of the small-diameter cylinder bottom 55. The structure where the through hole 58 is elongated is preferred in that multiple through holes 58 are provided at the small-diameter cylinder bottom 55. Furthermore, the structure where the length direction of the through hole 58 is aligned with the axial direction of the small-diameter cylinder bottom 55 is preferred in that the water flows from the outside of the small-diameter cylinder bottom 55 to the inside of the small-diameter cylinder bottom 55 through multiple through holes 58.

[0092] ○ in Figure 6 In the embodiment shown, the length direction of the through hole 58 may not be aligned with the axial direction of the bottom 55 of the small-diameter cylinder.

[0093] In one embodiment, the small-diameter cylinder portion 52 may also have a structure that does not have an annular diameter-reducing portion 53 in which the outer diameter gradually decreases as it moves from the large-diameter cylinder portion 51 toward the diameter-expanding portion 54.

[0094] In one embodiment, the end of the enlarged diameter portion 54 located on the side opposite to the large diameter cylindrical portion 51 may also extend spirally around the axis of the small diameter cylindrical portion 52.

[0095] In one embodiment, the oil separation chamber 42 may also extend along the axial direction of the rotation shaft 15. Furthermore, the oil separation cylinder 50 may be disposed within the oil separation chamber 42 with its axial direction aligned with that of the rotation shaft 15.

[0096] In this embodiment, the compressor 10 may not be the type driven by the motor 22, but may be the type driven by the vehicle's engine.

[0097] In this embodiment, the compressor 10 is used in a vehicle air conditioning system, but it is not limited to this. In short, the compressor 10 is only required to be a structure that compresses refrigerant gas, and its application can be appropriately changed.

[0098] In this embodiment, the compression mechanism C1 is a scroll type consisting of a fixed scroll 25 and a rotating scroll 26, but it is not limited to this; for example, it can also be a piston type or a blade type. In short, the structure of the compression mechanism C1 is not particularly limited.

[0099] The above embodiments include the structures described in the following notes.

[0100] <Postscript 1>

[0101] A compressor comprising:

[0102] case;

[0103] A rotating shaft, rotatably supported on the housing; and

[0104] A compression mechanism, housed within the housing, compresses the refrigerant gas under the action of the rotation of the rotating shaft.

[0105] The housing is divided into a discharge chamber and an oil separation chamber. The discharge chamber has a discharge port for discharging the refrigerant gas compressed by the compression mechanism to the outside of the housing and for discharging the refrigerant gas compressed by the compression mechanism into the discharge chamber. The oil separation chamber separates the oil contained in the refrigerant gas discharged into the discharge chamber.

[0106] The discharge chamber and the oil separation chamber are connected by a through hole.

[0107] A bottomed cylindrical oil separation cylinder is provided in the oil separation chamber.

[0108] The oil separator cylinder has the following features:

[0109] A large-diameter cylindrical section, fixed to the inner peripheral wall of the oil separation chamber and facing the discharge port opening; and

[0110] The smaller diameter cylindrical section has an outer diameter smaller than that of the larger diameter cylindrical section, and extends from the larger diameter cylindrical section toward a side opposite to the discharge port relative to the larger diameter cylindrical section.

[0111] The small-diameter cylindrical section causes the refrigerant gas flowing in from the through hole to generate a swirling flow.

[0112] The compressor is characterized in that,

[0113] The small-diameter cylindrical section has:

[0114] The annular expanding section gradually increases in outer diameter as it moves away from the large-diameter cylindrical section; and

[0115] The bottom of the small-diameter cylinder extends from the expanding section on the side opposite to the large-diameter cylinder section, which sandwiches the expanding section in the middle.

[0116] The bottom of the small-diameter cylinder is provided with multiple through holes that connect the outer side of the bottom of the small-diameter cylinder in the oil separation chamber to the opening of the large-diameter cylinder.

[0117] An annular gap is formed between the enlarged diameter section and the inner circumferential surface of the oil separation chamber.

[0118] The through hole opens between the portion of the large-diameter cylinder that is fixed on the inner circumferential surface of the oil separation chamber and the portion that divides the gap.

[0119] The total cross-sectional area of ​​the flow path of the plurality of through holes is larger than the radial cross-sectional area of ​​the flow path at the bottom of the small-diameter cylinder.

[0120] <Appendix 2>

[0121] The compressor according to Appendix 1 is characterized in that,

[0122] The outer diameter of the bottom of the small-diameter cylinder is smaller than the outer diameter of the expanded-diameter section.

[0123] <Appendix 3>

[0124] The compressor according to Appendix 1 is characterized in that,

[0125] The outer diameter of the bottom of the small-diameter cylinder is equal to the outer diameter of the expanded-diameter section.

[0126] <Appendix 4>

[0127] The compressor according to any one of Appendix 1 to Appendix 3 is characterized in that,

[0128] The small-diameter cylindrical section has an annular diameter-reducing section in which the outer diameter gradually decreases as it moves from the large-diameter cylindrical section toward the diameter-expanding section.

[0129] <Appendix 5>

[0130] The compressor according to Appendix 4 is characterized in that,

[0131] The inner diameter of the expanding section gradually increases as it moves away from the large-diameter cylinder section, and the inner diameter of the shrinking section gradually decreases as it moves away from the large-diameter cylinder section.

[0132] <Appendix 6>

[0133] The compressor according to any one of Appendix 1 to Appendix 5 is characterized in that,

[0134] The through hole is circular.

[0135] <Appendix 7>

[0136] The compressor according to any one of Appendix 1 to Appendix 5 is characterized in that,

[0137] The through hole is elongated.

[0138] <Postscript 8>

[0139] The compressor according to Appendix 7 is characterized in that,

[0140] The length direction of the through hole is consistent with the axial direction of the bottom of the small-diameter cylinder.

Claims

1. A compressor comprising: case; A rotating shaft, rotatably supported on the housing; and A compression mechanism, housed within the housing, compresses the refrigerant gas under the action of the rotation of the rotating shaft. The housing is divided into a discharge chamber and an oil separation chamber. The discharge chamber has a discharge port for discharging the refrigerant gas compressed by the compression mechanism to the outside of the housing and for discharging the refrigerant gas compressed by the compression mechanism into the discharge chamber. The oil separation chamber separates the oil contained in the refrigerant gas discharged into the discharge chamber. The discharge chamber and the oil separation chamber are connected by a through hole. A bottomed cylindrical oil separation cylinder is provided in the oil separation chamber. The oil separator cylinder has the following features: A large-diameter cylindrical section, fixed to the inner peripheral wall of the oil separation chamber and facing the discharge port opening; and The smaller diameter cylindrical section has an outer diameter smaller than that of the larger diameter cylindrical section, and extends from the larger diameter cylindrical section toward a side opposite to the discharge port relative to the larger diameter cylindrical section. The small-diameter cylindrical section causes the refrigerant gas flowing in from the through hole to generate a swirling flow. The compressor is characterized in that, The small-diameter cylindrical section has: The annular expanding section gradually increases in outer diameter as it moves away from the large-diameter cylindrical section; and The bottom of the small-diameter cylinder extends from the expanding section on the side opposite to the large-diameter cylinder section, which sandwiches the expanding section in the middle. The bottom of the small-diameter cylinder is provided with multiple through holes that connect the outer side of the bottom of the small-diameter cylinder in the oil separation chamber to the opening of the large-diameter cylinder. An annular gap is formed between the enlarged diameter section and the inner circumferential surface of the oil separation chamber. The through hole opens between the portion of the large-diameter cylinder that is fixed on the inner circumferential surface of the oil separation chamber and the portion that divides the gap. The total cross-sectional area of ​​the flow path of the plurality of through holes is larger than the cross-sectional area of ​​the flow path at the bottom of the small-diameter cylinder.

2. The compressor according to claim 1, characterized in that, The outer diameter of the bottom of the small-diameter cylinder is smaller than the outer diameter of the expanded-diameter section.

3. The compressor according to claim 1, characterized in that, The outer diameter of the bottom of the small-diameter cylinder is equal to the outer diameter of the expanded-diameter section.

4. The compressor according to any one of claims 1 to 3, characterized in that, The small-diameter cylindrical section has an annular diameter-reducing section in which the outer diameter gradually decreases as it moves from the large-diameter cylindrical section toward the diameter-expanding section.

5. The compressor according to claim 4, characterized in that, The inner diameter of the expanding section gradually increases as it moves away from the large-diameter cylinder section, and the inner diameter of the shrinking section gradually decreases as it moves away from the large-diameter cylinder section.

6. The compressor according to any one of claims 1 to 5, characterized in that, The through hole is circular.

7. The compressor according to any one of claims 1 to 5, characterized in that, The through hole is elongated.

8. The compressor according to claim 7, characterized in that, The length direction of the through hole is consistent with the axial direction of the bottom of the small-diameter cylinder.

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