compressor

Abstract

To improve oil separation performance while suppressing pressure loss of refrigerant gas. [Solution] The small-diameter cylindrical portion 52 generates a swirling flow in the refrigerant gas flowing in from the conduction hole 46, and the refrigerant gas flows towards the annular gap 59 between the enlarged diameter portion 54 and the inner circumferential surface of the oil separation chamber 42 while swirling around the small-diameter cylindrical portion 52. The outer diameter of the enlarged diameter portion 54 gradually increases as it moves away from the large-diameter cylindrical portion 51. Therefore, the refrigerant gas can easily swirl repeatedly around the small-diameter cylindrical portion 52 before reaching the annular gap 59. The refrigerant gas from which the oil has been separated passes through the gap 59 and flows into the inside of the small-diameter cylindrical bottom portion 55 from the outside of the small-diameter cylindrical bottom portion 55 through multiple through holes 58, and flows towards the opening of the large-diameter cylindrical portion 51. Since the sum of the flow path cross-sectional areas of the multiple through holes 58 is larger than the flow path cross-sectional area of ​​the small diameter cylinder bottom 55 in the radial direction, refrigerant gas can easily flow from the outside of the small diameter cylinder bottom 55 into the inside of the small diameter cylinder bottom 55 through the multiple through holes 58.

Description

Technical Field

[0001] The present invention relates to a compressor.

Background Art

[0002] A compressor includes a housing, a rotating shaft, and a compression mechanism. The rotating shaft is rotatably supported by the housing. The compression mechanism is housed inside the housing. The compression mechanism compresses refrigerant gas by the rotation of the rotating shaft. The housing has a discharge hole. The discharge hole discharges the refrigerant gas compressed by the compression mechanism to the outside of the housing. The housing partitions a discharge chamber and an oil separation chamber. Refrigerant gas compressed by the compression mechanism is discharged 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 conduction 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 cylinder portion and a small-diameter cylinder portion. The large-diameter cylinder portion is fixed to the inner peripheral wall of the oil separation chamber. The large-diameter cylinder portion opens toward the discharge hole. The small-diameter cylinder portion has an outer diameter smaller than that of the large-diameter cylinder portion. The small-diameter cylinder portion extends from the large-diameter cylinder portion toward the side opposite to the discharge hole with respect to the large-diameter cylinder portion. Then, the small-diameter cylinder portion generates a swirling flow in the refrigerant gas flowing in from the conduction hole. As a result, the oil contained in the refrigerant gas is separated from the refrigerant gas by centrifugal separation. The refrigerant gas from which the oil has been separated passes through the inside of the small-diameter cylinder portion and the inside of the large-diameter cylinder portion and is discharged to the outside of the housing through the discharge hole.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] Incidentally, in order to efficiently separate the oil contained in the refrigerant gas from the refrigerant gas itself, it is necessary to create a swirling flow of the refrigerant gas flowing in through the conduit using a small-diameter cylindrical section. To create a swirling flow of the refrigerant gas flowing in through the conduit using a small-diameter cylindrical section, the outer diameter of the small-diameter cylindrical section should be made as small as possible. This allows the refrigerant gas to swirl around the small-diameter cylindrical section as many times as possible, thus enabling efficient separation of the oil contained in the refrigerant gas from the refrigerant gas. However, if the outer diameter of the small-diameter cylindrical section is made too small, it becomes difficult for the refrigerant gas from which the oil has been separated to flow into the inside of the small-diameter cylindrical section, increasing the pressure loss of the refrigerant gas. Therefore, it is desirable to suppress the pressure loss of the refrigerant gas while improving the oil separation performance. [Means for solving the problem]

[0006] A compressor that solves the above problems comprises a housing, a rotating shaft rotatably supported by the housing, and a compression mechanism housed within the housing that compresses refrigerant gas by the rotation of the rotating shaft. The housing has a discharge port for discharging the refrigerant gas compressed by the compression mechanism to the outside of the housing, and divides the housing into a discharge chamber from which the refrigerant gas compressed by the compression mechanism is discharged, and an oil separation chamber for separating the oil contained in the refrigerant gas discharged into the discharge chamber. The discharge chamber and the oil separation chamber are electrically connected by a conductive hole, and the oil separation chamber is provided with a bottomed cylindrical oil separation cylinder. The oil separation cylinder is fixed to the inner circumferential wall of the oil separation chamber and has a large diameter cylindrical portion that opens toward the discharge port, and an outer diameter smaller than the outer diameter of the large diameter cylindrical portion, and the large diameter cylindrical portion is relative to the discharge port. The compressor has a small diameter cylindrical portion extending from the large diameter cylindrical portion toward the opposite side, the small diameter cylindrical portion is a compressor that generates a swirling flow in the refrigerant gas flowing in from the conduction hole, the small diameter cylindrical portion has an annular enlarged diameter portion whose outer diameter gradually increases as it moves away from the large diameter cylindrical portion, and a small diameter cylindrical bottom portion extending from the enlarged diameter portion toward the opposite side of the large diameter cylindrical portion with the enlarged diameter portion in between, the small diameter cylindrical bottom portion is provided with a plurality of through holes that penetrate so as to communicate the outside of the small diameter cylindrical bottom portion in the oil separation chamber with the opening of the large diameter cylindrical portion, an annular gap is formed between the enlarged diameter portion and the inner circumferential surface of the oil separation chamber, the conduction hole opens between the portion on the inner circumferential surface of the oil separation chamber where the large diameter cylindrical portion is fixed and the portion that partitions the gap, and the sum of the flow path cross-sectional areas of the plurality of through holes is greater than the flow path cross-sectional area of ​​the small diameter cylindrical bottom portion in the radial direction.

[0007] According to this design, the small-diameter cylindrical section generates a swirling flow in the refrigerant gas flowing in through the conduction hole, and the refrigerant gas flows towards the annular gap between the enlarged diameter section and the inner surface of the oil separation chamber while swirling around the small-diameter cylindrical section. At this time, the outer diameter of the enlarged diameter section gradually increases as it moves away from the large-diameter cylindrical section. Therefore, the refrigerant gas is more likely to repeatedly swirl around the small-diameter cylindrical section before reaching the annular gap. As a result, the oil contained in the refrigerant gas can be efficiently separated from the refrigerant gas. The refrigerant gas, from which the oil has been separated, then passes through the gap and flows from the outside of the small-diameter cylindrical bottom into the inside of the small-diameter cylindrical bottom through multiple through holes, and also flows towards the opening of the large-diameter cylindrical section. At this time, the sum of the flow path cross-sectional areas of the multiple through holes is larger than the flow path cross-sectional area in the radial direction of the small-diameter cylindrical bottom, so the refrigerant gas is more likely to flow from the outside of the small-diameter cylindrical bottom into the inside of the small-diameter cylindrical bottom through multiple through holes. Therefore, the pressure loss of the refrigerant gas can be suppressed. As a result, it is possible to improve oil separation performance while suppressing pressure loss of the refrigerant gas.

[0008] In the above-described compressor, the outer diameter of the small-diameter cylinder bottom is preferably smaller than the outer diameter of the enlarged diameter portion. This makes it easier to prevent oil from adhering to the end of the smaller diameter cylinder at the bottom of the enlarged section. Therefore, it is possible to avoid problems such as oil adhering to the end of the smaller diameter cylinder at the bottom of the enlarged section and the adhering oil obstructing the passage of refrigerant gas through the gap. As a result, the pressure loss of the refrigerant gas can be suppressed.

[0009] In the above-described compressor, the outer diameter of the small-diameter cylinder bottom portion is preferably equal to the outer diameter of the enlarged portion. According to this, the cross-sectional area of ​​the flow path inside the small-diameter cylinder bottom can be made as large as possible, making it easier for the refrigerant gas to flow inside the small-diameter cylinder bottom. As a result, the pressure loss of the refrigerant gas can be further suppressed.

[0010] In the above-described compressor, the small-diameter cylindrical portion may have an annular reduced-diameter portion whose outer diameter gradually decreases as it moves from the large-diameter cylindrical portion toward the enlarged-diameter portion. According to this design, the refrigerant gas from the conduction holes flows along the narrowed diameter section, making it easier for it to flow from the large-diameter cylindrical section towards the widened diameter section. Therefore, the refrigerant gas flows more easily towards the annular gap while swirling around the small-diameter cylindrical section, making it easier to separate the oil contained in the refrigerant gas from the refrigerant gas more efficiently.

[0011] In the above-described compressor, the inner diameter of the enlarged section should gradually increase as it moves away from the large-diameter cylindrical section, and the inner diameter of the reduced-diameter section should gradually decrease as it moves away from the large-diameter cylindrical section. This makes it possible to improve the oil separation performance due to the baffle effect.

[0012] In the above-described compressor, the through-hole is preferably circular in shape. A configuration in which the through-hole is circular is suitable for providing multiple through-holes at the bottom of a small-diameter cylinder. In the above-described compressor, the through-holes are preferably elongated. The configuration in which the through-holes are elongated is suitable for providing multiple through-holes at the bottom of a small-diameter cylinder.

[0013] In the above-described compressor, it is preferable that the longitudinal direction of the through-hole coincides with the axial direction of the small-diameter cylinder bottom. A configuration in which the longitudinal direction of the through-hole coincides with the axial direction of the small-diameter cylinder bottom is suitable for allowing fluid to flow from the outside of the small-diameter cylinder bottom into the inside of the small-diameter cylinder bottom through multiple through-holes. [Effects of the Invention]

[0014] According to this invention, it is possible to improve oil separation performance while suppressing pressure loss of the refrigerant gas. [Brief explanation of the drawing]

[0015] [Figure 1] Figure 1 is a cross-sectional view of the compressor in the embodiment. [Figure 2] Figure 2 is a cross-sectional view showing a magnified portion of the compressor. [Figure 3] Figure 3 is a perspective view of the oil separation cylinder. [Figure 4]FIG. 4 is a side view of the oil separation cylinder in the modified example. [Figure 5] FIG. 5 is a cross-sectional view of the oil separation cylinder. [Figure 6] FIG. 6 is a side view of the oil separation cylinder in the modified example.

Mode for Carrying Out the Invention

[0016] Hereinafter, an embodiment in which the compressor is embodied will be described according to FIGS. 1 to 3. The compressor of this embodiment is used, for example, in a vehicle air conditioner. <Basic Configuration of Compressor> As shown in FIG. 1, the compressor 10 includes a cylindrical housing 11. The housing 11 has a motor housing 12, a shaft support housing 13, and a discharge housing 14. The motor housing 12, the shaft support housing 13, and the discharge housing 14 are made of a metal material. The motor housing 12, the shaft support housing 13, and the discharge housing 14 are made of, for example, aluminum. Further, the compressor 10 includes a rotating shaft 15. The rotating shaft 15 is housed inside the housing 11.

[0017] 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 peripheral portion of the end wall 12a. The axial direction of the peripheral wall 12b coincides with the axial direction of the rotating shaft 15. The motor housing 12 has a plurality of female screw holes 12c. Each female screw hole 12c is formed at the open end of the peripheral wall 12b. In FIG. 1, for convenience of explanation, only one female screw hole 12c is shown. Further, the motor housing 12 has a suction port 12h. The suction port 12h sucks refrigerant gas. The suction port 12h is formed in a portion of the peripheral wall 12b located on the side of the end wall 12a. The suction port 12h communicates the inside and outside of the motor housing 12.

[0018] The motor housing 12 has a cylindrical bearing holding portion 12d. The bearing holding portion 12d protrudes from the central portion of the inner surface of the end wall 12a. The first end, which is one end in the axial direction of the rotating shaft 15, is inserted into the bearing holding portion 12d. The compressor 10 includes a bearing 16. The bearing 16 is, for example, a rolling bearing. The bearing 16 is provided between the inner peripheral surface of the bearing holding portion 12d and the outer peripheral surface of the first end of the rotating shaft 15. And the first end of the rotating shaft 15 is rotatably supported by the motor housing 12 via the bearing 16.

[0019] 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 peripheral portion of the end wall 17. The axial direction of the peripheral wall 18 coincides with the axial direction of the rotating shaft 15. Also, the shaft support housing 13 has an annular flange wall 19. The flange wall 19 extends radially outward of the rotating shaft 15 from the end portion on the opposite side of the end wall 17 on the outer peripheral surface of the peripheral wall 18.

[0020] The shaft support housing 13 has a circular hole-shaped insertion hole 17a. The insertion hole 17a is formed in the central portion of the end wall 17. The insertion hole 17a penetrates the end wall 17 in the thickness direction. The rotating shaft 15 is inserted into the insertion hole 17a. The tip surface 15e located on the second end side, which is the other end in the axial direction of the rotating shaft 15, is located inside the peripheral wall 18.

[0021] The compressor 10 includes a bearing 21. The bearing 21 is, for example, a rolling bearing. The bearing 21 is provided between the inner peripheral surface of the peripheral wall 18 and the outer peripheral surface of the rotating shaft 15. And the rotating shaft 15 is rotatably supported by the shaft support housing 13 via the bearing 21. Therefore, the shaft support housing 13 rotatably supports the rotating shaft 15. Thus, the rotating shaft 15 is rotatably supported with respect to the housing 11.

[0022] The support housing 13 has multiple bolt insertion holes 19a. Each bolt insertion hole 19a is formed on the outer circumference of the flange wall 19. Each bolt insertion hole 19a penetrates the flange wall 19 in the thickness direction. Each bolt insertion hole 19a of the flange wall 19 communicates with each female screw hole 12c of the motor housing 12. Note that in Figure 1, only one bolt insertion hole 19a is shown for illustrative purposes.

[0023] The compressor 10 includes a motor chamber 20. The motor chamber 20 is partitioned by a motor housing 12 and a shaft support housing 13. The motor housing 12 partitions the motor chamber 20 together with the shaft support housing 13. In this way, the motor chamber 20 is formed inside the housing 11. The motor chamber 20 is in communication with the intake port 12h. Refrigerant gas is drawn into the motor chamber 20 from the intake port 12h.

[0024] The compressor 10 includes a motor 22. The motor 22 is housed in a motor chamber 20. The motor 22 includes a cylindrical stator 23 and a cylindrical rotor 24. The rotor 24 is located 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) provided on the rotor core 24a.

[0025] The stator 23 has a cylindrical stator core 23a and a motor coil 23b. The stator core 23a is fixed to the inner surface of the peripheral wall 12b of the motor housing 12. The motor coil 23b is wound around the stator core 23a. Power controlled by an inverter (not shown) is supplied to the motor coil 23b, causing the rotor 24 to rotate. As a result, the rotating shaft 15 rotates integrally with the rotor 24. Therefore, the motor 22 rotates the rotating shaft 15.

[0026] The compressor 10 is equipped with a compression mechanism C1. The compression mechanism C1 has a fixed scroll 25 and an orbiting scroll 26. Therefore, the compressor 10 is equipped with a fixed scroll 25 and an orbiting scroll 26. The compression mechanism C1 is of the scroll type. Therefore, the compressor 10 is a scroll-type compressor. The orbiting scroll 26 revolves around the fixed scroll 25 by the rotation of the rotation axis 15.

[0027] The fixed scroll 25 has a fixed substrate 25a and a fixed spiral wall 25b. The fixed substrate 25a is disc-shaped. An ejection port 25h is formed in the center of the fixed substrate 25a. The ejection port 25h is a circular hole. The ejection port 25h penetrates the fixed substrate 25a in the thickness direction. The fixed spiral wall 25b rises from the fixed substrate 25a. The fixed scroll 25 also has an outer peripheral wall 25c. The outer peripheral wall 25c rises from the outer periphery of the fixed substrate 25a. The outer peripheral wall 25c surrounds the fixed spiral wall 25b.

[0028] The compressor 10 is equipped with a valve mechanism 25v. The valve mechanism 25v is mounted on the side of the fixed substrate 25a opposite to the fixed spiral wall 25b. The valve mechanism 25v is configured to open and close the discharge port 25h.

[0029] The orbiting scroll 26 has an orbiting base plate 26a and an orbiting spiral wall 26b. The orbiting base plate 26a is disc-shaped. The orbiting base plate 26a faces the fixed base plate 25a. The orbiting spiral wall 26b stands upright from the orbiting base plate 26a toward the fixed base plate 25a. The orbiting spiral wall 26b meshes with the fixed spiral wall 25b. The orbiting scroll 26 is located inside the outer peripheral wall 25c. The orbiting scroll 26 revolves inside the outer peripheral wall 25c. The tip surface of the fixed spiral wall 25b is in contact with the orbiting base plate 26a. The tip surface of the orbiting spiral wall 26b is in contact with the fixed base plate 25a.

[0030] The compressor 10 includes a compression chamber 27. The compression chamber 27 is partitioned by a fixed base plate 25a, a fixed spiral wall 25b, a rotating base plate 26a, and a rotating spiral wall 26b. Therefore, the compression chamber 27 is partitioned between the fixed scroll 25 and the rotating scroll 26. The compression chamber 27 takes in refrigerant gas from the outside and compresses it.

[0031] The compressor 10 is equipped with a boss portion 28. The rotating base plate 26a has a cylindrical boss portion 28. The boss portion 28 protrudes cylindrically from the end face 26e of the rotating base plate 26a opposite to the fixed base plate 25a. The axial direction of the boss portion 28 coincides with the axial direction of the rotation axis 15.

[0032] The rotating substrate 26a has multiple grooves 26d. The multiple grooves 26d are each formed around the boss portion 28 on the end face 26e of the rotating substrate 26a. The multiple grooves 26d are arranged at predetermined intervals in the circumferential direction of the rotation axis 15. Note that in Figure 1, only one groove 26d is shown for illustrative purposes. An annular ring member 29 is fitted into each groove 26d. A pin 30 is inserted into each ring member 29. Each pin 30 protrudes from the end face 13e on the rotating scroll 26 side of the pivot housing 13.

[0033] The compressor 10 is equipped with an elastic plate 31. The elastic plate 31 is annular in shape. The elastic plate 31 is sandwiched between the end face 13e of the pivot housing 13 and the open end face of the outer peripheral wall 25c. The elastic plate 31 constantly biases the orbiting scroll 26 toward the stationary scroll 25.

[0034] The compressor 10 is equipped with an eccentric shaft 32. The eccentric shaft 32 protrudes toward the orbiting scroll 26 from a position eccentric with respect to the axis L1 of the rotating shaft 15 at the tip surface 15e of the rotating shaft 15. The eccentric shaft 32 is integrally formed with the rotating shaft 15. The axial direction of the eccentric shaft 32 coincides with the axial direction of the rotating shaft 15. The eccentric shaft 32 is inserted into the boss portion 28.

[0035] The compressor 10 includes a balance weight 33 and a bush 34. The bush 34 is fitted to the outer circumferential surface of the eccentric shaft 32. The balance weight 33 is integrated with the bush 34. The balance weight 33 is integrally formed with the bush 34. The balance weight 33 is housed within the circumferential wall 18 of the support housing 13. The orbiting scroll 26 is supported on the eccentric shaft 32 so as to be rotatable relative to the eccentric shaft 32 via the bush 34 and rolling bearing B2.

[0036] The rotation of the rotating shaft 15 is transmitted to the orbiting scroll 26 via the eccentric shaft 32, bushing 34, and rolling bearing B2. This causes the orbiting scroll 26 to rotate on its own axis. Then, the rotation of the orbiting scroll 26 is prevented by the contact between each pin 30 and the inner surface of each ring member 29, allowing only the orbital motion of the orbiting scroll 26 to be permitted. As a result, the orbiting scroll 26 revolves with the orbiting spiral wall 26b in contact with the fixed spiral wall 25b. As the orbiting scroll 26 revolves, the volume of the compression chamber 27 decreases, and the refrigerant gas is compressed in the compression chamber 27. The orbiting scroll 26 revolves inside the outer peripheral wall 25c as the rotating shaft 15 rotates. The balance weight 33 counteracts the centrifugal force acting on the orbiting scroll 26 when it revolves. This reduces the amount of unbalance of the orbiting scroll 26.

[0037] The discharge housing 14 has a plate-shaped end wall 14a and a cylindrical circumferential wall 14b. The circumferential wall 14b extends cylindrically from the outer circumference of the end wall 14a. The axial direction of the circumferential wall 14b coincides with the axial direction of the rotation axis 15. The circumferential wall 14b surrounds the fixed scroll 25. Therefore, the fixed scroll 25 is housed within the housing 11. In this way, the compression mechanism C1 is housed within the housing 11.

[0038] The discharge housing 14 has multiple bolt insertion holes 14c. Each bolt insertion hole 14c is formed in the peripheral wall 14b. Note that in Figure 1, only one bolt insertion hole 14c is shown for illustrative purposes. Each bolt insertion hole 14c communicates with each bolt insertion hole 19a in the flange wall 19.

[0039] The bolts B1 passing through each bolt insertion hole 14c pass through each bolt insertion hole 19a in the flange wall 19 and are screwed into each female threaded hole 12c of the motor housing 12. This connects the support housing 13 to the peripheral wall 12b of the motor housing 12, and the discharge housing 14 to the flange wall 19 of the support housing 13. Therefore, the motor housing 12, the support housing 13, and the discharge housing 14 are arranged in this order, aligned in the axial direction of the rotation shaft 15. The fixed scroll 25 is sandwiched between the end wall 14a of the discharge housing 14 and the support housing 13. In this way, the fixed scroll 25 is fixed to the housing 11.

[0040] The compressor 10 is equipped with an intake passage 35. The intake 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 in a part of the inner 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 circumference of the flange wall 19 of the pivot housing 13. The first hole 37 penetrates the flange wall 19 in the thickness direction. The first hole 37 communicates with the first groove 36. The second groove 38 is formed in a part of the inner surface of the peripheral wall 14b of the discharge housing 14. The second groove 38 communicates with the first hole 37. The second hole 39 is formed in the outer surface wall 25c of the fixed scroll 25. The second hole 39 penetrates the outer surface wall 25c in the thickness direction. The second hole 39 communicates with the second groove 38. The second hole 39 communicates with the outermost part of the compression chamber 27.

[0041] The refrigerant gas in the motor chamber 20 passes through the first groove 36, the first hole 37, the second groove 38, and the second hole 39 and is drawn into the compression chamber 27. The refrigerant gas drawn into the compression chamber 27 is compressed within the compression chamber 27 by the orbital motion of the orbital scroll 26 accompanying the rotation of the rotating shaft 15. In this way, the compression mechanism C1 compresses the refrigerant gas by the rotation of the rotating shaft 15.

[0042] The compressor 10 includes a discharge chamber 40. The discharge chamber 40 is partitioned between the fixed base plate 25a and the end wall 14a of the discharge housing 14. Therefore, the housing 11 partitions the discharge chamber 40. The discharge chamber 40 is in communication with the discharge port 25h. The refrigerant gas compressed in the compression chamber 27 is discharged into the discharge chamber 40. Therefore, the refrigerant gas compressed by the compression mechanism C1 is discharged into the discharge chamber 40. The compressor 10 also 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.

[0043] The compressor 10 is equipped with 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 partitions 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 with respect to the rotation axis 15. Therefore, the oil separation chamber 42 extends radially with respect to the rotation axis 15.

[0044] The first end of the outer cylinder 43 is 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 is in communication with the oil separation chamber 42.

[0045] The outer cylinder 43 has a conduit hole 46. The discharge chamber 40 and the oil separation chamber 42 are connected by the conduit hole 46. The conduit hole 46 introduces the refrigerant gas discharged into the discharge chamber 40 into the oil separation chamber 42.

[0046] The discharge housing 14 has an oil drain hole 47. The first end of the oil drain hole 47 communicates with the side of the oil separation chamber 42 opposite to the discharge hole 44. The second end of the oil drain hole 47 communicates with the oil storage chamber 41. The oil separation chamber 42 communicates with the oil storage chamber 41 via the oil drain hole 47.

[0047] A back pressure chamber 48 is partitioned between the orbiting substrate 26a of the orbiting scroll 26 and the support housing 13. The back pressure chamber 48 is formed within the housing 11 on the side opposite to the fixed substrate 25a relative to the orbiting substrate 26a. The support housing 13 separates the back pressure chamber 48 from the motor chamber 20. The inside of the peripheral wall 18 of the support housing 13 is part of the back pressure chamber 48. Furthermore, the gap between the elastic plate 31 and the support housing 13 is also part of the back pressure chamber 48.

[0048] The compressor 10 is equipped with an oil return passage 49. The oil return passage 49 extends from the oil storage chamber 41 through the discharge housing 14 and the shaft support housing 13 to the back pressure chamber 48. Thus, the oil return passage 49 connects the oil storage chamber 41 and the back pressure chamber 48. The oil stored in the oil storage chamber 41 is then returned to the back pressure chamber 48 via the oil return passage 49.

[0049] <Oil Separator> As shown in Figure 2, an oil separation cylinder 50 is provided in the oil separation chamber 42. The oil separation cylinder 50 is a bottomed cylindrical shape. The oil separation cylinder 50 has a large diameter cylindrical section 51 and a small diameter cylindrical section 52. The large diameter cylindrical section 51 is cylindrical. The large diameter cylindrical section 51 is fixed to the inner circumferential wall 42a of the oil separation chamber 42 by being press-fitted into the inner circumferential wall 42a of the oil separation chamber 42. The axis of the large diameter cylindrical section 51 coincides with the axis of the outer cylinder 43. Therefore, the oil separation cylinder 50 is provided in the oil separation chamber 42 with its axial direction coinciding with the radial direction of the rotation axis 15. The first end of the large diameter cylindrical section 51 opens toward the discharge hole 44.

[0050] The small-diameter cylindrical portion 52 is continuous with the second end of the large-diameter cylindrical portion 51. The small-diameter cylindrical portion 52 extends from the large-diameter cylindrical portion 51 toward the opposite side of the discharge hole 44. The small-diameter cylindrical portion 52 has a smaller outer diameter than the large-diameter cylindrical portion 51. The axis of the small-diameter cylindrical portion 52 coincides with the axis of the large-diameter cylindrical portion 51.

[0051] As shown in Figures 2 and 3, the small-diameter cylindrical portion 52 has a reduced-diameter portion 53, an enlarged-diameter portion 54, and a small-diameter cylindrical bottom portion 55. The reduced-diameter portion 53 is annular. The reduced-diameter portion 53 extends from the second end of the large-diameter cylindrical portion 51. The first end of the reduced-diameter portion 53 is continuous with the second end of the large-diameter cylindrical portion 51. The second end of the reduced-diameter portion 53 is continuous with the first end of the enlarged-diameter portion 54. The outer diameter of the reduced-diameter portion 53 gradually decreases as it moves from the large-diameter cylindrical portion 51 toward the enlarged-diameter portion 54. The inner diameter of the reduced-diameter portion 53 gradually decreases as it moves away from the large-diameter cylindrical portion 51.

[0052] The enlarged diameter section 54 is annular. The enlarged diameter section 54 extends from the second end of the reduced diameter section 53. The outer diameter of the enlarged diameter section 54 gradually increases as it moves away from the large diameter cylindrical section 51. The end of the enlarged diameter section 54 located on the opposite side of the large diameter cylindrical section 51 is an annular shape extending around the axis of the small diameter cylindrical section 52. The boundary between the enlarged diameter section 54 and the reduced diameter section 53 is the part of the small diameter cylindrical section 52 where the outer diameter is smallest. The inner diameter of the enlarged diameter section 54 is constant.

[0053] The small-diameter cylindrical bottom 55 has a small-diameter circumferential wall 56 and a small-diameter bottom wall 57. The small-diameter circumferential wall 56 extends cylindrically from the enlarged diameter portion 54. Therefore, the small-diameter cylindrical bottom 55 extends from the enlarged diameter portion 54 toward the opposite side of the large-diameter cylindrical portion 51, with the enlarged diameter portion 54 in between. The outer diameter of the small-diameter circumferential wall 56 is constant. The inner diameter of the small-diameter circumferential wall 56 is constant. The inner diameter of the small-diameter circumferential wall 56 is equal to the inner diameter of the enlarged diameter portion 54. The outer diameter of the small-diameter circumferential wall 56 is smaller than the outer diameter of the enlarged diameter portion 54. In detail, the outer diameter of the small-diameter circumferential wall 56 is smaller than the outer diameter of the enlarged diameter portion 54. Thus, the outer diameter of the small-diameter cylindrical bottom 55 is smaller than the outer diameter of the enlarged diameter portion 54. The small-diameter bottom wall 57 closes the end of the small-diameter circumferential wall 56 that is opposite to the enlarged diameter portion 54. The small-diameter bottom wall 57 is disc-shaped.

[0054] Multiple through holes 58 are provided in the small-diameter cylindrical bottom 55. The multiple through holes 58 penetrate the small-diameter peripheral wall 56. The multiple through holes 58 penetrate so as to connect the outside of the small-diameter cylindrical bottom 55 in the oil separation chamber 42 with the opening of the large-diameter cylindrical section 51. The through holes 58 are circular in shape. The sum of the flow path cross-sectional areas of the multiple through holes 58 is greater than the flow path cross-sectional area of ​​the small-diameter cylindrical bottom 55 in the radial direction. The sum of the flow path cross-sectional areas of the multiple through holes 58 is greater than the area of ​​the small-diameter bottom wall 57.

[0055] As shown in Figure 2, an annular gap 59 is formed between the enlarged diameter portion 54 and the inner circumferential surface of the oil separation chamber 42. More specifically, the gap 59 is an annular space formed between the end of the enlarged diameter portion 54 located opposite to the large diameter cylindrical portion 51 and the inner circumferential surface of the oil separation chamber 42. The conduit hole 46 opens between the portion on the inner circumferential surface of the oil separation chamber 42 where the large diameter cylindrical portion 51 is fixed and the portion that demarcates the gap 59. The conduit hole 46 opens toward the small diameter cylindrical portion 52. The small diameter cylindrical portion 52 causes a swirling flow in the refrigerant gas flowing in from the conduit hole 46.

[0056] [Effect of the Embodiment] Next, the operation of the embodiment will be described. 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 conduit hole 46. The refrigerant gas from the conduit hole 46 flows along the reduced diameter section 53 and towards the expanded diameter section 54. The refrigerant gas flows towards the annular gap 59 between the expanded diameter section 54 and the inner circumferential surface of the oil separation chamber 42, while swirling around the small diameter cylindrical section 52. At this time, the outer diameter of the expanded diameter section 54 gradually expands as it moves away from the large diameter cylindrical section 51. Therefore, the refrigerant gas is easily able to swirl repeatedly around the small diameter cylindrical section 52 before reaching the annular gap 59. Then, centrifugal force is applied to the oil contained in the refrigerant gas, and the oil is separated from the refrigerant gas in the oil separation chamber 42.

[0057] The refrigerant gas, from which the oil has been separated, passes through the gap 59 and flows from the outside of the small-diameter cylindrical bottom 55 into the inside of the small-diameter cylindrical bottom 55 through multiple through holes 58, and also flows towards the opening of the large-diameter cylindrical portion 51. At this time, the sum of the flow path cross-sectional areas of the multiple through holes 58 is larger than the flow path cross-sectional area in the radial direction of the small-diameter cylindrical bottom 55, so the refrigerant gas flows easily from the outside of the small-diameter cylindrical bottom 55 into the inside of the small-diameter cylindrical bottom 55 through multiple through holes 58. Therefore, the pressure loss of the refrigerant gas is suppressed.

[0058] The refrigerant gas flowing toward the opening of the large-diameter cylindrical section 51 flows into the outer cylinder 43 through the opening of the large-diameter cylindrical section 51 and passes through the outer cylinder 43. The refrigerant gas that has passed through the outer cylinder 43 then flows out through the discharge hole 44 to an external refrigerant circuit (not shown).

[0059] The oil separated from the refrigerant gas in the oil separation chamber 42 flows toward the drain hole 47. The oil flowing toward the drain hole 47 is then discharged through the drain hole 47 into the oil storage chamber 41 and stored in the oil storage chamber 41. The oil stored in the oil storage chamber 41 is recirculated to the back pressure chamber 48 via the oil recirculation passage 49.

[0060] [Effects of the Embodiment] In this embodiment, the following effects can be obtained. (1) The small-diameter cylindrical portion 52 generates a swirling flow in the refrigerant gas flowing in from the conduction hole 46, and the refrigerant gas flows towards the annular gap 59 between the enlarged diameter portion 54 and the inner circumferential surface of the oil separation chamber 42 while swirling around the small-diameter cylindrical portion 52. At this time, the outer diameter of the enlarged diameter portion 54 gradually increases as it moves away from the large-diameter cylindrical portion 51. Therefore, the refrigerant gas is easily able to repeatedly swirl around the small-diameter cylindrical portion 52 before reaching the annular gap 59. As a result, the oil contained in the refrigerant gas can be efficiently separated from the refrigerant gas. The refrigerant gas from which the oil has been separated then passes through the gap 59 and flows into the inside of the small-diameter cylindrical bottom portion 55 from the outside of the small-diameter cylindrical bottom portion 55 through a plurality of through holes 58, and flows towards the opening of the large-diameter cylindrical portion 51. In this case, the sum of the flow path cross-sectional areas of the multiple through holes 58 is larger than the flow path cross-sectional area of ​​the small-diameter cylinder bottom 55 in the radial direction. Therefore, refrigerant gas can easily flow from the outside of the small-diameter cylinder bottom 55 into the inside of the small-diameter cylinder bottom 55 through the multiple through holes 58. Consequently, pressure loss of the refrigerant gas can be suppressed. As a result, pressure loss of the refrigerant gas can be suppressed while improving oil separation performance.

[0061] (2) The outer diameter of the small diameter cylinder bottom portion 55 is smaller than the outer diameter of the enlarged diameter portion 54. This makes it easier to prevent oil from adhering to the end of the enlarged diameter portion 54 on the small diameter cylinder bottom portion 55 side. Therefore, it is possible to avoid the problem of oil adhering to the end of the enlarged diameter portion 54 on the small diameter cylinder bottom portion 55 side and the adhering oil obstructing the passage of refrigerant gas through the gap 59. As a result, the pressure loss of the refrigerant gas can be suppressed.

[0062] (3) The small diameter cylindrical portion 52 has an annular reduced diameter portion 53 whose outer diameter gradually decreases as it moves from the large diameter cylindrical portion 51 towards the enlarged diameter portion 54. This allows the refrigerant gas from the conduction hole 46 to flow along the reduced diameter portion 53, making it easier for it to flow from the large diameter cylindrical portion 51 towards the enlarged diameter portion 54. Therefore, the refrigerant gas can easily flow towards the annular gap 59 while swirling around the small diameter cylindrical portion 52, making it easier to separate the oil contained in the refrigerant gas from the refrigerant gas more efficiently.

[0063] (4) The through-hole 58 is circular in shape. The configuration in which the through-hole 58 is circular is suitable for providing multiple through-holes 58 in the small-diameter cylindrical bottom 55. [Example of changes] The above embodiment can be implemented with the following modifications. The above embodiment and the following modifications can be combined with each other to the extent that they do not contradict each other technically.

[0064] ○ As shown in Figures 4 and 5, the outer diameter of the small-diameter cylindrical bottom 55 may be equal to the outer diameter of the enlarged diameter 54. More specifically, the outer diameter of the small-diameter peripheral wall 56 is equal to the outer diameter of the end of the enlarged diameter 54 located on the opposite side from the large-diameter cylindrical portion 51. This allows the flow path cross-sectional area inside the small-diameter cylindrical bottom 55 to be made as large as possible, making it easier for the refrigerant gas to flow inside the small-diameter cylindrical bottom 55. As a result, the pressure loss of the refrigerant gas can be further suppressed.

[0065] Furthermore, as shown in Figure 5, the inner diameter of the enlarged portion 54 may gradually increase as it moves away from the large-diameter cylindrical portion 51. This allows for improved oil separation performance due to the baffle effect.

[0066] ○ As shown in Figure 6, the through-hole 58 may be elongated. The longitudinal direction of the through-hole 58 coincides with the axial direction of the small-diameter cylinder bottom 55. The configuration in which the through-hole 58 is elongated is suitable for providing multiple through-holes 58 in the small-diameter cylinder bottom 55. Furthermore, the configuration in which the longitudinal direction of the through-hole 58 coincides with the axial direction of the small-diameter cylinder bottom 55 is suitable for allowing fluid to flow from the outside of the small-diameter cylinder bottom 55 into the inside of the small-diameter cylinder bottom 55 through multiple through-holes 58.

[0067] ○ In the embodiment shown in Figure 6, the longitudinal direction of the through hole 58 does not necessarily have to coincide with the axial direction of the small-diameter cylindrical bottom portion 55. ○ In this embodiment, the small-diameter cylindrical portion 52 may not have an annular reduced-diameter portion 53 in which the outer diameter gradually decreases as it moves from the large-diameter cylindrical portion 51 towards the enlarged-diameter portion 54.

[0068] ○ In this embodiment, the end of the enlarged diameter portion 54 located on the opposite side from the large diameter cylindrical portion 51 may extend spirally around the axis of the small diameter cylindrical portion 52. ○ In this embodiment, the oil separation chamber 42 may extend in the axial direction of the rotating shaft 15. The oil separation cylinder 50 may be provided in the oil separation chamber 42 such that the axial direction of the oil separation cylinder 50 coincides with the axial direction of the rotating shaft 15.

[0069] ○ In this embodiment, the compressor 10 does not have to be of the type driven by the motor 22, but may be of the type driven by, for example, the engine of a vehicle. ○ In this embodiment, the compressor 10 was used in a vehicle air conditioning system, but it is not limited to this. In short, the compressor 10 can be any compressor that compresses refrigerant gas, and the application of the compressor 10 can be changed as appropriate.

[0070] ○ In this embodiment, the compression mechanism C1 was a scroll type composed of a fixed scroll 25 and an orbiting scroll 26, but it is not limited to this, and may be a piston type or a vane type, for example. In short, the configuration of the compression mechanism C1 is not particularly limited.

[0071] The above embodiment includes the configuration described in the following appendix. <Note 1> Housing and A rotating shaft rotatably supported in the aforementioned housing, The housing comprises a compression mechanism that is housed within the housing and compresses the refrigerant gas by the rotation of the rotating shaft, The housing has a discharge port for discharging the refrigerant gas compressed by the compression mechanism to the outside of the housing, and divides the housing into a discharge chamber from which the refrigerant gas compressed by the compression mechanism is discharged, and an oil separation chamber for separating the oil contained in the refrigerant gas discharged into the discharge chamber. The discharge chamber and the oil separation chamber are electrically connected by a conductive hole. The oil separation chamber is provided with a bottomed cylindrical oil separation cylinder. The oil separation cylinder is A large-diameter cylindrical portion is fixed to the inner circumferential wall of the oil separation chamber and opens toward the discharge hole, It has an outer diameter smaller than the outer diameter of the large diameter cylindrical portion, and a small diameter cylindrical portion that extends from the large diameter cylindrical portion toward the opposite side of the discharge hole from the large diameter cylindrical portion, The small-diameter cylindrical portion is a compressor that generates a swirling flow in the refrigerant gas flowing in from the passage hole, The aforementioned small diameter cylindrical portion is An annular enlarged diameter portion whose outer diameter gradually increases as it moves away from the aforementioned large diameter cylindrical portion, It has a small diameter cylindrical bottom portion that extends from the enlarged diameter portion toward the opposite side from the large diameter cylindrical portion, with the enlarged diameter portion in between, The small-diameter cylindrical bottom is provided with a plurality of through holes that penetrate to connect the outside of the small-diameter cylindrical bottom in the oil separation chamber with the opening of the large-diameter cylindrical portion. An annular gap is formed between the enlarged diameter portion and the inner circumferential surface of the oil separation chamber. The aforementioned conductive hole is opened between the portion on the inner circumferential surface of the oil separation chamber where the large-diameter cylindrical portion is fixed and the portion that divides the gap. A compressor characterized in that the sum of the flow path cross-sectional areas of the multiple through holes is greater than the flow path cross-sectional area in the radial direction of the small-diameter cylinder bottom.

[0072] <Note 2> The compressor according to <Note 1>, characterized in that the outer diameter of the small-diameter cylinder bottom is smaller than the outer diameter of the enlarged diameter portion.

[0073] <Note 3> The compressor according to <Appendix 1>, characterized in that the outer diameter of the small-diameter cylinder bottom is equal to the outer diameter of the enlarged diameter portion.

[0074] <Note 4> The compressor according to any one of the following appendices: <Appendix 1> to <Appendix 3>, characterized in that the small diameter cylindrical portion has an annular reduced diameter portion whose outer diameter gradually decreases as it moves from the large diameter cylindrical portion toward the enlarged diameter portion.

[0075] <Note 5> The compressor as described in Appendix 4, characterized in that the inner diameter of the enlarged portion gradually increases as it moves away from the large-diameter cylindrical portion, and the inner diameter of the reduced portion gradually decreases as it moves away from the large-diameter cylindrical portion.

[0076] <Note 6> The compressor according to any one of <Appendix 1> to <Appendix 5>, characterized in that the through hole is circular in shape.

[0077] <Note 7> The compressor according to any one of <Appendix 1> to <Appendix 5>, characterized in that the through hole is elongated in shape.

[0078] <Note 8> The compressor according to Appendix 7, characterized in that the longitudinal direction of the through hole coincides with the axial direction of the small-diameter cylinder bottom. [Explanation of symbols]

[0079] 10... Compressor, 11... Housing, 15... Rotating shaft, 40... Discharge chamber, 42... Oil separation chamber, 42a... Inner circumferential wall, 44... Discharge hole, 46... Conduit hole, 50... Oil separation cylinder, 51... Large diameter cylinder section, 52... Small diameter cylinder section, 53... Reduced diameter section, 54... Expanded diameter section, 55... Small diameter cylinder bottom section, 58... Through hole, 59... Gap, C1... Compression mechanism.

Claims

1. Housing and A rotating shaft rotatably supported in the aforementioned housing, The housing comprises a compression mechanism that is housed within the housing and compresses the refrigerant gas by the rotation of the rotating shaft, The housing has a discharge port for discharging the refrigerant gas compressed by the compression mechanism to the outside of the housing, and divides the housing into a discharge chamber from which the refrigerant gas compressed by the compression mechanism is discharged, and an oil separation chamber for separating the oil contained in the refrigerant gas discharged into the discharge chamber. The discharge chamber and the oil separation chamber are electrically connected by a conductive hole. The oil separation chamber is provided with a bottomed cylindrical oil separation cylinder. The oil separation cylinder is A large-diameter cylindrical portion is fixed to the inner circumferential wall of the oil separation chamber and opens toward the discharge hole, It has an outer diameter smaller than the outer diameter of the large diameter cylindrical portion, and a small diameter cylindrical portion that extends from the large diameter cylindrical portion toward the opposite side of the discharge hole from the large diameter cylindrical portion, The small-diameter cylindrical portion is a compressor that generates a swirling flow in the refrigerant gas flowing in from the passage hole, The aforementioned small diameter cylindrical portion is An annular enlarged diameter portion whose outer diameter gradually increases as it moves away from the aforementioned large diameter cylindrical portion, It has a small diameter cylindrical bottom portion that extends from the enlarged diameter portion toward the opposite side from the large diameter cylindrical portion, with the enlarged diameter portion in between, The small-diameter cylindrical bottom is provided with a plurality of through holes that penetrate to connect the outside of the small-diameter cylindrical bottom in the oil separation chamber with the opening of the large-diameter cylindrical portion. An annular gap is formed between the enlarged diameter portion and the inner circumferential surface of the oil separation chamber. The aforementioned conductive hole is opened between the portion on the inner circumferential surface of the oil separation chamber where the large-diameter cylindrical portion is fixed and the portion that divides the gap. A compressor characterized in that the sum of the flow path cross-sectional areas of the multiple through holes is greater than the flow path cross-sectional area in the radial direction of the small-diameter cylinder bottom.

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

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

4. The compressor according to any one of claims 1 to 3, characterized in that the small diameter cylindrical portion has an annular reduced diameter portion whose outer diameter gradually decreases as it moves from the large diameter cylindrical portion toward the enlarged diameter portion.

5. The compressor according to claim 4, characterized in that the inner diameter of the enlarged portion gradually increases as it moves away from the large-diameter cylindrical portion, and the inner diameter of the reduced portion gradually decreases as it moves away from the large-diameter cylindrical portion.

6. The compressor according to any one of claims 1 to 3, characterized in that the through hole is circular in shape.

7. The compressor according to any one of claims 1 to 3, characterized in that the through hole is elongated.

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

Images