compressor

Abstract

To efficiently reduce pressure of fluid guided from a high-pressure region to a low-pressure region via a fluid passage while reducing the size of a compressor.SOLUTION: Oil guided from an oil storage chamber 41 to a back pressure chamber via a fluid passage 77 is reduced in pressure when flowing through a first spiral passage 72 and a second spiral passage 74. Consequently, pressure of the oil guided from the oil storage chamber 41 to the back pressure chamber via the fluid passage 77 is reduced more efficiently than a case where, for example, a narrow part is composed only of the first spiral passage 72 or the second spiral passage 74. Also, the second spiral passage 74 is located inside the first spiral passage 72. Therefore, even when a narrow member 60 is configured to divide the first spiral passage 72 and the second spiral passage 74, the size of the housing 11 is prevented from increasing in an axial direction X1.SELECTED DRAWING: Figure 2

Description

Technical Field

[0001] The present invention relates to a compressor.

Background Art

[0002] A compressor includes a compression mechanism and a housing. The compression mechanism compresses a fluid. The housing has a high-pressure region and a low-pressure region. The high-pressure region includes a discharge chamber where the fluid compressed by the compression mechanism is discharged. The low-pressure region has a lower pressure than the high-pressure region. Also, the compressor may include a fluid passage that guides the fluid in the high-pressure region to the low-pressure region. A throttle portion is provided in the fluid passage. Then, the fluid in the high-pressure region is guided to the low-pressure region through the fluid passage in a state of being decompressed by the throttle portion.

[0003] For example, as in Patent Document 1, a throttle member may be installed inside the housing. An insertion hole into which the throttle member is inserted is formed in the housing. A spiral groove is formed on the outer peripheral surface of the throttle member. Then, a spiral passage is defined by the spiral groove and the inner peripheral surface of the housing that partitions the insertion hole. The fluid guided from the high-pressure region to the low-pressure region through the fluid passage is decompressed when flowing through the spiral passage. Therefore, the spiral passage functions as a throttle portion provided in the fluid passage. Thus, the throttle member forms a throttle portion provided in the fluid passage.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] However, in a configuration where the fluid pressure is reduced by the flow of fluid through a spiral passage, as in Patent Document 1, a certain length of the spiral passage is necessary to sufficiently reduce the fluid pressure. Therefore, the length of the insertion hole into which the throttling member is inserted must also be sufficient to accommodate the length of the spiral passage, which increases the size of the housing. As a result, the compressor becomes larger. Thus, there is a need to efficiently reduce the pressure of the fluid being guided from the high-pressure region to the low-pressure region via the fluid passage, while miniaturizing the compressor. [Means for solving the problem]

[0006] A compressor that solves the above problems comprises a compression mechanism for compressing a fluid, a housing having a high-pressure region including a discharge chamber from which the fluid compressed by the compression mechanism is discharged, and a low-pressure region with a pressure lower than that of the high-pressure region, a fluid passage for guiding the fluid in the high-pressure region to the low-pressure region, and a throttling member that forms a throttling portion provided in the fluid passage, wherein the housing has a partition wall that divides the high-pressure region, the throttling member has a first cylindrical portion and a second cylindrical portion disposed inside the first cylindrical portion, and the throttling member is the first cylindrical portion The part is attached to the partition wall in a state where it is positioned inside the insertion part provided in the partition wall, and a first helical groove is formed on at least one of the inner circumferential surface of the insertion part and the outer circumferential surface of the first cylindrical part, which defines a first helical passage communicating with the high-pressure region, and a second helical groove is formed on at least one of the inner circumferential surface of the first cylindrical part and the outer circumferential surface of the second cylindrical part, which communicates with the first helical passage and defines a second helical passage located inside the first helical passage, and the first helical passage and the second helical passage constitute the throttling part.

[0007] According to this design, the fluid guided from the high-pressure region to the low-pressure region via the fluid passage is depressurized as it flows through the first and second helical passages. Therefore, compared to a case where the throttling section consists only of the first or second helical passage, for example, the pressure of the fluid guided from the high-pressure region to the low-pressure region via the fluid passage can be reduced more efficiently. Furthermore, the second helical passage is located inside the first helical passage. Thus, even if the throttling member is configured to partition the first and second helical passages, it is possible to suppress an increase in the size of the housing in the axial direction of the first and second cylindrical sections. As a result, it is possible to reduce the size of the compressor while efficiently reducing the pressure of the fluid guided from the high-pressure region to the low-pressure region via the fluid passage.

[0008] In the compressor described above, the throttling member has a columnar flow path forming portion located inside the second cylindrical portion, and a third helical groove is formed on at least one of the inner circumferential surface of the second cylindrical portion and the outer circumferential surface of the flow path forming portion, which communicates with the second helical passage and defines a third helical passage located inside the second helical passage, and the third helical passage may constitute a part of the throttling portion.

[0009] According to this design, the fluid guided from the high-pressure region to the low-pressure region via the fluid passage is depressurized not only through the first and second helical passages, but also as it flows through the third helical passage. Therefore, the pressure of the fluid guided from the high-pressure region to the low-pressure region via the fluid passage can be reduced even more efficiently. Furthermore, the third helical passage is located inside the second helical passage. Thus, even if the throttling member partitions the third helical passage in addition to the first and second helical passages, it is possible to suppress an increase in the size of the housing in the axial direction of the first and second cylindrical sections. As a result, while miniaturizing the compressor, the pressure of the fluid guided from the high-pressure region to the low-pressure region via the fluid passage can be reduced even more efficiently.

[0010] In the compressor described above, it is preferable that a notch is formed on the end face of the second cylindrical portion to connect the second helical passage and the third helical passage. According to this, for example, compared to a configuration in which the second helical passage and the third helical passage are connected by a hole that penetrates the second cylindrical portion, it becomes easier to secure the respective lengths of the second and third helical passages. [Effects of the Invention]

[0011] According to this invention, while miniaturizing the compressor, the pressure of the fluid being guided from the high-pressure region to the low-pressure region via the fluid passage can be efficiently reduced. [Brief explanation of the drawing]

[0012] [Figure 1] This is a cross-sectional view of a scroll compressor in an embodiment. [Figure 2] This is a cross-sectional view showing a magnified portion of a scroll compressor. [Figure 3] This is an exploded perspective view showing the aperture component. [Figure 4] This is an exploded perspective view showing a throttling member in another embodiment. [Figure 5] This is a cross-sectional view showing a magnified portion of a scroll compressor. [Modes for carrying out the invention]

[0013] Below, one embodiment of the compressor will be described with reference to Figures 1 to 3. The compressor in this embodiment is a scroll-type compressor. Scroll-type compressors are used, for example, in vehicle air conditioning systems.

[0014] <Basic configuration of a scroll compressor> As shown in Figure 1, the scroll compressor 10 is equipped with a cylindrical housing 11. The housing 11 includes a motor housing 12, a support housing 13, and a discharge housing 14. The motor housing 12, the support housing 13, and the discharge housing 14 are made of metal. For example, the motor housing 12, the support housing 13, and the discharge housing 14 are made of aluminum. The scroll compressor 10 also includes a rotating shaft 15. The rotating shaft 15 is housed within the housing 11.

[0015] 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 circumference of the end wall 12a. The axial direction of the peripheral wall 12b coincides with the axial direction of the rotation axis 15. The motor housing 12 has an intake port 12h. The intake port 12h draws in a refrigerant gas, which is a fluid. Carbon dioxide is used as the refrigerant gas. The refrigerant gas contains mist-like oil. The intake port 12h is formed in the peripheral wall 12b on the side of the end wall 12a. The intake port 12h connects the inside and outside of the motor housing 12.

[0016] The motor housing 12 has a cylindrical bearing holder 12d. The bearing holder 12d protrudes from the center of the inner surface of the end wall 12a. The first end, which is one axial end of the rotating shaft 15, is inserted into the bearing holder 12d. The scroll compressor 10 is equipped with a bearing 16. The bearing 16 is, for example, a rolling bearing. The bearing 16 is provided between the inner circumferential surface of the bearing holder 12d and the outer circumferential surface of the first end of the rotating shaft 15. The first end of the rotating shaft 15 is rotatably supported in the motor housing 12 via the bearing 16.

[0017] 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 rotary shaft 15. Further, the shaft support housing 13 has an annular flange wall 19. The flange wall 19 extends radially outward of the rotary 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.

[0018] 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 rotary shaft 15 is inserted into the insertion hole 17a. The tip surface 15e located on the other end side in the axial direction of the rotary shaft 15 is located inside the peripheral wall 18.

[0019] The scroll 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 rotary shaft 15. And the rotary shaft 15 is rotatably supported by the shaft support housing 13 via the bearing 21. Therefore, the shaft support housing 13 rotatably supports the rotary shaft 15. Thus, the rotary shaft 15 is rotatably supported with respect to the housing 11.

[0020] The scroll compressor 10 includes a motor chamber 20. The motor chamber 20 is partitioned by the motor housing 12 and the shaft support housing 13. The motor housing 12 partitions the motor chamber 20 together with the shaft support housing 13. Thus, the motor chamber 20 is formed in the housing 11. The motor chamber 20 communicates with the suction port 12h. Refrigerant gas from the suction port 12h is inhaled into the motor chamber 20.

[0021] The scroll 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 rotary shaft 15. The stator 23 surrounds the rotor 24. The rotor 24 has a rotor core 24a fixed to the rotary shaft 15 and a plurality of permanent magnets (not shown) provided on the rotor core 24a.

[0022] The stator 23 has a cylindrical stator core 23a and a motor coil 23b. The stator core 23a is fixed to the inner peripheral surface of the peripheral wall 12b of the motor housing 12. The motor coil 23b is wound around the stator core 23a. Then, when power controlled by an inverter (not shown) is supplied to the motor coil 23b, the rotor 24 rotates. As a result, the rotary shaft 15 rotates integrally with the rotor 24. Therefore, the motor 22 rotates the rotary shaft 15.

[0023] The scroll compressor 10 includes a compression mechanism C1. The compression mechanism C1 has a fixed scroll 25 and a orbiting scroll 26. Therefore, the scroll compressor 10 includes the fixed scroll 25 and the orbiting scroll 26. The compression mechanism C1 is of a scroll type. The orbiting scroll 26 revolves around the fixed scroll 25 due to the rotation of the rotary shaft 15.

[0024] The fixed scroll 25 has a fixed substrate 25a and a fixed spiral wall 25b. The fixed substrate 25a is disc-shaped. A discharge port 25h is formed at the center of the fixed substrate 25a. The discharge port 25h is in the shape of a circular hole. The discharge port 25h penetrates the fixed substrate 25a in the thickness direction. The fixed spiral wall 25b stands up from the fixed substrate 25a. Further, the fixed scroll 25 has an outer peripheral wall 25c. The outer peripheral wall 25c stands up from the outer peripheral portion of the fixed substrate 25a. The outer peripheral wall 25c surrounds the fixed spiral wall 25b.

[0025] The scroll 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.

[0026] 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.

[0027] The scroll compressor 10 is equipped with 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.

[0028] The scroll 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.

[0029] 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.

[0030] The scroll compressor 10 is equipped with an eccentric shaft 31. The eccentric shaft 31 protrudes from the tip surface 15e of the rotating shaft 15 and extends parallel to the rotating shaft 15 at a position eccentric with respect to the axis L1 of the rotating shaft 15. The eccentric shaft 31 is integrally formed with the rotating shaft 15. The axial direction of the eccentric shaft 31 coincides with the axial direction of the rotating shaft 15. The eccentric shaft 31 protrudes from the tip surface 15e of the rotating shaft 15 toward the orbiting scroll 26. The eccentric shaft 31 is inserted into the boss portion 28.

[0031] The scroll compressor 10 is equipped with a bush 32. The bush 32 is cylindrical. The bush 32 is fitted onto the outer surface of the eccentric shaft 31. The bush 32 is pivotable (swings) around the eccentric shaft 31.

[0032] The scroll compressor 10 is equipped with a balance weight 33. The balance weight 33 is integrated with the bush 32. The balance weight 33 is integrally formed with the bush 32. The balance weight 33 is located inside the peripheral wall 18 of the support housing 13.

[0033] The scroll compressor 10 is equipped with a bearing 34. The bearing 34 is a cylindrical sliding bearing. The bearing 34 is located inside the boss portion 28. The bearing 34 is positioned between the inner circumferential surface of the boss portion 28 and the outer circumferential surface of the bush 32. The bush 32 is rotatably supported by the boss portion 28 via the bearing 34.

[0034] The rotation of the rotating shaft 15 is transmitted to the orbiting scroll 26 via the eccentric shaft 31, bushing 32, and bearing 34. 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 circumferential 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. The orbiting scroll 26 revolves inside the outer circumferential 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.

[0035] The scroll compressor 10 is equipped with an elastic plate 35. The elastic plate 35 is annular in shape. The elastic plate 35 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 35 constantly biases the orbiting scroll 26 toward the stationary scroll 25.

[0036] 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.

[0037] The support housing 13 is connected to the open end face of the peripheral wall 12b of the motor housing 12. The discharge housing 14 is connected to the flange wall 19 of the support housing 13. Thus, the motor housing 12, the support housing 13, and the discharge housing 14 are arranged in this order in the axial direction of the rotating shaft 15. The fixed scroll 25 is sandwiched between the end wall 14a of the discharge housing 14 and the support housing 13. In this way, the fixed scroll 25 is fixed to the housing 11.

[0038] The scroll compressor 10 is equipped with an intake passage 36. The intake passage 36 has a first groove 36a, a first hole 36b, a second groove 36c, and a second hole 36d. The first groove 36a is formed in a part of the inner surface of the peripheral wall 12b of the motor housing 12. The first groove 36a opens at the open end of the peripheral wall 12b. The first hole 36b is formed on the outer circumference of the flange wall 19 of the pivot housing 13. The first hole 36b penetrates the flange wall 19 in the thickness direction. The first hole 36b communicates with the first groove 36a. The second groove 36c is formed in a part of the inner surface of the peripheral wall 14b of the discharge housing 14. The second groove 36c communicates with the first hole 36b. The second hole 36d is formed in the outer surface wall 25c of the fixed scroll 25. The second hole 36d penetrates the outer peripheral wall 25c in the thickness direction. The second hole 36d communicates with the second groove 36c. The second hole 36d communicates with the outermost part of the compression chamber 27.

[0039] The refrigerant gas in the motor chamber 20 passes through the first groove 36a, the first hole 36b, the second groove 36c, and the second hole 36d and is drawn into the compression chamber 27. The refrigerant gas drawn into the compression chamber 27 is compressed within the compression chamber 27 as the volume of the compression chamber 27 decreases due to the orbital motion of the orbiting scroll 26. In this way, the compression mechanism C1 compresses the refrigerant gas drawn into the housing 11. Therefore, the fluid compressed by the compression mechanism C1 includes refrigerant gas and oil.

[0040] The scroll compressor 10 includes a back pressure chamber 37. The back pressure chamber 37 is a space partitioned by the peripheral wall 18 of the support housing 13 and the end face 26e of the orbiting scroll 26. The scroll compressor 10 also includes a communication passage 38. The communication passage 38 connects the back pressure chamber 37 and the suction passage 36. The communication passage 38 is formed, for example, between the support housing 13 and the elastic plate 35.

[0041] The scroll compressor 10 is equipped with 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. The discharge chamber 40 is in communication with the discharge port 25h. Compressed refrigerant gas is discharged into the discharge chamber 40 by the compression mechanism C1. The scroll compressor 10 is also equipped with an oil storage chamber 41. The oil storage chamber 41 is formed in the end wall 14a of the discharge housing 14.

[0042] The scroll compressor 10 is equipped with an oil separation chamber 42. The oil separation chamber 42 is formed inside the discharge housing 14. 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 first end of the outer cylinder 43 is a discharge port 44 for discharging refrigerant gas to the outside. The discharge port 44 communicates with the oil separation chamber 42. The oil storage chamber 41 communicates with the oil separation chamber 42. The scroll compressor 10 is mounted on a vehicle such that the oil storage chamber 41 is positioned vertically below the oil separation chamber 42.

[0043] An inner cylinder 45 is fitted inside the oil separation chamber 42. The axial direction of the inner cylinder 45 coincides with the radial direction of the rotation axis 15. The first end of the inner cylinder 45 communicates with the discharge port 44. The second end of the inner cylinder 45 communicates with the side of the oil separation chamber 42 opposite to the discharge port 44. An inlet hole 46 is formed in the outer cylinder 43. The inlet hole 46 connects the discharge chamber 40 and the oil separation chamber 42. The inlet hole 46 introduces the refrigerant gas discharged from the discharge chamber 40 into the oil separation chamber 42.

[0044] The refrigerant gas, compressed in the compression chamber 27 and discharged into the discharge chamber 40 via the discharge port 25h, is introduced into the oil separation chamber 42 via the inlet hole 46. The refrigerant gas introduced into the oil separation chamber 42 swirls around the inner cylinder 45. This imparts centrifugal force to the oil contained in the refrigerant gas, causing the oil to separate from the refrigerant gas within the oil separation chamber 42. Thus, the oil separation chamber 42 separates the oil contained in the refrigerant gas discharged into the discharge chamber 40.

[0045] The refrigerant gas from which the oil has been separated flows into the inner cylinder 45 and passes through it. The refrigerant gas that has passed through the inner cylinder 45 then flows out through the discharge port 44 to an external refrigerant circuit (not shown). The oil separated from the refrigerant gas in the oil separation chamber 42 is stored in the oil storage chamber 41.

[0046] <High-pressure and low-pressure regions> The discharge chamber 40, the oil storage chamber 41, and the oil separation chamber 42 are at the discharge pressure. Therefore, the discharge chamber 40, the oil storage chamber 41, and the oil separation chamber 42 constitute the high-pressure region 50 within the housing 11, where the pressure is relatively high. Thus, the high-pressure region 50 includes the discharge chamber 40, from which the refrigerant gas compressed by the compression mechanism C1 is discharged. The end wall 14a of the discharge housing 14 is a partition wall that separates the discharge chamber 40, the oil storage chamber 41, and the oil separation chamber 42. Therefore, the end wall 14a of the discharge housing 14 is a partition wall that separates the high-pressure region 50.

[0047] The motor chamber 20 and the intake passage 36 are at intake pressure. Therefore, the pressure in the motor chamber 20 and the intake passage 36 is lower than the discharge pressure. Also, the pressure in the back pressure chamber 37 is an intermediate pressure, higher than the intake pressure and lower than the discharge pressure. Therefore, the back pressure chamber 37, the motor chamber 20, and the intake passage 36 are in a low-pressure region 51, where the pressure is lower than the high-pressure region 50. Thus, the housing 11 has a high-pressure region 50 and a low-pressure region 51.

[0048] <Filter component> As shown in Figure 2, the end wall 14a of the discharge housing 14 has a mounting recess 52. The mounting recess 52 is formed on the end wall 14a of the discharge housing 14 on the surface 14e that partitions the oil storage chamber 41 and is located on the side of the oil storage chamber 41 that is on the fixed scroll 25 side. The mounting recess 52 is circular in shape.

[0049] The scroll compressor 10 is equipped with a filter member 53. The filter member 53 has a hemispherical filter section 54 and an annular mounting section 55. The filter section 54 is configured to allow oil to pass through and to capture foreign matter contained in the oil. The mounting section 55 protrudes outward from the periphery of the filter section 54. The filter member 53 is attached to the end wall 14a of the discharge housing 14 by fitting the mounting section 55 into a mounting recess 52.

[0050] <Fluid passage> The end wall 14a of the discharge housing 14 has a first mounting recess 56 and a second mounting recess 57. The first mounting recess 56 is formed on the bottom surface of the mounting recess 52. The first mounting recess 56 is circular. The second mounting recess 57 is formed on the bottom surface of the first mounting recess 56. The second mounting recess 57 is circular. The axes of the mounting recess 52, the first mounting recess 56, and the second mounting recess 57 coincide. Therefore, the axial directions of the first mounting recess 56 and the second mounting recess 57 coincide.

[0051] The scroll compressor 10 is equipped with an inlet passage 58. The inlet passage 58 connects the inside of the second mounting recess 57 to the back pressure chamber 37. The first end of the inlet passage 58 opens to the bottom surface of the second mounting recess 57. As shown in Figure 1, the second end of the inlet passage 58 passes through the discharge housing 14 and the shaft support housing 13 and communicates with the back pressure chamber 37.

[0052] As shown in Figures 2 and 3, the scroll compressor 10 is equipped with a throttling member 60. The throttling member 60 has a first cylindrical member 61 and a second cylindrical member 62. The first cylindrical member 61 has a first cylindrical portion 63 and a closing portion 64. Therefore, the throttling member 60 has a first cylindrical portion 63. The first cylindrical portion 63 is cylindrical. The closing portion 64 is disc-shaped and closes the opening on the first end side of the first cylindrical portion 63.

[0053] The first cylindrical member 61 has a flow path forming portion 65. Therefore, the throttling member 60 has a flow path forming portion 65. The flow path forming portion 65 is cylindrical. The flow path forming portion 65 extends from the central part of the closure portion 64. The flow path forming portion 65 passes inside the first cylindrical portion 63. The tip of the flow path forming portion 65 protrudes to the outside of the first cylindrical portion 63 through the opening on the second end side of the first cylindrical portion 63. The axis of the flow path forming portion 65 coincides with the axis of the first cylindrical portion 63.

[0054] The second cylindrical member 62 is cylindrical in shape. A portion of the second cylindrical member 62 is located inside the first cylindrical portion 63. Therefore, the second cylindrical member 62 is a second cylindrical portion located inside the first cylindrical portion 63. Consequently, the throttling member 60 has a second cylindrical portion located inside the first cylindrical portion 63. The axis of the second cylindrical member 62 coincides with the axis of the first cylindrical portion 63. A mounting groove 66 is formed on the outer circumferential surface of the portion of the second cylindrical member 62 that protrudes from the first cylindrical portion 63. The mounting groove 66 is annular. A sealing member 67 is mounted in the mounting groove 66. The sealing member 67 is annular in shape.

[0055] The second cylindrical member 62 has a pair of notches 68. Each notch 68 is formed on the first end face 62a, which is the end face of the second cylindrical member 62. Each notch 68 is formed at a position 180 degrees away from the first end face 62a of the second cylindrical member 62 in the circumferential direction. The first end of each notch 68 opens onto the outer circumferential surface of the second cylindrical member 62. The second end of each notch 68 communicates with the inside of the second cylindrical member 62.

[0056] The second cylindrical member 62 is fixed to the first cylindrical member 61 by being press-fitted into the inner circumferential surface of the first cylindrical portion 63. At this time, the flow path forming portion 65 is press-fitted into the inner circumferential surface of the second cylindrical member 62. Therefore, the flow path forming portion 65 is located inside the second cylindrical portion. The tip surface of the flow path forming portion 65 is located inside the second cylindrical member 62.

[0057] The first cylindrical portion 63 of the first cylindrical member 61 is press-fitted into the inner circumferential surface 56a of the first mounting recess 56. The portion of the second cylindrical member 62 that protrudes from the first cylindrical portion 63 is press-fitted into the inner circumferential surface of the second mounting recess 57. As a result, the throttling member 60 is attached to the end wall 14a of the discharge housing 14.

[0058] The first cylindrical portion 63 is positioned inside the first mounting recess 56. In this embodiment, the inner circumferential surface 56a of the first mounting recess 56 functions as an insertion portion into which the first cylindrical portion 63 is positioned. Therefore, the throttling member 60 is attached to the end wall 14a of the discharge housing 14 with the first cylindrical portion 63 positioned inside the inner circumferential surface 56a of the first mounting recess 56, which is an insertion portion provided in the end wall 14a of the discharge housing 14. The axial directions of the first cylindrical portion 63, the second cylindrical member 62, and the inner circumferential surface 56a of the first mounting recess 56 are all the same. In the following description, "the axial directions of the first cylindrical portion 63, the second cylindrical member 62, and the inner circumferential surface 56a of the first mounting recess 56" may be simply referred to as "axial direction X1".

[0059] The sealing member 67 seals the space between the second cylindrical member 62 and the inner circumferential surface of the second mounting recess 57. The inside of the second cylindrical member 62 is in communication with the introduction passage 58. The open end face of the first cylindrical portion 63 is spaced apart from the bottom surface of the first mounting recess 56. Therefore, an annular gap 69 is formed inside the first mounting recess 56 between the open end face of the first cylindrical portion 63 and the bottom surface of the first mounting recess 56.

[0060] A first helical groove 71 is formed on the outer circumferential surface of the first cylindrical portion 63. The first end of the first helical groove 71 opens to the first end face of the first cylindrical portion 63. The second end of the first helical groove 71 opens to the second end face of the first cylindrical portion 63. The first helical groove 71, together with the inner circumferential surface 56a of the first mounting recess 56, defines the first helical passage 72.

[0061] A second helical groove 73 is formed on the outer circumferential surface of the second cylindrical member 62. The second helical groove 73 is formed on the outer circumferential surface of the second cylindrical member 62 in a portion located inside the first cylindrical portion 63. The first end of the second helical groove 73 is located on the outer circumferential surface of the second cylindrical member 62 in a portion that overlaps with the open end surface of the first cylindrical portion 63. The second end of the second helical groove 73 opens into the first end surface 62a of the second cylindrical member 62. The second end of the second helical groove 73 communicates with one of a pair of notches 68. The second helical groove 73, together with the inner circumferential surface of the first cylindrical portion 63, defines the second helical passage 74. The second helical passage 74 is located inside the first helical passage 72. The first helical passage 72 and the second helical passage 74 overlap in a direction perpendicular to the axial direction X1.

[0062] A third helical groove 75 is formed on the outer circumferential surface of the flow channel forming section 65. The first end of the third helical groove 75 is located at the base end of the flow channel forming section 65. The second end of the third helical groove 75 opens to the front end surface of the flow channel forming section 65. The third helical groove 75, together with the inner circumferential surface of the second cylindrical member 62, defines the third helical passage 76. The third helical passage 76 is located inside the second helical passage 74. The third helical passage 76 overlaps the first helical passage 72 and the second helical passage 74 in a direction perpendicular to the axial direction X1.

[0063] The first end of the first helical passage 72 communicates with the oil storage chamber 41 via the inside of the mounting recess 52. The second end of the first helical passage 72 communicates with the gap 69. The first end of the second helical passage 74 communicates with the gap 69. Therefore, the second helical passage 74 communicates with the first helical passage 72 via the gap 69. The second end of the second helical passage 74 communicates with one of the pair of notches 68. The first end of the third helical passage 76 communicates with one of the pair of notches 68. Therefore, the third helical passage 76 communicates with the second helical passage 74 via one of the pair of notches 68. Thus, the notches 68 connect the second helical passage 74 and the third helical passage 76. The second end of the third helical passage 76 communicates with the introduction passage 58 via the inside of the second cylindrical member 62.

[0064] The first helical passage 72, the gap 69, the second helical passage 74, the notch 68, the third helical passage 76, and the introduction passage 58 form a fluid passage 77. The fluid passage 77 connects the oil storage chamber 41 and the back pressure chamber 37. Therefore, the fluid passage 77 connects the high-pressure region 50 and the low-pressure region 51. The fluid passage 77 then guides the oil stored in the oil storage chamber 41 to the back pressure chamber 37. Thus, the fluid passage 77 guides the oil, which is the fluid in the high-pressure region 50, to the low-pressure region 51. In this way, the scroll compressor 10 is equipped with a fluid passage 77 that guides the fluid in the high-pressure region 50 to the low-pressure region 51.

[0065] The oil, guided from the oil storage chamber 41 to the back pressure chamber 37 via the fluid passage 77, is depressurized as it flows through the first helical passage 72, the second helical passage 74, and the third helical passage 76. Therefore, the first helical passage 72, the second helical passage 74, and the third helical passage 76 constitute a throttling section provided in the fluid passage 77. Thus, each of the first helical passage 72, the second helical passage 74, and the third helical passage 76 constitutes a part of the throttling section. In this way, the throttling member 60 forms a throttling section provided in the fluid passage 77.

[0066] [Effect of the Embodiment] Next, the operation of the embodiment will be described. The oil stored in the oil storage chamber 41 passes through the filter section 54. The filter section 54 captures foreign matter contained in the oil. After foreign matter has been removed by passing through the filter section 54, the oil is introduced into the back pressure chamber 37 via the first helical passage 72, the gap 69, the second helical passage 74, the notch 68, the third helical passage 76, and the introduction passage 58. The oil is depressurized as it passes through the first helical passage 72, the second helical passage 74, and the third helical passage 76. The pressure of the oil introduced into the back pressure chamber 37 contributes as back pressure that biases the orbiting scroll 26 toward the stationary scroll 25. The oil introduced into the back pressure chamber 37 flows into the communication passage 38. The oil that flows into the communication passage 38 is depressurized as it passes through the communication passage 38. The oil that has passed through the communication passage 38 is then recirculated into the suction passage 36.

[0067] [Effects of the Embodiment] In this embodiment, the following effects can be obtained. (1) The oil guided from the oil storage chamber 41 to the back pressure chamber 37 via the fluid passage 77 is depressurized as it flows through the first helical passage 72 and the second helical passage 74. Therefore, compared to, for example, the case where the throttling section consists only of the first helical passage 72 or the second helical passage 74, the pressure of the oil guided from the oil storage chamber 41 to the back pressure chamber 37 via the fluid passage 77 can be efficiently reduced. Also, the second helical passage 74 is located inside the first helical passage 72. Therefore, even if the throttling member 60 is configured to partition the first helical passage 72 and the second helical passage 74, it is possible to suppress an increase in the size of the housing 11 in the axial direction X1. As a result, the scroll compressor 10 can be miniaturized while efficiently reducing the pressure of the oil guided from the oil storage chamber 41 to the back pressure chamber 37 via the fluid passage 77.

[0068] (2) The oil guided from the oil storage chamber 41 to the back pressure chamber 37 via the fluid passage 77 is depressurized not only in the first helical passage 72 and the second helical passage 74, but also when it flows through the third helical passage 76. Therefore, the pressure of the oil guided from the oil storage chamber 41 to the back pressure chamber 37 via the fluid passage 77 can be reduced even more efficiently. In addition, the third helical passage 76 is located inside the second helical passage 74. Therefore, even if the throttling member 60 is configured to partition the third helical passage 76 in addition to the first helical passage 72 and the second helical passage 74, it is possible to suppress an increase in the size of the housing 11 in the axial direction X1. As a result, the scroll compressor 10 can be miniaturized while further reducing the pressure of the oil guided from the oil storage chamber 41 to the back pressure chamber 37 via the fluid passage 77.

[0069] (3) A notch 68 is formed in the first end face 62a of the second cylindrical member 62. This makes it easier to secure the respective lengths of the second helical passage 74 and the third helical passage 76 compared to a configuration in which the second helical passage 74 and the third helical passage 76 are connected by a hole that penetrates the second cylindrical member 62.

[0070] [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.

[0071] ○ As shown in Figures 4 and 5, the throttling member 60 may have a flow path forming portion 65 that is separate from the first cylindrical member 61. The flow path forming portion 65 is fixed to the second cylindrical member 62 by being press-fitted into the inner circumferential surface of the second cylindrical member 62. In the embodiments shown in Figures 4 and 5, the end face of the second cylindrical member 62 on the side of the closure portion 64 is in contact with the closure portion 64, but this is not limited to this, and the end face of the second cylindrical member 62 on the side of the closure portion 64 may be separated from the closure portion 64. In short, the flow path forming portion 65 only needs to be columnar and positioned inside the second cylindrical member 62. With this configuration, machinability can be improved compared to a configuration in which the first cylindrical member 61 has a flow path forming portion 65.

[0072] ○ In this embodiment, the first helical groove 71 may not be formed on the outer circumferential surface of the first cylindrical portion 63, but may be formed on the inner circumferential surface 56a of the first mounting recess 56. Alternatively, the first helical groove 71 may be formed on both the outer circumferential surface of the first cylindrical portion 63 and the inner circumferential surface 56a of the first mounting recess 56, extending in communication with each other. In short, it is sufficient that the first helical groove 71 defining the first helical passage 72 is formed on at least one of the inner circumferential surface 56a of the first mounting recess 56 and the outer circumferential surface of the first cylindrical portion 63.

[0073] ○ In this embodiment, the diaphragm member 60 may further have an insertion portion that covers the first cylindrical portion 63. The diaphragm member 60 may be attached to the end wall 14a of the discharge housing 14 with the first cylindrical portion 63 positioned inside the insertion portion. The first cylindrical member 61 is fixed to the insertion portion by the first cylindrical portion 63 being press-fitted into the inner circumferential surface of the insertion portion. The diaphragm member 60 may be attached to the end wall 14a of the discharge housing 14 by the insertion portion being press-fitted into the inner circumferential surface 56a of the first mounting recess 56. Thus, the diaphragm member 60 may be attached to the end wall 14a of the discharge housing 14 with the first cylindrical portion 63 positioned inside the insertion portion provided in the end wall 14a of the discharge housing 14. In this case, it is sufficient that a first helical groove 71 defining the first helical passage 72 is formed on at least one of the inner circumferential surface of the insertion portion and the outer circumferential surface of the first cylindrical portion 63.

[0074] ○ In this embodiment, the second helical groove 73 may not be formed on the outer circumferential surface of the second cylindrical member 62, but may be formed on the inner circumferential surface of the first cylindrical portion 63. Alternatively, the second helical groove 73 may be formed on both the outer circumferential surface of the second cylindrical member 62 and the inner circumferential surface of the first cylindrical portion 63, extending in communication with each other. In short, it is sufficient that the second helical groove 73 defining the second helical passage 74 is formed on at least one of the inner circumferential surface of the first cylindrical portion 63 and the outer circumferential surface of the second cylindrical member 62.

[0075] ○ In this embodiment, the third helical groove 75 may not be formed on the outer circumferential surface of the flow path forming portion 65, but may be formed on the inner circumferential surface of the second cylindrical member 62. Alternatively, the third helical groove 75 may be formed on both the outer circumferential surface of the flow path forming portion 65 and the inner circumferential surface of the second cylindrical member 62, extending in communication with each other. In short, it is sufficient that the third helical groove 75 defining the third helical passage 76 is formed on at least one of the inner circumferential surface of the second cylindrical member 62 and the outer circumferential surface of the flow path forming portion 65.

[0076] ○ In this embodiment, the throttling member 60 may not have a flow path forming portion 65. In short, the throttling member 60 may not have a configuration that partitions the third helical passage 76.

[0077] ○ In this embodiment, the fluid passage 77 may be configured such that oil flows in the order of, for example, the third helical passage 76, the second helical passage 74, and the first helical passage 72. In short, the order in which the oil passes through the first helical passage 72, the second helical passage 74, and the third helical passage 76 may be changed as appropriate.

[0078] ○ In this embodiment, the second helical passage 74 and the third helical passage 76 may be connected, for example, by a hole that penetrates the second cylindrical member 62. ○ In this embodiment, the scroll compressor 10 may be configured without a filter member 53.

[0079] ○ In this embodiment, the fluid passage 77 connected the oil storage chamber 41 and the back pressure chamber 37, but it is not limited to this, and for example, it may connect the oil storage chamber 41 and the suction passage 36. Thus, the fluid passage 77 may be configured to guide the oil in the oil storage chamber 41 to the suction passage 36. In short, the fluid passage 77 only needs to be configured to guide the fluid in the high-pressure region 50 to the low-pressure region 51. Therefore, the fluid passage 77 may be configured to guide, for example, the refrigerant gas discharged into the discharge chamber 40 to the back pressure chamber 37 or the suction passage 36. In this case, for example, the throttling member 60 may be attached to the fixed substrate 25a of the fixed scroll 25. Thus, the fixed substrate 25a is a partition wall that divides the high-pressure region 50, and the fixed scroll 25 constitutes a part of the housing 11.

[0080] ○ In this embodiment, the scroll compressor 10 does not have to be driven by a motor 22, but may be driven by, for example, a vehicle engine.

[0081] ○ In this embodiment, the scroll compressor 10 was used in a vehicle air conditioning system, but it is not limited to this. In short, the scroll compressor 10 can be any device that compresses refrigerant gas, and the application of the scroll compressor 10 can be changed as appropriate.

[0082] ○ In this embodiment, carbon dioxide was used as the refrigerant gas, but the invention is not limited to this, and for example, fluorocarbons (CFCs) may be used as the refrigerant gas. ○ In this embodiment, the object to be compressed by the scroll compressor 10 is not limited to a refrigerant gas, but may be a fluid such as air.

[0083] ○ 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. [Explanation of symbols]

[0084] 10...Scroll compressor, which is the compressor; 11...Housing; 14a...End wall, which is the partition wall; 40...Discharge chamber; 50...High-pressure region; 51...Low-pressure region; 56a...Inner circumferential surface as the insertion part; 60...Throscopy member; 62...Second cylindrical member, which is the second cylindrical part; 62a...First end face, which is the end face; 63...First cylindrical part; 65...Flow path forming part; 68...Notch; 71...First helical groove; 72...First helical passage forming the throttling section; 73...Second helical groove; 74...Second helical passage forming the throttling section; 75...Third helical groove; 76...Third helical passage forming the throttling section; 77...Fluid passage; C1...Compression mechanism.

Claims

1. A compression mechanism that compresses fluids, A housing having a high-pressure region including a discharge chamber from which the fluid compressed by the compression mechanism is discharged, and a low-pressure region where the pressure is lower than that of the high-pressure region, A fluid passage that guides the fluid in the high-pressure region to the low-pressure region, A compressor comprising a throttling member that forms a throttling portion in the fluid passage, The housing has partition walls that demarcate the high-pressure region, The aforementioned throttling member is The first cylindrical section, It has a second cylindrical portion disposed inside the first cylindrical portion, The restricting member is attached to the partition wall with the first cylindrical portion positioned inside the insertion portion provided in the partition wall. At least one of the inner circumferential surface of the insertion portion and the outer circumferential surface of the first cylindrical portion is formed with a first helical groove that defines a first helical passage communicating with the high-pressure region. At least one of the inner circumferential surface of the first cylindrical portion and the outer circumferential surface of the second cylindrical portion is formed with a second helical groove that communicates with the first helical passage and demarcates the second helical passage located inside the first helical passage. A compressor characterized in that the first helical passage and the second helical passage constitute the throttling section.

2. The throttling member has a columnar flow path forming portion located inside the second cylindrical portion, At least one of the inner circumferential surface of the second cylindrical portion and the outer circumferential surface of the flow path forming portion has a third helical groove formed therein that communicates with the second helical passage and demarcates a third helical passage located inside the second helical passage. The compressor according to claim 1, characterized in that the third spiral passage constitutes a part of the throttling section.

3. The compressor according to claim 2, characterized in that a notch is formed in the end face of the second cylindrical portion, connecting the second helical passage and the third helical passage.

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